POSITIVE DISPLACEMENT HEAT MACHINES WITH SCAVENGING
20200284148 ยท 2020-09-10
Inventors
Cpc classification
F02B53/04
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01C1/348
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F02B2075/025
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F04B35/002
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01C1/22
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01B7/14
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F02B75/28
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01B7/20
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
International classification
F01B7/20
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01C21/10
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F01C1/348
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
F04B35/00
MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
Abstract
A high efficiency positive Displacement Heat Machines, for applications such as engines with external heating, Internal Combustion Engines with reduced dirty emissions, heat pumps for ecology clear coolers or heaters, working with air from any source of mechanical energy, thermal processes with approximately constant pressure using an external High and Low Pressure Chambers (HPC and LPC that may be the Atmosphere) that are connecting to a Working Chamber (WC) correspondingly at the end of compression and expansion stages. The disclosed engines and heat pumps operate with displacing at least a part of the WF between said WC and HPC, without changing volume of the WC; with Pulse Pause Modulation of crankshaft speed; with remote expander for engine or compressor for heat pump. The expander or compressor are arranged without transferring mechanical work from another parts of the heat machine. The expander is used as power output from the engine, and the compressor is used as power input to the heat pump.
Claims
1. Method of operating a Positive Displacement Heat Machine (PDHM), the PDHM provided with at least a single Working Chamber (WC), arranged to change its volume during at least a part of a thermodynamic cycle and to transfer mechanical energy to/from a compressible Working Fluid (WF); the thermodynamic cycle including compression and expansion entailing Lower Pressure (LP) of the WF; the thermodynamic cycle further including Higher Pressure (HP), HP>LP; the thermodynamic cycle also including a Lowest Temperature (LT) of the WF; the thermodynamic cycle further including a High Temperature (HT), HT>LT; the PDHM is further provided with at least a single Low Pressure Chamber (LPC, 40), containing the WF with said LP; the LPC may be the atmosphere, otherwise the LPC is provided with means, arranged for thermal transfer between the LPC and an external medium; the LPC is provided with an LPC Input Part (LPCIP) for the WF and an LPC Output Part (LPCOP) for the WF with changed temperature; at least a single Low Pressure Input Mean (WCLPIM, 20) is provided between the WC and the LPCOP, and at least a single Low Pressure Output Mean (WCLPOM, 21) is provided between the WC and LPCIP, both arranged as controllable openings; the PDHM providing with at least a single High Pressure Chamber (HPC, 8), that contains the WF with said pressure HP; if said PDHM is the heat pump, the HPC 8 arranged for cooling the WF by heat transfer to external medium; at least a single High Pressure Controllable Opening (WCHPCO, 18) is provided between the WC and HPC; the thermodynamic cycle comprising: 1.1. moving at least a part of the WF from said WC to said LPCIP across said WCLPOM 21; 1.2. moving at least a part of the WF from said LPCOP to said WC across said WCLPIM 20; 1.3. changing a temperature of the WF in said LPC 40, and/or in said WC, and/or in said HPC 8; 1.4. compressing the WF in said WC with closed WCLPOM 21, WCLPIM 20, WCHPCO 18; 1.5. moving the WF across said WCHPCO 18; 1.6. expanding the WF inside said WC with closed WCHPCO 18; Characterized in that: during step 1.5, after ending compression in said WC, and when pressure in said WC is close to pressure in said HPC 8, opening said WCHPCO 18 and displacing at least a part of the WF between said WC and HPC 8, such that displacement of said part is not caused by changing the volume of the WC.
2. The method of claim 1, wherein at least a part of compressed WF is displaced between said WC and HPC 8, by the operations selected from the group, consisting of: a. changing at least a single mechanical volume; and whenever changing a volume of the WC (Vwc), displacing only a part of the WF by changing said Vwc; b. changing volume of any WF; c. using kinetic energy of any WF; d. changing pressure of any WF; e. any combination of two or more of the above; where several combinations are selected from the group, consisting of: 2.1. Combination of a and b for the Internal Heating Engine (IHE), further comprising: according to a, displacing a part of WF from said WC to HPC 8 by diminishing said Vwc, while said WCHPCO 18 is open; according to b, displacing additional part of the WF from said WC to HPC 8 by heating, thereby expanding a part of the WF inside said WC, where the heating part is far from said WCHPCO 18, and said additional part is closer to said WCHPCO 18; 2.2. according to c for the PDHM, using Inertial SCavenging (ISC), thereby initiating moving a part of the WF from said WC and initiating moving another part of the WF to said WC by any of the operations a, b, d, and continuing this moving due to kinetic energy of the WF and, optionally, due to kinetic energy of a scavenging means, if used; providing in the WC with a High Pressure Input Mean (WCHPIM 41), arranged as a controllable opening from the HPC 8 to the WC; initiating moving of the WF across said WCHPCO 18 and WCHPIM 41 or one of them, then opening WCHPIM 41 and WCHPCO 18 for ISC; 2.3. for the PDHM, scavenging across said WC by a blower, the blower may be based on the positive displacement principle, according to a, or by using kinetic energy of any part of the WF according to c, or using both a and c; 2.4. according to a, scavenging in the PDHM from and to said WC at least by changing an external volume, that is not volume of the WC; then according to c using ISC, 2.5. combination of b and c for the PDHM; separating the HPC 8 to two parts with a Single Direction Valve (HPSDV, 47) between them, and when the HPSDV 47 is closed, but said WCHPIM 41 and WCHPCO 18 are open, changing the ratio between temperatures of the WF in said two parts, to initiate a flow of the WF between said two parts across said WC due to changing volume of the WF according to b; according to c, using ISC to continue the flow across said WC and said two parts while said HPSDV 47 is open; 2.6. combination of d and b and c for the PDHM; separating the HPC 8 to two parts with said HPSDV 47, and when said HPSDV 47, WCHPIM 41, and WCHPCO 18 are closed, changing a ratio between temperatures of the WF in said two parts, so changing a ratio between pressures to be different from 1, this process take place with constant volume according to d; open said WCHPIM 41 and WCHPCO 18, initiating a flow of the WF between said two parts of the HPC across said WC according to d; when the ratio between pressures in said two parts of the HPC return approximately to 1, continue changing the ratio between temperatures with approximately constant pressure according to b and opening said HPSDV 47, whereby using ISC according to c, and so continue the flow across said WC, and said two parts of the HPC, and said HPSDV 47; to end scavenging, closing said HPSDV 47, WCHPIM 41 and WCHPCO 18; 2.7. combination of d and c for the PDHM; separating the HPC to two parts with said HPSDV 47, and when said HPSDV 47, and WCHPIM 41, and WCHPCO 18 are closed, changing a ratio between pressures of WF in these parts; opening said WCHPIM 41 and WCHPCO 18, initiating flow of the WF between said two parts across said WC according to d; when the ratio between pressures in said two parts is close to 1, opening said HPSDV 47, whereby using ISC according to c, across said WC, said two parts and said HPSDV 47; 2.8. combination of a, b, c for the ICE; according to a, after ending compression, opening said WCHPCO 18 and by diminishing said Vwc from Vec to Vmin, displacing at least a part of the WF to the HPC 8; according to b, additionally displacing to the HPC 8 with combustion inside the WC; according to c, during increasing Vwc from Vmin to a Begin Expansion Volume (Vbe), displacing another part of the WF from said HPC 8 to WC, using inertial flow of the WF inside said HPC 8, to avoid mixing between input flow to said WC and output gas from said WC; heating a part of the WF inside said HPC 8 before inputting this part to the WC; closing said WCHPCO 18, and then, optionally initiating additional combustion in the WC.
3. The method of claim 2, for the Internal Combustion Engine (ICE) of oscillating piston type with crankshaft, while using atmosphere as the LPC 40, further comprising: further providing in the HPC 8 of the heat machine, an input mean, named HPCIM 26, that includes a channel between said WCHPCO 18 and said HPC 8, the channel arranged with gradual increase in a transverse section from said WCHPCO 18 to said HPC 8; further providing in the heat machine, a sensor, named WCHPCIMDPS 28, arranged to measure a differential pressure between said WC and said HPCIM 26; after end compression, when a pressures in said WC and said HPCIM 26 are approximately equivalent, opening said WCHPCO 18 and displacing a part of the WF from said WC to HPCIM 26 by diminishing said Vwc; displacing an additional part of the WF from said WC to said HPCIM 26 by injection and combustion fuel into a part of the WF that is far from said WCHPCO 18, this part named a heating part of the WF, and due to heat expansion of said heating part, pushing said additional part, that is near said WCHPCO 18, into said HPCIM 26; further providing a temperature sensor inside said HPCIM 26, this sensor HPCIMTS 27 is arranged to measure a temperature of the WF in said HPCIM 26; regulating at least a time point when combustion begins in said heating part, this time point named Time Begin Heating (TimeBH), such that said temperature in said HPCIM 26 will be sufficiency smaller than the temperature of said heating part when combustion ends, with calculating or measuring this temperature by any way; after displacing a desired part of the WF from said WC, closing said WCHPCO 18 to begin expansion; selecting a working method from the group, consisting of: a. selecting said Vec approximately equivalent to Vmin, and displacing said WF mostly by heat expansion of said heating part, whereby will be near zero moving of said piston under pressure HP; b. selecting Vec>Vmin, and displacing the WF mostly by diminishing the Vwc, performing combustion mostly when said WCHPCO 18 is closed, whereby part of the WF having temperature slightly exceeds Tec, will be displaced to said HPC 8; c. compromises between cases a and b, with Vec>Vmin and begin combustion before closing said WCHPCO 18; d. ending combustion after closing said WCHPCO 18, whereby summed work of the cycle in said WC may be more than zero, even if Vbe=<Vec; e. adjusting Vbe>Vec; f. combination of d and e; g. selecting said Volumetric Compression Ratio (VCR) such that Pec<HP, then heating WF in approximately constant volume Vec, and when a pressure in said WC increases to HP or exceeds HP, opening said WCHPCO 18; h. any combination from a, b, d, e, g; further providing an expander 19, with an input from said HPC 8, and an output to said LPC 40 and arranging a volumetric ratio of the expander 19 such that pressure at the end of expanding in the expander 19 will be approximately equivalent to said LP; using the expander 19 as a source for at least a part of output power of the engine, while regulating the expander according to demands of a load; the expander is selected from the group, consisting of: 3.1. the expander 19 without combustion in it; 3.2. the expander 19 with combustion in it; 3.3. the expander 19 with injection and fuel combustion, to maintain approximately constant temperature during at least a part of expansion; further providing an Expander Input Heater (EIH) as a part of the HPC 8, to heat the WF that goes to the expander 19, where the EIH is selected from the group, consisting of: 3.4. the EIH including a heat exchanger 23 for heating the WF from output gas of the expander; 3.5. the EIH including a heat exchanger for heating the WF from output gas of the WC; 3.6. the EIH including a heat exchanger for heating the WF from external source; 3.7. the EIH including a part with fuel combustion inside the WF, preferably the part arranged with at least two envelopes, with combustion in internal envelope and surrounding volume connected to a part of the HPC 8 with relatively smaller temperature of the WF, whereby to diminish loss of heat; 3.8. any combination of 3.4-3.7; further providing in the heat machine a pressure sensor HPCPS 32, arranged to react to said HP in said HPC 8; for further regulating a ratio between throughputs of the expander 19 and the WC, with regulation of a cycle speed of the WC according to feedback from said HPCPS 32, such that pressure in said HPC 8 will be approximately equivalent to desired HP; further providing in the heat machine a pressure sensor WCLPCDPS 33, for measuring a differential pressure between said WC and LPC 40; controlling a time for ending closing said WCHPCO 18, while using feedback from the WCLPCDPS 33, such that at expansion to said Vee, pressure in said WC will not be smaller than the LP in said LPCIP; further providing in the heat machine a WCLPOM 21, arranged as a controllable opening from the WC to the LPCIP, and an WCLPIM 20, arranged as a controllable opening from the LPCOP to the WC; opening the WCLPOM 21 when expansion of the WC reaches Vee, Pee, with Pee>=LP, and when pressure inside the WC diminish to LP, opening WCLPIM 20, whereby to initiate ISC between the WC and LPC 40; optionally, providing a blower 9LP, arranged for scavenging between WC and LPC 40.
4. The method of claim 2, for the External Heating Engine (EHE), initiating ISC by changing the volume of the WC (Vwc); further providing the following means: WCHPCO 18, WCHPIM 41, HPCIM 26, WCHPCIMDPS 28, expander 19, HPCPS 32, WCLPCDPS 33, WCLPOM 21, WCLPIM 20; further providing in the IPC 8 of the heat machine an output mean HPCOM 44, that includes a channel between the IPC 8 and the WCHPIM 41, said channel arranged with gradually decreasing transverse section from said HPC 8 to WCHPIM 41, whereby to diminish loss of kinetic energy of the WF; further providing in the heat machine, a sensor WCHPCOMDPS 43, arranged to measure differential pressure between said WC and HPCOM 44; after ending compression, when the pressure in said WC is approximately equivalent to pressure in said HPCIM 26, opening said WCHPCO 18 and continuing diminishing said Vwc according to signal from said WCHPCIMDPS 28, whereby initiating flow of the WF from said WCHPCO 18 to said HPCIM 26; when pressure in the WC will be approximately the same or smaller than the pressure in said HPCOM 44, begin opening said WCHPIM 41 according to signal from said WCHPCOMDPS 43, whereby to begin ISC; ending closing said WCHPIM 41 and WCHPCO 18 when said Vwc will be approximately equivalent to said Vbe; further regulating a ratio between throughputs of the expander 19 and the WC, with regulation of a cycle speed of the WC according to feedback from said HPCPS 32, such that the pressure in said IPC 8 will be approximately equivalent to desired HP; further controlling a time for closing said WCHPCO 18 using feedback from the WCLPCDPS 33, such that after expansion to said Vee, pressure Pee in the WC will exceed the LP in said LPCIP; opening the WCLPOM 21 after expansion the WC to said Vee, Pee>LP, and when pressure inside the WC diminish to LP, opening WCLPIM 20, whereby initiating ISC between the WC and LPC 40; optionally, providing a blower for scavenging between WC and LPC 40.
5. The method of claim 2, for said External Combustion Engine (ECE), further providing WCHPCO 18, WCHPIM 41, HPCIM 26, WCHPCIMDPS 28, expander 19, HPCPS 32, WCLPCDPS 33, WCLPOM 21, WCLPIM 20, HPCOM 44, WCHPCOMDPS 43; further providing in the IPC 8 of the heat machine a Single Direction Valve (HPSDV, 47), for separating the IPC 8 to an input part (HPCIP), that includes said HPCIM 26, and an output part (HPCOP), that includes said HPCOM 44, the HPSDV 47 arranged to make directional flow of the WF inside the IPC 8 across said HPSDV 47 from said HPCIP to HPCOP, with a small pressure drop dP; directly controlling the HPSDV 47 by the dP, or by a driver, activated by a differential pressure sensor, for measuring the dP; after ending compression, begin opening said WCHPCO 18 and WCHPIM 41 according to signals from said WCHPCIMDPS 28 and WCHPCOMDPS 43; at the same time or a-little before that, opening said WCHPIM 41, to begin combustion in a part of the WF inside HPCOP, being near HPSDV 47, and pushing a part of the WF, heated in previously cycle in said HPCOP, to said WC across said WCHPIM 41, and and pushing the WF from said WC across said WCHPCO 18 to said HPCIP; if increasing of the heating volume of the WF is smaller than volume that must be scavenged, using this increasing to initiate ISC, which begins when said HPSDV 47 is open, with circulation across a closed loop including said HPSDV 47, HPCOP, HPCOM 44, WCHPIM 41, WC, WCHPCO 18, HPCIM 26, HPCIP; closing said WCHPIM 41, WCHPCO 18 to end scavenging; further controlling a time for closing said WCHPIM 41, WCHPCO 18, using feedback from said WCLPCDPS 33, such that after expansion to said Vee, pressure in said WC, Pee, will exceed said LP in said LPCIP; regulating a ratio between throughputs of said expander and said WC, with regulating a cycle speed of said WC according to feedback from said HPCPS 32, such that pressure in said IPC 8 will be approximately equivalent to the desired HP; opening the WCLPOM 21 after expansion the WC to said Vee, Pee>LP, and when pressure in said WC diminish to said LP, opening said WCLPIM 20, whereby to initiate ISC between said WC and LPC 40; optionally, providing a blower, arranged for scavenging between said WC and LPC 40.
6. The method of claim 2, for the EHE, with scavenging at least by changing of an external volume that is not volume of the WC, further providing said WCHPCO 18, WCHPIM 41, expander 19, HPCIM 26, HPCIMTS 27, HPCPS 32, HPCOM 44, WCHPCOMDPS 43, HPSDV 47, HPCIP, HPCOP; using the expander 19 of positive displacement type, the input of which is connected between said HPCIP and HPSDV 47; further providing phase difference sensors, arranged to detect difference between cycle phases of said WC and expander 19; performing synchronization between cycles of said WC and said expander 19, using signals from said HPCPS 32 and from said phase difference sensors, such that pressure in said HPC 8 will be approximately as desired, and after ending compression in said WC, at least a part of an input stroke of said expander 19 occurs; after ending compression in said WC, opening said WCHPCO 18 and WCHPIM 41, initiating scavenging flow of said WF from said HPCOP across said HPCOM 44, WCHPIM 41, WC, WCHPCO 18, HPCIM 26, HPCIP; adjusting the optimal scavenging duration, that take place when temperature T27, measured by said HPCIMTS 27, exceeds the temperature at end compression Tec, calculating Tec for appropriate adiabatic process which begins compression temperature Tbc; to increase the scavenging duration, caused by said expander 19, and so increasing T27, using Inertial Scavenging ISC, with opening said HPSDV 47 and circulation said WF across loop including said HPSDV 47, HPCOP, HPCOM 44, WCHPIM 41, WC, WCHPCO 18, HPCIM 26, HPCIP; closing said WCHPIM 41, WCHPCO 18 to end scavenging.
7. The method of claim 2, for the heat pump, with scavenging at least by changing of an external volume, that is not volume of the WC; the HPC 8 arranged for cooling the WF by a heat transfer to the external medium; further providing said WCHPCO 18, WCHPIM 41, HPCIM 26, HPCIMTS 27, HPCPS 32, HPCOM 44, WCHPCOMDPS 43, HPSDV 47, HPCIP, HPCOP; further providing a compressor 7 of positive displacement type, with input from said LPC 40, output to said HPC 8 and a pressure ratio approximately equivalent to HP/LP; using the compressor 7 as a receiver for at least a part of the input power of the heat pump; further providing additional heat exchanger 53 arranged for cooling the WF from output of the compressor 7, connecting the output of this heat exchanger 53 to said HPCOP, between said HPSDV 47 and HPCOM 44; further providing phase difference sensors, arranged to detect difference between cycle phases of said WC and compressor 7; performing further synchronization between cycles of said WC and said compressor, using signals from said HPCPS 32 and said phase difference sensors, such that pressure in said HPC 8 will be approximately as desired, and after ending compression in said WC, at least a part of an output stroke of said compressor 7 occurs; after ending compression in said WC, opening said WCHPCO 18 and WCHPIM 41, so at least during a part of said output stroke, and when said HPSDV 47 is closed, moving at least a part of said WF from said compressor 7 to said HPCOP, and moving a part of the WF across said HPCOM 44, WCHPIM 41, WC, WCHPCO 18, HPCIM 26, to said HPCIP; adjusting the optimal scavenging duration, that take place when said temperature T27, measured by said HPCIMTS 27, will be a-little smaller than temperature at end compression Tec; calculating Tec for appropriate adiabatic process with begin compression temperature Tbc; using Inertial Scavenging (ISC), with opening said HPSDV 47 and circulation said WF across loop including said HPSDV 7, HPCOP, HPCOM 44, WCHPIM 41, WC, WCHPCO 18, HPCIM 26, HPCIP, to increase the scavenging duration and diminish said T27; closing said WCHPIM 41, WCHPCO 18 to end scavenging.
8. The method of claim 2, for a heat engine, with scavenging between said WC and HPC 8 by a blower 9HP, and scavenging between said WC and LPC 40 by a blower 9LP, each blower is arranged as a rotating mean, capable of working as a turbine or as a compressor according to the difference of pressure between input and output of said mean, said mean connected to electrical machine that works as electrical generator or electrical motor and connected to an electrical accumulator across electrical controller; further providing said LPCIP, LPCOP, WCHPCO 18, WCLPOM 21, WCLPIM 20, WCHPIM 41, expander 19, HPCIM 26, WCHPCIMDPS 28, WCLPCDPS 33, HPCPS 32, WCHPCOMDPS 43; placing blower 9HP after the WCHPCO 18 placing blower 9LP between the WCLPOM 21 and LPCIP; when according to signal from the WCHPCIMDPS 28, pressure in the WC will be no smaller than pressure in the HPCIM 26, opening the WCHPCO 18; then when according to signal from the WCHPCOMDPS 43, pressure in the WC will be no more than pressure in the HPCOM 44, opening the WCHPIM 41, whereby scavenging by said blower 9HP; when according to signal from the WCLPCDPS 33, pressure in the WC will be no smaller than pressure in the LPCIP, opening the WCLPOM 21; then when according to signal from the WCLPCDPS 33, pressure in the WC will be no more than pressure in said LPCOP, opening the WCLPIM 20, whereby performing scavenging by said blower 9LP; defining difference dLP between pressures in said LPCOP and LPCIP by experiment, and using the dLP for fine controlling of said WCLPOM 21 and WCLPIM 20; further matching between throughputs of said WC and said expander 19, using signal from said HPCPS 32, so that pressure in said HPC 8 will be approximately as desired.
9. Oscillating piston type Positive Displacement Heat Machine (PDHM), with at least one cylinder and at least one piston, oscillating in said cylinder between two Dead Points (DPs) at which said piston changes direction, the DP at a High Pressure level HPDP, and the DP at a Low Pressure level LPDP; the PDHM include means, for converting linear movement of said piston to rotation of at least a single mean, named a crankshaft, and vice versa, to convert rotation of said crankshaft to linear movement of said piston; characterized in that is further comprises: at least one: Rotating position and Speed Sensor (RSS), arranged to measure a rotation angle and a rotation speed of the crankshaft; Energy Source (ES), arranged to send regulated energy to said piston and other Moving Parts (MP), connected to it and to said crankshaft; Energy Receiver (ER), arranged to receive a regulated energy from said MP; Kinetic Energy Controller (KEC), arranged for regulating a kinetic energy of said MP, such that the kinetic energy near the same type DP is changed between two cycles approximately to a desired value, named Acceleration Between Cycles (ABC), while using for this regulation said ES, ER and feedback from said RSS, said regulation include possibility for reducing the rotation speed approximately to zero at least near one of said DP; Fixation of Crankshaft (FC), arranged as a mean to fixate the crankshaft near at least one of said DP if the rotation speed near this DP is approximately zero; Initiator of Crankshaft Moving (ICM), arranged as a controllable energy source to initiate rotation of the crankshaft, the ICM is controllable by said KEC; any of said RSS, ES, ER, KEC, FC, ICM may be combined with any other from them or arranged with combined functions of them and may be any type; the improvement for possibility for working with Pulse Pause Modulation (PPM) of the crankshaft speed.
10. An engine according to claim 9, further comprising: a Hydraulic Accumulator (HA) with separate changeable volumes for a liquid and for a compressed gas, with the same high pressure and being inside a common envelope, arranged to stand against this high pressure; a Low Pressure Liquid Volume (LPLV); a Hydraulic Motor Pump (HMP), connected between said HA and LPLV, arranged for driving a vehicle or another load and to push the liquid to said HA, whereby to restore energy of the vehicle; a buffer 51, arranged as a combination of a First Energy Source and a First Energy Receiver, the buffer arranged to accumulate at least a part of energy of a working stroke and to return said part to a compression stroke of said ICE, said buffer selected from the group, consisting of: a. a hydraulic cylinder, connected to a second Hydraulic Accumulator; b. a pneumatic cylinder, connected to a pneumatic buffer; c. a spring; d. an electrical accumulator, controller and electrical machine, arranged to work as electrical motor during at least a part of said compression stroke, or as a generator during at least a part of said working stroke of said ICE; e. any combination from a, b, c, d; a second energy receiver, arranged as a hydraulic pump with a valve, controllable by said KEC and connected to said LPLV, and with an automatic output valve, connected to said HA; said controllable valve is open during input stroke of said hydraulic pump and then during a part of output stroke according to power that is needed from said hydraulic pump, said power is defined by said KEC; said buffer and the second energy receiver are connected to said piston of said ICE.
11. A method of operating a Heat Machine (HM) being a heat engine or a heat pump; the HM is provided with at least a single High Pressure Chamber (HPC, 8) and with at least a single Low Pressure Chamber (LPC, 40); the LPC may be atmosphere; the HM is provided with Energy Conversion Means (ECM), arranged for conversion algebraic sum of compression and expansion energy at least of a part of said WF to mechanical work, or vice versa; the ECM may be positive displacement type, and this case the ECM named Working Chamber (WC); part of the WC named WCC 35, being arranged only for compression; part of the WC named WCE 34, being arranged only for expansion; the WC may include separated parts WCE 34 and WCC 35, or arranged as at least a single chamber for compression and expansion; the ECM may include a turbine, for converting energy of compressed WF to kinetic energy of moving WF and then to mechanical work; the ECM may include an axial or radial compressor; the turbine, mechanically connected to any compressor (radial, axial, positive displacement or another) named turbo-compressor; the ECM may include combinations of any type WC, turbine, compressor, with at least a single stage for compression and at least a single stage for expansion; said Heat Machine (HIM) is working with a thermodynamic cycle, comprising: displacing at least a part of the WF between said ECM and said LPC 40; displacing at least a part of the WF between said ECM and said HPC 8; performing compression and expansion at least inside said ECM; changing heat energy of the WF by any way; characterized in that it further comprises the steps of: providing at least a single expander 19 or compressor 7, the expander or compressor arranged with at least a single stage, arranged without transferring a work from or to said ECM; connecting said expander 19 or compressor 7 between at least a single HPC 8 and at least a single LPC 40; arranging an expansion ratio of an expander and a compression ratio of a compressor which are approximately equivalent to the ratio of pressures between appropriate HPC and LPC; regulating the ratio between throughputs of said expander 19 or compressor 7 and the ECM, so that said pressure HP will be approximately as desired; using said expander as an output of at least a part of power from said engine, or using said compressor as an input of at least a part of power for said heat pump.
12. A method according to claim 11, further comprising: providing at least a single WCC 35 and at least a single LPC 40, being atmosphere, and so said LP is approximately equivalent to atmospheric pressure; compressing atmospheric air in said WCC 35 and displacing this compressed air with temperature Tec to said HPC 8; providing at least a single WCE 34, the WCC 35 and WCE 34 are reciprocating piston type, with separated cylinders for the WCE 34 and WCC 35; providing a regenerator, that includes at least a part of HPC 8 and of LPC 40; heating the air in the regenerator with begin heating parameters HP, Tec, using for this heating heat energy of a gas with parameters LP, Tee>Tec, that go from the outputs of said WCE 34 and said expander 19; sending in said regenerator cooled gas with parameters LP, Tout>Tec, from said regenerator to atmosphere, or to means, arranged for using heat energy of this cooled gas; expanding in the WCE 34 and in the expander 19, air, heated in said regenerator; during this expanding, injecting fuel into the WCE 34 and into the expander 19, such that at least a part of expanding will be approximately with constant temperature; providing at least a single beam; and pistons of the WCC 35 and WCE 34 connected to the beam; ensuring symmetrical distribution of forces, applied to the beam; said beam includes bearings connected to connecting rods, another sides of said rods with another bearings connected to crankshafts, while loading them with the same symmetrical forces; where no normal forces are applied to the cylinder, due to symmetrical structure with synchronization of crankshafts, such that crankshafts are rotating in opposite directions; diminishing loads on crankshafts by using at least a part of expansion energy from the WCE 34, for compression in the WCC 35; further diminishing loads on crankshafts by increasing summed kinetic energy of said beam, rods, pistons and other reciprocating parts, connected to them, relatively to summed kinetic energy of said crankshafts and other rotating parts, connected to them, and parts, used for said synchronization; regulating valves of the WCE 34 such that beginning output from said WCE 34 will be near the end of the expansion stroke and the pressure at end expansion will be near said LP; for this regulation, adjusting a time, when an input valve of the WCE 34 is open, the optimal value of this time named below an optimal time; providing a pressure sensor HPCPS 32; using said expander 19 as main energy output from the ICE, while regulating the ratio between throughputs of said expander and the ECM by regulating a mean rotation speed of said ECM according to feedback from said HPCPS 32, while increasing the speed when said HP is smaller than desired, and vice versa; if increasing said mean rotation speed is needed, increasing the time when an input valve of the WCE 34 is open, and vice versa, were in both cases, returning said time to said optimal time when said mean rotation speed is near the desired value.
13. A Positive Displacement Heat Machine with multi vane Rotor (PDHMR), that may be the heat engine or the heat pump, comprising: at least a single LPC 40 and least a single HPC 8; at least a single body 1 with left and right walls 14 and a rotor 2 between them; a plurality of vanes 3, being movable approximately along radius of said rotor 2; several working chambers (WC), each WC is formed by Surfaces of neighboring Vanes 3 (SV), parts of Surfaces of said Left and Right Walls 14 (SLRW), a part of Surface of said Body 1 (SB), and a part of Surface of said Rotor 2 (SR); wherein during rotation of said rotor 2, volume (Vwc) of every WC is changing between Vmin and Vmax; a space, enclosed between the SLRW, SB, SV, SR, where the Vwc is diminished to Vmin, named a High Pressure Space (HPS); a space, enclosed between the SLRW, SB, SV, SR, where the Vwc is increased to said Vmax, named a Low Pressure Space (LPS); at least a single Low Pressure Output Mean (WCLPOM, 21) and a Low Pressure Input Mean (WCLPIM, 20), both arranged as controllable openings between LPS and said LPC 40; means 9 for scavenging the WF between said LPS and said LPC 40; at least a single High Pressure Controllable Opening (WCHPCO, 18) provided between said HPS and HPC 8; where openings WCLPOM 21, WCLPIM 20, WCHPCO 18 are controlled, preferably be due to changing position of every WC relatively to appropriate opening; characterized in that is further comprises: means, arranged to initiate displacing at least a part of the WF between said HPC 8 and said WC, when being HPS, at least across said WCHPCO 18, such that displacement of said part is not caused by changing the volume of the WC.
14. The PDHMR according to claim 13, further comprising: a High Pressure Separator (HPSEP, 5), arranged to separate said HPS to an input and output parts, such that during moving said WC across said HPS, the volume of the input part is increases, and the volume of the output part diminishes, such that the changing in the volume of the HPS is relatively small; Separated HP Scavenging Window 12, that is separated by said HPSEP 5 to an input and output windows in a part of said body 1, enclosing said HPS, said output window is equivalent to said WCHPCO 18 and connected to the input of said HPC 8, and said input window is connected to the output of said HPC 8; a driver 6, arranged to move the HPSEP 5 approximately along radial direction with synchronization to rotation of said rotor 2 and with a small gap to said SR, such that the surface of the gap will be sufficiency smaller than the surface of said Scavenging Window 12; the SR is arranged with smooth changes of a radial distance to the rotation center, said distance is maximal near the tips of said vanes 3, and minimal between vanes 3; LP Scavenging Window 11 in part of said body 1, enclosing said LPS, said LP Scavenging Window 11 is equivalent to said WCLPOM 21, WCLPIM 20.
15. The method according to claim 11, wherein the heat pump is provided with at least single HPC 8 and at least single LPC 40, further comprising: providing at least the single Working Chamber (WC), including at least a single reciprocating piston and at least a single crankshaft, said WC is arranged for conversion of the algebraic sum Zwork of compression and expansion work at least of a part of the WF to mechanical work, or vice versa, the WC arranged for regulating said Zwork is near zero; providing in the WC, said controllable openings WCLPIM 20, WCLPOM 21, WCHPCO 18, WCHPIM 41; providing a hot and cool zones in the LPC 40, the hot zone is caused by heating from cooling objects; the HPC 8 is provided with a hot input and a cold output, where cooling in the HPC is caused by thermal transfer to any external medium; said heat pump is working according to the following cycle: after ending expansion in said WC, opening said WCLPOM 21 and WCLPIM 20 and performing LP scavenging the WF from said hot zone of LPC 40 across said WCLPIM 20, WC, WCLPOM 21 to said cool zone of LPC 40; compressing the WF in said WC to said HP; performing HP scavenging of the compressed WF from said cool output of HPC 8 across said WCHPIM 41, WC, WCHPCO 18 to said hot input of HPC 8; performing adiabatic expanding of the compressed WF in said WC, to said LP; regulating a compression and expansion ratio of the WC according to desired Low Temperature (LT); regulating a cycle speed of the WC according to desired throughput; providing at least a single stage compressor 7, arranged without transferring a work from, or to, said WC; arranging compression ratio of the compressor 7 to be approximately equivalent to HP/LP; connecting the input of said compressor to said hot zone of LPC 40; providing a cooling tube 53, arranged to supply the WF from the output of the compressor to said HPC 8, while cooling the WF in the cooling tube 53 by heat transfer to an external medium; connecting said compressor to an energy source, selected from the group, consisting of: a. wind turbine; b. engine powered by water; c. electrical motor; d. heat engine; e. animal; f. any combination from a, b, c, d, e; providing a pressure sensor HPCPS 32, arranged to react to said HP inside said HPC 8; regulating a ratio between throughputs of the compressor 7 and the WC, with regulation of throughputs of the compressor 7 according to feedback from said HPCPS 32, such that pressure in said HPC 8 will be approximately equivalent to desired HP; providing a LP blower 9LP, for said LP scavenging; selecting an HP scavenging from the group consisting of: 15.1. providing an HP blower 9HP, opening said WCHPIM 41 and WCHPCO 18 to begin HP scavenging and closing them to end HP scavenging; 15.2. synchronization of the HP scavenging to the output stroke of the compressor 7, being a positive displacement compressor; separating the HPC 8 to two parts with approximately equivalent volumes by the Single Direction Valve (HPSDV, 47) between them; connecting the output of said compressor 7 to a cooling tube 53 and connecting the output of said cooling tube 53 between said HPSDV 47 and said WCHPIM 41; when said HPSDV 47, and WCHPIM 41, and WCHPCO 18 are closed, increasing the pressure before said WCHPIM 41, using said synchronization HP scavenging to the output stroke of the compressor 7; after beginning increasing the pressure, opening said WCHPIM 41 and WCHPCO 18, initiating a flow of the WF between said two parts across said WC; when the ratio between pressures in said two parts will be near 1, opening said HPSDV 47, whereby using Inertial Scavenging (ISC) across said WC, said two parts and said HPSDV 47; closing said WCHPIM 41 and WCHPCO 18 to end HP scavenging; 15.3. using ISC, which is initiated by opening said WCHPCO 18 after end compression, while continuing diminishing the volume Vwc of the WC; when said Vwc will be close to Vmin and inertial of flow in said WCHPCO 18, causing diminishing of the pressure in said WC to be below the pressure before said WCHPIM 41, open WCHPIM 41 and continuing with ISC; closing said WCHPIM 41 and WCHPCO 18 to end HP scavenging.
16. The method of claim 15, further comprising: providing a distributor 50 of the WF, with an input connected to the output of the compressor, the distributor 50 is arranged to controllably divide the input flow of the FW between a first and a second outputs of the distributor 50, the first output connected to said cooling tube 53; providing a thermal isolated tube 24, connected to the second output, another tip of this tube 24 connected to a thermal isolated buffer volume 8B; providing an expander 19, with an input connected to the buffer volume 8B across controllable on/off valve 54, and mechanical output of the expander 19 connected to electrical generator 46; controlling the distributor 50 and the on/off valve 54 such that when a compressor power, caused by power of wind, is more than needed for the heat pump, the compressor 7 producing an overpower, part of the compressed WF is directed to the buffer volume 8B and the expander send said overpower to the electrical generator.
17. The method according to claim 11, for operating an electrical plant with heating at least from concentrated Sun rays, wherein a heater 8SH placed in focus of an optical concentrator, further comprising: providing at least a single electrical generator 46, arranged to convert mechanical energy to electrical energy; providing a Temperature Sensor (TSHT, 42), arranged to measure the HT; providing a pressure sensor HPCPS 32, arranged to react to said HP inside said HPC 8; placing the HPC 8 near a heater, that is arranged to heat the FW in the HPC, and placing the WC near the HPC 8; said TSHT 42, HPC 8, WC being a Near Heater Means (NHM); regulating the Zwork near zero by regulation valves of the WC; placing the LPC 40, expander 19 and electrical generator 46 as far from the heater 8SH as needed, to avoid shading the optical concentrator from Sun rays; said LPC 40, expander 19, electrical generator 46, being a Remote Means (RM); connecting the input of the expander 19 to said HPC 8 with a thermal isolated tube 24; placing connections between said RM and NHM, such that this connections are shaded by said thermal isolated tube 24, or vice versa, whereby to avoid additional shading of the optical concentrator; mechanically connecting said expander 19 to said electrical generator 46; regulating the throughput of the WC according to the received heat, such that said HT, measured by said TSHT 42, will be near a desired optimum; regulating a throughput of the expander 19 according to said HP, while increasing the throughput of the expander if the HP is more than desired, and vice versa, measuring said HP by said HPCPS 32; regulating the throughput by the following group, consisting of: a. regulating the input and output valves of the expander 19; b. using at least a single additional working volume, by connecting or disconnecting said working volume from a main shaft of the expander 19; c. using at least two expanders 19 and two electrical generators 46, each expander connected to appropriate electrical generator, and connecting or disconnecting expanders to said HPC 8 and LPC 40 according to desired summed throughput, with appropriate connecting and disconnecting electrical generators from electrical load; d. using the mechanical connection between the expander 19 and electrical generator 46 with controllable transmission; e. using the expander 19 with regulating working volume; f. any combination between a-e; further matching the electrical power of the electrical generator 46 to the mechanical power of the expander 19 by regulating the electrical load; further placing the Sun heater 8SH inside the thermal isolated chamber with a window, that is approximately normal to optical axis of the Sun concentrator, and arranging that the receiving surfaces of the Sun heater 8SH are sufficiency larger than the surface of said window, thereby placing most of receiving surfaces not in parallel to said window.
18. The method of any one of claims 3-8, 12, 15-17, wherein the PDHM is an oscillating piston type with at least a single piston and a single crankshaft; further providing: at least one Rotating Speed Sensor (RSS), at least one controllable Energy Receiver (ER), at least one controllable Energy Source (ES), at least one Fixation of Crankshaft (FC), at least one Initiation of Crankshaft Moving (ICM), and at least one Kinetic Energy Controller (KEC); arranging the KEC for regulating the throughput of the WC, according to feedback from said HPCPS 32, such that pressure in said HPC 8 will be approximately equivalent to a desired HP, by changing an Acceleration Between Cycles (ABC), so that ABC>0 for acceleration, ABC<0 for deceleration; regulating, according to signal from said RSS, kinetic energy of said Moving Parts (MP) by said KEC, such that when said piston is near a Dead Point (DP), the speed of said crankshaft, will be near a desired local minimum, including approximately zero; if the speed is near zero, optionally performing fixation of said MP near this DP by said FC, and after a Time of Pause (TimeP), initiating rotation by said ICM; regulating a value of the local minimum and TimeP according to the feedback from said HPCPS 32 using said KEC, with feedback from said RSS and controlling the distribution of the energy between said ES and ER; further using mentioned regulations of the local minimum and TimeP, to control a time for displacing the WF between said WC and HPC 8 and between said WC and LPC 40, and to control power from zero to maximum, and to control the throughput of the WC; wherein any of said RSS, ES, ER, KEC, FC, ICM may be combined with any other from them or arranged with combined functions of them and may be any type, including using kinetic energy of any part, thereby allowing working with Pulse Pause Modulation (PPM).
19. A two stroke reciprocating piston engine apparatus, comprising: a) at least single thermally isolated High Pressure Chamber (HPC) 8 with Working Fluid (WF) compressed to High Pressure (HP), volume of said HPC 8 is sufficiency more, than end compression volume Vec; b) at least single Cylinder 15 with two Assemblies 16, each Assembly includes: b.1) two Crankshafts having minimal Inertial Moment, each Crankshaft is not connected to external load; b.2) a Piston, connected to a central part of a Beam; b.3) a Buffer 51, connected to central part of the Beam opposite to the Piston, for accumulating Energy from Expansion (EE) of WF (gas) during working stroke of said Piston, and return the EE during compression stroke as Energy for Compression (EC), while EE and EC are approximately the same, EE=EC; b.4) two connecting rods, one side of every connecting rod connected with bearing to a tip of the Beam, and another side with another bearing connected to corresponding Crankshaft being connecting to a synchronization gear; the crankshafts are arranged to rotate to opposite directions due to said gears; at least one of said crankshafts with addition gear and synchronization Belt connected to corresponding crankshaft of another said Assembly; c) said two Assemblies 16, are arranged such, that: c.1) symmetrically moving each of said two Pistons inside said Cylinder 15 between High Pressure Dead Point (HPDP), that is near a central part of Cylinder 15, and a Low Pressure Dead Point(LPDP), that is near a tip of Cylinder 15, so in Cylinder 15 there are two said HPDPs and two said LPDPs; c.2) symmetrically moving all parts, such that inertial forces are balanced; c.3) symmetrically loading all parts by gas forces, such that there are no forces between said pistons and Cylinder 15; c.4) volume (Vmin) between said two HPDP is equivalent or smaller than said Vec, such that said pistons are not displacing all compressed WF to said HPC 8, thereby diminishing moving pistons under said HP; c.5) Assemblies 16 and all rotating means in it or connected to it, including said Belt, have a minimum Inertial Moment, limited only by mechanical strength, but the Reciprocating Parts in the Assemblies 16 may have a large mass, thereby diminishing dynamic load on said bearings; d) a Working Chamber High Pressure Controllable Opening (WCHPCO) 18 in said central part of Cylinder 15, between two said HPDP, the WCHPCO 18 arranged to control a flow of WF between said Cylinder 15 and HPC 8, such that: d.1) said flow begins after ending compression and when the pressure in Cylinder 15 is approximately equivalent to said HP; d.2) said flow ends when volume in said Cylinder 15 is increased to Vbe, and Vbe is equivalent or more than said Vec; e) a fuel Injector 25A between two said HPDP, remote from said WCHPCO 18; said Injector 25A arranged for combustion after end compression, such that: e.1) after opening said WCHPCO 18, displacing at least a part of compressed WF to said HPC 8 due to heat expansion of combusted product, thereby diminishing moving of said Piston under said HP; e.2) minimum mixing between said displacing part and said combusted product; e.3) preferably ending combustion before expanding to said Vbe; f) a sensor HPCIMTS 27, arranged to measure temperature T27 of the WF in the HPC 8 after said WCHPCO 18; g) a Remote Expander 19, arranged as power output of the engine, without transferring energy from, or to, Assembling 16, with expansion from said HP to Atmospheric pressure; h) at least a single Electrical Machine 22, mechanically connected to any of said Crankshafts, for receiving energy, for providing energy, arranged to control rotation of said Crankshafts, the power of said Machine 22 is sufficiency smaller, than the power of said Expander 19; i) a Rotating Speed and position Sensor (RSS) 31, mechanically connected to said Electrical Machine 22 or to the Crankshaft; j) a pressure sensor HPCPS 32, arranged to measuring differential pressure between HPC 8 and Atmosphere; k) a Controller 29, arranged to: k.1) control said WCHPCO 18 and Injector 25A, such that EE=EC, with using feedback from said RSS 31; k.2) control said WCHPCO 18 and Injector 25A, such that if need fast changing of mean speed of said Crankshaft, EE>EC, or EE<EC according to desired changing; k.3) control said Electrical Machine 22, such that kinetic energy of said Assembling 16 at position according to at least one of said HPDP or LPDP, will be desired volume, including zero, with using for this control feedback from said RSS 31; k.4) if the speed of said Crankshaft near at least one of said HPDP or LPDP is near zero, optionally fixating said Assembling 16 during desired Fixation Time, using said Electrical Machine 22 for this fixation; k.5) initiating moving of said Crankshaft with said Electrical Machine 22; k.6) synchronization the mean cycle speed of Assembling 16 with throughput of said Expander 19, such that the pressure HP in said IPC 8, measured by said HPCPS 32, will be as desired; k.7) controlling said Injector 25A and WCHPCO 18 for minimum mixing, mentioned in e.2, with using signal from said RSS 31 and HPCIMTS 27; for optimal case, T27 is not sufficiency more, than temperature at end compression Tec; k.8) controlling said Injector 25A and WCHPCO 18, such that pressure at the end expansion will be not substantially more than Atmospheric pressure; 1) at least a single Fuel Injector 25B, preferably inside said IPC 8, and optionally in Expander 19.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
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DETAILED DESCRIPTION OF THE INVENTION
Glossary and Abbreviations
[0133] Adiabatic process takes place when no heat transfers. Parameters of adiabatic process: [0134] P, V, TPressure, Volume, Temperature (gradus K) of Working Fluid (WF, any gas); [0135] bc, ecbegin, end compression; for example, Pbc, Pec. [0136] be, eebegin, end expansion. [0137] Cp and Cvare the thermal capacities of WF when P or V is constant. [0138] kathe adiabatic coefficient, ka=Cp/Cv; for Air, ka=1.4. [0139] For compression: kv=Vbc/Vec>1; kp=Pec/Pbc=kv.sup.ka>1; kt=Tec/Tbc=kv.sup.(ka-1)>1. [0140] There, most cases for compression and expansion, parameters kv, kp, kt are the same. [0141] For expansion: kv=Vee/Vbe>1; kp=Pbe/Pee=kv.sup.ka>1; kt=Tbe/Tee=kv.sup.(ka-1)>1. [0142] WWork of gas; for expansion and compression, |W| is the same, if Vbc=Vee, Vec=Vbe, Pbc=Pee, Pec=Pbe:
Expansion: W=(Pbe*VbePee*Vee)/(ka1)=Pbe*Vbe/(ka1)*(11/kt)>0;
Compression: W=(Pec*VecPbc*Vbc)/(ka1)=Pec*Vec/(ka1)*(11/kt)<0; [0143] EEis the Energy from Expansion of the gas in the WC, defined as:
EE=W+W(input to expander)W(work against atmospheric pressure). [0144] CEEnergy for Compression of the WF in the WC, defined as:
CE=W(input to compressor)W(output from compressor)W. [0145] MWMechanical work; MW=EECE. For engine, MW>0; for heat pump, MW<0. [0146] EfEfficiency of engine, defined as: Ef=MW/TE, TE is thermal energy. [0147] EfaEfficiency of engine for adiabatic compression and expansion.
[0148] Brayton adiabatic cycle consist adiabatic compression and expansion and constant pressure heating and cooling. Engine efficiency: Efa=(TecTbc)/Tec. Heat pump, if cooling: COP=Tee/(TbeTee).
[0149] Blower (9) implies a separate design or set of parts, arranged to displace the WF inside the heat machine, if for this displacing need a small difference of pressure.
[0150] Components of air are N.sub.2, O.sub.2, CO.sub.2, H.sub.2O, etc. as they are in a normal air with appropriate concentrations.
[0151] Clear output implies Output products of engine with CO.sub.2 and H.sub.2O or only H.sub.2O, with concentrations of the dirty output products below than appropriate standard.
[0152] Coefficient of Performance (see COP, Heat Pump), this term is used for Heat Pump.
[0153] COP=Thermal Energy (TE)/Mechanical Work (MW). TE transferred between cool and heat objects.
[0154] Compressor of inertial type converts mechanical energy to pressure and kinetic energy of the WF.
[0155] Compressor of positive displacement type converts mechanical energy to pressure energy of the WF.
[0156] Controllable Opening: Controllable imply any type of control, including, for example, changing position of any mean relatively to the opening; piston may close and open a scavenging window, a valve driver may close or open a valve, the valve may be any type.
[0157] Cylinder is positivedisplacement working chamber in general, not restricted to circular cross-section.
[0158] Dirty output products are output products of engine, except components of air.
[0159] Efficiency of the heat engine is Mechanical Work (MW)/Thermal Energy (TE).
[0160] Expander of inertial type is a Turbine, using compressible WF.
[0161] Expander of positive displacement typesee Positive displacement.
[0162] External heating engine, have the WC where take place near adiabatic thermodynamic processes. Heat is transferred to external volume that may be a heat exchanger or external combustion chamber.
[0163] Heat machine convert a part of Thermal Energy (TE) to Mechanical Work (MW) or vice versa (see Heat pump).
[0164] Heat pump uses MW to move TE opposite to spontaneous heat flow; may work as cooler or heater.
[0165] Internal heating engine (IHE), for example a spark ignition or Diesel type, have a working chamber (WC), for example a space bounded by a piston and a cylinder, where take place thermodynamic processes, including combustion of a fuel inside compressed air.
[0166] Inertial Scavenging (ISC), see Scavenging. Initiating moving a part of a WF from and (or) to WC and continue this moving due to kinetic energy of the WF and, in addition, due to kinetic energy of any mean, if it designed for ISC.
[0167] Local minimum of a velocity, V1 min, defined there according: V1>V1 min<V2, where V1, V1 min, V2 are velocity points inside any part of cycle at appropriate time points t1<t1 min<t2 with minimum detectable differences V1V1 min and V2V1 min. Local minimum of piston speed=0 at dead points (crankshaft angles 0 and 180), and it is absolute minimum as well. The crankshaft rotation speed may have a local minimum after end compression.
[0168] Main shaft, means the shaft which converts reciprocating piston motion into rotary motion or vice versa.
[0169] There, term crankshaft means the shaft which converts reciprocating piston motion into rotary motion or vice versa, but main shaft means the shaft which converts any motion into rotary motion or vice versa. For example, in Vankel engine, planetary motion converted to rotation by main shaft. So, the main shaft is wider definition than crankshaft.
[0170] Output products are CO.sub.2, H.sub.2O, CO, N.sub.xO.sub.y (for example, NO), etc., depended upon the fuel type and the combustion quality. After ideal combustion of good fuels, output products are CO.sub.2 and H.sub.2O, or only H.sub.2O if Hydrogen (H.sub.2) is used.
[0171] Dissociation of N.sub.2 and O.sub.2 begin approximately above 2000 K and increase concentration of N.sub.xO.sub.y in output products.
[0172] Combustion temperature in prior art ICE is more than 2000 K and is sufficiency more in local volumes if bad mixing.
[0173] After cooling, not all N.sub.xO.sub.y is decomposed to N.sub.2 and O.sub.2. So, N.sub.xO.sub.y in output may be with using every type of fuel.
[0174] Positive displacement, according to IPC (International Patent Classification), means the way the energy of the WF is transformed into mechanical energy, in which variations of volume created by the WF in the WC produce equivalent displacements of the mechanical member transmitting the energy, the dynamic effect of the WF current being of minor importance.
[0175] Pump, according to IPC, means a device for raising, forcing, compressing, or exhausting fluid by mechanical or other means. Pump includes fans or blowers.
[0176] Scavenging, according to IPC, means forcing the combustion residues from the cylinders other than by movement of the working pistons, and thus includes tuned exhaust systems. There, term scavenging is used not only for the combustion residues and exhaust, and imply displacing at least a part of the WF from the WC and displacing another part of the WF to the WC by any way, that cause essentially more displacing than according to changing volume of the WC during this displacing process, including a case with constant volume of the WC or even changing this volume against direction of this displacing. See above Inertial Scavenging, ISC.
[0177] Sterling cycle, in ideal, includes constant volume heat transfer in regenerator, isothermal compression and expansion, constant volume heating and cooling.
[0178] Turbine converts kinetic energy of the WF to mechanical energy.
[0179] Working fluid (WF), according to IPC, means the driven fluid in a pump and the driving fluid in an engine. The WF may be in a gaseous state, i.e., compressible, or liquid. In the former case coexistence of two states is possible. There, term working fluid used as well for heat pump. During working cycle in engine or heat pump, the WF may be converted from gaseous to liquid state or vice versa.
Abbrevations
[0180] DPDead Point, it is position of crankshaft in reciprocating piston machine, and appropriate position of the piston, where the piston change direction of moving. At the DP, the piston cannot change rotation speed of the crankshaft. For free piston machines, DP is position of piston, where it change direction of moving. [0181] EHEExternal Heating Engine. [0182] ECEExternal Combustion Engine (ECE is the type of EHE). [0183] HMHeat Machine, there may be engine or heat pump. [0184] HPDPHigh Pressure Dead Pointthe DP, where pressure in the cylinder is approximately equivalent to the High Pressure level. [0185] ICEInternal Combustion Engine. [0186] IPCInternational Patent Classification. [0187] ISCInertial Scavenging, see above Scavenging, Inertial Scavenging. [0188] LPDPLow Pressure Dead Pointthe DP, where pressure in the cylinder is approximately equivalent to the Low Pressure level. LPDP is equivalent to the Bottom Dead Center, where scavenging between combustion gas and free air. [0189] PDHMPositive Displacement Heat Machine. [0190] PDHMRPDHM with multi vane Rotor. [0191] PPMPulse Pause Modulation. Working mode of the PDHM with reciprocating piston, when it may be stopped at the Dead Point and begin moving after a controllable time. [0192] RPCReciprocating Piston and Crankshaft, wide using type of the PDHM.
Abbreviations of Parts
[0193] The referenced numbers are from drawings; see section Numbers of parts for all drawings.
[0194] Buffer (51), a mean that combine functions of Energy Receiver (ER) and Energy Source (ES), see ER, ES. Preferable a gas buffer. [0195] C (7)Compressor, with input from LPC, output to HPC, a volumetric ratio arranged so, that pressure at end compressing approximately equivalent to HP in HPC; using the compressor as a receiver for at least a part of input power of the heat pump. [0196] E (19)Expander, with input from HPC, output to LPC, a volumetric ratio arranging so, that pressure at end expanding approximately equivalent to LP; using the expander as a source for at least a part of output power of the engine, with regulating the expander according to demands of a load.
[0197] ECMEnergy Conversion Means, arranging to work with at least a part of the WF, used in a thermodynamic cycle of the heat machine, with converting energy of compressed WF to mechanical work, and reverse converting, with conversion algebraic sum of compression and expansion energy to a work, named Zwork; supposing, that expansion work is positive, and compression negative, Zwork<0 is according to receiving external work, Zwork>0 is according to producing output work; all parts, that need to make the Zwork, named Zmachine. [0198] ECM of positive displacement type named Working Chamber (WC); [0199] WC, arranged only for compression, named WCC and is a part of the ECM; [0200] WC, arranged only for expansion, named WCE and is a part of the ECM; the WC may include separated parts WCE and WCC or arranged as a single chamber for both functions. [0201] A part of ECM, converting energy of compressed WF to kinetic energy of moving WF and then to mechanical work, named turbine; [0202] A part of ECM, converting mechanical work to kinetic energy of moving WF and then to energy of compressed WF, named axial or radial compressor according to working principle; [0203] A turbine, mechanically connected to radial or axial compressor, named turbo-compressor. [0204] EIHExpander Input Heater. [0205] EREnergy Receiver. [0206] ESEnergy Source. ER, ES may be mechanical, hydraulic, electrical means, or another; separated, or both in the same design. Examples for the same design: electrical machine, hydraulic machine, gas buffer (51), inertial mass. An example for ER is a hydraulic pump with a single direction input and output valves. [0207] FCFixation of Crankshaft, a mean to fixate the crankshaft near at least one of Dead Point if the rotation speed near it, is approximately zero; [0208] HAHydraulic Accumulator, with separated liquid and compressed gas volumes inside a common envelope with a common high pressure. [0209] HMPHydraulic MotorPump. [0210] HPC (8)High Pressure Chamber, include function of pressure buffer volume (it is not buffer 51), heating or cooling. [0211] HPCPS (32)pressure sensor arranged to react to the HP in the HPC; most cases may be electrical or mechanical output. [0212] HPCBPS (56)HPC buffer volume pressure sensor. About 32 and 56 see description to
[0245] Parameters of Heat Machines [0246] ABCAcceleration Between Cycles, according to difference between kinetic energy of Moving Parts (MP) at begin and at end of the thermodynamic cycle. [0247] CEEnergy for Compression of the Working Fluid (WF) in the Working Chamber (WC). [0248] d (any parameter)delta, a small changing of any parameter, for example dHP. [0249] EEEnergy from Expansion of the WF in the WC. [0250] HP or PHHigh Pressure, there most cases it is pressure at end compression (Pec), but sometimes due to combustion, HP>Pec. [0251] HT or THHigh Temperature, measured by sensor TSHT (42). [0252] LP or PLLow Pressure, most cases it is pressure at begin compression. [0253] LT or TLLow Temperature. [0254] MWMechanical Work. [0255] Mreciprocating mass of assembling 16. [0256] mRRotating mass on radius R, this mass equivalent to sunmed inertial moment. [0257] OEOver Energy, energy of buffer 51 minus compression energy, see explain to
[0287] NUMBERS OF PARTS FOR ALL DRAWINGS [0288] 1. Body with non-limited length. [0289] 2. Rotor with specific shape. [0290] 3. Vanes. [0291] 4. Slots, sizes according to the vane. [0292] 5. Separator. [0293] 6. Driver for the separator. [0294] 7. Compressor. [0295] 8. High Pressure Chamber (HPC), include function of pressure buffer volume (it is not buffer [0296] 51), heating or cooling. [0297] 8BHPC, thermal isolated buffer volume. [0298] 8CHPC, cool part. [0299] 8FTubes with combustion product inside HPC. [0300] 80PHPCOPHPC Output Part. [0301] 8HHPC, hot part. [0302] 8SHSun Heater (a part of the HPC). [0303] 8RHPC with function of regenerator. [0304] 9. Blower. [0305] 10. Heat exchanger, counter flow type. [0306] 11. LP scavenging window. [0307] 12. Separated HP scavenging window. [0308] 13. Main shaft. In the prior art,
[0361] Parameters are examples by computer simulations. Parts according to NUMBERS OF PARTS FOR ALL DRAWINGS.
[0362] With reference to
[0377] The counter flow heat exchanger 10 transferring heat from air with parameters Pec, Tec to water, that is with atmospheric pressure (0.1 MPa) inside tubes. Hot water may be used, or cooled by atmospheric air in external heat exchanger. Every WC formed by surfaces of neighboring vanes 3, parts of surfaces of the side walls 14, a part of surface of the body 1, and a part of surface of the rotor 2. During rotation of the rotor 2, volume (Vwc) of every WC is changing between Vmin and Vmax, kv=<Vmax/Vmin. A space, where the Vwc is diminished to Vmin, named a High Pressure Space (HPS); a space, where the Vwc is increased to theVmax, named a Low Pressure Space (LPS). Prefer a small as possible gap between tip of separator 5 and rotor 2. For example, if swing of oscillation of Separator 5 is 15 mm, may be: 0<gap<0.3 mm, even larger gap is not critical. Synchronization gear between rotor 2 and driver 6 is not shown. Shape of rotor 2 is according to oscillation of separator 5 and caused by design of driver 6.
[0378] WORKING CYCLE include scavenging by blower 9 at LPS, so output cool air with parameters LP=Pee, Tee, is displacing by room air with Pbc=LP, Tbc. During moving WC from LPS to HPS, take place compression to HP=Pec, Tec. Then scavenging in HPS between the WC and HPC 8, so air with Pec, Tec, is displacing by air with Pbe=HP, Tbe. During moving WC from HPS to LPS, take place expansion to Pee, Tee. Length of scavenging windows 11, 12 is according to length L of body 1, so L may be large (see example below). In the prior art, all windows are inside side walls, so L limited by speed of air during scavenging.
[0379] So, the main principle is: displacing the WF between WC(HPS) and HPC 8, with very small changing volume of the WC.
[0380] Scavenging across WC by a blower (Separator 5); the blower is based on the positive displacement principle.
[0381] Below Example According Computer Calculations for this Home Conditioner.
[0382] Rotation speed Wr=63 rad/s, length of body L=1 m (this large L is practically impossible for the prior art), internal radius of body 1, Rb=72 mm, throughput V=0.045 m.sup.3/s, kv=1.358, kp=1.535, kt=1.13; Pbc=0.1 MPa, Pec=0.1535 MPa, Tbc=300 K, Tec=339 K, Tbe=308.sup.0K=35 C., Tee=273 K=0 C. COP=Tee/(Tbe-Tee)=7.8 (if no loss). Density of Air at 0 C. is 1.27 kg/m.sup.3. Power: Pcool=(Tbc-Tee) K.*1000 J/kg/ K.*1.27 kg/m.sup.3*0.045 m.sup.3/s=1549 W; mechanical power: Pmech=Pcool/COP=199 W, it is power that need for Air compressor 7 if no loss. In assembling, that include body 1, rotor 2 and vanes 3, compression and expansion energy are the same (ECEE=Zero); if no loss, it no send and no get mechanical energy and so named Zmachine (see GLOSSARY . . . ). It get from a room V=0.045 m.sup.3/s with Tbc (see above WORKING CYCLE) and send to the room the same V, but with Tee. To keep BALANCE OF AIR MASSE, throughput from air compressor 7 is: V7=V*Tbc/TeeV=0.00945 m.sup.3/s. May to place it out of the room, and connect input to external air. If dT between external hot air and the room air is 5 K, ventilation by V7 add to the room heat power 54 W.
[0383] Example for Cooling Power for a Room 20 m.sup.2:
[0384] Thermal transfer coefficient x=8 W/M.sup.2/ K; surface for thermal transfer S=90 m.sup.2; mean dT between room air and walls 2.5 K; cooling power=8*90*2.5=1800 W. Calculated above Pcool=1549 W is for Wr=63 rad/s. May increase Wr to 16% and get Pcool=1800 W.
[0385] Below are Calculations for Loss (AG), in G, Calculated that Increasing Wr to 16% May Diminish COP to 2%.
[0386] A. For compressor 7, with output power 199 W, suppose loss7=20 W.
[0387] B. If air speed during scavenging is 9 m/s (twice more than linear speed of rotor 2), and volume V=0.045 m.sup.3/s loss all kinetic energy 4 times during cycle, vortex loss is: loss V=9 W.
[0388] C. Sizes of Capron vane 3 is (1*8*1000) mm.sup.3. For 6 vanes and Wr=63 rad/s, inertial force on surface of body 1, is: Pw=16N. If friction coefficient kfr=0.2, sliding of vanes along surface of body 1 cause loss Pw=14.5 Watt.
[0389] D. Pressure in slot 4 is maximum between pressures from a left and right sides of vane 3, and it is Pec. According to computer simulation, mean difference of pressures that press vane to body, is: dp12 m=0.33*(Pec-Pbc)=1.8N/cm.sup.2. Suppose that dp12 m placed on from vane width, so on 0.5 mm, and pressure forces on the rest part are compensated. So mean radial pressure force from all vanes is 54 N, and for mentioned kfr and Wr, it cause loss Pfr=49 W.
[0390] E_. Load from pressure force (for version at
[0391] F. Pressure force PN, normal to side surface of vane 3, cause friction force X, directed along radius. When vane 3 is moving from slot 4, force SF, pressing vane 3 to body 1, is: SF=PIX, where PI is sum of pressure and inertial forces along radius. Must PI>X, else vane 3 cannot move from slot 4. When vane 3 is moving to slot 4, SF=PI+X. So, mean SF=PI, and force X cannot cause addition loss caused by sliding vane 3 along body 1. But, friction between vane 3 and surface of slot 4 cause loss: lossX=PN*FRN*S*Wr/6.3, where S is sliding distance, for this example S=8 mm per revolution; FRN is friction coefficient, suppose it is 0.1. So, loss caused by friction between slots and vanes: lossX=3.6 W.
[0392] G. With loss, mechanical power (see A-F) is: 199+20+9+14.5+49+2.3+3.6=297 Watt; COP_real=1549/297=5.22.
[0393] It is true for car conditioner, connected directly to engine. If compressor 7 work from electrical motor, and addition motor is connected to Zmachine to compensate loss, both motors with efficiency 0.9, COPe=5.22*0.9=4.69. For car, electrical energy produced by generator with efficiency 0.9 (the best case), so COPee=4.69*0.9=4.22. Separated HP scavenging window 12 (
[0394] If increase Wr to 16%, Pcool*1.16=1800 W (see Example for cooling power for a room 20 m.sup.2), but loss increase.
[0395] Are loss, proportional to Wr.sup.2 or to Wr.sup.3. So, 1.16.sup.2=1.35, and 1.16.sup.3=1.56. For this case, mechanical power for Wr*1.16, is:
199*1.16+20*1.16+9*1.35+14.5*1.56+49*1.16+2.3*1.16+3.6*1.16=353;
COPw=1800/353=5.1. So, when Wr increased to 16%, COP diminished to 2%, that mostly caused by loss from inertial force, proportional to Wr.sup.3. With reference to
[0396] With reference to
Comparing with Prior Art
[0397] For the prior art (
[0398] According to F, lossX=3.6 W, but for the prior art, 3.6*3*3=32 W, so as 3 times more PN and 3 times more S. Note, that lossX calculated for friction coefficient FRN=0.1. Larger FRN is problematic for the prior art.
[0399] The rotating ring restrict version with no-load rotor 2, that is important for large power, see above explain to
[0400] The rotating ring restrict possibility for current of gas across windows in body 1, and are possible only windows in side walls 14. So length of body is very small (or must small Wr), else vortex loss is too large.
[0401] Without the rotating ring, the prior art practically cannot work so as large friction loss. With the rotating ring, must be only a small length of body or small Wr.
[0402] To keep BALANCE OF AIR MASSE (see above), relation between volumes of hot and cool gas must be according to Tbc/Tee, but Tbc and Tee are not constant. In the prior art, this relation caused by hard design, that cause loss of COP and sound noise if Tbc/Tee is not optimal. In the invention, this problem is solved by regulation of compressor 7. Another advantage of invention is that compressor 7 is small (V7=0.00945 m.sup.3/s). Zmachine with V=0.045 m.sup.3/s is placed in the cooling room, but compressor 7, that get main power, may be directly connected to engine of car, to wind turbine, etc.,
[0403] and placed out of roomsee above example with recommended ventilation rate . . . .
[0404] With reference to
[0405] In the cylinder take place a thermodynamic cycle with summed compression and expansion work may be near zero (Zwork=0, see GLOSSARY . . . ), so it is Zmachine that generates compressed gas to make mechanical work by the expander. Displacing a part of the WF from the WC to HPC due to diminishing volume of the WC and due to combustion in it, with Pulse Pause Modulation (PPM) in Zmachine. Due to PPM, time for combustion is optimal and not caused by mean rotation speed, so, efficiency of the engine and quality of combustion is maximal for every working mode. Engine of a car most time is working at a partly load, and for prior art, mean efficiency may be twice smaller than optimal. Remote expanders may be connected directly to wheels. Due to PPM, throughput of Zmachine is according to demand of the expanders. For maximum power, it is possible combustion in HPC and in expanders.
[0406] The embodiment at
[0407] Assembling 16 include the piston, beam, buffer 51, connecting rods, crankshafts, bearings, and synchronization gears 17 with belt. All these parts are referenced as 16, see in addition
[0408] Working cycle include scavenging in cylinder 15 by blower 9 across at least a single valve WCLPIM 20 and WCLPOM 21, but prefer using several valves to diminish vortex and thermal loss; in addition, for this purposes, head of piston 16 have a streamlined shape. Below see more after scavenging. After end compression in cylinder 15, begin opening WCHPCO 18, and compressed air, during output time Tout (
[0409] Opening WCHPCO 18 begin by driver 30 when differential pressure dPx from sensor 28 is near zero. Appropriate value dPx is defining with controller 29 by feedback to avoid a fast jump of dPx. Inside interval Tout (
[0410] After closing WCHPCO 18 and end combustion, begin expansion, at this point volume of cylinder 15 is Vbe. If Vec=Vbe, and no combustion during expansion, and no loss, summed work of cycle is zero (Zwork=0), and all output work is from expander 19.
[0411] Possible mode d, with end combustion after closing WCHPCO 18, or mode e, with Vbe>Vec, or mode f with combination d and e, this causes Zwork>0 and may be Pec>LP. According to parameters in Explain to Table_Z1 (see below), may calculate, that if dP=PeeLP=0.01 MPa, it cause loss 0.4 J, while useful work is at least 635 J.
[0412] A small Zwork may compensate friction loss, may be used by electrical machine 22 and stored in electrical accumulator (no shown). According to working mode of electrical machine 22, mean speed of crankshaft 16 may be changed. At end expansion in cylinder 15, must open valves 21, then 20. As mentioned, scavenging may be initiated by blower 9. During scavenging, piston 16 may stay any controlled time (see below EXPLAIN FOR PPM), that cause a good scavenging with a small power of blower 9. If Pee>LP, may use ISC (see GLOSSARY . . . ). To begin scavenging, at end expansion stroke, with using signal from Rotating Speed and position Sensor (RSS) 31, controller 29 with one of drivers 30 (not shown) open valve 21. Due to long tube with diffuser, energy of over pressure (Pee>LP), is converted to kinetic energy of moving gas. When according to signal from sensor 33, pressure in cylinder 15 is near Atmospheric pressure, another driver 30 (not shown) open valve 20 and take place ISC. For mentioned parameters in Explain to Table_Z1, dP=0.01 MPa cause beginning scavenging speed: (2*dP/density).sup.0.5=200 m/s, that is good to initiate ISC even for maximum power.
[0413] Version g:
[0414] Selecting the Volumetric Compression Ratio (VCR) such that Pec<HP, then performing combustion in approximately constant volume Vec, and when the pressure in the WC increases to HP or exceeds HP, according to the dPx, opening WCHPCO 18. A small part of fuel, prefer Hydrogen, injected before end compression, and combustion may be initiated by spark (a sparker and injector not shown). Version g cause preheating for good and fast combustion of fuel from Injector 25A. For minimum power, used only Injector 25A.
[0415] Displacing the Removing Part May be, for Example, According to the Following Several Versions:
[0416] Version a.
[0417] Selecting the Vec to be approximately equivalent to Vmin, and displacing the removing part mostly by heat expansion of the heating part, whereby will be near zero moving of piston 16 under pressure HP, and so minimum friction loss. Version a cause partly mixing between the heating and removing parts, so T27>Tec. Vmin is a construction parameter. Vec is according to begin opening WCHPCO 18 that cause regulation of VCR. Volumetric Expansion Ratio (VER) in cylinder 15, caused by Vbe, that is according to end closing WCHPCO 18 if then there is no combustion. If after closing WCHPCO 18 there no combustion, preferably Vbe will be slightly above Vec (Vbe>=Vec for example, Vbe=1.1*Vec).
[0418] Version b.
[0419] Selecting Vec>Vmin, and displacing the WF mostly by moving piston 16, performing combustion mostly when WCHPCO 18 is closed, so T27 is near Tec=Tbc*VCR.sup.(ka-1), ka=1.4. T27=Tec cause the best using of regenerator 23, minimum heat loss in HPC 8 and the widest regulation of cycle power: minimum power with temperature Tec inside HPC 8, and maximum power with using Injectors 25(B, C, D), as explained above. Version b cause more friction loss, than Version a.
[0420] Version c.
[0421] Compromises between Versions a and b, with Vec>Vmin and begin combustion before closing WCHPCO 18.
[0422] Version h.
[0423] Combination of the following three processes: [0424] After ending compression, opening WCHPCO 18 and by diminishing Vwc to Vmin, displacing a part of the WF (air) to HPC 8. [0425] Additional displacing WF to HPC 8 with combustion inside Cylinder 15, caused by Injector 25A. [0426] During increasing Vwc from Vmin to Vbe, displacing combustion product from tube 8F to Cylinder 15. For this purpose, using the inertial property of the gas flowed from WCHPCO 18. Due to the high speed of this flow, the WF cannot return to Cylinder 15, and without mixing with the combustion product that has been partly directed to cylinder 15 from at least single Tube 8F. This product is created by combustion in Tube 8F due to Injector 25B. Due to appropriate volume of Tube 8F, combustion in Tube 8F has been finished before input to Cylinder 15. After closing WCHPCO 18, expansion of combustion product inside Cylinder 15 begins. So, only a part of exhaust from Cylinder 15 caused by combustion during a short time.
Explain to Table_Z1
[0427] So as Table_Z1 used only to compare parameters, supposed, that no loss of heat to walls of WC and expander. If calculate this loss according to empiric formula for ICE (from many versions, selected not too optimistic and not too pessimistic), efficiency (Ef) diminish to (1.5-2.5)%. Comparing to prior art ICE, this small drop of Ef caused by mentioned smaller time for heat transfer, smaller temperature of gas, larger temperature of walls and using 2 pistons in the same cylindersee SUMMARY OF THE INVENTION . . . This empiric formula is for large vortex, that need for better combustion, but increase thermal loss, while in this invention, vortex is smaller and so smaller thermal loss. The formula is: X=(1+1.24*pvm)*(T*P.sup.2*10.sup.10).sup.0.33, where Xthermal transfer coefficient, pvmpiston mean velocity.
[0428] In Table_Z1, Ef includes viscosity loss in regenerator, vortex and friction loss. For example, in string 6, Ef=63.0%, but without this loss, Ef=63.5%; this small distinction due to roller bearings (that is problematic for prior art, see below Regulation near HPDP) and a small moving of piston under maximum P (large moving in prior art, up to Virtual zero Volume,
[0429] Working mode is according Version c (see above). Zwork=0, adiabatic expansion in WC (cylinder 15), partly isothermal expansion in expander 19. kv=12, kt=2.7, Pbc=0.1 MPa, Pec=3.24 MPa, Tbc=300 K, Tec=806 K, Vbc=Vee=1090 cm.sup.3, Vec=Vbe=91 cm.sup.3, Vmin=45 cm.sup.3, Tmax=1700 K, Tee=634 K. During closing WCHPCO 18, near Vmin, begin combustion in WC with using Injector 25A. Supposed combustion with constant P=Pec, with expansion to Vbe due to appropriate work of Injector 25A. WCHPCO 18 may be open during this combustion and mistakes compensated by any small current of WF across WCHPCO 18. End combustion and closing WCHPCO 18 at Vbe=Vec, Tmax, so P=Pee=Pbc, Zwork=0. Mass of input air (in Vbc) is 1.32 g, from it 0.63 g with Pec, Tec is sent to HPC 8. Inside HPC 8, THPC=1500 K>Tec, so as before input to expander 19, take place heating in regenerator 23 (between hot and cool gas, dTr=14 K) and then combustion using Injector 25C (this combustion no need if minimum power, but Table_Z1 calculated for maximum power).
[0430] Compression energy CE=1/(ka1)*(Pbc*VbcPec*Vec)Pbc*(VecVbc)=367 J. Addition 140 J caused by output a part of compressed air dV=VecVmin=46 cm.sup.3 to HPC 8, the same dV and 140 J returned by heat expansion during mentioned combustion from Injector 25A. Pair of buffers 51 must supply 367+140=507 J. Moving piston cause addition friction loss according dV=46 cm.sup.3. For Version a (above), dV=0. In prior art, piston push all volume Vec=91 cm.sup.3.
[0431] In Table_Z1 named: Qregheat, transferred in regenerator 23; Veexpart of volume of expander 19 with isothermal expansion, begin combustion after end input from HPC; J/cyclework in cycle; Efefficiency.
TABLE-US-00001 TABLE_Z1 Engine with partly isothermal expander Qreg, J Veex, % J/cycle Ef, % string 0 0 635 62 1 0 11 799 60.9 2 4 18 858 60.4 3 39 22 878 60.9 4 75 26 901 61.5 5 219 47 964 63 6 454 96 997 63.7* 7 *Examples for dTr and gas friction loss QrL in regenerator: dTr = 14 C., QrL = 4 J, Ef = 63.7%; dTr = 24 K, QrL = 2 J, Ef = 63.5%; dTr = 5 K, QrL = 11 J, Ef = 63.5%. So, dTr = 14 K seems the best (Ef = 63.7%), but prefer dTr = 24 K, so as near the same efficiency may get with twice smaller regenerator and so lower cost and weight.
[0432] From Table_Z1 may see that for engine without regenerator, a good efficiency, but a small power (J/cycle), may get with adiabatic expansion in expander (string 1). The same engine with partly isothermal expansion have a smaller efficiency, but power increase (string 3 is local minimum of efficiency, when regenerator only begin to work).
[0433] The best mode seems at string 7, but even a mean size regenerator with optimal dTr improve parameters of engine (string 6) and this case seems as optimal, see
There are Mentioned Injectors 25 (A-D) on FIG. 2A
[0434] A. Prefer using a good fuel, so as a short time for combustion in cylinder 15. At a full power mode, using<30% from fuel inside cylinder 15. Prefer using CH4 or H2.
[0435] B. Option if no used regenerator 23. So as a large time for combustion in the HPC, may use a bad fuel.
[0436] C. Option for over-heating after regenerator 23, or addition heating before expander 19 to avoid thermal loss in a long tube 8. A mean time for combustion, but a large temperature before combustion, so may use a bad fuel.
[0437] D. Heating in expander 19 if used regenerator 23. If no regenerator, Injector 25D is option for a pic power. Time for combustion in expander 19 is according to working mode.
[0438] If expander 19 directly connected to a wheel, for the wheel D=50 cm and velocity 120 km/h, need 1270 rev/min that is not a large speed for combustion.
[0439] Combustion in expander 19 begin at a temperature T4>Tec (if used regenerator or Injector 25B or 25C), that help for combustion. Output gas from expander 19 goes across regenerator 23, so is a large time to end combustion.
[0440] So, in the expander 19 no must be used a good fuel.
Explain for PPM (Pulse Pause Modulation)
[0441] Free piston engine (prior art 8, 9) may work with PPM, when piston is fixated at Low Pressure Dead Point (LPDP). Advantage of PPM is wide regulation time for scavenging at LPDP with optimal compression, combustion and expansion time. No crankshaft; output energy used by hydraulic plunger pump and stored in accumulator. For PPM in the prior art used controllable hydraulic valve, that cause large loss. Between other problems of free piston engines, is very small time for combustion.
[0442] In the invention, speed of crankshaft 16 near LPDP and HPDP have independent regulations by controller 29, including possibility to fixate crankshaft 16. So have advantages of prior art, but without problems of it. Time for combustion is regulated, PPM not cause addition loss, the crankshaft no transfer power, small masse, small load on bearings, so used roller bearings, may use plastic or Aluminum crankshaft.
[0443] Due to PPM, possible fine synchronization between working cycle of cylinder 15 and expander 19, for example with input stroke of expander 19 when WF is pushed from cylinder 15 to HPC 8. So, may be used a small volume HPC 8 without large changing of pressure HP_in it (this changing may cause loss efficiency).
Regulation Near LPDP
[0444] For embodiment
[0445] Near LPDP, force caused by buffer 51 is sufficiency smaller than pressure force in HPDP. Prefer, that regulation of cycles per second or fixation of crankshaft 16 take place only at LPDP, and near HPDP a large pressure force partly compensated by inertial force for every working mode. For this purpose, energy from buffer 51 must be more, then Compression Energy CE, and this over energy transferred to kinetic energy near HPDP. So moving parts of assembling 16 include functions of ER and ES (see ABBREVIATIONS OF PARTS). This compensation is not possible in prior art.
Acceleration of Crankshaft
[0446] When crankshaft 16 is fixed at any DP (Dead Point), roller bearings are under static load. When crankshaft 16 is moving, roller bearings are under dynamic load. For good lifetime, permissible dynamic load must be 5-20 times smaller, than static. During moving, inertial forces are against loads from gas forces or from buffer 51, so, dynamic load diminish. It is very useful effect. With smaller dynamic loads, not only roller friction diminish, but may use light roller bearings and so diminish slide friction between rollers and separator, caused by inertial forces from reciprocating moving. To increase mentioned useful effect, may increase masse of parts with reciprocating moving, but prefer diminish inertial moment of rotating parts. For electrical machine with magnetic rotor: Me=L*D*a; I=b*L*D.sup.4 so I=C*Me*D.sup.3, where Me is moment of magnetic force; L, D, I are length, diameter, inertial moment of rotor; C=b/a=constant. I may be very small (with the same Me) if diminish D. So, summed inertial moment is mostly caused by inertial moment of crankshaft 16. Main power output is from expander 19, crankshaft 16 no send power (except a small power to or from electrical machine 22). So, rotating moment, transferred by crankshaft 16, is very small. Crankshaft 16 from Aluminum or plastic may be fast accelerated near any DP by at least a single electrical machine 22. Prefer, that every side of every crankshaft is connected to electrical machine 22. Example below explains mentioned useful effect (partly compensation of gas force).
[0447] Suppose, that radius of crankshaft 16 is R=5 cm, Vbc=1090 cm.sup.3 (see Explain to Table_Z1). Used 2 pistons 16 in the same cylinder 15 (
[0448] Prefer to avoid fixation near HPDP, so exist kinetic energy near HPDP (see above). To compensate Fmax=14360 N, acceleration A of reciprocating parts mast be: A=Fmax/M=2872 m/s.sup.2. Rotation speed Wr is not constant. To get A, must Wr=(A/R).sup.0.5=240 rad/s=2290 rev/min. To get this Wr at HPDP, energy of buffer 51 (
[0449] As calculated, near HPDP, Wr=240 rad/sec. So as was fixation, Wr=0 at LPDP. What Wr is, for example, at angle 90 ? At this angle, near Eb/2=127 J is converted to any kinetic energy C and to energy of pressured gas. If was moving from LPDP, energy used for compression is small (most energy converted near HPDP). Suppose, that C=100 J, so, near angle 90: Wr=(2*C/(mR+M)/R.sup.2).sup.0.5=124 rad/s=1185 rev/min. It is approximately maximum mean rotation speed if fixation near LPDP was zero time, or, without fixation, Wr at LPDP was very small. With mentioned parameters mR=0.3 kg and M=5 kg, cannot sufficiency increase mean speed, so as it cause too large inertial force at HPDP. Due to fixation at LPDP, regulation to low mean speed is unlimited, but Wr at HPDP is near mentioned optimal 240 rad/s. If M=1.25 kg, instead 240 rad/s get 480 rad/s with full compensation of gas force. To calculate minimum M, suppose, that used two Aluminum rods (
[0450] Regulation near HPDP By OE (see Acceleration of crankshaft), is possible regulating a time Tout+Toin (
Synchronization to Expander 19
[0451] Expander 19 may be directly connected to wheel of a car. To regulate rotation moment, may regulate input valve of expander, combustion in expander, regulate output valve of the expander to avoid a large mistake of VER in the expander, or using more than a single expander. Controller 29 with using PPM, regulation of valve 18 and feedback from pressure sensor 32 inside HPC 8, must control frequency of cycles in cylinder 15 according to throughput of expander 19, so that pressure HP_in HPC 8 will be approximately constant.
[0452] With reference to
[0453] With reference to
[0454] With reference to
[0455] Drivers for all valves (20, 21, and 18) may include a spring with a large energy and power, to fast open and close a valve. When opened and closed, a valve fixated by electrical magnet, that can produce a large force to fixate it. This type of driver may find in prior art. If instead output valve 21 used a simple window, diminish useful part of piston stroke.
[0456] With reference to
[0457] Main distinctions from
[0458] The embodiment on
[0465] For
[0469] Working cycle include simultaneously input stroke by compressor 35 and output stroke by expander 34, kinetic energy of assembling 16S diminish that caused by friction and vortex loss; then, simultaneously compression and expansion strokes, kinetic energy of assembling 16S increase, so as expansion energy a-little more then compression energy to compensate mentioned loss. Zwork=0. Air from compressor 35 with Tec goes to HPC 8R, where heated by combustion product from isothermal expander 34 and remote isothermal expander 19, this gas with Tee=Tbe go to input part 40R and then to Atmosphere with output temperature a-little more than Tec (if ideal regeneration, with Tee). Tec is a-little more than Tbc so as kv is small and so as compressor 35 is cooled. If Tec=Tbc and no loss, efficiency is as for cycle Carnot: Ef=1Tbc/Tee. As mentioned, isothermal expansion is due to appropriate speed of combustion, caused by injectors 25A and 25D. Work of Expander 19 is output work, produced by the engine. If the engine used for a car, prefer placing expander 19 near a wheel, and regenerator 8R, 40R near expander 19, to diminish length of tubes 24 with hot compressed gas. Zmachine (34, 35) work with PPM algorithm with synchronization to expander 19 as explained for
[0470] With reference to
[0471] With references to
[0472] With reference to
[0473] Distinction between
Example for n=4 Stage Compressor According to Table_n, String 4.2
[0474] Input to every Compressor stage (C) and output from Expander (E) begin from 180 with force Cfi=2127N. Cfi cause acceleration and input work: wcp=213 J, so during this input, wcp is converted to kinetic energy. Return this wcp will be during compression, from 0 to 180. Fixation of crankshaft is possible near angle 180, where static load on bearings is minimum, it is mentioned Cfi. Maximum acceleration caused by force Efz from expander and begin from 0 with force EfzCfi=127742127=10647N. For compression used mentioned wcp, returned from kinetic energy, and expansion energy (285 J), at all 213+285=498 J. In the table, instead mentioned expansion energy, may see negative energy we (285 J), that get compressor from expander. All expansion energy used for compression (Zwork=0).
[0475] Due to converting between expansion and compression energy, stroke from 00 to 1800 is fast, with large accelerations, and stroke from 180 to 0 is slower, with only kinetic energy, redistributed between moving masses. Moving masses and compressed gas make functions of ES (Energy Source) and ER (Energy Receiver). Note: For n=1, expansion energy is 365 J>285 J, so as near isothermal 4-stage compressor (string 4.2) is better, then adiabatic (n=1). So, for n=1, Ef=63.5, but for string 4.2, Ef=71.5%, that is closer to Carnot cycle with Ef=75%.
In Table_n, n is Quantity of Stages with Adiabatic Compression
[0476] Pbc=0.1 MPa. After last stage: Pec=Pbe=1.22 MPa. For 4 stages: kp1=kp2=kp3=kp4=1.87; kp1*kp2*kp3*kp4=12.2. Vbc=1000 cm.sup.3, Tbc=300 K. Cooling after 1 and 2 stages to Tbcn=322 K, but after 3 stage, to TbcN=305 K=Tbc for last, 4 stage. After regenerator (8R, 40R): TH=Tbe=Tee=1200 K. For Carnot cycle: Ef=1Tbc/TH=75%. [0477] Ef is efficiency of engine; [0478] wcp is input work from all compressor stages; [0479] we is work from expander, all this work used for compression (so Zwork=0); [0480] Cf is summed forces from compressors 35 during output from all stages; [0481] Cfi is summed forces from compressors 35 during input to all stages; [0482] Efz is pic force from expander 34 of Zmachine. [0483] Tec is output temperature of a last stage of compressor (gradus C). If dT in regenerator is 5 C., [0484] Tec+5 C. is temperature of output to atmosphere. The smaller Tec, the larger Efficiency Ef. [0485] Tbcn is temperature after cooling in every stage, but TbcN is temperature before a last stage.
TABLE-US-00002 TABLE_n Engine with multistage compressor. n Ef, % wcp, J wc, J Cf, N Cfi, N Efz, N Tec, C. Tbcn, K TbcN, K 6 72.1 350 280 6769 3501 12521 70 322 305 n Ef, % wcp, J wc, J Cf, N Cfi, N Efz, N Tec, C. Tbcn, K TbcN, K 5 71.9 282 282 6219 2815 12622 79 322 305 4.1 71.1 217 289 5845 2175 12948 112 322 322 4.2 71.5 213 285 5748 2127 12774 91 322 305* 4.3 71.9 211 281 5679 2108 12600 112 305 322 4.4 72.3 206 277 5583 2060 12422 91 305 305 3 70.9 143 291 5462 1432 13036 114 322 305 2 69.7 73 303 5760 726 13580 162 322 1 63.6 0 365 11226 0 16344 348
[0486] From Table_n see, that efficiency Ef increase with quantity of stages n, but n>4 seems too large, so as a small increasing of Ef may be covered by loss in valves. Loss no including in calculations. [0487] Distinctions between strings 4.1-4.4 are cooling Tbcn, TbcN, that cause changing of Ef and other parameters.
[0488] At string 4.4 is the best efficiency (between 4.1-4.4) due to the best cooling.
[0489] For a large cost and large power engine with perfect thermal isolated and a large regenerator (8R, 40R) calculated Ef>63% is close to reality.
[0490] For n=1, we=365 J is compression energy, and it is compensated by work of expander 34. For n>1, summed compression energy for all stages (wcp+|wc|) increase, but it partly compensated by wcp (input to compressor), so the wc part, that give expander, diminish and Ef increase.
[0491] Disadvantage of Embodiment
[0492] Using crankshaft to get and return energy wcp need large inertial moment of crankshaft, so more load on bearings during moving with PPM, so as inertial moment of crankshaft diminish acceleration an sufficiency part of gas force is placed on bearings; the rest part of gas force accelerate piston and connected parts.
[0493] Advantage: no need a buffer.
[0494]
[0495] Note: even for 1 stage compressor, may use this buffer to have a large rotation speed near HPDP, but a smaller speed (up to 0) at LPDP.
[0496]
[0497] With reference to
[0498] The EHE is working according to Brayton cycle. If closed cycle, need hermetic envelope, and LP may be more than Atmospheric pressure. This cause heat from LPC 40 (long and large volume tubes, current initiated by Blower 9LP) is dissipated to Atmosphere. HPC 8 includes Sun Heater 8SH; it may be inside hermetic envelope (not shown) with low thermal conductive gas or vacuum; 8SH is separated from light source with glass that is low transparence for infra red ray. Heat transfer to and from Working Fluid (WF) is with constant pressure HP and LP correspondingly. Compression and expansion in cylinder 15 is adiabatic, with approximately the same kp=HP/LP and the same compression and expansion work (Zmachine). Volume of WF after Sun heater 8SH is more, than after compression in cylinder 15. Addition (due to heating to Tbe) volume of WF with HP=Pbe=Pec, HT=Tbe>Tec, across Thermal Isolated Tube 24 go to Remote Expander 19, where make useful work that converted to electricity by Electrical Generator 46. Remote parts are: 9LP, 19, 24, 40, 46. Other parts are small and placed from back side of Sun Heater 8SH and no dashing a Sun Concentrator (not shown).
[0499] With reference to
[0500] With reference to
[0501] Below explain, how works controller 29. When volume of cylinder 15 is near Vec according to signal from RSS 31, and dP (measured by sensor WCHPCIMDPS 28) is near zero (dP=0), by driver 30 begin opening valve WCHPCO 18. This condition (must be volume Vec when dP=0) is according to regulation, explained below in PPM regulation. During initiating time tini (
[0502] End expansion volume Vee detected by RSS 31, then WCLPOM 21 and WCLPIM 20 are opening by drivers 30, and due to blower 9LP, WF with parameters Pbc=LP and Tbc=LT go inside cylinder 15, while WF with Tee go to LPC 40. Instead blower 9LP, possible ISC, for example see explanation of
[0503] Version with additional Blower 9HP may be needed in case of large pressure drop across Heater 9SH, causing bad work of ISC. Blower 9HP gets addition power, but for this version may be Vec=Vmin and so diminishes friction loss. Every blower 9HP, 9LP is arranged as a rotating mean, capable to working as a turbine or as a compressor according to difference of pressure between input and output of the rotating mean. This rotating mean, when connected to electrical machine, is working as electrical generator or electrical motor and is connected to electrical accumulator across electrical Controller (29). Electrical machine of Blower 9HP is placed out of the hot zone, with appropriate sealing envelope (not shown). Obviously, appropriate control of valves (20, 21, 18, 41) may cause large energy of gas flow when scavenging begins. This energy may be accumulated by Blowers 9LP, 9HP, but this case is more practical for ICE (see explanation below about dWv to Table_Zwork).
PPM Regulation
[0504] Optimal Tbe selected as a compromise between infrared loss from 8SH when Tbe is high, and small Ef, when Tbe is small; Tbe measured by TSSH 48. A throughput of Remote Expander 19 is regulated to keep pressure HP, measured by HPCPS 32, near optimal. If HP is too small, must diminish throughput of expander 19, and vice versa. When HP is optimal, mentioned condition Vec when dp=0 is true. For example, may regulate throughput of expander 19 by regulating input and output valves of expander 19. Note, that for car, power of expander 19 is according to load, but for Sun Power Plantvice versa: power of electrical generator 46 and, so, expander 19, must be according to Sun Heater.
[0505] If used Electrical Generator 46 synchronous type, this regulation cause changing rotating moment of Electrical Generator 46 and so changing electrical current and power, that must be according to power of Sun Heater 8SH. Receiving surface of 8SH is sufficiency more than a surface normal to concentrated Sun rays. Most ray energy, that go across this normal surface, is absorbed by the receiving surface of 8SH, but infra-red loss is equivalent to loss from the virtual normal surface, heated to TH+dt, where dt may be, for example, 20 C. and need for thermal transfer from 8SH to WF.
[0506] Example from Computer Calculation.
[0507] HT=750 K=477 C., LP=7 atm, HP=56 atm, Ef=42% with calculated thermal and friction loss in cylinder 15. For ideal Brayton cycle: Ef=44.6%; for Carnot cycle: Ef=(HTLT)/HT=60%. Diameter of cylinder 15 is 45 mm, stroke 240 mm, cycle work=81 J, so power is 4 kW for 3000 cycles/min. If common efficiency (including loss in Sun concentrator, heater 8SH, expander 19, generator 46) is 25%, and power of Sun radiation is 1 kW/m.sup.2, need Sun concentrator surface 16 m.sup.2. Calculated for this EHE, good Ef=42% caused by scavenging between Cylinder 15 and HPC 8, by PPM regulation and due to using large, but low cost, high efficiency remote expander 19 and generator 46, that impossible for prior art. To increase Ef, must increase HT, that is possible with using special glass (available today), transparent for Sun Spector, but no transparent for infra red loss from heating surface of heater 8SH.
[0508] With reference to
[0509] HPC 8 include Sun Heater 8SH, and HPC 8 separated by valve HPSDV 47 to an input part HPCIP and an output part HPCOP (80P). HPSDV 47 may be directly controlled by dP between two sides of it, or from a driver (not shown), activated by sensor of this dP (not shown), this case dP may be near zero due to high sensitivity of this sensor.
[0510] By combustion in the HPCOP, initiating scavenging between WC (cylinder 15) and HPC, that includes parts 8SH, 26, and 44. Is used PPM. LPC is Atmosphere, WF is air, open cycle, but Versions P and 47P are without combustion (so may be LP>0.1 MPa, closing cycle). Scavenging between WC and LPC is initiated by blower 9.
[0511] With reference to
[0512] After end compression in Cylinder 15 (at volume Vec), begin opening of WCHPCO 18, WCHPIM 41, and begin combustion in the HPCOP, caused by Injector 25A. Combusted product from previously cycle pushed to cylinder 15, so as HPSDV 47 is closed and Injector 25A is placed near HPSDV 47. Simultaneously, compressed air pushed to the HPCIP. So, heat expansion of WF in HPCOP initiates scavenging between Cylinder 15 and HPC 8; scavenging continue when HPSDV 47 is open. When volume of cylinder 15 return Vbe=Vec, end closing of valves WCHPCO 18, WCHPIM 41. So as scavenging caused by combustion in HPCOP, possible Vec=Vmin. So as combustion may continue during scavenging, this scavenging may be fast. May end combustion before than valves 18, 41 are closed, this causes ISC to begin. Scavenging time, when valves 18, 41 are opened, adjusted by controller 29 with feedback from temperature T27, measured by sensor 27, placed in HPCIP. About optimal T27 see explain to
[0513] Version P.
[0514] This case does not need combustion. Main principle: Scavenging between WC and HPC proceeds by changing volume in Expander 19, and then using ISC. By PPM, end compression in Cylinder 15 is synchronistic to at least a part of input stroke of Expander 19, that cause diminishing pressure in part of HPC named HPCIP, while HPSDV 47 is closed. Signals from WCHPCIMDPS 28 and WCHPCOMDPS 43, initiate opening WCHPCO 18 and WCHPIM 41 by controller 29 with appropriate drivers 30, so begin scavenging. Then, due to kinetic energy of WF, pressure in HPCOP and HPCOM 44 diminish, that cause opening HPSDV 47 and scavenging continue with ISC. After scavenging time tsc (see above), valves 18 and 41 are closed.
[0515] Version 47P.
[0516] Instead HPSDV 47, HPSDV 47P is used. Scavenging between Cylinder 15 and HPC 8 proceeds by combination of two factors: increasing pressure in part 8SH due to heating from Sun light, and then ISC. HPC 8 is separated to two parts 8HS and HPCIP with valve HPSDV 47P. When valves HPSDV 47, WCHPIM 41, and WCHPCO 18 are closed, part 8SH is (temporarily) hermetically sealed by WCHPIM 41 and WCHPCO 18, and heating by Sun light causes changing ratio between pressures in parts 8SH and HPCIP. Opening WCHPIM 41 and WCHPCO 18, initiates flow of the WF between the two parts across Cylinder 15; when ratio between pressures in parts 8HS and HPCIP is close to 1, opening the HPSDV 47, thereby proceeding with ISC, with control valves WCHPIM 41, WCHPCO 18 and time tsc as explained. During scavenging, input valve (not shown) of Expander 19 is closed.
[0517] Comparing Between Versions
[0521] With reference to
[0522] The embodiment comprising parts: 7, 8B, 8C, 8H, 9LP, 9HP, 10, 15-22, 24, 26-33, 40, 41, 43, 44-46, 49, 50, 52-56, 58 and optionally 47.
[0523] On View A-A may see items 26 and 44, designed to improve inertial scavenging. Valve drivers 30 are not shown.
[0524] The Heat pump working according to open reverse Brayton cycle, LPC 40 is atmosphere.
[0525] Output of Compressor 7 across Distributor 50 connected to Cool part 8C of HPC and to thermal isolated Buffer Volume 8B, that across on/off valve 54 connected to Expander 19, mechanically connected to Electrical Generator 46.
[0526] At cooling mode, the LPC is a cooling room, and the HPC cooled by external air.
[0527] At heating mode, the LPC is atmosphere, and the HPC cooled by a room air.
[0528] Blowers (turbines) 9LP, 9HP, 9E are working during all cycle from any small power source.
[0529] Working Algorithm Includes:
[0530] Closing WCHPIM 41 and WCHPCO 18, thereby separating the HPC 8 to two parts (8C, 8H); changing a ratio between pressures of WF in these parts, using blower 9HP; opening the WCHPIM 41 and WCHPCO 18, and so initiating flow of the WF between parts 8C and 8H across Cylinder 15, then using ISC; closing the WCHPIM 41 and WCHPCO 18 to end ISC. So, after compression in Cylinder 15, scavenging is initiated by Blower 9HP.
[0531] After expansion in Cylinder 15, scavenging initiated by Blower 9LP.
[0532] Air current across heating section of Heat exchanger 10 initiated by Blower 9E.
Current of Air During Cooling Cycle
[0533] Input air from roomValve 52cIRcompression in Cylinder 15sink heat to Atmosphere in Heat Exchanger 10 with heating section connected by valve 52cEAexpansionValve 52cORto room.
Current of Air During Heating Cycle
[0534] Input air from AtmosphereValve 52HIAcompression in Cylinder 15sink heat to room in Heat Exchanger 10 with heating section connected by valve 52HERexpansionValve 52HOAto Atmosphere.
[0535] All sections of Valve 52 may be connected together mechanically.
[0536] Piston assembling 16 is shown at HPDP (Dead Point when end compression), so volume of Cylinder 15 (WC) is Vmin. Due to scavenging after end compression, Vmin is large and so surfaces of valves WCHPCO 18 and WCHPIM 41 may be large, vortex loss and time for scavenging is small.
[0537] HP scavenging from volume 8C across cylinder 15 to volume 8H is initiated by blower 9HP when valves WCHPCO 18 and WCHPIM 41 are open. Power of blower 9HP is regulated by controller 29 for optimal HP scavenging. It is optimal when temperature after output from cylinder 15, T27, measured by HPCIMTS 27, is a-little smaller than Tec; Tec=Tbc*kv.sup.(ka-1), Tbc measured by TSBC 45, kv may be regulated by valves 20 and 21. T27<Tec due to partly mixing in cylinder 15 with input air with Tbe, measured by TSBE 55. In case of over scavenging, a large part of input air with Tbe goes to output from Cylinder 15, so T27 sufficiency smaller then Tec. Over scavenging cause increasing of vortex loss.
[0538] During HP scavenging, air with begin parameters HP, T27, is pushed across Heat Exchanger 10 by Blower 9HP and is cooled. Air across heating section of Heat Exchanger 10, is pushed by Blower 9E.
[0539] If the Heat pump working with cooling mode, heat from compressed air (T27, HP) is sinking to Atmosphere; with heating mode, this heat sinking to a room; reconnection between Atmosphere and the room by Valves 52cEA, 52HER.
[0540] After end expansion in cylinder 15, WCLPIM 20 and WCLPOM 21 must be open, and cooled (due to adiabatic expansion) air across 52cOR go to the room; at heating mode, this cooled air go to Atmosphere across 52HOA.
[0541] Optimal LP scavenging is controlled by: sensor TSBC 45, measuring Tbc, that is as well temperature of scavenging air in input of cylinder 15; by sensor TSILPC 58, measuring mean temperature after output from cylinder 15, it is T58; by TSBE 55, measuring Tbe. For optimal LP scavenging, T58 is a-little more than Tee, Tee=Tbe/kv.sup.(ka-1). If over scavenging, T58 is too large, that caused by mixing with air with Tbc. If scavenging is not good (for example, a small time for scavenging), T58 is close to Tee and throughput of cool air diminish, pumping of heat energy diminish, while mechanical loss is approximately the same and so efficiency of the heat pump diminish.
[0542] Over scavenging not diminish pumping of heat energy, but increase vortex loss. For air conditioner, over scavenging is not critical (in any case, output air is mixed with hot air in the room), but prefer avoid over scavenging if the heat pump used for refrigerator.
[0543] Throughput of the Heat Pump Controlled by PPM.
[0544] If HP, measured by HPCPS 32, increase over desired level, part of throughput of Remote Compressor 7 must be directed to buffer 8B across Distributor 50 and thermal isolated tube 24.
[0545] Buffer 8B is large volume, thermal isolated and used as energy source for Remote Expander 19, connected to Electrical Generator 46. Pressure inside Buffer 8B is measured by HPCBPS 56. If this pressure is smaller then desired minimum, must close valve 54, and vice versa.
[0546] If throughput of Remote Compressor 7 is too small, may using an addition compressor (not shown) from any energy source, for example from Remote Expander 19, reconnecting it to the addition compressor.
[0547] One of advantages of Heat Pump (
[0548] Version with Valve HPSDV 47 may work without Blower 9HP, but preferably with using for heat pump only mentioned addition compressor (below named compressor). This method for the heat pump, with scavenging at least by changing of an external volume (in this case, the volume in a compressor of positive displacement type). For this version, providing phase difference sensors (not shown), arranged to detect difference between cycle phases of Cylinder 15 and the compressor. Controller 29 provides synchronization between cycles of Cylinder 15 and the compressor, using signals from HPCPS 32 and the phase difference sensors, so that pressure in HPC 8 will be approximately as desired, and after end compression in Cylinder 15, take place at least a part of an output stroke of the compressor. So, when HPSDV 47 is closed, initiating ISC. Adjusting the optimal scavenging duration, for optimal T27, as explained above.
[0549] Synchronization with Compressor 7, working from wind energy (and so with wide swing of rotation speed) may be problematic, so this version is practical only with mentioned additional compressor.
[0550] With reference to
[0551] The embodiment (
[0552] Calculations are for adiabatic process. Above in Explain to Table_Z1 mentioned, that heat loss may diminish Ef to 1.5-2.5%. Mass of fuel is smaller than 5% from mass of air. Volume of HPC is 1500 cm.sup.3; Vbc=1000 cm.sup.3, Tbc=300 K, Pbc=0.1 MPa, Pec=3.975 MPa, Tec=859 K; Tbe=Tmax=2000 K; Pee=0.1043 MPa, Tee=697 K. Virtual work, workv=0.06 J, may be caused by expansion from Pee, Tee, Vee=Vbc, to virtual: Pbc, 688 K, 1030 cm.sup.3. This work named virtual, so as it may be used (for example, by turbine), but often it is not used even in prior art, where workv is large. There, workv is small and may be used for ISC. Used heat=826 J. Tbe/Tee=Tec/Tbc=2.87.
[0553] Work: 0.06 (workv)+20.5 (Zwork)+510 (expander)=530 J; Ef.=530/826=64%, if no loss of heat to walls of WC and expander. Temperature in HPC, THPCes=1246 K, calculated supposing a full mixing inside cylinder 15 during output to HPC, caused by combustion. In Table_Zwork (below) may see, that THPCes caused by Vbe. Really, THPCes is smaller, and without mentioned mixing, THPCes=Tec. To get a full power, must addition combustion in HPC 8 or in expander 19, and combustion in cylinder 15 to Tmax. Combustion in HPC 8 or expander 19 is better than in WC (cylinder 15) so as more time, more temperature at begin combustion, better mixing. So, for the same fuel, output from expander is clearer than output from WC. So, for clearer output, prefer to diminish output from WC. Below, mass of combusted product, that go from WC to atmosphere, named Moutwc, and all output named Mout (for a full power). Both Moutwc and Mout caused by the same proportion coefficient k (according to combustion energy of fuel, that is near 47e6 J/kg; mass air/fuel, is 15-20 for a full power).
[0554] From mass of air in cycle, Mbc=1161 mg, and mass, displaced from WC to HPC, mtoHPC=639 mg, may calculate Moutwc/Mout. So, Moutwc=(MbcmtoHPC)*(TmaxTec)*k; Mout=Mbc*(TmaxTec)*k; Moutwc/Mout=X=(MbcmtoHPC)/Mbc=522/1161=0.45. Calculating X by another way: X=300/688*1030/1000=0.45.
[0555] Due to PPM, combustion inside WC may be optimal, so as possible regulation a time for combustion (see explain of PPM for
[0556] Zwork used by the Hydraulic pump 16G, that include electrical controlled input valve 16V and automatic Output Valves 16O. As example, mean velocity of piston and plunger (assembling 16P) is 8 m/s and it is velocity of oil mass 5G; kinetic energy of oil is lost and for 2 pumps and 2 strokes is 0.3 J (for
[0557] For oil velocity 4 m/s across valve 16V, dP=0.8N/cm.sup.2. Surface of valve 16V is 2 cm.sup.2, so an electrical magnet must make 1.6N (in this case, the magnetic gap>0) to compensate this dP. If acceleration of valve 16V is 1 mm during 1 ms, and mass 5 g, mean acceleration force from spring is 10 N, pic force is 20 N. So, the electrical magnet must make>21.6N when magnetic gap is zero. Electrical magnet at
[0558] Calculated above small loss (0.3 J=0.05% from the cycle work) in valve 16V is due to fixation of assembling 16G by crankshaft, but not by any valve. For prior art [9], fixation caused by closing a valve (named in the Prior Art a FREQUENCY CONTROL VALVE), and driver of it must compensate force, for this example: 2000 N/2 cm.sup.2*2 cm.sup.2=4000 N, so construction of this valve must be another and loss in it is more. From prior art [9]: . . . the frequency control valve of 50 bar would for example result in an energy loss of 31 J. Compared to a total pump work of 410 J, this would be a loss of 7.7% . . . . This then sets the requirements for the frequency control valve: a rather large valve with an extremely fast opening response time. An opening time of a few milliseconds is acceptable since the valve can start to open at the end of the previous stroke . . . .
[0559] Compare loss 7.7% in valve of prior art [9], with loss 0.05% in valve according to
Table_Zwork Illustrate Working of Engine with Hydraulic Pump (FIG. 7)
[0560] Zwork (Zw)=EWzCWz, where EWz is expansion, and CWz is compression works in Zmachine; if Zw>>0, it used by the hydraulic pump. Main output (EW) is from Expander. dWv=virtual work for expansion from Pee, Vee=1000 cm.sup.3, to 1 atm up to virtual volume Vwcv,cm.sup.3; work=Zw+dWv+EW, Ef=work/heat (if no loss). Vwcv no exist in reality in this embodiment; it included to work, so as it may be used by any addition volume (VwcvVee), but it is not practical. CWz=376 J, Pec39.7 atm, Tec859K, Tmax in WC=1900 K; gas with THPCes from HPC go to expander; Vec=72, Vmin=67 cm.sup.3. Changing of parameters caused by begin expansion volume Vbe.
TABLE-US-00003 TABLE_Zwork Engine with hydraulic pump Zw Vbe Tee Pee dWv Vwcv Work EWJ THPCes Ef J cm.sup.3 K MPa J cm.sup.3 J J K % 18.9 71.5 662 0.104 0.05 1026 497 478 1216 64.2 108 81.5 697 0.124 1.87* 1166 520 410 1179 64.5 194 91.5 730 0.145 6.09 1303 549 349 1153 64.7 236 96.5 746 0.156 9.04 1371 565 319 1140 64.8
[0561] From TableZwork may see, that Zw (Zwork) may be a sufficiency part of the full output work (530 J); for prior art, Zw is a full work of engine and so dWv, that practically not used (to use it, must expansion from Vee=1000 cm.sup.3 to Vwcv, that for prior art is sufficiency more, than in Table_Zwork), cause a loss of efficiency. In embodiment
[0563] Below example about friction loss in bearings and rings (
TABLE-US-00004 TABLE_fr Friction loss Vmin fzr bfr dWv Zw cm.sup.3 J J J J 71.5 4.1 0.3 0.07 20.6 56.5 4.73 2.9 0.05 19.7 46.5 5.13 3.8 0.03 15.4
[0564] From the last string may see, that if after end compression at Vec=72 cm.sup.3, piston continue moving to Vmin=46.5 cm.sup.3 with pushing compressed gas to HPC, friction loss is maximum: 5.13+3.8=8.93 J, that caused by moving piston and crankshaft against Pec. Then displacing compressed gas continues by any of methods explained above. For Prior Art [3] with proportional sizes, Vmin=0, all gas pushed by piston, and loss is sufficiency more than for Vmin=46.5 cm.sup.3.
[0565] Optimal is Vmin=71.5 cm.sup.2: due to near zero moving piston after end compression, friction loss is minimum (4.4 J). dWv=0.07 J used for inertial scavenging, that help to Blower 9.