Heat engine with a dynamically controllable hydraulic outlet

Abstract

A heat engine with a dynamically controllable hydraulic outlet driven by a high-pressure pump and a gas turbine that include a pressure vessel (1), a lid (1.1), a movable partition (2), a gas working space (4), a liquid working space (5), and a recuperator (7), wherein a sealing (1.4) is disposed between the pressure vessel (1) and the lid (1.1), wherein in the inner space of the pressure vessel (1) the partition (2) is movably attached to a folded membrane (3) which is attached to the lid (1.1), wherein the partition (2) divides the inner space of the pressure vessel (1) into the gas working space (4) and the liquid working space (5), and shaped parts (1.8) are arranged within the pressure vessel, which define an external gas channel (10) which is led between a shell of the pressure vessel (1) and the shaped parts.

Claims

1. A heat engine with a dynamically controlled outlet, driven by a high-pressure pump and a gas turbine comprising: a pressure vessel having an inner space, a lid, a movable partition, a gas working space, a liquid working space, and a recuperator, characterized in that: a sealing is disposed between the pressure vessel and the lid, wherein in the inner space of the pressure vessel, the partition is movably attached to a folded membrane which is further attached to the lid, wherein the partition divides the inner space of the pressure vessel into the gas working space and the liquid working space, wherein the gas working space occupies a larger area thereof, the gas working space being surrounded by a folded permeable membrane in the area of the first partition, and further, shaped parts are arranged within the pressure vessel, which define an external gas channel, wherein the external gas working channel is led between a shell of the pressure vessel and the shaped parts, a circumferential gas channel is located between the shaped parts and the folded membrane and further between a first permeable membrane and the partition, wherein the gas working space is filled with a micro structure made of a solid material with porosity higher than 99% of its volume, and is surrounded by a second permeable membrane to which a recuperator is connected, a heating exchanger being positioned within the recuperator and connected to an inlet and outlet of a heat transfer medium, wherein the recuperator is further surrounded by the shaped parts, and is separated from the gas working space by the second permeable membrane, the external gas channel is fed into space of the recuperator on the opposite side of its connection to the gas working space, wherein the external gas channel is connected to a pneumatic actuator chamber, into which is further fed an inner gas channel, connected to the circumferential gas channel.

2. The heat engine according to claim 1, characterized in that the pneumatic actuator comprises a stator and a rotor of an electric engine and a chamber in which an impeller is positioned with blades and gas rectifiers, wherein the impeller is connected to a shaft of the rotor of the electric engine by means of a flat spring, wherein the rotor of the electric engine is housed in a magnetic bearing or a bearing.

3. The heat engine according to claim 1, characterized in that, the shell of the pressure vessel constitutes a middle part, which is disposed between the lid and a bottom, wherein the bottom abuts a ring, which is disposed on a dispensing plate, wherein the dispensing plate is connected to the lid by means of studs and further the sealing is disposed between the lid, the middle part and the bottom.

4. The heat engine according to claim 1, characterized in that the microstructure (4.1) is a material with porosity higher than 99% based on its overall volume, with density from 110.sup.4 to 0.03 g cm.sup.3.

5. The heat engine according to claim 1 characterized in that the micro structure is selected from one of group consisting of: carbon, ceramic, metal microfibers, nano-fibers, aero-graphite, and graphite aerogel.

6. The heat engine according to claim 1, characterized in that the folded membrane (3) is impermeable to gas.

7. The heat engine according to claim 1, characterized in that the micro structure is disposed between meshes arranged at a distance from each other, wherein the meshes are disposed in planes perpendicular to a motion vector of the partition, which are connected to the folds of the folded permeable membrane.

8. The heat engine according to claim 7, characterized in that the meshes are formed of carbon, ceramic or metal fibers, wherein mutual distance of the meshes and mesh fibers in the plane thereof are in the range of 100 to 10,000 times the mean distance of the micro structure elements.

9. The heat engine according to claim 4 characterized in that the micro structure is selected from one of group consisting of: carbon, ceramic, metal microfibers, nano-fibers, aero-graphite, and graphite aerogel.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) The invention will be explained with reference to the accompanying drawings, where

(2) FIG. 1 illustrates an exemplary embodiment with an internal exchanger in the expansion phase,

(3) FIG. 2 illustrates an exemplary embodiment with an internal exchanger in the compression phase,

(4) FIG. 3 illustrates a detail of an electric recuperator,

(5) FIG. 4 illustrates an exemplary embodiment of a heat engine with an exchanger in the shell in the expansion phase,

(6) FIG. 5 illustrates an exemplary embodiment of a heat engine with an exchanger in the shell in the compression phase,

(7) FIG. 6 illustrates a detail B of the embodiment of a gas actuator, in an embodiment with a roller bearing,

(8) FIG. 7 illustrates a view of an A-A section of a pneumatic actuator,

(9) FIG. 8 illustrates a detail of the pneumatic actuator in the embodiment with the magnetic bearing,

(10) FIG. 9 illustrates the actuator impeller,

(11) FIG. 10 illustrates a detail C of the embodiment of the filling of the working space,

(12) FIG. 11 illustrates; an exemplary embodiment of the mesh,

(13) FIG. 12 illustrates a detail of the D embodiment of the mesh edge fastened to the folds of the folded permeable membrane.

DESCRIPTION OF AN EXEMPLARY EMBODIMENT

(14) The present invention will be explained in the following description of an exemplary embodiment of a heat engine with a dynamically controllable hydraulic output with reference to the corresponding drawings. In the present drawings, the invention is illustrated by means of an exemplary embodiment of a heat engine with an internal heat exchanger and a heat engine with a heating heat exchanger in the pressure vessel shell.

(15) The heat engine with an internal heat exchanger is shown in FIGS. 1 and 2. In this embodiment the heat engine consists of a pressure vessel 1 and a lid 1.1 between which a seal A A is arranged. The pressure vessel 1 is in cylindrical shape and is optimal from the perspective of volume compactness and internal pressure, wherein such a container shape is not a prerequisite for the correct operation of the apparatus. The pressure vessel 1 is. further divided by a partition 2 into Iwo working spaces. These are a gas working space 4 and a liquid working space 5, into which is fed a liquid channel 5.2, which is terminated by a hydraulic inlet/outlet 5.1, serving to discharge the mechanical work from the heat engine. The gas working space 4 occupies a larger portion of the pressure vessel 1, its optimal shape is compact, similar to ball with the smallest surface relative to the volume, wherein this gas working space 4 is surrounded by a first permeable membrane 4.5, a folded permeable membrane 4.4 and a second permeable membrane 4.6. In addition, shaped parts 1.8 are provided within the pressure vessel I which define the external gas channel 10 which is located between the shell of the pressure vessel 1 and the shaped parts 1.8; while the circumferential gas channels 4.3 are located between the shaped parts 1.8 and the first permeable membrane 4.5, partition 2, folded membrane 3 and folded permeable membrane 4.4. In order to ensure an arranged and definable movement 12 of the working gas and to minimize the temperature changes of the working gas due to chaotic flow, heat radiation and conduction within the gas working space 4, it is filled with a microstructure 4.1 This microstructure 4.1 consists of a material resistant to cyclic temperature changes in the engine temperature range and has sufficient resilience and strength within this temperature range. The microstructure 4.1. has porosity greater than 99% based on its total volume, with a density of from 110.sup.4 to 0.03 g cm.sup.3. Uniformity and the method of joining individual elements in the microstructure 4.1 must allow for volumetric changes without permanent deformation and with a high service life. Suitable materials for making the microstructure 4.1 are carbon, ceramic and metal micro and nanofibres, aerographite, graphite aerogel or other materials meeting the abovementioned conditions of material properties.

(16) This microstructure 4.1 can be reinforced by meshes 4.2 spaced apart from each other, wherein the meshes 4.2 are oriented perpendicularly to the direction of dimensional changes of the gas working space 4 during the working phases. The meshes 4.2 are formed by intertwined fibres within a ring having a V or W shape turned by 90. The fibres in the form of a netting can be attached to the rings by soldering, gluing, pressing into the edge of one ring or between two rings, or by inserting between two rings before welding. The rings and therefore the folded permeable membrane 4.4 are made of thin metal plate with high elasticity and fatigue resistance; the ideal material is alloy steel or titanium alloy. The rings are provided with holes 4.7 on the circumference, which provide for the folded permeable membrane 4.4 assembled from these rings its permeability to the working gas; see FIG. 10 and FIG. 12. The spaces between the meshes 4.2 are filled with the microstructure 4.1. The purpose of the meshes 4.2 is to maintain the uniform microstructure 4.1 both in the changes in the volume of the gas working space 4 and in the internal movement 12 of the working gas. The arrangement of the meshes 4.2 and the microstructure 4.1 within the gas working space 4 is illustrated in FIG. 10 and FIG. 11. FIG. 12 illustrates a detail D of the embodiment of the edge of the folded permeable membrane 4.4. For high temperature applications, the mesh 4.2 fibres could be made of carbon, ceramic or metal.

(17) The design of both the gas working space 4 and the liquid working space 5 must allow movement of the partition 2, which separates them. The design of the partition 2 and the folded membrane 3 is designed to withstand the pressure in the gas working space 4 even after the liquid has been discharged from the liquid working space 5. The folded membrane 3 forms at the same time a heat exchange surface between the working gas flowing in the internal gas channel 10.1 and the hydraulic liquid within the liquid working space 5, forming a second heat exchanger. In this part of the circumferential gas channel 4.3, the working gas will be conducted so as to maximize the heat exchange between the working gas and the folded membrane 3. The flow of the working gas in one phase (in the other one vice versa) will be conducted from the chamber of the pneumatic actuator 6 to the internal gas channel 10.1, then in this part of the circumferential gas channel 4.3, then to the permeable membrane 4.5 and the folded permeable membrane 4.4 into the gas working space 4 and into the recuperator 7, in which a heat exchanger 8 is disposed, which is connected to the inlet 7 outlet 8.1 of the heat transfer medium, the working gas is further passed through the external gas channel 10 to the chamber 6.1 which is a part of the pneumatic actuator 6. Structurally it is necessary to ensure best possible ratio between the volume of the gas working space 4 and the volume of the other parts of the heat engine in which the working gas is located.

(18) FIG. 3 illustrates a variant of an embodiment of the recuperator 7 with an electric heating element 8.2. In this embodiment, the electric heating element 8.2 is connected between the recuperator 7 and the gas working space, which is electrically connected by means of electrical wires 9.1 to a control unit 9, which is connected to a source 9.2 of electric voltage. The recuperator 7 further abuts the shaped parts 1.8 and is separated from the side of the gas operating space 4 by the second permeable membrane 4.6, wherein the second end of the recuperator 7 is connected to the external gas channel 10.

(19) The function of the heat engine in this embodiment is as follows. The movement of the working gas within the gas working space 4 extends from the centre of the gas working space 4 to the inner shell of the pressure vessel 1 and vice versa. Filling of the gas working space 4 serves to ensure a uniform flow of the working gas within the working space and also due to the alternation of the flow direction of the working gas to the formation of a high temperature region 14 moving during the working phases in almost the entire volume of the gas operating space 4. Flow direction and rate of the working gas varies throughout all parts of the heat engine. Upon a request for pressure increase and compression in the liquid working space 5, the working gas flows from the pneumatic actuator 6 through the external gas channel 10 through the recuperator 7 and the heat exchanger 8.2 through the internal volume of the gas working space 4 into the circumferential gas channels 4.3. In this way, the average temperature of the working gas inside the device increases and there is an increase in pressure and expansion in the gas working chamber 4 and at the same time compression occurs in the liquid working space. With the request to reduce the pressure and expansion in the liquid working space, the working gas is conducted from the pneumatic actuator 6 through the internal gas channel 10.1 to the circumferential gas channels 4.3 disposed at the walls of the gas working space 4, further through the inner volume of the gas working space 4 and then through the heat exchanger 8 and recuperator 7. This reduces the average working gas temperature inside the device, and pressure reduction and compression occurs in the gas working space 4, while at the same time expansion occurs in the liquid working space. The liquid working space 5 reacts to the expansion and compression of the gas working space 4 with practically the same working pressure, the working space 5 decreases upon expansion of the liquid working space 4 at the same ratio; and the working space 5 increases upon compression of the gas operating space 4 at the same ratio. The engine performs work by changing the pressure and volume in the liquid working space 5. The sum of the volumes of both working spaces 4 and 5 is practically the same in all working phases. The engine in different operating phases is shown in FIGS. 1 and 2. In the case that the engine will operate at the inlet/outlet of the heat transfer medium 8.1 at temperatures lower than in the liquid working space, and in the case that the heat transfer medium will remove heat from the engine, the phases of expansion and compression will be reversed with respect to the direction of the internal flow of the working gas.

(20) The inventive pressure vessel 1 with an internal heat exchanger in technical practice must resist only to normal temperatures at the outlet of the working gas from the recuperator 7 to the external gas channel 10.

(21) Another embodiment of a heat engine with a heat exchanger at the shell of a pressure vessel is illustrated in FIG. 4 and FIG. 5. This embodiment of the heat engine is different from the solution shown in FIG. 1 and FIG. 2. The embodiment differs in the design of the pressure vessel 1, which must in this case withstand high temperatures. The pressure vessel 1 consists of the following parts. A central part 1.2, which is disposed between a lid 1.1. and a ring 1.5. A central part 1.2 abuts a bottom 1.3 which is supported on the ring 1.5, wherein said ring is connected to the lid 1.1 by means of studs 17 which pass through the dispensing plate 1.6. Further, a seal 1.4 is provided between the lid 1.1 and the central part 1.2 and also the bottom 1.3 of the pressure vessel 1.

(22) From the point of view of the efficiency of the heat engine, it is necessary that the abovementioned parts of the pressure vessel A be made of a material with the highest thermal resistance possible and at the same time with a mechanical strength that is capable of withstanding the changing internal pressure. Common materials that withstand high temperatures have solid crystalline atomic bonds but they withstand the cyclical effects of stress and relaxation only with difficulties. This load may in places of natural defects cause them to increase and thus gradually reduce the strength of such material. These loads also result from uneven heating of parts. Optimal design of parts loaded with high temperature ensures that they ate in constant pressure and do not create relaxation states with internal tensions. This can only be achieved by introducing additional pressure on the part by preloading it. This preloading should be introduced into these parts of the pressure vessel 1; into the central part 1.2, into the ring 1.5 and into the bottom 1.3. The ideal preloading material is carbon fibre, which is capable of transferring high tensile stress even at high temperatures. In the present embodiment, said parts of pressure vessel 1, such as the bottom 1.3 of the pressure vessel and the central part 1.2 of the pressure vessel 1, are designed as a composite of high tensile stress crystalline material at high temperatures and preloaded carbon fibres as a high tensile stress material at high temperatures. Moreover, the material of the bottom 1.3 of the pressure vessel 1 is also required to be of the highest thermal conductivity or energy permeability, especially for electromagnetic radiation, in respect to the function of its inner face as a heat exchanger. The ideal material for the bottom 1.3 of the pressure vessel is, in terms of thermal conductivity, for example, crystalline silicon carbide (SiC), or its modifications. In terms of energy permeability, sapphire glass (Al.sub.2O.sub.3) is the ideal material for the bottom of the pressure vessel.

(23) The shell of the pressure vessel 1 adjacent to the external gas channel 10 can at the same time also serve as a heat exchanger and a heat recuperator in the variants of FIG. 1 and FIG. 2 as well as in the variant of FIG. 4 and FIG. 5, thereby complementing the function of the folded membrane 3 as a heat exchanger.

(24) As can be seen from the accompanying drawings, the individual connected components of the heat engine are sealed using the seal 1.4. The lid 1.1 of the pressure vessel 1 is provided with an access to the pneumatic actuator 6 in the form of a service lid 6.2. In the case of a maintenance-free version of the pneumatic actuator 6 with magnetic bearings 6.8, it is possible to make joints on the service lid 6.2 as well as a permanent joint during production with higher impermeability.

(25) In order to ensure the lowest possible hydraulic losses and quick engine reactions, large cross-sections of the liquid channels 5.2 are preferable. The liquid in the liquid working space 5 also serves as a cooling medium. As the power increases, liquid exchange in the liquid working space 5 increases as well, and so does also heat dissipation from the heat engine. In the design of the connection of the liquid channels 5.2 to the liquid working space 5, it is preferable to provide a support of the one-way circular flow of the internal liquid within the liquid working space 5 so as to maximize liquid exchange and transfer of heat to or from the folded membrane 3 in the liquid working space 5.

(26) The largest area for cooling the working gas is the folded membrane 3, in addition to its surface; also its small thickness is advantageous. In an exchanger of such a design, the volume of the working gas bound in its space at the completion of the expansion phase reduces, which helps to increase the efficiency with minimal volume of the working gas outside the gas working space. The folded membrane 3 may be supplemented with other heat exchange surfaces and elements providing a greater flow around the entire surface thereof.

(27) It is possible to modify the design with respect to a specific assignment of output dynamics, average power and peak performance requirements. Appropriate dimensioning of individual parts of the system can greatly enhance the required hydraulic output 5.1 characteristics. Upon requiring high dynamics and efficiency, the device can be designed with heat exchangers with a large heat transfer surface, optimal heat storage capacity in the recuperator 7. The recuperator 7 and heat exchangers should have the best ratio of pressure loss and efficiency. The higher power of the pneumatic actuator 6 and the cross-sections of the internal and external gas channels 10.1 and 10 can provide greater engine dynamics. For high dynamics, helium is also a preferred working gas.

(28) As can be seen from FIG. 1, FIG. 2, FIG. 4 and FIG. 5, the pressure vessel lid 1.1 of both of the heat engine variants described is identical. Details of an embodiment of the pneumatic actuator 6 in variants with different bearings are illustrated in FIG. 6 and FIG. 8. With this arrangement of the pneumatic actuator 6, a space is provided in the cover 1.1 for their placement. This space is covered by a service lid 6.2. A seal 1.4 is provided in the space between the service lid 6.2 and the lid 1.1. In this space, the stator 6.6 and the rotor 6.5 of an electric engine and the impeller 6.3 are arranged. The rotor 6.5 of the electric engine is stored in the magnetic bearing 6.8 and/or the ball bearing 6.7. The pneumatic actuator 6 comprises a chamber 6.1 and an impeller 6.3. The impeller 6.3 is secured to the rotor 6.5 shaft of the electric engine via a flat spring 6.4. An example of the impeller 6.3 is shown in FIG. 9. The impeller 6b in this embodiment consists in a flat spring 6.4 mounted on a rotor 6.5, which is connected to blades 6.11 which are reciprocally housed by gas rectifiers 6.12.

(29) FIG. 7 illustrates an A-A section through the lid 1.1 of the pressure vessel 1, in which the pneumatic actuator 6 is located. It is evident from the A-A section that there are liquid channels 5.2 in the cover 1.1 between which the internal gas channels 10.1 and the external gas channels 10 are separated by a partition 1.9. Inside the space of lid 1.1 of the pressure vessel 1 is formed a chamber 6.1. of the pneumatic actuator 6 in which the impeller 6.3 is arranged. In the space of the lid 1.1, electromagnets 6.10 which deflect the impeller are located in place above the blades of the impeller 6.3. In the middle of the lid 1.1 of the pressure vessel 1 is located, in its axis, a rotor 6.5 of an electric engine, which forms the axis of the impeller 6.3.

(30) The pneumatic actuator 6 drives and controls the movement of the working gas. This is driven by a rotor 6.5 of an electric engine. The rotation speed rotor 6.5 of the electric engine determines the rate of movement of the working gas. The direction of movement 12 of the working gas is determined by the setting of the impeller 6.3 against a pair of the internal gas channel 10.1 and the external gas channel 10. The change of the setting of the impeller 6.3 is enabled by its elastic attachment to the rotor 6.5 of the electric engines. This resilient mounting allows the impeller 6.3 to deflect in a direction parallel to the axis of rotation. This deflection ideally, but not necessarily, is enabled by the flat spring 6.4 The deflection of the impeller 6.3 in the directions of the axis of rotation of rotor 6.5 can be achieved by means of electromagnets 6.10 but can also be carried out by electronically controlled magnetic bearings 6.8 by firmly coupling the impeller 6.3 with the rotor 6.5 of an electric engine. A position sensor 6.9 measures the actual position of the impeller 6.3 and serves as a feedback means for an electronic control unit 9 for controlling the movement of the impeller 6.3, Wherein the electronic control unit 9 is connected to electromagnets 6.10, magnetic bearings 6.8 and the stator 6.6 of an electric engine by means of electric wires 9.2. In an exemplary embodiment of a heat engine comprising a heat exchanger in its shell according to FIG. 4 and FIG. 5, a temperature sensor/sensors 9.3, preferably provided in the circumferential gas channels 4.3 at the inlet to the gas working space 4, are necessary for controlling the movement of the impeller and thermal protection of the device.

INDUSTRIAL APPLICABILITY

(31) The device can be used as a dynamically controlled hydraulic pressure/volume source for hydraulic actuators with a thermal energy source and with no heed for hydraulic pumps and valves. It can be used wherever hydraulic drives are used and it is preferred for their faster operation and with higher efficiency while using a more available heat source.

(32) In a regular cyclical mode of phase alternation, when the hydraulic output is replenished by two unidirectional valves, the device can serve as a high-pressure pump. The device can be used to gain mechanical work if there is enough thermal energy or in case of inability to use a normal source of motion energy, such as an electric engine, an internal combustion engine, etc. Great possibilities are offered, for example, for the direct transfer of solar energy to mechanical work. In technical practice, the employment of this solution offers wide applicability as a source of energy in the desalination of seawater by the reverse osmosis method.

LIST OF REFERENCE NUMERALS

(33) 1. pressure vessel 1.1 lid of the pressure vessel 1.2 middle part of the pressure vessel 1.3 bottom of the pressure vessel 1.4 sealing 1.5 ring 1.6 dispensing plate 1.7 pretensioned studs 1.8 shaped parts 1.9 channel partition 2. partition 3. folded membrane 4. gas working space 4.1 microstructure 4.2 mesh 4.3 circumferential gas channels 4.4 folded permeable membrane 4.5 first permeable membrane 4.6 second permeable membrane 4.7 hole 5. liquid working space 5.1 hydraulic inlet/outlet 5.2 liquid channel 6. pneumatic actuator 6.1 chamber 6.2 service lid 6.3 impeller 6.4 flat spring 6.5 rotor of the electric engine 6.6 stator of the electric engine 6.7 bearing 6.8 magnetic bearing 6.9 position sensor 6.10 electromagnet 6.11 blades 6.12 gas rectifiers 7. recuperator 8. heat exchanger 8.1 inlet/outlet of the heat transfer medium 8.2 electric heating element 9. electronic control unit 9.1 electrical wires 9.2 source of electric voltage 9.3 temperature sensor 10. external gas channel 10.1 internal gas channel 11. source of radiant energy 12. direction of movement of the working gas 13. direction of movement of the inner parts 14. high temperature gradient area