Ejector heat pump

Abstract

A vapor compression system (200; 400; 600; 700; 800; 900; 1000) comprises a plurality of valves (260, 262, 264; 260) controllable to define a first mode flowpath and a second mode flowpath. The first mode flowpath is sequentially through: a compressor (22); a first heat exchanger (30); a first nozzle (228; 624); and a separator (48), and then branching into: a first branch returning to the compressor; and a second branch passing through an expansion device (70) and a second heat exchanger (64) to the rejoin the flowpath between the first heat exchanger and the separator. The second mode flowpath is sequentially through: the compressor; the second heat exchanger; a second nozzle (248; 625); and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and first heat exchanger to the rejoin the flowpath between the first heat exchanger and the separator.

Claims

1. A vapor compression system (200; 400; 700; 800; 900; 1000) comprises a plurality of valves (260, 262, 264; 260) controllable to define: a first mode flowpath sequentially through: a compressor (22); a first heat exchanger (30); a first motive nozzle (228) of a first ejector; and a separator (48), and then branching into: a first branch returning to the compressor; and a second branch passing through an expansion device (70) device and a second heat exchanger (64) to the rejoin the flowpath between the first heat exchanger and the separator; and a second mode flowpath sequentially through: the compressor; the second heat exchanger; a second nozzle (248) of a second ejector; and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and first heat exchanger to the rejoin the flowpath between the first heat exchanger and the separator, wherein at least one of: the plurality of valves are controllable to; or one or more check valves (920, 922) are positioned to: in the first mode block a reverse flow through the second ejector; and in the second mode block a reverse flow through the first ejector.

2. A vapor compression system (200; 400; 700; 800; 900; 1000) comprising: a compressor (22); a first heat exchanger (30); a second heat exchanger (64); a first ejector (220) having a first motive nozzle; a second ejector (222) having a second motive nozzle; a separator (48) having: an inlet (50); a liquid outlet (52); and a vapor outlet (54); an expansion device (70); and a plurality of conduits, wherein the system further comprises a plurality of valves (260, 262, 264; 260) controllable to define: a first mode flowpath sequentially through: the compressor; the first heat exchanger; the first motive nozzle (228); and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and second heat exchanger to the rejoin the flowpath between the first heat exchanger and the separator; and a second mode flowpath sequentially through: the compressor; the second heat exchanger; the second motive nozzle (248); and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and first heat exchanger to the rejoin the flowpath between the first heat exchanger and the separator, wherein at least one of: the plurality of valves are controllable to; or one or more check valves (920, 922) are positioned to: in the first mode block a reverse flow through the second ejector; and in the second mode block a reverse flow through the first ejector.

3. The vapor compression system of claim 2 wherein: one or more check valves (920, 922) are positioned to block reverse flow through at least one of the first ejector and second ejector.

4. The vapor compression system of claim 2 wherein: the first heat exchanger is a refrigerant-air heat exchanger and the second heat exchanger is a refrigerant-water heat exchanger.

5. The vapor compression system of claim 2 wherein the plurality of valves comprises: a first four way valve (260); and a second four way valve (262).

6. A vapor compression system (200; 400; 700; 900; 1000) comprising: a compressor (22); a first heat exchanger (30); a second heat exchanger (64); a first ejector (220) comprising: a motive flow inlet (222); a secondary flow inlet (224); and an outlet (226); and a separator (48) having: an inlet (50); a liquid outlet (52); and a vapor outlet (54); an expansion device (70); and a plurality of conduits, wherein the system further comprises: a second ejector (240) comprising: a motive flow inlet (242); a secondary flow inlet (244); and an outlet (246); a plurality of valves (260, 262, 264) controllable to define: a first mode flowpath sequentially through: the compressor; the first heat exchanger; the first ejector from the first ejector motive flow inlet through the first ejector outlet; and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and second heat exchanger to the first ejector secondary flow inlet, a second mode flowpath sequentially through: the compressor; the second heat exchanger; the second ejector from the second ejector motive flow inlet through the second ejector outlet; and the separator, and then branching into: a first branch returning to the compressor; and a second branch passing through the expansion device and first heat exchanger to the second ejector secondary flow inlet, wherein at least one of: the plurality of valves are controllable to; or one or more check valves (920, 922) are positioned to: in the first mode block a reverse flow through the second ejector secondary flow inlet; and in the second mode block a reverse flow through the first ejector secondary flow inlet.

7. The vapor compression system of claim 6 wherein: the first ejector and the second ejector are of different sizes.

8. The vapor compression system of claim 7 wherein: the first ejector has a greater throat cross-sectional area than the second ejector.

9. The vapor compression system of claim 7 wherein: the first ejector has a greater mixer cross-sectional area than the second ejector.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic view of a prior art ejector refrigeration system.

(2) FIG. 2 is an axial sectional view of a prior art ejector.

(3) FIG. 3 is a schematic view of a second ejector refrigeration system in a cooling mode.

(4) FIG. 4 is a schematic view of the second ejector refrigeration system in a heating mode.

(5) FIG. 5 is a schematic view of a third ejector refrigeration system in a cooling mode.

(6) FIG. 6 is a schematic view of a fourth ejector refrigeration system in a cooling mode.

(7) FIG. 6A is an enlarged view of a twin ejector assembly of the system of FIG. 6, taken at view 6A of FIG. 6.

(8) FIG. 7 is a schematic view of a twin ejector assembly of FIG. 6 in a heating mode.

(9) FIG. 8 is a schematic view of a fifth ejector refrigeration system in a cooling mode.

(10) FIG. 9 is a schematic view of a sixth ejector refrigeration system in a cooling mode.

(11) FIG. 10 is a schematic view of a seventh ejector refrigeration system in a cooling mode.

(12) FIG. 11 is a schematic view of an eighth ejector refrigeration system in a cooling mode.

(13) Like reference numbers and designations in the various drawings indicate like elements.

DETAILED DESCRIPTION

(14) FIG. 3 shows a modified system 200 wherein various components may be similar to corresponding components mentioned regarding FIGS. 1 and 2. The system 200 is configured to allow at least two normal modes of operation. A first normal mode is a cooling mode similar to the mode described for the system of FIG. 1. A second normal mode is a heating mode wherein the heat absorption and heat rejection functions of the two heat exchangers are reversed. The system 200 may be used for climate control purposes wherein: in the cooling mode chilled water from the heat exchanger 64 is used to cool a building; and in the heating mode heated water from the heat exchanger 64 is used to heat the building. Thus, in this example, the heat exchanger 64 is still a refrigerant-water heat exchanger and the heat exchanger 30 is still a refrigerant-air heat exchanger (e.g., an outdoor heat exchanger transferring heat to or from a fan-forced outdoor air flow).

(15) To provide for switching between these two modes (and any additional modes) relative to the baseline system of FIG. 1, the system 200 may add additional refrigerant lines/conduits and one or more additional refrigerant valves controlling flow along those lines/conduits.

(16) Additionally, the single ejector of FIG. 1 is replaced with two ejectors 220, 240. The ejectors 220 and 240 are respectively associated with the cooling mode and heating mode and optimized in size and any other properties for use in those respective modes. The respective ejectors 220, 240 have respective motive flow or primary flow inlets 222, 242; suction flow or secondary flow inlets 224, 244; outlets 226, 246; motive nozzles 228, 248; diffusers 230, 250; mixers 232, 252; and the like.

(17) The exemplary added valves (260, 262, 264) include a four-way valve 260 linking the compressor discharge line/conduit with a conduit/line of the cooling mode secondary loop between the expansion device 70 and the heat exchanger 64. The exemplary valve 262 is also a four-way valve linking the line/conduit of the cooling mode primary loop between the heat exchanger 30 and ejectors on the one hand and a line/conduit of the secondary loop between the heat exchanger 64 and the ejector 220 secondary flow inlet 224 on the other hand.

(18) A third valve 264 is a three-way valve selectively providing communication between the valve 262 on the one hand and either the first ejector secondary flow inlet or the second ejector secondary flow inlet.

(19) FIG. 3 shows refrigerant flow directions associated with operating in the cooling mode. FIG. 4 shows refrigerant flow directions associated with operating in the heating mode.

(20) The exemplary valves 260 and 262 are illustrated as rotary element valves having a rotary element (e.g., rotated manually or via an electric actuator) having a plurality of passageways which selectively register with associated ports in a housing. The exemplary valves 260 and 262 have two sets of passageways: a first set which registers with the housing ports in the cooling mode and a second set which registers with the housing ports in the heating mode. Alternative valves might involve using the same passageways for both modes but with a different orientation. Yet alternative valves include other configurations such as spool valves and the like.

(21) The three-way valve 264 may also be a simple rotary valve, spool valve, or the like. Due to the simple switching function of this valve, its passageways in its valve element are not shown.

(22) Operation in the cooling mode is as described for FIG. 1. The exemplary ejector 240 is effectively disabled. For example, the valve 264 may pass communication to the secondary flow inlet 224 of the first ejector 220 while blocking communication with the secondary flow inlet 244 of the second ejector 240. Similarly, potential motive flow through the second ejector 240 may be blocked via the needle of the second ejector being in a closed condition.

(23) Subject to the action of the valve 264, the two ejectors are effectively physically in parallel with their primary unit inlets 222, 242 in communication with the valve 262 and their outlets in communication with the separator inlet 50. This allows, via use of the valve 264, either of the ejectors to operate and discharge into the separator 48 so that the same separator 48 is used with both ejectors and the system has only a single separator.

(24) In the FIG. 4 condition, the valves are shifted into the heating mode so that compressor discharge (along a primary flowpath or loop 60) passes through the valve 260 to the heat exchanger 64. At this point, it is seen how the switching of modes may change the nominal function of portions of lines/conduits. In the cooling mode, the entire line/conduit between the compressor discharge port 26 and the first heat exchanger 30 inlet 32 would be regarded as a discharge line. In the heating mode, a proximal portion of that same physical line (i.e., the portion between the compressor discharge port 26 and the valve 260) remains a portion of a discharge line but the remainder of the discharge line is now formed by a segment of what had formerly been the secondary loop 62 between the valve 260 and the heat exchanger 64 inlet 66. The remaining section of the cooling mode discharge line between the valve 260 and the first heat exchanger 30 inlet 32 becomes, in the heating mode, a segment of the secondary loop 62 line. In this capacity, the valve 260 thus passes flow expanded by the expansion device 70 to the first heat exchanger 30 inlet 32.

(25) Thus, it is seen that the valve 260 addresses switching of the roles of the heat exchangers 30 and 64 at their inlet ends. Similarly, the valve 262 addresses the role reversal at outlet ends of the heat exchangers in that it passes outlet flows from the heat exchangers. In the FIG. 3 cooling mode, the valve 262 passes refrigerant from the heat exchanger 30 to the ejectors (more particularly, to the motive/primary flow inlet 222 of the first ejector 220 with the second ejector 240 being shutoff). In the cooling mode, the valve 262 also passes refrigerant from the heat exchanger 64 to the secondary flow inlet 224 via the valve 264 (which simultaneously blocks the secondary flow inlet 244 of the second ejector).

(26) In the FIG. 4 heating mode, the valve 262 passes refrigerant flow from the heat exchanger 64 to the ejectors (e.g., to the motive/primary flow inlet 242 of the second ejector 240 in similar fashion to passing of refrigerant to the first ejector 220 in the cooling mode). In the heating mode, the valve 262 also passes refrigerant from the heat exchanger 30 to the secondary flow inlet 244 via the valve 264.

(27) The two ejectors may have one or more of several asymmetries relative to each other to tailor the ejectors for the particular anticipated conditions of respective cooling mode and heating mode operation. For example, one highly likely difference is the throat area. Specifically, first ejector 220 (the ejector used in the normal cooling mode) may have one or more different size and/or capacity parameters than the second ejector 240 (the ejector used in the normal heating mode). The nature and direction of asymmetry may depend on design conditions (e.g., a system designed for warm summers and warm winters may have a difference relative to one designed for cool summers and cool winters).

(28) For example throat cross-sectional area of one ejector may be greater than that of the other ejector (e.g., at least 5% greater or at least 10% or at least 20% or at least 30% or at least 50%, with exemplary upper ends on ranges being 100% greater or 80% greater or 60% greater). Another possible difference is mixer cross-sectional area. This area may differ by the same amounts as those listed for throat area.

(29) The FIGS. 3 and 4 system further differs, for example, from CN204115293U in that the CN204115293U system passes refrigerant through a given heat exchanger in two different directions in the respective two modes. The FIGS. 3 and 4 system does not reverse refrigerant direction in a given heat exchanger between the two modes. This preserves the relationship between refrigerant flow and the flow of whatever heat transfer medium (e.g., water or air) the refrigerant interacts with in the heat exchangers. This may maintain the relationship in the highest heat transfer condition without additional expenses of altering the flow of the heat transfer medium. For example there may be an essentially pure counterflow relation in the refrigerant-water heat exchanger and a cross-counter relation in the refrigerant-air heat exchanger. However, an alternative FIG. 8 system 700 does reverse refrigerant flow direction in the individual heat exchangers between the cooling mode (shown) and the heating mode (not shown). Transition to heating mode is similar to the transition between FIGS. 3 and 4.

(30) FIG. 5 shows an alternate system 400 otherwise similar to the system 200 but adding a suction line heat exchanger (SLHX) 402. The SLHX is a refrigerant-refrigerant heat exchanger having a first refrigerant leg 404 in heat exchange relation with a second refrigerant leg 406. The first refrigerant leg is positioned between the valve 262 and the ejector motive/primary flow inlets. The second leg 406 is placed in the suction line between the separator vapor outlet and the compressor suction port or inlet. This positioning allows the suction line heat exchanger to act as a suction line heat exchanger in both the cooling mode and the heating mode. In both such modes, the first leg 404 will be a heat rejection leg and the second leg 406 will be a heat absorption leg. A heating mode of the system 400 reflects a similar switching relative to FIG. 5 as FIG. 4 is to FIG. 3.

(31) FIG. 1 further shows a controller 140. The controller may receive user inputs from an input device (e.g., switches, keyboard, or the like) and sensors (not shown, e.g., pressure sensors and temperature sensors at various system locations). The controller may be coupled to the sensors and controllable system components (e.g., valves, the bearings, the compressor motor, vane actuators, and the like) via control lines (e.g., hardwired or wireless communication paths). The controller may include one or more: processors; memory (e.g., for storing program information for execution by the processor to perform the operational methods and for storing data used or generated by the program(s)); and hardware interface devices (e.g., ports) for interfacing with input/output devices and controllable system components.

(32) FIG. 6 shows a system 600 comprising a twin ejector assembly 602. The ejector assembly has at least two inlets 604, 606, and at least one outlet. The exemplary ejector has a pair of outlets 608, 610. In the exemplary embodiment, these outlets feed conduits 612, 614 having respective valves 616, 618. The exemplary lines 612, 614 merge to form the line 46 feeding the separator inlet 50. Accordingly, alternatively phrased, the junction or a portion along the line 46 may be treated as a single outlet in this embodiment.

(33) As is discussed further below the exemplary ejector assembly 602 has at least two modes of operation. In one or more first modes, the inlet 604 is a motive or primary flow inlet and the inlet 606 is a suction or secondary flow inlet. In one or more second modes, the functions are reversed so that the inlet 604 is the suction or secondary flow inlet and the inlet 606 is the motive or primary flow inlet.

(34) Otherwise similar to the FIG. 3 embodiment, the respective ports 604 and 606 are coupled to/fed by the respective lines from the heat exchangers 30 and 64. Thus this illustrated embodiment eliminates the valves 262 and 264, thus saving their costs.

(35) The exemplary ports 604, 606 are coupled to respective nozzle units 620, 622. The exemplary nozzle units are nozzle/needle units having a nozzle 624, 625 and a needle 626, 627. The nozzle may be configured as the motive nozzle discussed above having similar features which are not separately discussed. FIG. 6A shows a needle actuator 630 which may be similar to needle actuators in the prior art or as otherwise may be developed (e.g., electromagnet/solenoid type actuators, stepper actuators, and the like).

(36) Each unit 620, 622 comprises a body 640 holding the motive nozzle 624, 625. FIG. 6A shows, for the unit 620, an inlet flow passing through the inlet 604 into a chamber 642 surrounding the needle, and then through an inlet 644 of the motive nozzle 624. FIG. 6A further shows each of the units 620, 622 associated with a respective mixer/diffuser unit 650, 652 which may have similar features to mixers and diffusers discussed above or otherwise developed.

(37) FIG. 6A shows one condition for the motive nozzle of the first unit 620 but a different second condition for the motive nozzle of the unit 622. This exemplary second condition is a bypass condition wherein the central passageway of the motive nozzle is bypassed along a flowpath 660. An exemplary flowpath 660 is a generally annular flowpath surrounding the motive nozzle 624, 625. The exemplary bypass is opened up via a motion of the motive nozzle. An exemplary motion is an axial retraction. An exemplary retraction disengages the underside 662 of a flange 664 of the motive nozzle from a surface 666 of an internal shoulder of the housing 640 to open up the flow along the path 660. A closing motion would involve the opposite direction.

(38) The opening of the flow along the path 660 may be accompanied by a closing of flow along the central passageway of the subject motive nozzle (e.g., via a sealing engagement of the needle with the throat).

(39) Exemplary motive nozzle actuation may be via solenoid, stepper motor, or the like. An exemplary actuator 670 may have a fixed portion 672 (e.g., solenoid coil unit) and a moving portion 674 (e.g., solenoid plunger). The moving portion may be coupled to the associated motive nozzle by a linkage 676 (e.g., a circumferential array of arms having first ends mounted at a downstream end of the plunger and second ends mounted to the flange to define a cage). The cross-sectional area along the flowpath 660 is substantially greater than the minimum cross-sectional area along the flowpath through the motive nozzle (e.g., the throat area). This can allow the open flow passage 660 of one of the units 620, 622 to carry a suction/secondary flow driven by a motive flow passed through the central passageway of the other of the units 620, 622. To do this, the two units 620, 622 feed a plenum 680 having respective inlets receiving flows from the units 620, 622 and outlet ports positioned to feed the mixer(s) and diffuser(s). In the exemplary implementation, each mixer/diffuser unit is approximately aligned with its associated nozzle unit 620, 622. When a given nozzle unit is utilized to pass motive flow, the associated mixer/diffuser 650, 652 may be open (e.g., via its valve 616, 618) while the other mixer/diffuser unit is closed.

(40) The crossing orientation of the nozzle units and mixer/diffuser units may facilitate flow mixing (e.g., as opposed to having a parallel orientation). Based upon anticipated flow conditions, the angles may be optimized considering the complicated momentum mixing during the supersonic two phase flow process. Exemplary angles between axes of the two nozzle units may be between 0 and 90 or 30 and 90 or 40 and 70. Similarly, exemplary angles between axes of the two mixer/diffuser units may be between 0 and 90 or 30 and 90 or 40 and 70.

(41) Switching between the heating mode and cooling mode may involve a similar actuation of valves 260 and 262 as is used in either of the other embodiments. The valve 264 is eliminated or avoided. FIG. 7 shows a condition of the ejector assembly 602 in the heating mode wherein the motive nozzle state/position and the needle state are reversed relative to their FIG. 6A counterparts.

(42) In the exemplary system 600, switching between the heating mode and cooling mode involves the actuation of the nozzle actuators 670 of the two units, the needle actuators 630 of the two units, and the four-way valve 260. For example, in the cooling mode, the flow passage through the four-way valve 260 is shown in FIG. 6 and the flow passage through the twin ejector is shown in FIG. 6A; in the heating mode, the flow passage through the four-way valve 260 is similar to that in FIG. 4 and the flow passage through the twin ejector assembly is as shown in FIG. 7. In this way, both the second four-way valve 262 and three-way valve 264 are eliminated or avoided.

(43) In the exemplary system 600, the motive nozzle units and the mixer/diffuser units may have similar asymmetries to those of the ejectors of the FIGS. 3 and 5 embodiments. Additional variations may relate to the relationships between the nozzle units 620, 622 and the mixer/diffuser units 650, 652. A further variation on the FIG. 6 system is the FIG. 9 system 800. This preserves the valves of the FIG. 3 system 200 to allow greater flexibility in operation. This, for example, allows the roles of the nozzle units to be switched within a given mode.

(44) FIGS. 10 and 11 show respective systems 900 and 1000 that omit the three-way valve. Flow through individual compressors is controlled by valves specific to those compressors. For example, the FIG. 2 needle valve may be closed to block motive/primary flow. Suction/secondary flow may be blocked directly via valves in the lines feeding the secondary flow inlets or indirectly by valves at the ejector outlets (in combination with needle closing). The illustrated examples have one-way valves (check valves) 920, 922 positioned to block reverse flow from the secondary flow inlets.

(45) Either or both ejectors may be used in each of the cooling and heating modes. The particular ejector or combination of ejectors used in a given mode may be selected to best correspond to the requirements of such mode. FIG. 10 shows the system in a cooling mode with only the first ejector 220 active. The four-way valve 260 is positioned between the outlet of the heat exchanger 64 and the inlets of the ejectors. The needle of the second ejector 240 is closed and the check valve 922 prevents reverse flow from the outlet of the second ejector back through the secondary flow inlet. Alternatively, the second ejector could be active or both ejectors could be active. The illustrated refrigerant lines and valves provide for a reversed refrigerant flow direction through the heat exchangers in heating mode as discussed previously.

(46) In contrast to FIG. 10, the system 1000 of FIG. 11 preserves refrigerant flow direction through the heat exchangers in heating mode as discussed previously by positioning the four-way valve 260 between the expansion valve 70 outlet and the inlets of the heat exchanger 64. For purposes of illustration, both ejectors are shown active in the illustrated cooling mode although either could be individually active.

(47) The systems may be made using otherwise conventional or yet-developed materials and techniques.

(48) The use of first, second, and the like in the description and following claims is for differentiation within the claim only and does not necessarily indicate relative or absolute importance or temporal order. Similarly, the identification in a claim of one element as first (or the like) does not preclude such first element from identifying an element that is referred to as second (or the like) in another claim or in the description.

(49) One or more embodiments have been described. Nevertheless, it will be understood that various modifications may be made. For example, when applied to an existing basic system, details of such configuration or its associated use may influence details of particular implementations. Accordingly, other embodiments are within the scope of the following claims.