CN100507403C - Ejector and ejector cycle device - Google Patents

Ejector and ejector cycle device Download PDF

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Publication number
CN100507403C
CN100507403C CNB2006100844439A CN200610084443A CN100507403C CN 100507403 C CN100507403 C CN 100507403C CN B2006100844439 A CNB2006100844439 A CN B2006100844439A CN 200610084443 A CN200610084443 A CN 200610084443A CN 100507403 C CN100507403 C CN 100507403C
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China
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cold
producing medium
refrigerant
injector
compressor
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CN1869551A (en
Inventor
武内裕嗣
斋藤美歌
押谷洋
西田伸
杉浦崇之
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Denso Corp
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Denso Corp
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Abstract

An ejector cycle device includes a compressor that draws and compresses refrigerant, a radiator that radiates heat of high-pressure refrigerant discharged from the compressor, an ejector, a branch passage branched from a refrigerant passage between the radiator and a nozzle portion of the ejector and coupled to a suction port of the ejector, a throttle unit that is arranged in the branch passage and decompresses refrigerant, and an evaporator that is arranged on a downstream side of refrigerant flow of the throttle unit in the branch passage and evaporates refrigerant. Accordingly, even when a suction performance of the ejector is lowered, refrigerant can flow through the evaporator.

Description

Injector and ejector cycle device
Technical field
The present invention relates to the ejector cycle device of a kind of injector and use injector.Ejector cycle device can be applicable to the vapour pressure miniature kind of refrigeration cycle of using injector.
Background technology
For the vapour pressure miniature kind of refrigeration cycle of using injector, for example proposed, as use vapour/liquid/gas separator and be used for only liquid phase refrigerant being flow to the JP-B1-3322263 of the injector of evaporimeter (corresponding to USP 6,477,857, USP 6,574,987) the vapour pressure miniature kind of refrigeration cycle described in.In addition, JP-A-2005-37093 (corresponding to US 2005/0011221A) has proposed vapour pressure miniature kind of refrigeration cycle, vapour pressure miniature kind of refrigeration cycle comprises between vapour/liquid/gas separator and evaporimeter, and the control between having before and after itself is near the differential valve of the differential pressure between being proportional to before and after the injector, and differential valve arranged in series and the check-valves that allows direction that cold-producing medium only flows from the liquid refrigerant outlet of vapour/liquid/gas separator at cold-producing medium to flow therewith.
Yet, utilize one of the problem of the vapour pressure miniature kind of refrigeration cycle of above-mentioned conventional injector to be, when the performance of injector descends, particularly, under the situation of low external air temperature, the refrigerant amount that flows through evaporimeter reduces, and causes the performance of evaporimeter to descend.For this reason, even require to provide when the performance of injector descends, cold-producing medium also can flow through the loop structure of evaporimeter.
In addition, at USP 6,550, illustrated that wherein the heat of low temperature side is delivered to the vapour pressure miniature heat pump cycle of high temperature side by utilizing injector in 265.At this, the ejector type heat pump cycle is provided as by utilizing two cross valves to change two heat exchangers between high temperature side and low temperature side.
Yet the heat pump cycle that is made of two cross valves has increased cost, has also reduced the convenience of its installation.
In addition, we have known ejector cycle device, and the nozzle segment of injector forms as a whole with the pressure reduction device that separates with nozzle segment each other in the ejector cycle device, thereby (for example reduced size, corresponding to USP 6,871,506 JP-A-2004-44906).
In JP-A-2004-44906 in the disclosed circulation, become as a whole injector to be connected to the downstream of radiator with adjustable throttling, reservoir is connected to the downstream of injector, the liquid phase refrigerant outlet of reservoir is connected to the inlet of evaporimeter, and the outlet of evaporimeter is connected to the ejector refrigerant suction inlet.Therefore, only relevant by the refrigerant amount of evaporimeter suction with the inlet capacity of injector.Therefore for this reason, when the high pressure of circulation with when the difference between the low pressure diminishes and the input of injector descends, the inlet capacity of injector descends, and the refrigerant flow of evaporimeter descends, and in the case, evaporimeter can not apply cooling capacity fully.
Summary of the invention
In view of the above problems, the object of the present invention is to provide a kind of ejector cycle device with injector, even when wherein the injector intake performance descends, cold-producing medium also flows to evaporimeter.
Another object of the present invention is to provide a kind of ejector cycle device with injector, it can utilize high temperature side and low temperature side in the simple structure conversion kind of refrigeration cycle.
Another object of the present invention is to provide a kind of ejector cycle device that can reduce cost and between high temperature side and low temperature side, change.
A further object of the present invention is to provide a kind of injector and the ejector cycle device that uses injector and have simple branched bottom structure.
A further object of the present invention is to provide a kind of simple structure of utilizing to become as a whole injector with the throttling unit.
According to an aspect of the present invention, ejector cycle device comprises: the compressor of suction and compressed refrigerant; Distribute the radiator of the heat of the high-pressure refrigerant of discharging from compressor; Comprise that the pressure with the high-pressure refrigerant in radiator downstream can be converted to the speed energy,, and be used for by the injector of injection stream from the suction inlet of nozzle segment suction cold-producing medium with the nozzle segment of decompression and swell refrigeration agent; From the coolant channel branch between the nozzle segment of radiator and injector, and be connected to the branched bottom of the suction inlet of injector; Be arranged in the branched bottom and the throttling unit (throttling arrangement) of reduced-pressure refrigerant; And be arranged in the branched bottom, the downstream of the cold-producing medium of throttling unit stream and the evaporimeter of vaporized refrigerant, wherein, branched bottom (55) is directly connected to the suction inlet of injector (30), thereby the cold-producing medium in injector (30) downstream can not be introduced in the branched bottom (55).Therefore, though when the evaporimeter inlet capacity when low external air temperature descends, also cold-producing medium can be guided into evaporimeter, and can keep the cooling capacity of evaporimeter.
For example, flow controlling unit can be arranged in the coolant channel between radiator and the injector, and the flow of control cold-producing medium.In the case, can easily regulate refrigerant flow in the complete alternation.
Vapour/liquid/gas separator can be between the outlet and compressor of injector, cold-producing medium is separated into vapor phase refrigerant and liquid phase refrigerant, so that vapor phase refrigerant is supplied to compressor and gathers liquid phase refrigerant.In addition, heat is regained the unit can be between injector and compressor, with exchanged heat between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucked by compressor.As selection, heat is regained the unit can be between vapour/liquid/gas separator and compressor, with the cold-producing medium that flows out radiator and flow out vapour/liquid/gas separator and the cold-producing medium that sucks by compressor between exchanged heat.As selection, heat is regained the unit can be between injector and vapour/liquid/gas separator, with at the cold-producing medium and the outflow jet that flow out radiator and flow to exchanged heat between the cold-producing medium of vapour/liquid/gas separator.Therefore, can utilize heat to regain the unit and reclaim heat effectively.
In addition, a plurality of recuperation of heat parts can be between injector and compressor, and between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucks by compressor exchanged heat.In the case, vapour/liquid/gas separator can be between the low pressure refrigerant passage of a plurality of recuperation of heat parts.
In ejector cycle device, the liquid refrigerant feed path can be set to from vapour/liquid/gas separator inhalant liquid cryogen, and return mechanism can not be arranged in the liquid refrigerant feed path to allow cold-producing medium to flow in the direction that flows out vapour/liquid/gas separator.In the case, can make the upstream side that flows to the cold-producing medium stream of evaporimeter from the liquid phase refrigerant of liquid refrigerant feed path supply.
According to a further aspect in the invention, ejector cycle device comprises: the compressor of suction, compression and discharging refrigerant; Be arranged on cold-producing medium by the injector in the refrigerant circulation passage of compressor cycle, wherein ejector is useful on the nozzle segment of the inlet of introducing the preceding high-pressure refrigerant of decompression, cold-producing medium flows the suction inlet that sucks by the injection of refrigerant from nozzle segment, and is used to eject the outlet from the cold-producing medium of nozzle and suction inlet; Be connected to the branched bottom of the suction inlet of the inlet of injector and injector; Be arranged on the heat exchanger in the branched bottom; And supply to injector inlet at high-pressure refrigerant, and cold-producing medium supplies to outlet from first pattern and the high-pressure refrigerant that heat exchanger flows to suction inlet, and cold-producing medium flows to the passage converting unit of changing between second pattern of heat exchanger from the suction inlet of injector.Therefore, high temperature side and low temperature side can utilize the simple structure conversion in circulation.
Heat exchanger can be used as first heat exchanger and arranges.In the case, the throttling unit can be between the inlet and first heat exchanger of injector, and to make first heat exchanger be low temperature in first pattern, and to make first heat exchanger be high temperature in second pattern.In addition, second heat exchanger can be arranged in the refrigerant circulation passage, and becomes high temperature and the low temperature that becomes in second pattern in first pattern.
Even in this case, heat is regained the unit also can be between injector and compressor, and heat exchange in first pattern between the cold-producing medium that flows out second heat exchanger and outflow jet and the cold-producing medium that sucked by compressor.
In addition, second injector and second branched bottom can be arranged on the second heat exchanger side.In the case, second injector has the inlet that the high-pressure refrigerant in the downstream of first heat exchanger flows into when second pattern, second branched bottom will guide the into suction inlet of second injector from the cold-producing medium of the refrigerant circulation passage branch of the upstream side of first injector inlet, and second heat exchanger can be arranged in second branched bottom and vaporized refrigerant, thereby applies cooling capacity in second pattern.
According to a further object of the present invention, the injector that is used for kind of refrigeration cycle comprises: reduce the pressure of cold-producing medium, thus the nozzle segment of swell refrigeration agent; The suction part that cold-producing medium sucks by the high speed cold-producing medium that sprays from nozzle segment; Be used to mix the cold-producing medium that sprays from nozzle segment with supercharging and from sucking the diffusion part of the cold-producing medium that part sucks; The first pontes that is communicated with the upstream side of nozzle segment; Second coupling part that is communicated with the downstream of diffusion part; With partially communicating the 3rd coupling part of suction; And the 4th coupling part that is communicated with the upstream side of nozzle segment.Therefore, can make the branched-refrigerant passage of injector simple.In addition, similar with the 4th coupling part, can form the 5th and the 6th coupling part simply.
For example, controlling organization can be made as the opening of control nozzle segment.In addition, controlling organization can be set to control the opening of the coolant channel that passes the 4th coupling part.
In addition, controlling organization can be provided with the pin in the coolant channel that is arranged on nozzle segment, and passing an end of the coolant channel of the 4th coupling part can be in the coolant channel of nozzle segment and the relative opening of side surface of pin.As selection, throttling arrangement can be set to the cold-producing medium stream that the 4th coupling part is flow through in throttling.For example, throttling arrangement can maybe can be arranged in the coolant channel that is connected to the 4th coupling part between the 4th coupling part and the first pontes.
According to another object of the present invention, a kind of injector that is used to have the kind of refrigeration cycle of evaporimeter, comprise: have the nozzle segment of decompression and swell refrigeration agent, and by suck the spout part of the suction part of cold-producing medium from evaporimeter from the high speed cold-producing medium of nozzle ejection; And become as a whole with injector and be reduced in the upstream side branch of nozzle segment, and flow out the throttling unit of refrigerant pressure of the upstream side of evaporimeter.The overall structure of injector and throttling arrangement (for example, throttling unit) therefore, can be set.
In the case, one of nozzle segment and throttling unit can constitute the area that changes coolant channel at least.In addition, the throttling unit can be contained in the housing that holds nozzle segment.
In addition, nozzle segment can be for changing the variable-nozzle part of coolant channel area, the throttling unit can be for changing the variable restrictor mechanism of coolant channel area, and the area of the area of the coolant channel of variable-nozzle part and the coolant channel of variable restrictor mechanism can change by common aisle spare control device.In the case, the aisle spare control device shrinks or increases the area of the coolant channel of the area of coolant channel of variable-nozzle part and variable restrictor mechanism simultaneously.
As selection, the throttling unit can be arranged on the outside of the housing that is used to hold nozzle segment, and the throttling unit can be connected to housing by the refrigerant pipe integral body with about 5cm or shorter length.In addition, variable-nozzle part and variable restrictor mechanism can be by single drive part controls.
According to another object of the present invention, ejector cycle device comprises: thus comprise the pressure swell refrigeration agent that reduces cold-producing medium, and suck the injector of the nozzle segment of cold-producing medium by the high speed cold-producing medium that sprays from nozzle segment; The evaporimeter of the cold-producing medium that evaporation sucks in the upstream side branch of nozzle segment and by injector; And the pressure of cold-producing medium that is reduced in the upstream side branch of nozzle segment, thereby swell refrigeration agent and cold-producing medium is supplied to the throttling arrangement of evaporimeter.In the case, throttling arrangement and injector are shaped to.Therefore, can make the simple in structure of ejector cycle device.
Description of drawings
Below the reference accompanying drawing, preferred implementation is elaborated the more clear and easy understanding that becomes of other purpose of the present invention and advantage.
Fig. 1 is to use the sketch of vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of the injector of first embodiment of the invention;
Fig. 2 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of second embodiment of the invention;
Fig. 3 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of third embodiment of the invention;
Fig. 4 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of four embodiment of the invention;
Fig. 5 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of fifth embodiment of the invention;
Fig. 6 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of sixth embodiment of the invention;
Fig. 7 is to use the sketch of vapour pressure miniature kind of refrigeration cycle of the injector of seventh embodiment of the invention;
Fig. 8 is to use the p-h figure of the vapour pressure miniature kind of refrigeration cycle of the injector among Fig. 7;
Fig. 9 is to use the sketch of vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of the injector of eighth embodiment of the invention;
Figure 10 is to use the p-h figure of the vapour pressure miniature kind of refrigeration cycle of the injector among Fig. 9;
Figure 11 is to use the sketch of vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of the injector of ninth embodiment of the invention;
Figure 12 is the sketch of the ejector cycle device in the twelveth embodiment of the invention, and has shown air cooling down operation pattern;
Figure 13 is the sketch of the air heat operator scheme in the ejector cycle device among Figure 15;
Figure 14 is the sketch of the ejector cycle device in the thirteenth embodiment of the invention;
Figure 15 is the sketch of the ejector cycle device in the twelveth embodiment of the invention;
The 13 embodiment Figure 16 is the sketch of the ejector cycle device in the seventeenth embodiment of the invention;
Figure 17 is the sketch of the ejector cycle device in the eighteenth embodiment of the invention;
Figure 18 is the cutaway view of the 18 embodiment injector;
Figure 19 A is the sketch that shows the state of the coolant channel area that shrinks (throttling) injector, and Figure 19 B is the sketch that shows the state of the coolant channel area that increases injector;
Figure 20 is the sketch of the ejector cycle device in the nineteenth embodiment of the invention;
Figure 21 is the schematic sectional view of the injector of the 19 embodiment;
Figure 22 is the schematic sectional view of the injector of the 20 embodiment;
Figure 23 is the schematic sectional view of the injector of the fixed restrictive valve improved procedure that is increased to the 18 embodiment.
The specific embodiment
(first embodiment)
Hereinafter, will utilize Fig. 1 to describe first embodiment of the present invention in detail.Fig. 1 is to use the sketch according to the vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of first embodiment of the invention injector.In this embodiment, use the vapour pressure miniature kind of refrigeration cycle of injector typically to be used to use carbon dioxide (CO according to the present invention 2) as this air-conditioner of the vehicle of cold-producing medium.
Compressor 10 provides the drive source drives that drives the engine (not shown) freely power, and suction and compressed refrigerant.Compressor 10 in this embodiment adopts variable conpacitance compressors, and the mode that this variable conpacitance compressor becomes set point of temperature with the temperature of the cold-producing medium that sucks by compressor 10 is controlled the refrigerant flow (refrigerant velocities of discharge or capacity) of discharge changeably.The refrigerant flow (refrigerant velocities of discharge or capacity) of discharging is by the control of electronic control unit (not shown).Radiator 20 is to blow out from the cold-producing medium of compressor 10 discharges with from the hair-dryer (not shown), thus the high-side heat exchanger of heat exchange between the vehicle car air outside of cooling refrigeration agent.
Injector 30 reduces the refrigerant pressure that flows out radiator 20, thereby swell refrigeration agent and the vapor phase refrigerant that sucks in evaporimeter 50 evaporations from suction inlet 33, evaporimeter 50 will be explained below, and expansion energy is converted to the pressure energy, thereby increases the suction pressure of compressor 10.The cold-producing medium that flows out this injector 30 sucks by compressor 10.In this mode, form the refrigerant circulation passage of ejector cycle device.
In this refrigerant circulation passage, the branch point of branched bottom 55 of suction inlet 33 of the cold-producing medium of branch stream being introduced above-mentioned injector 30 is between the nozzle 31 of radiator 20 and injector 30, and nozzle 31 will specify in the back.In this branched bottom, the low-pressure side heat exchanger of evaporimeter 50 as heat exchange between air that blows into vehicle car and liquid phase refrigerant is set, with the evaporation liquid phase refrigerant, thereby apply cooling capacity.
In addition, upstream side at the cold-producing medium of this evaporimeter 50 stream, be provided with reduce the refrigerant pressure that sucks by evaporimeter 50 throttling unit 40 (in this embodiment, be fixed restrictive valve, as capillary), thereby guarantee to reduce the pressure (evaporating pressure) in the evaporimeter 50, and control flows to the refrigerant flow of evaporimeter 50.
At this, as shown in Figure 1, injector 30 constitutes by following: the pressure that will flow out the high-pressure refrigerant of radiator 20 can be converted to the pressure of speed energy (velocity head) with the reduction cold-producing medium, thus the nozzle 31 of swell refrigeration agent; The suction part 33 of the vapor phase refrigerant that suction is evaporated in evaporimeter 50; Suck cold-producing medium by the high speed cold-producing medium stream (injection stream) that sprays from nozzle 31 from sucking part 33, and simultaneously will be from the mixing portion of nozzle 31 cold-producing medium that sprays and the refrigerant mixed that sucks from evaporimeter 50; And the speed that will flow out the cold-producing medium of mixing portion can be converted to the pressure energy, thereby increases the diffusion part of refrigerant pressure.
In addition, the end side of suction part 33 forms along with the close mixing portion of passage, the taper shape that the area of section of passage reduces gradually.Diffusion part forms along with the close refrigerant outlet of passage, the taper shape that the area of section of passage increases gradually.
Secondly, explanation is used the operation of the vapour pressure miniature kind of refrigeration cycle of said structure.When drive compression machine 10, vapor phase refrigerant sucks from the suction side by compressor 10, and refrigerant compressed is discharged to radiator 20.Cold-producing medium by radiator 20 cooling is divided into the driving stream of the nozzle 31 that flows to injector 30 and passes the inlet flow of throttling arrangement 40 and evaporimeter 50.
The pressure that flows to the cold-producing medium of nozzle 31 reduces with the cold-producing medium in expansion and the suction evaporimeter 50.The cold-producing medium of the inlet flow that sucks from evaporimeter 50 mixes at mixing portion with the cold-producing medium that the driving of spraying from nozzle 31 is flowed.The cold-producing medium that mixes has its dynamic pressure that is converted to static pressure by diffusion part, turns back to compressor 10 then.On the other hand, the cold-producing medium of inlet flow has its pressure that reduces by throttling unit 40 (throttling arrangement), flows to evaporimeter 50 then.And from the air heat absorption that blows into vehicle car with evaporation, suck by injector 30 then.
At this moment, in mixing portion, drive stream and mix in this way with inlet flow, promptly drive the momentum that flows and inlet flow momentum and conservation.Therefore, the pressure of cold-producing medium (static pressure) also increases at mixing portion.On the contrary, at diffusion part, as mentioned above, the area of section of passage increases gradually, so the speed of cold-producing medium can (dynamic pressure) be converted to pressure energy (static pressure).Therefore, in injector 30, the pressure of cold-producing medium all increases at mixing portion with at diffusion part.
Mixing portion and be commonly referred to as pressure at diffusion part and increase part 32.In other words, in desirable injector 30, the pressure of cold-producing medium increases at mixing portion in this way, i.e. also increasing at diffusion part in this way with conservation of the momentum of the momentum of driving stream and inlet flow, i.e. energy conservation.
Secondly, will the feature and the effect of this embodiment be described.The ejector cycle device of this embodiment comprises: the compressor of suction and compressed refrigerant; Distribute the radiator 20 of the heat of the high-pressure refrigerant of discharging from compressor 10; The pressure of the high-pressure refrigerant in radiator 20 downstreams can be converted to speed can be reducing the pressure of cold-producing medium, thus swell refrigeration agent and suck injection of refrigerant device 30; To introduce from the radiator 20 of refrigerant circulation passage and the cold-producing medium stream of the branch point branch between the injector 30, and make injector 30 suck the branched bottom 55 of cold-producing medium, refrigerant circulation passage comprises compressor 10, radiator 20 and injector 30, and cold-producing medium circulation in the refrigerant circulation passage; Be arranged in the branched bottom 55 and reduce the throttling unit 40 of cold-producing medium flowing pressure; And be arranged in the branched bottom 55, the downstream and the vaporized refrigerant of the cold-producing medium of throttling unit 40 stream, thereby apply the evaporimeter 50 of cooling capacity.
According to this embodiment, at the upstream side of injector 30, cold-producing medium stream is divided into and flows to as the driving stream of the injector 30 of refrigerant circulation passage and flow to inlet flow as the evaporimeter 50 of branched bottom 55.Therefore, though when the intake performance of injector 30 because the vapour pressure miniature kind of refrigeration cycle of the injector that low external air temperature when reducing, also can be realized using cold-producing medium to flow through evaporimeter 50.
In addition, the pressure in injector 30 exits is by becoming the pressure that is higher than evaporimeter 50 because the pressure increase effect of injector 30 increases pressure, and therefore, the suction pressure of compressor 10 also is higher than the pressure in evaporimeter 50 exits.In other words, even use above-mentionedly when having the simple cycle structure of injector 30, also can increase refrigeration capacity effectively, and also can increase the suction pressure of compressor 10 effectively by increasing enthalpy difference, evaporimeter 50 remains on low pressure and low temperature simultaneously.Therefore, can suitably reduce compression power, and strengthen the COP in the vapour pressure miniature kind of refrigeration cycle of using injector 30 with simple structure.
(second embodiment)
Fig. 2 is to use the sketch according to the vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of the injector of second embodiment of the invention.Below the feature that second embodiment is different with first embodiment will be described mainly.In this embodiment, be arranged on refrigerant circulation passage between radiator 20 and nozzle segment 31 and the branched bottom 55 as the flow control valve 45 of the volume control device that is used for controlling refrigerant flow.
In the basic loop structure of first embodiment, the flow of control cold-producing medium even changeable flow type injector is used as injector 30, when the flow that drives stream reduced, the flow of inlet flow increased, and does not have what change so that flow through the whole flow of the cold-producing medium of compressor 10.In the case, the flow of cold-producing medium can not controlled as we wish.
In the ejector cycle device of second embodiment, by upstream side flow control valve 45 is set at the branch point of branched bottom 55, can easily control the whole flow of cold-producing medium, and not change the flow-rate ratio that drives between stream and the inlet flow.In this embodiment, flow control valve 45 can also can be firm discharge control module (firm discharge control device) for electric flow control valve 45 that can variable control refrigerant flow.
(the 3rd embodiment)
Fig. 3 is to use the sketch according to the vapour pressure miniature kind of refrigeration cycle of the injector 30 of third embodiment of the invention.The 3rd embodiment and the different feature of above-mentioned each embodiment will mainly be described below.In this embodiment, circulating refrigerant is divided into vapor phase refrigerant and liquid phase refrigerant, and only vapor phase refrigerant is supplied to compressor 10, and the vapour/liquid/gas separator 60 that gathers liquid phase refrigerant is between the outlet and compressor 10 of injector 30.
Vapour/liquid/gas separator 60 among Fig. 3 is for the cold-producing medium of outflow jet 30 flows to, and the cold-producing medium that flows to is separated into vapor phase refrigerant and liquid phase refrigerant and gathers the reservoir of liquid phase refrigerant.The vapor phase refrigerant of separating sucks by compressor 10, and the liquid phase refrigerant that separates accumulates in vapour/liquid/gas separator 60.When vapour/liquid/gas separator 60 was arranged in the basic loop structure of first embodiment, vapour/liquid/gas separator 60 was as being used for that cold-producing medium is separated into vapour and liquid cold-producing medium and being used to gather the reservoir of the liquid phase refrigerant that separates.
Therefore,, can prevent that liquid phase refrigerant from returning compressor 10 and, and further be controlled at the refrigerant amount that circulates in the circulation to suitable amount by compressor 10 compressions according to this embodiment.In addition, the liquid phase refrigerant that does not need to be used for to flow out shown in above-mentioned JP-3322263 enters the pipe of evaporimeter 50, therefore, can use have this pipe or jar common vapour/liquid/gas separator 60, can reduce cost like this.In the 3rd embodiment, when liquid phase refrigerant turns back to compressor 10 and is not problem, can also recommend to use the structure that does not have vapour/liquid/gas separator 60 as first embodiment.
(the 4th embodiment)
Fig. 4 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle of the injector of four embodiment of the invention.The 4th embodiment and the different feature of above-mentioned each embodiment will mainly be described below.In this embodiment, regain the internal exchanger 70 of unit between injector 30 and compressor 10 as the heat of exchanged heat between the cold-producing medium that flows out radiator 20 and outflow jet 30 and the cold-producing medium that sucks by compressor 10.According to this, the latent heat of the liquid phase refrigerant of outflow jet 30 can reclaim by the enthalpy that utilizes internal exchanger 70 to reduce evaporimeter 50 inlets.
In addition, vapour/liquid/gas separator 60 can be between injector 30 and compressor 10.The cold-producing medium that flows out radiator 20 and flow out vapour/liquid/gas separator 60 and the cold-producing medium that sucks by compressor 10 between the internal exchanger 70 of exchanged heat between vapour/liquid/gas separator 60 and compressor 10.According to this, internal exchanger 70 can carry out heat exchange in the downstream of vapour/liquid/gas separator 60.As a result, can prevent that liquid phase refrigerant from flowing to compressor 10.
(the 5th embodiment)
Fig. 5 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle of the injector of fifth embodiment of the invention.The 5th embodiment and the different feature of above-mentioned each embodiment will mainly be described below.In this embodiment, vapour/liquid/gas separator 60 is between injector 30 and compressor 10.At the cold-producing medium and the outflow jet 30 that flow out radiator 20 and the internal exchanger 70 that flows to exchanged heat between the cold-producing medium of vapour/liquid/gas separator 60 between injector 30 and compressor 10.According to this, internal exchanger 70 carries out heat exchange at the upstream side of vapour/liquid/gas separator 60.For this reason, can prevent that liquid phase refrigerant from flowing to compressor 10.Therefore in addition, can prevent from excessively to increase the discharge temperature of compressor 10, increase the durability of high pressure side pipe etc.
(the 6th embodiment)
Fig. 6 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle of the injector of sixth embodiment of the invention.The 6th embodiment and the different feature of above-mentioned each embodiment will mainly be described below.In this embodiment, regain a plurality of internal exchanger 70A of unit as the heat of exchanged heat between the cold-producing medium that flows out radiator 20 and outflow jet 30 and the cold-producing medium that sucks by compressor 10,70B is between injector 30 and compressor 10.Vapour/liquid/gas separator 60 is positioned at a plurality of internal exchanger 70A, and a plurality of low pressure refrigerant passage 72a of 70B are between the 72b.In this, label 71a, 71b represent to flow out the internal exchanger 70A of cold-producing medium of radiator 20 and the high-pressure refrigerant passage of 70B.
According to this, a plurality of internal exchanger 70A are set, 70B, and vapour/liquid/gas separator 60 is positioned at a plurality of internal exchanger 70A, and the low pressure refrigerant passage 72a of 70B is between the 72b.Therefore, heat exchanges between the outlet of the outlet of injector 30 and vapour/liquid/gas separator 60.Therefore, high-pressure refrigerant can pass through the cold refrigerant cools of vapour/liquid/gas separator 60 outlets, and the refrigerant temperature in internal exchanger 70 exits can reduce by the cold-producing medium (particularly liquid refrigerant) in injector 30 exits.Therefore, can further increase refrigeration capacity and cycle efficieny.
In this embodiment, the sequence of flow of the cold-producing medium in the cold-producing medium in injector 30 exits and vapour/liquid/gas separator 60 exits is presented among Fig. 6, but sequence of flow also can be opposite.In addition, internal exchanger 70A, 70B and vapour/liquid/gas separator 60 can constitute integral module.
(the 7th embodiment)
Fig. 7 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle of the injector of seventh embodiment of the invention.Fig. 8 is the p-h figure that shows the vapour pressure miniature kind of refrigeration cycle of using the injector among Fig. 7.The 7th embodiment and the different feature of above-mentioned each embodiment will mainly be described below.In this embodiment, the cold-producing medium that flows to branched bottom 55 from radiator 20 is as the cold-producing medium that flows through internal exchanger 70.
According to this embodiment, as shown in Figure 7, internal exchanger 70 is arranged on the upstream side of injector 30 in the branched bottom 55, and is arranged on the inlet flow side of branched bottom 55, carries out heat exchange with the cold-producing medium with outflow jet 30.Therefore, can prevent the cold excessively increase in injector 30 porch, and operate kind of refrigeration cycle, and not reduce the expansion-loss energy in the injector 30, therefore increase the pressure recruitment of injector 30.In addition, can reduce the evaporating temperature of evaporimeter 50 and increase cooling performance.In Fig. 8, " a " to " g " represents the mode of operation corresponding to the position " a " to " g " of ejector cycle device among Fig. 7 respectively.
(the 8th embodiment)
Fig. 9 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle (ejector cycle device) of the injector 30 of eighth embodiment of the invention.Figure 10 is the p-h figure that shows the vapour pressure miniature kind of refrigeration cycle of using the injector among Fig. 9.The 8th embodiment and the different feature of above-mentioned each embodiment will mainly be described below.
In this embodiment, vapour/liquid/gas separator 60 between injector 30 and compressor 10, and the cold-producing medium that flows to branched bottom 55 and flow out vapour/liquid/gas separator 60 and the cold-producing medium that sucks by compressor 10 between the internal exchanger 70 of heat exchange between vapour/liquid/gas separator 60 compressors 10.
According to this embodiment, in the vapour pressure miniature kind of refrigeration cycle of the injector that uses the 7th embodiment, the low pressure refrigerant passage 72 of internal exchanger 70 is formed between vapour/liquid/gas separator 60 and the compressor 10.Therefore, the suction of compressor 10 heat (from the point " d " of the p-h figure of Figure 10 to point " a ") increase reducing the suction density of compressor 10, thereby reduce the flow of cold-producing medium.Therefore, can further reduce the compression power of compressor 10.In Figure 10, " a " to " g " represents the mode of operation corresponding to the position " a " to " g " of ejector cycle device among Fig. 9 respectively.
(the 9th embodiment)
Figure 11 shows the sketch of use according to the vapour pressure miniature kind of refrigeration cycle of the injector of ninth embodiment of the invention.This embodiment is identical with the 6th embodiment, and wherein: the heat that is provided with exchanged heat between the cold-producing medium that also sucks by compressor 10 as cold-producing medium and outflow jet 30 at outflow radiator 20 is regained a plurality of internal exchanger 70A of unit, 70B; And vapour/liquid/gas separator 60 is positioned at a plurality of internal exchanger 70A, and a plurality of low pressure refrigerant passage 72a of 70B are between the 72b.In this embodiment, be provided with a plurality of internal exchanger 70A that regain the unit as the heat of exchanged heat between the cold-producing medium that flows to branched bottom 55 and outflow jet 30 and the cold-producing medium that sucks by compressor 10,70B, and vapour/liquid/gas separator 60 is positioned at a plurality of internal exchanger 70A, a plurality of low pressure refrigerant passage 72a of 70B are between the 72b.
According to this embodiment, be provided with a plurality of internal exchanger 70A, 70B, and vapour/liquid/gas separator 60 is positioned at a plurality of low pressure refrigerant passage 72a, between the 72b.Therefore, heat exchanges between the outlet of the outlet of injector 30 and vapour/liquid/gas separator 60.Therefore, high-pressure refrigerant can pass through the cold refrigerant cools in the exit of vapour/liquid/gas separator 60, and the refrigerant temperature in internal exchanger 70 exits can reduce by the cold-producing medium (particularly liquid phase condensate agent) in injector 30 exits.Therefore, can further increase refrigeration capacity and cycle efficieny.
In this embodiment, the sequence of flow of the cold-producing medium in the cold-producing medium in injector 30 exits and vapour/liquid/gas separator 60 exits is presented among Figure 11, but sequence of flow also can be opposite.In addition, internal exchanger 70A, 70B and vapour/liquid/gas separator 60 can constitute integral module.
(the tenth embodiment)
Hereinafter, will describe the tenth embodiment of the present invention in detail by utilizing Figure 12 and 13.Figure 12 is the sketch that shows according to the ejector cycle device of tenth embodiment of the invention, and has shown the cooling down operation pattern, for example, and air cooling down operation pattern.In addition, Figure 13 is the heating operation pattern that shows in the ejector cycle device of Figure 12, for example, and the sketch of air heat operation.
The cooling down operation pattern is for becoming low temperature by making as the indoor heat exchanger or the vehicle mounting heat exchanger that use the side heat exchanger, and cooling is as the air that is used for air-conditioning of medium to be cooled or the operator scheme of water.The cooling down operation pattern can be the air cooling down operation when being used for air-conditioning, maybe can be refrigeration when being used for refrigerator or refrigerating plant or refrigeration operation.
The heating operation pattern is for becoming high temperature by making as the indoor heat exchanger or the vehicle mounting heat exchanger that use the side heat exchanger, and heating is as the air that is used for air-conditioning of medium to be heated or the operator scheme of water.The heating operation pattern can be the operation of the air heat when being used for air-conditioning, maybe can maybe can be the water heating operation when being used for water heater for when the heating operation that is used for the high-temperature storage unit.In this embodiment, ejector cycle device according to the present invention is used to use carbon dioxide (CO 2) as the air-conditioning of this vehicle of cold-producing medium.
Compressor 10 provides from drive source as driving the driving force of engine (not shown), and suction and compressed refrigerant, compressor 10 in this embodiment adopts variable conpacitance compressors, and this variable conpacitance compressor is controlled its delivery flow (discharge capacity) changeably so that the refrigerant temperature that sucks by compressor 10 becomes the mode of predetermined temperature.The delivery flow of compressor 10 (discharge capacity) is by electronic control unit 100 controls as control device.
Be connected to the discharge side of compressor 10 as the cross valve 160 of passage converting unit, and the high-pressure refrigerant that conversion is discharged from compressor 10 also (for example supplies to outdoor heat exchanger 20, radiator in the cooling down operation pattern), or the outlet of injector, above-mentioned both will be explained below.Cross valve 160 is by electronic control unit 100 controls.
Outdoor heat exchanger 20 is at the cold-producing medium of internal flow and the heat exchanger of heat exchange between as the vehicle car air outside of being blown by the hair-dryer (not shown) of external fluid.In addition, as the indoor heat exchanger 50 (for example, the evaporimeter in the cooling down operation pattern) of first heat exchanger for blow at the cold-producing medium of internal flow with by the hair-dryer (not shown) vehicle car as the air of the air-conditioning of external fluid between the heat exchanger of heat exchange.
Label 40 is for being used to reduce the throttling unit such as the capillary (fixed restrictive valve) of mobile refrigerant pressure.Injector 30 reduces the pressure of the cold-producing medium of delivery chamber's external heat exchanger 20 by nozzle segment 31, thereby swell refrigeration agent and the vapor phase refrigerant of indoor heat exchanger 50, evaporating from 33 suctions of suction part, and expansion energy is converted to the pressure energy, thereby increase the suction pressure of compressor 10.The cold-producing medium that flows out this injector 30 sucks by compressor 10.In this way, refrigerant circulation passage is formed in the ejector cycle device.
Injector 30 has: the first pontes that is communicated with the larger diameter side of nozzle segment 31; Be positioned at from the downstream of the injection stream of nozzle segment 31 and second coupling part that is communicated with the diffusion part of injector 30; And the 3rd coupling part that is communicated with the smaller diameter side that is formed at nozzle segment 31 suction space on every side.In this embodiment, the direction of the cold-producing medium stream during cooling down operation in second coupling part and the 3rd coupling part and the refrigerant flow direction reversal during the heating operation.In cooling down operation, second coupling part becomes the outlet of injector 30, and the 3rd coupling part becomes the suction inlet of injector 30.In heating operation, second coupling part becomes the inlet of injector 30, and the 3rd coupling part becomes the outlet of injector 30.
In this refrigerant circulation passage, branch point is arranged between the nozzle segment 31 of outdoor heat exchanger 20 and injector 30, and is provided with the branched bottom 55 that is used for this branch point is connected to suction part 33.In addition, throttling unit 40 is arranged on the branch point side of branched bottom 55, and indoor heat exchanger 50 is arranged on suction part 33 sides of branched bottom 55.
Secondly, will the operation of the ejector cycle device of said structure be described.At first, as shown in figure 12, with the air cooling down operation pattern (first pattern in the present invention) of explanation indoor heat exchanger 50 as the evaporimeter of low temperature side.When compressor 10 started, vapor phase refrigerant sucked from the suction side by compressor 10, and refrigerant compressed is discharged to outdoor heat exchanger 20 by cross valve 160.Cold-producing medium by the outdoor air in the outdoor heat exchanger 20 cooling is branched off into the driving stream of the nozzle 31 that flows to injector 30 and passes the inlet flow of throttling unit 40 and indoor heat exchanger 50.
Compression and expansion flow to the cold-producing medium of nozzle 31, and suck cold-producing medium in evaporimeter 50.Mixing portion, mix with the cold-producing medium of the driving stream that sprays from nozzle 31 from the cold-producing medium of the inlet flow of the suction inlet 33 of evaporimeter 50 inspiration injectors 30.The cold-producing medium that mixes has its dynamic pressure that is converted to static pressure by diffusion part, and the cold-producing medium of outflow jet 30 turns back to compressor 10 by cross valve 160.On the contrary, the cold-producing medium of inlet flow has its pressure that reduces by throttling unit 40, flows to indoor heat exchanger 50 then.The cold-producing medium that flows to indoor heat exchanger 50 is by from blowing into the absorption of air thermal evaporation that vehicle car is used for air-conditioning, so that cooling is used for the air of air-conditioning, the suction inlet 33 of inspiration injector 30 then.
At this moment, in the mixing portion of injector 30, mix in this way with inlet flow, promptly drive the momentum that flows and the momentum sum conservation of inlet flow from indoor heat exchanger 50 from the driving of nozzle 31 stream.Therefore, the pressure of cold-producing medium (static pressure) also increases at mixing portion.In addition, as mentioned above, in the diffusion part of injector 30, the area of section of passage increases gradually, and therefore, the speed of cold-producing medium can (dynamic pressure) be converted to pressure energy (static pressure).Therefore, in injector 30, the pressure of cold-producing medium all increases at mixing portion and diffusion part.
Therefore, mixing portion and diffusion part are commonly referred to pressure increases part 32.In other words, in desirable injector 30, the pressure of cold-producing medium increases at mixing portion in this way, promptly drives the momentum of stream and the momentum sum conservation of inlet flow, and the pressure of cold-producing medium increases at diffusion part in the mode of the conservation of energy.
Secondly, explanation indoor heat exchanger 50 is as shown in figure 13 become on high-tension side heating operation pattern (second pattern among the present invention).When compressor 10 started, vapor phase refrigerant sucked from the suction side by compressor 10, and refrigerant compressed supplies to the outlet side (diffusion side) of injector 30 by cross valve 160.
The cold-producing medium of supplying with from second coupling part of injector 30 flows through diffusion part and mixing portion, arrives the end of the smaller diameter side of nozzle segment 31.At this moment, because the end of nozzle segment 31 is the minor diameter opening, so cold-producing medium is difficult to flow to nozzle segment 31, cold-producing medium flows to the suction space around nozzle segment 31, and flows out to the 3rd coupling part (sucking part 33).
As a result, cold-producing medium flows on the contrary with flow direction as the fluid pump of injector 30, flows to heat exchanger 50 then.Therefore,, or be not provided with the valve that to close its passage, can prevent that a large amount of cold-producing mediums from flowing to nozzle segment 31 yet even the nozzle segment 31 of injector 30 is opened always.
When the nozzle segment 31 of injector 30 is provided with needle-valve as the valve of passage that can opening and closing nozzle segment 31, also can recommends to be provided for closing the driving mechanism of needle-valve, and the control module 100 with the device that is used to control driving mechanism is provided.In addition, open/close valves can be arranged on the upstream side of nozzle segment 31, that is to say, in the passage of heat exchanger 20, open/close valves can be passed through control module 100 opening and closing.
Flow through injector 30 and flow out the cold-producing medium that sucks part 33 and flow through indoor heat exchanger 50, and heat the air that is used for air-conditioning, be cooled thereby air flows to vehicle car.The cold-producing medium that flows out indoor heat exchanger 50 has its pressure that reduces by throttling unit 40, then flowed into chamber external heat exchanger 20 and from extraneous air heat absorption and evaporation.The cold-producing medium of delivery chamber's external heat exchanger 20 flows through cross valve 160 and turns back to compressor 10.
Secondly, will the feature and the effect of the tenth embodiment be described.At first, the ejector cycle device of this embodiment comprises: the compressor 10 of suction, compression and discharging refrigerant; Injector 30, injector 30 is arranged in the refrigerant circulation passage with the cold-producing medium that flows by compressor 10 and has inlet and the outlet that is one another in series and connects, and will be ejected into outlet from the high-pressure refrigerant of this inlet supply, thereby suck cold-producing medium from suction inlet 33, and cold-producing medium is transported to outlet; Inlet is connected to the branched bottom 55 of suction inlet 33; Be arranged on the indoor heat exchanger 50 in the branched bottom 55; And cross valve 160.Cross valve 160 supplies to the inlet of nozzle 31 of injector 30 and cold-producing medium and flows to first pattern of suction inlet 33 from indoor heat exchanger 50 at high-pressure refrigerant, and high-pressure refrigerant supplies between the outlet of injector 30 and cold-producing medium flows to indoor heat exchanger 50 from suction inlet 33 second pattern and changes.
In this embodiment, the high-pressure refrigerant stream of discharging from compressor 10 is changed flowing to injector 30 inlets and flow between the outlet by cross valve 160.When the high-pressure refrigerant of discharging from compressor 10 flow to outlet, injector 30 played the passage that cold-producing medium flows through such as the effect of simple pipe.
According to this, high temperature side in the ejector cycle device and low temperature side are changed by simple structure.Therefore, can reduce cost and increase the easiness that this circulation is installed.In this embodiment, when indoor heat exchanger 50 as first heat exchanger, and outdoor heat exchanger 20 is during as second heat exchanger, the 3rd heat exchanger can be between injector 30 and compressor 10.This 3rd heat exchanger can be made of the unit that separates with indoor heat exchanger 50, and can be set to and indoor heat exchanger 50 moving air independently.In addition, the 3rd heat exchanger can constitute with indoor heat exchanger 50 integral body, and is provided with in the mode of series flow air.
The throttling unit 40 that indoor heat exchanger 50 is become make indoor heat exchanger 50 become high temperature in the low temperature and second pattern is between the inlet and indoor heat exchanger 50 of the nozzle 31 of injector 30.Becoming the outdoor heat exchanger 20 that becomes low temperature in the high temperature and second pattern in first pattern is arranged in the refrigerant circulation passage.According to this, the vapour pressure miniature heat pump cycle that will be delivered to high temperature side in the heat of low temperature side can be formed between indoor heat exchanger 50 and the outdoor heat exchanger 20.
In this embodiment, because CO 2As cold-producing medium, so on high-tension side refrigerant pressure is greater than critical pressure.In the state of the two phase flow that the gas of the pressure with subcritical pressure mixes with liquid, the speed of cold-producing medium stream reduces by the slippage (slip ofliquid and gas) (imbalance of speed) of liquids and gases in the nozzle segment 31, therefore, the pressure recruitment for injector 30 efficient reduces.Yet according to this embodiment, by the high-pressure refrigerant of operation supercritical pressure, the cold-producing medium in the injector 30 becomes single-phase flow.Therefore, this can increase the efficient of injector 30 itself, and increases the recruitment of injector 30 pressure, therefore can increase cooling performance.
(the 11 embodiment)
Figure 14 is the sketch that shows according to the ejector cycle device in the eleventh embodiment of the invention.Below the different piece of this embodiment and the 10 embodiment will be described mainly.In this embodiment, as when first pattern between the cold-producing medium of delivery chamber's external heat exchanger 20 and outflow jet 30 and the cold-producing medium that sucks by compressor 10 internal exchanger 70 of the heat recovery units of heat exchange between injector 30 and compressor 10.
According to this, the effect that enthalpy is reduced in indoor heat exchanger 50 porch increased cold the generation by internal exchanger 70 is provided as sleeve pipe.Therefore, can increase the enthalpy difference between the entrance and exit of indoor heat exchanger 50, therefore, increase the cooling performance of indoor heat exchanger 50.
In kind of refrigeration cycle with internal exchanger 70, compare with the traditional kind of refrigeration cycle that does not have internal exchanger 70, increase the degree of superheat of compressor 10 suction sides, increase the discharge temperature of compressor 10.Yet in the present invention, suction pressure can increase by the pressure increase effect of injector 30, therefore, can prevent the increase of discharge temperature.In this embodiment, as shown in figure 14, the high-pressure refrigerant passage 71 of internal exchanger 70 is arranged between the inlet of outdoor heat exchanger 20 and nozzle 31, and the low pressure refrigerant passage 72 of internal exchanger 70 is arranged between the suction inlet of the outlet of injector 30 and compressor 10.The high-pressure refrigerant passage 71 of internal exchanger 70 can be between the branch point and nozzle segment 31 of branched bottom 55.
(the 12 embodiment)
Figure 15 is the sketch that shows according to the ejector cycle device in the twelveth embodiment of the invention.This embodiment and the above-mentioned the tenth and the different piece of the 11 embodiment will be described below.In this embodiment, the cold-producing medium that flows to branched bottom 55 is as the cold-producing medium that flows through internal exchanger 70.That is to say that as shown in figure 15, first coolant channel 71 of internal exchanger 70 is arranged in the branched bottom 55, and second coolant channel 72 of internal exchanger 70 is arranged on the outlet side (diffuser side) of injector 30.According to this embodiment, the effect of enthalpy is reduced by increasing cold generation in indoor heat exchanger 50 porch.Therefore, can increase the enthalpy difference between the entrance and exit of indoor heat exchanger 50, therefore, increase the cooling performance of indoor heat exchanger 50.
In addition, as mentioned above, when other heat exchanger (the 3rd heat exchanger) was between injector 30 and compressor 10, the enthalpy in indoor heat exchanger 50 exits reduced, therefore, the enthalpy from the 3rd heat exchanger entrance place at the cold-producing medium of indoor heat exchanger 50 interflow reduces in the cooling down operation pattern.Therefore, also can increase the cooling performance of the 3rd heat exchanger in the cooling down operation pattern.
(the 13 embodiment)
Figure 16 is the sketch that shows according to the ejector cycle device in the thirteenth embodiment of the invention.In above-mentioned the tenth to the 12 embodiment,, change by 160 pairs of direction of refrigerant flow of cross valve in order between air heat operation and air cooling down operation, to change.Yet, in this embodiment, in order in the cooling down operation of heat pump cycle, to remove the frost of indoor heat exchanger 50, control cross valve 160.When heat pump cycle in first pattern (air cooling down operation) during continued operation, the indoor heat exchanger 50 (evaporimeter) that reaches low temperature may have deposition frost thereon.
At the temperature operation lower, therefore need be provided with white removal device in particular as the indoor heat exchanger 50 of first heat exchanger than the 3rd heat exchanger 51.In addition, because the white removal time is influential to whole heat pump capacity, therefore, preferably has the white removal device that direct effect also can be shortened the required white removal time.Therefore, as above-mentioned the tenth to the 12 embodiment, cross valve 160 is transformed into the rightabout of cold-producing medium stream, thereby removes frost.According to this, can efficiently remove frost at short notice by the simple operations of only changing cross valve 160.
In addition, the cold-producing medium stream of the nozzle segment 31 that flows through injector 30 is interrupted.In addition, when making cold-producing medium flow out suction inlet 33, the cold-producing medium stream of nozzle segment 31 is interrupted.According to this, flow to the pattern of first heat exchanger 50 from suction inlet 33 at cold-producing medium, cross the cold-producing medium stream of nozzle segment 31 by interrupt flow, can make high temperature refrigerant flow through first heat exchanger 50 and do not lose, therefore improve the frost of first heat exchanger 50 and remove performance.
In brief, remove operation (defrost operation) according to the frost of this embodiment, frost can efficiently be removed in the short period of time.The structure of can interrupt flow crossing the cold-producing medium of nozzle segment 31 can realize by closing the variable nozzle mechanism (not shown) fully, maybe can On/Off device (not shown) be set by the upstream side at the cold-producing medium stream of nozzle segment 31 and realize.In addition, this white removal method is not limited to the ejection-type heat pump cycle, also can be applied to the vapour pressure miniature kind of refrigeration cycle of using the normal injection device.
The deposition of frost detects by the temperature sensor (not shown) that is arranged in the heat exchanger 50 when removing frost, and operate in when carrying out than long time stipulated time under the predetermined temperature continuously, cold-producing medium stream is oppositely removed operation to start frost by cross valve 160.As selection, for each external air temperature scope of determining, the accumulative total operating time of compressor 10 can be determined in advance.In the case, the accumulative total that at every turn reaches regulation starts frost and removes operation during the operating time.Become the heating operation state by the cross valve 160 that makes the cooling down operation state, provide frost to remove behaviour's stipulated time thus, or up to detect the effect of removing frost by temperature sensor 50b till.
In addition, blow into space to be cooled in order to prevent hot-air, the hair-dryer 50a of evaporimeter 50 can stop when frost is removed operation.In addition, injector 30 can so constitute so that removing operating period at frost closes fully, so that high temperature refrigerant stream is flow to heat exchanger 50 reliably.In addition, also recommend circulation among Figure 16 as the circulation of cooling down operation special use.
Under the situation of the circulation of cooling down operation special use, when the frost that needs indoor heat exchanger 50 was removed operation, cross valve 160 was backwards to frost and removes mode of operation.In addition, in Figure 16, by will be arranged in the branched bottom heat exchanger 50 as outdoor heat exchanger and by with heat exchanger 20 as the indoor heat exchanger that uses the side heat exchanger, circulation can be used as the circulation of heating operation special use.In the case, when the frost that needs outdoor heat exchanger 50 was removed operation, cross valve 160 was backwards to frost and removes mode of operation.
According to this embodiment, when heat exchanger 50 needs that connect between the suction inlet of the upstream side of injector 30 and injector 30 are removed frost, high-pressure refrigerant is supplied with from the outlet of injector 30, and supplies to heat exchanger 50 by the suction inlet 33 of injector 30, removes operation thereby carry out frost.As a result, can remove the frost that is used as the heat exchanger 50 of the evaporimeter in the cooling down operation usually by simple structure and control.
In the above-described embodiment, the cold-producing medium circulation has at least one injector 30 and at least one heat exchanger 50.Heat exchanger 50 can be arranged on the inferior pipeline between the nozzle entrance of the suction inlet of injector 30 and injector 30.In this case, heat exchanger 50 is carried out by its cold-producing medium and the heat exchange between the external agency that will be cooled or heat.For example, under the situation of cooling down operation, heat exchanger 50 is for being positioned at the heat exchanger in the room that will be cooled.On the other hand, under the situation of heating operation, heat exchanger 50 is for to be positioned at the heat exchanger outside the heated room.Circulate on the main line between the outlet of injector 30 and compressor 10 and do not have external heat exchanger.Circulation can be included at least one internal exchanger 70 on its main line.Circulation can have controller 100 as shown in figure 12, realizes predetermined cooling or heating properties on the heat exchanger 50 with at least one operation factors and operating in of compressor 10 by control such as the extent of opening of throttle part (40,45,34).Compressor 10 can be fixed capacity type, variable capacity type or the motor driving type with switch-clutch.Throttle part (40,45,34) can be a magnetic valve, and this magnetic valve can be regulated the opening degree of throttling passage wherein.In a preferred embodiment, controller 100 control operation factors are lower than the certain amount that allows according to compressor 10 with the liquid refrigerating dosage that keeps flowing into compressor 10.For example, be in drying regime or superheat state, controller control valve 40 and compressor 10 in order to keep the cold-producing medium on compressor 10 suction inlets.
(the 14 embodiment)
Figure 17 shows that injector of the present invention and ejector cycle device are applied to be used for the air-conditioning of vehicle and the example of refrigeration plant.
At first, the refrigerant circulation passage 110 that is used for circulating refrigerant is arranged on ejector cycle device.In refrigerant circulation passage 110, compressor 111 sucks, compresses also discharging refrigerant, and is rotated and driving by vehicle traction engine (not shown) by electromagnetic clutch 111a and band.
In this embodiment, use by discharge swash plate type (the swash plate type) variable conpacitance compressor of volume from the control signal continuous control of outside.At this, discharge volume and mean that cold-producing medium sucks and the geometric volume of the operating space of compression, and mean the top dead-centre of piston stroke and the cylinder volume between the bottom dead centre.
In the swash plate type variable conpacitance compressor, the pressure of rotating room or swash plate chamber (swash chamber) (not shown) is by utilizing the control of discharge pressure and suction pressure, with the angle of inclination that changes wobbler and change piston stroke, thus make get rid of volume can be near changing continuously in from 0% to 100% the scope.
Compressor 111 has electromagnetic type capacity control drive 111b, so that the pressure of control rotating room.The pressure of the low pressure refrigerant by compressor 111 suction sides produces the electromagnetic mechanism (not shown) that pressure reaction mechanism's (not shown) of power F1 and the pressure by low pressure refrigerant Ps produces the electromagnetic force F2 relative with power F1 and is arranged among this electromagnetic type capacity control drive 111b.
The electromagnetic force F2 of this electromagnetic mechanism determines by the electric current that control is exported from the conditioning control unit 122 (A/C ECU) that will be explained below.The pressure of rotating room guides into by the valve body (not shown) according to the power F1 of the pressure P s of response low pressure refrigerant and electromagnetic force F2 displacement by changing that the flow of the high-pressure refrigerant of rotating room changes.
In addition, the discharge volume of compressor 111 can continuously change from 100% to 0% by the pressure of control rotating room is approaching.Therefore, arrive near 0% by reducing the discharge volume, compressor 111 can reach the state that operation stops substantially.Therefore, the rotating shaft that can use compressor 11 is connected to the no-clutch structure of vehicle motor always by belt wheel and band V.
Refrigerant radiator 112 is arranged on the discharge side of the cold-producing medium of compressor 111.Radiator 112 is heat exchange between high-pressure refrigerant of discharging from compressor 111 and the extraneous air (vehicle car air outside) that blows out by the hair-dryer 112a that is used for radiator 112, thus the heat exchanger of cooling high-pressure refrigerant.
The hair-dryer 112a that is used for radiator 112 drives by drive motor 112b.And when applying voltage from 122 outputs of the conditioning control unit that will be explained below, drive motor 112b rotation also drives.In addition, in this embodiment, freon base cold-producing medium commonly used is as the cold-producing medium of circulation in the circulation, and therefore, ejector cycle device constitutes the subcritical pressure boiler circulation that high pressure is not higher than the cold-producing medium critical pressure.Therefore, radiator 112 usefulness act on the condenser of condensating refrigerant.
Injector 114 is connected to the downstream of radiator 112 by refrigerant pipe 113.Injector 114 in this embodiment is carried out the pressure that is used to reduce refrigerant pressure and is reduced the function of device, and also carries out the function of refrigerant cycle apparatus of suction effect (effect of the carrying secretly) circulating refrigerant of the cold-producing medium stream that is used for going out by high velocity jet.In addition, injector 114 pressure of carrying out the refrigerant pressure that reduces the branch point that flows to the branched bottom 118 that will be explained below and branched bottom 118 reduces the function of device.
The structure of the injector 114 of this embodiment will utilize Figure 18 to illustrate.Injector 114 is made of housing 114a, nozzle segment 114b, diffusion part 114c and aisle spare controlling organization 115.
Housing 114a plays the effect of the constituent part of fixing and protection injector 114.Housing 114a has: the cold-producing medium that flows out refrigerant pipe 113 flows to the cold-producing medium inflow entrance 114d (the first pontes) of injector 114; The cold-producing medium that flows to from cold-producing medium inflow entrance 114d flows to the branched-refrigerant flow export 114e (the 4th coupling part) of branched bottom 118a; And the refrigerant suction port 114f (the 3rd coupling part) that is set to be communicated with and suck cold-producing medium from branched bottom 118b with the refrigerant injection mouth 114h of nozzle segment 114b.
Refrigerant pipe 113 is connected to cold-producing medium inflow entrance 114d, and branched bottom 118a is connected to refrigerant suction port 114f, and branched bottom 118a is connected to branched-refrigerant flow export 114e in the mode of passing through.Leak so that prevent cold-producing medium by being welded to connect these coupling parts.
Nozzle segment 114b reduces the area of the coolant channel of cold-producing medium, and reduces the pressure of cold-producing medium so that with the swell refrigeration agent of constant entropy mode and be fixed among the housing 114a.
Nozzle segment 114b has: make the internal communication of cold-producing medium inflow entrance 114d and nozzle segment 114b so that cold-producing medium flows to the cold-producing medium inflow entrance 114g of nozzle segment 114b; To be ejected into the refrigerant injection mouth 114h the mixing portion 114j that will be explained below from the cold-producing medium that cold-producing medium inflow entrance 114g flows to nozzle segment 114b; And the upstream side that is arranged on refrigerant injection mouth 114h, and the branched-refrigerant flow export 114i that the inside of nozzle segment 114b is communicated with branched-refrigerant flow export 114e.
In addition, the branched bottom 118a that passes branched-refrigerant flow export 114e waits by welding and is connected to branched-refrigerant flow export 114i, leaks so that prevent cold-producing medium.
In addition, mixing portion 114j is formed among the housing 114a, the downstream of the cold-producing medium of refrigerant injection mouth 114h stream.Mixing portion 114j is set to cold-producing medium that will eject from refrigerant injection mouth 114h and the refrigerant mixed that sucks part 114f suction from cold-producing medium.
Form pressure and increase the downstream that diffusion part 114c partly is arranged on mixing portion 114j cold-producing medium stream.This diffusion part 114c forms the shape of the aisle spare that increases cold-producing medium gradually, and plays deceleration cold-producing medium stream to increase the effect of refrigerant pressure.In other words, diffusion part 114c can be converted to its pressure energy with the speed of cold-producing medium.
In addition, diffusion part 114c has diffuse flow outlet 1141 (second coupling parts) of the cold-producing medium outflow of passing diffusion part 114c.Diffusion part 114c also leaks so that prevent cold-producing medium by connections such as welding.
Aisle spare controlling organization 115 is fixed to the top (top side among Figure 18) of the nozzle segment 114b of housing 114a by utilizing screw etc. by seal etc., leaks so that prevent cold-producing medium.Injector 114 and aisle spare controlling organization 115 integral body form overall structure.
Aisle spare controlling organization 115 is made of pin 115a and drive part 115b.Pin 115a has shape with the inner passage of nozzle segment 114b near the end portion of identical elongated point and the shaft portion that is connected to rotor 115c.The shaft portion of pin 115a is connected to rotor 115c by the coupling part of screw-type, therefore, when the coupling part of rotation screw-type, the shaft portion of pin 115a can be in nozzle segment 115b, along its length (direction among Figure 18 shown in the arrow) move.
Drive part 115b is made of the stepper motor of knowing.When control signal (pulse signal) during from 122 outputs of the conditioning control unit that will be explained below, the rotor 115c rotation of drive part 115b.When rotor 115c rotated, the coupling part of the screw-type of rotor 115c rotated with mobile pin 115a.
At this, flow through the control of the refrigerant amount of refrigerant injection mouth 114h and branched-refrigerant flow export 114i with reference to Figure 19 A and 24B explanation.Figure 19 A shows that pin 115a is at the mobile state of direction (direction shown in the arrow A among Figure 19 A) near refrigerant injection mouth 114h.
At first, be formed at annular gap between the upstream portion of pin 115a and branched-refrigerant flow export 114i and become throttling passage C by branched-refrigerant flow export 114i and refrigerant injection mouth 114h.When pin 115a when moving near the direction of refrigerant injection mouth 114h, the area of this throttling passage C reduces.
Simultaneously, be formed at annular gap between the end of refrigerant injection mouth 114h and pin 115a and become throttling passage D by branched-refrigerant jet 114h.When this pin 115a when moving near the direction of refrigerant injection mouth 114h, the area of throttling passage D reduces.
The cold-producing medium that passes throttling passage C flows through branched-refrigerant flow export 114i and arrives branched bottom 118a.Simultaneously, the cold-producing medium that does not flow out to branched bottom 118a passes throttling passage D, and discharges from refrigerant injection mouth 114h.In other words, cold-producing medium is in the downstream of throttling passage C branch.
Figure 19 B shows that pin 115a is at the mobile state of direction (direction shown in the arrow B among Figure 19 B) away from refrigerant injection mouth 114h.When pin 115a when this direction B moves, compare with Figure 19 A, the area of throttling passage C increases and the area of throttling passage D also increases.
Therefore, when pin 115a moves by drive part 115b, be branched off into the area of coolant channel of branched bottom 118a and the aisle spare of the cold-producing medium that sprays from the refrigerant injection mouth 114h of nozzle segment 114b and change.
Be summarized as follows, pin 115a is the aisle spare control device in the embodiment for this reason, and the throttling passage C that is made of nozzle segment 114a and pin 115a becomes variable restrictor mechanism.In addition, in embodiment, cold-producing medium comprises the structure of cold-producing medium in the upstream side branch of nozzle segment 114b in the structure of the upstream side branch of the refrigerant injection mouth 114h of injector 114.
Secondly, first evaporimeter 116 is connected to the downstream of cold-producing medium stream of the diffusion part 114c of injector 114.First evaporimeter 116 is arranged in the shell spare of the air-conditioning unit (not shown) that vehicle installs, and cools off the operation that is used for the air of vehicle car air conditioning.
Specifically, the air that is used for the air-conditioning vehicle compartment blows into first evaporimeter 116 by the first evaporator blower 116a of vehicle car air-conditioning unit.Then, pressure absorbs heat and evaporation by the low pressure refrigerant that injector 114 reduces from the air that is used for the air-conditioning vehicle compartment, thereby is used in the air cooling in air-conditioning vehicle compartment, thereby applies cooling capacity.
The first evaporator blower 116a drives by drive motor 116b, and when drive motor 116b have from conditioning control unit 122 outputs that will be explained below apply voltage the time, also driving of drive motor 116b rotation.
The reservoir 117 that is used for that liquid phase refrigerant is separated with vapor phase refrigerant is connected to the downstream of the refrigeration stream of first evaporimeter 116.In addition, the downstream of the vapor phase refrigerant of reservoir 117 is connected to compressor 111, suck by compressor 111 so that flow out the vapor phase refrigerant of reservoir 117, and circulation in refrigerant circulation passage 110 once more.
Branched bottom 118 is connected to the branched-refrigerant flow export 114e of injector 114.This branched bottom 118 is by the branched bottom 118a that the branched-refrigerant flow export 114e of injector 114 is connected to the inlet of second evaporimeter 119, and the branched bottom 118b formation that the outlet of second evaporimeter 119 is connected to the refrigerant suction port 114f of injector 114.
Second evaporimeter 119 is arranged in the refrigerator (not shown) that is installed in the vehicle car, and is used to cool off the cooling down operation of refrigerator inside.
For example, the air in the refrigerator blows into second evaporimeter 119 as the air that is used to cool off refrigerator inside by the second evaporator blower 119a.Then, the low pressure refrigerant that reduces by injector 114 of pressure absorbs heat and evaporation in second evaporimeter 119 from the air that is used for cooling off refrigerator inside.Thereby be used in the air cooling of cooling refrigerator inside.
The second evaporator blower 119a drives by drive motor 119b, and when drive motor 119b have from conditioning control unit 122 outputs that will be explained below apply voltage the time, also driving of drive motor 119b rotation.
In addition, this embodiment is provided with the cold-producing medium guiding channel 120 that is used for the liquid phase refrigerant side of reservoir 117 is connected to second evaporimeter, 119 inlets.This cold-producing medium guiding channel 120 guides the into coolant channel of second evaporimeter 119 for being used for the liquid phase refrigerant of reservoir 117.Only allow cold-producing medium to be arranged on the cold-producing medium guiding channel 120 from the check-valves 121 that reservoir 117 flows to second evaporimeter 119.
Conditioning control unit 122 by comprise CPU, ROM, RAM etc. with and the microcomputer of knowing of peripheral circuit constitute.Conditioning control unit 122 carries out various calculating and processing according to the control program that is stored among the ROM, to control the operation of above-mentioned various part (111a, 111b, 112b, 115b, 116b, 119b).
In addition, will be input to conditioning control unit 122 from the detection signal of one group of various sensor with from the various operation signals of guidance panel (not shown).Specifically, this group sensor comprises the temperature sensor 123 of the temperature T s2 of the cold-producing medium that detects second evaporimeter, 119 exits, and the pressure sensor 124 that is used to detect the refrigerant pressure Ps2 in second evaporimeter, 119 exits.In addition, guidance panel is provided with the temperature setting switch of chilling temperature of being used to set space to be cooled etc.
Secondly, in said structure, with the operation of this embodiment of explanation.When compressor 111 drove by vehicle motor, cold-producing medium sucked and compression by compressor 111, and enters the high temperature and high pressure state, discharges then.Then, the cold-producing medium of discharging from compressor 111 flows to radiator 112.In radiator 112, high temperature refrigerant cools off by extraneous air, thus condensation.The liquid phase refrigerant that flows out radiator 112 flows through the cold-producing medium inflow entrance 114d and the cold-producing medium inflow entrance 114g of refrigerant pipe 113, injector 114, enters nozzle segment 114b.
Conditioning control unit 122 calculates the degree of superheat of the cold-producing medium in second evaporimeter, 119 exits according to the detected value Ts2 of temperature sensor 123 and the detected value Ps2 of pressure sensor 124.Conditioning control unit 122 changes the flow that supplies to the cold-producing medium of second evaporimeter 119 from the branched-refrigerant flow export 114e of injector 114 in the mode that the degree of superheat becomes in the prescribed limit.
Specifically, when the degree of superheat of the cold-producing medium in second evaporimeter, 119 exits becomes when being higher than setting, conditioning control unit 122 outputs to control signal (pulse signal) the drive part 115b of aisle spare controlling organization 115, so that the refrigerant flow at branched-refrigerant flow export 114e place diminishes, moving pin 115a, thereby reduce throttling passage C in the A of Figure 19 A direction.On the contrary, when the degree of superheat of cold-producing medium becomes when being lower than setting, conditioning control unit 122 outputs to drive part 115b with control signal, so that the refrigerant flow at branched-refrigerant flow export 114e place becomes big, moving pin 115a, thereby increase throttling passage C in the B of Figure 19 B direction.
In addition, when pin 115a was mobile as mentioned above, not only the refrigerant flow that supplies to second evaporimeter 119 from branched-refrigerant flow export 114e changed, and the refrigerant flow that ejects refrigerant injection mouth 114h also changes.
At this, in the ejector cycle device of the upstream side branch of the nozzle segment 14b of injector 14, the refrigerant flow that flows out radiator 112 equals refrigerant flow that ejects refrigerant injection mouth 114h and flow into first evaporimeter 116 and the summation that flows to the refrigerant flow of second evaporimeter 119 from branched-refrigerant flow export 114e at the cold-producing medium that flows out radiator 12.
For this reason, in order to apply high cooling capacity in complete alternation, the cold-producing medium that flows out evaporimeter 112 need suitably be distributed to first evaporimeter 116 and second evaporimeter 119.
Therefore, the ejector cycle device of this embodiment is set at the refrigerant flow at refrigerant injection mouth 114h place and the refrigerant flow at branched-refrigerant flow export 114e place changes in linkage.Therefore, the flow-rate ratio between the evaporimeter 116,119 can be set at when the degree of superheat of the cold-producing medium in second evaporimeter, 119 exits becomes setting, can obtain high cooling capacity in complete alternation.This ejector cycle device can be by suitably the shape of design branched-refrigerant flow export 114e and nozzle segment 114b and the size of pin 115a realize.
The air heat absorption that the cold-producing medium that has in the above described manner the flow of determining and eject refrigerant injection mouth 114h blows out from the first evaporator blower 116a of first evaporimeter 116 is to apply cooling capacity.The cold-producing medium that flows out first evaporimeter 116 flows to reservoir 117 and is separated into vapor phase refrigerant and liquid phase refrigerant.The vapor phase refrigerant of separating sucks once more by compressor 111.
The cold-producing medium that flows to branched bottom 118a from branched-refrigerant flow export 114e flows through second evaporimeter 119.In addition, the liquid phase refrigerant that separates by reservoir 117 also passes through suction effect inspiration second evaporimeter 119 of injector 114.
In this way, the refrigerant flow that flows through second evaporimeter 119 also can be controlled by the liquid phase refrigerant that is sucked by reservoir 117.Therefore, the value of the cooling capacity that the flow-rate ratio between the evaporimeter 116,119 can more approaching increase complete alternation.
The cold-producing medium that flows to second evaporimeter 119 absorbs heat to apply cooling capacity from the air that blows by the second evaporator blower 119a.The vapor phase refrigerant of evaporation is by branched-refrigerant passage 118b in second evaporimeter 119, refrigerant suction port 113d from injector 114 sucks by injector 114, and mix at mixing portion with the liquid phase refrigerant that flows through nozzle segment 114b, flow to first evaporimeter 116 then.
As mentioned above, in this embodiment, the cold-producing medium in the downstream of injector 114 diffusion part 114c supplies to first evaporimeter 116, also can supply to second evaporimeter 119 from branched-refrigerant flow export 114e and have the cold-producing medium that reduces pressure.Therefore, first evaporimeter 116 and second evaporimeter 119 can apply cooling down operation simultaneously.
In cooling down operation, the evaporating pressure of the cold-producing medium of first evaporimeter 116 is for increasing the pressure of the cold-producing medium of pressure by diffusion part 114c.Because the outlet of second evaporimeter 119 is connected to refrigerant suction port 114f, so after reducing pressure by nozzle segment 113a, the minimum pressure of cold-producing medium can be applied to second evaporimeter 119 immediately.
Thus, can make the evaporator pressure (evaporator temperature) of the cold-producing medium of second evaporimeter 119 be lower than the evaporator pressure (evaporator temperature) of the cold-producing medium of first evaporimeter 116.Therefore, first evaporimeter 116 can be used for the air-conditioning vehicle compartment, and second evaporimeter 119 can be used for being installed in the refrigerator of vehicle car.
Because can passing through the pressure increase effect of the diffusion part 114c of injector 114, the suction pressure of compressor 111 increases, so, the increase that the compression work amount of compressor 111 can be passed through the suction pressure of compressor 111 reduces, and that is to say, can produce the effect of save compressed machine 111 power.
In addition, in this embodiment, reduce the variable-nozzle part of the refrigerant pressure of the refrigerant injection mouth 114h that ejects injector 114, and the refrigerant pressure of reduction outflow branched-refrigerant flow export 114e is formed integral in the injector 114 with the variable restrictor mechanism that controls flow with the control flow.Therefore, do not need like this to be provided with and reduce the throttling unit of refrigerant pressure, thereby reduce the size of ejector cycle device with the cold-producing medium among the expansion branched bottom 118a.
In addition, throttling passage C, D can move pin 115a (aisle spare control device) interlock control by drive part 115b.Therefore, can reduce the refrigerant flow that flows through variable-nozzle part and flow through flow-rate ratio fluctuation between the refrigerant flow of variable restrictor mechanism.As a result, can easily control this flow-rate ratio, and the flow-rate ratio that can avoid evaporating between the device 116,119 fluctuates to the suitable flow-rate ratio between the evaporimeter 116,119.
(the 15 embodiment)
In above-mentioned the 14 embodiment, ejector cycle device is provided with reservoir 117, cold-producing medium guiding channel 120, check-valves 121, temperature sensor 123 and pressure sensor 124.Yet, in this embodiment, as shown in figure 20, there are not these parts, and the refrigerant pipe 113 in radiator 112 downstreams is provided with the receiver 131 that vapor phase refrigerant is separated with liquid phase refrigerant, detect the temperature sensor 133 of the refrigerant temperature Ts1 in first evaporimeter, 116 exits, and the pressure sensor 134 that detects the refrigerant pressure Ps1 in first evaporimeter, 116 exits.
Because there has not been reservoir 117, so compressor 111 is connected to the downstream of first evaporimeter 116.The detected value of temperature sensor 133 and pressure sensor 134 outputs to conditioning control unit 122.
In addition, in the injector 114 of above-mentioned the 18 embodiment, the variable restrictor mechanism that reduces refrigerant pressure is made of throttling passage C, and this cold-producing medium flows out by the branched-refrigerant flow export 114i that is made of nozzle segment 114b and enters branched-refrigerant outlet 114e.Yet, in this embodiment, do not have injector 114, and be provided with injector 130 with above-mentioned variable restrictor mechanism.
The structure of the injector 130 of the 19 embodiment is described with reference to Figure 21 below, and the same with the 18 embodiment, injector 130 is made of housing 130a, nozzle segment 130b, diffusion part 130c and aisle spare controlling organization 132.
The same with the 18 embodiment, housing 130a has cold-producing medium inflow entrance 130d (the first pontes) and refrigerant suction port 130f (the 3rd cold-producing medium).In addition, housing 130a has the cold-producing medium flow export 130e (the 4th coupling part) that the cold-producing medium that flows to from cold-producing medium inflow entrance 130d flows out to branched bottom 118a.In addition, refrigerant pipe 113 is connected to cold-producing medium inflow entrance 130, and branched bottom 118b is connected to refrigerant suction port 130f, and branched bottom 118a is connected to branched-refrigerant flow export 130e.
Nozzle segment 130b has cold-producing medium inflow entrance 130g and refrigerant injection mouth 130h.In addition, nozzle segment 130b has the branched-refrigerant flow export 130i that the inside that makes nozzle segment 130b is communicated with branched-refrigerant flow export 130e.Even this branched-refrigerant flow export 130i is arranged on the pin 132a of the aisle spare controlling organization 132 that will be explained below when moving, the constant position of refrigerant flow of branched-refrigerant flow export 130e.Therefore, injector 130 is not provided with variable restrictor mechanism.
Then, thus in order to reduce the pressure swell refrigeration agent of the cold-producing medium that flows out to branched-refrigerant flow export 130e from the inside of nozzle segment 130b, housing 130a has the fixed restrictive valve 130k that is arranged on therebetween.In this embodiment, fixed restrictive valve 130k is arranged among the housing 130a, but certainly, also can be arranged in the pipe of branched bottom 118a.In addition, the fixed restrictive valve 130k of this embodiment specifically is made of aperture (orifice), but also can be made of capillary.
Secondly, aisle spare controlling organization 132 is set at the refrigerant flow that the refrigerant injection mouth 130h of nozzle segment 130b is ejected in control.The same with the 18 embodiment, aisle spare controlling organization 132 is made of pin 132a, drive part 132b and rotor 132c.Aisle spare controlling organization 132 is by the refrigerant flow of mobile pin 132a with the refrigerant injection mouth 130h of change nozzle segment 130b.
Control signal outputs to drive part 132b from conditioning control unit 122.The 15 embodiment is identical with the 14 embodiment on other aspects.
Below explanation is had the operation of this embodiment of this structure, the same with the 14 embodiment, the cold-producing medium of discharging from compressor 111 cools off by radiator 112, and is separated into vapor phase refrigerant and liquid phase refrigerant by receiver (receiver) 131.The liquid phase refrigerant of outflow receiver 131 flows to nozzle segment 130b by the cold-producing medium inflow entrance 130d and the cold-producing medium inflow entrance 130g of injector 130.
Conditioning control unit 122 calculates the degree of superheat of the cold-producing medium in first evaporimeter, 116 exits according to the detected value Ts1 of temperature sensor 133 and the detected value Ps1 of pressure sensor 134.Then, the same with the 18 embodiment, conditioning control unit 122 moves pin 132a, so that the mode of the degree of superheat in predetermined scope changes the area of throttling passage D, thereby changes the flow of the cold-producing medium of the refrigerant injection mouth 130h that ejects injector 130.
At this, the coolant channel area that is formed at the fixed restrictive valve 130k among the branched-refrigerant flow export 130e is designed to the size stipulated in this way in advance, promptly when the degree of superheat of the cold-producing medium in first evaporimeter, 116 exits becomes setting, between evaporimeter 116,119, be created in the flow-rate ratio that can apply high cooling capacity in the complete alternation.
Determine the refrigerant flow of refrigerant injection mouth 130h of nozzle segment 130b and the refrigerant flow of fixed restrictive valve 130k, the cold-producing medium that flows through refrigerant injection mouth 130h applies cooling capacity in first evaporimeter 116.The cold-producing medium that flows out first evaporimeter 116 sucks by compressor 111 once more.The cold-producing medium in first evaporimeter, 116 exits becomes the vapor phase refrigerant of the degree of superheat with regulation, therefore, liquid phase refrigerant inspiration compressor 111 can not take place.
The cold-producing medium that flows through fixed restrictive valve 130k flows through branched bottom 118a, and flows to second evaporimeter 119.Then, cold-producing medium applies cooling capacity and flows through branched bottom 118b in second evaporimeter 119, and sucks by the refrigerant suction port 130d of injector 130 from injector 130.Then, cold-producing medium mixes at mixing portion 130j with the liquid phase refrigerant that flows through nozzle segment 130b, flows to first evaporimeter 116 then.
As mentioned above, the same with the 14 embodiment, in this embodiment, can in first evaporimeter 116 and second evaporimeter 119, carry out cooling down operation simultaneously equally, compare with the cold-producing medium evaporating pressure of first evaporimeter 116, can reduce the cold-producing medium evaporating pressure of second evaporimeter 119.In addition, can reduce the compression work amount of compressor 111 and the effect that power is saved in generation.
In addition, in this embodiment, reduce the variable-nozzle part of the refrigerant pressure of the refrigerant injection mouth 130h eject injector 130, and reduce the refrigerant pressure that flows through branched-refrigerant outlet 130e and be formed integral in the injector 130 with the fixed restrictive valve 130k of control refrigerant flow with the control flow.Therefore, do not need to be provided with the fixed restrictive valve that reduces refrigerant pressure in the branched bottom 118, therefore can reduce the size of ejector cycle device.
In addition, the refrigerant flow that flows through the variable-nozzle part changes by pin 132a and drive part 132b, with the flow-rate ratio between the control evaporimeter 116,119.Therefore, can in complete alternation, apply high cooling capacity by simple structure.
(the 16 embodiment)
The injector 114 of the 18 embodiment reduces the refrigerant injection mouth 114h that ejects injector 114 by nozzle segment 114b and pin 115a refrigerant pressure to be controlling its flow, and reduce flow out branched-refrigerant flow export 114e to the refrigerant pressure of branched bottom 118a to control its flow.Yet, in the 16 embodiment, do not have injector 114, and be provided with injector 140.Other points of this embodiment are identical with the 14 embodiment.
The injector 140 of the 16 embodiment is described with reference to Figure 22 below.Injector 140 is made of housing 140a, nozzle segment 140b, diffusion part 140c, aisle spare controlling organization 141, tube connector 142 and variable restrictor mechanism 143.
The same with the 15 embodiment, housing 140a has cold-producing medium inflow entrance 140d (the first pontes) and refrigerant suction port 140f (the 3rd cold-producing medium).In addition, housing 140a has the tube connector flow export 140e that the cold-producing medium that flows to from cold-producing medium inflow entrance 140d flows out to tube connector 142.Refrigerant pipe 113 is connected to cold-producing medium inflow entrance 140d, and branched bottom 118b is connected to refrigerant suction port 140f, and tube connector 142 is connected to throttle mechanism flow export 140e.
The same with the 19 embodiment, nozzle segment 140b has cold-producing medium inflow entrance 140g and refrigerant injection mouth 140h.In addition, nozzle segment 140b has the tube connector flow export 140i that the inside that makes nozzle segment 140b is communicated with tube connector flow export 140e.This tube connector flow export 140i is arranged on the refrigerant flow of outflow tube connector flow export 140e not by the position of aisle spare controlling organization 141 changes.
In addition, diffusion part 140c is structurally identical with the 19 embodiment with aisle spare controlling organization 141.Aisle spare controlling organization 141 is made of pin 141a, drive part 141b and rotor 141c.
Tube connector 142 is for to be connected to the refrigerant pipe of the tube connector inflow entrance 143d that will be explained below with tube connector flow export 140e, and for example has approximately 5cm or shorter length.
Secondly, variable restrictor mechanism 143 is made of variable restrictor shell 143a, throttling part 143b and aisle spare controlling organization 143c.Variable restrictor shell 143a has makes the cold-producing medium that flows out tube connector 142 flow out to tube connector inflow entrance 143d in the variable restrictor mechanism 143 and the branched-refrigerant flow export 143e (the 4th coupling part) that flows out to branched bottom 118a from the cold-producing medium that tube connector inflow entrance 143d flows to.
Tube connector 142 is connected to tube connector inflow entrance 143d, and branched bottom 118a is connected to branched-refrigerant flow export 143e, and leak so that prevent cold-producing medium by being welded to connect its coupling part.
Throttling part 143b has the internal communication that makes tube connector inflow entrance 143d and throttling part 143b, and cold-producing medium flow to the cold-producing medium inflow entrance 143f of throttling part 143b, and reduce the refrigerant pressure that flows to throttling part 143b from cold-producing medium inflow entrance 143f and reduce a mouthful 143g with the refrigerant pressure of swell refrigeration agent.
The same with aisle spare controlling organization 141, aisle spare controlling organization 143c is made of pin 143h, drive part 143i and rotor 143j.Aisle spare controlling organization 143c changes the refrigerant flow that flows through refrigerant pressure reduction mouthful 143g by mobile pin 143h, with the reduction refrigerant pressure, thus the swell refrigeration agent.
At this, injector 140 and aisle spare controlling organization 141 are bonded to each other and are overall structure.The tube connector 142 of variable restrictor shell 143a by having 5cm and shorter length of the housing 140a of injector 140 and variable restrictor mechanism 143 connects so that its indissociable state is whole each other.Housing 140a, tube connector 142 and variable restrictor shell 143a can be connected to each other with the state that it can separate by screw by seal etc.
Below explanation is had the operation of this embodiment of this structure, the same with the 18 embodiment, the cold-producing medium of discharging from compressor 111 cools off by radiator 112, and flows to injector 140 from the cold-producing medium inflow entrance 140d of injector 140.The cold-producing medium that flows to injector 140 is branched off into cold-producing medium that flows to tube connector 142 and the cold-producing medium that ejects from refrigerant injection mouth 140h at the upstream side of the refrigerant injection mouth 140h of nozzle segment 140b.The cold-producing medium that flows to tube connector 142 flows to the throttling part 143b of variable restrictor mechanism 143.
Conditioning control unit 122 calculates the degree of superheat of the cold-producing medium in second evaporimeter, 119 exits according to the detected value Ts2 of temperature sensor 123 and the detected value Ps2 of pressure sensor 124.Then, conditioning control unit 122 is so that the mode of the degree of superheat in predetermined scope controlled the refrigerant flow of the variable restrictor mechanisms 143 that constitute with injector 140 integral body.Specifically, conditioning control unit 122 outputs to drive part 143j with mobile pin 143h with control signal, flows through the refrigerant flow that refrigerant pressure reduces mouthful 143g so that change.
In addition, the same with the 15 embodiment, conditioning control unit 122 changes the refrigerant flow that sprays from the refrigerant injection mouth 140h of injector 140 in this way, and promptly the flow-rate ratio between the evaporimeter 116,119 can apply high cooling capacity in whole circulation.
As mentioned above, conditioning control unit 122 determines that the refrigerant pressure of variable restrictor mechanism 143 reduces the refrigerant flow of mouthful 143g and ejects the refrigerant flow of the refrigerant injection mouth 140h of nozzle segment 140b, applies high cooling capacity so that flow through the cold-producing medium of nozzle segment 140b in first evaporimeter 116.The cold-producing medium that flows out first evaporimeter 116 sucks by compressor 111 once more.The cold-producing medium that flows through refrigerant pressure reduction mouthful 143g and flow out among the branched bottom 118a applies cooling capacity in second evaporimeter 119, sucked by the refrigerant suction port 140f of injector 140 by branched bottom 118b then
The same with the 14 embodiment, even in this structure, also can in first evaporimeter 116 and second evaporimeter 119, carry out cooling effect simultaneously.In addition, compare, can reduce the cold-producing medium evaporating pressure of second evaporimeter 119 with the cold-producing medium evaporating pressure of first evaporimeter 116.In addition, can reduce the compression work amount of compressor 111 and the effect that power is saved in generation.
In addition, in this embodiment, variable restrictor mechanism 143 is as a whole with 140 one-tenth of injectors.Therefore, this can eliminate for the needs that the throttle mechanism in the branched bottom 118 is set, and therefore can reduce the size and the weight of ejector cycle device.
In addition, in this embodiment, can change refrigerant flow that flows through the variable-nozzle part and the refrigerant flow that flows through variable restrictor mechanism 143 separately.Therefore, the refrigerant flow that flows through nozzle segment 140b and flow to first evaporimeter 116 be can control respectively, and branched bottom 118 and the refrigerant flow that flows to second evaporimeter 119 flow through.Therefore, can in whole circulation, apply high cooling capacity.
(other embodiments)
The present invention is not limited to above-mentioned embodiment, and can differently revise in the following manner.
In the 15 embodiment, use injector 130 with variable-nozzle part 130b and fixed restrictive valve 130k.Yet, even use the area of the coolant channel of fixed nozzle part, and have the injector of the variable restrictor mechanism that is used to reduce the refrigerant pressure that flows out to branched bottom 118a, also can produce the effect same with the 15 embodiment.
In the 16 embodiment, the drive part 141b of variable-nozzle part 140b and the drive part 143j of variable restrictor mechanism 143 constitute respectively.Yet the pin 141a of variable-nozzle part 140b and the pin 143h of variable restrictor mechanism 143 can be connected to each other, and two pin 141a, 143h can be by single drive part controls.
In the 14 to the 16 embodiment, illustrated that first evaporimeter 116 is used for the embodiment that air-conditioning vehicle compartment and second evaporimeter 119 are used for the refrigerator of vehicle.Yet, can be with identical by the space of second evaporimeter, 119 coolings by the space of first evaporimeter, 116 coolings.
In the 14 to the 16 embodiment, variable conpacitance compressor is as compressor 111, but fixedly positive displacement compressor or electrically-driven compressors also can be used as compressor 111.In addition, under the situation of fixing positive displacement compressor, also can recommend by discharging capacity by the ratio of electromagnetic clutch control operation state NOT-AND operation state (operation than) control cold-producing medium.In addition, under the situation of electrically-driven compressors, also can recommend by control rotation number control cold-producing medium discharge rate.
In the 14 to the 16 embodiment, the high pressure that kind of refrigeration cycle has been described is not higher than the embodiment of subcritical pressure boiler circulation of the critical pressure of cold-producing medium, but the present invention also can use the supercritical pressure circulation that the high pressure of kind of refrigeration cycle is higher than the critical pressure of cold-producing medium.
In the 14 embodiment, the flow of cold-producing medium is according to the refrigerant superheat degree control in second evaporimeter, 119 exits.In the 15 embodiment, the flow of cold-producing medium is according to the refrigerant superheat degree control in first evaporimeter, 116 exits.Yet the coolant channel area can be according to the flow of the cold-producing medium of discharging from compressor 111, the refrigerant pressure and the controls such as temperature and degree of supercooling in radiator 112 exits.
For example, have in the circulation of its pressure that is increased to the supercritical pressure state by compressor 111 at cold-producing medium, the cold-producing medium of heat radiation does not become liquid phase in radiator 112.Therefore, only need be according to the coolant channel area of the throttling unit of the coolant channel area of the nozzle segment of the refrigerant pressure in radiator 112 exits and temperature control injector and branched bottom.
In the 14 to the 16 embodiment, the flow control valve by Step-motor Control can be used as aisle spare controlling organization 115,132,141 and variable restrictor mechanism 143, but also can use other flow control valves.For example, can use conversion to be used to use a plurality of variable restrictor unit with fixed restrictive valve of different characteristic.In addition, also can recommend to be used in combination the mechanical variable restrictor mechanism and the electric variable restrictor mechanism of above-mentioned each embodiment.
For example, as shown in figure 23, the injector 114 of the 14 embodiment can be connected to branched bottom 118a by fixed restrictive valve 114k.Throttle orifice or capillary can be used as fixed restrictive valve 114k.
In the 14 to the 16 embodiment, use first evaporimeter 116 and second evaporimeter 119, but can increase the quantity of evaporimeter, for example, can use three or more evaporimeters.The pressure that reduces the cold-producing medium of the evaporimeter supply to increase can form with injector is whole with the throttling unit (throttling arrangement) of swell refrigeration agent.According to this, can further reduce the size and the weight of ejector cycle device.
For example, in the structure of the 14 to the 16 embodiment, can be provided for the part between the cold-producing medium inflow entrance 114d of the outlet of radiator 112 and injector 114 is connected to the outlet of first evaporimeter 116 and second branched bottom of the part between the reservoir 117.In addition, throttling unit (throttling arrangement) and the 3rd evaporimeter can be arranged in second branched bottom, and the throttling unit that is arranged in second branched bottom can form with injector 114 integral body.
In the above-described embodiment, use the air-conditioning that is used for vehicle according to injector of the present invention and ejector cycle device.Yet, also can use the heat pump cycle of the refrigerator that is used for vehicle, fixedly refrigerator, fixedly reach in freezer, air cooling unit and water heater according to injector of the present invention and ejector cycle device.
In the above-described embodiment, freon base cold-producing medium, carbon dioxide (CO 2) basic cold-producing medium or the basic cold-producing medium of hydrocarbon (HC) can be used as cold-producing medium.Therefore, the term freon meaning is the total term that comprises the organic compound of carbon, fluorine, chlorine and hydrogen, and freon is widely used in cold-producing medium.
Freon base cold-producing medium comprises HCFC (hydrochlorofluorocarbon/ hydrogen cfc) basic cold-producing medium and the basic cold-producing medium of HFC (hydrofluorocarbon/ hydrofluorocarbons), because freon base cold-producing medium is ozone layer depletion not, so be the cold-producing medium that is called the substitute of freon.
In addition, the basic cold-producing medium of HC (hydrocarbon) is the cold-producing medium material that comprises hydrogen and carbon and be present in nature.This HC base cold-producing medium comprises R600a (isobutene) and R290 (propane).
Should be appreciated that this changes and improvements mode is all in the scope of the present invention that appended claims limited.

Claims (12)

1. ejector cycle device comprises:
The compressor (10) of suction and compressed refrigerant;
Distribute the radiator (20) of the heat of the high-pressure refrigerant of discharging from compressor;
Comprising that pressure with the high-pressure refrigerant in radiator downstream can be converted to speed can be with the nozzle segment of decompression and swell refrigeration agent, and is used for by the injector (30) of injection stream from the suction inlet of nozzle segment suction cold-producing medium;
From the coolant channel branch between the nozzle segment of radiator and injector, and be connected to the branched bottom (55) of the suction inlet of injector;
Be arranged in the branched bottom and the throttling unit (40) of reduced-pressure refrigerant; And
Be arranged in the branched bottom, the downstream of the cold-producing medium of throttling unit stream and the evaporimeter (50) of vaporized refrigerant,
Wherein, branched bottom (55) is directly connected to the suction inlet of injector (30), thereby the cold-producing medium in injector (30) downstream can not be introduced in the branched bottom (55).
2. ejector cycle device according to claim 1 also comprises:
Be arranged in the coolant channel between radiator and the injector, and the flow controlling unit (34) of control refrigerant flow.
3. ejector cycle device according to claim 1 also comprises:
Vapour/liquid/gas separator (60), this vapour/liquid/gas separator (60) and are separated into vapor phase refrigerant and liquid phase refrigerant with cold-producing medium between the outlet and compressor of injector, so that vapor phase refrigerant is supplied to compressor and gathers liquid phase refrigerant.
4. ejector cycle device according to claim 1 also comprises:
Between injector and compressor, regain unit (70) with the heat of exchanged heat between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucks by compressor.
5. ejector cycle device according to claim 3 also comprises:
Between vapour/liquid/gas separator and compressor, with the cold-producing medium that flows out radiator and flow out vapour/liquid/gas separator and the cold-producing medium that sucks by compressor between the heat of exchanged heat regain unit (70).
6. ejector cycle device according to claim 3 also comprises:
Between injector and vapour/liquid/gas separator, to regain unit (70) at the cold-producing medium and the outflow jet that flow out radiator and the heat that flows to exchanged heat between the cold-producing medium of vapour/liquid/gas separator.
7. ejector cycle device according to claim 3 also comprises:
A plurality of recuperation of heat parts (70A, 70B), these a plurality of recuperation of heat parts are between injector and compressor, and between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucks by compressor exchanged heat, wherein vapour/liquid/gas separator is positioned between a plurality of low pressure refrigerant passages (72a, 72b) of recuperation of heat part.
8. according to any one described ejector cycle device of claim 4 to 7, the cold-producing medium that wherein flows to branched bottom is as flowing through the cold-producing medium that heat is regained the unit and flowed out radiator.
9. ejector cycle device according to claim 1 and 2 also comprises:
Vapour/liquid/gas separator between injector and compressor (60); And
Have by its cold-producing medium and flow to first coolant channel of branched bottom, and regain unit (70) by its heat of second coolant channel that flows out the vapor phase refrigerant inspiration compressor of vapour/liquid/gas separator from radiator.
10. ejector cycle device according to claim 3 also comprises:
Suck the liquid refrigerant feed path (65) of liquid phase refrigerant from vapour/liquid/gas separator; And
Be arranged in the liquid refrigerant feed path, and the backstop (80) that allows cold-producing medium to flow in the direction that flows out vapour/liquid/gas separator,
Wherein make the upstream side that flows to the cold-producing medium stream of evaporimeter from the liquid phase refrigerant of liquid refrigerant feed path supply.
11. ejector cycle device according to claim 10, wherein injector is the variable injecting device with the variable restrictor mechanism that can control refrigerant flow.
12. ejector cycle device according to claim 1, wherein the pressure of the high-pressure refrigerant of discharging from compressor is critical pressure or higher.
CNB2006100844439A 2005-05-24 2006-05-24 Ejector and ejector cycle device Expired - Fee Related CN100507403C (en)

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