CN100436962C - Refrigeration cycle device with injector - Google Patents
Refrigeration cycle device with injector Download PDFInfo
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- CN100436962C CN100436962C CNB2006101091535A CN200610109153A CN100436962C CN 100436962 C CN100436962 C CN 100436962C CN B2006101091535 A CNB2006101091535 A CN B2006101091535A CN 200610109153 A CN200610109153 A CN 200610109153A CN 100436962 C CN100436962 C CN 100436962C
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Abstract
The invention provides a refrigeration cycle device with an ejector (13), which has a first and a second compressors (11,21) for sucking in and compressing coolant and first and second coolers (12,22). A control device (100) controls a refrigerant discharge rate from a first compressor (11) and a refrigerant discharge rate from a second compressor (21) in response to a requested cooling capacity to control a total refrigerant flow rate circulated in the refrigeration cycle (1) and the ratio of a refrigerant flow rate (G1) jetted from a nozzle part (13a) of an ejector (13) to a refrigerant flow rate (G2) sucked from a refrigerant suction port (13b) of the ejector (13). The control of a refrigerant flow rate through a first evaporator (14) and a refrigerant flow rate through a second evaporator (24) in response to the requested cooling capacity can further increase cooling performance.
Description
Technical field
The present invention relates to a kind of refrigerating circulating apparatus that uses injector, described injector is used to make the refrigerant decompression in the nozzle segment and is used to increase the pressure that sprays and be inhaled into the refrigerant in the compressor from described nozzle segment.
Background technology
Disclose a kind of steam compression type refrigerating circulating apparatus that uses injector among the JP-B1-3322263.In JP-B1-3322263, refrigerating circulating apparatus comprises first evaporimeter and second evaporimeter, wherein said first evaporimeter is configured in the downstream as the cryogen flow of the injector of refrigerant decompressor and cooling circulation device, and second evaporimeter is configured in the upstream side of cryogen flow of the refrigerant suction inlet of described injector.
In the refrigerating circulating apparatus disclosed in the JP-B1-3322263, suck the gas phase refrigerant of discharging from second evaporimeter by utilizing reduction owing to the pressure that flow at high speed caused of refrigerant when the nozzle segment from injector sprays.In addition, the pressure of the speed energy of the refrigerant of expansion by injector increase part convert pressure to can be increasing the pressure of refrigerant, thereby can reduce the driving force of compressor.
Second evaporimeter that is positioned at first evaporimeter in injector downstream and is positioned at the injector suction side can show endothermic effect (endothermic effect), thereby has cooling performance.Yet, in this case, be difficult to regulate the amount of refrigerant that flow to first and second evaporimeters exactly, thereby reduce the cooling performance of first and second evaporimeters.
Summary of the invention
Consider foregoing problems, an object of the present invention is to provide a kind of refrigerating circulating apparatus, thereby can improve cooling performance effectively with injector.
According to an aspect of the present invention, a kind of refrigerating circulating apparatus comprises: first compressor 11, described first compressor are used to suck and the refrigerant of compression refrigerant to have compressed from its discharge; Be used to radiate first radiator 12 of the heat of the refrigerant of discharging from first compressor 11; Injector 13 with nozzle segment 13a and refrigerant suction inlet 13b; Be used to evaporate first evaporimeter 14 of the refrigerant of outflow jet 13; Second compressor 21, described second compressor are used to suck and the refrigerant of compression refrigerant to have compressed from its discharge; Be used to radiate second radiator 22 of the heat of the refrigerant of discharging from second compressor 21; Be used to make from the refrigerant decompression of second radiator, 22 outflows and the decompressor 23 that expands, 23A; And second evaporimeter 24, described second evaporimeter is used to evaporate decompressor 23, the refrigerant that 23A reduced pressure, and be used to make the refrigerant that has evaporated to flow into refrigerant suction inlet 13b.In this refrigerating circulating apparatus, first evaporimeter 14 is connected to first compressor 11 and second compressor 21, so that the refrigerant that first evaporimeter 14 is evaporated is assigned between first compressor 11 and second compressor 21 and is inhaled in it.Therefore, use first and second compressors 11,12 can control flow exactly through the refrigerant of first and second evaporimeters 14,24.In addition, when accumulator 54 is set at the upstream of first and second compressors 11,12, can prevent that liquid refrigerant from flowing in first and second compressors 11,12.
In addition, in the amount that the refrigerant discharge rate of first compressor 11 and refrigerant pressure are reduced by nozzle segment 13a at least one can be regulated, and in the amount that reduced by decompressor 23 of the refrigerant discharge rate of second compressor 21 and refrigerant pressure at least one can be regulated.Therefore, at least one in the refrigerant pressure decrease of refrigerant discharge rate by regulating first compressor 11 and nozzle segment 13a can be regulated from the flow rate G1 of the refrigerant of nozzle segment 13a ejection.In addition, at least one in the refrigerant pressure decrease of refrigerant discharge rate by regulating second compressor 21 and decompressor 23 can be regulated the flow of refrigerant speed G2 that sucks from refrigerant suction inlet 13b.Therefore, can regulate flow rate G1 exactly through the refrigerant of first evaporimeter 14 and second evaporimeter 24, G2, thus improve the cooling performance of described refrigerating circulating apparatus.
For example, control device 100 can be regulated at least one in the refrigerant pressure decrease of the refrigerant discharge rate of first compressor 11 and nozzle segment 13a, regulates in the refrigerant pressure decrease of the refrigerant discharge rate of second compressor 21 and decompressor 23 at least one simultaneously.In this case, can control at an easy rate from the flow rate G1 of the refrigerant of nozzle segment 13a ejection and the ratio of the flow rate G2 of the refrigerant that sucks from refrigerant suction inlet 13b.In addition, control device 100 can be controlled from the ratio of flow rate with the flow rate of the refrigerant that sucks from refrigerant suction inlet 13b of the refrigerant of nozzle segment 13a ejection according to the degree of superheat in the exit of second evaporimeter 24.In this case, can control flow rate best according to the degree of superheat through the refrigerant of second evaporimeter 24.Therefore, can further improve cooling performance, drive described refrigerating circulating apparatus simultaneously effectively.
In addition, the described refrigerating circulating apparatus refrigerant temperature checkout gear 95 that can be provided with the refrigerant pressure checkout gear 94 of the refrigerant pressure that is used to detect second evaporimeter, 24 exits and be used to detect the refrigerant temperature in second evaporimeter, 24 exits.In this case, control device 100 calculates the refrigerant degree of superheat in second evaporimeter, 24 exits according to refrigerant pressure checkout gear 94 detected refrigerant pressures and refrigerant temperature checkout gear 95 detected refrigerant temperatures.Therefore, controller 100 can calculate the refrigerant degree of superheat in second evaporimeter, 24 exits at an easy rate from the pressure and temperature of refrigerant.Alternatively, control device 100 is controlled from the ratio of flow rate with the flow rate of the refrigerant that sucks from refrigerant suction inlet 13b of the refrigerant of nozzle segment 13a ejection according to refrigerant pressure checkout gear 94 detected refrigerant pressures and refrigerant temperature checkout gear 95 detected refrigerant temperatures.This can control flow rate through the refrigerant of second evaporimeter 24 best according to the pressure and temperature of refrigerant.Therefore, the refrigerant degree of superheat that need not to calculate place of each control time just can further be improved cooling performance, and the while drives described refrigerating circulating apparatus effectively.
In addition, the refrigerant discharge rate of first compressor 11 can be regulated, and the refrigerant discharge rate of second compressor 21 can be regulated.In this case, decompressor 23 can be used as fixed restriction device 23.Alternatively, the refrigerant discharge rate of second compressor 21 and refrigerant pressure can be regulated by the amount that decompressor 23A is reduced.In this case, when the refrigerant discharge rate of second compressor 21 was reduced to a scheduled volume, refrigerant pressure can increase by the amount that decompressor 23A is reduced.Therefore, need when second compressor 21 is driven into runs steadily, to regulate flow rate when very little when flow rate by decompressor 23 through the refrigerant of second evaporimeter 24.
When the refrigerant discharge rate of second compressor 21 was reduced to described scheduled volume, the refrigerant discharge rate of second compressor 21 was fixed on described scheduled volume, made to drive second compressor 21 safely under the condition of steady running.In addition, the amount that the refrigerant discharge rate of second compressor 21 and refrigerant pressure are reduced by decompressor 23A does not need to change simultaneously, is easy to the control circulation thereby cause.
In addition, first container 52 is positioned at the upstream side of the nozzle segment 13a of the downstream of first radiator 12 and injector 13, in order to will be divided into vapor refrigerant and liquid refrigerant from the refrigerant of first radiator 12, and second container 51 is positioned at the downstream of second radiator 22 and the upstream side of second evaporimeter 24, in order to will be divided into vapor refrigerant and liquid refrigerant from the refrigerant of second radiator 22.In addition, the refrigerant from first evaporimeter 14 diverges at the branch point Z place of first compressor 11 and second compressor, 21 upstreams.In this case, accumulator 54 is positioned at the downstream of first evaporimeter 14 and the upstream of branch point Z, in order to will being divided into vapor refrigerant and liquid refrigerant from the refrigerant of first evaporimeter 14, and is used for excessive refrigerant is stored within it.In addition, expansion valve 53 is between the nozzle segment 13a of first radiator 12 and injector 13.In this case, the extent of opening of expansion valve 53 can be regulated according to the degree of superheat of the refrigerant that flows out first evaporimeter 14.
Description of drawings
Other purpose of the present invention and advantage will be from easier clear the presenting below in conjunction with the accompanying drawing detailed description of preferred embodiments.
Fig. 1 is for showing the schematic diagram according to the steam compression type refrigerating circulating apparatus of the first embodiment of the present invention.
Fig. 2 is the flow chart of the control operation of the controller among demonstration first embodiment.
Fig. 3 is for showing the schematic diagram of steam compression type refrigerating circulating apparatus according to a second embodiment of the present invention.
Fig. 4 is the flow chart of the control operation of the controller among demonstration second embodiment.
Fig. 5 is the schematic diagram of the steam compression type refrigerating circulating apparatus of demonstration a third embodiment in accordance with the invention.
Fig. 6 is the flow chart of the control operation of the controller among demonstration the 3rd embodiment.
Fig. 7 is the temperature difference T of demonstration first compressor 11 and the curve map of the relation between the rotating speed of target (target revolution).
Fig. 8 is the flow chart of the control operation of the step S230 of demonstration Fig. 6.
Fig. 9 is for showing the curve map of the relation between degree of superheat SH and the cooling capacity.
Figure 10 is the schematic diagram of demonstration according to an example of the steam compression type refrigerating circulating apparatus of another embodiment.
The specific embodiment
Hereinafter will the preferred embodiments of the present invention be described with reference to accompanying drawing.
(first embodiment)
Fig. 1 is for showing the schematic diagram according to the steam compression type refrigerating circulating apparatus 1 of implementing the first embodiment of the present invention.This embodiment shows an example, and wherein refrigerating circulating apparatus 1 is applied in the vehicle.
The refrigerating circulating apparatus 1 of described embodiment comprises and is used to suck and a plurality of compressors (for example, two compressors, first compressor 11 and second compressor 21) of compression refrigerant.First compressor 11 and second compressor 21 are for regulating the compressor with variable displacement (variable displacement compressor) that refrigerant is discharged ability according to the variation of discharge rate, perhaps for regulating the motor compressor (electric compressor) that refrigerant is discharged ability by regulating motor speed.
When the fluorocarbon refrigerant of normality is used as the refrigerant of the refrigerant cycle that is used for refrigerating circulating apparatus 1, described circulation is subcritical cycle (subcritical cycle), its mesohigh can not surpass the critical pressure of refrigerant, so radiator 12 usefulness act on the condenser that refrigerant is condensed.On the contrary, when using high pressure to surpass the refrigerant (carbon dioxide (CO for example of critical pressure
2)) time, therefore refrigerating circulating apparatus 1 becomes overcritical circulation (superscritical cycle), and makes refrigerant remain on supercriticality and radiate heat and can not condense.
The nozzle segment 13a of the injector 13 among the embodiment of going back is the fixed nozzle with fixing nozzle opening degree.Therefore, be not provided for the drive unit of driving needle valve body (needle valve body), for example stepping motor or similar device.
The mixing portion 13c that is used to mix the refrigerant that sucks from the high speed refrigerant of nozzle segment 13a and from refrigerant suction inlet 13b is set at the part in downstream of the cryogen flow of nozzle segment 13a and refrigerant suction inlet 13b.
Diffuser 13d is set at the downstream of the cryogen flow of the mixing portion 13c in the injector 13.The shape that diffuser 13d formation increases the zone, path of refrigerant gradually, and show the effect that the cryogen flow of sening as an envoy to is slowed down and increased refrigerant pressure, that is, the speed power conversion of refrigerant is become the effect of pressure energy.
In the injector 13 of described embodiment, mixing portion 13c also forms the shape that the zone, path that makes refrigerant increases gradually.The structure that mixing portion 13c and diffuser 13d are constructed increases part as the pressure in the injector 13 of described embodiment.
Refrigerant individual path 20 in the downstream that is arranged in first evaporimeter 14 and the branch point Z place of upstream side that is positioned at first compressor 11 of coolant circulation route 10 diverge to.The downstream of refrigerant individual path 20 is connected to the refrigerant suction inlet 13b of injector 13.
In refrigerant individual path 20, second compressor 21 directly is configured in after the downstream of branch point Z, and second radiator 22 is configured in the refrigerant discharge side of second compressor 21.Second radiator 22 is configured to be parallel to first radiator 12, and exchange blows with the heat between the extraneous air (air outside the vehicle cabin (vehicle cabin)) of cooling high-pressure refrigerant from the high-pressure refrigerant of second compressor, 21 discharges and by above-mentioned cooling fan 36.
Be configured in part place as the expansion valve 23 of decompressor from the downstream of the cryogen flow of second radiator 22.Second evaporimeter 24 is configured in the part place, downstream from the cryogen flow of expansion valve 23.The expansion valve 23 of described embodiment is fixed restriction mechanism (a fixed restriction device), more specifically, can be made of fixed restrictive valve (for example throttle orifice).
In described embodiment, two evaporimeters 14 and 24 are assembled integratedly and are contained in the housing 30.In the air duct that is limited in housing 30, air (air that will cool off) is blown by general air blast (electric fan) 31 on the direction of arrow A, thereby makes the air that is blown by two evaporimeters 14 and 24 coolings.
Air by two evaporimeters 14 and 24 coolings is sent to the sharing space 40 that will cool off.Therefore, two evaporimeters 14 and 24 are suitable for cooling off the sharing space 40 that will cool off.
In these two evaporimeters 14 and 24, be configured in the upstream side that first evaporimeter 14 in the coolant circulation route 10 in injector 13 downstreams is positioned at air current A.Second evaporimeter 24 that is connected to the refrigerant suction inlet 13b of injector 13 is positioned at the downstream of air current A.
When the refrigerating circulating apparatus 1 of described embodiment is used in the refrigerating circulating apparatus that is used for vehicle air conditioning, the space 40 of vehicle inside space for cooling off.When the refrigerating circulating apparatus 1 of described embodiment is used in the refrigerating circulating apparatus that is used for refrigerator car, the space 40 of the space in the freezer of refrigerator car and the freezer for cooling off.
In Fig. 1, the structure of being represented by reference symbol 100 is the controller that is used for air-conditioning.Controller 100 is corresponding to the control device among the described embodiment.
Now, the operation of the steam compression type refrigerating circulating apparatus 1 of first embodiment will be described hereinafter according to said structure.
Fig. 2 is the flow chart of the schematic control operation of display controller 100.As shown in Figure 2, controller 100 at first calculates required cooling capacity (step S110).More specifically, the temperature difference T between the temperature in the preset temperature in the space 40 that calculating will be cooled off and the space that will cool off 40, the temperature in the space 40 that wherein will cool off is detected by Inside Air Temperature sensor 90.
Then, calculate the whole flow rate (step S120) of refrigerant.The whole circulation flow rate is from first compressor 11 and second compressor 12 is discharged and the whole flow rate of the refrigerant in process coolant circulation route 10 and refrigerant branch road path 20.The whole flow rate of this of refrigerant is corresponding to the flow rate through the refrigerant of first evaporimeter 14.
Carry out the calculating of total flow of refrigerant speed by known method, for example, described known method is a kind of flow rate computational methods of utilizing the rational expression between predefined cooling condition and the flow of refrigerant speed, perhaps is the pressure sensor that relates to the on high-tension side refrigerant pressure that is provided for detecting refrigerating circulating apparatus 1 and low-pressure lateral pressure and a kind of flow rate computational methods of calculating according to the detected value of two sensors.
After this, calculate the optimal flow speed ratio (step S130) that sets in advance (mapped) with respect to total flow rate.Promptly, in step S130, the ratio that controller calculates the flow rate G2 of refrigerant through refrigerant branch road path 20 time that sucks from the flow rate G1 of refrigerant through coolant circulation route 10 time of the nozzle segment 13a ejection of injector 13 and refrigerant suction inlet 13b from injector 13 is with as the optimal flow speed ratio.
Then, the iptimum speed that is calculated from step S130 is than the best refrigerant discharge rate that calculates first compressor 11 and second compressor 21.When compressor 11 and 21 is the variable displacement type, determine optimum capacity.When compressor 11 and 21 was motor compressor, the optimum speed of each motor was determined to control the operation (step S160) of first and second compressors 11 and 21.
At last, the operation of the drive motor of control cooling fan 36 and air blast 31 producing optimal air amounts (step S170) from cooling fan 36 and air blast 31, and then makes the operation of controller return step S110.
When starting first compressor 11 shown in Fig. 1 and second compressor 21, the control operation meeting of above-mentioned controller 100 causes gas refrigerant to flow to the branch of branch point Z from first evaporimeter 14, and be inhaled into compressor 11 and 21 and by compressor 11 and 12 the compression.
By the compression of first compressor 11 and from the cryogen flow of the high temperature of its discharge and high pressure to first radiator 12.In first radiator 12, the hyperthermia induced cryogen cools off by extraneous air (air that the vehicle compartment is outer) and condenses.The high pressure liquid phase refrigerant that flows out from first radiator 12 flows towards injector 13.
On the contrary, flow into second radiator 22 by the compression of second compressor 21 and from the high temperature and the high-pressure refrigerant of its discharge.In second radiator 22, the hyperthermia induced cryogen is cooled by extraneous air (air of outside) and condenses.The high pressure liquid phase refrigerant that flows out from second radiator 22 becomes the low-pressure refrigerant that flows into second evaporimeter 24 by expansion valve 23 decompressions.In second evaporimeter 24, the absorption of air heat that the quilt that refrigerant flows from the direction in arrow A blows also then evaporates.
13 interior cryogen flow are depressurized by nozzle segment 13a and expand from first radiator 12 to injector.Therefore, the pressure of refrigerant can be converted into the speed energy at nozzle segment 13a place, so that refrigerant is with the jet ejection of high speed from nozzle segment 13a.At this moment, because the decline of refrigerant pressure is sucked from refrigerant suction inlet 13b through the refrigerant (gas phase refrigerant) after second evaporimeter 24 of branch's refrigerant paths 20.
In the mixing portion 13c that is arranged on nozzle segment 13a downstream, mix mutually to flow into diffuser 13d with the refrigerant that sucks from refrigerant suction inlet 13b from the refrigerant of nozzle segment 13a ejection.In diffuser 13d, the speed of refrigerant (expansion) energy converts the pressure energy to by the zone, path that enlarges refrigerant, thereby causes the increase of refrigerant pressure.
The refrigerant that flows out from the diffuser 13d of injector 13 flows into first evaporimeter 14.The absorption of air heat that low temperature that flows in first evaporimeter 14 and low-pressure refrigerant can be on the direction in arrow A blow from the quilt of first evaporimeter, 14 outside processes also then evaporates.Evaporate that gas phase refrigerant after the branch at above-mentioned branch point Z place is inhaled into first compressor 11 and second compressor 21 once more and by these two compressor compresses.
Refrigerant pressure increases part (promptly by the pressure of injector 13, mixing portion 13c and diffuser 13d) and increase, so that the refrigerant evaporating pressure (refrigerant evaporating temperature) in second evaporimeter 24 is lower than the refrigerant evaporating pressure (refrigerant evaporating temperature) in first evaporimeter 14.
Refrigerant evaporating temperature first evaporimeter 14 higher with respect to the flow direction A of the air that is blowed is configured in upstream side, and the second lower evaporimeter 24 of refrigerant evaporating temperature is configured in the downstream.This can guarantee the refrigerant evaporating temperature at first evaporimeter, 14 places at an easy rate and the temperature of the air that blowed between difference and the difference between the temperature of the refrigerant evaporating temperature at second evaporimeter, 24 places and the air that blowed.
Therefore, the cooling performance of first evaporimeter 14 and second evaporimeter 24 all can be improved.Therefore, the cooling performance of the shared cooling space 40 that cool off is improved effectively by the combination of first and second evaporimeters 14 and 24.First and second compressors 11 and 21 suction pressure are increased by the pressurization of mixing portion 13c and diffuser 13d, thereby have reduced the driving force of compressor 11 and 21.
Therefore, from the refrigerant of the nozzle segment 13a of injector 13 ejection through coolant circulation route 10 time flow rate G1 and inferred from the flow rate G2 of refrigerant the time that the refrigerant suction inlet 13b of injector 13 sucks and to be had the optimal flow speed ratio that is calculated the step S130 through refrigerant individual path 20.The flow rate (summation of G1 and G2) of the whole refrigerant of circulation is for total flow rate of being calculated among the step S120 and corresponding to cooling capacity in refrigerating circulating apparatus 1.
Therefore, can regulate according to required cooling capacity through the flow rate (G1+G2) of the refrigerant of first evaporimeter 14 and through the flow rate (G2) of the refrigerant of second evaporimeter 24, thereby allow the further cooling performance that improves.
Usually, under the very little condition of cycling hot load, high pressure and the difference between the low pressure in the circulation can diminish, thereby cause the less input of injector 13.In this case, only decide through the flow rate of the refrigerant of second evaporimeter on the refrigerant inlet capacity of injector.This can cause the reduction of the flow of refrigerant speed of the reduction of refrigerant inlet capacity of input minimizing, injector of injector and second evaporimeter, thereby makes the cooling performance that is difficult to guarantee second evaporimeter.
On the contrary, according to this present embodiment, the cryogen circuit of refrigerating circulating apparatus 1 diverges at the upstream side of compressor, and parallel the linking to each other of path of the path of the nozzle segment 13a of refrigerant input injector 13 and the refrigerant suction inlet 13b that refrigerant is inhaled into injector 13. Compressor 11 and 21 is separately positioned on two paths of the rate of discharge that is used to control refrigerant.
Therefore, not only utilize the refrigerant inlet capacity of injector 13 but also utilize the refrigerant of compressor 21 to suck and the discharge ability can be fed to refrigerant refrigerant individual path 20.Even when the minimizing of the input that injector 13 occurs caused the phenomenon of reduction of refrigerant inlet capacity of injector 13, this also can reduce the reduction degree of the flow of refrigerant speed on second evaporimeter 24.Therefore, even under the condition of the low heat load in refrigerating circulating apparatus 1, also guarantee the cooling performance of second evaporimeter 24 easily.
In addition, controller 100 can be controlled the flow rate G2 of the refrigerant that sucks from the flow rate G1 of the refrigerant of the nozzle segment 13a of injector 13 ejection and from the refrigerant suction inlet 13b of injector 13 at an easy rate by the operation of controlling first compressor 11 and second compressor 21.
In addition, injector 13 can be the type of the extent of opening of fixed nozzle part 13a, and expansion valve 23 can be fixed restrictive valve.Therefore, do not need the nozzle opening governor motion of injector 13, the choke valve opening governor motion and the similar device of expansion valve 23.This can simplify the structure of refrigerating circulating apparatus, thereby cost is reduced.
Although an example has been described in first embodiment, wherein steam compression type refrigerating circulating apparatus 1 is used in the refrigerating circulating apparatus that is used for vehicle, yet the refrigerating circulating apparatus that applies the present invention to it is particularly useful for being used for the air-conditioning of vehicle (for example bus or the inner analog that has than large space).
The known air-conditioning that is used for bus or analog has the aforesaid large space that air-conditioning is housed, and therefore comprises a plurality of coolant compressors that refrigerating circulating apparatus is installed, and loop number is corresponding to the quantity of compressor.For example, known air-conditioning is equipped with and two irrelevant refrigerating circulating apparatus systems of compressor.
On the contrary, in the air-conditioning of the refrigerating circulating apparatus 1 that adopts first embodiment, even when using two compressors to show the cooling capacity of two evaporimeters, generally also can partly use the refrigerant pipeline system, thereby allow the simplification pipeline in low-pressure side.
(second embodiment)
Then, with reference to Fig. 3 and Fig. 4 the second embodiment of the present invention is described hereinafter.
Compare with the first above-mentioned embodiment, the decompressor that the difference of second embodiment and first embodiment is to flow into the refrigerant of second evaporimeter is variable decompressor (variable decompressionmeans).In a second embodiment, the designated identical reference symbol of element that has with first embodiment, and therefore will omit explanation hereinafter to these elements.
As shown in Figure 3, in a second embodiment, the decompressor of refrigerant individual path 20 is an electric expansion valve 23A.The reduction that controller 100 is regulated refrigerant pressure by the extent of opening of regulating electric expansion valve 23A.
As shown in Figure 4, after step S130, whether the operating condition that controller 100 can be identified for obtaining the best refrigerant discharge rate of second compressor 21 is stable operating condition (step S140).More specifically, in step S140, determine whether to obtain the best refrigerant discharge rate (G2) that is used to circulate, unless second compressor 21 is to be equal to or less than the desired speed of can stable operation and driving second compressor 21 (for example, near the lower limit of rotating speed, perhaps described lower limit rotating speed) running.
When unless second compressor 21 can stable operation and drive its desired speed running to be equal to or less than, otherwise in the time of can't obtaining best flow of refrigerant speed, promptly, when the best refrigerant discharge rate that is used to circulate for second compressor 21 too hour, the rotating speed of second compressor 21 can be fixed on desired speed, and the extent of opening of electric expansion valve 23A is limited to handle small flow speed (step S150).Then, in step S160, compressor 11 and 21 operation all are controlled.
In a second embodiment, when second compressor, 21 runs steadilies, controller 100 is controlled flow of refrigerant speed G2 by the refrigerant discharge rate of regulating second compressor 21, simultaneously the fixing extent of opening of the choke valve of electric expansion valve 23A.When being difficult to obtain the steady running of second compressor 21, controller 100 meetings are controlled flow of refrigerant speed G2 by the extent of opening of the choke valve of adjusting electric expansion valve 23A, fix the refrigerant discharge rate of second compressor 21 simultaneously.
Therefore, when need be through the amount of refrigerant of second evaporimeter 24 more after a little while, the rotating speed (control rate of discharge) of the stable operation location that this demand can be by control second compressor 21 or the extent of opening by control electric expansion valve 23A obtain.
In addition, because the decrease of the refrigerant pressure of the refrigerant discharge rate of second compressor 21 and electric expansion valve 23A need not to change simultaneously,, controller 100 controls so carrying out easily.
Under the situation that the decrease of the refrigerant pressure of the refrigerant discharge rate of second compressor 21 and electric expansion valve 23A needs to change simultaneously, when need be through the amount of refrigerant of second evaporimeter 24 seldom the time, rate of discharge combines to regulate flow rate the adjusting of second compressor 21 in can the scope of steady running with the adjusting of the extent of opening of the choke valve that is undertaken by electric expansion valve 23A.
(the 3rd embodiment)
Then, will the third embodiment of the present invention be described hereinafter according to Fig. 5 to Fig. 9.
The main difference of the 3rd embodiment and first embodiment is, is adjusted in the flow rate of flowing refrigerant in second evaporimeter 24 after heat exchange according to the degree of superheat of refrigerant.In the 3rd embodiment, the designated identical reference symbol of element that has with first embodiment, and therefore will omit explanation hereinafter to these elements.
As shown in Figure 5, in the refrigerating circulating apparatus 1 of described embodiment, the high pressure sensor 91 that is used for detecting the on high-tension side refrigerant pressure of coolant circulation route 10 is set at the downstream of first compressor 11 of coolant circulation route 10 and the upstream side of first radiator 12.In addition, the high pressure sensor 92 that is used for detecting the on high-tension side refrigerant pressure of coolant circulation route 20 is set at the downstream of second compressor of refrigerant individual path 20 and the upstream side of second radiator 22.
On the other hand, the low pressure sensor 93 of refrigerant pressure that is used for detecting the low-pressure side of coolant circulation route 10 is set at the downstream of first evaporimeter 14 of coolant circulation route 10 and the upstream side of first compressor 11 (in this embodiment, branch point Z upstream side).In addition, the low pressure sensor 94 of refrigerant pressure that is used for detecting the low-pressure side of refrigerant individual path 20 is set at the upstream side of the refrigerant suction inlet 13b of the downstream of second evaporimeter 24 of refrigerant individual path 20 and injector 13.
In addition, be used to detect the downstream part that on air-flow direction A, is arranged on second evaporimeter 24 through the air temperature sensor 95 of the temperature of the cooling air of second evaporimeter 24.
In the 3rd embodiment, first and second compressors 11 and 21 are the motor compressor that is driven by phase inverter (inverter).First compressor 11 comprises a negative circuit 11a, and second compressor 21 comprises a negative circuit 21a.Therefore, controller 100 is suitable in control first and second compressors 11 and control signal being outputed to these negative circuits 11a and 21a at 21 o'clock.
Now, the operation of the steam compression type refrigerating circulating apparatus 1 of the 3rd embodiment will be described hereinafter according to said structure.
Fig. 6 is the flow chart of the schematic control operation of the controller 100 of this embodiment of demonstration.
As shown in Figure 6, during when the connection ignition switch and from power supply supply direct current, controller 100 at first presets tentation data or similar information (step S101).Then, controller 100 reads signal (step S102) from above-mentioned various sensors and temperature setting switch or similar device.
Then, calculate target air temperature (step S110A).That is, in step S110A, the preset temperature in the space 40 that calculating will be cooled off and by the temperature difference T (corresponding to required cooling capacity) between the temperature in the detected spaces that will cool off 40 of Inside Air Temperature sensor 90.Step S110 during step S110A implements corresponding to first and second.
After execution in step S110A, determine the rotating speed (rotating speed of target) (step S210) of first compressor 11 according to the target air temperature that is calculated.As shown in Figure 7, for example, from shown in relation determine the rotating speed of target of first compressor 11.
That is, calculate rotating speed of target by proofreading and correct current tachometer according to temperature difference T.This can represent by following relational expression:
Rotating speed of target=current rotating speed ± based on the rotating speed recruitment of the temperature difference.
Therefore, when difference DELTA T was very big, the rotating speed of first compressor 11 can significantly increase, thereby made the recruitment of the flow of refrigerant speed on the coolant circulation route 10 very big.On the contrary, when difference DELTA T was very little, the recruitment of the rotating speed of first compressor 11 was very little, thereby the increase of the flow of refrigerant speed on the coolant circulation route 10 is diminished.
After execution in step S210 is with the rotating speed of target that calculates first compressor 11, calculate the degree of superheat SH (step S220) of the refrigerant in second evaporimeter, 24 exits.More specifically, calculate the degree of superheat SH of the refrigerant in second evaporimeter, 24 exits according to the refrigerant temperature in the refrigerant pressure in second evaporimeter, 24 exits and second evaporimeter, 24 exits, wherein said refrigerant pressure is detected by low pressure sensor 94, and described refrigerant temperature is that the temperature estimation from air temperature sensor 95 detected cooling blow air draws.
After execution in step S220, determine the rotating speed of target (step S230) of second compressor 21 according to the refrigerant degree of superheat SH in second evaporimeter, 24 exits that calculated.In step S230, for example, determine the rotating speed of target of second compressor 21 according to the flow chart shown in Fig. 8.
As shown in Figure 8, whether the refrigerant degree of superheat SH that determines second evaporimeter, 24 exits is not less than " a " and also is not more than " b " (step S231).When definite degree of superheat SH to the scope of " b " time (if step S231 is for being), in fact keeps the rotating speed (step S232) of second compressor 21 at " a ".
When determining that in step S231 degree of superheat SH to the scope of " b " time, does not determine whether the degree of superheat SH of refrigerant is lower than " a " (step S233) at " a ".When definite degree of superheat SH was lower than " a ", the rotating speed of second compressor 21 can be reduced to the level (step S234) that is lower than current rotating speed.When in step S233, determining that degree of superheat SH is not less than " a " (described step is after step S231, that is, when definite degree of superheat SH essence exceeds " b "), the rotating speed of second compressor 21 can be increased to a level (step S235) that is higher than current rotating speed.
Determine super heat value " a " and " b " from as shown in Figure 9 degree of superheat SH and the relation between the cooling capacity into the definite basis the flow chart shown in Fig. 8.As the result of the wholwe-hearted research of inventor, find this relation shown in Fig. 9, show that simultaneously the degree of superheat SH of the refrigerant in second evaporimeter, 24 exits does not have much affect to cooling capacity.
As the degree of superheat SH of the refrigerant in second evaporimeter, 24 exits during less than " a ", the liquid refrigerants in second evaporimeter 24 can not evaporate yet, and can't obtain enough cooling capacities thus.
In addition, as the refrigerant degree of superheat SH in second evaporimeter, 24 exits during greater than " b ", the amount that flows into the refrigerant of second evaporimeter 24 is insufficient, and heat-shift therefore and between the gas phase refrigerant at the part place, downstream in second evaporimeter 24 and the blow air.The heat exchanger effectiveness in first evaporimeter 14 in addition, enters first evaporimeter 14 by injector 13, so can reduce owing to have the refrigerant of big degree of superheat SH.In addition, when refrigerant degree of superheat SH exceeds " b " in the exit of second evaporimeter 24, this can't show enough cooling capacities.
Therefore, in step S230, calculate and determine the rotating speed of target of second compressor 21, (promptly with the scope of the refrigerant degree of superheat SH that keeps second evaporimeter, 24 exits, the numerical value of a≤SH≤b), described scope can show predeterminated level or higher levels of cooling capacity.
More specifically, can repeat following operation: the rotating speed → increase flow of refrigerant speed G2 → reduction degree of superheat SH of big degree of superheat SH → increase compressor 21; And the rotating speed of small offence temperature SH → reduction compressor 21 → reduction flow of refrigerant speed G2 → increase degree of superheat SH.Therefore, this can cause numerical value to satisfy the relation of a≤SH≤b.
After execution in step S230 and the step before other, the indicated control signal of rotating speed of target outputs to the negative circuit 11a and the 21a of first and second compressors 11 and 21, thereby controls the running of first and second compressors 11 and 21.In addition, operation control outputs to the drive motor of cooling fan 36 and the drive motor of air blast 31, with the air (step S160A) from cooling fan 36 and air blast 31 generation optimised quantities.Then, operation can be returned the starting point of the flow chart among Fig. 6.
By said structure and operation, controller 100 is controlled from the flow rate G1 of the refrigerant of nozzle segment 13a ejection and the ratio of the flow rate G2 of the refrigerant that sucks from refrigerant suction inlet 13b according to the refrigerant degree of superheat SH in second evaporimeter, 24 exits, thereby can control flow rate G2 through the refrigerant of second evaporimeter 24 best according to degree of superheat SH.Therefore, can carry out effective driving and can not be subjected to the influence of fluctuating load, and can obtain stable cooling performance, thereby improve the coefficient of performance (COP).
Can calculate the refrigerant degree of superheat SH in second evaporimeter, 24 exits at an easy rate according to the pressure and temperature of the refrigerant in second evaporimeter, 24 exits.In addition, the pressure and temperature of the refrigerant in second evaporimeter, 24 exits is based on the detection numerical value of low pressure sensor 94 and air temperature sensor 95, and therefore the checkout gear that is specifically designed to detection degree of superheat SH need not be set.Therefore, the structure of refrigerating circulating apparatus 1 can not become complicated.
Be similar to first embodiment, fixed restrictive valve is applied in the expansion valve 23 in refrigerant branch road path 20 and need not to use relatively expensive electric expansion valve, thereby can implement described control to obtain stable cooling performance.
(other embodiment)
Although proved absolutely the present invention together with its preferred embodiment, yet to be that various changes and modification will become clear to those skilled in the art with reference to accompanying drawing with mentioning.
For example, in the first and the 3rd above-mentioned embodiment, first and second compressors 11 and 21 are the variable displacement type, and the nozzle segment 13a of injector and expansion valve 23 are the fixed restriction type.In above-mentioned second embodiment, first and second compressors 11 and 21 are the variable displacement type, and the nozzle segment 13a of injector is the throttling fixed type, and electric expansion valve 23A is the variable restrictor type.Yet refrigerating circulating apparatus of the present invention is not limited thereto.For example, in the amount that the refrigerant of first compressor 11 is discharged and refrigerant pressure is reduced by injector nozzle part 13a at least one can be regulated, and in the amount that the refrigerant of second compressor 21 is discharged and refrigerant pressure is reduced by expansion valve 23 at least one can be regulated.
According to one in these measurements, can regulate at least one in the amount that the refrigerant discharge rate of first compressor 11 and refrigerant pressure reduced by injector nozzle part 13a, thereby can regulate from the flow rate G1 of the refrigerant of nozzle segment 13a ejection.In addition, can regulate at least one in the amount that the refrigerant discharge rate of second compressor 21 and refrigerant pressure reduced by expansion valve 23, thereby can regulate the flow of refrigerant speed G2 that sucks from the refrigerant suction inlet 13b of injector.
That is, can regulate flow rate, thereby cause the further improvement of cooling performance through the refrigerant of first evaporimeter 14 and second evaporimeter 24.
In addition, although in the 3rd above-mentioned embodiment, calculate the refrigerant degree of superheat SH in second evaporimeter, 24 exits according to low pressure sensor 94 detected pressure and air temperature sensor 95 detected detected temperatures, yet can use any other element that can detect or calculate degree of superheat SH.For example, the refrigerant temperature sensor can be arranged on the downstream of second evaporimeter 24 together with low pressure sensor 94.
In addition, in the 3rd above-mentioned embodiment, calculate the refrigerant degree of superheat SH in second evaporimeter, 24 exits, and according to the degree of superheat control flow rate ratio that is calculated.Yet, when demonstration send as an envoy to flow rate that degree of superheat SH obtains appropriate value in advance than the time, can be according to making degree of superheat SH obtain the described flow rate of appropriate value than the control of implementing second compressor 21.
Even be that refrigerant degree of superheat SH according to second evaporimeter, 24 exits controls the flow rate ratio in this case, with being appreciated that.This can obtain good cooling performance and need not all to calculate degree of superheat SH in each program.
For example, when first and second compressors 11 and 21 identical in specification, and degree of superheat SH in flow rate than φ=0.5 (G1: G2=1: in the time of 1) and when obviously obtaining an appropriate value, first compressor 11 is controlled to have identical rotating speed with second compressor 21.This can significantly simplify control.
Alternatively, the refrigerant degree of superheat SH that need not to calculate second evaporimeter, 24 exits can calculate total flow rate (corresponding to the flow rate of G1+G2), and consider refrigerant degree of superheat SH in advance, compressor 11 all is controlled the flow rate ratio that shines upon mutually or be associated with described relation to obtain with 21 rotating speed.Even be that refrigerant degree of superheat SH according to second evaporimeter, 24 exits controls the flow rate ratio in this case, with being appreciated that.
In the control flow chart shown in Fig. 6, can omit the step S220 that calculates degree of superheat SH according to the pressure and temperature of the refrigerant in second evaporimeter, 24 exits, and from nozzle segment 13a directly the ratio of flow rate G1 and the flow rate G2 of the refrigerant that sucks from refrigerant suction inlet 13b of the refrigerant of ejection can be controlled.This can control flow rate through second evaporimeter 24 best according to the pressure and temperature of refrigerant.Therefore, can further improve cooling performance, simultaneously drive described circulation effectively, and need not to calculate the refrigerant degree of superheat SH at each place in control time.
In each above-mentioned embodiment, refrigerating circulating apparatus 1 is made of first and second compressors 11 and 21, first and second radiators 12 and 22, injector 13, expansion valve 23 or 23A and first and second evaporimeters 14 and 24, and described all devices are connected with each other by pipeline.Yet in refrigerating circulating apparatus, parts are not limited only to these elements.
For example, if necessary, as shown in Figure 10, refrigerating circulating apparatus can suitably be provided with any one in container 51 and 52, expansion valve 53 and the accumulator 54.Herein, container 51 and 52 is used to make refrigerant to punish into liquid and steam in each radiator 12,22 downstream part, simultaneously excessive refrigerant is stored in the described container.Particularly, first container 52 is positioned at the upstream side of the nozzle segment 13a of the downstream of first radiator 12 and injector 13, in order to will be divided into vapor refrigerant and liquid refrigerant from the refrigerant of first radiator 12.In addition, second container 51 is positioned at the downstream of second radiator 22 and the upstream side of second evaporimeter 24, in order to will be divided into vapor refrigerant and liquid refrigerant from the refrigerant of second radiator 22.When the nozzle segment 13a of injector 13 was the fixed restriction type, expansion valve 53 was carried out precision adjustment to the refrigerant pressure of the nozzle segment 13a that flows into injector 13 according to the degree of superheat of the refrigerant that flows out from first evaporimeter 14.Expansion valve 53 makes the extent of opening that can come variable expansion valve 53 according to the degree of superheat of the refrigerant that flows out first evaporimeter 14 between the nozzle segment 13a of first radiator 12 and injector 13.
In addition, accumulator 54 is used for partly refrigerant being divided into liquid and steam so that excessive refrigerant is stored in it at upstream of compressor, regulates the oil mass of returning compressor simultaneously.Accumulator 54 is positioned at the downstream of first evaporimeter 14 and the upstream of first and second compressors.
Although in each above-mentioned embodiment the refrigerating circulating apparatus that is used for vehicle has been described, yet has been apparently, except that the circulation that is used for vehicle, the present invention can be applied to fixedly refrigerating circulating apparatus or similar device in the same manner.
In each above-mentioned embodiment, do not state clearly the type of refrigerant, but refrigerant can be the overcritical circulation that is applied to steam compressed type or in the subcritical cycle any, for example the replacement fluorine Lyons (substitute Freon) or the carbon dioxide (CO of fluorine Lyons (CFC) base or HC base
2).Term fluorine described herein Lyons is the general term of the organic compound be made up of carbon, fluorine, chlorine and hydrogen, and is widely used as refrigerant.Fluorine Lyons base refrigerant comprises the basic refrigerant of HCFC (HCFC), HFC (hydrogen fluorine carbide) basic refrigerant and similar refrigerant, owing to they can not damage the ozone layer, so be known as replacement fluorine dragon (substitute flons).
In addition, the basic refrigerant of HC (hydrocarbon) is to comprise the refrigerant materials of hydrogen and carbon and be present in occurring in nature.This HC base refrigerant comprises R600a (iso-butane), R290 (propane) and similar material.
This change and modification are understood to be in the scope of the present invention that is limited by claims.
Claims (23)
1. refrigerating circulating apparatus comprises:
First compressor (11), described first compressor are used to suck and the refrigerant of compression refrigerant to have compressed from its discharge;
Be used for first radiator (12) of radiation from the heat of the refrigerant of first compressor (11) discharge;
The injector (13) that comprises nozzle segment (13a) and refrigerant suction inlet (13b), the pressure that wherein said nozzle segment is used for the refrigerant that will flow out from first radiator (12) can convert the speed energy to, and be used to make refrigerant decompression and expansion, suck refrigerant from described refrigerant suction inlet by cryogen flow from nozzle segment (13a) ejection;
Be used to evaporate first evaporimeter (14) of the refrigerant of outflow jet (13);
Second compressor (21), described second compressor are used to suck and the refrigerant of compression refrigerant to have compressed from its discharge;
Be used for second radiator (22) of radiation from the heat of the refrigerant of second compressor (21) discharge;
Be used to make refrigerant decompression of flowing out second radiator (22) and the decompressor that expands (23,23A); And
Second evaporimeter (24), described second evaporimeter be used to evaporate decompressor (23, the 23A) refrigerant that is reduced pressure, second evaporimeter (24) is connected to refrigerant suction inlet (13b),
Wherein first evaporimeter (14) is connected to first compressor (11) and second compressor (21), so that be assigned between first compressor (11) and second compressor (21) and be inhaled in its described two compressors from the refrigerant of first evaporimeter (14).
2. refrigerating circulating apparatus according to claim 1 further comprises:
Accumulator (54), described accumulator is positioned at the downstream of first evaporimeter (14) and the upstream of described first and second compressors, in order to will being divided into vapor refrigerant and liquid refrigerant, and be used for excessive refrigerant is stored within it from the refrigerant of first evaporimeter (14).
3. refrigerating circulating apparatus according to claim 1 and 2 further comprises:
Expansion valve (53), described expansion valve are positioned between the nozzle segment (13a) of first radiator (12) and injector (13), and wherein the extent of opening of expansion valve (53) is regulated according to the degree of superheat of the refrigerant that flows out first evaporimeter (14).
4. refrigerating circulating apparatus according to claim 1 and 2 further comprises:
First container (52), described first container are positioned at the upstream side of the nozzle segment (13a) of the downstream of first radiator (12) and injector (13), in order to being divided into vapor refrigerant and liquid refrigerant from the refrigerant of first radiator (12); And
Second container (51), described second container are positioned at the downstream of second radiator (22) and the upstream side of second evaporimeter (24), in order to being divided into vapor refrigerant and liquid refrigerant from the refrigerant of second radiator (22).
5. refrigerating circulating apparatus according to claim 1, wherein:
Injector (13) comprises that also pressure increases part (13c, 13d), described pressure increases part and is used for when the refrigerant from nozzle segment (13a) ejection mixes mutually with the refrigerant that sucks from refrigerant suction inlet (13b) the speed power conversion being become pressure energy, thereby increases the pressure of refrigerant;
In the amount that the refrigerant discharge rate of first compressor (11) and refrigerant pressure are reduced by nozzle segment (13a) at least one can be regulated; And
In the amount that the refrigerant discharge rate of second compressor (21) and refrigerant pressure are reduced by decompressor (23) at least one can be regulated.
6. refrigerating circulating apparatus according to claim 5, further comprise control device (100), described control device is used for regulating at least one of amount that the refrigerant discharge rate of first compressor (11) and refrigerant pressure reduced by nozzle segment (13a), refrigerant discharge rate and the refrigerant pressure of regulating second compressor (21) simultaneously pass through decompressor (23,23A) at least one in the amount that is reduced is with the ratio of control from flow rate with the flow rate of the refrigerant that sucks from refrigerant suction inlet (13b) of the refrigerant of nozzle segment (13a) ejection.
7. refrigerating circulating apparatus according to claim 6, wherein control device (100) is controlled from the ratio of flow rate with the flow rate of the refrigerant that sucks from refrigerant suction inlet (13b) of the refrigerant of nozzle segment (13a) ejection according to the refrigerant degree of superheat in the exit of second evaporimeter (24).
8. refrigerating circulating apparatus according to claim 7, the refrigerant temperature checkout gear (95) that further comprises the refrigerant pressure checkout gear (94) of the refrigerant pressure that is used to detect second evaporimeter (24) exit and be used to detect the refrigerant temperature in second evaporimeter (24) exit
Wherein control device (100) calculates the degree of superheat according to detected refrigerant pressure of refrigerant pressure checkout gear (94) and the detected refrigerant temperature of refrigerant temperature checkout gear (95).
9. refrigerating circulating apparatus according to claim 6, the refrigerant temperature checkout gear (95) that further comprises the refrigerant pressure checkout gear (94) of the refrigerant pressure that is used to detect second evaporimeter (24) exit and be used to detect the refrigerant temperature in second evaporimeter (24) exit
Wherein control device (100) is controlled from the ratio of flow rate with the flow rate of the refrigerant that sucks from refrigerant suction inlet (13b) of the refrigerant of nozzle segment (13a) ejection according to the detected refrigerant pressure of refrigerant pressure checkout gear (94) and the detected refrigerant temperature of refrigerant temperature checkout gear (95).
10. refrigerating circulating apparatus according to claim 8, wherein refrigerant pressure checkout gear (94) is for being configured in the pressure sensor (94) of second evaporimeter (24) outlet side, and refrigerant temperature checkout gear (95) is for being used for detecting the temperature sensor (95) through the temperature of the external fluid of second evaporimeter (24).
11. refrigerating circulating apparatus according to claim 5, wherein the refrigerant discharge rate of the refrigerant discharge rate of first compressor (11) and second compressor (21) all can be regulated.
12. refrigerating circulating apparatus according to claim 5, wherein the refrigerant discharge rate of the refrigerant discharge rate of first compressor (11) or second compressor (21) can be regulated.
13. refrigerating circulating apparatus according to claim 12, wherein the refrigerant discharge rate of first compressor (11) can be regulated.
14. refrigerating circulating apparatus according to claim 12, wherein the refrigerant discharge rate of second compressor (21) can be regulated.
15. refrigerating circulating apparatus according to claim 11, wherein nozzle segment (13a) has fixing extent of opening.
16. refrigerating circulating apparatus according to claim 11, wherein decompressor (23) is fixed restriction device (23).
17. according to each described refrigerating circulating apparatus in the claim 5 to 12,
Wherein the refrigerant discharge rate of second compressor (21) and refrigerant pressure can be regulated by the amount that decompressor (23A) is reduced, and
Wherein, when the refrigerant discharge rate of second compressor (21) was reduced to a scheduled volume, refrigerant pressure increased by the amount that decompressor (23) is reduced.
18. refrigerating circulating apparatus according to claim 17, wherein, when the refrigerant discharge rate of second compressor (21) was reduced to described scheduled volume, the refrigerant discharge rate of second compressor (21) was fixed on described scheduled volume.
19. according to each described refrigerating circulating apparatus in the claim 5 to 12, wherein first evaporimeter (14) is oriented to cool off respectively different spaces with second evaporimeter (24).
20. according to each described refrigerating circulating apparatus in the claim 5 to 12, wherein first evaporimeter (14) and second evaporimeter (24) are oriented to cool off single space.
21., further comprise according to each described refrigerating circulating apparatus in the claim 5 to 12:
First container (52), described first container are positioned at the upstream side of the nozzle segment (13a) of the downstream of first radiator (12) and injector (13), in order to being divided into vapor refrigerant and liquid refrigerant from the refrigerant of first radiator (12); And
Second container (51), described second container are positioned at the downstream of second radiator (22) and the upstream side of second evaporimeter (24), in order to being divided into vapor refrigerant and liquid refrigerant from the refrigerant of second radiator (22).
22. according to each described refrigerating circulating apparatus in the claim 5 to 12, wherein locate to diverge at a branch point (Z) of first compressor (11) and second compressor (21) upstream from the refrigerant of first evaporimeter (14), described device further comprises:
Accumulator (54), described accumulator is positioned at the downstream of first evaporimeter (14) and the upstream of branch point (Z), in order to will being divided into vapor refrigerant and liquid refrigerant, and be used for excessive refrigerant is stored within it from the refrigerant of first evaporimeter (14).
23., further comprise according to each described refrigerating circulating apparatus in the claim 5 to 12:
Expansion valve (53), described expansion valve are positioned between the nozzle segment (13a) of first radiator (12) and injector (13), and wherein, the extent of opening of expansion valve (53) is regulated according to the degree of superheat of the refrigerant that flows out first evaporimeter (14).
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| Application Number | Priority Date | Filing Date | Title |
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| JP2005227065 | 2005-08-04 | ||
| JP2005227065 | 2005-08-04 | ||
| JP2006014186 | 2006-01-23 |
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| CN1908553A CN1908553A (en) | 2007-02-07 |
| CN100436962C true CN100436962C (en) | 2008-11-26 |
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| CNB2006101091535A Expired - Fee Related CN100436962C (en) | 2005-08-04 | 2006-08-03 | Refrigeration cycle device with injector |
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