JP2016211827A - Refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the leakage of a refrigerant from a refrigerant hose in a refrigeration cycle device which employs a hydrofluoroolefin-system refrigerant.SOLUTION: A multi-layered hose having a rubber layer 15a and a resin layer 15c as a high-pressure refrigerant hose for connecting a discharge port of a compressor 11 and a refrigerant flow-in port of a heat radiator 12 is employed to a refrigerant cycle device in which HFO-1234f is employed as a refrigerant, and PAG oil is employed as refrigerator oil. Furthermore, a refrigerant which is boosted by a diffuser passage 13c of an ejector 13 is separated in an air-liquid separation space 30f, the separated air-phase refrigerant is made to flow into a suction side of the compressor 11, and the separated liquid-phase refrigerant is made to flow into an evaporator 14, thus constituting a cycle constitution. By this constitution, a saturated air-phase refrigerant which is higher in pressure than an outlet-side refrigerant of the evaporator 14 is sucked into the compressor 11, a temperature of a discharge refrigerant of the compressor 11 is lowered, and the deterioration of the high-pressure refrigerant hose is thereby suppressed.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a vapor compression refrigeration cycle apparatus.

  Conventionally, in a vapor compression refrigeration cycle apparatus mounted on a vehicle, a refrigerant hose formed of rubber and resin is generally used as a refrigerant transportation pipe connected to the suction side and discharge side of the compressor. Has been. Thereby, it is suppressed that the vibration of a compressor will be transmitted to other vehicle equipment or a vehicle interior.

  For example, Patent Document 1 discloses a refrigerant hose of this type having a multilayer structure in which an outer peripheral layer is formed of rubber and an inner peripheral layer is formed of resin. In the refrigerant hose of Patent Document 1, by providing the resin layer, the refrigerant in the refrigeration cycle apparatus is prevented from leaking outside through the rubber layer.

JP-A-5-52280

  By the way, in order to cope with recent environmental problems such as global warming, it is desired to employ a refrigerant having a low global warming potential as a refrigerant of the refrigeration cycle apparatus.

  However, a hydrofluoroolefin-based refrigerant (for example, HFO-1234yf) that has been attracting attention as a refrigerant having a relatively low global warming potential is a refrigeration having an OH group, such as a general PAG oil (polyalkylene glycol oil). Decomposition with machine oil mixed in will produce hydrofluoric acid. Such hydrofluoric acid promotes deterioration due to oxidation of the resin layer of the refrigerant hose.

  In addition, HFO-1234yf has a lower water vapor partial pressure than a hydrofluorocarbon-based refrigerant (for example, HFC-134a) that has been conventionally used. For this reason, when a hydrofluoroolefin-based refrigerant is employed, external moisture easily penetrates the rubber layer and the resin layer and enters the refrigeration cycle apparatus. Such moisture promotes deterioration due to hydrolysis of the resin layer of the refrigerant hose.

  When the deterioration of the resin layer of the refrigerant hose proceeds, the refrigerant in the refrigeration cycle apparatus passes through the rubber layer and leaks to the outside, and the refrigeration cycle apparatus cannot exhibit the refrigeration capacity.

  In view of the above points, an object of the present invention is to suppress refrigerant leakage from a refrigerant hose in a refrigeration cycle apparatus that employs a hydrofluoroolefin-based refrigerant.

  The present invention is based on the knowledge of the present inventors that deterioration due to oxidation and hydrolysis of the resin layer of the refrigerant hose in a refrigeration cycle apparatus that employs a hydrofluoroolefin refrigerant is likely to proceed in a high temperature environment. It was made.

That is, in the invention according to claim 1, the compressor (11) that compresses and discharges the refrigerant mixed with the refrigeration oil, and the radiator (12, 12) that dissipates the high-pressure refrigerant discharged from the compressor (11). 121), the nozzle (32, 20a) for depressurizing the refrigerant flowing out from the radiator (12, 121), and the suction action of the high-speed jet refrigerant jetted from the nozzle (32, 20a) Body (30, 20b) formed with a pressure increasing part (13c, 20e) for mixing and increasing the pressure of the refrigerant suction port (31b, 20e) and the refrigerant sucked from the refrigerant suction port (31b, 20e). The gas-liquid that separates the gas-liquid refrigerant flowing out from the pressure-increasing section (13c, 20e) and causes the separated gas-phase refrigerant to flow out to the suction port side of the compressor (11). A separation means (30f, 21), an evaporator (14) for evaporating the liquid-phase refrigerant separated by the gas-liquid separation means (30f, 21) and flowing it out to the refrigerant suction port (31b, 20e) side; A high-pressure refrigerant hose (15) connecting the discharge port of the compressor (11) and the refrigerant inlet of the radiator (12, 121),
The high-pressure refrigerant hose (15) is formed in a multilayer structure, and some layers of the high-pressure refrigerant hose (15) are made of rubber, and another part of the layers is made of resin that suppresses the permeation of the refrigerant. And
A hydrofluoroolefin-based refrigerant is employed as the refrigerant, and a refrigeration cycle apparatus employing an OH group as the refrigerating machine oil is a feature.

  According to this, the compressor (11) sucks in the refrigerant whose pressure has been increased by the pressure increase parts (13c, 20e) of the ejectors (13, 20) and is separated by the gas-liquid separation means (30f, 21). Saturated gas phase refrigerant (refrigerant having no superheat degree) can be sucked. Therefore, the temperature of the refrigerant discharged from the compressor (11) can be lowered as compared with a normal refrigeration cycle apparatus that causes the compressor (11) to suck the refrigerant having the superheat degree flowing out of the evaporator (14).

  For this reason, the temperature of the refrigerant | coolant which distribute | circulates a high pressure refrigerant | coolant hose (15) can be lowered | hung rather than a normal refrigerating cycle apparatus, and the progress of deterioration by oxidation of a high pressure refrigerant | coolant hose (15) and degradation by hydrolysis is suppressed. be able to. As a result, even in a refrigeration cycle apparatus in which a hydrofluoroolefin-based refrigerant is employed as the refrigerant and a refrigerant having an OH group is employed as the refrigerating machine oil, the deterioration of the high-pressure refrigerant hose (15) is suppressed. The refrigerant leakage from the high-pressure refrigerant hose (15) can be suppressed.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is a partial cross section perspective view of the high pressure refrigerant hose of a 1st embodiment. It is III-III sectional drawing of FIG. It is a Mollier diagram which shows the change of the state of the refrigerant | coolant in the ejector type refrigeration cycle of 1st Embodiment. It is a Mollier diagram for demonstrating the temperature fall of the discharge refrigerant | coolant in the ejector-type refrigerating cycle of 1st Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment.

(First embodiment)
The first embodiment of the present invention will be described below with reference to FIGS. As shown in FIG. 1, the vapor compression refrigeration cycle apparatus according to the present invention is configured as an ejector refrigeration cycle 10 including an ejector 13 as refrigerant decompression means. This ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior (indoor space) that is a space to be air-conditioned. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.

  Further, in the ejector refrigeration cycle 10, HFO-1234yf, which is a hydrofluoroolefin refrigerant, is adopted as the refrigerant, and the high pressure side refrigerant pressure in the cycle from the discharge port of the compressor 11 to the ejector 13 is the criticality of the refrigerant. The subcritical refrigeration cycle does not exceed the pressure.

  Further, refrigerating machine oil for lubricating the compressor 11 is mixed in the refrigerant. As this refrigerating machine oil, one having compatibility with the liquid phase refrigerant is adopted. More specifically, in this embodiment, PGA oil (polyalkylene glycol oil) having an OH group is employed as the refrigerating machine oil.

  In the ejector-type refrigeration cycle 10, the compressor 11 sucks the refrigerant and discharges it until it becomes high-pressure refrigerant. The compressor 11 is disposed in an engine room together with an internal combustion engine (engine) (not shown) that outputs a driving force for traveling the vehicle. The compressor 11 is driven by a rotational driving force output from the engine via a pulley, a belt, and the like.

  More specifically, in the present embodiment, a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity is employed as the compressor 11. The compressor 11 has a discharge capacity control valve (not shown) for changing the discharge capacity. The operation of the discharge capacity control valve is controlled by a control current output from an air conditioning control device 50 described later.

  A refrigerant inlet side of the condensing part 12a of the radiator 12 is connected to the discharge port of the compressor 11 via a high-pressure refrigerant hose 15. As shown in FIGS. 2 and 3, the high-pressure refrigerant hose 15 is formed in a multilayer structure with rubber, resin, or the like.

  More specifically, a rubber layer 15 a containing a base fabric 15 b is disposed on the outermost peripheral layer of the high-pressure refrigerant hose 15. As the base fabric 15b, one made of polyester or the like can be used. As the rubber layer 15a, one made of EPDM (ethylene propylene diene copolymer rubber), HNBR (hydrogenated nitrile rubber), or the like can be employed. A resin layer 15c is disposed on the inner peripheral side of the rubber layer 15a. As the resin layer 15c, one formed of nylon 6, nylon 66, or the like can be used.

  In the present embodiment, by connecting the compressor 11 and the radiator 12 via the high-pressure refrigerant hose 15, vibration during the operation of the compressor 11 is transmitted to other in-vehicle devices such as the radiator 12 and the vehicle interior. It is suppressed that it is done. Accordingly, a low-pressure refrigerant hose 16 that connects 31d of an ejector 13 and a suction port of the compressor 11 described later is also equivalent to the high-pressure refrigerant hose 15.

  The radiator 12 is a heat exchanger for heat radiation that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12d. .

  More specifically, the heat radiator 12 exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d, and dissipates the high-pressure gas-phase refrigerant to condense and condense the part 12a. In addition, the receiver 12b that separates the gas-liquid of the refrigerant that has flowed out of the condensing unit 12a and stores excess liquid-phase refrigerant, and the liquid-phase refrigerant that has flowed out of the receiver 12b and the outside air blown from the cooling fan 12d exchange heat. This is a so-called subcool condenser that includes a supercooling unit 12c that supercools the liquid refrigerant.

  The cooling fan 12d is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device 50.

  A refrigerant inlet 31 a of the ejector 13 is connected to the refrigerant outlet side of the supercooling portion 12 c of the radiator 12. The ejector 13 functions as a refrigerant pressure reducing means for reducing the pressure of the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 and flowing it to the downstream side, and is described later by the suction action of the refrigerant flow injected at a high speed. It also functions as a refrigerant circulating means (refrigerant transporting means) for sucking (transporting) and circulating the refrigerant flowing out of the evaporator 14.

  Furthermore, the ejector 13 according to the present embodiment also functions as a gas-liquid separation unit that separates the gas-liquid of the decompressed refrigerant. That is, the ejector 13 of the present embodiment is configured as an ejector with a gas-liquid separation function (ejector module).

  In addition, the up and down arrows in FIG. 1 indicate the up and down directions in a state where the ejector 13 is mounted on the vehicle. Therefore, the up and down directions in a state where the constituent devices of the other ejector refrigeration cycle 10 are mounted on the vehicle are not limited to this. Further, FIG. 1 shows an axial sectional view of the ejector 13.

  As shown in FIG. 1, the ejector 13 according to the present embodiment includes a body 30 configured by combining a plurality of constituent members. The body 30 is formed of a prismatic or cylindrical metal or resin. The body 30 is formed with a plurality of refrigerant inlets and outlets, a plurality of internal spaces, and the like.

  As a plurality of refrigerant inflow / outflow ports formed in the body 30, a refrigerant inflow port 31 a that causes the refrigerant that has flowed out from the radiator 12 to flow inside, a refrigerant suction port 31 b that sucks the refrigerant that has flowed out from the evaporator 14, The liquid-phase refrigerant outlet 31c that causes the liquid-phase refrigerant separated in the gas-liquid separation space 30f formed in the evaporator to flow out to the refrigerant inlet side of the evaporator 14 and the gas-phase refrigerant separated in the gas-liquid separation space 30f A gas-phase refrigerant outlet 31d that flows out to the suction side of the compressor 11 is formed.

  The internal space formed in the body 30 includes a swirling space 30a for swirling the refrigerant flowing in from the refrigerant inflow port 31a, a decompression space 30b for decompressing the refrigerant flowing out of the swirling space 30a, and an outflow from the decompression space 30b. A pressurizing space 30e for allowing the refrigerant to flow in, a gas-liquid separation space 30f for separating the gas and liquid of the refrigerant flowing out from the pressurizing space 30e, and the like are formed.

  The swirl space 30a and the gas-liquid separation space 30f are formed in a substantially cylindrical rotating body shape. The decompression space 30b and the pressure increase space 30e are formed in a substantially truncated cone-shaped rotating body shape that gradually expands from the swirl space 30a side toward the gas-liquid separation space 30f side. The central axes of these spaces are all arranged coaxially. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (central axis) on the same plane.

  A nozzle 32 is fixed inside the body 30 by means such as press fitting. The nozzle 32 is formed of a substantially conical metal (for example, stainless steel) cylindrical member that tapers in the refrigerant flow direction. The swirl space 30 a is disposed above the nozzle 32, and the decompression space 30 b is disposed inside the nozzle 32.

  The refrigerant inflow passage 31e that connects the refrigerant inlet 31a and the swirling space 30a extends in the tangential direction of the inner wall surface of the swirling space 30a when viewed from the central axis direction of the swirling space 30a. Thereby, the refrigerant that has flowed into the swirl space 30a from the refrigerant inflow passage 31e flows along the inner wall surface of the swirl space 30a and swirls around the central axis of the swirl space 30a.

  Here, since centrifugal force acts on the refrigerant swirling in the swirling space 30a, the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side in the swirling space 30a. Therefore, in the present embodiment, during normal operation of the ejector refrigeration cycle 10, the refrigerant pressure on the central axis side in the swirling space 30a is set to the pressure that becomes the saturated liquid phase refrigerant, or the refrigerant boils under reduced pressure (causes cavitation). The dimensions of the swirl space 30a and the like are set so that the pressure is reduced until the pressure is reached.

  Such adjustment of the refrigerant pressure on the central axis side in the swirling space 30a can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the swirling space 30a. Furthermore, the swirl flow velocity can be adjusted by adjusting, for example, dimensions such as an area ratio between the passage sectional area of the refrigerant inflow passage and the vertical sectional area in the axial direction of the swirling space 30a. The swirling flow rate means the flow rate of the refrigerant in the swirling direction in the vicinity of the outermost peripheral portion of the swirling space 30a.

  Therefore, in the present embodiment, the part of the body 30 and the nozzle 32 that forms the swirl space 30a and the swirl space 30a are formed inside the nozzle 32 by causing a swirl flow in the refrigerant that has flowed out of the radiator 12. Swirling flow generating means for flowing into the refrigerant passage (nozzle passage 13a described later). That is, in the present embodiment, the ejector 13 and the swirl flow generating means are integrally configured.

  Further, a suction passage 13b that guides the refrigerant sucked from the refrigerant suction port 31b to the downstream side of the refrigerant flow in the decompression space 30b and the upstream side of the refrigerant flow in the pressurization space 30e is formed inside the body 30. ing.

  A resin passage forming member 35 is disposed inside the decompression space 30b and the pressure increase space 30e. The passage forming member 35 is formed in a substantially conical shape that spreads toward the outer peripheral side as it is separated from the decompression space 30b, and the central axis of the passage formation member 35 is also arranged coaxially with the central axis of the decompression space 30b and the like. ing.

  The shape of the vertical cross section in the axial direction is annular (from the circular shape) between the inner peripheral surface of the part forming the pressure reducing space 30b and the pressure increasing space 30e of the body 30 and the conical side surface of the passage forming member 35. A refrigerant passage having a donut shape excluding a small-diameter circular shape arranged on the same axis is formed.

  Among the refrigerant passages, the refrigerant passage formed between the portion of the nozzle 32 forming the pressure reducing space 30b and the top portion of the conical side surface of the passage forming member 35 is a passage toward the downstream side of the refrigerant flow. It is formed in a shape that reduces the cross-sectional area small. Due to this shape, the refrigerant passage forms a nozzle passage 13a that functions as a nozzle that is isentropically decompressed and ejected.

  More specifically, the nozzle passage 13a of the present embodiment gradually reduces the passage cross-sectional area from the inlet side of the nozzle passage 13a toward the minimum passage area portion, and from the minimum passage area portion to the outlet side of the nozzle passage 13a. It is formed in a shape that gradually increases the cross-sectional area of the passage. That is, in the nozzle passage 13a of the present embodiment, the refrigerant passage cross-sectional area changes in the same manner as a so-called Laval nozzle.

  As a result, in the nozzle passage 13a of the present embodiment, the refrigerant is jetted while being increased in speed so as to have a supersonic speed (a flow speed faster than the two-phase sound speed).

  The refrigerant passage formed between the portion forming the pressure increasing space 30e of the body 30 and the portion on the downstream side of the conical side surface of the passage forming member 35 gradually increases the passage sectional area toward the downstream side of the refrigerant flow. It is formed in the shape to be made. Due to this shape, the refrigerant passage 13c functions as a diffuser portion (pressure increase portion) that mixes the injected refrigerant injected from the nozzle passage 13a and the suctioned refrigerant sucked through the suction passage 13b to increase the pressure. Is forming.

  In addition, an element 37 is disposed inside the body 30 as driving means (driving mechanism) that displaces the passage forming member 35 and changes the passage sectional area of the minimum passage area portion of the nozzle passage 13a. More specifically, the element 37 has a diaphragm 37a that is displaced according to the temperature and pressure of the refrigerant (that is, the refrigerant flowing out of the evaporator 14) flowing through the suction passage 13b.

  The diaphragm 37a is displaced in a direction (vertical lower side) in which the cross-sectional area of the minimum passage area portion of the nozzle passage 13a is enlarged as the temperature (superheat degree) of the refrigerant flowing out of the evaporator 14 increases. 14 As the temperature (degree of superheat) of the refrigerant flowing out decreases, the refrigerant is displaced in a direction (vertical direction upper side) to reduce the passage sectional area of the minimum passage area portion of the nozzle passage 13a. The displacement of the diaphragm 37a is transmitted to the passage forming member 35 through the operating rod 37b.

  The passage forming member 35 receives a load from a coil spring 40 that is an elastic member. The coil spring 40 applies a load that urges the passage forming member 35 toward the side of reducing the passage sectional area of the minimum passage area portion of the nozzle passage 13a.

  For this reason, the passage forming member 35 has an inlet-side load that is received by the pressure of the high-pressure refrigerant (nozzle passage 13a inlet-side refrigerant) on the swirl space 30a side, and a low-pressure refrigerant (diffuser passage 13c outlet-side refrigerant) on the gas-liquid separation space 30f side. Displacement is performed so that the outlet side load received by pressure, the element side load received from the element 37 via the operating rod 37b, and the elastic member side load received from the coil spring 40 are balanced.

  More specifically, the passage forming member 35 is displaced so as to increase the passage sectional area of the minimum passage area portion of the nozzle passage 13a as the temperature (superheat degree) of the refrigerant flowing out of the evaporator 14 increases. On the other hand, as the temperature (degree of superheat) of the refrigerant flowing out of the evaporator 14 decreases, the refrigerant is displaced so as to reduce the passage sectional area of the minimum passage area portion of the nozzle passage 13a.

  In the present embodiment, the passage forming member 35 is displaced in accordance with the superheat degree of the refrigerant flowing out of the evaporator 14 in this way, so that the superheat degree SH of the evaporator 14 outlet side refrigerant approaches the predetermined reference superheat degree KSH. Further, the passage sectional area of the minimum passage area portion of the nozzle passage 13a is adjusted.

  Next, the gas-liquid separation space 30 f is disposed on the lower side of the passage forming member 35. This gas-liquid separation space 30f constitutes a centrifugal-type gas-liquid separation means for rotating the refrigerant flowing out of the diffuser passage 13c around the central axis and separating the gas-liquid of the refrigerant by the action of centrifugal force. That is, in the present embodiment, the gas-liquid separation space 30f is formed inside the body 30, so that the ejector 13 and the gas-liquid separation means are integrally configured.

  Further, the internal volume of the gas-liquid separation space 30f is such that even if a load fluctuation occurs in the cycle and the refrigerant circulation flow rate circulating in the cycle fluctuates, the surplus refrigerant cannot be substantially accumulated. . In addition, an orifice 31i serving as a decompression unit that decompresses the refrigerant flowing into the evaporator 14 is disposed in the liquid phase refrigerant passage that connects the gas-liquid separation space 30f and the liquid phase refrigerant outlet 31c.

  The liquid refrigerant inlet 31c of the ejector 13 is connected to the refrigerant inlet side of the evaporator 14. The evaporator 14 performs heat exchange between the low-pressure refrigerant decompressed by the ejector 13 and the blown air blown into the vehicle interior from the blower fan 14a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a vessel. The blower fan 14 a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device 50.

  The refrigerant suction port 31b of the ejector 13 is connected to the refrigerant outlet of the evaporator 14. Further, the suction side of the compressor 11 is connected to the gas-phase refrigerant outlet 31 d of the ejector 13 via the low-pressure refrigerant hose 16. The basic configuration of the low-pressure refrigerant hose 16 is the same as that of the high-pressure refrigerant hose 15.

  Next, an outline of the electric control unit of the present embodiment will be described. The air conditioning control device 50 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The air conditioning control device 50 performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the various electric actuators 11, 12d, 14a and the like described above.

  The air-conditioning control device 50 includes an internal air temperature sensor that detects the vehicle interior temperature (internal air temperature) Tr, an external air temperature sensor that detects the external air temperature Tam, a solar radiation sensor that detects the solar radiation amount As in the vehicle interior, and an evaporator 14. A sensor group for air conditioning control such as an evaporator temperature sensor for detecting the refrigerant evaporation temperature (evaporator temperature) Te and a discharge refrigerant pressure sensor for detecting the pressure (discharge refrigerant pressure) Pd of the compressor 11 discharge refrigerant is connected. The detection values of these sensor groups are input.

  In the present embodiment, an evaporator temperature sensor that detects the heat exchange fin temperature of the evaporator 14 is used. However, the evaporator temperature sensor detects the temperature of other parts of the evaporator 14. A temperature detection means may be adopted, or a temperature detection means for detecting the temperature of the refrigerant flowing through the evaporator 14 or the refrigerant on the outlet side of the evaporator 14 may be adopted.

  Further, an operation panel (not shown) disposed near the instrument panel in front of the passenger compartment is connected to the input side of the air conditioning control device 50, and operation signals from various operation switches provided on the operation panel are air-conditioned. Input to the control device 50. As various operation switches provided on the operation panel, an air conditioning operation switch that requires that the vehicle air conditioner performs air conditioning in the vehicle interior, a vehicle interior temperature setting switch that sets the vehicle interior temperature Tset, and the like are provided.

  In addition, the air-conditioning control device 50 of the present embodiment is configured such that a control unit that controls the operation of various devices to be controlled connected to the output side is integrally configured. The configuration (hardware and software) for controlling the operation of each control target device constitutes the control means of each control target device.

  For example, in this embodiment, the structure which controls the refrigerant | coolant discharge capability of the compressor 11 by controlling the action | operation of the discharge capacity | capacitance control valve of the compressor 11 comprises the discharge capability control means 50a. Of course, the discharge capacity control means 50a may be configured as a separate control device with respect to the air conditioning control device 50.

  Next, the operation of this embodiment in the above configuration will be described. In the vehicle air conditioner of the present embodiment, when the air conditioning operation switch on the operation panel is turned on (ON), the air conditioning control device 50 executes an air conditioning control program stored in advance.

  In this air conditioning control program, the detection signal of the above-mentioned sensor group for air conditioning control and the operation signal of the operation panel are read. Then, based on the read detection signal and operation signal, a target blowing temperature TAO that is a target temperature of the air blown into the vehicle interior is calculated.

The target blowing temperature TAO is calculated based on the following formula F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × As + C (F1)
Note that Tset is the vehicle interior temperature set by the temperature setting switch, Tr is the internal air temperature detected by the internal air temperature sensor, Tam is the external air temperature detected by the external air temperature sensor, and As is the solar radiation amount detected by the solar radiation sensor. is there. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

  Further, in the air conditioning control program, the operating states of various control target devices connected to the output side of the air conditioning control device 50 are determined based on the calculated target blowing temperature TAO and the detection signal of the sensor group. In other words, a control signal, a control voltage, a control current, a control pulse, etc. that are output to various devices to be controlled are determined.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control current output to the discharge capacity control valve of the compressor 11 is determined as follows. First, the target evaporation temperature TEO of the refrigerant in the evaporator 14 is determined based on the target blowing temperature TAO with reference to a control map stored in advance in the storage circuit of the air conditioning controller 50.

  Then, based on the deviation (TEO-Te) between the refrigerant evaporation temperature Te detected by the evaporator temperature sensor and the target evaporation temperature TEO, the refrigerant evaporation temperature Te approaches the target evaporation temperature TEO using a feedback control method. The control current output to the discharge capacity control valve of the compressor 11 is determined.

  More specifically, in the air conditioning control program of the present embodiment, the discharge capacity control means 50a increases as the temperature difference between the evaporator outlet temperature TEO and the refrigerant evaporation temperature Te increases, that is, the ejector refrigeration cycle 10. As the heat load increases, the discharge capacity (refrigerant discharge capacity) of the compressor 11 is controlled so that the circulating refrigerant flow rate circulating in the cycle increases.

  Moreover, about the ventilation capability of the ventilation fan 14a, ie, the control voltage output to the ventilation fan 14a, it determines with reference to the control map previously memorize | stored in the memory | storage circuit of the air-conditioning control apparatus 50 based on the target blowing temperature TAO. To do.

  More specifically, in this control map, the control voltage is determined so that the blowing capacity of the blower fan 14a becomes substantially maximum when the target blowing temperature TAO is in the extremely low temperature range or the extremely high temperature range. Further, the control voltage is determined so that the blowing capacity of the blowing fan 14a gradually decreases from the substantially maximum value as the target blowing temperature TAO moves from the extremely low temperature range or the extremely high temperature range to the intermediate temperature range.

  And the air-conditioning control apparatus 50 outputs the determined control signal etc. to various control object apparatus. After that, until the operation of the vehicle air conditioner is requested, reading of the detection signal and operation signal described above at every predetermined control cycle → calculation of the target blowing temperature TAO → determination of operating states of various control target devices → control signal The control routine such as output is repeated.

  As a result, in the ejector refrigeration cycle 10, the refrigerant flows as shown by the thick solid arrows in FIG. And the state of a refrigerant | coolant changes as shown to the Mollier diagram of FIG.

  More specifically, the high-temperature and high-pressure refrigerant (point a in FIG. 4) discharged from the compressor 11 flows into the condenser 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat. Condensed. The refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid phase refrigerant separated by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (point a in FIG. 4 → b point).

  The supercooled liquid phase refrigerant that has flowed out of the supercooling section 12c of the radiator 12 is isentropically decompressed and injected in the nozzle passage 13a of the ejector 13 (point b → point c in FIG. 4). At this time, the element 37 of the ejector 13 displaces the passage forming member 35 so that the superheat degree SH of the evaporator 14 outlet side refrigerant (point h in FIG. 4) approaches the predetermined reference superheat degree KSH.

  And the refrigerant | coolant (point h of FIG. 4) which flowed out from the evaporator 14 is attracted | sucked from the refrigerant suction port 31b by the suction effect | action of the injection refrigerant | coolant injected from the nozzle channel | path 13a. The refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the refrigerant suction port 31b flow into the diffuser passage 13c and merge (point c → d, point h ′ → d in FIG. 4).

  Here, the suction passage 13b of the present embodiment is formed in a shape in which the passage cross-sectional area gradually decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage 13b increases the flow velocity while reducing its pressure (point h → point h ′ in FIG. 4). Thereby, the speed difference between the suction refrigerant and the injection refrigerant is reduced, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser passage 13c is reduced.

  In the diffuser passage 13c, the kinetic energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage cross-sectional area. As a result, the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d → point e in FIG. 4). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (point e → f, point e → g in FIG. 4).

  The liquid-phase refrigerant separated in the gas-liquid separation space 30f is decompressed by the orifice 31i of the ejector 13 (point g → point g ′ in FIG. 4) and flows out from the liquid-phase refrigerant outlet 31c. The liquid-phase refrigerant that has flowed out of the liquid-phase refrigerant outlet 31c flows into the evaporator 14, absorbs heat from the blown air blown by the blower fan 14a, and evaporates (point g ′ → point h in FIG. 4). Thereby, blowing air is cooled.

  On the other hand, the gas-phase refrigerant separated in the gas-liquid separation space 30f is sucked into the compressor 11 and compressed again (point f → point a in FIG. 4).

  The ejector refrigeration cycle 10 of the present embodiment operates as described above and can cool the blown air blown into the vehicle interior.

  At this time, in the ejector type refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure has been increased in the diffuser passage 13 c of the ejector 13 is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 can be reduced compared with the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked by the compressor are substantially equal. Coefficient of performance (COP) can be improved.

  Further, according to the ejector 13 of the present embodiment, by turning the refrigerant in the swirling space 30a, the refrigerant pressure on the turning center side in the swirling space 30a is reduced to the pressure that becomes the saturated liquid phase refrigerant, or the refrigerant is depressurized. The pressure can be reduced to boiling (causing cavitation). Thus, a columnar gas-phase refrigerant (air column) is present on the inner peripheral side of the swivel center axis, and the vicinity of the swirl center line in the swirl space 30a is a gas single phase and the surroundings are two phases of a liquid single phase. It can be in a separated state.

  Then, by causing the refrigerant in the two-phase separation state in the swirl space 30a to flow into the nozzle passage 13a, the wall surface boiling that occurs when the refrigerant is separated from the outer peripheral side wall surface of the annular refrigerant passage in the nozzle passage 13a. The boiling of the refrigerant is promoted by interfacial boiling by the boiling nuclei generated by the cavitation of the refrigerant on the central axis side of the annular refrigerant passage.

  Thereby, the refrigerant flowing into the minimum passage area portion of the nozzle passage 13a is in a gas-liquid mixed state in which the gas phase and the liquid phase are uniformly mixed. Then, the flow of refrigerant in the gas-liquid mixed state is choked in the vicinity of the minimum passage area, and the gas-liquid mixed refrigerant that has reached the speed of sound by this choking is accelerated and injected in the divergent portion.

  Thus, the energy conversion efficiency in the nozzle passage 13a can be improved by efficiently accelerating the gas-liquid mixed state refrigerant to a sound speed or higher by boiling promotion by both wall surface boiling and interface boiling. And the improvement of this energy conversion efficiency can aim at the further improvement of COP of the ejector type refrigerating cycle 10 by increasing the pressure | voltage rise amount of the refrigerant | coolant in the diffuser channel | path 13c.

  In addition, since the ejector 13 of the present embodiment can displace the passage forming member 35 by the action of the element 37 that is a drive mechanism, the minimum passage area of the nozzle passage 13a according to the load fluctuation of the ejector refrigeration cycle 10. The cross-sectional area of the passage can be adjusted. Therefore, the ejector 13 can be appropriately operated in accordance with the load fluctuation of the ejector refrigeration cycle 10.

  Here, according to the study by the present inventors, the hydrofluoroolefin-based refrigerant employed in the ejector-type refrigeration cycle 10 of the present embodiment is a refrigerating machine oil having an OH group such as a general PAG oil. It has been found that hydrolytic acid is produced when it is decomposed in a mixed state.

  This is because the hydrofluoroolefin-based refrigerant has a double bond between carbon atoms, and one of the double bonds is broken to cause an addition reaction to bond with the OH group of PAG oil. . Then, when an addition reaction occurs, fluorine ions in the refrigerant are decomposed to generate hydrofluoric acid. Such hydrofluoric acid promotes the deterioration of the resin layer 15c of the high-pressure refrigerant hose 15 (the same applies to the low-pressure refrigerant hose 16) due to oxidation.

  Moreover, the hydrofluoroolefin type refrigerant has a lower saturated water concentration under the same temperature condition and the same pressure condition than the conventionally used hydrofluorocarbon type refrigerant (for example, HFC-134a). For this reason, when a hydrofluoroolefin-based refrigerant is employed, external moisture easily penetrates the rubber layer and the resin layer and enters the refrigeration cycle apparatus. Such intrusion of moisture promotes deterioration of the resin layer 15c due to hydrolysis.

  When the deterioration of the resin layer 15c proceeds, the refrigerant in the ejector refrigeration cycle 10 permeates the rubber layer 15a and leaks to the outside, and the ejector refrigeration cycle 10 cannot exhibit the refrigeration capacity. There is a risk that. Further, according to the study by the present inventors, it has been found that deterioration due to oxidation and hydrolysis due to hydrolysis of the high-pressure refrigerant hose 15 is likely to proceed in a high temperature environment.

  On the other hand, in the ejector refrigeration cycle 10 of the present embodiment, the compressor 11 sucks the refrigerant whose pressure is increased in the diffuser passage 13c of the ejector 13, and the saturated gas separated in the gas-liquid separation space 30f. Phase refrigerant (refrigerant that does not have superheat) can be sucked.

  Therefore, as shown in the Mollier diagram of FIG. 5, in the ejector type refrigeration cycle 10 of the present embodiment indicated by the solid line, the temperature of the refrigerant discharged from the compressor 11 can be lowered as compared with the normal refrigeration cycle apparatus indicated by the broken line. . Thereby, the temperature of the refrigerant | coolant which distribute | circulates the high pressure refrigerant | coolant hose 15 can be lowered | hung rather than a normal refrigerating cycle apparatus, and the progress of degradation by the oxidation of the high pressure refrigerant | coolant hose 15 and degradation by hydrolysis can be suppressed.

  Here, the normal refrigeration cycle apparatus is a general vapor compression refrigeration cycle apparatus in which a compressor, a radiator, a decompression device, and an evaporator are connected in an annular shape. In a normal refrigeration cycle apparatus, the pressure of the suction refrigerant sucked into the compressor is substantially equal to the refrigerant evaporation pressure in the evaporator, and the suction refrigerant has a superheat degree.

  As a result, as in the ejector refrigeration cycle 10 of the present embodiment, even a refrigeration cycle apparatus in which a hydrofluoroolefin-based refrigerant is employed as the refrigerant and an OH group is employed as the refrigerating machine oil. The deterioration of the high-pressure refrigerant hose 15 can be suppressed, and the refrigerant leakage from the high-pressure refrigerant hose 15 can be suppressed.

  Further, the gas-liquid separation means (gas-liquid separation space 30 f) of the present embodiment is formed integrally with the ejector 13 by being formed inside the body 30 of the ejector 13. According to this, since the connection part of the ejector 13 and the gas-liquid separation means can be abolished, the refrigerant leaks through a rubber seal member (for example, an O-ring) disposed in the connection part, It is possible to suppress moisture from entering the cycle.

(Second Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 6, an ejector refrigeration cycle 10 a including a radiator 121 and an ejector 20 and a gas-liquid separator 21 configured as separate components will be described. In FIG. 6, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals.

  More specifically, the refrigerant inlet side of the condensing part 12a of the radiator 121 is connected to the discharge port of the compressor 11 of the present embodiment via the high-pressure refrigerant hose 15. The radiator 121 according to the present embodiment is a receiver-integrated condenser in which a condenser 12a and a liquid receiver (receiver) 12e that stores a liquid-phase refrigerant condensed in the condenser 12a are integrated.

  Moreover, the ejector 20 of this embodiment has the nozzle 20a and the body 20b. In the ejector 20, a Laval nozzle is adopted as the nozzle 20a, which is set so that the flow rate of the injected refrigerant injected from the refrigerant injection port is equal to or higher than the speed of sound during normal operation of the ejector refrigeration cycle 10a. Of course, a tapered nozzle whose refrigerant passage cross-sectional area gradually decreases may be employed as the nozzle 20a.

  A tubular portion 20c extending coaxially with the axial direction of the nozzle 20a is provided on the upstream side of the refrigerant flow of the nozzle 20a. A swirling space 20d that swirls the refrigerant that has flowed into the nozzle 20a is formed inside the cylindrical portion 20c. The swirling space 20d is a substantially cylindrical space extending coaxially with the axial direction of the nozzle 20a.

  Further, the refrigerant inflow passage for allowing the refrigerant to flow into the swirl space 20d from the outside of the ejector 20 extends in the tangential direction of the inner wall surface of the swirl space 20d when viewed from the central axis direction of the swirl space 20d. As a result, the supercooled liquid phase refrigerant that has flowed out of the supercooling portion 12c of the radiator 12 and flowed into the swirling space 20d flows along the inner wall surface of the swirling space 20d as in the first embodiment, and the swirling space 20d. Swivel around the center axis.

  Therefore, in this embodiment, the cylindrical part 20c and the swirl space 20d constitute swirl flow generating means for swirling the supercooled liquid phase refrigerant flowing into the nozzle 20a around the axis of the nozzle 20a. That is, in the present embodiment, the ejector 20 (specifically, the nozzle 20a) and the swirl flow generating means are integrally configured.

  The body 20b is formed of a substantially cylindrical metal (for example, aluminum) or resin, and functions as a fixing member that supports and fixes the nozzle 20a therein and forms an outer shell of the ejector 20. More specifically, the nozzle 20a is fixed by press-fitting so as to be housed inside the longitudinal end of the body 20b. Therefore, the refrigerant does not leak from the fixed portion (press-fit portion) between the nozzle 20a and the body 20b.

  In addition, a refrigerant suction port 20e provided so as to penetrate the inside and outside of the outer peripheral surface of the body 20b and communicate with the refrigerant injection port of the nozzle 20a is formed in a portion corresponding to the outer peripheral side of the nozzle 20a. Yes. The refrigerant suction port 20e is a through hole that sucks the refrigerant that has flowed out of the evaporator 14 from the outside to the inside of the ejector 20 by the suction action of the injection refrigerant injected from the nozzle 20a.

  Further, inside the body 20b, a suction passage for leading the suction refrigerant sucked from the refrigerant suction port 20e to the refrigerant injection port side of the nozzle 20a, and a suction refrigerant and a jet refrigerant flowing into the ejector 20 from the refrigerant suction port 20e. A diffuser portion 20f is formed as a boosting portion that boosts the pressure by mixing the two.

  The diffuser portion 20f is disposed so as to be continuous with the outlet of the suction passage, and is formed by a space that gradually expands the refrigerant passage area. Thereby, while mixing the injected refrigerant and the suction refrigerant, the function of decelerating the flow rate and increasing the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant, that is, the function of converting the velocity energy of the mixed refrigerant into pressure energy Fulfill.

  The refrigerant inlet side of the gas-liquid separator 21 is connected to the refrigerant outlet of the diffuser part 20f. The gas-liquid separator 21 is a gas-liquid separation unit that separates the gas-liquid refrigerant flowing out of the diffuser portion 20 f of the ejector 20. The gas-liquid separator 21 performs the same function as the gas-liquid separation space 30f described in the first embodiment.

  Further, in the present embodiment, a gas / liquid separator 21 having a relatively small internal volume is adopted so that the separated liquid phase refrigerant is almost stored and flows out from the liquid phase refrigerant outlet. Of course, you may employ | adopt what has a function as a liquid storage means to store the excess liquid phase refrigerant | coolant in a cycle.

  The gas-phase refrigerant outlet of the gas-liquid separator 21 is connected to the suction port side of the compressor 11 via a low-pressure refrigerant hose 16. The refrigerant inlet side of the evaporator 14 is connected to the liquid-phase refrigerant outlet of the gas-liquid separator 21 via a fixed throttle 22. The fixed aperture 22 performs the same function as the orifice 31i described in the first embodiment. Specifically, an orifice, a capillary tube, or the like can be adopted as the fixed throttle 22.

  Further, in the ejector refrigeration cycle 10a of the present embodiment, an electric flow rate adjusting valve 23 as a refrigerant flow rate adjusting means is provided in a refrigerant passage from the outlet side of the supercooling portion 12c of the radiator 12 to the inlet side of the ejector 20. Has been placed. The flow rate adjusting valve 23 includes a valve body that can change the refrigerant passage area, and an electric actuator that changes the refrigerant passage area by displacing the valve body.

  The refrigerant passage area of the flow rate adjusting valve 23 is sufficiently larger than the passage sectional area of the refrigerant passage (throttle passage) of the nozzle 20 a of the ejector 20. Therefore, the flow rate adjusting valve 23 of the present embodiment can adjust the flow rate of the refrigerant flowing into the nozzle 20a with almost no refrigerant decompression effect. Further, the operation of the flow rate adjusting valve 23 is controlled by a control signal output from the air conditioning control device 50.

  Moreover, the superheat degree sensor 51 as a superheat degree detection means which detects the superheat degree of the evaporator 14 exit side refrigerant | coolant is connected to the input side of the air conditioning control apparatus 50 of this embodiment as a sensor group for air conditioning control. Yes. More specifically, the superheat degree sensor 51 of this embodiment detects the superheat degree of the refrigerant flowing through the refrigerant passage from the refrigerant outlet of the evaporator 14 to the refrigerant suction port 20e of the ejector 20.

  As superheat degree detection means, instead of the superheat degree sensor 51, an evaporator outlet side temperature sensor for detecting the temperature of the evaporator 14 outlet side refrigerant, and an evaporator outlet side for detecting the pressure of the evaporator 14 outlet side refrigerant. A pressure sensor may be employed. And the air-conditioning control apparatus 50 may calculate a superheat degree based on the detected value of an evaporator exit side temperature sensor and an evaporator exit side pressure sensor.

  Furthermore, the air conditioning control device 50 of the present embodiment controls the operation of the flow rate adjustment valve 23 so that the detection value of the superheat degree sensor 51 (superheat degree SH of the evaporator 14 outlet side refrigerant) approaches the reference superheat degree KSH. . Moreover, in this embodiment, the structure (hardware and software) which controls the action | operation of the flow regulating valve 23 among the air-conditioning control apparatuses 50 comprises the superheat degree control means 50b.

  Other configurations and operations of the ejector refrigeration cycle 10a are the same as those of the ejector refrigeration cycle 10 of the first embodiment. That is, the ejector refrigeration cycle 10a of the present embodiment has a cycle configuration substantially equivalent to that of the ejector refrigeration cycle 10 described in the first embodiment, and operates in the same manner as the first embodiment.

  Further, similarly to the first embodiment, even in a refrigeration cycle apparatus in which a hydrofluoroolefin-based refrigerant is employed as the refrigerant and a refrigerant having an OH group is employed as the refrigerating machine oil, the high-pressure refrigerant hose 15 Deterioration can be suppressed and refrigerant leakage from the high-pressure refrigerant hose 15 can be suppressed.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, the example in which HFO-1234yf is adopted as the hydrofluoroolefin-based refrigerant has been described, but the refrigerant is not limited to this. For example, in addition to HFO-1234yf, HFO-1234ze and HFO-1234zd may be used. Furthermore, it may be a mixed refrigerant obtained by mixing at least two of these refrigerants, or a mixed refrigerant containing at least one of these refrigerants.

  (2) In the above-described embodiment, the deterioration of the low-pressure refrigerant hose 16 is not mentioned, but as described above, the deterioration of the resin layer 15c due to oxidation and the deterioration due to hydrolysis are likely to proceed in a high-temperature environment. Therefore, it is extremely effective to suppress the deterioration of the high-pressure refrigerant hose 15 through which the high-temperature refrigerant flows as in the above-described embodiment.

  On the other hand, the low-pressure refrigerant hose 16 is less prone to deterioration than the high-pressure refrigerant hose because the low-temperature and low-pressure refrigerant flows. Therefore, when the problem of deterioration due to oxidation and hydrolysis of the low-pressure refrigerant hose 16 does not occur, the base cloth 15b may be abolished from the rubber layer 15a of the low-pressure refrigerant hose 16, or the resin layer 15c is abolished. May be. Thereby, the manufacturing cost of the ejector-type refrigeration cycle 10, 10a can be reduced.

  (3) Each component apparatus which comprises the ejector-type refrigerating cycle 10 and 10a is not limited to what was disclosed by the above-mentioned embodiment.

  For example, in the above-described embodiment, an example in which an engine-driven compressor is employed as the compressor 11 has been described. However, the compressor 11 includes a fixed displacement compression mechanism and an electric motor, and is supplied with electric power. You may employ | adopt the electric compressor which act | operates by. In the electric compressor, the refrigerant discharge capacity can be controlled by adjusting the rotation speed of the electric motor.

  In the above-described second embodiment, the example in which the ejector 20 has a fixed nozzle that does not change the passage cross-sectional area of the minimum passage area portion has been described. However, as the ejector 20, the passage breakage of the minimum passage area portion is described. You may employ | adopt what has the variable nozzle comprised so that an area could be changed.

  As such a variable nozzle, a needle-shaped or conical valve body that tapers from the diffuser portion side toward the nozzle side is disposed in a refrigerant passage (nozzle passage) in the nozzle, and this valve body is an electric actuator. What is necessary is just to set it as the structure which adjusts a channel | path cross-sectional area by displacing by etc.

  (4) In the above-described embodiment, the example in which the ejector refrigeration cycle 10, 10a according to the present invention is applied to a vehicle air conditioner has been described. However, the application of the ejector refrigeration cycle 10, 10a is not limited thereto. For example, the present invention may be applied to a stationary air conditioner, a cold storage container, a cooling / heating device for a vending machine, and the like.

  In the above-described embodiment, the radiator 12 of the ejector refrigeration cycle 10, 10a is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 14 is a use-side heat exchanger that cools the blown air. Yes. On the other hand, the evaporator 14 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.

DESCRIPTION OF SYMBOLS 11 Compressor 12, 121 Radiator 13, 20 Ejector 32, 20a Nozzle 30, 20b Body 31b, 20e Refrigerant suction port 13c, 20e Diffuser channel | path, Diffuser part (pressure | voltage rise part)
30f, 21 Gas-liquid separation space, gas-liquid separator (gas-liquid separation means)
14 Evaporator 15 High-pressure refrigerant hose

Claims (3)

A compressor (11) that compresses and discharges refrigerant mixed with refrigerating machine oil;
Radiators (12, 121) for radiating high-pressure refrigerant discharged from the compressor (11);
Refrigerant suction for sucking the refrigerant by the suction action of the nozzle (32, 20a) for depressurizing the refrigerant flowing out from the radiator (12, 121) and the high-speed jet refrigerant jetted from the nozzle (32, 20a) Body (30, 20b) formed with a pressure increasing part (13c, 20e) for mixing and increasing the pressure of the suction refrigerant sucked from the port (31b, 20e) and the jet refrigerant and the refrigerant suction port (31b, 20e) An ejector (13, 20) having:
Gas-liquid separation means (30f, 21) for separating the gas-liquid refrigerant flowing out from the pressure-increasing section (13c, 20e) and flowing out the separated gas-phase refrigerant to the suction port side of the compressor (11); ,
An evaporator (14) for evaporating the liquid-phase refrigerant separated by the gas-liquid separation means (30f, 21) and flowing it out to the refrigerant suction port (31b, 20e) side;
A high-pressure refrigerant hose (15) connecting the discharge port of the compressor (11) and the refrigerant inlet of the radiator (12, 121),
The high-pressure refrigerant hose (15) is formed in a multilayer structure,
A part of the high-pressure refrigerant hose (15) is formed of rubber, and another part of the layer is formed of a resin that suppresses permeation of the refrigerant;
As the refrigerant, a hydrofluoroolefin-based refrigerant is employed,
As the refrigerating machine oil, one having an OH group is employed.   The refrigeration cycle apparatus according to claim 1, wherein a refrigerant having a saturated water concentration lower than that of HFC-134a is employed as the refrigerant.   The gas-liquid separation means is formed integrally with the ejector (13, 20) by being formed inside the body (30, 20b). The refrigeration cycle apparatus described.

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