WO2018016219A1 - Cycle de réfrigération de type-éjecteur - Google Patents

Cycle de réfrigération de type-éjecteur Download PDF

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Publication number
WO2018016219A1
WO2018016219A1 PCT/JP2017/021414 JP2017021414W WO2018016219A1 WO 2018016219 A1 WO2018016219 A1 WO 2018016219A1 JP 2017021414 W JP2017021414 W JP 2017021414W WO 2018016219 A1 WO2018016219 A1 WO 2018016219A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
passage
valve body
refrigerant passage
Prior art date
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PCT/JP2017/021414
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English (en)
Japanese (ja)
Inventor
龍 福島
照之 堀田
池上　真
Original Assignee
株式会社デンソー
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Publication of WO2018016219A1 publication Critical patent/WO2018016219A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits

Definitions

  • the present disclosure relates to an ejector refrigeration cycle including an ejector.
  • an ejector-type refrigeration cycle which is a vapor compression refrigeration cycle apparatus including an ejector
  • This type of ejector sucks the refrigerant flowing out of the evaporator from the refrigerant suction port and sucks the injected refrigerant and the sucked refrigerant in the ejector refrigeration cycle by the suction action of the high-speed jet refrigerant jetted from the nozzle section.
  • a suction pressurizing action (so-called pump action) in which the pressure is increased by mixing in the section is exhibited.
  • the refrigerant whose pressure has been increased by the pump action of the ejector is caused to flow out to the suction port side of the compressor.
  • the pressure of the suction refrigerant can be increased as compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the suction refrigerant sucked into the compressor are substantially equal. Therefore, in the ejector refrigeration cycle, the power consumption of the compressor can be reduced as compared with a normal refrigeration cycle apparatus, and the coefficient of performance (COP) of the cycle can be improved.
  • the pumping action of the ejector described above is caused by the suction action and speed energy of the injected refrigerant injected from the nozzle part, so that the flow rate of the injected refrigerant decreases during low load operation where the flow rate of refrigerant circulating in the cycle decreases.
  • the pumping action is also reduced. If the pumping action is reduced, the refrigerant cannot flow into the evaporator, and the ejector refrigeration cycle may not be able to exhibit the refrigeration capacity.
  • Patent Document 1 discloses an ejector refrigeration cycle configured to be able to switch between a refrigerant circuit during normal operation and a refrigerant circuit during low-load operation.
  • the ejector-type refrigeration cycle of Patent Document 1 includes a bypass passage that allows the high-pressure refrigerant flowing out of the radiator to flow around the nozzle portion of the ejector.
  • the refrigerant circuit is switched to a refrigerant circuit that causes high pressure refrigerant to flow into the nozzle portion of the ejector and cause the ejector to exert a pumping action.
  • the high-pressure refrigerant is caused to flow into the bypass passage and switched to a similar refrigerant circuit of a normal refrigerant cycle device.
  • Patent Document 1 the ejector refrigeration cycle of Patent Document 1 employs a three-way valve as a refrigerant circuit switching device for switching the refrigerant circuit.
  • Patent Document 1 does not describe a specific configuration of the three-way valve.
  • a detection device for determining the operation condition of the electric three-way valve and a control device for controlling the operation of the electric three-way valve are provided. Necessary. For this reason, it becomes easy to invite the enlargement as the whole ejector type refrigerating cycle, and the complexity of a control mode. Therefore, it is desirable that a refrigerant circuit switching device that automatically operates according to a load change by a mechanical mechanism is employed.
  • a refrigerant circuit switching device of a mechanical mechanism for example, when a differential pressure valve that opens and closes a bypass passage according to a pressure difference between a high-pressure side refrigerant and a low-pressure side refrigerant in a cycle, the differential pressure valve is bypassed during low load operation. Even if the passage is opened, the inlet side of the nozzle part of the ejector cannot be closed. As a result, the high-pressure refrigerant flows into both the bypass passage and the nozzle portion of the ejector, and the refrigerant circuit cannot be switched reliably.
  • an object of the present disclosure is to provide an ejector-type refrigeration cycle in which a refrigerant circuit can be switched mechanically and reliably according to a load change.
  • an ejector refrigeration cycle includes a compressor that compresses and discharges a refrigerant, a radiator that dissipates heat from the refrigerant discharged from the compressor, and an outflow from the radiator.
  • An ejector having a boosting unit that sucks the refrigerant from the refrigerant suction port by the suction action of the jetted refrigerant jetted from the nozzle unit that depressurizes the refrigerant, and mixes the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port to boost the pressure;
  • An evaporator that evaporates the refrigerant and flows out to the refrigerant suction port side, a bypass path that bypasses the nozzle section and guides the refrigerant radiated by the radiator to the upstream side from the refrigerant outlet of the evaporator, and a bypass path
  • a decompression section for decompressing the refrigerant flowing into the evaporator, and opening and closing the first refrigerant passage for guiding the refrigerant radiated by the radiator to the nozzle section side, and bypassing the refrigerant radiated by the radiator
  • the circuit switching valve is configured by a mechanical mechanism that closes the other when either one of the first refrigerant passage and the second refrigerant passage is opened. Further, when the differential pressure before and after subtracting the refrigerant pressure on the suction port side from the refrigerant pressure on the discharge port side of the compressor is lower than a predetermined reference front and rear differential pressure, the circuit switching valve Open the passage.
  • the circuit switching valve a mechanical mechanism that closes one of the first refrigerant passage and the second refrigerant passage when the other one is opened is adopted, and the front-rear differential pressure is the reference front-rear differential pressure. When it is lower than that, the one that opens the second refrigerant passage is adopted.
  • the circuit switching valve sets the reference front-rear differential pressure so as to open the first refrigerant passage side, so that the refrigerant radiated by the radiator flows into the ejector nozzle section.
  • the refrigerant circuit can be switched to.
  • annular cycle a normal refrigeration cycle in which the second refrigerant passage side opens and the refrigerant radiated by the radiator flows into the evaporator through the bypass passage. Therefore, it is easy to return the refrigeration oil remaining in the evaporator to the compressor at the start of the cycle.
  • the pressure difference obtained by subtracting the low-pressure side pressure of the refrigerant on the downstream side of the decompression section from the high-pressure side pressure of the refrigerant on the upstream side of the circuit switching valve as the circuit switching valve is a predetermined reference pressure.
  • the difference is greater than or equal to the difference, the first refrigerant passage is opened and the second refrigerant passage is closed. Further, when the pressure difference is lower than the reference pressure difference, the first refrigerant passage is closed and the first refrigerant passage is closed. You may employ
  • the first refrigerant passage is opened when the high pressure side pressure of the refrigerant upstream of the circuit switching valve is equal to or higher than a predetermined reference high pressure side pressure as the circuit switching valve.
  • the second refrigerant passage may be closed, and when the high-pressure side pressure is lower than the reference high-pressure side pressure, the first refrigerant passage may be closed and the second refrigerant passage may be opened.
  • the front-rear differential pressure when the high-pressure side pressure is the reference high-pressure side pressure may be set to the reference front-rear differential pressure.
  • refrigerant dissipated by a radiator means a refrigerant dissipated by at least a part of the radiator.
  • leading to the upstream side of the refrigerant outlet of the evaporator includes guiding to the upstream side of the refrigerant inlet of the evaporator. Furthermore, if it is upstream from the refrigerant outlet of the evaporator, it also includes guiding to the downstream side of the refrigerant outlet of the evaporator (for example, in the refrigerant passage of the evaporator).
  • the first embodiment will be described with reference to FIGS.
  • the ejector refrigeration cycle 10 of this embodiment shown in the overall configuration diagram of FIG. 1 is applied to a vehicle air conditioner, and has a function of cooling blown air that is blown into a vehicle interior (indoor space) that is an air-conditioning target space. Fulfill. Therefore, the fluid to be cooled in the ejector refrigeration cycle 10 is blown air.
  • the refrigerant circuit can be switched according to the air conditioning heat load. More specifically, during normal operation, the circuit is switched to a refrigerant circuit through which refrigerant flows as shown by the black arrows in FIG. 1, and during low load operation where the thermal load of the ejector refrigeration cycle 10 is lower than during normal operation. 1 can be switched to a refrigerant circuit through which the refrigerant flows, as indicated by the white arrows in FIG.
  • the ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as a refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure.
  • This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
  • the compressor 11 sucks the refrigerant and discharges it until it becomes a high-pressure refrigerant.
  • the compressor 11 is disposed in an engine room together with an engine (internal combustion engine) that outputs a driving force for vehicle travel.
  • the compressor 11 is an engine-driven compressor that is driven by a rotational driving force output from the engine via a pulley, a belt, and the like.
  • the compressor 11 is a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity.
  • 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 a control device described later.
  • the refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port of the compressor 11.
  • 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 the outside air (outside air) blown from the cooling fan 12d. .
  • the radiator 12 is arranged on the vehicle front side in the engine room.
  • the condensing unit 12a is a heat exchange unit for condensation that 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.
  • the receiver unit 12b is a refrigerant container that separates the gas-liquid refrigerant flowing out from the condensing unit 12a and stores excess liquid-phase refrigerant.
  • the supercooling unit 12c is a heat exchange unit for supercooling that heat-exchanges the liquid refrigerant flowing out from the receiver unit 12b and the outside air blown from the cooling fan 12d to supercool the liquid refrigerant.
  • the cooling fan 12d is an electric blower whose rotation speed (amount of blown air) is controlled by a control voltage output from the control device.
  • FIG. 2 is a schematic cross-sectional view showing a state in which the circuit switching valve 13 is switched to a refrigerant circuit that causes the refrigerant flowing out of the radiator 12 to flow into the nozzle portion 15a side of the ejector 15.
  • FIG. 3 is a schematic cross-sectional view showing a state where the circuit switching valve 13 is switched to a refrigerant circuit that allows the refrigerant flowing out of the radiator 12 to flow into the bypass passage 20 side.
  • FIG. 4 is a schematic view showing a state where the circuit switching valve 13 instantaneously opens both the refrigerant passage on the nozzle portion 15a side and the refrigerant passage on the bypass passage 20 side when the circuit switching valve 13 switches the refrigerant circuit.
  • FIG. 4 is a schematic view showing a state where the circuit switching valve 13 instantaneously opens both the refrigerant passage on the nozzle portion 15a side and the refrigerant passage on the bypass passage 20 side when the circuit switching valve 13 switches the refrigerant circuit.
  • the circuit switching valve 13 includes a valve body 31, a valve body 32, a coil spring 33, and the like. As shown in FIGS. 2 to 4, the valve body 31 is formed in a prismatic shape or a cylindrical shape by combining a plurality of structural members made of metal or resin. The valve body 31 forms an outer shell of the circuit switching valve 13 and houses a valve body 32, a coil spring 33, and the like therein.
  • the valve body 31 has a high-pressure refrigerant inlet 31a, a first refrigerant outlet 31b, and a second refrigerant outlet 31c.
  • a plurality of refrigerant passages such as an inflow passage 30a, a first refrigerant passage 30b, and a second refrigerant passage 30c are formed inside the valve body 31.
  • the high-pressure refrigerant inlet 31a is a refrigerant inlet through which the refrigerant that has flowed out of the radiator 12 flows into the inflow passage 30a.
  • the first refrigerant outlet 31b is a refrigerant outlet through which refrigerant flowing through the first refrigerant passage 30b flows out to the nozzle portion 15a side of the ejector 15 (more specifically, to the refrigerant inlet side of the expansion valve 14 described later).
  • the second refrigerant outlet 31c is a refrigerant outlet through which the refrigerant flowing through the second refrigerant passage 30c flows out to the bypass passage 20 side.
  • the first refrigerant passage 30b is a refrigerant passage that communicates with the inflow passage 30a and guides the refrigerant flowing out of the radiator 12 to the nozzle portion 15a side of the ejector 15.
  • the second refrigerant passage 30c is a refrigerant passage that communicates with the inflow passage 30a and guides the refrigerant flowing out of the radiator 12 to the bypass passage 20 side.
  • the valve body 32 includes a spherical ball valve 32a that opens and closes the inlet of the first refrigerant passage 30b, and a disk-like plate valve 32b that opens and closes the inlet of the second refrigerant passage 30c.
  • a rubber seal member 32c is disposed in a portion of the plate-like valve 32b that contacts the inlet of the second refrigerant passage 30c.
  • the ball valve 32a and the plate valve 32b are connected by a connecting rod extending in the displacement direction of the valve body 32.
  • the plate valve 32b is displaced toward the side that opens the second refrigerant passage 30c.
  • the plate-like valve 32b is displaced toward the side closing the second refrigerant passage 30c.
  • valve body 32 is connected to a pressure receiving portion 34 disposed in a columnar space of the second refrigerant passage 30c on the downstream side of the refrigerant flow with respect to the plate-like valve 32b.
  • the pressure receiving part 34 is formed of a metal columnar member.
  • the inner diameter of the second refrigerant passage 30c and the outer diameter of the pressure receiving portion 34 are in a dimensional relationship with a clearance fit. For this reason, the pressure receiving part 34 is disposed in the second refrigerant passage 30c so as to be slidable in the central axis direction.
  • an O-ring as a seal member is disposed in the gap between the inner peripheral surface of the second refrigerant passage 30c and the outer peripheral surface of the pressure receiving portion 34, and the refrigerant does not leak from these gaps.
  • the pressure receiving portion 34 is formed with an orifice hole 34a extending in the central axis direction and communicating the inlet side of the second refrigerant passage 30c and the outlet side of the second refrigerant passage 30c.
  • the orifice hole 34a is formed with a sufficiently thin diameter with respect to the second refrigerant passage 30c.
  • the refrigerant flowing through the second refrigerant passage 30c and flowing out from the second refrigerant outlet 31c is decompressed when passing through the orifice hole 34a. Further, a differential pressure between the inlet side pressure Pri of the inlet side refrigerant in the orifice hole 34a and the outlet side pressure Pro of the outlet side refrigerant in the orifice hole 34a acts on the pressure receiving portion 34.
  • the orifice hole 34a is a pressure reducing unit that depressurizes the refrigerant flowing into the evaporator 19 to be described later via the bypass passage 20.
  • the pressure reducing part is formed in the circuit switching valve 13
  • the pressure reducing part and the circuit switching valve are integrally formed.
  • the coil spring 33 is an elastic member that applies a load to the valve body portion 32 while the ball valve 32a closes the first refrigerant passage 30b and the plate-like valve 32b opens the second refrigerant passage 30c.
  • the load of the coil spring 33 of this embodiment is set as follows. First, in the following description, a value obtained by subtracting the low pressure side pressure PL of the refrigerant downstream of the orifice hole 34a from the high pressure side pressure PH of the refrigerant upstream of the circuit switching valve 13 is defined as a pressure difference ⁇ P.
  • the load of the coil spring 33 of the present embodiment opens the first refrigerant passage 30b and closes the second refrigerant passage 30c. Is set to On the other hand, when the pressure difference ⁇ P is lower than the reference pressure difference K ⁇ P, the first refrigerant passage 30b is closed and the second refrigerant passage 30c is opened.
  • the low-pressure side pressure PL is the pressure of the refrigerant on the downstream side of the orifice hole 34a, the pressure of the refrigerant on the inlet side of the evaporator 19, the pressure of the refrigerant on the outlet side of the evaporator 19 described later, or the compressor 11
  • the pressure of the suction refrigerant can be adopted.
  • the pressure of the evaporator 19 outlet side refrigerant is adopted as the low pressure side pressure PL.
  • the outlet side pressure Pro of the outlet side refrigerant of the orifice hole 34a may be adopted as the low pressure side pressure PL.
  • the front-rear differential pressure ⁇ Pc obtained by subtracting the refrigerant pressure on the suction side from the refrigerant pressure on the discharge port side of the compressor 11 when the pressure difference ⁇ P is the reference pressure difference K ⁇ P is obtained.
  • the pressure is defined as K ⁇ Pc. Therefore, when the front-rear differential pressure ⁇ Pc is lower than the reference front-rear differential pressure K ⁇ Pc, the load of the coil spring 33 according to the present embodiment closes the first refrigerant passage 30b and the second refrigerant. It is set to open the passage 30c.
  • the circuit switching valve 13 of the present embodiment is a mechanical mechanism that selectively opens one of the first refrigerant passage 30b and the second refrigerant passage 30c (that is, closes the other when one of them is opened). It consists of
  • the set load and various specifications of the coil spring 33 are determined so as to satisfy the following formulas F1 to F3.
  • A1 is the difference between the high pressure side pressure PH and the inlet side pressure Pri of the valve body portion 32 when the valve body portion 32 closes the second refrigerant passage 30c. This is the first pressure receiving area A1 where pressure acts.
  • a ⁇ b> 2 is a second pressure receiving area A ⁇ b> 2 in which a differential pressure between the inlet side pressure Pri and the outlet side pressure Pro of the pressure receiving unit 34 acts.
  • Fsp1 is a first set load Fsp1 that the coil spring 33 acts on the valve body portion 32 when the pressure difference ⁇ P becomes the reference pressure difference K ⁇ P.
  • FIG. 2 to FIG. 4 a portion corresponding to the diameter of the first pressure receiving area A1 having a circular shape is denoted by A1. The same applies to the second pressure receiving area A2 and the third pressure receiving area.
  • the relationship of the above formula F1 is realized by the difference between the inner diameter and the outer diameter of the cylindrical seat portion 31d with which the seal member 32c of the plate valve 32b abuts.
  • the set load and various specifications of the coil spring 33 are determined so as to satisfy the relationships of the following formulas F4 to F6.
  • A3 indicates that when the valve body 32 closes the first refrigerant passage 30b, the high pressure side pressure PH and the first refrigerant passage 30b side ( That is, it is the third pressure receiving area A3 on which the differential pressure with the nozzle side pressure Pnoz on the inlet side of the nozzle portion 15a acts.
  • Fsp2 is a second set load Fsp2 that the coil spring 33 acts on the valve body portion 32 when the valve body portion 32 closes the first refrigerant passage 30b.
  • valve body 31 is provided with a receiving member 33a for supporting the coil spring 33.
  • the receiving member 33a is fixed to the valve body 31 with screws. Therefore, the load of the coil spring 33 can be adjusted by displacing the receiving member 33a.
  • the refrigerant inlet side of the expansion valve 14 is connected to the first refrigerant outlet 31b of the circuit switching valve 13.
  • the expansion valve 14 is a so-called external pressure equalizing box type temperature expansion valve.
  • the expansion valve 14 is a flow rate adjusting device that depressurizes the high-pressure liquid-phase refrigerant that has flowed out of the supercooling portion 12c of the radiator 12 until it becomes an intermediate-pressure refrigerant and adjusts the circulating refrigerant flow rate that circulates in the cycle. Further, the expansion valve 14 of the present embodiment adjusts the circulating refrigerant flow rate so that the superheat degree SH of the evaporator 19 outlet side refrigerant approaches a predetermined reference superheat degree KSH.
  • Such an expansion valve 14 includes a temperature sensing part having a displacement member (diaphragm) that is displaced according to the temperature and pressure of the refrigerant that has flowed out of the evaporator 19, and the outlet of the evaporator 19 according to the displacement of the displacement member. It is possible to employ one in which the valve opening degree (refrigerant flow rate) is adjusted by a mechanical mechanism so that the superheat degree of the side refrigerant approaches the reference superheat degree.
  • the inlet side of the nozzle portion 15 a of the ejector 15 is connected to the refrigerant outlet of the expansion valve 14.
  • the ejector 15 functions as a decompression device that decompresses the refrigerant flowing out of the expansion valve 14 (that is, the refrigerant flowing out of the radiator 12) during normal operation.
  • the ejector 15 injects the refrigerant that has flowed out of the expansion valve 14 by reducing the pressure at the nozzle portion 15a, and the refrigerant that has flowed out of the evaporator 19 by the suction action of the injected refrigerant that is injected at a high speed (that is, the evaporator 19). It functions as a refrigerant transport device that sucks and transports (exit-side refrigerant).
  • the ejector 15 has a nozzle portion 15a and a body portion 15b.
  • the nozzle portion 15a is formed of a substantially cylindrical member made of metal (stainless steel in the present embodiment) that gradually tapers in the direction of refrigerant flow.
  • the nozzle portion 15a decompresses the refrigerant in an isentropic manner in the refrigerant passage formed inside.
  • a throat portion (minimum passage area portion) having the smallest passage cross-sectional area is formed, and further, from the throat portion toward the refrigerant injection port for injecting the refrigerant.
  • a divergent portion in which the refrigerant passage area is enlarged is formed. That is, the nozzle portion 15a is configured as a Laval nozzle.
  • the nozzle unit 15a is set such that the flow rate of the injected refrigerant injected from the refrigerant injection port is equal to or higher than the sonic speed during normal operation of the ejector refrigeration cycle 10.
  • the body portion 15b is formed of a cylindrical member made of metal (in this embodiment, made of an aluminum alloy), and functions as a fixing member that supports and fixes the nozzle portion 15a therein, and forms an outer shell of the ejector 15. To do.
  • the nozzle portion 15a is fixed by press-fitting so as to be accommodated inside the longitudinal end of the body portion 15b. For this reason, a refrigerant
  • a refrigerant suction port 15c provided so as to penetrate the inside and outside of the outer peripheral surface of the body portion 15b and communicate with the refrigerant injection port of the nozzle portion 15a is provided in a portion corresponding to the outer peripheral side of the nozzle portion 15a. Is formed.
  • the refrigerant suction port 15c is a through hole that sucks the refrigerant that has flowed out of the evaporator 19 into the ejector 15 by the suction action of the injection refrigerant that is injected from the nozzle portion 15a.
  • a suction passage that guides the suction refrigerant sucked from the refrigerant suction port 15c to the refrigerant injection port side of the nozzle portion 15a, and a suction refrigerant that flows into the ejector 15 through the suction passage.
  • a diffuser portion 15d which is a pressure increasing portion that increases the pressure by mixing the injected refrigerant, is formed.
  • the diffuser portion 15d is disposed so as to be continuous with the outlet of the suction passage, and is formed so that the refrigerant passage area gradually increases.
  • the inlet side of the accumulator 16 is connected to the refrigerant outlet of the diffuser part 15d.
  • the accumulator 16 is a gas-liquid separation unit that separates the gas-liquid refrigerant flowing out of the diffuser unit 15d.
  • the accumulator 16 is provided with a gas phase refrigerant outlet through which the separated gas phase refrigerant flows out and a liquid phase refrigerant outlet through which the separated liquid phase refrigerant flows out.
  • One refrigerant inlet of the three-way joint 18 is connected to the liquid phase refrigerant outlet of the accumulator 16 via a check valve 17.
  • the check valve 17 only allows the refrigerant flowing out from the liquid-phase refrigerant outlet of the accumulator 16 to flow to the three-way joint 18 side.
  • the three-way joint 18 is a pipe joint having three refrigerant outlets.
  • two of the three refrigerant inlets / outlets are used as refrigerant inlets, and the remaining one is used as a refrigerant outlet.
  • the refrigerant inlet of the evaporator 19 is connected to the refrigerant outlet of the three-way joint 18. Therefore, the check valve 17 is a suppression mechanism that suppresses the refrigerant from flowing from the inlet side of the evaporator 19 to the liquid phase refrigerant outlet side of the accumulator 16.
  • the evaporator 19 performs heat exchange between the low-pressure refrigerant decompressed by the ejector 15 and the blown air blown into the vehicle compartment from the blower fan 19a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a vessel.
  • the blower fan 19a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.
  • the refrigerant suction port 15 c side of the ejector 15 is connected to the outlet side of the evaporator 19. Further, the suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 16.
  • bypass passage 20 guides the refrigerant radiated by the radiator 12 to the side of the three-way joint 18 disposed on the upstream side of the refrigerant flow from the refrigerant outlet of the evaporator 19 by bypassing the nozzle portion 15a of the ejector 15. It is a refrigerant passage.
  • a control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and its peripheral circuits. This control device performs various calculations and processes based on a control program stored in the ROM. The control device controls the operation of the various electric compressors 11 and the cooling fan 12d described above.
  • the control device is connected to a plurality of air conditioning control sensor groups such as an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, an evaporator temperature sensor, an outlet side temperature sensor, and an outlet side pressure sensor.
  • the detected value is input.
  • the inside air temperature sensor is an inside air temperature detecting device that detects the vehicle interior temperature.
  • the outside air temperature sensor is an outside air temperature detecting device that detects outside air temperature.
  • a solar radiation sensor is a solar radiation amount detection apparatus which detects the solar radiation amount in a vehicle interior.
  • the evaporator temperature sensor is an evaporator temperature detection device that detects the blown air temperature (evaporator temperature) of the evaporator 19.
  • the outlet side temperature sensor is an outlet side temperature detecting device that detects the temperature of the radiator 12 outlet side refrigerant.
  • the outlet-side pressure sensor is an outlet-side pressure detection device that detects the pressure of the radiator 12 outlet-side refrigerant.
  • an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device.
  • various operation switches provided on the operation panel there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.
  • control device of the present embodiment is configured such that a control unit that controls the operation of various control target devices connected to the output side is integrally configured.
  • the configuration (hardware and software) for controlling the operation of the system constitutes a control unit of each control target device.
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 by controlling the operation of the discharge capacity control valve of the compressor 11 constitutes the discharge capacity control unit.
  • the discharge capacity control unit may be configured as a separate control device with respect to the control device.
  • the operation of the ejector refrigeration cycle 10 of the present embodiment having the above configuration will be described.
  • the refrigerant circuit during normal operation and the refrigerant circuit during low-load operation can be switched.
  • the refrigerant circuit is switched to the refrigerant circuit during normal operation, and the pressure difference ⁇ P Is switched to the refrigerant circuit at the time of low load operation when the pressure difference is equal to or less than the reference pressure difference K ⁇ P.
  • the control device executes an air conditioning control program stored in advance, and the electric motor and cooling fan of the compressor 11 12d and the operation of the blower fan 19a are controlled.
  • the refrigerant in the ejector refrigeration cycle 10 is often pressure-equalized, except when the vehicle is restarted in a short time after stopping.
  • the front-rear differential pressure ⁇ Pc is lower than the reference front-rear differential pressure K ⁇ Pc. Therefore, in the circuit switching valve 13, as shown in FIG. 3, the first refrigerant passage 30b is closed and the second refrigerant passage 30c is opened.
  • the refrigerant pressure in the cycle has a relationship shown in the following formulas F7 to F10.
  • PH Pri (F7) Pri> Pro (F8) Pro ⁇ PL (F9) Pro ⁇ Pnoz (F10)
  • the load on the side that opens the first refrigerant passage 30b due to the pressure difference ⁇ P that is, (A2-A3) ⁇ ⁇ P
  • the state where the second refrigerant passage 30c is opened is maintained until it becomes larger than the set load Fsp2.
  • the pressure of the refrigerant on the outlet side of the radiator 12 (that is, the refrigerant pressure at the high pressure refrigerant inlet 31a of the circuit switching valve 13) is adopted as the high pressure side pressure PH. Further, the pressure of the refrigerant on the inlet side of the expansion valve 14 (that is, the refrigerant pressure at the first refrigerant outlet 31b of the circuit switching valve 13) is employed as the nozzle side pressure Pnoz.
  • valve body portion When the pressure difference ⁇ P between the high-pressure side pressure PH and the low-pressure side pressure PL is expanded by the suction compression action of the compressor 11 during normal operation and reaches the reference pressure difference K ⁇ P, the valve body portion is shown in FIG.
  • the 32 ball valves 32a open the first refrigerant passage 30b, and the plate-like valve 32b is displaced to close the second refrigerant passage 30c. That is, both the first refrigerant passage 30b and the second refrigerant passage 30c are opened.
  • the pressure in the cycle changes to a relationship represented by mathematical formulas F11 and F12 below.
  • PH ⁇ Pri (F12) the first refrigerant passage 30b is caused by the pressure difference ⁇ P. Is larger than the second set load Fsp2 on the side where the first refrigerant passage 30b is closed instantaneously.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the condenser 12 a of the radiator 12.
  • the refrigerant flowing into the condensing part 12a exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat to condense.
  • the refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b.
  • the liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d by the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 5). Point ⁇ b).
  • the valve body 32 opens the first refrigerant passage 30b and closes the second refrigerant passage 30c, so that the refrigerant flowing into the inflow passage 30a flows from the first refrigerant outlet 31b. It flows out and flows into the expansion valve 14.
  • the refrigerant that has flowed into the expansion valve 14 is decompressed in an enthalpy manner until it becomes an intermediate pressure refrigerant (point b ⁇ point b1 in FIG. 5).
  • the opening degree of the expansion valve 14 is adjusted such that the superheat degree SH of the evaporator 19 outlet side refrigerant (point h in FIG. 5) approaches the reference superheat degree KSH.
  • the intermediate pressure refrigerant that has flowed out of the expansion valve 14 flows into the nozzle portion 15 a of the ejector 15.
  • the refrigerant flowing into the nozzle portion 15a is isentropically depressurized and injected (point b1 ⁇ c in FIG. 5).
  • the refrigerant on the outlet side of the evaporator 19 is sucked from the refrigerant suction port 15 c of the ejector 15 by the suction action of the jet refrigerant.
  • the refrigerant injected from the nozzle portion 15a and the suction refrigerant sucked from the refrigerant suction port 15c flow into the diffuser portion 15d (point c ⁇ d, point h1 ⁇ d in FIG. 5).
  • the suction passage of the present embodiment is formed in a shape in which the passage cross-sectional area decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage increases the flow velocity while decreasing the pressure (point h ⁇ point h1 in FIG. 5). 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 portion 15d is reduced.
  • the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area.
  • the pressure of the mixed refrigerant of the injected refrigerant and the suction refrigerant increases (point d ⁇ point e in FIG. 5).
  • the refrigerant that has flowed out of the diffuser portion 15d flows into the accumulator 16 and is separated into gas and liquid.
  • a pressure loss occurs (point g ⁇ point g1 in FIG. 5).
  • the ejector refrigeration cycle 10 during normal operation operates as described above, and can cool the blown air blown into the passenger compartment.
  • 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.
  • the suction pressure increase action (so-called pump action) of the ejector 15 during normal operation is caused by the suction action and speed energy of the high-speed jet refrigerant injected from the nozzle portion 15a.
  • the nozzle portion 15a of the ejector 15 is bypassed and switched to a refrigerant circuit that allows the refrigerant to flow, so that the refrigeration capacity can be reliably exhibited.
  • valve body portion 32 of the valve body 32 is shown in FIG.
  • the ball valve 32a is displaced toward the side of closing the first refrigerant passage 30b, and the plate valve 32b opens the second refrigerant passage 30c. That is, both the first refrigerant passage 30b and the second refrigerant passage 30c are opened.
  • the first pressure receiving area A1 is larger than the second pressure receiving area A2 as shown in Formula F1, and therefore, as shown in Formula F3, the first refrigerant passage 30b is caused by the pressure difference ⁇ P. Is smaller than the second set load Fsp1 on the side that closes the first refrigerant passage 30b instantaneously (ie, A2 ⁇ K ⁇ P).
  • the high-temperature and high-pressure refrigerant (point a in FIG. 6) discharged from the compressor 11 is supercooled by the radiator 12 in the same manner as during normal operation. It becomes a phase refrigerant (point a ⁇ b in FIG. 6).
  • the supercooled liquid phase refrigerant that has flowed out of the supercooling portion 12 c of the radiator 12 flows into the inflow passage 30 a of the circuit switching valve 13.
  • valve body 32 closes the first refrigerant passage 30b and opens the second refrigerant passage 30c, so that the refrigerant that has flowed into the inflow passage 30a goes to the second refrigerant passage 30c. Inflow.
  • the refrigerant flowing into the second refrigerant passage 30c is decompressed in an enthalpy manner at an orifice hole 34a provided in the pressure receiving portion 34 of the valve body 32 (point b ⁇ point g in FIG. 6), and the second refrigerant outlet 31c. And flows into the bypass path 20.
  • the refrigerant flowing into the bypass passage 20 flows into the evaporator 19 via the three-way joint 18.
  • the refrigerant flowing into the evaporator 19 absorbs heat from the blown air blown by the blower fan 19a and evaporates (g point ⁇ h point in FIG. 6). Thereby, blowing air is cooled.
  • the refrigerant that has flowed out of the evaporator 19 flows into the refrigerant suction port 15 c of the ejector 15.
  • the flow rate characteristic of the orifice hole 34a of the present embodiment is that the refrigerant that flows out of the evaporator 19 (that is, the refrigerant on the outlet side of the evaporator 19) is a saturated gas phase refrigerant or gas-liquid when the low load operation is performed. It is set to be a two-phase refrigerant. For this reason, the expansion valve 14 closes the throttle passage during low-load operation.
  • coolant is a saturated gaseous-phase refrigerant
  • the gas-phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again (point h ⁇ point a in FIG. 6).
  • the ejector refrigeration cycle 10 during low-load operation operates as described above, and can cool the blown air blown into the passenger compartment.
  • the discharge capacity control unit of the control device increases the refrigerant discharge capacity of the compressor 11.
  • the pressure difference ⁇ P becomes larger than the reference pressure difference K ⁇ P
  • the valve body portion 32 of the circuit switching valve 13 opens the first refrigerant passage 30b and closes the second refrigerant passage 30c.
  • a mechanical mechanism is employed as the circuit switching valve 13 that closes one of the first refrigerant passage 30b and the second refrigerant passage 30c when the other is opened. Further, as the circuit switching valve 13, a valve that opens the second refrigerant passage when the front-rear differential pressure ⁇ Pc is lower than the reference front-rear differential pressure K ⁇ Pc is employed.
  • the circuit switching valve 13 opens the first refrigerant passage 30b, so that the refrigerant dissipated by the radiator 12 can flow into the nozzle portion 15a of the ejector 15. Further, at the time of low load operation, the circuit switching valve 13 opens the second refrigerant passage 30c side so that the refrigerant radiated by the radiator 12 flows into the bypass passage 20 and is led to the refrigerant inlet side of the evaporator 19. Can do.
  • the refrigerant circuit can be switched mechanically and reliably in accordance with the load fluctuation.
  • the front-rear differential pressure ⁇ Pc becomes lower than the reference front-rear differential pressure K ⁇ Pc.
  • the second refrigerant passage 30c is opened, and the refrigerant radiated by the radiator 12 is caused to flow into the evaporator 19 via the bypass passage 20.
  • a normal refrigeration cycle (so-called annular cycle) can be formed. Therefore, the refrigerating machine oil staying in the evaporator 19 is easily returned to the compressor 11 at the start of the cycle.
  • the circuit switching valve 13 when the pressure difference ⁇ P is greater than or equal to the reference pressure difference K ⁇ P, the first refrigerant passage 30b is opened, and the pressure difference ⁇ P is lower than the reference pressure difference K ⁇ P.
  • the one that opens the second refrigerant passage 30c is employed.
  • the pressure difference ⁇ P is greater than or equal to the reference pressure difference K ⁇ P. In this case, it is possible to instantaneously switch from the refrigerant circuit during normal operation to the refrigerant circuit during low-load operation.
  • the second pressure receiving area A2, the third pressure receiving area A3, and the set load Fsp2 of the coil spring 33 are set so as to satisfy the above formulas F4 to F6, the pressure difference ⁇ P becomes lower than the reference pressure difference K ⁇ P. In this case, it is possible to instantaneously switch from the refrigerant circuit during low load operation to the refrigerant circuit during normal operation.
  • the pressure reducing portion is configured by the orifice hole 34a of the pressure receiving portion 34, the pressure reducing portion can be easily formed.
  • a refrigerant passage that connects the upstream and downstream sides of the refrigerant flow of the pressure receiving portion 34 may be formed in the valve body 31, and an orifice, a capillary tube, or the like as a decompression portion may be disposed in the refrigerant passage.
  • FIG. 7 is a schematic cross-sectional view showing a state in which the circuit switching valve 24 switches to a refrigerant circuit that allows the refrigerant flowing out of the radiator 12 to flow into the nozzle portion 15a side of the ejector 15.
  • FIG. 8 is a schematic cross-sectional view showing a state in which the circuit switching valve 24 is switched to a refrigerant circuit that allows the refrigerant flowing out of the radiator 12 to flow into the bypass path 20 side.
  • the circuit switching valve 24 includes a valve body 41, a first valve body portion 42, a first coil spring 43, a first drive mechanism 44, a second valve body portion 45, a second coil spring 46, a second drive mechanism 47, and the like. Yes.
  • the valve body 41 is formed in a prismatic shape or a cylindrical shape by combining a plurality of structural members made of metal or resin.
  • the valve body 41 forms an outer shell of the circuit switching valve 24 and houses the first valve body portion 42, the first coil spring 43, the second valve body portion 45, the second coil spring 46, and the like.
  • the valve body 41 is formed with a high-pressure refrigerant inlet 41a, a first refrigerant outlet 41b, and a second refrigerant outlet 41c similar to the circuit switching valve 13 described in the first embodiment.
  • a plurality of refrigerant passages such as an inflow passage 40a, a first refrigerant passage 40b, and a second refrigerant passage 40c similar to the circuit switching valve 13 are formed inside the valve body 41.
  • the first valve body portion 42 is a cylindrical valve body that opens and closes the first refrigerant passage 40b.
  • the first coil spring 43 is a first elastic member that applies a load on the side that opens the first refrigerant passage 40 b to the first valve body portion 42.
  • the first drive mechanism 44 is for displacing the first valve body 42 according to the high-pressure side pressure PH of the refrigerant upstream of the circuit switching valve 24 (in this embodiment, the pressure of the refrigerant on the outlet side of the radiator 12). Outputs driving force.
  • the first drive mechanism 44 is attached to the outside of the valve body 41 as shown in FIGS.
  • the first drive mechanism 44 has a first case 44a and a first diaphragm 44b.
  • the first case 44a is a first space forming member formed by joining the opening side of metal cup-shaped members (that is, cup-shaped members). For this reason, a space is formed inside the first case 44a.
  • the 1st diaphragm 44b which is a 1st pressure response member is arrange
  • the first diaphragm 44b is formed of a metal circular thin plate.
  • the outer peripheral edge of the first diaphragm 44b is fixed to the first case 44a over the entire circumference. For this reason, the internal space of the first case 44a is partitioned into two spaces, a first enclosure space 44c and a first introduction space 44d, by the first diaphragm 44b.
  • an inert gas in this embodiment, helium gas
  • the first introduction space 44d communicates with the inflow passage 40a.
  • the refrigerant pressure in the first introduction space 44d becomes the high-pressure side pressure PH of the radiator 12 outlet-side refrigerant. Therefore, the first diaphragm 44b is displaced according to the pressure difference between the pressure of the inert gas in the enclosed space 44c and the high-pressure side pressure PH.
  • the inert gas in the first enclosed space 44c does not change greatly even if the temperature changes slightly. For this reason, the pressure in the 1st enclosure space 44c of this embodiment becomes substantially constant under the general use environment of the ejector-type refrigeration cycle 10. Accordingly, the first diaphragm 44b of the present embodiment is displaced substantially according to the high pressure side pressure PH of the radiator 12 outlet side refrigerant.
  • the displacement of the first diaphragm 44b is transmitted to the first valve body portion 42 via the columnar first operating rod 42a extending in the displacement direction of the first valve body portion 42.
  • the high-pressure side pressure PH is equal to or higher than a predetermined reference high-pressure side pressure KPH, the first enclosed space 44c so that the first valve body portion 42 opens the first refrigerant passage 40b.
  • the reference sealing pressure of the inert gas is set.
  • the second valve body portion 45 is a spherical valve body that opens and closes the second refrigerant passage 40c.
  • the second coil spring 46 is a second elastic member that applies a load on the side that closes the second refrigerant passage 40 c to the second valve body portion 45.
  • the second drive mechanism 47 outputs a driving force for displacing the second valve body portion 45 according to the high-pressure side pressure PH of the refrigerant upstream of the circuit switching valve 24.
  • the second drive mechanism 47 is attached to the outside of the valve body 41 as shown in FIGS.
  • the basic configuration of the second drive mechanism 47 is the same as that of the first drive mechanism 44. Accordingly, the second drive mechanism 47 includes a second case 47a that is a second space forming member and a second diaphragm 47b that is a second pressure responsive member.
  • the internal space of the second case 47a is divided into two spaces, a second enclosure space 47c and a second introduction space 47d, by a second diaphragm 47b. Similar to the first diaphragm 44b of the first drive mechanism 44, the second diaphragm 47b is displaced substantially according to the high-pressure side pressure PH of the radiator 12 outlet side refrigerant.
  • the displacement of the second diaphragm 47 b is transmitted to the second valve body 45 via a cylindrical second operating rod 45 a extending in the displacement direction of the second valve body 45.
  • the circuit switching valve 24 of the present embodiment when the high pressure side pressure PH is equal to or higher than the reference high pressure side pressure KPH, the first refrigerant passage 40b is opened and the second refrigerant passage 40c is closed.
  • the high pressure side pressure PH is lower than the reference high pressure side pressure KPH, the first refrigerant passage 40b is closed and the second refrigerant passage 40c is opened.
  • the front-rear differential pressure ⁇ Pc of the compressor 11 when the high-pressure side pressure PH is the reference high-pressure side pressure KPH is defined as a reference front-rear differential pressure K ⁇ Pc.
  • the front-rear differential pressure ⁇ Pc is lower than the reference front-rear differential pressure K ⁇ Pc, such as when starting a general cycle, the first refrigerant passage 40b is opened. While closing, the second refrigerant passage 40c is opened.
  • a fixed throttle is disposed as a decompression unit that decompresses the refrigerant flowing into the evaporator 19 in the bypass passage 20.
  • this fixed throttle an orifice, a capillary tube or the like can be employed.
  • the circuit switching valve 24 having the first and second drive mechanisms 44 and 47 is employed.
  • the drive mechanism that displaces the pressure responsive member (diaphragm) by the pressure difference between the gas pressure in the enclosed space and the refrigerant pressure in the introduction space the pressure in the introduction space (in this embodiment, the high pressure side pressure PH). )
  • the enclosed space functions as a damper. For this reason, sudden displacement of the pressure responsive member (diaphragm) is suppressed.
  • the refrigerant circuit can be switched mechanically and reliably according to the load fluctuation.
  • the first valve body portion 42 of the present embodiment is formed with a first pilot hole 42b that allows the inflow passage 40a and the first refrigerant passage 40b to communicate with each other.
  • the first operating rod 42a is arranged to open and close the first pilot hole 42b according to the displacement of the first diaphragm 44b.
  • the valve body 41 is formed with a communication passage 41d for communicating the inflow passage 40a and the first refrigerant passage 40b.
  • Other configurations of the circuit switching valve 24 are the same as those of the second embodiment.
  • the operation of the circuit switching valve 24 of this embodiment will be described.
  • the high-pressure side pressure PH increases, the first diaphragm 44b is displaced to the side that reduces the first enclosed space 44c.
  • the high pressure side pressure PH becomes equal to or higher than the reference high pressure side pressure KPH, the first operating rod 42a connected to the first diaphragm 44b opens the first pilot hole 42b.
  • the refrigerant flowing out of the radiator 12 flows into the downstream side of the first valve body portion 42 through the communication passage 41d and the first pilot hole 42b.
  • the pressure difference between the refrigerant pressure upstream of the refrigerant flow of the first valve body portion 42 and the refrigerant pressure of the downstream side is reduced, and the first valve body portion 42 opens the first refrigerant passage 40b by the load of the first coil spring 43. .
  • the first diaphragm 44b is displaced to the side that expands the first enclosed space 44c, and the first operating rod 42a closes the first pilot hole 42b of the first valve body portion 42.
  • the high pressure side pressure PH becomes equal to or higher than the reference high pressure side pressure KPH, the first valve body 42 is displaced together with the first operating rod 42a to close the first refrigerant passage 40b.
  • circuit switching valve 24 other operations of the circuit switching valve 24 are the same as in the second embodiment. Also in the circuit switching valve 24 of this embodiment, when the high pressure side pressure PH is equal to or higher than the reference high pressure side pressure KPH, the first refrigerant passage 40b is opened and the second refrigerant passage 40c is closed. On the other hand, when the high pressure side pressure PH is lower than the reference high pressure side pressure KPH, the first refrigerant passage 40b is closed and the second refrigerant passage 40c is opened.
  • the first valve body 42 can be opened by opening and closing the pilot hole 42b. Accordingly, the first valve body portion 42 can be opened with a relatively small driving force, and an increase in the size of the first drive mechanism 44 can be suppressed.
  • the second valve body portion 45 communicates the inflow passage 40a and the second refrigerant passage 40c.
  • the second pilot hole 45b may be provided, and the second diaphragm 47b of the second drive mechanism 47 may be connected to a second operating rod 45a that opens and closes the second pilot hole 45b.
  • the circuit switching valve 25 includes a valve body 51, a first valve body 52, a first coil spring 53, a second valve body 55, a second coil spring 56, a common drive mechanism 57, a common operation rod 58, and the like.
  • the valve body 51 is formed in a prismatic shape or a cylindrical shape by combining a plurality of structural members made of metal or resin.
  • the valve body 51 forms an outer shell of the circuit switching valve 24 and accommodates a first valve body 52, a first coil spring 53, a second valve body 55, a second coil spring 56, a common operating rod 58, and the like. To do.
  • the valve body 51 is formed with a high-pressure refrigerant inlet 51a, a first refrigerant outlet 51b, and a second refrigerant outlet 51c similar to the circuit switching valve 13 described in the first embodiment.
  • a plurality of refrigerant passages such as an inflow passage 50a, a first refrigerant passage 50b, and a second refrigerant passage 50c similar to the circuit switching valve 13 are formed inside the valve body 51.
  • the first valve body 52 is a cylindrical valve body that opens and closes the inlet of the first refrigerant passage 50b.
  • the first coil spring 53 is a first elastic member that applies a load that closes the first refrigerant passage 50 b to the first valve body 52.
  • a through hole penetrating in the axial direction is formed at the center of the first valve body 52.
  • a common operating rod 58 is disposed inside the through hole.
  • the second valve body portion 55 is a spherical valve body that opens and closes the inlet portion of the second refrigerant passage 50c.
  • the second coil spring 56 is a second elastic member that applies a load on the side that closes the second refrigerant passage 50 c to the second valve body portion 55.
  • the common drive mechanism 57 has a common case 57a that is a common space forming member and a common diaphragm 57b that is a common pressure response member.
  • the internal space of the shared case 57a is divided into two spaces, a shared enclosed space 57c and a shared introduction space 57d, by a shared diaphragm 57b.
  • the common diaphragm 57b is displaced substantially according to the high pressure side pressure PH of the radiator 12 outlet side refrigerant.
  • the displacement of the common diaphragm 57b is caused by the first valve body 52 and the second valve body through the cylindrical common operating rod 58 extending in the displacement direction of the first valve body 52 and the second valve body 55. 55 is transmitted to both.
  • the common operation rod 58 is also displaced to the same side as the common diaphragm 57b.
  • the 1st valve body part 52 is displaced to the side which closes the 1st refrigerant path 50b with the load of the 1st coil spring 53.
  • the 2nd valve body part 55 is displaced to the side which opens the 2nd refrigerant path 50c with the common action
  • the first refrigerant passage 50b is opened and the second refrigerant passage 50c is closed, so that the high-pressure side pressure PH is
  • the reference sealing pressure of the inert gas in the shared sealing space 57c is set so that the first refrigerant passage 50b is closed and the second refrigerant passage 50c is opened.
  • the cycle configuration of the ejector refrigeration cycle is not limited to the configuration disclosed in the above-described embodiment.
  • an auxiliary evaporator that evaporates the refrigerant may be disposed between the refrigerant outlet of the diffuser portion 15 d of the ejector 15 and the inlet of the accumulator 16.
  • the refrigerant evaporating pressure (refrigerant evaporating temperature) in the auxiliary evaporator can be made higher than the refrigerant evaporating pressure (refrigerant evaporating temperature) in the evaporator 19 by the boosting action of the ejector 15. Therefore, in both evaporators, the refrigerant can be evaporated at different temperature zones. Furthermore, even during low-load operation, the evaporator 19 and the auxiliary evaporator can be connected in series, and the refrigeration capacity can be exhibited in both evaporators.
  • an internal heat exchanger for exchanging heat between the high-pressure refrigerant flowing out from the radiator 12 and the low-pressure refrigerant flowing out from the evaporator 19 or the suction refrigerant sucked into the compressor 11 may be added to the ejector refrigeration cycle 10. Good.
  • Each component device constituting the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.
  • a normal radiator including only the condensing unit 12a may be employed.
  • a receiver-integrated condenser that integrates a receiver (receiver) that separates the gas-liquid of the refrigerant radiated by this radiator and stores excess liquid phase refrigerant is adopted. Also good.
  • the expansion valve 14 is adopted.
  • the expansion valve 14 is not an essential component in the ejector refrigeration cycle.
  • the expansion valve 14, the ejector 15, the accumulator 16, and the like may be integrally configured.
  • a needle-shaped or conical valve body portion is disposed inside the nozzle portion 15a of the ejector 15, and the valve body portion is displaced so that the superheat degree SH of the evaporator 19 outlet side refrigerant approaches the reference superheat degree KSH.
  • the expansion valve 14 and the ejector 15 may be integrated.
  • the refrigerant is not limited to this.
  • HFO refrigerants R1234yf, HFO-1234ze, HFO-1234zd
  • a supercritical refrigeration cycle in which carbon dioxide is employed as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
  • the ejector refrigeration cycle 10 is applied to a vehicle air conditioner.
  • the application of the ejector refrigeration cycle 10 is not limited thereto.
  • the present invention may be applied to a stationary air conditioner, a cold / hot storage, a cooling / heating device for a vending machine, and the like.
  • the radiator 12 of the ejector-type refrigeration cycle 10 including the ejector 15 is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air
  • the evaporator 19 is used side heat exchange that cools the blown air. It is a vessel.
  • the evaporator 19 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air
  • the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Safety Valves (AREA)

Abstract

Un cycle de réfrigération du type-éjecteur est pourvu : d'un compresseur; d'un radiateur; d'un éjecteur; d'un évaporateur; un passage de dérivation pour dévier le réfrigérant qui a libéré la chaleur dans le radiateur loin de la partie de la buse de l'éjecteur et guider le réfrigérant vers le côté amont de la sortie de réfrigérant de l'évaporateur; une unité de décompression (34a) pour décompresser le réfrigérant s'écoulant dans l'évaporateur par l'intermédiaire du passage de dérivation; et une vanne de commutation de circuit (13) pour ouvrir et fermer un premier passage de réfrigérant (30b) pour guider le réfrigérant vers la partie de buse, et ouvrir et fermer un second passage de réfrigérant (30c) pour guider le réfrigérant vers le passage de dérivation. La vanne de commutation de circuit est constituée d'un mécanisme mécanique pour fermer le premier passage de réfrigérant (30b) ou le second passage de réfrigérant (30c) lorsque l'autre passage de réfrigérant est ouvert. La vanne de commutation de circuit ouvre le second passage de réfrigérant (30c) lorsque la différence de pression avant-après (ΔPc) obtenue par soustraction de la pression du réfrigérant sur le côté d'admission du compresseur à partir de la pression du réfrigérant sur le côté de décharge, est inférieure à une référence préréglée avant-après la différence de pression (KΔPc).
PCT/JP2017/021414 2016-07-18 2017-06-09 Cycle de réfrigération de type-éjecteur WO2018016219A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017089964A (ja) * 2015-11-09 2017-05-25 株式会社デンソー エジェクタ式冷凍サイクル
WO2022038950A1 (fr) * 2020-08-17 2022-02-24 株式会社デンソー Dispositif à cycle de réfrigération

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JP2017089964A (ja) * 2015-11-09 2017-05-25 株式会社デンソー エジェクタ式冷凍サイクル
WO2022038950A1 (fr) * 2020-08-17 2022-02-24 株式会社デンソー Dispositif à cycle de réfrigération
JP7472714B2 (ja) 2020-08-17 2024-04-23 株式会社デンソー 冷凍サイクル装置

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