JP2019138617A - Ejector-type refrigeration cycle and ejector module - Google Patents

Abstract

To provide an ejector-type refrigeration cycle which can properly change a throttle opening of a suction-side decompression part according to a thermal load of the cycle.SOLUTION: A suction-side decompression part for decompressing a refrigerant flowing into a suction-side evaporator 19 comprises a suction-side decompression device 15 constituted of a mechanical mechanism which becomes a fixed throttle when a pressure difference ΔP which is obtained by subtracting low-stage side pressure Peo being the pressure of the refrigerant flowing out of the suction-side evaporator 19 from inlet-side pressure Pni being the pressure of the refrigerant flowing into a nozzle part 14a of an ejector 14 is larger than a reference pressure difference KΔP, and also becomes a variable throttle for increasing a throttle opening accompanied by a decrease of the pressure difference ΔP when the pressure difference ΔP is not larger than the reference pressure difference KΔP. By this constitution, it is avoided that the flow rate of the refrigerant flowing into the suction-side evaporator 19 becomes short by increasing the throttle opening at a low-load operation.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an ejector refrigeration cycle including an ejector, and an ejector module applied to the ejector refrigeration cycle.

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle that is a vapor compression refrigeration cycle including an ejector is known. In this type of ejector refrigeration cycle, the pressure of the refrigerant sucked into the compressor can be increased by the pressure increasing action of the diffuser portion of the ejector. Thereby, in the ejector type refrigeration cycle, the power consumption of the compressor can be reduced and the coefficient of performance (COP) of the cycle can be improved.

  For example, Patent Document 1 discloses an ejector-type refrigeration cycle that is applied to an air conditioner and cools blown air that is blown into an air-conditioning target space.

  More specifically, the ejector refrigeration cycle of Patent Document 1 includes a branching portion that branches the flow of the high-pressure refrigerant that has flowed out of the radiator, and a suction-side evaporator that evaporates the low-pressure refrigerant and cools the blown air. Yes. Then, one refrigerant branched at the branching portion flows into the nozzle portion of the ejector, and the other refrigerant branched at the branching portion is depressurized by the suction side decompression portion and flows into the suction side evaporator. Further, the refrigerant has a cycle configuration in which the refrigerant flowing out from the suction side evaporator is sucked from the refrigerant suction port of the ejector.

  In Patent Document 1, an example in which a fixed throttle with a fixed throttle opening is employed as the suction-side decompression unit, the degree of superheat of the refrigerant on the outlet side of the suction-side evaporator approaches a predetermined reference superheat degree. In addition, there are also disclosed an example in which a temperature type expansion valve for adjusting the throttle opening is adopted, and an electric variable throttle device in which the throttle opening can be adjusted by a control signal output from the control device.

Japanese Patent No. 5217121

  However, if a fixed throttle is used as the suction side pressure reducing unit as in Patent Document 1, the cooling capacity of the suction side evaporator can be sufficiently exhibited during normal operation, but it flows into the suction side evaporator during low load operation. In some cases, the flow rate (mass flow rate) of the refrigerant is insufficient, and the cooling capacity of the suction-side evaporator is not sufficiently exhibited. If a temperature expansion valve is used as the suction side decompression unit, the flow rate of the refrigerant flowing into the suction side evaporator during low load operation or the like decreases, and the temperature of the blown air cooled by the suction side evaporator The distribution sometimes expanded.

  In addition, if an electric variable throttle device is employed as the suction side pressure reducing unit, not only will the suction side pressure reducing unit be increased in size, but also a sensor that outputs a signal for controlling the operation of the electric variable throttle device. Since this is necessary, the overall size of the ejector refrigeration cycle is increased. Furthermore, complicated control is required to adjust the throttle opening of the electric variable throttle device in accordance with the load fluctuation of the cycle.

  In view of the above points, an object of the present invention is to provide an ejector-type refrigeration cycle in which the throttle opening degree of the suction-side decompression unit can be appropriately changed according to the thermal load of the cycle.

  Another object of the present invention is to provide an ejector module that can appropriately change the throttle opening degree of the suction-side decompression unit when applied to an ejector refrigeration cycle.

In order to achieve the above object, the invention described in claim 1 includes a compressor (11) that compresses and discharges a refrigerant, a radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and a radiator. The refrigerant is sucked from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle part (14a) for depressurizing the refrigerant that has flowed out, and the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port is An ejector (14) for increasing the pressure, a suction side decompression unit (15 ... 60a) for decompressing the refrigerant, and a suction side evaporator (evaporating the refrigerant decompressed by the suction side decompression unit) 19)
The suction-side decompression unit is an ejector refrigeration cycle that changes the throttle opening based on the inlet-side pressure (Pni) that is the pressure of the refrigerant flowing into the nozzle unit.

  According to this, since the suction side pressure reducing section (15... 60a) changes the throttle opening based on the inlet side pressure (Pni), the suction side pressure reducing section (15... 60a) is changed according to the cycle load fluctuation. Thus, it is possible to provide an ejector type refrigeration cycle that can appropriately change the throttle opening.

  In the ejector-type refrigeration cycle having the above characteristics, the suction-side decompression section (15, 15a, 15c, 15e) flows out from the suction-side decompression section from the inlet-side pressure (Pni) that is the pressure of the refrigerant flowing into the nozzle section. It may have a mechanical mechanism for increasing the throttle opening as the pressure difference (ΔP) is reduced by subtracting the low-stage pressure (Peo), which is the refrigerant pressure.

  According to this, since the suction side decompression section (15... 15e) increases the throttle opening as the pressure difference (ΔP) decreases, when the pressure difference (ΔP) decreases as in low load operation. In addition, the throttle opening can be increased. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator (19) during the low load operation.

  Further, since the suction side pressure reducing section (15... 15e) has a mechanical mechanism that changes the throttle opening according to the pressure difference (ΔP), a complicated configuration or control is required to change the throttle opening. And so on. Therefore, it is possible to provide an ejector refrigeration cycle with a simple configuration that can appropriately change the throttle opening of the suction-side decompression section (15... 15e) according to cycle load fluctuations.

  In the ejector-type refrigeration cycle having the above characteristics, the suction side pressure reducing units (15b, 15d) increase the throttle opening as the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle unit, decreases. It may have a mechanical mechanism.

  According to this, since the suction side pressure reducing part (15b, 15d) increases the throttle opening as the inlet side pressure (Pni) decreases, the inlet side pressure (Pni) decreases as in low load operation. When this is done, the throttle opening can be increased. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator (19) during the low load operation.

  Furthermore, since the suction side pressure reducing section (15b, 15d) has a mechanical mechanism for changing the throttle opening according to the inlet side pressure (Pni), a complicated configuration or There is no need for control or the like. Therefore, it is possible to provide an ejector type refrigeration cycle with a simple configuration that can appropriately change the throttle opening of the suction side pressure reducing sections (15b, 15d) in accordance with cycle load fluctuations.

  In the ejector-type refrigeration cycle having the above characteristics, the suction-side decompression unit (60, 60a) may have an electrical mechanism that opens and closes the refrigerant passage when supplied with electric power.

  According to this, when the inlet side pressure (Pni) is decreased, the suction side pressure reducing section (60, 60a) can substantially increase the throttle opening by opening the refrigerant passage. It is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator (19) during the load operation.

  Furthermore, since an electrical mechanism that simply opens and closes the refrigerant passage is employed as the suction side decompression unit (60, 60a), the suction side decompression unit is more than when an electrical mechanism that can adjust the throttle opening with high accuracy is employed. An increase in the size of the suction side decompression section (60, 60a) can be suppressed. Therefore, it is possible to provide an ejector refrigeration cycle that can appropriately change the throttle opening of the suction-side decompression unit suction-side decompression unit (60, 60a) according to cycle load fluctuations without causing an increase in size. .

The invention according to claim 9 includes a compressor (11) that compresses and discharges the refrigerant, a radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and a suction-side evaporator (12) that evaporates the refrigerant. 19) An ejector module applied to an ejector refrigeration cycle (10) having
The nozzle part (14a) that decompresses and injects a part of the refrigerant that has flowed out of the radiator, and the suction side decompression part (15c, 15d) that decompresses another part of the refrigerant that has flowed out of the heatsink. ), A body part (21) in which a suction refrigerant inlet (21a) for allowing the refrigerant flowing out from the suction side evaporator to flow in by suction action of the injection refrigerant injected from the nozzle part, and the injection refrigerant and the refrigerant suction port A pressure increasing unit (14d) for increasing the pressure of the mixed refrigerant with the sucked suction refrigerant,
The suction side decompression unit is an ejector module that changes the throttle opening based on the inlet side pressure (Pni) that is the pressure of the refrigerant flowing into the nozzle unit.

  According to this, since the suction side decompression section (15c, 15d) changes the throttle opening based on the inlet side pressure (Pni), when applied to the ejector refrigeration cycle (10), the load of the cycle It is possible to provide an ejector module capable of appropriately changing the throttle opening degree of the suction side pressure reducing sections (15c, 15d) according to fluctuations.

  Further, in the ejector module having the above characteristics, the suction side pressure reducing unit (15c) is a low stage which is the pressure of the refrigerant flowing out from the suction side pressure reducing unit from the inlet side pressure (Pni) which is the pressure of the refrigerant flowing into the nozzle unit. A mechanical mechanism may be provided that increases the throttle opening as the pressure difference is reduced by subtracting the side pressure (Peo).

  According to this, since the suction side decompression unit (15c) increases the throttle opening as the pressure difference (ΔP) decreases, the applied ejector refrigeration cycle (10) is in a low load operation. When the pressure difference (ΔP) is reduced as time passes, the throttle opening can be increased. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant that flows out to the suction side evaporator (19) side during the low load operation.

  Furthermore, since the suction side pressure reducing part (15c) has a mechanical mechanism that changes the throttle opening according to the pressure difference (ΔP), in order to increase the throttle opening, a complicated configuration, control, etc. I don't need it. Therefore, when applied to an ejector-type refrigeration cycle (10), an ejector module is provided that can appropriately change the throttle opening of the suction-side decompression unit (15c) in accordance with cycle load fluctuations, with a simple configuration. can do.

  In the ejector module having the above characteristics, the suction side pressure reducing portion (15d) is a mechanical mechanism that increases the throttle opening as the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle portion, decreases. You may have.

  According to this, since the suction side pressure reducing part (15d) increases the throttle opening as the inlet side pressure (Pni) decreases, the applied ejector refrigeration cycle (10) becomes a low load operation. When the inlet side pressure (Pni) decreases as in the case where the throttle valve is open, the throttle opening can be increased. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant that flows out to the suction side evaporator (19) side during the low load operation.

  Furthermore, since the suction side pressure reducing portion (15d) is configured by a mechanical mechanism that changes the throttle opening according to the inlet side pressure (Pni), a complicated configuration or control is required to increase the throttle opening. Is not required. Therefore, when applied to an ejector-type refrigeration cycle (10), an ejector module capable of appropriately changing the throttle opening of the suction-side decompression unit (15d) with a simple configuration in accordance with the cycle load fluctuation is provided. can do.

  In addition, the “mechanical mechanism” described in the claims means a mechanism that operates by a load due to fluid pressure, a load due to a spring, or the like without requiring supply of electric power. “Electrical mechanism” means a mechanism that operates when electric power is supplied.

  Further, the reference numerals in parentheses of each means described in this column and in the claims are an example showing the correspondence with the specific means described in the embodiments described later.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is typical sectional drawing at the time of the aperture_diaphragm | restriction opening degree of the suction side decompression device of 1st Embodiment being the minimum. It is typical sectional drawing at the time of the aperture opening degree of the suction side decompression device of a 1st embodiment being the maximum. It is a graph which shows the relationship between the pressure difference in the attraction | suction side decompression device of 1st Embodiment, and a throttle opening. It is typical sectional drawing when the aperture opening degree of the suction side decompression device of a 2nd embodiment is the minimum. It is typical sectional drawing at the time of the aperture opening degree of the suction side decompression device of a 2nd embodiment being the maximum. It is typical sectional drawing at the time of the aperture opening degree of the attraction | suction side decompression device of 3rd Embodiment being the minimum. It is typical sectional drawing at the time of the aperture opening degree of the suction side decompression device of a 3rd embodiment being the maximum. It is a graph which shows the relationship between the inlet side pressure in the suction side pressure reduction apparatus of 3rd Embodiment, and a throttle opening. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. It is a front view of the ejector module of 4th Embodiment. It is XII-XII sectional drawing of FIG. 11, Comprising: It is sectional drawing when the aperture | throttle opening degree of the suction | inhalation pressure reduction part of the ejector module of 4th Embodiment is the minimum. It is XII-XII sectional drawing of FIG. 11, Comprising: It is sectional drawing when the aperture | throttle opening degree of the suction side pressure reduction part of the ejector module of 4th Embodiment is the maximum. It is sectional drawing when the aperture opening degree of the suction | inhalation pressure reduction part of the ejector module of 5th Embodiment is the minimum. It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. It is sectional drawing when the aperture opening degree of the suction | inhalation pressure reduction part of the ejector module of 7th Embodiment is the minimum. It is sectional drawing when the aperture opening degree of the suction | inhalation pressure reduction part of the ejector module of 7th Embodiment is the maximum. It is a whole block diagram of the ejector-type refrigerating cycle of 8th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 9th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 10th Embodiment. It is a time chart which shows the electricity supply state to the on-off valve of the pulse width modulation control performed in 10th Embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. 1-4. The ejector-type refrigeration cycle 10 of this embodiment is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is a space to be air-conditioned. Therefore, the fluid to be cooled in the ejector refrigeration cycle 10 is blown air.

  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 of the cycle does not exceed the critical pressure of the refrigerant. Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant. A part of the refrigeration oil circulates in the cycle together with the refrigerant.

  In the ejector refrigeration cycle 10 shown in the overall configuration diagram of FIG. 1, a compressor 11 sucks in refrigerant, compresses it, and discharges it. More specifically, the compressor 11 of the present embodiment is an electric compressor that is configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.

  As the compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. The electric motor is a motor whose rotation speed (that is, refrigerant discharge capacity) is controlled by a control signal output from the air conditioning control device 40, and any type of an AC motor or a DC motor can be adopted. Good.

  The refrigerant inlet side of the radiator 12 is connected to the discharge port of the compressor 11. The radiator 12 is a heat exchanger for condensing by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12a to dissipate the high-pressure refrigerant and condense it. The cooling fan 12 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 40.

  The refrigerant outlet of the radiator 12 is connected to the inlet side of the branch portion 13. The branch part 13 branches the flow of the refrigerant that has flowed out of the radiator 12. The branch part 13 has a three-way joint structure having three refrigerant inlets and outlets communicating with each other, one of the three refrigerant inlets and outlets being a refrigerant inlet and the other two being refrigerant outlets. .

  One refrigerant outlet of the branch part 13 is connected to the inlet side of the nozzle part 14 a of the ejector 14. The other refrigerant outlet of the branch part 13 is connected to the high-pressure side inlet 51 a side of the suction-side decompression device 15.

  The ejector 14 has a nozzle part 14a that decompresses and injects the refrigerant that has flowed out of the radiator 12, and functions as a refrigerant decompression part. Further, the ejector 14 functions as a refrigerant circulation section that sucks and circulates the refrigerant from the outside by the suction action of the refrigerant injected from the refrigerant injection port of the nozzle portion 14a.

  In addition to this, the ejector 14 converts the kinetic energy of the mixed refrigerant of the refrigerant injected from the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c into pressure energy, and increases the pressure of the mixed refrigerant. It fulfills the function as a part.

  More specifically, the ejector 14 has a nozzle portion 14a and a body portion 14b. The nozzle portion 14a is formed of a substantially cylindrical metal (stainless alloy in the present embodiment) that gradually tapers in the refrigerant flow direction. The nozzle part 14a is an isentropic decompression of the refrigerant in the refrigerant passage formed inside.

  The refrigerant passage formed in the nozzle portion 14a includes a throat portion that reduces the passage cross-sectional area the most, and a divergent portion in which the passage cross-sectional area gradually increases from the throat toward the refrigerant injection port that injects the refrigerant. Is formed. That is, the nozzle part 14a of this embodiment is configured as a Laval nozzle.

  Further, in the present embodiment, the nozzle portion 14a is set such that the flow rate of the injected refrigerant injected from the refrigerant injection port during the normal operation of the cycle is equal to or higher than the speed of sound. Of course, you may comprise the nozzle part 14a with a tapered nozzle.

  The body portion 14b is formed of a substantially cylindrical metal (in this embodiment, aluminum). The body portion 14b functions as a fixing member that supports and fixes the nozzle portion 14a therein and forms an outer shell of the ejector 14. More specifically, the nozzle portion 14a is fixed by press-fitting so as to be housed inside the longitudinal end of the body portion 14b. The body part 14b may be formed of resin.

  Of the outer peripheral surface of the body portion 14b, a portion corresponding to the outer peripheral side of the nozzle portion 14a is formed with a refrigerant suction port 14c provided so as to penetrate the inside and the outside and communicate with the refrigerant injection port of the nozzle portion 14a. ing. The refrigerant suction port 14c is a through hole that sucks the refrigerant that has flowed out from a suction side evaporator 19 described later into the ejector 14 by the suction action of the jet refrigerant injected from the nozzle portion 14a.

  A suction passage and a diffuser portion 14d are formed inside the body portion 14b. The suction passage is a refrigerant passage that guides the suction refrigerant sucked from the refrigerant suction port 14c to the refrigerant injection port side of the nozzle portion 14a. The diffuser unit 14d is a pressure increasing unit that increases the pressure by mixing the suction refrigerant and the injection refrigerant.

  The suction passage is formed in a space between the outer peripheral side around the tapered tip of the nozzle portion 14a and the inner peripheral side of the body portion 14b, and the refrigerant passage area of the suction passage is directed toward the refrigerant flow direction. It is gradually shrinking. Thereby, the flow rate of the suction refrigerant flowing through the suction passage is gradually increased to reduce energy loss (so-called mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 14d.

  The diffuser portion 14d is a portion where a refrigerant passage extending in a truncated cone shape is formed so as to be continuous with the outlet of the suction passage. In the diffuser portion 14d, the passage cross-sectional area gradually increases toward the downstream side of the refrigerant flow. The diffuser part 14d converts the kinetic energy of the mixed refrigerant into pressure energy by such a passage shape.

  More specifically, the cross-sectional shape of the inner peripheral wall surface of the body portion 14b that forms the diffuser portion 14d of the present embodiment is formed by combining a plurality of curves. And since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 14d gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be increased in an isentropic manner.

  The refrigerant inlet side of the outflow side evaporator 18 is connected to the outlet of the diffuser portion 14d. The outflow side evaporator 18 exchanges heat between the refrigerant flowing out from the diffuser portion 14d and the blown air blown from the indoor blower 18a toward the vehicle interior, evaporating the refrigerant and exerting an endothermic effect, thereby generating blown air. It is a heat exchanger for endothermic cooling.

  The indoor blower 18a is an electric blower in which the rotation speed (that is, the amount of blown air) is controlled by a control voltage output from the air conditioning control device 40. Furthermore, the suction port side of the compressor 11 is connected to the refrigerant outlet side of the outflow side evaporator 18.

  Next, the suction side decompression device 15 will be described. The suction-side decompression device 15 is a suction-side decompression unit that decompresses the other refrigerant branched in the branching unit 13 until it becomes a low-pressure refrigerant and flows out to the refrigerant inlet side of the suction-side evaporator 19.

  When the pressure difference ΔP (ΔP = Pni−Peo) obtained by subtracting the low-stage pressure Peo from the inlet side pressure Pni is larger than a predetermined reference pressure difference KΔP, the suction side pressure reducing device 15 It becomes. Further, when the pressure difference ΔP is equal to or smaller than the reference pressure difference KΔP, a mechanical mechanism is formed that serves as a variable throttle that increases the throttle opening as the pressure difference ΔP decreases.

  Therefore, the suction side pressure reducing device 15 changes the throttle opening based on the inlet side pressure Pni. The mechanical mechanism is a mechanism for displacing the valve body portion or the like by a load due to fluid pressure, a load due to a spring, or the like without requiring supply of electric power.

  The inlet side pressure Pni is the pressure of the refrigerant flowing into the nozzle portion 14a. The low-stage pressure Peo is the pressure of the refrigerant that has flowed out of the suction-side decompression device 15 (the pressure of the refrigerant that has flowed out of the suction-side evaporator 19 in this embodiment). The reference pressure difference KΔP is set to a value slightly larger than the pressure difference ΔP at which the cooling ability of the suction side evaporator 19 is not sufficiently exhibited when the suction side pressure reducing device 15 has the minimum throttle opening. Has been.

  The detailed configuration of the suction side pressure reducing device 15 will be described with reference to FIGS. The suction side decompression device 15 has a bottomed cylindrical body 51. The body part 51 is formed by combining a plurality of structural members made of metal (in this embodiment, made of aluminum). The body 51 forms the outer shell of the suction-side decompression device 15 and functions as a housing that houses the valve body 52 and the like therein. The body part 21 may be formed of resin.

  A high-pressure side inlet 51 a to which the other refrigerant outlet side of the branch part 13 is connected is formed on one end side in the axial direction of the body part 51. On the other end side in the axial direction of the body portion 51, a bottom portion 51b is provided so as to close the other end side.

  A plurality of throttle passages 50a and 50b are formed in the bottom 51b to depressurize the refrigerant flowing from the high pressure side inlet 51a. As these throttle passages, there are provided a regular throttle passage 50a arranged at the center of the body 51 and extending along the central axis, and a plurality of auxiliary throttle passages 50b arranged on the outer peripheral side of the regular throttle passage 50a. ing. The plurality of auxiliary throttle passages 50 b are arranged at equiangular intervals around the central axis of the body portion 51.

  On the side surface of the body portion 51, a pressure introduction port 51c and a pressure outlet port 51d are formed. The pressure introduction port 51 c is a refrigerant inlet that introduces the refrigerant that has flowed out of the suction side evaporator 19 into the pressure introduction space 50 c of the body portion 51. The pressure outlet 51d is a refrigerant outlet through which the refrigerant in the pressure introduction space 50c flows out to the refrigerant suction port 14c side of the ejector 14.

  A substantially cylindrical valve body 52 is housed inside the body 51. The valve body 52 is made of the same metal as the body 51. The central axis of the valve body 52 is arranged coaxially with the central axis of the body 51. The valve body portion 52 is disposed so as to be slidable in the axial direction inside the body portion 51.

  A communication passage 52 a extending along the central axis is formed at the center of the valve body 52. For this reason, the communication passage 52a can communicate the high-pressure side inlet 51a and the inlet side of the regular throttle passage 50a regardless of the displacement of the valve body 52.

  At both end portions of the valve body portion 52, enlarged diameter portions 52b and 52c extending to the outer peripheral side are provided. The pressure introduction space 50 c is formed by a space surrounded by the enlarged diameter portions 52 b and 52 c and the inner peripheral surface of the body portion 51. The enlarged diameter portions 52b and 52c receive an inlet side pressure receiving surface that receives the pressure of the refrigerant flowing into the body portion 51 from the high pressure side inlet 51a and the pressure of the refrigerant that flows into the pressure introduction space 50c from the pressure introduction port 51c. A low-stage pressure receiving surface is formed.

  Here, the refrigerant that has flowed into the body portion 51 from the high-pressure side inlet 51 a is the other refrigerant branched at the branch portion 13. Therefore, the pressure of the refrigerant flowing into the body 51 from the high pressure side inlet 51a is equal to the inlet side pressure Pni. The pressure of the refrigerant flowing into the pressure introduction space 50c from the pressure introduction port 51c is the low stage side pressure Peo. The area of the inlet side pressure receiving surface and the area of the lower stage pressure receiving surface are set to be approximately equal.

  A seal member such as an O-ring is interposed in the gap between the inner peripheral surface of the body 51 and the outer peripheral surfaces of the enlarged diameter portions 52b and 52c, and the refrigerant does not leak from the gap between these members. Therefore, in the suction side decompression device 15, the refrigerant that has flowed into the body portion 51 from the high pressure side inlet 51a and the refrigerant that has flowed into the pressure introduction space 50c from the pressure introduction port 51c are not mixed.

  Further, the valve body 52 receives a load on the high-pressure side inlet 51a side (that is, the side away from the bottom 51b) from the coil spring 53 that is an elastic member. A regulating member 51 f that regulates the displaceable range of the valve body 52 is disposed inside the body 51. Thereby, it is suppressed that the valve body part 52 falls out from the body part 51. FIG.

  For this reason, the valve body 52 of the present embodiment is displaced according to the load generated by the pressure difference ΔP (ΔP = Pni−Peo) obtained by subtracting the outlet side pressure Peo from the inlet side pressure Pni and the load received from the coil spring 53. .

  More specifically, in the suction side pressure reducing device 15, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the valve body 52 is displaced to the side that compresses and contracts the coil spring 53 as shown in FIG. Then, it comes into contact with the bottom 51b. As a result, all the auxiliary throttle passages 50b are closed. Therefore, the suction side decompression device 15 becomes a fixed throttle. At this time, the throttle opening degree of the suction side pressure reducing device 15 is determined by the passage sectional area of the regular throttle passage 50a.

  When the pressure difference ΔP becomes equal to or less than the reference pressure difference KΔP, the valve body 52 is displaced toward the high-pressure side inlet 51a due to the load of the coil spring 53. As a result, the inlet of the auxiliary throttle passage 50b is opened, and the communication passage 52a communicates with both the regular throttle passage 50a and the auxiliary throttle passage 50b. At this time, the throttle opening degree of the suction side pressure reducing device 15 is determined by the total value of the passage sectional area of the regular throttle passage 50a and the opening area on the inlet side of the auxiliary throttle passage 50b.

  Further, as shown in FIG. 3, as the pressure difference ΔP is reduced, when the valve body 52 is displaced toward the high pressure side inlet 51a until it comes into contact with the regulating member 51f, the inlet portion of the auxiliary throttle passage 50b is fully opened. . At this time, the throttle opening degree of the suction side pressure reducing device 15 is determined by the total passage sectional area of the passage sectional area of the regular throttle passage 50a and the passage sectional area of the auxiliary throttle passage 50b.

  As a result, in the suction side pressure reducing device 15 of the present embodiment, as shown in FIG. 4, when the pressure difference ΔP is larger than the reference pressure difference KΔP, it can be a fixed throttle. Further, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, the variable throttle that increases the throttle opening as the pressure difference ΔP decreases until the inlet of the auxiliary throttle passage 50b is fully opened. It can be. The reference pressure difference KΔP can be adjusted by changing the load of the coil spring 53.

  As shown in FIG. 1, the refrigerant inlet side of the suction side evaporator 19 is connected to the outlet of the suction side pressure reducing device 15 (specifically, the outlets of the throttle passages 50 a and 50 b). The suction-side evaporator 19 exchanges heat between the low-pressure refrigerant decompressed by the suction-side decompression device 15 and the blown air that has passed through the outflow-side evaporator 18, evaporates the refrigerant, and exerts an endothermic action, thereby blowing air. It is a heat exchanger for heat absorption which cools.

  The refrigerant outlet of the suction side evaporator 19 is connected to the pressure introduction port 51 c side of the suction side decompression device 15. The refrigerant outlet port 14 c side of the ejector 14 is connected to the pressure outlet port 51 d of the suction side pressure reducing device 15. In other words, the refrigerant outlet of the suction side evaporator 19 is connected to the refrigerant suction port 14 c side of the ejector 14 via the pressure introduction space 50 c of the suction side pressure reducing device 15.

  Further, the outflow side evaporator 18 and the suction side evaporator 19 of the present embodiment are integrally configured. Specifically, each of the outflow side evaporator 18 and the suction side evaporator 19 includes a plurality of tubes that circulate the refrigerant, and a collection or distribution of refrigerants that are arranged at both ends of the plurality of tubes and circulate through the tubes. And a so-called tank-and-tube heat exchanger having a pair of collective distribution tanks.

  Then, the outflow side evaporator 18 and the suction side evaporator 19 are integrated by forming the collecting / distributing tank of the outflow side evaporator 18 and the suction side evaporator 19 with the same member. In the present embodiment, the outflow side evaporator 18 and the suction side evaporator 19 are connected in series with the blowing air flow so that the outflow side evaporator 18 is arranged upstream of the blowing air flow with respect to the suction side evaporator 19. Is arranged. Accordingly, the blown air flows as shown by the arrows drawn by the two-dot chain line in FIG.

  Next, the electric control unit of the ejector refrigeration cycle 10 of the present embodiment will be described. The air conditioning control device 40 (not shown) is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, and performs various calculations and processing based on an air conditioning control program stored in the ROM. The operation of the various control target devices 11, 12a, 18a connected to is controlled.

  On the input side of the air-conditioning control device 40, an inside air temperature sensor that detects the vehicle interior temperature Tr, an outside air temperature sensor that detects the outside air temperature Tam, a solar radiation sensor that detects the amount of solar radiation As in the vehicle interior, and a blowout from the suction side evaporator 19 A group of sensors for air conditioning control such as an evaporator temperature sensor for detecting the blown air temperature (evaporator temperature) Tefin is connected, and detection values of these air conditioning sensor groups are input.

  Further, an operation panel (not shown) is connected to the input side of the air conditioning control device 40, and operation signals from various operation switches provided on the operation panel are input to the air conditioning control device 40. As various operation switches provided on the operation panel, an air conditioning operation switch that requests air conditioning, a vehicle interior temperature setting switch that sets the vehicle interior temperature, and the like are provided.

  Note that the air conditioning control device 40 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. A configuration (hardware and software) for controlling the operation of the control target device constitutes a control unit of each control target device. For example, the configuration for controlling the operation of the compressor 11 constitutes a compressor control unit.

  Next, the operation of the ejector refrigeration cycle 10 of the present embodiment having the above configuration will be described. When the air-conditioning operation switch on the operation panel is turned on (ON), the air-conditioning control device 40 executes an air-conditioning control program stored in advance to control the operations of the various control target devices 11, 12a, and 18a.

  In this air conditioning control program, the target blowing temperature TAO of the blown air blown into the vehicle interior is calculated based on the detection signal of the air conditioning control sensor group and the operation signal from the operation panel. And based on the target blowing temperature TAO etc., the operating state of each control object apparatus is determined. For example, about the compressor 11, it determines so that a refrigerant | coolant discharge capability (in this embodiment, rotation speed) may be reduced with the raise of the target blowing temperature TAO.

  Here, the target blowing temperature TAO is a value having a correlation with the amount of cooling heat that the ejector refrigeration cycle needs to generate in order to keep the passenger compartment at a desired temperature (in other words, the cooling heat load of the ejector refrigeration cycle 10). It is.

  Therefore, when cooling the passenger compartment, reducing the refrigerant discharge capacity of the compressor 11 as the target blowing temperature TAO increases increases the refrigerant discharge capacity of the compressor 11 as the cooling heat load decreases. It means to lower. And if the air-conditioning control apparatus 40 reduces the refrigerant | coolant discharge capability of the compressor 11 with the reduction | decrease in cooling heat load, the inlet side pressure Pni will fall and the pressure difference (DELTA) P will also reduce.

  Therefore, in the present embodiment, an operation condition in which the cooling heat load is relatively high and the pressure difference ΔP is larger than the reference pressure difference KΔP is defined as normal operation. The normal operation is performed when the outside air temperature is relatively high, for example, in summer.

  An operation condition in which the cooling heat load is relatively low and the pressure difference ΔP is equal to or less than the reference pressure difference KΔP is defined as low load operation. The low load operation is executed, for example, when the outside air temperature is relatively low, such as in spring or autumn, or when anti-fogging of the vehicle window is performed at the low outside air temperature.

  When the air conditioning control device 40 operates the compressor 11, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed. The flow of the refrigerant flowing out of the radiator 12 is branched at the branching section 13. One refrigerant branched by the branch part 13 flows into the nozzle part 14 a of the ejector 14.

  The refrigerant that has flowed into the nozzle portion 14a of the ejector 14 is decompressed in an isentropic manner at the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. Then, the refrigerant that has flowed out of the suction-side evaporator 19 by the suction action of the injection refrigerant is sucked from the refrigerant suction port 14 c through the pressure introduction space 50 c of the suction-side decompression device 15.

  The injection refrigerant injected from the refrigerant injection port of the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c flow into the diffuser portion 14d. In the diffuser portion 14d, the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. Thereby, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant increases. The refrigerant whose pressure has been increased in the diffuser section 14d flows into the outflow side evaporator 18.

  The refrigerant flowing into the outflow side evaporator 18 absorbs heat from the blown air blown by the indoor blower 18a and evaporates. Thereby, the blowing air blown by the indoor blower 18a is cooled. The refrigerant flowing out from the outflow side evaporator 18 is sucked into the compressor 11 and compressed again.

  On the other hand, the other refrigerant branched at the branch portion 13 flows into the high-pressure side inlet 51 a of the suction-side decompression device 15.

  Here, during normal operation, since the valve body 52 closes the auxiliary throttle passage 50b, the suction-side decompression device 15 becomes a fixed throttle, and the total flow rate of the refrigerant flowing into the suction-side decompression device 15 enters the regular throttle passage 50a. It is decompressed and flows out. Further, during low load operation, the valve body 52 opens the auxiliary throttle passage 50b, so that the refrigerant flowing into the suction side pressure reducing device 15 is decompressed and flows out in both the normal throttle passage 50a and the auxiliary throttle passage 50b. To do.

  The refrigerant that has flowed out of the suction side decompression device 15 flows into the suction side evaporator 19. The refrigerant flowing into the suction side evaporator 19 absorbs heat from the blown air after passing through the outflow side evaporator 18 and evaporates. Thereby, the blast air after passing the outflow side evaporator 18 is further cooled. The refrigerant that has flowed out of the suction side evaporator 19 is sucked from the refrigerant suction port 14c.

  Therefore, according to the ejector-type refrigeration cycle 10 of the present embodiment, the outflow side evaporator 18 and the suction side evaporator 19 can be used in the vehicle interior during normal operation and low load operation regardless of load fluctuations. It is possible to cool the blown air sent to the air.

  Further, in the ejector refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure has been increased by the diffuser portion 14 d of the ejector 14 is sucked into the compressor 11 via the outflow side evaporator 18. According to this, the consumption power of the compressor 11 is reduced and the coefficient of performance of the cycle is reduced compared to the 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. (COP) can be improved.

  Further, in the ejector refrigeration cycle 10 of the present embodiment, the suction side pressure reducing device 15 becomes a fixed throttle that depressurizes the refrigerant in the regular throttle passage 50a during normal operation. Therefore, by appropriately setting the passage cross-sectional area of the regular throttle 50a, the cooling capacity of the suction-side evaporator 19 is not insufficient during normal operation.

  However, if a fixed throttle is used as the suction side pressure reducing unit, the flow rate (mass flow rate) of the refrigerant flowing into the suction side evaporator 19 during low load operation is insufficient, leading to insufficient cooling capacity in the suction side evaporator 19. Sometimes.

  In contrast, since the ejector refrigeration cycle 10 of the present embodiment includes the suction-side decompression device 15, the throttle opening can be increased as the pressure difference ΔP is reduced during low-load operation. Therefore, it is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator 19 during the low load operation.

  Furthermore, since the suction side pressure reducing device 15 is configured by a mechanical mechanism that changes the throttle opening according to the pressure difference ΔP, a complicated configuration or control is required to change the throttle opening. Nor. That is, according to the ejector-type refrigeration cycle 10 of the present embodiment, the suction-side decompression device 15 is employed, so that the throttle opening of the suction-side decompression unit is appropriately set according to cycle load fluctuations with a simple configuration. Can be changed.

  Further, in the suction side pressure reducing device 15 of the present embodiment, the pressure of the refrigerant flowing out from the suction side evaporator 19 is introduced as the low stage side pressure Peo. According to this, the pressure difference ΔP can be expanded by the pressure loss in the suction side evaporator 19. Therefore, it becomes easy to detect the pressure difference ΔP, and the throttle opening degree of the suction side pressure reducing device 15 can be changed more appropriately.

(Second Embodiment)
This embodiment demonstrates the example which employ | adopted the suction side pressure reduction apparatus 15a shown in FIG. 5, FIG. 6 as a suction side pressure reduction part with respect to 1st Embodiment. 5 and 6 are drawings corresponding to FIGS. 2 and 3 described in the first embodiment, respectively. 5 and 6, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  The basic configuration of the suction-side decompressor 15a is the same as that of the suction-side decompressor 15 described in the first embodiment. That is, the suction side pressure reducing device 15a becomes a fixed throttle when the pressure difference ΔP is larger than the reference pressure difference KΔP. Further, when the pressure difference ΔP is equal to or smaller than the reference pressure difference KΔP, a mechanical mechanism is formed that serves as a variable throttle that increases the throttle opening as the pressure difference ΔP decreases.

  In the suction side pressure reducing device 15a, as shown in FIGS. 5 and 6, a high pressure side inlet 51a and a low pressure side outlet 51e are formed on the side surface of the body portion 51 formed in a bottomed cylindrical shape. A valve body 52 formed in a cylindrical shape is accommodated in the body 51. The central axis of the valve body 52 is arranged coaxially with the central axis of the body 51. The valve body portion 52 is disposed so as to be slidable in the axial direction inside the body portion 51.

  A communication passage 52a that connects the high-pressure side inlet 51a and the low-pressure side outlet 51e is formed inside the cylindrical valve body 52. Furthermore, the regulating member 51f of the present embodiment is arranged so that the valve body 52 is displaced within a range in which the communication passage 52a can communicate the high pressure side inlet 51a and the low pressure side outlet 51e. In other words, the regulating member 51f of the present embodiment is arranged such that the operating range of the valve body 52 is within a range in which the communication path 52a can communicate the high pressure side inlet 51a and the low pressure side outlet 51e. Yes.

  An inlet side pressure receiving surface that receives the pressure of the refrigerant that has flowed into the body portion 51 from the high pressure side inlet 51 a is formed on one end side in the axial direction of the valve body portion 52. Further, on the other end side in the axial direction of the valve body 52, a low-stage pressure receiving surface that receives the pressure of the refrigerant flowing into the pressure introducing space 50c from the pressure introducing port 51c is formed. The area of the inlet side pressure receiving surface and the area of the lower stage pressure receiving surface are set to be approximately equal.

  Further, the valve body 52 receives a load from the coil spring 53 on the high-pressure side inlet 51a side (that is, the side on which the pressure introduction space 50c is expanded). For this reason, the valve body 52 of the present embodiment is displaced according to the load generated by the pressure difference ΔP and the load received from the coil spring 53, as in the first embodiment.

  More specifically, in the suction-side pressure reducing device 15a, when the pressure difference ΔP is larger than the reference pressure difference KΔP, as shown in FIG. 5, the coil spring is kept until the valve body 52 comes into contact with the regulating member 51f. 53 is displaced to the side to be compressed.

  In the suction side pressure reducing device 15a, the regulating member 51f is arranged so that the valve body portion 52 does not completely block the inlet portion of the low pressure side outlet 51e. Therefore, the suction side pressure reducing device 15a when the pressure difference ΔP is larger than a predetermined reference pressure difference KΔP is a fixed throttle. At this time, the opening degree of the suction side pressure reducing device 15a is determined by the opening area of the inlet portion of the low pressure side outlet 51e.

  When the pressure difference ΔP becomes equal to or smaller than the reference pressure difference KΔP, the valve body 52 is displaced toward the side where the pressure introduction space 50c is expanded by the load of the coil spring 53. Thereby, the opening area of the inlet part of the low voltage | pressure side exit 51e increases. That is, the throttle opening degree of the suction side pressure reducing device 15a increases as the pressure difference ΔP decreases.

  Furthermore, as shown in FIG. 6, when the valve body 52 is displaced to the side that expands the pressure introduction space 50 c most as the pressure difference ΔP decreases, the inlet portion of the low pressure side outlet 51 e is fully opened. . At this time, the throttle opening of the suction side pressure reducing device 15a is determined by the passage cross-sectional area of the refrigerant passage leading to the low pressure side outlet 51e.

  As a result, in the suction-side pressure reducing device 15a of the present embodiment, as in the suction-side pressure reducing device 15 described in the first embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the fixed throttle It can be. Further, when the pressure difference ΔP is equal to or smaller than the reference pressure difference KΔP, a variable throttle that increases the throttle opening degree as the pressure difference ΔP decreases until the low-pressure side outlet 51e is fully opened. Can do.

  Also in the ejector refrigeration cycle 10 of the present embodiment, the operating condition in which the pressure difference ΔP is larger than the reference pressure difference KΔP is the normal operation, and the operating condition in which the pressure difference ΔP is less than or equal to the reference pressure difference KΔP. Use low-load operation. Other configurations and operations of the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, since the ejector refrigeration cycle 10 of the present embodiment includes the suction-side decompression device 15a, the same effects as those of the first embodiment can be obtained. That is, according to the ejector-type refrigeration cycle 10 of the present embodiment, the suction-side decompression device 15a is employed, so that the throttle opening degree of the suction-side decompression unit is appropriately set according to the cycle load fluctuation with a simple configuration. Can be changed.

(Third embodiment)
In the present embodiment, an example will be described in which a suction-side decompression device 15b shown in FIGS. 7 and 8 is employed as the suction-side decompression unit with respect to the first embodiment. 7 and 8 are drawings corresponding to FIGS. 5 and 6 described in the second embodiment, respectively.

  The suction side pressure reducing device 15b becomes a fixed throttle when the inlet side pressure Pni is larger than a predetermined reference inlet side pressure KPni. Furthermore, when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, a mechanical mechanism is provided that serves as a variable throttle that increases the throttle opening as the inlet side pressure Pni is reduced. Therefore, the suction side pressure reducing device 15b changes the throttle opening based on the inlet side pressure Pni.

  Further, the reference inlet side pressure KPni is slightly lower than the inlet side pressure Pni at which the cooling ability of the suction side evaporator 19 is not sufficiently exhibited when the suction side pressure reducing device 15b has the minimum throttle opening. It is set to a large value.

  Moreover, in the suction side pressure reducing device 15b, as shown in FIGS. 7 and 8, the pressure introduction port 51c and the pressure outlet port 51d of the body portion 51 are abolished with respect to the suction side pressure reducing device 15a described in the second embodiment. Has been. A space formed on the other end side of the valve body 52 is a spring chamber 50d in which the coil spring 53 is accommodated. An outside air introduction hole 51g is formed in a portion of the body portion 51 where the spring chamber 50d is formed, and the pressure of the spring chamber 50d is the pressure of the outside air.

  For this reason, the valve body 52 of the present embodiment is displaced according to the load generated by the pressure difference obtained by subtracting the pressure Psp in the spring chamber 50 d from the inlet side pressure Pni and the load received from the coil spring 53. Here, the pressure Psp in the spring chamber 50d is equivalent to the external air pressure and is substantially constant. Therefore, the valve body 52 of the present embodiment is displaced substantially according to the load generated by the inlet side pressure Pni and the load received from the coil spring 53.

  More specifically, in the suction side pressure reducing device 15b, when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, as shown in FIG. 7, the valve body 52 comes into contact with the regulating member 51f. Until the coil spring 53 is pushed and shrunk (that is, the spring chamber 50d is shrunk). Thereby, the suction side decompression device 15b becomes a fixed throttle similarly to the suction side decompression device 15a described in the second embodiment.

  When the inlet side pressure Pni becomes equal to or lower than the reference inlet side pressure KPni, the valve body 52 is displaced toward the side of enlarging the spring chamber 50d by the load of the coil spring 53. Thereby, the opening area of the inlet part of the low voltage | pressure side exit 51e increases. That is, the throttle opening degree of the suction side pressure reducing device 15b increases as the inlet side pressure Pni decreases.

  Furthermore, as shown in FIG. 8, when the valve body 52 is displaced to the side that expands the spring chamber 50d most with the decrease in the inlet side pressure Pni, the inlet portion of the low pressure side outlet 51e is fully opened. . At this time, the throttle opening degree of the suction side pressure reducing device 15b is determined by the passage cross-sectional area of the refrigerant passage leading to the low pressure side outlet 51e.

  As a result, in the suction side pressure reducing device 15b of the present embodiment, as shown in FIG. 9, when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, a fixed throttle can be obtained. Further, when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, the variable throttle that increases the throttle opening as the inlet side pressure Pni decreases until the low pressure side outlet 51e is fully opened. It can be. The reference inlet side pressure KPni can be adjusted by changing the load of the coil spring 53.

  In the ejector refrigeration cycle 10 of the present embodiment, the operating condition in which the inlet side pressure Pni is larger than the reference inlet side pressure KPni is a normal operation, and the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni. The operating conditions are low load operation. Other configurations and operations of the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, since the ejector refrigeration cycle 10 of the present embodiment includes the suction-side decompression device 15b, the same effects as those of the first embodiment can be obtained. That is, according to the ejector-type refrigeration cycle 10 of the present embodiment, the suction-side decompression device 15b is employed, so that the throttle opening degree of the suction-side decompression unit is appropriately set according to the load fluctuation of the cycle with a simple configuration. Can be changed.

(Fourth embodiment)
In the present embodiment, the configuration corresponding to the branching section 13, the ejector 14, and the suction-side decompression device 15 described in the first embodiment is integrated as an ejector module 20 as shown in FIGS. ) Will be described. More specifically, the ejector module 20 is obtained by integrating component devices surrounded by a broken line in the overall configuration diagram of FIG. That is, the centrifugal branching portion 13a, the ejector 14, the suction side pressure reducing device 15c, and the like are integrated.

  For simplification of illustration and clarification of explanation, the refrigerant flow direction in the ejector 14 shown in the overall configuration diagram of FIG. 10 is different from the refrigerant flow direction in the ejector 14 shown in FIGS. It has become.

  The ejector module 20 has a prismatic body part 21. The body part 21 is formed by combining a plurality of constituent members made of metal (in this embodiment, made of aluminum). The body portion 21 supports and fixes the ejector 14 and constitutes a part of the suction side pressure reducing device 15c and the like. The body part 21 may be formed of resin.

  In the body portion 21, a regular throttle passage 50a and an auxiliary throttle passage 50b that exhibit the same function as in the first embodiment are formed. In the present embodiment, there is one auxiliary throttle passage 50b. Further, inside the body portion 21, refrigerant passages such as a high-pressure side refrigerant passage 20a, a suction refrigerant passage 20b, a pressure introduction passage 20c, and an outflow side passage 20d are formed.

  The high-pressure side refrigerant passage 20a is a refrigerant passage that guides the other refrigerant branched by the centrifugal branching portion 13a to the inlet side of the suction-side decompression device 15c. The suction refrigerant passage 20b is a refrigerant passage that guides the refrigerant flowing out from the suction side evaporator 19 to the refrigerant suction port 14c of the ejector 14. In addition, the refrigerant | coolant suction port 14c of this embodiment is formed in multiple numbers around the central axis of the body part 14b of the ejector 14. As shown in FIG. The plurality of refrigerant suction ports 14 c are open in the internal space of the body portion 21.

  The pressure introduction passage 20c is a refrigerant passage that guides the refrigerant flowing out from the suction side evaporator 19 to the pressure introduction space 50c of the suction side decompression device 15c. The outflow side passage 20 d is a refrigerant passage that guides the refrigerant flowing out from the outflow side evaporator 18 to the suction side of the compressor 11.

  Further, the body portion 21 is formed with refrigerant outlets such as a low-pressure side outlet 51e, a suction refrigerant inlet 21a, an outflow refrigerant inlet 21b, and an outflow refrigerant outlet 21c.

  The low-pressure side outlet 51e is a refrigerant outlet through which the refrigerant decompressed by the suction-side decompression device 15c (specifically, the regular throttle passage 50a and the auxiliary throttle passage 50b) flows out to the refrigerant inlet side of the suction-side evaporator 19. is there. The suction refrigerant inlet 21a is a refrigerant inlet through which the refrigerant that has flowed out of the suction-side evaporator 19 due to the suction action of the injection refrigerant injected from the nozzle portion 14a flows.

  The outflow refrigerant inlet 21b is a refrigerant inlet through which the refrigerant that has flowed out of the outflow side evaporator 18 flows into the outflow side passage 20d. The outflow refrigerant outlet 21 c is a refrigerant outlet through which the refrigerant flowing through the outflow side passage 20 d flows out to the suction side of the compressor 11. As shown in FIG. 11, the outflow refrigerant inlet 21 b and the outflow refrigerant outlet 21 c are opened in a shape that fits the tank portion of the outflow side evaporator 18.

  Next, the ejector 14 of the present embodiment is fixed to the body portion 21 by means such as press fitting. At this time, at least a part of a portion forming the diffuser portion 14 d of the body portion 14 b of the ejector 14 is fixed so as to protrude from the body portion 21.

  Of the parts forming the diffuser part 14d, the part protruding from the body part 21 is used for collecting and distributing the outflow side evaporator 18 when the ejector module 20 is connected to the outflow side evaporator 18 and the suction side evaporator 19. It becomes a connecting portion that is inserted into and fixed to a dedicated tank communicating with the tank or the collecting / distributing tank.

  Moreover, the centrifugal branch part 13a is integrally formed in the nozzle part 14a of this embodiment in the refrigerant | coolant flow upstream. A high-pressure side inlet 51a through which the other refrigerant branched by the branch part 13 flows is formed in the most upstream part of the refrigerant flow of the centrifugal branch part 13a. The centrifugal branching portion 13a is formed in a cylindrical shape, and is a portion for turning the flow of the refrigerant flowing from the high-pressure side inlet 51a around the central axis of the nozzle portion 14a.

  Furthermore, a through-hole 13b penetrating inside and outside is formed on the cylindrical side surface of the centrifugal branching portion 13a. The internal space of the turning part 14e communicates with the high-pressure side refrigerant passage 20a through the through hole 13b. Therefore, in the centrifugal branching portion 13a, one refrigerant having a relatively high dryness on the turning center side is depressurized by the nozzle portion 14a, and the other refrigerant having a relatively low dryness on the outer peripheral side is reduced by the suction side pressure reducing device 15c. The refrigerant flow can be branched so as to reduce the pressure at.

  Next, the basic configuration of the suction-side decompression device 15c is the same as that of the suction-side decompression device 15 described in the first embodiment. That is, the suction side pressure reducing device 15c becomes a fixed throttle when the pressure difference ΔP is larger than the reference pressure difference KΔP. Further, when the pressure difference ΔP is equal to or smaller than the reference pressure difference KΔP, a mechanical mechanism is formed that serves as a variable throttle that increases the throttle opening as the pressure difference ΔP decreases.

  In the suction-side pressure reducing device 15c of the present embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, as shown in FIG. The auxiliary throttle passage 50b is closed by displacing the introduction space 50c to the side on which the introduction space 50c is reduced. Therefore, the suction side decompression device 15 becomes a fixed throttle. At this time, the throttle opening degree of the suction side pressure reducing device 15 is determined by the passage sectional area of the regular throttle passage 50a.

  When the pressure difference ΔP becomes equal to or smaller than the reference pressure difference KΔP, the pressure introduction space 50c is displaced toward the side to be expanded by the load of the coil spring 53. Thereby, the high-pressure side refrigerant passage 20a communicates with both the regular throttle passage 50a and the auxiliary throttle passage 50b. Therefore, the throttle opening degree of the suction side pressure reducing device 15c is determined by the total value of the passage sectional area of the regular throttle passage 50a and the opening area of the inlet portion of the auxiliary throttle passage 50b.

  Furthermore, as shown in FIG. 13, when the valve body 52 is displaced to the side where the pressure introduction space 50 c is expanded most as the pressure difference ΔP decreases, the inlet portion of the auxiliary throttle passage 50 b is fully opened. At this time, the throttle opening degree of the suction side pressure reducing device 15 is determined by the total passage sectional area of the passage sectional area of the regular throttle passage 50a and the passage sectional area of the auxiliary throttle passage 50b.

  As a result, in the suction-side pressure reducing device 15c of the present embodiment, as in the suction-side pressure reducing device 15 described in the first embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the fixed throttle It can be. Furthermore, when the pressure difference ΔP is equal to or smaller than the reference pressure difference KΔP, a variable throttle that increases the throttle opening as the pressure difference ΔP is reduced until the auxiliary throttle passage 50b is fully opened. Can do.

  Also in the ejector refrigeration cycle 10 of the present embodiment, the operating condition in which the pressure difference ΔP is larger than the reference pressure difference KΔP is the normal operation, and the operating condition in which the pressure difference ΔP is less than or equal to the reference pressure difference KΔP. Use low-load operation. Other configurations and operations of the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, since the ejector refrigeration cycle 10 of the present embodiment includes the ejector module 20 in which the suction side decompression device 15c is integrated, the same effects as those of the first embodiment can be obtained. Furthermore, in this embodiment, since a part of the components of the ejector refrigeration cycle 10 is integrated as the ejector module 20, it is possible to reduce the size and improve the productivity of the ejector refrigeration cycle 10 as a whole. it can.

(Fifth embodiment)
This embodiment demonstrates the example which changed the structure of the ejector module 20 with respect to 4th Embodiment, as shown in FIG. The ejector module 20 of the present embodiment employs a suction side pressure reducing device 15d. FIG. 14 is a drawing corresponding to FIG. 12 described in the fourth embodiment.

  The basic configuration of the suction-side decompression device 15d is the same as that of the suction-side decompression device 15b described in the third embodiment. That is, the suction side pressure reducing device 15d is a fixed throttle when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, and when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni. Is composed of a mechanical mechanism that becomes a variable throttle that increases the throttle opening as the inlet side pressure Pni is reduced.

  More specifically, in the ejector module 20 of the present embodiment, the pressure introduction passage 20c is eliminated. Outside air is introduced into the spring chamber 50d in which the coil spring 53 is accommodated via the outside air introduction hole 51g. Therefore, the pressure in the spring chamber 50d is the pressure of the outside air.

  Therefore, in the suction side pressure reducing device 15d, when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, as shown in FIG. The spring chamber 50d is displaced toward the side to be reduced. Thereby, the suction-side decompression device 15d becomes a fixed throttle as in the fourth embodiment.

  When the inlet side pressure Pni becomes equal to or lower than the reference inlet side pressure KPni, the valve body 52 is displaced toward the side of enlarging the spring chamber 50d by the load of the coil spring 53. Thereby, like the fourth embodiment, the high-pressure side refrigerant passage 20a communicates with both the regular throttle passage 50a and the auxiliary throttle passage 50b. Furthermore, when the valve body 52 is displaced to the side where the spring chamber 50d is expanded most with the decrease in the inlet side pressure Pni, the inlet portion of the auxiliary throttle passage 50b is fully opened.

  As a result, in the suction side pressure reducing device 15d of the present embodiment, when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, similarly to the suction side pressure reducing device 15b described in the third embodiment, It can be a fixed aperture. Furthermore, when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, a variable throttle that increases the throttle opening as the inlet side pressure Pni decreases can be obtained.

  In the ejector refrigeration cycle 10 of the present embodiment, the operating condition in which the inlet side pressure Pni is larger than the reference inlet side pressure KPni is a normal operation, and the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni. The operating conditions are low load operation. Other configurations and operations of the ejector refrigeration cycle 10 are the same as those in the third embodiment.

  Therefore, since the ejector refrigeration cycle 10 of the present embodiment includes the ejector module 20 in which the suction-side decompression device 15d is integrated, the same effects as those of the third embodiment can be obtained. Furthermore, in this embodiment, since a part of the components of the ejector refrigeration cycle 10 is integrated as the ejector module 20, it is possible to reduce the size and improve the productivity of the ejector refrigeration cycle 10 as a whole. it can.

(Sixth embodiment)
In the present embodiment, an example in which the suction side pressure reducing device 15e is applied to the ejector refrigeration cycle 10a shown in the overall configuration diagram of FIG. 15 will be described.

  In the ejector type refrigeration cycle 10a, the branching section 13 and the outflow side evaporator 18 are eliminated from the ejector type refrigeration cycle 10 described in the first embodiment, and a gas-liquid separator 22 is provided. The gas-liquid separator 22 is a gas-liquid separator that stores the surplus liquid-phase refrigerant separated by separating the gas-liquid of the refrigerant flowing out from the diffuser part 14d.

  Further, in the ejector refrigeration cycle 10 a, the inlet side of the nozzle portion 14 a of the ejector 14 is connected to the outlet of the radiator 12. The gas-phase refrigerant outlet of the gas-liquid separator 22 is connected to the suction port side of the compressor 11, and the liquid-phase refrigerant outlet of the gas-liquid separator 22 is connected to the refrigerant inlet side of the suction-side decompression device 15 e. Yes. The suction-side decompression device 15 e decompresses the liquid-phase refrigerant separated by the gas-liquid separator 22 and flows it out to the refrigerant inlet side of the suction-side evaporator 19.

  The suction-side pressure reducing device 15e introduces an inlet-side introduction pipe that introduces an inlet-side pressure Pni that is the pressure of the refrigerant flowing into the nozzle portion 14a, and a low-stage pressure Peo that is the pressure of the refrigerant that has flowed out of the suction-side evaporator 19. It has a low-stage introduction pipe to be introduced.

  The suction side pressure reducing device 15e is a fixed throttle when the pressure difference ΔP is larger than the reference pressure difference KΔP, and when the pressure difference ΔP is less than or equal to the reference pressure difference KΔP, Along with the reduction, it is composed of a mechanical mechanism that becomes a variable throttle that increases the throttle opening. Other configurations of the ejector refrigeration cycle 10a are the same as those of the ejector refrigeration cycle 10 described in the first embodiment.

  Next, the operation of the ejector refrigeration cycle 10a in the above configuration will be described. In the present embodiment, an operation condition in which the pressure difference ΔP is larger than the reference pressure difference KΔP is a normal operation, and an operation condition in which the pressure difference ΔP is less than or equal to the reference pressure difference KΔP is a low load operation.

  When the air conditioning control device 40 operates the compressor 11, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed. The refrigerant that has flowed out of the radiator 12 flows into the nozzle portion 14 a of the ejector 14.

  The refrigerant that has flowed into the nozzle portion 14a of the ejector 14 is decompressed in an isentropic manner at the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. And the refrigerant | coolant which flowed out from the suction side evaporator 19 is attracted | sucked from the refrigerant | coolant suction opening 14c by the suction effect | action of an injection refrigerant | coolant.

  The injection refrigerant injected from the refrigerant injection port of the nozzle portion 14a and the suction refrigerant sucked from the refrigerant suction port 14c flow into the diffuser portion 14d. The refrigerant whose pressure has been increased by the diffuser section 14 d flows into the gas-liquid separator 22. The gas-phase refrigerant separated by the gas-liquid separator 22 is sucked into the compressor 11 and compressed again. On the other hand, the liquid-phase refrigerant separated by the gas-liquid separator 22 flows into the suction side decompression device 15e.

  At this time, during normal operation, the suction side pressure reducing device 15e is a fixed throttle. Further, at the time of low load operation, the suction side pressure reducing device 15e becomes a variable throttle that increases the throttle opening as compared with the normal operation as the pressure difference ΔP decreases. The refrigerant decompressed by the suction side decompression device 15 e flows into the suction side evaporator 19.

  The refrigerant flowing into the suction side evaporator 19 absorbs heat from the blown air blown by the indoor blower 18a and evaporates. Thereby, the blowing air blown by the indoor blower 18a is cooled. The refrigerant that has flowed out of the suction side evaporator 19 is sucked from the refrigerant suction port 14c.

  Therefore, according to the ejector refrigeration cycle 10a of the present embodiment, the blown air blown into the vehicle interior by the suction-side evaporator 19 during normal operation and low load operation regardless of load fluctuations. Can be cooled.

  Furthermore, since the ejector-type refrigeration cycle 10a includes the suction side pressure reducing device 15e, the throttle opening can be increased as the pressure difference ΔP is reduced during low-load operation. Therefore, similarly to the first embodiment, it is possible to suppress a shortage of the flow rate of the refrigerant flowing into the suction side evaporator 19 during the low load operation.

  Further, similarly to the suction side pressure reducing device 15b described in the third embodiment, when the inlet side pressure Pni is larger than the reference inlet side pressure KPni, the ejector refrigeration cycle 10a becomes a fixed throttle. When the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, the suction side pressure reduction configured by a mechanical mechanism that becomes a variable throttle that increases the throttle opening degree as the inlet side pressure Pni is reduced. May be adopted. According to this, the same effect as the third embodiment can be obtained.

(Seventh embodiment)
In the present embodiment, an example will be described in which a damper portion 54 is added to the suction-side decompression device 15c of the ejector module 20 described in the fourth embodiment, as shown in FIGS. 16 and 17 correspond to FIGS. 12 and 13 described in the fourth embodiment, respectively.

  The damper part 54 delays the change of the throttle opening degree of the suction side pressure reducing device 15c with respect to the change of the inlet side pressure Pni. More specifically, the damper portion 54 of the present embodiment generates a resistance force that hinders the displacement of the valve body portion 52 when the pressure difference ΔP changes with the change of the inlet side pressure Pni. The displacement speed of 52 is reduced.

  The damper portion 54 has an oil space forming member 54a and a ring member 54c. The oil space forming member 54a, together with the valve body 52, forms an oil space 50e in which oil is enclosed. The ring member 54c prevents oil from flowing in the oil space 50e.

  The oil space forming member 54 a is made of the same material as the valve body 52 and is formed in a substantially cylindrical shape similar to the valve body 52. At the end of the oil space forming portion 54a away from the regular throttle passage 50a and the like (in this embodiment, the other end side in the axial direction of the oil space forming member 54a) An enlarged diameter portion 54b having the same diameter as the enlarged diameter portion 52b formed on the end side is formed.

  One axial end side of the oil space forming portion 54a is fixed to the other axial end side of the valve body portion 52 by means such as press fitting or screwing. At this time, the central axis of the valve body 52 and the central axis of the oil space forming portion 54a are arranged coaxially. Further, the enlarged diameter portion 52b of the valve body portion 52 and the enlarged diameter portion 54b of the oil space forming member 54a are arranged with an interval in the axial direction.

  A seal member such as an O-ring is interposed in the gap between the inner peripheral surface of the body 21 and the outer peripheral surfaces of the enlarged diameter portions 52b and 54b. Therefore, the refrigerant does not leak from the gap between these members. For this reason, an annular sealed space surrounded by the inner peripheral surface of the body 21, the valve body 52, and the oil space forming member 54a is formed inside the body 21. In the present embodiment, this sealed space is the oil space 50e. And oil, such as mineral oil, is enclosed in the oil space 50e.

  Further, an annular ring member 54c is fixed to an inner peripheral surface of a portion of the body 21 that forms the oil space 50e. For this reason, when the valve body 52 and the oil space forming member 54a are displaced, the oil flows through the gap between the inner peripheral surface of the ring member 54c and the outer peripheral surface of the oil space forming member 54a.

  The resistance force when oil flows through the gap between the inner peripheral surface of the ring member 54c and the outer peripheral surface of the oil space forming member 54a becomes a resistance force that hinders the displacement of the valve body 52 and the oil space forming member 54a. . In FIG. 16 and FIG. 17, the enclosed oil is indicated by dot hatching for clarity of illustration.

  Other configurations and operations of the ejector module 20 are the same as those in the fourth embodiment. Therefore, also in the ejector type refrigeration cycle 10 including the ejector module 20 of the present embodiment, the same effect as that of the fourth embodiment can be obtained.

  Furthermore, since the ejector module 20 of the present embodiment includes the damper portion 54, even if the pressure difference ΔP suddenly changes, it is possible to prevent the throttle opening degree of the suction side pressure reducing device 15c from changing suddenly. In addition, the throttle opening degree of the suction side decompression unit can be appropriately changed.

(Eighth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 18, an example in which a suction side pressure reducing unit having a Joule heat type on-off valve 60 will be described. The on-off valve 60 is configured by an electrical mechanism that opens and closes the refrigerant passage when supplied with electric power. The electric mechanism is a mechanism that displaces the valve body portion and the like when electric power is supplied. The opening / closing operation of the opening / closing valve 60 is controlled by a control voltage output from the air conditioning control device 40.

  The Joule heat type on-off valve 60 has a valve body portion that opens and closes the refrigerant passage, and a thermal deformation portion that thermally expands due to Joule heat generated when electric power is supplied. Then, the deformation of the thermally deformable portion is transmitted to the valve body portion to displace the valve body portion, thereby opening and closing the refrigerant passage.

  More specifically, a regular throttle passage 50a and an auxiliary throttle passage 50b connected in parallel to each other are formed in the Joule heat type on-off valve 60 of the present embodiment. The valve body functions to open and close the auxiliary throttle passage 50b. The thermal deformation portion is made of metal or silicon. The deformation of the thermal deformation portion is transmitted to the valve body portion via the arm portion.

  The arm part is formed in an elongated shape. One end of the arm is fixed to the main body of the on-off valve 60. A valve body is disposed at the other end of the arm. Furthermore, the thermal deformation part is connected to the longitudinal intermediate position of the arm part. For this reason, when the arm portion is displaced along with the deformation of the thermally deformable portion, the amount of deformation of the thermally deformable portion is amplified and transmitted to the valve body portion by the action of the lever having one end portion of the arm portion as a fulcrum.

  Furthermore, as shown in FIG. 18, an inlet-side pressure sensor 41a and a low-stage pressure sensor 41b are connected to the input side of the air-conditioning control device 40 of the present embodiment. The inlet side pressure sensor 41a is an inlet side pressure detector that detects the inlet side pressure Pni. The low-stage pressure sensor 41b is a low-stage pressure detector that detects the low-stage pressure Peo. Other configurations of the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Next, the operation of this embodiment in the above configuration will be described. The air conditioning control device 40 of the present embodiment does not supply power to the on-off valve 60 during normal operation where the pressure difference ΔP is greater than the reference pressure difference KΔP. For this reason, only the regular throttle passage 50a is open in the on-off valve 60 during normal operation. As a result, during normal operation, the operation is the same as in the first embodiment.

  Further, the air conditioning control device 40 supplies power to the on-off valve 60 during low load operation in which the pressure difference ΔP is equal to or less than the reference pressure difference KΔP. For this reason, both the regular throttle passage 50a and the auxiliary throttle passage 50b are open in the on-off valve 60 during low load operation. As a result, at the time of low load operation, the operation is the same as in the first embodiment.

  Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, the same effects as those of the first embodiment can be obtained. Further, in the present embodiment, since the Joule heat type on-off valve 60 is adopted as the suction side pressure reducing unit, an electric expansion valve or a solenoid type equipped with a stepping motor or the like capable of adjusting the throttle opening degree with high accuracy. In contrast to the case where an on-off valve or the like is employed, it is possible to reduce the size of the suction-side decompression unit and to save power.

  That is, according to the ejector-type refrigeration cycle 10 of the present embodiment, the on-off valve 60 is employed as the suction-side decompression unit, so that the suction-side decompression unit can be adjusted according to cycle load fluctuations without increasing the size. It is possible to appropriately change the throttle opening degree.

(Ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 19, as compared with the eighth embodiment, a fixed throttle 62 corresponding to the regular throttle passage 50a and a Joule heat type on-off valve 60a are provided as a suction side pressure reducing unit. The example which employ | adopted what has is demonstrated.

  As shown in FIG. 19, the on-off valve 60a and the fixed throttle 62 are connected in parallel to the refrigerant flow. In the on-off valve 60a, the regular throttle passage 50a is eliminated. Other configurations and operations of the on-off valve 60a and the ejector refrigeration cycle 10 are the same as those in the eighth embodiment.

  Accordingly, the ejector refrigeration cycle 10 of the present embodiment operates in the same manner as in the eighth embodiment, and the same effects as in the eighth embodiment can be obtained.

(10th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 20, an example in which the fixed aperture 60 is omitted from the ninth embodiment will be described. Other configurations of the ejector refrigeration cycle 10 are the same as those in the ninth embodiment.

  The air conditioning control device 40 of this embodiment controls the operation of the on-off valve 60a by pulse width modulation control (so-called PWM control). In the pulse width modulation control, the substantial passage cross-sectional area of the on-off valve 60a can be changed by energizing and de-energizing at a constant period and changing the ratio of the energizing time in one period.

  More specifically, in the present embodiment, as shown in FIG. 21, the pressure difference ΔP is larger than the ratio of the energization time during normal operation in which the pressure difference ΔP is larger than the reference pressure difference KΔP. Increase the proportion of energization time during low-load operation as follows. Thereby, the substantial passage cross-sectional area (that is, the throttle opening) of the on-off valve 60a at the time of low load operation is increased more than that at the time of normal operation.

  Even if the pulse width modulation control such as the air conditioning control device 40 of the present embodiment is executed, the same effect as in the first embodiment can be obtained. Further, in the present embodiment, since the on-off valve 60a is employed as the suction-side decompression unit, the responsiveness of opening and closing the refrigerant passage is higher than when a solenoid-type on-off valve or the like is employed, and the suction-side decompression unit. The cross-sectional area of the passage (that is, the throttle opening) can be changed more appropriately.

(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 first, second, and fourth embodiments described above, the pressure of the refrigerant that has flowed out of the suction side evaporator 19 is adopted as the low stage side pressure Peo. It is not limited to. The low stage side pressure Peo may be the pressure of the refrigerant that has flowed out of the suction side pressure reducing devices 15, 15a, 15c. More specifically, the pressure of the refrigerant flowing through the refrigerant flow path from the outlet of the suction side pressure reducing devices 15, 15a, 15c to the refrigerant outlet of the ejector 14 may be used.

  Further, in the above-described embodiment, the reference pressure difference KΔP and the reference inlet side pressure KPni are determined based on the pressure difference ΔP or the inlet side pressure Pni at which the cooling capacity in the suction side evaporator 19 is not sufficiently exhibited. However, the determination of the reference pressure difference KΔP and the reference inlet side pressure KPni is not limited to this.

  For example, the temperature difference of the blown air cooled by the suction side evaporator 19 may be determined to be a value slightly higher than the pressure difference ΔP or the inlet side pressure Pni at which the temperature difference becomes larger than the reference temperature difference. The temperature distribution of the blown air is defined by a temperature difference obtained by subtracting the minimum temperature from the maximum temperature of the blown air immediately after being cooled by the suction side evaporator 19. The reference temperature difference may be set to a value at which the occupant begins to feel uncomfortable due to the temperature distribution.

  (2) The suction side decompression unit is not limited to the suction side decompression devices 15 to 15d and the on-off valves 60 and 60a disclosed in the above-described embodiment. For example, in the above-described second and fifth embodiments, the example in which the pressure in the spring chamber 50d is the external pressure has been described, but the pressure in the spring chamber 50d is not limited to this. If the pressure in the spring chamber 50d can be made substantially constant, the spring chamber 50d may be evacuated.

  Further, in the suction side pressure reducing device 15, the same effect may be obtained by displacing the bottom 51b side as a valve body portion like a so-called poppet valve. Further, like the so-called spool valve, the auxiliary throttle passage 50b may be opened and closed by the cylindrical side surfaces of the enlarged diameter portions 52b and 52c.

  In the suction side pressure reducing device 15c, the example in which the auxiliary throttle passage 50b is configured by one refrigerant passage has been described. However, the auxiliary throttle passage 50b may be configured by a plurality of refrigerant passages. And according to the displacement of the valve body part 52, you may make it change a throttle opening by changing the number of the refrigerant paths to open.

  Further, a suction side pressure reducing device that selectively opens and closes the regular throttle passage 50a and the auxiliary throttle passage 50b may be employed. That is, it is possible to employ one that opens one of the regular throttle passage 50a and the auxiliary throttle passage 50b and closes the other. In this case, the passage sectional area of the auxiliary throttle passage 50b may be set larger than the passage sectional area of the regular throttle passage 50a.

  In addition, a ball valve that changes the cross-sectional area of the passage by changing the angle of the spherical or cylindrical valve body may be adopted as the suction side pressure reducing device. An orifice corresponding to the regular throttle passage 50a may be formed in the valve body 50a.

  In the above-described eighth to tenth embodiments, an example in which a Joule heat type is employed as the on-off valves 60, 60a has been described, but a solenoid type solenoid valve may of course be employed.

  Furthermore, since the Joule heat type on-off valves 60 and 60a can be formed in a relatively thin plate shape, they may be integrated with other cycle components. For example, the Joule heat type on-off valves 60 and 60 a may be integrated with at least one of the branch portion 13, the ejector 14, the outflow side evaporator 18, and the suction side evaporator 19.

  (3) In the above-described seventh embodiment, the example in which the damper portion 54 is added to the suction-side decompression device 15c of the ejector module 20 described in the fourth embodiment has been described. Of course, the connection is made in the fifth embodiment. A damper portion 54 may be added to the suction side pressure reducing device 15d. In this case, the damper portion 54 functions to reduce the displacement speed of the valve body portion 52 by generating a resistance force that prevents the displacement of the valve body portion 52 when the inlet side pressure Pni changes.

  In addition, a configuration in which the damper portion 54 is added to the suction-side decompression device 15c described in the seventh embodiment, and a configuration in which the damper portion 54 is added to the suction-side decompression device 15d in the fifth embodiment are the centrifugal branching portion 13a and It may be separated from the ejector 14. And what added the damper part 54 to the suction side decompression device 15c, and what added the damper part 54 to the suction side decompression device 15d of 5th Embodiment of the ejector-type refrigerating cycle 10 demonstrated in 1st Embodiment. You may employ | adopt as a suction side pressure reduction part.

  (4) In the above-described eighth and ninth embodiments, the example in which the air conditioning control device 40 supplies power to the on-off valves 60 and 60a when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP has been described. However, the present invention is not limited to this. For example, when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, the air conditioning control device 40 may supply power to the on-off valves 60 and 60a. According to this, the same effect as the third embodiment can be obtained.

  Similarly, in the ejector refrigeration cycle 10 described in the tenth embodiment, when the inlet side pressure Pni is equal to or lower than the reference inlet side pressure KPni, the air conditioning control device 40 increases the ratio of the energization time. Also good.

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

  For example, in the above-described embodiment, an example in which an electric compressor is employed as the compressor 11 has been described. However, the compressor 11 is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like. An engine driven compressor may be employed. Furthermore, as an engine-driven compressor, the variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or the refrigerant discharge capacity can be adjusted by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch A fixed-capacity compressor can be employed.

  Moreover, in the above-mentioned embodiment, although the detailed structure of the heat radiator 12 is not mentioned, the receiver integrated condenser which has the receiver part (in other words, liquid receiver) which stores the condensed refrigerant | coolant as the heat radiator 12. FIG. May be adopted. Furthermore, you may employ | adopt what is called a subcool type | mold condenser comprised including the supercooling part which supercools the liquid-phase refrigerant | coolant which flowed out from the receiver part.

  Moreover, although the above-mentioned 1st-3rd embodiment demonstrated the example which employ | adopted the thing of a three-way joint structure as the branch part 13, the branch part 13 is not limited to this. For example, the ejector refrigeration cycle 10 of the first to third embodiments may employ a centrifugal gas-liquid separator structure similar to the centrifugal branching portion 13a.

  In the above-described embodiment, the example in which the outflow side evaporator 18 and the suction side evaporator 19 are integrally configured has been described. However, the outflow side evaporator 18 and the suction side evaporator 19 are configured separately. Also good. And in the outflow side evaporator 18 and the suction side evaporator 19, different refrigerant target fluids may be cooled in different temperature zones.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted R134a as a refrigerant | coolant, a refrigerant | coolant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Or you may employ | adopt the mixed refrigerant | coolant etc. which mixed multiple types among these refrigerant | coolants. Furthermore, 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.

  (6) In each above-mentioned embodiment, although ejector type refrigerating cycle 10 concerning the present invention was applied to a vehicle air conditioner, application of ejector type refrigerating cycle 10 is not limited to this. For example, the present invention may be applied to stationary air conditioners, cold storages, other cooling and heating devices, and the like.

DESCRIPTION OF SYMBOLS 10, 10a Ejector type refrigeration cycle 11 Compressor 12 Radiator 14 Ejector 14a Nozzle part 14c Refrigerant suction port 15-15e Suction side decompression device (suction side decompression part)
19 Suction side evaporator 20 Ejector module 60, 60a On-off valve (suction side pressure reducing part)

Claims (13)

A compressor (11) for compressing and discharging the refrigerant;
A radiator (12) for dissipating heat from the refrigerant discharged from the compressor;
The refrigerant sucked from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle part (14a) for depressurizing the refrigerant flowing out of the radiator, and sucked from the jetted refrigerant and the refrigerant suction port An ejector (14) for increasing the pressure of the refrigerant mixed with the refrigerant;
A suction side decompression section (15, 15a-15e, 60, 60a) for decompressing the refrigerant;
A suction side evaporator (19) for evaporating the refrigerant depressurized by the suction side decompression unit and causing the refrigerant to flow out to the refrigerant suction port side,
The suction-side decompression unit is an ejector-type refrigeration cycle that changes the throttle opening based on an inlet-side pressure (Pni) that is a pressure of a refrigerant flowing into the nozzle unit.   The suction side decompression unit is configured to reduce the pressure difference (ΔP) by subtracting the low stage side pressure (Peo) that is the pressure of the refrigerant flowing out from the suction side decompression unit from the inlet side pressure (Pni). The ejector-type refrigeration cycle according to claim 1, further comprising a mechanical mechanism for increasing the opening.   The ejector refrigeration cycle according to claim 2, wherein the low-stage pressure is a pressure of a refrigerant flowing out of the suction-side evaporator.   2. The ejector refrigeration cycle according to claim 1, wherein the suction side pressure reducing unit has a mechanical mechanism that increases a throttle opening as the inlet side pressure (Pni) decreases.   The ejector according to any one of claims 1 to 4, wherein the suction side pressure reducing unit includes a damper portion (54) for delaying a change in the throttle opening with respect to a change in the inlet side pressure (Pni). Refrigeration cycle.   The ejector-type refrigeration cycle according to claim 1, wherein the suction-side decompression unit has an electrical mechanism that opens and closes a refrigerant passage when supplied with electric power.   The electrical mechanism has a valve body part that opens and closes the refrigerant passage, and a thermal deformation part that thermally expands by Joule heat, and transmits the deformation of the thermal deformation part to the valve body part. The ejector-type refrigeration cycle according to claim 6, wherein the ejector-type refrigeration cycle is of a Joule heat type that displaces. A branch part (13) for branching the flow of the refrigerant flowing out of the radiator,
The inlet side of the nozzle part is connected to one outlet of the branch part (13),
The ejector-type refrigeration cycle according to any one of claims 1 to 7, wherein an inlet side of the suction side decompression unit is connected to the other outlet of the branch part (13). An ejector refrigeration cycle (10) having a compressor (11) that compresses and discharges refrigerant, a radiator (12) that dissipates heat from the refrigerant discharged from the compressor, and a suction side evaporator (19) that evaporates the refrigerant. ) Ejector module applied to
A nozzle part (14a) for depressurizing and injecting a part of the refrigerant flowing out of the radiator;
A suction side decompression section (15c) for decompressing another part of the refrigerant flowing out of the radiator;
A body part (21) formed with a suction refrigerant inlet (21a) for allowing the refrigerant flowing out of the suction side evaporator to flow in due to the suction action of the jet refrigerant injected from the nozzle part;
A pressure increasing unit (14d) for increasing the pressure of the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port;
The suction side decompression unit is an ejector module that changes a throttle opening based on an inlet side pressure (Pni) that is a pressure of a refrigerant flowing into the nozzle unit.   The suction-side decompression unit reduces the throttle opening as the pressure difference is reduced by subtracting the low-stage pressure (Peo), which is the pressure of the refrigerant flowing out from the suction-side decompression unit, from the inlet-side pressure (Pni). The ejector module according to claim 9, comprising an increasing mechanical mechanism.   The ejector module according to claim 10, wherein the low-stage pressure is a pressure of the refrigerant sucked from the refrigerant suction port.   The ejector module according to claim 9, wherein the suction side pressure reducing unit includes a mechanical mechanism that increases a throttle opening as the inlet side pressure (Pni) decreases.   The ejector according to any one of claims 9 to 12, wherein the suction side pressure reducing unit includes a damper portion (54) for delaying a change in the throttle opening with respect to a change in the inlet side pressure (Pni). module.

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