JP7119785B2 - Ejector refrigeration cycle and ejector module - Google Patents

Description

The present invention relates to an ejector refrigerating cycle having an ejector and an ejector module applied to the ejector refrigerating cycle.

2. Description of the Related Art Conventionally, an ejector-type refrigerating cycle, which is a vapor compression-type refrigerating cycle provided with an ejector, is known. In this type of ejector-type refrigerating cycle, the pressurizing action of the diffuser portion of the ejector can increase the pressure of the refrigerant sucked into the compressor. As a result, in the ejector 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 Literature 1 discloses an ejector-type refrigeration cycle that is applied to an air conditioner and cools air that is blown into an air-conditioned space.

More specifically, the ejector-type refrigeration cycle of Patent Document 1 includes a branching portion that branches the flow of high-pressure refrigerant that has flowed out from a radiator, and a suction-side evaporator that evaporates the low-pressure refrigerant and cools the blown air. there is One of the refrigerants branched at the branching portion is made to flow into the nozzle portion of the ejector, and the other refrigerant branched at the branching portion is decompressed by the suction side decompression portion and flowed into the suction side evaporator. Furthermore, the cycle configuration is such that the refrigerant flowing out from the suction-side evaporator is sucked from the refrigerant suction port of the ejector.

Further, in Patent Document 1, there is an example in which a fixed throttle with a fixed throttle opening is adopted as a suction-side decompression unit, and the degree of superheat of the refrigerant on the outlet side of the suction-side evaporator approaches a predetermined reference degree of superheat. Also disclosed is an example employing a thermal expansion valve for adjusting the throttle opening, and an example employing an electric variable throttle device capable of adjusting the throttle opening by a control signal output from a control device.

Japanese Patent No. 5217121

However, when a fixed throttle is adopted as the suction side decompression section as in Patent Document 1, the cooling capacity of the suction side evaporator can be sufficiently exhibited during normal operation, but the cooling capacity of the suction side evaporator can be sufficiently exhibited during normal operation, but the air 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. In addition, if a thermal expansion valve is used as the suction side pressure reducing section, the flow rate of the refrigerant flowing into the suction side evaporator decreases during low load operation, etc., and the temperature of the air cooled by the suction side evaporator decreases. The distribution may have widened.

Further, if an electric variable throttle device is adopted as the suction side decompression unit, not only does the suction side decompression unit become large, but a sensor or the like for outputting a signal for controlling the operation of the electric variable throttle device is required. Since it is necessary, it invites an increase in the size of the entire ejector type refrigeration cycle. In addition, complicated control is required to adjust the throttle opening of the electric variable throttle device according to cycle load fluctuations.

SUMMARY OF THE INVENTION An object of the present invention is to provide an ejector-type refrigeration cycle capable of appropriately changing the throttle opening of a suction-side decompression unit in accordance with the heat load of the cycle.

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

In order to achieve the above object, the invention according to claim 1 provides a compressor (11) for compressing and discharging refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and Refrigerant is sucked from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle portion (14a) for decompressing the flowing out refrigerant, and the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port is produced. An ejector (14) for increasing the pressure, a suction side decompression section ( 15, 15a, 15c, 15e ) for decompressing the refrigerant, and a suction for evaporating the refrigerant decompressed by the suction side decompression section and flowing out to the refrigerant suction port side. a side evaporator (19),
The suction side decompression section changes the throttle opening based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section . It has a mechanical mechanism that increases the throttle opening as the pressure difference (ΔP) obtained by subtracting the low-stage pressure (Peo), which is the pressure of the refrigerant flowing out from the It is an ejector-type refrigerating cycle, which is the pressure of the refrigerant that has flowed out of the suction-side evaporator .

According to this, the suction side pressure reducing section (15... 15e ) changes the opening degree of the throttle based on the inlet side pressure (Pni), so that the suction side pressure reducing section (15... 15e ) changes according to the load fluctuation of the cycle. It is possible to provide an ejector-type refrigerating cycle capable of appropriately changing the opening of the throttle.

In addition , the suction side pressure reducing section (15... 15e ) has an inlet side pressure (Pni) which is the pressure of the refrigerant flowing into the nozzle section, and a low stage side pressure (Peo) which is the pressure of the refrigerant flowing out from the suction side pressure reducing section. It has a mechanical mechanism that increases the throttle opening as the pressure difference (ΔP) that is subtracted from is reduced.

According to this, the suction side decompression section (15...15e) increases the throttle opening as the pressure difference (.DELTA.P) decreases. In addition, the aperture opening can be increased. Therefore, it is possible to prevent the flow rate of the refrigerant flowing into the suction side evaporator (19) from becoming insufficient during low-load operation.

Furthermore, since the suction-side decompression units (15...15e) have a mechanical mechanism that changes the opening of the throttle according to the pressure difference (ΔP), complicated configuration and control are required to change the opening of the throttle. etc. is not required. Therefore, it is possible to provide an ejector-type refrigerating cycle that can appropriately change the throttle opening of the suction-side decompression units (15 . . . 15e) according to the load fluctuation of the cycle with a simple configuration.

Further, the invention according to claim 3 comprises a compressor (11) for compressing and discharging the refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and reducing the pressure of the refrigerant discharged from the radiator. The ejector (14) sucks the refrigerant from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle portion (14a) to increase the pressure of the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port. ), a suction side decompression section (15c, 15d) that decompresses the refrigerant, and a suction side evaporator (19) that evaporates the refrigerant decompressed by the suction side decompression section and causes it to flow out to the refrigerant suction port side. prepared,
The suction side decompression section changes the throttle opening based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section. It is an ejector type refrigeration cycle having a damper section (54) that delays temperature change.
According to this, the same effect as the invention described in claim 1 can be obtained.
In the ejector type refrigerating cycle having the characteristics described above, the suction side pressure reducing section ( 15d ) is a machine that increases the throttle opening as the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section, decreases. It may have a functional mechanism.

According to this, the suction side decompression section ( 15d ) increases the throttle opening as the inlet side pressure (Pni) drops, so when the inlet side pressure (Pni) drops like during low-load operation, In addition, the aperture opening can be increased. Therefore, it is possible to prevent the flow rate of the refrigerant flowing into the suction side evaporator (19) from becoming insufficient during low-load operation.

Furthermore, since the suction side decompression section ( 15d ) has a mechanical mechanism that changes the throttle opening in accordance with the inlet side pressure (Pni), a complicated configuration, control, etc. are necessary to change the throttle opening. is not required. Therefore, it is possible to provide an ejector-type refrigeration cycle with a simple structure that can appropriately change the throttle opening of the suction side pressure reducing section ( 15d ) according to the load fluctuation of the cycle.

Further, the invention according to claim 6 comprises a compressor (11) for compressing and discharging refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and a suction side evaporator ( 19) An ejector module applied to an ejector refrigeration cycle (10) having
A nozzle portion (14a) for reducing the pressure of a part of the refrigerant flowing out of the radiator and injecting the refrigerant, and a suction side pressure reducing portion ( 15c) for reducing the pressure of another part of the refrigerant flowing out of the radiator. a body portion (21) formed with a suction refrigerant inlet (21a) into which the refrigerant flowing out of the suction side evaporator flows due to the suction action of the injection refrigerant injected from the nozzle portion; a pressurizing section (14d) for pressurizing the mixed refrigerant with the sucked refrigerant,
The suction side decompression section changes the aperture opening degree based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section ,
The suction-side decompression unit has a mechanical mechanism that increases the opening of the throttle as the pressure difference obtained by subtracting the low-stage pressure (Peo), which is the pressure of the refrigerant flowing out of the suction-side decompression unit, from the inlet-side pressure decreases. and the low stage pressure is the ejector module pressure which is the pressure of the refrigerant sucked from the suction refrigerant inlet .

According to this, the suction side decompression section (15c) changes the throttle opening based on the inlet side pressure ( Pni ). Accordingly, it is possible to provide an ejector module capable of appropriately changing the throttle opening of the suction side decompression section ( 15c) .

Further , the suction side decompression section (15c) subtracts the low stage side pressure (Peo), which is the pressure of the refrigerant flowing out from the suction side decompression section, from the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section. It has a mechanical mechanism that increases the throttle opening as the pressure difference is reduced .

According to this, the suction-side decompression section (15c) increases the throttle opening as the pressure difference (ΔP) decreases, so the applied ejector-type refrigeration cycle (10) is in low-load operation. The throttle opening can be increased when the pressure difference (.DELTA.P) is reduced, as is the case. Therefore, it is possible to prevent the flow rate of the refrigerant flowing out to the suction side evaporator (19) from becoming insufficient during low-load operation.

Furthermore, since the suction side decompression section (15c) has a mechanical mechanism that changes the opening of the throttle in accordance with the pressure difference (ΔP), a complicated configuration and control are required to increase the opening of the throttle. I don't even need it. Therefore, when applied to an ejector type refrigerating cycle (10), it provides an ejector module that can appropriately change the throttle opening of the suction side pressure reducing section (15c) according to the load fluctuation of the cycle with a simple configuration. can do.

Further, according to the eighth aspect of the invention, there is provided a compressor (11) for compressing and discharging refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and a suction side evaporator ( 19) An ejector module applied to an ejector refrigeration cycle (10) having
A nozzle part (14a) for reducing the pressure of a part of the refrigerant flowing out of the radiator and injecting the refrigerant, and a suction side pressure reducing part (15d) for reducing the pressure of another part of the refrigerant flowing out of the radiator. a body portion (21) formed with a suction refrigerant inlet (21a) into which the refrigerant flowing out of the suction side evaporator by the suction action of the injection refrigerant injected from the nozzle portion is formed; a pressurizing section (14d) for pressurizing the mixed refrigerant with the sucked refrigerant,
The suction side decompression section changes the throttle opening based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section, and the suction side decompression section changes the inlet side pressure (Pni). It is an ejector module having a damper section (54) that delays the change in the opening degree of the diaphragm.
According to this, the same effect as the sixth aspect of the invention can be obtained.
Further, in the ejector module having the above characteristics, the suction side pressure reducing section (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 section, decreases. may have

According to this, the suction side decompression section (15d) increases the throttle opening as the inlet side pressure (Pni) decreases, so that the applied ejector type refrigeration cycle (10) operates at a low load. When the inlet side pressure (Pni) is lowered as in the case where the valve is closed, the opening of the throttle can be increased. Therefore, it is possible to prevent the flow rate of the refrigerant flowing out to the suction side evaporator (19) from becoming insufficient during low-load operation.

Furthermore, since the suction side decompression section (15d) is composed of a mechanical mechanism that changes the throttle opening in accordance with the inlet side pressure (Pni), a complicated configuration, control, etc. are required to increase the throttle opening. is not required. Therefore, when applied to an ejector type refrigerating cycle (10), it is possible to provide an ejector module that can appropriately change the throttle opening of the suction side pressure reducing section (15d) according to the load fluctuation of the cycle with a simple configuration. 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 the supply of electric power. "Electrical mechanism" means a mechanism that operates when electric power is supplied.

Also, the reference numerals in parentheses of each means described in this column and the scope of claims are examples showing the correspondence with specific means described in the embodiments described later.

1 is an overall configuration diagram of an ejector-type refrigerating cycle according to a first embodiment; FIG. FIG. 4 is a schematic cross-sectional view of the suction-side decompression device of the first embodiment when the throttle opening is minimized; FIG. 4 is a schematic cross-sectional view of the suction-side decompression device of the first embodiment when the throttle opening is maximized; It is a graph which shows the relationship between the pressure difference and throttle opening in the suction side decompression device of 1st Embodiment. FIG. 11 is a schematic cross-sectional view of the suction-side decompression device of the second embodiment when the throttle opening is minimized; FIG. 11 is a schematic cross-sectional view of the suction-side decompression device of the second embodiment when the throttle opening is maximized; FIG. 11 is a schematic cross-sectional view of the suction-side decompression device of the third embodiment when the throttle opening is minimized; FIG. 11 is a schematic cross-sectional view of the suction-side decompression device of the third embodiment when the throttle opening is maximized; It is a graph which shows the relationship between the entrance side pressure and throttle opening in the suction side decompression device of 3rd Embodiment. 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. FIG. 12 is a cross-sectional view taken along line XII-XII in FIG. 11, and is a cross-sectional view when the throttle opening degree of the suction side decompression section of the ejector module of the fourth embodiment is minimized. FIG. 12 is a cross-sectional view taken along line XII-XII in FIG. 11, and is a cross-sectional view when the throttle opening degree of the suction side decompression section of the ejector module of the fourth embodiment is maximized. FIG. 12 is a cross-sectional view of the ejector module of the fifth embodiment when the throttle opening degree of the suction-side decompression section is minimized; It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. FIG. 20 is a cross-sectional view of the ejector module of the seventh embodiment when the throttle opening degree of the suction side decompression section is minimized; FIG. 20 is a cross-sectional view of the ejector module of the seventh embodiment when the throttle opening degree of the suction-side decompression section is maximized; FIG. 11 is an overall configuration diagram of an ejector-type refrigerating cycle according to an eighth embodiment; FIG. 11 is an overall configuration diagram of an ejector-type refrigerating cycle according to a ninth embodiment; FIG. 11 is an overall configuration diagram of an ejector-type refrigerating cycle according to a tenth embodiment; FIG. 14 is a time chart showing the state of energization of the on-off valve for pulse width modulation control executed in the tenth embodiment; FIG.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. 1 to 4. FIG. The ejector-type refrigerating cycle 10 of this embodiment is applied to a vehicle air conditioner, and has a function of cooling air blown into a vehicle interior, which is a space to be air-conditioned. Therefore, the fluid to be cooled by the ejector type refrigerating cycle 10 is blown air.

The ejector-type refrigerating cycle 10 employs an HFC-based refrigerant (specifically, R134a) as a refrigerant, and constitutes a subcritical refrigerating cycle in which the refrigerant pressure on the high-pressure side of the cycle does not exceed the critical pressure of the refrigerant. Further, the refrigerant contains refrigerating machine oil for lubricating the compressor 11 . Also, part of the refrigerating machine oil circulates through the cycle together with the refrigerant.

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

Various compression mechanisms such as a scroll compression mechanism and a vane compression mechanism can be used as the compression mechanism. Further, the electric motor has its rotation speed (that is, refrigerant discharge capacity) controlled by a control signal output from the air conditioning control device 40. Either an AC motor or a DC motor may be used. good.

A refrigerant inlet side of a radiator 12 is connected to a discharge port of the compressor 11 . The radiator 12 is a condensing heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the outside air (outside air) blown by the cooling fan 12a to radiate and condense the high-pressure refrigerant. The cooling fan 12 a is an electric blower whose rotation speed (blown air volume) 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 branching portion 13 branches the flow of the refrigerant flowing out from 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 port of the branch portion 13 is connected to the inlet side of the nozzle portion 14 a of the ejector 14 . The other refrigerant outlet port of the branch portion 13 is connected to the high-pressure side inlet 51a side of the suction side decompression device 15 .

The ejector 14 has a nozzle portion 14a for depressurizing and injecting the refrigerant flowing out from the radiator 12, and functions as a refrigerant pressure reducing portion. Further, the ejector 14 functions as a refrigerant circulation section that draws and circulates the refrigerant from the outside by the suction action of the injection 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 injected refrigerant injected from the nozzle portion 14a and the sucked refrigerant sucked from the refrigerant suction port 14c into pressure energy, and energy conversion for raising the pressure of the mixed refrigerant. functions as a department.

More specifically, the ejector 14 has a nozzle portion 14a and a body portion 14b. The nozzle portion 14a is made of a substantially cylindrical metal (stainless alloy in this embodiment) or the like that gradually tapers in the flow direction of the coolant. The nozzle portion 14a decompresses the refrigerant isentropically in a refrigerant passage formed therein.

The coolant passage formed inside the nozzle portion 14a has a throat portion in which the cross-sectional area of the passage is reduced most, and a diverging portion in which the cross-sectional area of the passage gradually increases as it goes from the throat to the refrigerant injection port for injecting the refrigerant. is formed. That is, the nozzle portion 14a of this embodiment is configured as a Laval nozzle.

Further, in this embodiment, the nozzle portion 14a is set so that the flow velocity of the refrigerant injected from the refrigerant injection port during normal operation of the cycle is greater than or equal to the speed of sound. Of course, the nozzle portion 14a may be configured with a tapered nozzle.

The body portion 14b is made of a substantially cylindrical metal (aluminum in this embodiment). The body portion 14b functions as a fixing member for supporting and fixing the nozzle portion 14a inside, and forms an outer shell of the ejector 14. As shown in FIG. More specifically, the nozzle portion 14a is fixed by press fitting so as to be accommodated inside the body portion 14b on one end side in the longitudinal direction. The body portion 14b may be made of resin.

A refrigerant suction port 14c is formed on the outer peripheral surface of the body portion 14b at a portion corresponding to the outer peripheral side of the nozzle portion 14a so as to penetrate through the inside and outside thereof and communicate with the refrigerant injection port of the nozzle portion 14a. ing. The refrigerant suction port 14c is a through hole through which the refrigerant flowing out from the suction-side evaporator 19, which will be described later, is sucked into the ejector 14 by the suction action of the 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 portion 14d is a pressure increasing portion that mixes the suction refrigerant and the injection refrigerant to increase the pressure.

The suction passage is formed in the space between the outer peripheral side of the tapered distal end portion of the nozzle portion 14a and the inner peripheral side of the body portion 14b. gradually shrinking. As a result, the flow velocity of the suction refrigerant flowing through the suction passage is gradually increased to reduce the 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 in which a refrigerant passage extending like a truncated cone 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 expands toward the downstream side of the refrigerant flow. The diffuser portion 14d converts the kinetic energy of the mixed refrigerant into pressure energy due to such a passage shape.

More specifically, the cross-sectional shape of the inner peripheral wall surface of the body portion 14b forming the diffuser portion 14d of this embodiment is formed by combining a plurality of curved lines. Since the degree of expansion of the cross-sectional area of the refrigerant passage of the diffuser portion 14d gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be isoentropically pressurized.

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

The indoor blower 18 a is an electric blower whose number of revolutions (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 at the branch unit 13 until it becomes a low-pressure refrigerant and causes it to flow 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 pressure Pni is larger than the predetermined reference pressure difference KΔP, the suction side pressure reducing device 15 is closed to the fixed throttle. becomes. Furthermore, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, it is configured with a mechanical mechanism that functions as a variable throttle that increases the opening of the throttle as the pressure difference ΔP decreases.

Therefore, the suction side decompression device 15 changes the throttle opening based on the inlet side pressure Pni. Note that the mechanical mechanism is a mechanism that displaces the valve body or the like by a load due to fluid pressure, a load due to a spring, or the like, without requiring the 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 flowing out of the suction-side decompression device 15 (in this embodiment, the pressure of the refrigerant flowing out of the suction-side evaporator 19). The reference pressure difference KΔP is set to a value slightly larger than the pressure difference ΔP at which the cooling capacity of the suction-side evaporator 19 is not sufficiently exhibited when the suction-side decompression device 15 is at the minimum throttle opening. It is

A detailed configuration of the suction side decompression device 15 will be described with reference to FIGS. 2 to 4. FIG. The suction side decompression device 15 has a bottomed cylindrical body portion 51 . The body portion 51 is formed by combining a plurality of constituent members made of metal (made of aluminum in this embodiment). The body portion 51 forms the outer shell of the suction-side pressure reducing device 15 and also functions as a housing that accommodates the valve body portion 52 and the like therein. The body portion 21 may be made of resin.

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

A plurality of throttle passages 50a and 50b are formed in the bottom portion 51b to reduce the pressure of the refrigerant flowing from the high pressure side inlet 51a. As these throttle passages, a regular throttle passage 50a arranged in the center of the body portion 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 are provided. ing. The plurality of auxiliary throttle passages 50b are arranged around the central axis of the body portion 51 at equal angular intervals.

A side surface of the body portion 51 is formed with a pressure introduction port 51c and a pressure outlet port 51d. 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 lead-out port 51d is a coolant outlet that allows the coolant in the pressure lead-in space 50c to flow out toward the coolant suction port 14c side of the ejector 14 .

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

A communication passage 52a extending along the central axis is formed in the central portion of the valve body portion 52 . Therefore, 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 portion 52. As shown in FIG.

Both end portions of the valve body portion 52 are provided with enlarged diameter portions 52b and 52c that widen toward the outer peripheral side. 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 have 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 flowing 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 portion 51 from the high pressure side inlet 51a becomes equal to the inlet side pressure Pni. The pressure of the refrigerant that has flowed into the pressure introduction space 50c from the pressure introduction port 51c is the low-stage pressure Peo. The area of the pressure-receiving surface on the inlet side and the area of the pressure-receiving surface on the low-stage side are set substantially equal.

Sealing members such as O-rings are interposed between the inner peripheral surface of the body portion 51 and the outer peripheral surfaces of the enlarged diameter portions 52b and 52c, so that the refrigerant does not leak through the gaps between these members. Therefore, in the suction side pressure reducing device 15, the refrigerant flowing into the body portion 51 from the high pressure side inlet 51a and the refrigerant flowing into the pressure introducing space 50c from the pressure introducing port 51c are not mixed.

Further, the valve body portion 52 receives a load on the side of the high pressure side inlet 51a (that is, the side away from the bottom portion 51b) from a coil spring 53, which is an elastic member. A restricting member 51f that restricts the displaceable range of the valve body portion 52 is arranged inside the body portion 51 . This prevents the valve body portion 52 from falling off from the body portion 51 .

Therefore, the valve body portion 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 decompression device 15, when the pressure difference ΔP is greater than the reference pressure difference KΔP, the valve body portion 52 is displaced to compress the coil spring 53 as shown in FIG. and abut against the bottom portion 51b. This closes all the auxiliary throttle passages 50b. Therefore, the suction side decompression device 15 becomes a fixed throttle. At this time, the throttle opening of the suction-side decompression device 15 is determined by the cross-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 load of the coil spring 53 displaces the valve body portion 52 toward the high pressure side inlet 51a. 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 decompression device 15 is determined by the total value of the passage cross-sectional area of the regular throttle passage 50a and the inlet side opening area of the auxiliary throttle passage 50b.

Further, as shown in FIG. 3, as the pressure difference ΔP decreases, the valve body portion 52 displaces toward the high-pressure side inlet 51a until it comes into contact with the restricting member 51f, and 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 cross-sectional area of the normal throttle passage 50a and the auxiliary throttle passage 50b.

As a result, in the suction side decompression device 15 of the present embodiment, as shown in FIG. 4, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the throttle can be fixed. Further, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, the variable throttle is operated to increase the throttle opening as the pressure difference ΔP decreases until the inlet of the auxiliary throttle passage 50b is fully opened. can be Also, 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 decompression device 15 (specifically, the outlets of the throttle passages 50a and 50b). The suction-side evaporator 19 exchanges heat between the low-pressure refrigerant decompressed by the suction-side decompression device 15 and the blowing air that has passed through the outflow-side evaporator 18, evaporating the refrigerant to exhibit heat absorption, thereby reducing the heat of the blowing air. It is an endothermic heat exchanger that cools the

A 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 suction port 14 c side of the ejector 14 is connected to the pressure outlet port 51 d of the suction side decompression device 15 . That is, the refrigerant suction port 14 c side of the ejector 14 is connected to the refrigerant outlet of the suction side evaporator 19 via the pressure introduction space 50 c of the suction side decompression device 15 .

Also, the outflow side evaporator 18 and the suction side evaporator 19 of the present embodiment are configured integrally. Specifically, each of the outflow side evaporator 18 and the suction side evaporator 19 includes a plurality of tubes through which refrigerant flows, and collection or distribution of the refrigerant that is arranged on both end sides of the plurality of tubes and flows through the tubes. It is composed of a so-called tank-and-tube type heat exchanger, which has a pair of collecting and distributing tanks.

By forming the collecting and distributing tanks of the outflow-side evaporator 18 and the suction-side evaporator 19 from the same material, the outflow-side evaporator 18 and the suction-side evaporator 19 are integrated. In this embodiment, the outflow-side evaporator 18 and the suction-side evaporator 19 are arranged in series with respect to the blown air flow so that the outflow-side evaporator 18 is arranged upstream of the suction-side evaporator 19 in the blown air flow. are placed in Therefore, the blown air flows as indicated by the arrows drawn by the two-dot chain line in FIG.

Next, the electric control part of the ejector-type refrigerating cycle 10 of this embodiment is demonstrated. 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 processes based on an air-conditioning control program stored in the ROM. to control the operation of various controlled devices 11, 12a, and 18a connected to.

The input side of the air-conditioning control device 40 includes an inside air temperature sensor for detecting the vehicle interior temperature Tr, an outside air temperature sensor for detecting the outside air temperature Tam, a solar radiation sensor for detecting the amount of solar radiation As in the vehicle interior, and A sensor group for air conditioning control such as an evaporator temperature sensor for detecting the blown air temperature (evaporator temperature) Tefin is connected, and the detection values of these air conditioning sensor group 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 this operation panel are input to the air conditioning control device 40 . Various operation switches provided on the operation panel include an air conditioning operation switch for requesting air conditioning, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.

The air-conditioning control device 40 of the present embodiment is configured integrally with a control unit that controls the operation of various control target devices connected to the output side of the air-conditioning control device 40. A configuration (hardware and software) for controlling the operation of the controlled device constitutes the control section of each controlled device. For example, a configuration that controls the operation of the compressor 11 constitutes a compressor control section.

Next, the operation of the ejector type refrigerating cycle 10 of this 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 a pre-stored air-conditioning control program to control the operation of the various controlled devices 11, 12a, 18a.

In this air conditioning control program, a target blowout temperature TAO of air to be blown into the passenger compartment is calculated based on the detection signals from the sensor group for air conditioning control and the operation signal from the operation panel. Then, based on the target air temperature TAO and the like, the operating state of each controlled device is determined. For example, the compressor 11 is determined so that the refrigerant discharge capacity (rotational speed in the present embodiment) is decreased as the target blowout temperature TAO increases.

Here, the target blowout temperature TAO is a value that correlates with the amount of cold heat required to be generated by the ejector refrigeration cycle in order to keep the vehicle interior at a desired temperature (in other words, the cooling heat load of the ejector refrigeration cycle 10). is.

Therefore, when the vehicle interior is cooled, reducing the refrigerant discharge capacity of the compressor 11 as the target blowout temperature TAO rises will reduce the refrigerant discharge capacity of the compressor 11 as the cooling heat load decreases. means to lower. When the air conditioning control device 40 reduces the refrigerant discharge capacity of the compressor 11 as the cooling heat load decreases, the inlet side pressure Pni decreases and the pressure difference ΔP also decreases.

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

An operating 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. Low-load operation is performed, for example, when the outside temperature is relatively low, such as in spring or autumn, or when anti-fogging is performed on the car window when the outside temperature is low.

When the air conditioning control device 40 operates the compressor 11 , the high-temperature, high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12 . The refrigerant that has flowed into the radiator 12 exchanges heat with the outside air blown from the cooling fan 12a, and is cooled and condensed. The flow of refrigerant flowing out of radiator 12 is branched at branching portion 13 . One of the refrigerants branched at the branching portion 13 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 isoentropically decompressed in the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. Due to the suction action of the jetted refrigerant, the refrigerant flowing out of the suction side evaporator 19 is sucked from the refrigerant suction port 14c through the pressure introduction space 50c 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 expansion of the refrigerant passage area converts the speed energy of the refrigerant into pressure energy. This increases the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant. The refrigerant pressurized by the diffuser portion 14 d flows into the outflow side evaporator 18 .

The refrigerant that has flowed into the outflow side evaporator 18 absorbs heat from the air blown by the indoor fan 18a and evaporates. Thereby, the air blown by the indoor fan 18a is cooled. The refrigerant that has flowed out of the outflow side evaporator 18 is sucked into the compressor 11 and compressed again.

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

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

The refrigerant that has flowed out of the suction side pressure reducing device 15 flows into the suction side evaporator 19 . The refrigerant that has flowed into the suction side evaporator 19 absorbs heat from the air that has passed through the outflow side evaporator 18 and evaporates. As a result, the blown air after passing through the outflow side evaporator 18 is further cooled. The refrigerant that has flowed out of the suction-side evaporator 19 is sucked through the refrigerant suction port 14c.

Therefore, according to the ejector-type refrigerating cycle 10 of the present embodiment, regardless of load fluctuations, both during normal operation and during low-load operation, the outflow side evaporator 18 and the suction side evaporator 19 keep the vehicle interior The blast air blown to the can be cooled.

Furthermore, in the ejector type refrigerating cycle 10 of the present embodiment, the refrigerant pressurized by the diffuser portion 14d of the ejector 14 is sucked into the compressor 11 via the outflow side evaporator 18 . According to this, the power consumption of the compressor 11 is reduced and the coefficient of performance of the cycle is reduced compared to a normal refrigeration cycle device in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked into the compressor are substantially equal. (COP) can be improved.

In addition, in the ejector type refrigerating cycle 10 of the present embodiment, the suction side pressure reducing device 15 serves as a fixed throttle for decompressing the refrigerant in the regular throttle passage 50a during normal operation. Therefore, by appropriately setting the passage cross-sectional area of the normal use throttle passage 50a, insufficient cooling capacity of the suction side evaporator 19 is not caused during normal operation.

However, if a fixed throttle is adopted as the suction side decompression section, the flow rate (mass flow rate) of the refrigerant flowing into the suction side evaporator 19 is insufficient during low load operation, resulting in insufficient cooling capacity in the suction side evaporator 19. Sometimes.

In contrast, since the ejector-type refrigerating cycle 10 of the present embodiment includes the suction-side pressure reducing device 15, the opening of the throttle can be increased as the pressure difference ΔP is reduced during low-load operation. Therefore, it is possible to prevent the flow rate of the refrigerant flowing into the suction-side evaporator 19 from becoming insufficient during low-load operation.

Furthermore, since the suction-side decompression device 15 is composed of a mechanical mechanism that changes the opening of the throttle according to the pressure difference ΔP, complicated construction and control are required to change the opening of the throttle. Nor. That is, according to the ejector type refrigerating cycle 10 of the present embodiment, since the suction side decompression device 15 is employed, the throttle opening of the suction side decompression section can be adjusted appropriately according to the load fluctuation of the cycle with a simple configuration. can be changed to

Further, in the suction-side decompression 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 pressure Peo. According to this, the pressure difference ΔP can be increased due to the pressure loss in the suction-side evaporator 19 . Therefore, it becomes easier to detect the pressure difference ΔP, and the throttle opening of the suction-side decompression device 15 can be changed more appropriately.

(Second embodiment)
In the present embodiment, an example in which the suction side decompression device 15a shown in FIGS. 5 and 6 is adopted as the suction side decompression unit in contrast to the first embodiment will be described. 5 and 6 are drawings corresponding to FIGS. 2 and 3 described in the first embodiment, respectively. Moreover, in FIGS. 5 and 6, the same reference numerals are given to the same or equivalent parts as in the first embodiment. This also applies to the following drawings.

The basic configuration of the suction side decompression device 15a is the same as the suction side decompression device 15 described in the first embodiment. That is, the suction side decompression device 15a becomes a fixed throttle when the pressure difference ΔP is larger than the reference pressure difference KΔP. Furthermore, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, it is configured with a mechanical mechanism that functions as a variable throttle that increases the opening of the throttle as the pressure difference ΔP decreases.

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

A communication passage 52a is formed inside the columnar valve body portion 52 for communicating the high-pressure side inlet 51a and the low-pressure side outlet 51e. Furthermore, the restricting member 51f of the present embodiment is arranged such that the valve body portion 52 is displaced within a range where the communicating 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 so that the operating range of the valve body portion 52 is within a range in which the communication passage 52a can communicate the high-pressure side inlet 51a and the low-pressure side outlet 51e. there is

One axial end of the valve body portion 52 is formed with 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 51a. A low-stage pressure receiving surface that receives the pressure of the refrigerant that has flowed into the pressure introduction space 50c from the pressure introduction port 51c is formed on the other axial end side of the valve body portion 52 . The area of the pressure-receiving surface on the inlet side and the area of the pressure-receiving surface on the low-stage side are set substantially equal.

Further, the valve body portion 52 receives a load from the coil spring 53 on the side of the high pressure side inlet 51a (that is, the side that expands the pressure introduction space 50c). Therefore, the valve body portion 52 of this embodiment is displaced according to the load caused 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 decompression device 15a, when the pressure difference ΔP is greater than the reference pressure difference KΔP, as shown in FIG. 53 is displaced to the side where it is compressed.

In the suction side decompression device 15a, a 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, when the pressure difference ΔP is larger than the predetermined reference pressure difference KΔP, the suction side decompression device 15a becomes a fixed throttle. At this time, the aperture opening degree of the suction side decompression device 15a is determined by the opening area of the inlet portion of the low pressure side outlet 51e.

Then, when the pressure difference ΔP becomes equal to or less than the reference pressure difference KΔP, the load of the coil spring 53 displaces the valve body portion 52 to the side that expands the pressure introduction space 50c. This increases the opening area of the inlet portion of the low pressure side outlet 51e. In other words, the throttle opening of the suction-side decompression device 15a increases as the pressure difference ΔP decreases.

Furthermore, as shown in FIG. 6, when the valve body portion 52 is displaced to the side that expands the pressure introduction space 50c most as the pressure difference ΔP is reduced, the inlet portion of the low pressure side outlet 51e is fully opened. . At this time, the throttle opening degree of the suction side decompression 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 decompression device 15a of this embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the fixed throttle can be Further, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, a variable throttle is used in which the opening degree of the throttle is increased as the pressure difference ΔP is reduced until the low-pressure side outlet 51e is fully opened. can be done.

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

Therefore, since the ejector-type refrigerating cycle 10 of this embodiment includes the suction-side pressure reducing device 15a, the same effects as those of the first embodiment can be obtained. That is, according to the ejector type refrigerating cycle 10 of the present embodiment, since the suction side decompression device 15a is adopted, the throttle opening of the suction side decompression section can be adjusted appropriately according to the load fluctuation of the cycle with a simple configuration. can be changed to

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

The suction-side decompression device 15b becomes a fixed throttle when the inlet-side pressure Pni is higher than the predetermined reference inlet-side pressure KPni. Furthermore, when the inlet side pressure Pni is lower than the reference inlet side pressure KPni, it is configured with a mechanical mechanism that becomes a variable throttle that increases the throttle opening as the inlet side pressure Pni decreases. Therefore, the suction side decompression 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 capacity of the suction-side evaporator 19 is not sufficiently exhibited when the suction-side decompression device 15b is at the minimum throttle opening. set to a large value.

7 and 8, in the suction side pressure reducing device 15b, unlike the suction side pressure reducing device 15a described in the second embodiment, the pressure introduction port 51c and the pressure outlet port 51d of the body portion 51 are eliminated. It is A space formed on the other end side of the valve body portion 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 in the spring chamber 50d is the pressure of the outside air.

Therefore, the valve body portion 52 of this embodiment is displaced according to the load generated by the pressure difference obtained by subtracting the pressure Psp in the spring chamber 50d from the inlet side pressure Pni and the load received from the coil spring 53 . Here, the pressure Psp inside the spring chamber 50d is equivalent to the outside air pressure and is substantially constant. Therefore, the valve body portion 52 of this embodiment is substantially displaced according to the load caused 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 higher than the reference inlet-side pressure KPni, as shown in FIG. to the side of compressing the coil spring 53 (that is, the side of contracting the spring chamber 50d). As a result, the suction-side decompression device 15b becomes a fixed throttle, like 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 load of the coil spring 53 displaces the valve body portion 52 to the side that expands the spring chamber 50d. This increases the opening area of the inlet portion of the low pressure side outlet 51e. That is, the opening degree of the throttle of the suction-side decompression device 15b increases as the inlet-side pressure Pni decreases.

Furthermore, as shown in FIG. 8, when the valve body portion 52 is displaced to the side that expands the spring chamber 50d most as the inlet side pressure Pni decreases, the inlet portion of the low pressure side outlet 51e is fully opened. . At this time, the throttle opening degree of the suction side decompression 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 decompression device 15b of this embodiment, as shown in FIG. 9, when the inlet side pressure Pni is higher than the reference inlet side pressure KPni, a fixed throttle can be used. Further, when the inlet-side pressure Pni is equal to or lower than the reference inlet-side pressure KPni, until the low-pressure side outlet 51e is fully opened, the variable throttle that increases the throttle opening as the inlet-side pressure Pni decreases. can be Also, the reference inlet pressure KPni can be adjusted by changing the load of the coil spring 53 .

In the ejector type refrigerating cycle 10 of the present embodiment, the operating condition in which the inlet pressure Pni is higher than the reference inlet pressure KPni is normal operation, and the inlet pressure Pni is equal to or lower than the reference inlet pressure KPni. Low load operation is assumed to be the operating condition in which the Other configurations and operations of the ejector type refrigeration cycle 10 are the same as those of the first embodiment.

Therefore, since the ejector-type refrigerating cycle 10 of this embodiment includes the suction-side pressure reducing device 15b, the same effects as those of the first embodiment can be obtained. That is, according to the ejector-type refrigerating cycle 10 of the present embodiment, since the suction-side pressure reducing device 15b is employed, the throttle opening of the suction-side pressure reducing section can be adjusted appropriately according to the load fluctuation of the cycle with a simple configuration. can be changed to

(Fourth embodiment)
In the present embodiment, the configurations corresponding to the branch portion 13, the ejector 14, and the suction side decompression device 15 described in the first embodiment are integrated (modularized) as an ejector module 20 as shown in FIGS. ) will be explained. More specifically, the ejector module 20 is formed by integrating the components surrounded by the dashed lines in the overall block diagram of FIG. 10 . That is, the centrifugal branching part 13a, the ejector 14, the suction side decompression device 15c, etc. are integrated.

For the sake of illustration simplification 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 portion 21 . The body portion 21 is formed by combining a plurality of constituent members made of metal (made of aluminum in this embodiment). The body portion 21 supports and fixes the ejector 14, and constitutes a part of the suction side decompression device 15c and the like. The body portion 21 may be made of resin.

Inside the body portion 21, a regular throttle passage 50a and an auxiliary throttle passage 50b are formed which exhibit the same functions as those of the first embodiment. In this embodiment, one auxiliary throttle passage 50b is provided. 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 at the centrifugal branch portion 13a to the inlet side of the suction side pressure reducing device 15c. The suction refrigerant passage 20 b is a refrigerant passage that guides the refrigerant flowing out of the suction side evaporator 19 to the refrigerant suction port 14 c of the ejector 14 . A plurality of refrigerant suction ports 14c of this embodiment are formed around the central axis of the body portion 14b of the ejector 14. As shown in FIG. A plurality of refrigerant suction ports 14 c are open within the internal space of body portion 21 .

The pressure introduction passage 20c is a refrigerant passage that guides the refrigerant flowing out of 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 that has flowed out of the outflow-side evaporator 18 to the suction side of the compressor 11 .

Further, the body portion 21 is formed with refrigerant inlets and 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. be. The suction refrigerant inlet 21a is a refrigerant inlet into which the refrigerant flowing out from 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 that allows the refrigerant that has flowed out of the outflow-side evaporator 18 to flow into the outflow-side passage 20d. The outflow refrigerant outlet 21 c is a refrigerant outlet for causing the refrigerant that has flowed through the outflow side passage 20 d to flow 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 this embodiment is fixed to the body portion 21 by means such as press fitting. At this time, at least a portion of the portion forming the diffuser portion 14d of the body portion 14b of the ejector 14 is fixed so as to protrude from the body portion 21 .

A portion protruding from the body portion 21 of the portion forming the diffuser portion 14d 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 part that is inserted and fixed in a dedicated tank that communicates with a tank or a collective distribution tank.

Further, a centrifugal branching portion 13a is integrally formed on the upstream side of the refrigerant flow in the nozzle portion 14a of the present embodiment. A high-pressure side inlet 51a into which the other refrigerant branched at the branching portion 13 flows is formed at the most upstream portion of the refrigerant flow of the centrifugal branching portion 13a. The centrifugal branch portion 13a is formed in a cylindrical shape, and is a portion that causes the flow of the refrigerant that has flowed in from the high pressure side inlet 51a to swirl around the central axis of the nozzle portion 14a.

Further, a through hole 13b is formed through the cylindrical side surface of the centrifugal branching portion 13a. The internal space of the swirl portion 14e communicates with the high pressure side refrigerant passage 20a via the through hole 13b. For this reason, in the centrifugal branching portion 13a, one refrigerant with relatively high dryness on the center side of the swirl is decompressed by the nozzle portion 14a, and the other refrigerant with relatively low dryness on the outer peripheral side is depressurized by the suction side decompression device 15c. The flow of refrigerant 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 the suction side decompression device 15 described in the first embodiment. That is, the suction side decompression device 15c becomes a fixed throttle when the pressure difference ΔP is larger than the reference pressure difference KΔP. Furthermore, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, it is configured with a mechanical mechanism that functions as a variable throttle that increases the opening of the throttle as the pressure difference ΔP decreases.

In the suction side decompression device 15c of the present embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, as shown in FIG. ) to close the auxiliary throttle passage 50b. Therefore, the suction side decompression device 15c becomes a fixed throttle. At this time, the throttle opening of the suction side decompression device 15c is determined by the cross-sectional area of the normal throttle passage 50a.

Then, when the pressure difference ΔP becomes equal to or less than the reference pressure difference KΔP, the load of the coil spring 53 displaces the pressure introduction space 50c to the expanding side. As a result, 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 of the suction-side decompression device 15c is determined by the sum of the passage cross-sectional area of the regular throttle passage 50a and the opening area of the inlet portion of the auxiliary throttle passage 50b.

Further, as shown in FIG. 13, as the pressure difference ΔP decreases, the valve body portion 52 displaces to the side that expands the pressure introduction space 50c most, and 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 cross-sectional area of the normal throttle passage 50a and the auxiliary throttle passage 50b.

As a result, in the suction side decompression device 15c of the present embodiment, similarly to the suction side decompression device 15 described in the first embodiment, when the pressure difference ΔP is larger than the reference pressure difference KΔP, the fixed throttle can be Furthermore, when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, a variable throttle is employed in which the throttle opening is increased as the pressure difference ΔP decreases until the auxiliary throttle passage 50b is fully opened. can be done.

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

Therefore, the ejector-type refrigerating cycle 10 of this embodiment includes the ejector module 20 integrated with the suction-side decompression device 15c, so that the same effects as those of the first embodiment can be obtained. Furthermore, in the present embodiment, some of the components of the ejector refrigeration cycle 10 are integrated as the ejector module 20, so that the size of the ejector refrigeration cycle 10 as a whole can be reduced and the productivity can be improved. can.

(Fifth embodiment)
In this embodiment, as shown in FIG. 14, an example in which the configuration of the ejector module 20 is changed from the fourth embodiment will be described. The ejector module 20 of this embodiment employs a suction side decompression device 15d. Note that 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 the suction side decompression device 15b described in the third embodiment. That is, the suction-side decompression device 15d becomes a fixed throttle when the inlet-side pressure Pni is higher 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 opening of the throttle as the inlet side pressure Pni is reduced.

More specifically, in the ejector module 20 of this 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 through an 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 higher than the reference inlet-side pressure KPni, as shown in FIG. the spring chamber 50d is contracted). As a result, 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 load of the coil spring 53 displaces the valve body portion 52 to the side that expands the spring chamber 50d. Thus, similarly to the fourth embodiment, the high-pressure side refrigerant passage 20a communicates with both the regular throttle passage 50a and the auxiliary throttle passage 50b. Further, when the valve body portion 52 is displaced to the side that expands the spring chamber 50d most as the inlet side pressure Pni decreases, the inlet portion of the auxiliary throttle passage 50b is fully opened.

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

In the ejector-type refrigerating cycle 10 of the present embodiment, the operating condition in which the inlet-side pressure Pni is higher than the reference inlet-side pressure KPni is defined as normal operation, and the inlet-side pressure Pni is equal to or lower than the reference inlet-side pressure KPni. Low load operation is assumed to be the operating condition in which the Other configurations and operations of the ejector refrigeration cycle 10 are the same as those of the third embodiment.

Therefore, since the ejector type refrigerating cycle 10 of the present embodiment includes the ejector module 20 integrated with the suction side decompression device 15d, the same effects as those of the third embodiment can be obtained. Furthermore, in the present embodiment, some of the components of the ejector refrigeration cycle 10 are integrated as the ejector module 20, so that the size of the ejector refrigeration cycle 10 as a whole can be reduced and the productivity can be improved. can.

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

The ejector type refrigerating cycle 10a has the gas-liquid separator 22 instead of the branching portion 13 and the outflow side evaporator 18 in contrast to the ejector type refrigerating cycle 10 described in the first embodiment. The gas-liquid separator 22 is a gas-liquid separation unit that separates the gas-liquid of the refrigerant flowing out from the diffuser portion 14d and stores the separated surplus liquid-phase refrigerant.

Furthermore, in the ejector type refrigerating cycle 10a, the outlet of the radiator 12 is connected to the inlet side of the nozzle portion 14a of the ejector 14. As shown in FIG. Further, 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 pressure reducing device 15e. there is The suction-side decompression device 15 e decompresses the liquid-phase refrigerant separated by the gas-liquid separator 22 and causes it to flow out to the refrigerant inlet side of the suction-side evaporator 19 .

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

The suction side decompression device 15e becomes a fixed throttle when the pressure difference ΔP is greater than the reference pressure difference KΔP, and when the pressure difference ΔP is equal to or less than the reference pressure difference KΔP, the pressure difference ΔP is reduced. It is composed of a mechanical mechanism that serves as a variable aperture that increases the opening of the aperture as it shrinks. 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 type refrigerating cycle 10a having the above configuration will be described. In this embodiment, the operating condition under which the pressure difference ΔP is greater than the reference pressure difference KΔP is normal operation, and the operating condition under which the pressure difference ΔP is equal to or less than the reference pressure difference KΔP is low load operation.

When the air conditioning control device 40 operates the compressor 11 , the high-temperature, high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12 . The refrigerant that has flowed 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 isoentropically decompressed in the nozzle portion 14a and is injected from the refrigerant injection port of the nozzle portion 14a. Then, the refrigerant flowing out of the suction-side evaporator 19 is sucked from the refrigerant suction port 14c by the suction action of the jetted refrigerant.

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 pressurized by the diffuser portion 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 pressure reducing device 15e.

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

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

Therefore, according to the ejector-type refrigerating cycle 10a of the present embodiment, regardless of load fluctuations, the suction-side evaporator 19 blows air into the passenger compartment during normal operation and during low-load operation. can be cooled.

Furthermore, since the ejector-type refrigerating cycle 10a is provided with the suction-side decompression device 15e, it is possible to increase the throttle opening as the pressure difference ΔP decreases during low-load operation. Therefore, as in the first embodiment, it is possible to prevent the flow rate of the refrigerant flowing into the suction-side evaporator 19 from becoming insufficient during low-load operation.

Further, in the ejector type refrigerating cycle 10a, similarly to the suction side decompression device 15b described in the third embodiment, when the inlet side pressure Pni is higher than the reference inlet side pressure KPni, the throttle is fixed. , when the inlet side pressure Pni is lower than the reference inlet side pressure KPni, the suction side depressurizing mechanism configured with a mechanical mechanism that becomes a variable throttle that increases the throttle opening as the inlet side pressure Pni decreases. department may be adopted. According to this, an effect similar to that of the third embodiment can be obtained.

(Seventh embodiment)
In this embodiment, as shown in FIGS. 16 and 17, a damper section 54 is added to the suction side decompression device 15c of the ejector module 20 described in the fourth embodiment. 16 and 17 are drawings corresponding to FIGS. 12 and 13 described in the fourth embodiment, respectively.

The damper section 54 delays the change in the throttle opening of the suction-side decompression device 15c with respect to the change in the inlet-side pressure Pni. More specifically, the damper portion 54 of the present embodiment generates a resistance force that prevents displacement of the valve body portion 52 when the pressure difference ΔP changes with a change in the inlet side pressure Pni. 52 is to reduce the displacement speed.

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

The oil space forming member 54 a is made of the same material as the valve body portion 52 and is formed in a substantially cylindrical shape similar to the valve body portion 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 in the axial direction of the oil space forming member 54a), a An enlarged diameter portion 54b having the same diameter as the enlarged diameter portion 52b formed on the end side is formed.

One end in the axial direction of the oil space forming portion 54a is fixed to the other end in the axial direction of the valve body portion 52 by means of press fitting, screwing, or the like. At this time, the central axis of the valve body portion 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 spaced apart in the axial direction.

Sealing members such as O-rings are interposed in gaps 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 will not leak from the gaps between these members. Therefore, an annular closed space surrounded by the inner peripheral surface of the body 21, the valve body portion 52 and the oil space forming member 54a is formed inside the body 21. As shown in FIG. In this embodiment, this sealed space is an oil space 50e. Oil such as mineral oil is enclosed in the oil space 50e.

Further, an annular ring member 54c is fixed to the inner peripheral surface of the portion of the body 21 that forms the oil space 50e. Therefore, when the valve body portion 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 when 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 becomes the resistance force that prevents displacement of the valve body portion 52 and the oil space forming member 54a. . In FIGS. 16 and 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 in the fourth embodiment. Therefore, the ejector refrigerating cycle 10 including the ejector module 20 of this embodiment can also obtain the same effect as the fourth embodiment.

Furthermore, since the ejector module 20 of the present embodiment includes the damper portion 54, even if the pressure difference ΔP suddenly changes, the throttle opening of the suction-side decompression device 15c is prevented from suddenly changing. It is possible to further appropriately change the throttle opening of the suction side decompression unit.

(Eighth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 18, an example will be described in which a suction-side decompression unit having a Joule heat type on-off valve 60 is employed. The on-off valve 60 is configured by an electric mechanism that opens and closes the refrigerant passage by being supplied with electric power. It should be noted that the electrical mechanism is a mechanism that displaces the valve body or the like by supplying electric power. 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 a refrigerant passage, and a thermal deformation portion that thermally expands due to Joule heat generated when electric power is supplied. By transmitting the deformation of the thermal deformation portion to the valve body, the valve body is displaced to open and close the refrigerant passage.

More specifically, a regular throttle passage 50a and an auxiliary throttle passage 50b connected in parallel are formed inside 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. Deformation of the thermal deformation portion is transmitted to the valve body portion via the arm portion.

The arm 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 arranged at the other end of the arm. Furthermore, the thermally deformed portion is connected to the arm portion at a longitudinally intermediate position. Therefore, when the arm is displaced due to the deformation of the thermally deformable portion, the amount of deformation of the thermally deformable portion is amplified by the action of the lever with one end of the arm serving as a fulcrum and transmitted to the valve body.

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

Next, the operation of this embodiment with 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 when the pressure difference ΔP is greater than the reference pressure difference KΔP. Therefore, only the regular throttle passage 50a is open in the on-off valve 60 during normal operation. As a result, during normal operation, it operates in the same manner as in the first embodiment.

Further, the air conditioning control device 40 supplies electric 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. Therefore, 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, it operates in the same manner as in the first embodiment during low-load operation.

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

That is, according to the ejector type refrigerating cycle 10 of the present embodiment, since the on-off valve 60 is employed as the suction side pressure reducing section, the suction side pressure reducing section can be operated according to the load fluctuation of the cycle without increasing the size. can appropriately change the aperture opening.

(Ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 19, in contrast to the eighth embodiment, a fixed throttle 62 corresponding to the normal throttle passage 50a and a Joule heat type on-off valve 60a are added as the suction side pressure reducing section. An example of adopting what is provided will be described.

As shown in FIG. 19, the on-off valve 60a and the fixed throttle 62 are connected in parallel with 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 in the eighth embodiment.

Therefore, the ejector-type refrigerating cycle 10 of this embodiment operates in the same manner as in the eighth embodiment, and can obtain the same effects as in the eighth embodiment.

(Tenth embodiment)
In this embodiment, as shown in the overall configuration diagram of FIG. 20, an example in which the fixed diaphragm 60 is eliminated from the ninth embodiment will be described. Other configurations of the ejector type refrigeration cycle 10 are the same as those of 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, energization and non-energization are performed in a constant cycle, and the substantial passage cross-sectional area of the on-off valve 60a can be changed by changing the ratio of the energization time in one cycle.

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

Even if pulse width modulation control is executed like the air conditioning control device 40 of this embodiment, the same effects as those of the first embodiment can be obtained. Furthermore, in the present embodiment, since the on-off valve 60a is used as the suction side pressure reducing unit, compared to the case where a solenoid type on/off valve or the like is used, the responsiveness of opening and closing the refrigerant passage is high, and the suction side pressure reducing unit It is possible to more appropriately change the passage cross-sectional area (that is, throttle opening) of the part.

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

(1) In the first, second, and fourth embodiments described above, the pressure of the refrigerant flowing out of the suction-side evaporator 19 is used as the low-stage pressure Peo. is not limited to The low-stage pressure Peo may be the pressure of the refrigerant flowing out of the suction-side decompression devices 15, 15a, and 15c. More specifically, the pressure of the refrigerant flowing through the refrigerant flow path from the outlets of the suction-side decompression devices 15, 15a, and 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 pressure KPni are determined based on the pressure difference ΔP or the inlet pressure Pni at which the cooling capacity of 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, it may be set to a value slightly higher than the pressure difference ΔP or the inlet side pressure Pni at which the temperature distribution of the blown air cooled by the suction side evaporator 19 expands beyond the reference temperature difference. The temperature distribution of the blast air is defined by the temperature difference obtained by subtracting the minimum temperature from the maximum temperature of the blast air immediately after being cooled by the suction-side evaporator 19 . Then, the reference temperature difference may be set to a value that causes the passenger 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 embodiments. For example, in the second and fifth embodiments described above, the pressure in the spring chamber 50d is the outside air pressure, but the pressure in the spring chamber 50d is not limited to this. If the pressure in the spring chamber 50d can be kept substantially constant, the spring chamber 50d may be evacuated.

Further, in the suction side pressure reducing device 15, like a so-called poppet valve, the bottom portion 51b side may be displaced as a valve body portion to obtain the same effect. Furthermore, like a 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.

Further, in the suction-side pressure reducing device 15c, an example in which the auxiliary throttle passage 50b is configured with one refrigerant passage has been described, but the auxiliary throttle passage 50b may be configured with a plurality of refrigerant passages. The throttle opening may be changed by changing the number of open refrigerant passages according to the displacement of the valve body portion 52 .

Further, as the suction-side decompression device, a device that selectively opens and closes the regular throttle passage 50a and the auxiliary throttle passage 50b may be employed. That is, it is also possible to adopt a system in which one of the regular throttle passage 50a and the auxiliary throttle passage 50b is opened and the other is closed. In this case, the passage cross-sectional area of the auxiliary throttle passage 50b may be set larger than the passage cross-sectional area of the regular throttle passage 50a.

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

In addition, in the eighth to tenth embodiments described above, the opening/closing valves 60 and 60a are of the Joule heat type, but of course, solenoid type electromagnetic valves may also be used.

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 , 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 seventh embodiment described above, an example was described in which the damper section 54 was added to the suction side decompression device 15c of the ejector module 20 described in the fourth embodiment. A damper section 54 may be added to the suction side decompression 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 displacement of the valve body portion 52 when the inlet side pressure Pni changes.

Further, the suction-side decompression device 15c described in the seventh embodiment with the damper portion 54 added thereto, or the suction-side decompression device 15d of the fifth embodiment with the damper portion 54 added thereto may be added to the centrifugal branching portion 13a or the It may be separate from the ejector 14 . The suction-side decompression device 15c with the damper portion 54 added thereto, or the suction-side decompression device 15d of the fifth embodiment with the damper portion 54 added thereto may be added to the ejector-type refrigeration cycle 10 described in the first embodiment. You may employ|adopt as a suction side pressure reduction part.

(4) In the above-described eighth and ninth embodiments, the air conditioning control device 40 supplies electric 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. , but not limited to. For example, the air conditioning control device 40 may supply power to the on-off valves 60 and 60a when the inlet pressure Pni is equal to or lower than the reference inlet pressure KPni. According to this, an effect similar to that of the third embodiment can be obtained.

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

(5) Each constituent device constituting the ejector type refrigeration cycle 10 is not limited to those disclosed in the above-described embodiment.

For example, in the above-described embodiment, an example in which an electric compressor is employed as the compressor 11 has been described. An engine driven compressor may be employed. Furthermore, as an engine-driven compressor, it is possible to adjust the refrigerant discharge capacity by changing the compressor operating rate by changing the discharge capacity, or by changing the compressor operating rate by switching the electromagnetic clutch. A fixed displacement compressor can be employed.

Further, in the above-described embodiment, no reference is made to the detailed configuration of the radiator 12, but as the radiator 12, a receiver-integrated condenser having a receiver portion (in other words, liquid receiver) that stores the condensed refrigerant. may be adopted. Furthermore, a so-called subcooling type condenser configured to have a supercooling section that supercools the liquid-phase refrigerant that has flowed out of the receiver section may be employed.

Further, in the above-described first to third embodiments, an example in which the three-way joint structure is adopted as the branch portion 13 has been described, but the branch portion 13 is not limited to this. For example, the ejector refrigerating cycle 10 of the first to third embodiments may employ a centrifugal gas-liquid separator structure similar to the centrifugal branching portion 13a.

Further, in the above-described embodiment, an example in which the outflow-side evaporator 18 and the suction-side evaporator 19 are integrally configured has been described. good too. Then, the outflow-side evaporator 18 and the suction-side evaporator 19 may cool different refrigerant target fluids in different temperature zones.

Also, in the above-described embodiment, an example in which R134a is used as the refrigerant has been described, but the refrigerant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be employed. Alternatively, a mixed refrigerant or the like in which a plurality of types of these refrigerants are mixed may be adopted. Furthermore, a supercritical refrigerating cycle may be constructed in which carbon dioxide is employed as the refrigerant and the pressure of the refrigerant on the high pressure side is equal to or higher than the critical pressure of the refrigerant.

(6) In each of the embodiments described above, the ejector refrigeration cycle 10 according to the present invention is applied to a vehicle air conditioner, but application of the ejector refrigeration cycle 10 is not limited to this. For example, it may be applied to a stationary air conditioner, a cold storage, and other cooling and heating devices.

10, 10a Ejector-type refrigerating cycle 11 Compressor 12 Radiator 14 Ejector 14a Nozzle 14c Refrigerant suction port 15-15e Suction side decompression device (suction side decompression section)
19 suction side evaporator 20 ejector module 60, 60a on-off valve (suction side decompression unit)

Claims (9)

a compressor (11) for compressing and discharging refrigerant;
a radiator (12) for dissipating heat from the refrigerant discharged from the compressor;
Refrigerant is sucked from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle portion (14a) for decompressing the refrigerant flowing out of the radiator, and the jetted refrigerant and the suction sucked from the refrigerant suction port an ejector (14) for increasing the pressure of the mixed refrigerant with the refrigerant;
a suction side decompression unit ( 15, 15a, 15c, 15e ) for decompressing the refrigerant;
a suction side evaporator (19) that evaporates the refrigerant decompressed in the suction side decompression unit and causes it to flow out to the refrigerant suction port side;
The suction side decompression section changes the opening degree of the throttle based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section ,
The suction-side decompression unit reduces the opening degree of the throttle as the pressure difference (ΔP) obtained by subtracting the low-stage pressure (Peo), which is the pressure of the refrigerant flowing out of the suction-side decompression unit, from the inlet-side pressure is reduced. has a mechanical mechanism that increases
The low-stage pressure is the pressure of the refrigerant flowing out of the suction-side evaporator in the ejector-type refrigerating cycle. The ejector-type refrigerating cycle according to claim 1 , wherein the suction-side decompression section ( 15c ) has a damper section (54) that delays a change in the throttle opening with respect to a change in the inlet-side pressure. a compressor (11) for compressing and discharging refrigerant;
a radiator (12) for dissipating heat from the refrigerant discharged from the compressor;
Refrigerant is sucked from the refrigerant suction port (14c) by the suction action of the jetted refrigerant jetted from the nozzle portion (14a) for decompressing the refrigerant flowing out of the radiator, and the jetted refrigerant and the suction sucked from the refrigerant suction port an ejector (14) for increasing the pressure of the mixed refrigerant with the refrigerant;
a suction side decompression unit ( 15c, 15d ) for decompressing the refrigerant;
a suction side evaporator (19) that evaporates the refrigerant decompressed in the suction side decompression unit and causes it to flow out to the refrigerant suction port side;
The suction side decompression section changes the opening degree of the throttle based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section ,
An ejector type refrigerating cycle , wherein the suction side decompression section has a damper section (54) that delays a change in the throttle opening with respect to a change in the inlet side pressure . 4. The ejector type refrigerating cycle according to claim 3 , wherein the suction side decompression section ( 15d ) has a mechanical mechanism that increases the throttle opening as the inlet side pressure decreases. A branching part (13) for branching the flow of the refrigerant flowing out of the radiator,
The inlet side of the nozzle portion is connected to one outlet of the branch portion (13),
5. The ejector type refrigerating cycle according to any one of claims 1 to 4 , wherein the inlet side of the suction side decompression section is connected to the other outlet of the branch section (13). An ejector refrigeration cycle (10) having a compressor (11) for compressing and discharging refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and a suction side evaporator (19) for evaporating the refrigerant. ), the ejector module applied to
a nozzle part (14a) for reducing the pressure of a part of the refrigerant flowing out of the radiator and injecting the refrigerant;
a suction side decompression part (15c) for decompressing another part of the refrigerant flowing out of the radiator;
a body portion (21) formed with a suction refrigerant inlet (21a) through which the refrigerant flowing out of the suction side evaporator flows due to the suction action of the injection refrigerant injected from the nozzle portion;
a boosting unit (14d) for boosting a mixed refrigerant of the injection refrigerant and the suction refrigerant sucked from the suction refrigerant inlet ,
The suction side decompression section changes the opening degree of the throttle based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section ,
The suction-side decompression unit reduces the throttle opening as the pressure difference obtained by subtracting the low-stage pressure (Peo), which is the pressure of the refrigerant flowing out of the suction-side decompression unit, from the inlet-side pressure (Pni) is reduced. has a mechanical mechanism that increases
The ejector module , wherein the low-stage pressure is the pressure of the refrigerant sucked from the suction refrigerant inlet . 7. The ejector module according to claim 6 , wherein the suction side decompression section has a damper section (54) that delays a change in the throttle opening with respect to a change in the inlet side pressure (Pni). An ejector refrigeration cycle (10) having a compressor (11) for compressing and discharging refrigerant, a radiator (12) for dissipating heat from the refrigerant discharged from the compressor, and a suction side evaporator (19) for evaporating the refrigerant. ), the ejector module applied to
a nozzle part (14a) for reducing the pressure of a part of the refrigerant flowing out of the radiator and injecting the refrigerant;
a suction side decompression part ( 15d ) for decompressing another part of the refrigerant flowing out of the radiator;
a body portion (21) formed with a suction refrigerant inlet (21a) through which the refrigerant flowing out of the suction side evaporator flows due to the suction action of the injection refrigerant injected from the nozzle portion;
a boosting unit (14d) for boosting a mixed refrigerant of the injection refrigerant and the suction refrigerant sucked from the suction refrigerant inlet ,
The suction side decompression section changes the opening degree of the throttle based on the inlet side pressure (Pni), which is the pressure of the refrigerant flowing into the nozzle section ,
The suction side decompression section has an ejector module (54) that delays a change in the throttle opening with respect to a change in the inlet side pressure (Pni) . 9. The ejector module according to claim 8 , wherein the suction side decompression section has a mechanical mechanism that increases the degree of throttle opening as the inlet side pressure (Pni) decreases.

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