CN1869551A - Injectors and injection circulators - Google Patents

Abstract

A spray cycle device comprising: the refrigerant compressor includes a compressor (10) sucking and compressing a refrigerant, a radiator (20) radiating heat of a high-pressure refrigerant discharged from the compressor, an ejector (30), a branch passage (55) branched from a refrigerant passage between the radiator and a nozzle portion of the ejector and connected to a suction port of the ejector, a throttle unit (40) disposed in the branch passage and decompressing the refrigerant, and an evaporator (50) disposed at a refrigerant flow downstream side of the throttle unit in the branch passage and evaporating the refrigerant. Therefore, even if the suction performance of the ejector is lowered, the refrigerant can flow through the evaporator.

Description

Injectors and injection circulators

technical field

The present invention relates to an injector and an injection cycle device using the injector. The ejector cycle device can be applied to a vapor compression refrigeration cycle using an ejector.

Background technique

For a vapor compression type refrigeration cycle using an ejector, for example, JP-B1-3322263 (corresponding to USP 6,477,857, Vapor compression refrigeration cycle described in USP 6,574,987). In addition, JP-A-2005-37093 (corresponding to US 2005/0011221A) proposes a vapor compression type refrigeration cycle, which includes a vapor/liquid separator and an evaporator located between A differential pressure valve whose control is nearly proportional to the differential pressure between the front and back of the ejector, and which is arranged in series with this differential pressure valve and allows the refrigerant to flow only in the direction in which the refrigerant flows from the liquid refrigerant outlet of the vapor/liquid separator check valve.

However, one of the problems of the vapor compression type refrigeration cycle using the above-mentioned conventional ejector is that when the performance of the ejector decreases, especially, in the case of low outside air, the amount of refrigerant flowing through the evaporator decreases, resulting in evaporation performance of the device degrades. For this reason, it is required to provide a circulation structure in which refrigerant can flow through the evaporator even when the performance of the ejector is degraded.

Furthermore, in USP 6,550,265, a vapor compression type heat pump cycle in which heat from a low temperature side is transferred to a high temperature side by using an ejector is described. Here, an ejector type heat pump cycle is provided to switch two heat exchangers between a high temperature side and a low temperature side by using two four-way valves.

However, the heat pump cycle composed of two four-way valves increases the cost and reduces the convenience of its installation.

In addition, we have already known jet cycle devices in which the nozzle portion of the injector and the pressure reducing means separated from the nozzle portion are integrally formed with each other, thereby reducing the size (for example, JP-A-2004 corresponding to USP 6,871,506 -44906).

In the cycle disclosed in JP-A-2004-44906, the ejector integrated with the adjustable throttle valve is connected to the downstream side of the radiator, the accumulator is connected to the downstream side of the ejector, and the liquid-phase refrigerant of the accumulator The outlet is connected to the inlet of the evaporator, and the outlet of the evaporator is connected to the ejector refrigerant suction. Therefore, the amount of refrigerant sucked by the evaporator is only related to the suction capacity of the ejector. For this, when the difference between the high and low pressure of the cycle becomes smaller and thus the input to the ejector drops, the suction capacity of the ejector drops and the refrigerant flow to the evaporator drops, in which case the evaporator cannot fully apply cooling capacity.

Contents of the invention

In view of the above-mentioned problems, an object of the present invention is to provide an ejector cycle device in which refrigerant flows into an evaporator even when the ejector suction performance decreases.

Another object of the present invention is to provide an ejector cycle device having an ejector that can switch a high temperature side and a low temperature side in a refrigeration cycle with a simple structure.

Another object of the present invention is to provide an injection cycle device capable of reducing costs and switching between a high temperature side and a low temperature side.

Still another object of the present invention is to provide an injector and an injection cycle device using the injector and having a simple branch passage structure.

Still another object of the present invention is to provide an injector integrated with a throttling unit with a simple structure.

According to an aspect of the present invention, the injection cycle device includes: a compressor that sucks and compresses refrigerant; a radiator that dissipates heat of high-pressure refrigerant discharged from the compressor; including converting the pressure energy of the high-pressure refrigerant downstream of the radiator For speed energy, to decompress and expand the nozzle part of the refrigerant, and the injector for the suction port of the refrigerant sucked from the nozzle part by the jet flow; branched from the refrigerant passage between the radiator and the nozzle part of the ejector , and connected to the branch passage of the suction port of the ejector; a throttling unit (throttling device) provided in the branch passage and depressurizing the refrigerant; and a downstream side of the refrigerant flow of the throttling unit provided in the branch passage And the evaporator that evaporates the refrigerant. Therefore, even when the suction capacity of the evaporator drops at low outside air temperatures, refrigerant can be guided into the evaporator, and the cooling capacity of the evaporator can be maintained.

For example, a flow control unit may be provided in the refrigerant passage between the radiator and the injector, and control the flow of the refrigerant. In this case, the refrigerant flow rate in the full cycle can be easily adjusted.

A vapor/liquid separator may be located between an outlet of the ejector and the compressor to separate refrigerant into vapor-phase refrigerant and liquid-phase refrigerant so as to supply the vapor-phase refrigerant to the compressor and accumulate the liquid-phase refrigerant. In addition, a heat recovery unit may be located between the ejector and the compressor to exchange heat between refrigerant flowing out of the radiator and refrigerant flowing out of the ejector and sucked by the compressor. Alternatively, a heat recovery unit may be located between the vapor/liquid separator and the compressor to exchange heat between refrigerant flowing out of the radiator and refrigerant flowing out of the vapor/liquid separator and drawn in by the compressor. Alternatively, a heat recovery unit may be located between the ejector and the vapor/liquid separator to exchange heat between the refrigerant flowing out of the radiator and the refrigerant flowing out of the ejector and into the vapor/liquid separator. Therefore, heat can be efficiently recovered by the heat recovery unit.

In addition, a plurality of heat recovery members may be located between the ejector and the compressor, and exchange heat between refrigerant flowing out of the radiator and refrigerant flowing out of the ejector and sucked by the compressor. In this case, the vapor/liquid separator may be located between the low-pressure refrigerant passages of the plurality of heat recovery elements.

In the jet cycle device, a liquid refrigerant supply passage may be provided to suck liquid refrigerant from the vapor/liquid separator, and a non-return device may be provided in the liquid refrigerant supply passage to allow the refrigerant to flow out of the vapor/liquid separator direction flow. In this case, the liquid-phase refrigerant supplied from the liquid-state refrigerant supply passage may be made to flow into the upstream side of the refrigerant flow of the evaporator.

According to another aspect of the present invention, the injection cycle device includes: a compressor that sucks, compresses, and discharges refrigerant; The nozzle part of the inlet of the high-pressure refrigerant in the front, the suction port of the refrigerant sucked by the jet flow of the refrigerant from the nozzle part, and the discharge port for discharging the refrigerant from the nozzle and the suction port; the inlet connected to the ejector and the branch passage of the suction port of the ejector; the heat exchanger provided in the branch passage; and the first mode in which the high-pressure refrigerant is supplied to the ejector inlet, and the refrigerant flows from the heat exchanger to the suction port, and the high-pressure refrigerant A channel switching unit that is supplied to the discharge port, and the refrigerant flows from the suction port of the ejector to the second mode of the heat exchanger. Therefore, the high temperature side and the low temperature side can be switched using a simple structure in the cycle.

A heat exchanger can be arranged as the first heat exchanger. In this case, the throttling unit may be located between the inlet of the ejector and the first heat exchanger, and make the first heat exchanger low temperature in the first mode, and make the first heat exchanger low temperature in the second mode. high temperature. In addition, a second heat exchanger may be provided in the refrigerant circulation passage, and become high temperature in the first mode and low temperature in the second mode.

Even in this case, the heat recovery unit can be located between the ejector and the compressor, and between the refrigerant flowing out of the second heat exchanger and the refrigerant flowing out of the ejector and sucked in by the compressor in the first mode heat exchange.

In addition, the second ejector and the second branch passage may be provided on the second heat exchanger side. In this case, the second ejector has an inlet into which the high-pressure refrigerant on the downstream side of the first heat exchanger flows in in the second mode, and the second branch channel circulates the refrigerant from the upstream side of the inlet of the first ejector The branched refrigerant is guided into the suction port of the second ejector, and a second heat exchanger may be disposed in the second branch channel and evaporate the refrigerant, thereby applying cooling capacity in the second mode.

According to still another object of the present invention, an ejector for a refrigerating cycle includes: a nozzle portion for reducing the pressure of the refrigerant to expand the refrigerant; a suction portion for the refrigerant to be sucked by the high-speed refrigerant injected from the nozzle portion; for mixing and a diffuser portion of pressurized refrigerant injected from the nozzle portion and refrigerant sucked from the suction portion; a first connection portion communicated with the upstream side of the nozzle portion; a second connection portion communicated with the downstream side of the diffuser portion; a third connection portion in partial communication; and a fourth connection portion in communication with the upstream side of the nozzle portion. Therefore, branched refrigerant passages of the ejector can be made simple. Furthermore, similarly to the fourth connection part, the fifth and sixth connection parts can be simply formed.

For example, the control mechanism can be made to control the opening of the nozzle portion. In addition, the control mechanism may be configured to control the opening of the refrigerant passage passing through the fourth connection portion.

In addition, the control mechanism may be provided with a needle provided in the refrigerant passage of the nozzle portion, and one end of the refrigerant passage passing through the fourth connection portion may open in the refrigerant passage of the nozzle portion opposite to a side surface of the needle. Alternatively, throttling means may be provided to throttle the refrigerant flow through the fourth connecting portion. For example, the throttling device may be located between the fourth connection portion and the first connection portion, or may be provided in a refrigerant passage connected to the fourth connection portion.

According to another object of the present invention, an ejector for a refrigeration cycle having an evaporator, comprising: a nozzle portion having decompression and expansion refrigerant, and sucking refrigerant from the evaporator by high-velocity refrigerant ejected from the nozzle the injection part of the suction part; and the throttling unit which is integrated with the ejector and reduces the pressure of the refrigerant which is branched at the upstream side of the nozzle part and flows out of the upstream side of the evaporator. Therefore, an integral structure of the injector and the throttling device (for example, a throttling unit) may be provided.

In this case, at least one of the nozzle portion and the throttling unit may be configured to change the area of the refrigerant passage. In addition, the throttle unit may be housed in a housing that accommodates the nozzle portion.

In addition, the nozzle part can be a variable nozzle part that can change the area of the refrigerant passage, the throttling unit can be a variable throttling mechanism that can change the area of the refrigerant passage, the area of the refrigerant passage of the variable nozzle part and the variable throttling mechanism The area of the refrigerant passage can be changed by the common passage area control device. In this case, the passage area control means simultaneously contracts or increases the area of the refrigerant passage of the variable nozzle portion and the area of the refrigerant passage of the variable throttle mechanism.

Alternatively, a throttling unit may be provided outside a housing for accommodating the nozzle portion, and the throttling unit may be integrally connected to the housing through a refrigerant pipe having a length of about 5 cm or less. In addition, the variable nozzle section and the variable throttle mechanism can be controlled by a single drive section.

According to another object of the present invention, the injection cycle device includes: an ejector including a nozzle portion that reduces the pressure of the refrigerant to expand the refrigerant and draws the refrigerant through the high-velocity refrigerant injected from the nozzle portion; evaporates upstream of the nozzle portion an evaporator of refrigerant branched sideways and sucked through the ejector; and a throttling device that reduces the pressure of the refrigerant branched at the upstream side of the nozzle portion, thereby expanding the refrigerant and supplying the refrigerant to the evaporator. In this case, the throttling device is integrally formed with the injector. Therefore, the structure of the injection cycle device can be simplified.

Description of drawings

Other objects and advantages of the present invention will become clearer and easier to understand by the following detailed description of preferred embodiments with reference to the accompanying drawings.

1 is a schematic diagram of a vapor compression refrigeration cycle (ejection cycle device) using an ejector according to a first embodiment of the present invention;

2 is a schematic diagram of a vapor compression type refrigeration cycle using an ejector according to a second embodiment of the present invention;

3 is a schematic diagram of a vapor compression refrigeration cycle using an ejector according to a third embodiment of the present invention;

4 is a schematic diagram of a vapor compression refrigeration cycle using an ejector according to a fourth embodiment of the present invention;

5 is a schematic diagram of a vapor compression refrigeration cycle using an ejector according to a fifth embodiment of the present invention;

6 is a schematic diagram of a vapor compression refrigeration cycle using an ejector according to a sixth embodiment of the present invention;

7 is a schematic diagram of a vapor compression refrigeration cycle using an ejector according to a seventh embodiment of the present invention;

Figure 8 is a p-h diagram of a vapor compression refrigeration cycle using the ejector in Figure 7;

9 is a schematic diagram of a vapor compression refrigeration cycle (ejection cycle device) using an ejector according to an eighth embodiment of the present invention;

Figure 10 is a p-h diagram of a vapor compression refrigeration cycle using the ejector in Figure 9;

11 is a schematic diagram of a vapor compression refrigeration cycle (ejection cycle device) using an ejector according to a ninth embodiment of the present invention;

12 is a schematic diagram of a vapor compression refrigeration cycle (ejection cycle device) using an ejector according to a tenth embodiment of the present invention;

13 is a schematic diagram of a vapor compression refrigeration cycle (ejection cycle device) using an ejector according to an eleventh embodiment of the present invention;

Figure 14 is a p-h diagram of a vapor compression refrigeration cycle using the ejector in Figure 13;

Fig. 15 is a schematic diagram of an injection cycle device in a twelfth embodiment of the present invention, and shows an air cooling mode of operation;

Figure 16 is a simplified diagram of the air heating mode of operation in the jet cycle device of Figure 15;

Fig. 17 is a schematic diagram of a spray cycle device in a thirteenth embodiment of the present invention;

Fig. 18 is a schematic diagram of an injection cycle device in a fourteenth embodiment of the present invention;

Fig. 19 is a schematic diagram of a spray cycle device in a fifteenth embodiment of the present invention;

Fig. 20 is a schematic diagram of the injection cycle device in the sixteenth embodiment of the present invention;

Fig. 21 is a schematic diagram of a spray cycle device in a seventeenth embodiment of the present invention;

Fig. 22 is a schematic diagram of an injection cycle device in an eighteenth embodiment of the present invention;

Fig. 23 is a sectional view of an injector according to an eighteenth embodiment;

Fig. 24A is a diagram showing a state of constricting (throttling) the refrigerant passage area of the injector,

Fig. 24B is a diagram showing a state of increasing the refrigerant passage area of the ejector;

Fig. 25 is a schematic diagram of an injection cycle device in a nineteenth embodiment of the present invention;

26 is a schematic sectional view of an injector of a nineteenth embodiment;

27 is a schematic cross-sectional view of an injector of a twentieth embodiment;

Fig. 28 is a schematic sectional view of an injector in which a fixed throttle is added to a modification of the eighteenth embodiment.

Detailed ways

(first embodiment)

Hereinafter, a first embodiment of the present invention will be described in detail using FIG. 1 . 1 is a schematic diagram of a vapor compression type refrigeration cycle (ejection cycle apparatus) using an ejector according to a first embodiment of the present invention. In this embodiment, a vapor compression type refrigeration cycle using the ejector according to the present invention is typically used for such an air conditioner for a vehicle using carbon dioxide (CO ₂ ) as a refrigerant.

The compressor 10 is supplied with driving force from a driving source such as a driving motor (not shown), and sucks and compresses refrigerant. When the compressor 10 in this embodiment employs a variable capacity compressor that variably controls the flow rate of the discharged refrigerant (discharged refrigerant flow rate) so that the temperature of the refrigerant sucked by the compressor 10 becomes a predetermined temperature. dose rate or volume). The discharged refrigerant flow rate (discharged refrigerant speed or volume) is controlled by an electronic control unit (not shown). Radiator 20 is a high-pressure side heat exchanger for heat exchange between refrigerant discharged from compressor 10 and air outside the vehicle cabin blown from a blower (not shown) to cool the refrigerant.

The ejector 30 reduces the pressure of the refrigerant flowing out of the radiator 20, thereby expanding the refrigerant and sucking the vapor-phase refrigerant evaporated in the evaporator 50 from the suction port 33. The evaporator 50 will be described later and converts the expansion energy into pressure energy. , thereby increasing the suction pressure of the compressor 10. Refrigerant flowing out of this ejector 30 is sucked through the compressor 10 . In this manner, the refrigerant circulation passage of the jet cycle device is formed.

In this refrigerant circulation passage, the branch point of the branch passage 55 that introduces the branched refrigerant flow into the suction port 33 of the above-mentioned ejector 30 is located between the radiator 20 and the nozzle 31 of the ejector 30, and the nozzle 31 will be described in detail later. illustrate. In this branch passage, the evaporator 50 is provided as a low-pressure side heat exchanger exchanging heat between air blown into the vehicle compartment and liquid-phase refrigerant to evaporate the liquid-phase refrigerant, thereby applying cooling capacity.

In addition, on the upstream side of the refrigerant flow of this evaporator 50, a throttling unit 40 (in this embodiment, a fixed throttle such as a capillary tube) that reduces the pressure of the refrigerant sucked through the evaporator 50 is provided, so that It is ensured that the pressure in the evaporator 50 (evaporating pressure) is reduced, and the flow rate of refrigerant flowing into the evaporator 50 is controlled.

Here, as shown in FIG. 1 , the ejector 30 is composed of a nozzle that converts the pressure energy of the high-pressure refrigerant flowing out of the radiator 20 into velocity energy (velocity head) to reduce the pressure of the refrigerant, thereby expanding the refrigerant. 31; the suction part 33 that sucks the vapor-phase refrigerant evaporated in the evaporator 50; the refrigerant is sucked from the suction part 33 by the high-speed refrigerant flow (jet flow) sprayed from the nozzle 31, and at the same time, the refrigerant sprayed from the nozzle 31 The mixing part where the refrigerant is mixed with the refrigerant drawn from the evaporator 50; and the diffusion part that converts the velocity energy of the refrigerant flowing out of the mixing part into pressure energy, thereby increasing the pressure of the refrigerant.

In addition, the tip side of the suction portion 33 is formed in a conical shape in which the cross-sectional area of the passage gradually decreases as the passage approaches the mixing portion. The diffusion portion is formed in a conical shape in which the cross-sectional area of the passage gradually increases as the passage approaches the refrigerant outlet.

Next, the operation of the vapor compression type refrigeration cycle using the above structure will be described. When the compressor 10 is driven, vapor-phase refrigerant is sucked from the suction side through the compressor 10 , and the compressed refrigerant is discharged to the radiator 20 . The refrigerant cooled by the radiator 20 is divided into a driving flow flowing into the nozzle 31 of the ejector 30 and a suction flow passing through the throttling device 40 and the evaporator 50 .

The refrigerant flowing into the nozzle 31 has a pressure lowered to expand and suck the refrigerant in the evaporator 50 . The refrigerant of the suction flow sucked from the evaporator 50 is mixed with the refrigerant of the driving flow injected from the nozzle 31 at the mixing portion. The mixed refrigerant has its dynamic pressure converted to static pressure by the diffusion part, and then returns to the compressor 10 . On the other hand, the refrigerant of the suction flow has its pressure reduced by the throttling unit 40 (throttling device), and then flows into the evaporator 50 . And absorb heat from the air blown into the vehicle cabin to be evaporated, and then inhaled through the ejector 30 .

At this time, in the mixing section, the driving flow is mixed with the suction flow in such a way that the sum of the momentum of the driving flow and the momentum of the suction flow is conserved. Therefore, the pressure (static pressure) of the refrigerant also increases in the mixing portion. On the contrary, in the diffusion part, as described above, the cross-sectional area of the passage gradually increases, so that the velocity energy (dynamic pressure) of the refrigerant is converted into pressure energy (static pressure). Therefore, in the ejector 30, the pressure of the refrigerant increases both at the mixing portion and at the diffusing portion.

The mixing section and the diffusion section are generally referred to as the pressure increasing section 32 . In other words, in the ideal ejector 30, the pressure of the refrigerant increases in the mixing part in such a way that the sum of the momentum of the driving flow and the suction flow is conserved and in the diffusing part in such a way that the energy is conserved.

Next, features and effects of this embodiment will be described. The jet cycle device of this embodiment includes: a compressor that sucks and compresses refrigerant; a radiator 20 that dissipates heat of the high-pressure refrigerant discharged from the compressor 10; and converts the pressure energy of the high-pressure refrigerant on the downstream side of the radiator 20 into The speed can reduce the pressure of the refrigerant, thereby expanding the refrigerant and sucking the refrigerant into the ejector 30; introducing the refrigerant flow branched from the branch point between the radiator 20 and the ejector 30 of the refrigerant circulation channel, and making The injector 30 sucks the branch passage 55 of the refrigerant, the refrigerant circulation passage includes the compressor 10, the radiator 20, and the ejector 30, and the refrigerant circulates in the refrigerant circulation passage; it is arranged in the branch passage 55 and reduces the refrigerant flow The throttling unit 40 for pressure; and the evaporator 50 provided in the branch passage 55 on the downstream side of the refrigerant flow of the throttling unit 40 and evaporates the refrigerant, thereby applying cooling capacity.

According to this embodiment, on the upstream side of the ejector 30 , the refrigerant flow is divided into a driving flow flowing into the ejector 30 as a refrigerant circulation passage and a suction flow flowing into the evaporator 50 as a branch passage 55 . Therefore, even when the suction performance of the ejector 30 decreases due to low outside air temperature, a vapor compression type refrigeration cycle using the ejector in which refrigerant flows through the evaporator 50 can be realized.

In addition, the pressure at the outlet of the ejector 30 becomes higher than that of the evaporator 50 by increasing the pressure due to the pressure increase of the ejector 30 , and thus, the suction pressure of the compressor 10 is also higher than the pressure at the outlet of the evaporator 50 . In other words, even when the above-described simple cycle structure with the ejector 30 is used, the refrigeration capacity can be effectively increased, and the suction pressure of the compressor 10 can also be effectively increased by increasing the enthalpy difference while the evaporator 50 is maintained at low pressure and low temperature. Therefore, it is possible to appropriately reduce the compression power and enhance the COP in the vapor compression type refrigeration cycle using the ejector 30 having a simple structure.

(second embodiment)

Fig. 2 is a schematic diagram of a vapor compression type refrigeration cycle (ejection cycle device) using an ejector according to a second embodiment of the present invention. The features of the second embodiment that differ from the first embodiment will be mainly described below. In this embodiment, a flow control valve 45 as a flow control means for controlling the flow of refrigerant is provided in the refrigerant circulation passage between the radiator 20 and the nozzle portion 31 and the branch passage 55 .

In the basic cycle structure of the first embodiment, even if the variable flow rate type ejector is used as the ejector 30 to control the flow rate of the refrigerant, when the flow rate of the driving flow decreases, the flow rate of the suction flow increases so that the flow rate of the compressor 10 flows. There is no change in the overall flow of refrigerant. In this case, the flow of refrigerant is not controlled as desired.

In the jet cycle device of the second embodiment, by providing the flow control valve 45 on the upstream side of the branch point of the branch passage 55, the entire flow rate of the refrigerant can be easily controlled without changing the flow rate between the driving flow and the suction flow. Compare. In this embodiment, the flow control valve 45 may be an electric flow control valve 45 capable of variably controlling the refrigerant flow, or may be a fixed flow control unit (fixed flow control device).

(third embodiment)

FIG. 3 is a schematic diagram of a vapor compression type refrigeration cycle using an ejector 30 according to a third embodiment of the present invention. The features of the third embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, circulating refrigerant is divided into vapor-phase refrigerant and liquid-phase refrigerant, and only vapor-phase refrigerant is supplied to the compressor 10, and a vapor/liquid separator 60 accumulating liquid-phase refrigerant is located at the ejector Between the outlet of 30 and the compressor 10.

The vapor/liquid separator 60 in FIG. 3 is an accumulator where the refrigerant flowing out of the injector 30 flows in, separates the incoming refrigerant into vapor phase refrigerant and liquid phase refrigerant, and accumulates the liquid phase refrigerant. The separated vapor-phase refrigerant is sucked through the compressor 10 , while the separated liquid-phase refrigerant is accumulated in the vapor/liquid separator 60 . When the vapor/liquid separator 60 is provided in the basic cycle structure of the first embodiment, the vapor/liquid separator 60 serves as a reservoir for separating refrigerant into vapor and liquid refrigerant and for accumulating the separated liquid-phase refrigerant. device.

Therefore, according to this embodiment, it is possible to prevent the liquid-phase refrigerant from returning to the compressor 10 and being compressed by the compressor 10, and further control the amount of refrigerant circulating in the cycle to an appropriate amount. Furthermore, there is no need for a tube for passing the outgoing liquid phase refrigerant into the evaporator 50 as shown in the aforementioned IP-3322263, therefore, a normal vapor/liquid separator 60 with such a tube or tank can be used, which reduces costs. In the third embodiment, when the return of the liquid-phase refrigerant to the compressor 10 is not a problem, it is also recommended to use the structure without the vapor/liquid separator 60 as in the first embodiment.

(fourth embodiment)

4 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to a fourth embodiment of the present invention. The features of the fourth embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, an internal heat exchanger 70 as a heat recovery unit that exchanges heat between the refrigerant flowing out of the radiator 20 and the refrigerant flowing out of the ejector 30 and sucked by the compressor 10 is located between the ejector 30 and the compressor 10 . Between 10. According to this, the latent heat of the liquid-phase refrigerant flowing out of the ejector 30 can be recovered by reducing the enthalpy at the inlet of the evaporator 50 using the internal heat exchanger 70 .

Additionally, a vapor/liquid separator 60 may be located between the ejector 30 and the compressor 10 . An internal heat exchanger 70 that exchanges heat between the refrigerant flowing out of the radiator 20 and the refrigerant flowing out of the vapor/liquid separator 60 and sucked by the compressor 10 is located between the vapor/liquid separator 60 and the compressor 10 . According to this, the internal heat exchanger 70 can perform heat exchange on the downstream side of the vapor/liquid separator 60 . As a result, liquid-phase refrigerant can be prevented from flowing into the compressor 10 .

(fifth embodiment)

5 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to a fifth embodiment of the present invention. The features of the fifth embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, the vapor/liquid separator 60 is located between the ejector 30 and the compressor 10 . An internal heat exchanger 70 that exchanges heat between refrigerant flowing out of the radiator 20 and refrigerant flowing out of the ejector 30 and into the vapor/liquid separator 60 is located between the ejector 30 and the compressor 10 . According to this, the internal heat exchanger 70 performs heat exchange on the upstream side of the vapor/liquid separator 60 . For this reason, it is possible to prevent liquid-phase refrigerant from flowing into the compressor 10 . Furthermore, excessive increase in the discharge temperature of the compressor 10 can be prevented, thus increasing the durability of the high-pressure side pipe and the like.

(sixth embodiment)

FIG. 6 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to a sixth embodiment of the present invention. The features of the sixth embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, a plurality of internal heat exchangers 70A, 70B as heat recovery units for exchanging heat between the refrigerant flowing out of the radiator 20 and the refrigerant flowing out of the ejector 30 and sucked by the compressor 10 are located at the ejector 30 and compressor 10. The vapor/liquid separator 60 is located between the plurality of low pressure refrigerant passages 72a, 72b of the plurality of internal heat exchangers 70A, 70B. In this regard, reference numerals 71a, 71b denote high-pressure refrigerant passages of the internal heat exchangers 70A and 70B of the refrigerant flowing out of the radiator 20 .

According to this, a plurality of internal heat exchangers 70A, 70B are provided, and the vapor/liquid separator 60 is located between the low-pressure refrigerant passages 72a, 72b of the plurality of internal heat exchangers 70A, 70B. Thus, heat is exchanged between the outlet of the ejector 30 and the outlet of the vapor/liquid separator 60 . Therefore, the high-pressure refrigerant can be cooled by the cold refrigerant at the outlet of the vapor/liquid separator 60, and the temperature of the refrigerant at the outlet of the internal heat exchanger 70 can be lowered by the refrigerant (especially liquid refrigerant) at the outlet of the ejector 30 . Therefore, refrigeration capacity and cycle efficiency can be further increased.

In this embodiment, the flow sequence of the refrigerant at the outlet of the ejector 30 and the refrigerant at the outlet of the vapor/liquid separator 60 is shown in FIG. 6 , but the flow sequence may also be reversed. Furthermore, the internal heat exchangers 70A, 70B and the vapor/liquid separator 60 may be formed as an integral module.

(seventh embodiment)

7 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to a seventh embodiment of the present invention. FIG. 8 is a p-h diagram showing a vapor compression type refrigeration cycle using the ejector in FIG. 7 . The features of the seventh embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, the refrigerant flowing from the radiator 20 into the branch passage 55 is used as the refrigerant flowing through the internal heat exchanger 70 .

According to this embodiment, as shown in FIG. heat exchange. Therefore, it is possible to prevent an increase in subcooling at the inlet of the ejector 30 and operate a refrigeration cycle without reducing expansion loss energy in the ejector 30, thereby increasing the amount of pressure increase of the ejector 30. In addition, it is possible to lower the evaporation temperature of the evaporator 50 and increase cooling performance. In FIG. 8, "a" to "g" denote operating states corresponding to positions "a" to "g" of the injection cycle device in FIG. 7, respectively.

(eighth embodiment)

Fig. 9 is a schematic diagram showing a vapor compression type refrigeration cycle (ejection cycle device) using an ejector 30 according to an eighth embodiment of the present invention. FIG. 10 is a p-h diagram showing a vapor compression type refrigeration cycle using the ejector in FIG. 9 . The features of the eighth embodiment that differ from the above-described respective embodiments will be mainly described below.

In this embodiment, the vapor/liquid separator 60 is located between the ejector 30 and the compressor 10 , and the refrigerant flowing into the branch channel 55 and the refrigerant flowing out of the vapor/liquid separator 60 and sucked by the compressor 10 Between the vapor/liquid separator 60 and the compressor 10 is an internal heat exchanger 70 for heat exchange.

According to this embodiment, in the vapor compression type refrigeration cycle using the ejector of the seventh embodiment, the low-pressure refrigerant passage 72 of the internal heat exchanger 70 is formed between the vapor/liquid separator 60 and the compressor 10 . Therefore, the suction superheat of the compressor 10 (from point "d" to point "a" of the p-h diagram of FIG. 10) increases to reduce the suction density of the compressor 10, thereby reducing the flow rate of the refrigerant. Therefore, the compression power of the compressor 10 can be further reduced. In FIG. 10, "a" to "g" denote operating states corresponding to positions "a" to "g" of the injection cycle device in FIG. 9, respectively.

(ninth embodiment)

11 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to a ninth embodiment of the present invention. This embodiment is the same as the sixth embodiment in that a plurality of internal exchangers are provided as heat recovery units for exchanging heat between the refrigerant flowing out of the radiator 20 and the refrigerant flowing out of the ejector 30 and sucked by the compressor 10. Heater 70A, 70B; and vapor/liquid separator 60 are located between the plurality of low pressure refrigerant passages 72a, 72b of the plurality of internal heat exchangers 70A, 70B. In this embodiment, a plurality of internal heat exchangers 70A, 70B are provided as heat recovery units that exchange heat between the refrigerant flowing into the branch passage 55 and the refrigerant flowing out of the ejector 30 and sucked by the compressor 10 , and the vapor/liquid separator 60 is located between the plurality of low-pressure refrigerant passages 72a, 72b of the plurality of internal heat exchangers 70A, 70B.

According to this embodiment, a plurality of internal heat exchangers 70A, 70B are provided, and the vapor/liquid separator 60 is located between the plurality of low-pressure refrigerant passages 72a, 72b. Thus, heat is exchanged between the outlet of the ejector 30 and the outlet of the vapor/liquid separator 60 . Therefore, the high-pressure refrigerant can be cooled by the cold refrigerant at the outlet of the vapor/liquid separator 60, and the temperature of the refrigerant at the outlet of the internal heat exchanger 70 can be cooled by the refrigerant at the outlet of the ejector 30 (especially liquid-phase condensation). agent) decreased. Therefore, refrigeration capacity and cycle efficiency can be further increased.

In this embodiment, the flow sequence of the refrigerant at the outlet of the ejector 30 and the refrigerant at the outlet of the vapor/liquid separator 60 is shown in FIG. 11 , but the flow sequence may also be reversed. Furthermore, the internal heat exchangers 70A, 70B and the vapor/liquid separator 60 may be formed as an integral module.

(tenth embodiment)

Fig. 12 is a schematic diagram showing a vapor compression type refrigeration cycle (ejection cycle device) using an ejector according to a tenth embodiment of the present invention. The features of the tenth embodiment that differ from the above-described respective embodiments will be mainly described below. In this embodiment, a liquid refrigerant supply channel 65 for discharging liquid phase refrigerant from the vapor/liquid separator 60 is provided and disposed in the liquid refrigerant supply channel 65, and the refrigerant is only allowed to flow out of the vapor/liquid separator 60. A check valve (check device, check unit) 80 that flows in the direction of 60 so that the liquid-phase refrigerant supplied from the liquid refrigerant supply passage 65 flows into the upstream side of the refrigerant flow of the evaporator 50 .

The vapor/liquid separator 60 separates the refrigerant discharged from the ejector 30 into vapor-phase refrigerant and liquid-phase refrigerant, and returns the liquid-phase refrigerant from the liquid refrigerant supply passage 65 to the upstream of the evaporator 50, thereby increasing The amount of refrigerant flowing through the evaporator 50. According to this embodiment, the refrigeration capacity can be enhanced by increasing the enthalpy difference in the evaporator 50, and the power can be reduced by increasing the suction pressure of the compressor 10, thus greatly increasing the COP.

The liquid refrigerant supply passage 65 does not need to be provided with a differential pressure valve for controlling pressure, but only needs to be provided with the check valve 80 . In this embodiment, when there is little liquid refrigerant in the vapor/liquid separator 60 , the gas refrigerant flows into the evaporator 50 to increase the pressure loss, thereby preventing the refrigerant from flowing out of the vapor/liquid separator 60 . On the contrary, when there is much liquid refrigerant in the vapor/liquid separator 60 , the pressure loss decreases, so more liquid refrigerant flows into the evaporator 50 . In this manner, the flow of refrigerant from the vapor/liquid separator 60 can be automatically controlled.

To make this action appropriate, the degree to which liquid refrigerant moves out of the vapor/liquid separator 60 can be adjusted. Furthermore, the check valve 80 may be provided with a fixed throttle for creating a pressure difference. In addition, the throttle unit 40 does not need to be a variable throttle, but may be a variable throttle.

In addition, the ejector 30 is a variable ejector 30 having a variable throttling mechanism 34 capable of controlling the refrigerant flow rate. According to this, the flow rate of the refrigerant can be controlled by the variable throttling mechanism 34 of the variable injector 30, therefore, the throttling unit 40 of the branch passage 55 can be a fixed throttling valve, such as a capillary tube.

(eleventh embodiment)

13 is a diagram showing a vapor compression type refrigeration cycle using an ejector according to an eleventh embodiment of the present invention. In this embodiment, the internal heat exchanger 70 is provided in a vapor compression type refrigeration cycle using the ejector of FIG. 12 . FIG. 14 is a p-h diagram showing a vapor compression type refrigeration cycle using the ejector in FIG. 13 . In FIG. 14, "a" to "g" denote operating states corresponding to positions "a" to "g" of the injection cycle device in FIG. 13, respectively. According to this, as in the eighth embodiment, especially in the vapor compression type refrigeration cycle using the ejector of FIG. between. Therefore, the suction superheat of the compressor 10 (from point g to point a of the p-h diagram of FIG. 14 ) increases to reduce the suction density of the compressor 10, thereby reducing the flow rate of the refrigerant. Therefore, the compression power of the compressor 10 can be further reduced.

This structure is also effective in a supercritical pressure refrigeration cycle. The high-pressure refrigerant passage 71 of the internal heat exchanger 70 in this embodiment is on the outflow side of the radiator 20, but may also be on the inflow side of the branch passage 55 as in the seventh to ninth embodiments. Furthermore, in this embodiment, the low-pressure refrigerant passage 72 of the internal heat exchanger 70 is formed between the vapor/liquid separator 60 and the compressor 10 . However, as in the fifth and seventh embodiments, the low-pressure refrigerant passage 72 of the internal heat exchanger 70 may also be formed between the ejector 30 and the vapor/liquid separator 60, or as in the sixth and ninth embodiments. , a plurality of internal heat exchangers 70A, 70B of both sides may be provided.

In the above-described embodiments, the injection cycle device is typically used for an air conditioner of a vehicle. However, the jet cycle device can also be used in heating units such as water heaters, and cooling units such as refrigeration and cooling units including vehicle-mounted and stationary types. Furthermore, in the above-described embodiments, a critical pressure cycle using carbon dioxide (CO ₂ ) may be used as the refrigeration cycle in the jet cycle device. However, a jet cycle device using an ejector in which the pressure of the high-pressure refrigerant is lower than the critical pressure of the refrigerant may be used, and the refrigerant may be a hydrocarbon (HC)-based natural refrigerant or a Freon-based refrigerant.

Furthermore, in the above-described embodiment, a variable capacity compressor is used as the compressor 10 . However, an electrically operated compressor that can easily control the number of rotations may be used. In addition, the fixed injector 30 is used in the above-mentioned embodiment, but it is also recommended that a throttling unit (not shown) be provided on the upstream side of the refrigerant flow from the nozzle 31 of the injector 30, and that the pressure of the refrigerant passes through this throttling unit and Nozzles 31 are reduced in two stages.

The fixed injector 30 that cannot control the flow rate is used in the first to ninth embodiments described above, but a mechanically or electrically variable injector 30 that can control the flow rate may also be used. The flow of the ejector 30 can be performed by controlling the flow of the compressor 10 (including on/off control). Alternatively, the flow rate of the ejector 30 can be set in the ejector 30 according to the state (pressure or temperature) of the refrigerant at the outlet of the radiator 20, or the state (pressure or temperature) of the refrigerant at the outlet of the evaporator 50. The variable throttling mechanism control.

(twelfth embodiment)

Hereinafter, a twelfth embodiment of the present invention will be described in detail by using FIGS. 15 and 16 . 15 is a schematic diagram showing an injection cycle device according to a twelfth embodiment of the present invention, and shows a cooling operation mode, for example, an air cooling operation mode. In addition, FIG. 16 is a diagram showing a heating operation mode, for example, an air heating operation, in the spray cycle device of FIG. 15 .

The cooling operation mode is an operation mode in which air or water for air conditioning as a medium to be cooled is cooled by making an indoor heat exchanger or a vehicle-mounted heat exchanger as a use-side heat exchanger low temperature. The cooling operation mode may be an air cooling operation when used for an air conditioner, or may be a cooling or freezing operation when used for a refrigerator or a freezer.

The heating operation mode is an operation mode for heating air or water for air conditioning as a medium to be heated by making an indoor heat exchanger or a vehicle-mounted heat exchanger as a use-side heat exchanger high temperature. The heating operation mode may be an air heating operation when used for an air conditioner, or may be a heating operation when used for a high temperature storage unit, or may be a water heating operation when used for a water heater. In this embodiment, the injection cycle device according to the present invention is used for an air conditioner of such a vehicle using carbon dioxide (CO ₂ ) as a refrigerant.

The compressor 10 is supplied with a driving force from a driving source such as a driving motor (not shown), and sucks and compresses refrigerant, and the compressor 10 in this embodiment adopts a variable capacity compressor that compresses The discharge flow rate (discharge capacity) is variably controlled so that the temperature of the refrigerant sucked by the machine 10 becomes a predetermined temperature. The discharge flow rate (discharge capacity) of the compressor 10 is controlled by an electronic control unit 100 as a control device.

The four-way valve 160 as a channel conversion unit is connected to the discharge side of the compressor 10, and converts high-pressure refrigerant discharged from the compressor 10 and is supplied to the outdoor heat exchanger 20 (for example, a radiator in a cooling operation mode), Or the outlet of the injector, both of which will be described later. The four-way valve 160 is controlled by the electronic control unit 100 .

The outdoor heat exchanger 20 is a heat exchanger that exchanges heat between refrigerant flowing inside and air outside the vehicle compartment blown by a blower (not shown) as an external fluid. In addition, the indoor heat exchanger 50 (for example, an evaporator in the cooling operation mode) as a first heat exchanger is the connection between the refrigerant flowing inside and the air conditioner blown into the vehicle cabin by a blower (not shown) as an external fluid. A heat exchanger for exchanging heat between air and air.

Reference numeral 40 is a throttling unit such as a capillary tube (fixed throttle valve) for reducing the pressure of the flowing refrigerant. The ejector 30 reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 20 through the nozzle portion 31, thereby expanding the refrigerant and sucking the vapor-phase refrigerant evaporated in the indoor heat exchanger 50 from the suction portion 33, and converting the expansion energy into The pressure energy, thereby increasing the suction pressure of the compressor 10. Refrigerant flowing out of this ejector 30 is sucked through the compressor 10 . In this way, a refrigerant circulation passage is formed in the injection cycle device.

The injector 30 has: a first connecting portion communicating with the large-diameter side of the nozzle portion 31; a second connecting portion located on the downstream side of the spray flow from the nozzle portion 31 and communicating with a diverging portion of the injector 30; A third connection portion in which the suction space around the small-diameter side of the nozzle portion 31 communicates. In this embodiment, the direction of refrigerant flow in the second connection portion and the third connection portion during the cooling operation is opposite to the direction of refrigerant flow during the heating operation. In the cooling operation, the second connection portion becomes an outlet of the ejector 30 , and the third connection portion becomes a suction inlet of the ejector 30 . In a heating operation, the second connection portion becomes an inlet of the injector 30 , and the third connection portion becomes an outlet of the injector 30 .

In this refrigerant circulation passage, a branch point is provided between the outdoor heat exchanger 20 and the nozzle part 31 of the ejector 30, and a branch passage 55 for connecting this branch point to the suction part 33 is provided. Furthermore, the throttling unit 40 is disposed on the branch point side of the branch passage 55 , and the indoor heat exchanger 50 is disposed on the suction portion 33 side of the branch passage 55 .

Next, the operation of the injection cycle apparatus constructed as described above will be described. First, as shown in FIG. 15 , an air cooling operation mode in which the indoor heat exchanger 50 is used as an evaporator on the low temperature side (the first mode in the present invention) will be described. When the compressor 10 is activated, the vapor-phase refrigerant is sucked from the suction side through the compressor 10 , and the compressed refrigerant is discharged to the outdoor heat exchanger 20 through the four-way valve 160 . The refrigerant cooled by the outdoor air in the outdoor heat exchanger 20 is branched into a driving flow flowing into the nozzle 31 of the ejector 30 and a suction flow passing through the throttling unit 40 and the indoor heat exchanger 50 .

The refrigerant flowing into the nozzle 31 is compressed and expanded, and the refrigerant is sucked in the evaporator 50 . The refrigerant of the suction flow sucked into the suction port 33 of the ejector 30 from the evaporator 50 is mixed with the refrigerant of the driving flow injected from the nozzle 31 in the mixing portion. The mixed refrigerant has its dynamic pressure converted into static pressure through the diffusion part, and the refrigerant flowing out of the ejector 30 returns to the compressor 10 through the four-way valve 160 . On the contrary, the refrigerant of the suction flow has its pressure reduced by the throttling unit 40 and then flows into the indoor heat exchanger 50 . The refrigerant flowing into the indoor heat exchanger 50 is evaporated by absorbing heat from the air for air conditioning blown into the vehicle cabin to cool the air for air conditioning, and then sucked into the suction port 33 of the ejector 30 .

At this time, in the mixing portion of the ejector 30, the driving flow from the nozzle 31 is mixed with the suction flow from the indoor heat exchanger 50 in such a manner that the sum of the momentum of the driving flow and the momentum of the suction flow is conserved. Therefore, the pressure (static pressure) of the refrigerant also increases in the mixing portion. In addition, as described above, in the diverging portion of the ejector 30, the cross-sectional area of the passage gradually increases, and thus, the velocity energy (dynamic pressure) of the refrigerant is converted into pressure energy (static pressure). Therefore, in the ejector 30, the pressure of the refrigerant increases at both the mixing part and the diffusing part.

Therefore, the mixing section and the diffusion section are generally referred to as the pressure increasing section 32 . In other words, in an ideal ejector 30, the pressure of the refrigerant increases in the mixing portion in such a way that the sum of the momentum of the driving flow and the momentum of the suction flow is conserved, and the pressure of the refrigerant increases in the diffusing portion in a manner that conserves energy .

Next, the heating operation mode (the second mode in the present invention) in which the indoor heat exchanger 50 changes to the high pressure side as shown in FIG. 16 will be described. When the compressor 10 is activated, the vapor-phase refrigerant is sucked from the suction side by the compressor 10 , and the compressed refrigerant is supplied to the outlet side (diffusion side) of the ejector 30 through the four-way valve 160 .

The refrigerant supplied from the second connection portion of the ejector 30 flows through the diffusion portion and the mixing portion, and reaches the tip of the nozzle portion 31 on the small diameter side. At this time, since the tip of the nozzle portion 31 is opened with a small diameter, it is difficult for the refrigerant to flow into the nozzle portion 31, the refrigerant flows into the suction space surrounding the nozzle portion 31, and flows out to the third connection portion (suction portion 33). .

As a result, the refrigerant flows opposite to the flow direction of the fluid pump as the ejector 30 and then flows into the heat exchanger 50 . Therefore, even if the nozzle portion 31 of the ejector 30 is always open, or is not provided with a valve that can close the passage thereof, a large amount of refrigerant can be prevented from flowing into the nozzle portion 31 .

When the nozzle portion 31 of the injector 30 is provided with a needle valve as a valve that can open and close the passage of the nozzle portion 31, it is also recommended to provide a drive mechanism for closing the needle valve and provide a device with a control mechanism for the drive mechanism. The control unit 100. In addition, the opening/closing valve may be provided on the upstream side of the nozzle portion 31 , that is, in the passage of the heat exchanger 20 , the opening/closing valve may be opened and closed by the control unit 100 .

The refrigerant flowing through the ejector 30 and out of the suction portion 33 flows through the indoor heat exchanger 50 and heats air for air conditioning, which flows into the vehicle compartment to be cooled. The refrigerant flowing out of the indoor heat exchanger 50 has its pressure reduced by the throttling unit 40, then flows into the outdoor heat exchanger 20 and absorbs heat from the outside air and evaporates. The refrigerant flowing out of the outdoor heat exchanger 20 flows through the four-way valve 160 and returns to the compressor 10 .

Next, features and effects of the twelfth embodiment will be described. First, the ejector cycle device of this embodiment includes: a compressor 10 that sucks, compresses, and discharges refrigerant; The inlet and the discharge port are connected in series, and the high-pressure refrigerant supplied from the inlet is sprayed to the discharge port, thereby sucking the refrigerant from the suction port 33 and delivering the refrigerant to the discharge port; the branch connecting the inlet to the suction port 33 the passage 55 ; the indoor heat exchanger 50 provided in the branch passage 55 ; and the four-way valve 160 . The four-way valve 160 is in a first mode in which high-pressure refrigerant is supplied to the inlet of the nozzle 31 of the ejector 30 and the refrigerant flows from the indoor heat exchanger 50 to the suction port 33 , and high-pressure refrigerant is supplied to the discharge port of the ejector 30 and The second mode in which the refrigerant flows from the suction port 33 to the indoor heat exchanger 50 is switched.

In this embodiment, the high pressure refrigerant flow discharged from the compressor 10 is switched between flowing to the inlet of the ejector 30 and flowing to the discharge through the four-way valve 160 . When the high-pressure refrigerant discharged from the compressor 10 flows to the discharge port, the ejector 30 functions as a passage through which the refrigerant flows, such as a simple pipe.

According to this, the high-temperature side and the low-temperature side in the injection cycle device are switched by a simple construction. Therefore, the cost can be reduced and the ease of installing this cycle can be increased. In this embodiment, when the indoor heat exchanger 50 is used as the first heat exchanger and the outdoor heat exchanger 20 is used as the second heat exchanger, the third heat exchanger may be located between the ejector 30 and the compressor 10 between. This third heat exchanger may be constituted by a unit separate from the indoor heat exchanger 50 , and may be provided to flow air independently from the indoor heat exchanger 50 . In addition, the third heat exchanger may be integrally formed with the indoor heat exchanger 50 and arranged to flow air in series.

The throttling unit 40 that makes the indoor heat exchanger 50 low temperature in the first mode and high temperature in the second mode is located between the inlet of the nozzle 31 of the ejector 30 and the indoor heat exchanger 50 . The outdoor heat exchanger 20 that becomes high temperature in the first mode and low temperature in the second mode is disposed in the refrigerant circulation passage. According to this, a vapor compression type heat pump cycle that transfers heat at a low temperature side to a high temperature side may be constituted between the indoor heat exchanger 50 and the outdoor heat exchanger 20 .

In this embodiment, since _CO2 is used as the refrigerant, the refrigerant pressure on the high pressure side is greater than the critical pressure. In the state of a two-phase flow in which gas and liquid are mixed at a pressure lower than the critical pressure, the velocity of the refrigerant flow in the nozzle portion 31 is reduced by slip of liquid and gas (imbalance of velocity) , therefore, the pressure increase for injector 30 efficiency is reduced. However, according to this embodiment, by operating high-pressure refrigerant at a supercritical pressure, the refrigerant in the ejector 30 becomes a single-phase flow. Therefore, this can increase the efficiency of the injector 30 itself, and increase the amount of increase in the pressure of the injector 30, and thus can increase the cooling performance.

(thirteenth embodiment)

Fig. 17 is a schematic diagram showing an injection cycle device in a thirteenth embodiment according to the present invention. Differences between this embodiment and the twelfth embodiment will be mainly described below. In this embodiment, the internal heat exchanger 70 as a heat recovery unit that exchanges heat between the refrigerant flowing out of the outdoor heat exchanger 20 and the refrigerant flowing out of the ejector 30 and sucked by the compressor 10 in the first mode Located between the ejector 30 and the compressor 10 .

According to this, the effect of reducing enthalpy at the inlet of the indoor heat exchanger 50 is produced by providing the inner heat exchanger 70 such as a jacket with increased subcooling. Therefore, it is possible to increase the enthalpy difference between the inlet and the outlet of the indoor heat exchanger 50 , thus increasing the cooling performance of the indoor heat exchanger 50 .

In the refrigeration cycle with the internal heat exchanger 70 , the degree of superheat on the suction side of the compressor 10 is increased, and the discharge temperature of the compressor 10 is increased, compared with a conventional refrigeration cycle without the internal heat exchanger 70 . However, in the present invention, the suction pressure can be increased by the pressure increasing action of the ejector 30, and therefore, the increase of the discharge temperature can be prevented. In this embodiment, as shown in FIG. 17 , the high-pressure refrigerant passage 71 of the internal heat exchanger 70 is disposed between the outdoor heat exchanger 20 and the inlet of the nozzle 31 , and the low-pressure refrigerant passage 72 of the internal heat exchanger 70 It is provided between the outlet of the ejector 30 and the suction port of the compressor 10 . The high-pressure refrigerant passage 71 of the internal heat exchanger 70 may be located between a branch point of the branch passage 55 and the nozzle part 31 .

(fourteenth embodiment)

Fig. 18 is a diagram showing an injection cycle device in a fourteenth embodiment according to the present invention. Differences between this embodiment and the above-described twelfth and thirteenth embodiments will be described below. In this embodiment, the refrigerant flowing into the branch passage 55 is used as the refrigerant flowing through the internal heat exchanger 70 . That is to say, as shown in FIG. (diffuser side). According to this embodiment, the effect of reducing enthalpy at the inlet of the indoor heat exchanger 50 is produced by increasing subcooling. Therefore, it is possible to increase the enthalpy difference between the inlet and the outlet of the indoor heat exchanger 50 , thus increasing the cooling performance of the indoor heat exchanger 50 .

In addition, as described above, when an additional heat exchanger (third heat exchanger) is located between the ejector 30 and the compressor 10, the enthalpy at the outlet of the indoor heat exchanger 50 decreases, and therefore, the The enthalpy at the inlet of the third heat exchanger where the refrigerant joins is reduced in the cooling mode of operation. Therefore, it is also possible to increase the cooling performance of the third heat exchanger in the cooling operation mode.

(fifteenth embodiment)

Fig. 19 is a schematic diagram showing an injection cycle device in a fifteenth embodiment according to the present invention. Differences between this embodiment and the above-described twelfth and fourteenth embodiments will be described below. In this embodiment, first, the third heat exchanger 51 that exchanges heat between the refrigerant and the air for air conditioning blown into the vehicle cabin is located between the ejector 30 and the compressor 10, and the second throttling unit 41 (throttling device) is located between the suction portion 33 and the indoor heat exchanger 50 .

According to this, in the case of the air heating operation mode (second mode), high-pressure refrigerant discharged from the compressor 10 flows through the heat exchanger 51 to reach a state where it can heat external fluid (outside air). Then, the high-pressure refrigerant flows through the ejector 30, is decompressed by the second throttling unit 41, and flows through the indoor heat exchanger 50, thereby reaching a state where it can cool the external fluid (outside air). Therefore, when the air used for air conditioning flows through the indoor heat exchanger 50 and the third heat exchanger 51 successively, the air used for air conditioning may be dehumidified and may be heated at an appropriate temperature.

On the contrary, when the second throttle unit 41 is fully opened, the third heat exchanger 51 and the indoor heat exchanger 50 function as heat exchangers for air heating. In addition, the air can be dehumidified and heated by controlling the throttling degree of the second throttling unit 41 . In addition, the indoor heat exchanger 50 and the third heat exchanger 51 may be formed as an integral unit. In this case, it is possible to reduce the cost by forming it as a whole, and remove an extra space between the heat exchangers 50, 51, thus improving the ease of installing the heat exchangers 50, 51.

(Sixteenth embodiment)

Fig. 20 is a diagram showing an injection cycle device in a sixteenth embodiment according to the present invention. Differences between this embodiment and the above-described twelfth to fifteenth embodiments will be described below. In this embodiment, the injector 30 is used as the first injector, and the second injector 35 and the second branch passage 56 are provided on the outdoor heat exchanger 20 side. In the jet cycle device, high-pressure refrigerant on the downstream side of the indoor heat exchanger 50 flows into the inlet of the nozzle portion 31 of the second ejector 35 at the time of the air heating operation mode (second mode). In addition, the second branch passage 56 guides the refrigerant flow branched from the refrigerant circulation passage, and the outdoor heat exchanger 20 is disposed in the second branch passage 56 and evaporates the refrigerant.

In the air cooling operation mode (first mode), the second ejector 35 may only be used as a refrigerant passage.

In the air cooling mode of operation and the air heating mode of operation, it is desirable to reduce the power of the compressor 10 by the pressure increasing action of the ejector 30 . However, in the structure of the twelfth embodiment, the action of the ejector 30 can be produced in the air cooling operation mode, but in the air heating operation mode, the cycle is the same as the general expansion valve cycle. According to the sixteenth embodiment, the second injector 35 is also provided on the outdoor heat exchanger 20 side. Thus, also in the air heating mode of operation, the power reducing effect of the compressor 10 can be produced by the pressure increasing effect of the ejector 35 . In FIG. 20 , the fourth heat exchanger 21 is located between the second ejector 35 and the compressor 10 .

(Seventeenth embodiment)

Fig. 21 is a schematic diagram showing an injection cycle device in a seventeenth embodiment according to the present invention. In the above-described twelfth to sixteenth embodiments, in order to switch between the air heating operation and the air cooling operation, the refrigerant flow direction is switched by the four-way valve 160 . However, in this embodiment, in order to remove frost of the indoor heat exchanger 50 in the cooling operation of the heat pump cycle, the four-way valve 160 is controlled. When the heat pump cycle is continuously operated in the first mode (air cooling operation), the indoor heat exchanger 50 (evaporator), which reaches a low temperature, may have frost deposited thereon.

In particular, the indoor heat exchanger 50 serving as the first heat exchanger operates at a lower temperature than the third heat exchanger 51 (see FIG. 19 ), and thus needs to be provided with a frost removing device. Furthermore, since the frost removal time has an impact on the overall heat pump capacity, a frost removal device that has a direct effect and can shorten the required frost removal time is preferred. Therefore, like the above-described twelfth to sixteenth embodiments, the four-way valve 160 is switched to the opposite direction of refrigerant flow, thereby removing frost. According to this, frost can be efficiently removed in a short time by a simple operation of only switching the four-way valve 160 .

In addition, the flow of refrigerant flowing through the nozzle portion 31 of the ejector 30 may be interrupted. Furthermore, when the refrigerant is caused to flow out of the suction port 33, the flow of the refrigerant of the nozzle portion 31 is interrupted. According to this, in the mode in which the refrigerant flows from the suction port 33 to the first heat exchanger 50, by interrupting the flow of refrigerant flowing through the nozzle portion 31, high-temperature refrigerant can flow through the first heat exchanger 50 without loss. , thus improving the frost removal performance of the first heat exchanger 50 .

In short, according to the frost removing operation (defrosting operation) of this embodiment, frost can be efficiently removed in a short time. The structure that can interrupt the refrigerant flowing through the nozzle part 31 can be realized by completely closing the variable nozzle mechanism (not shown), or can be realized by providing an opening/closing device (not shown) on the upstream side of the refrigerant flow of the nozzle part 31. )accomplish. In addition, this frost removal method is not limited to an ejector type heat pump cycle, but can also be applied to a vapor compression type refrigeration cycle using a normal ejector.

When the deposition of frost is detected by a temperature sensor (not shown) provided in the heat exchanger 50 when removing frost, and the operation is continuously performed at a predetermined temperature for a time longer than a prescribed time, the refrigerant flows through the four-way valve 160 reverse to start frost removal operation. Alternatively, the accumulated operating time of the compressor 10 may be previously determined for each determined outside air temperature range. In this case, the frost removal operation is started every time the prescribed accumulated operation time is reached. By turning the four-way valve 160 in the cooling operation state into the heating operation state, the frost removal operation is provided for a predetermined time, or until the effect of frost removal is detected by the temperature sensor 50b.

In addition, in order to prevent hot air from being blown into the space to be cooled, the blower 50a of the evaporator 50 may be stopped during the frost removal operation. In addition, the ejector 30 may be constructed so as to be completely closed during the frost removal operation so as to reliably flow the high-temperature refrigerant flow to the heat exchanger 50 . In addition, the cycle in Fig. 21 is also recommended as a dedicated cycle for cooling operations.

In the case of a cooling-operation-dedicated cycle, when the frost-removing operation of the indoor heat exchanger 50 is required, the four-way valve 160 is reversed to the frost-removing operation state. In addition, in FIG. 21, by using the heat exchanger 50 provided in the branch passage as an outdoor heat exchanger, and by using the heat exchanger 20 as an indoor heat exchanger as a use-side heat exchanger, the cycle can be used as A dedicated cycle for heating operations. In this case, when the frost removal operation of the outdoor heat exchanger 50 is required, the four-way valve 160 is reversed to the frost removal operation state.

According to this embodiment, when the heat exchanger 50 connected between the upstream side of the ejector 30 and the suction port of the ejector 30 needs to remove frost, the high-pressure refrigerant is supplied from the outlet of the ejector 30 and passes through the outlet of the ejector 30. The suction port 33 is supplied to the heat exchanger 50, thereby performing a frost removal operation. As a result, frost can be removed from the heat exchanger 50, which is generally used as an evaporator in cooling operation, by a simple structure and control.

In the above-described embodiments other than the ones shown in FIGS. 19 , 20 , the refrigerant cycle has at least one ejector 30 and at least one heat exchanger 50 . The heat exchanger 50 may be provided on the secondary pipeline between the suction port of the ejector 30 and the nozzle inlet of the ejector 30 . In this case, the heat exchanger 50 performs heat exchange between refrigerant passing therethrough and an external medium to be cooled or heated. For example, in the case of a cooling operation, the heat exchanger 50 is a heat exchanger located in the room to be cooled. On the other hand, in the case of heating operation, the heat exchanger 50 is a heat exchanger located outside the room to be heated. The cycle has no external heat exchanger between the outlet of the ejector 30 and the compressor 10 on the main line. The cycle may include at least one internal heat exchanger 70 on its main line. The cycle may have a controller 100 as shown in FIG. 15 to achieve a predetermined value on the heat exchanger 50 by controlling at least one operational factor such as the degree of opening of the throttling member (40, 45, 34) and the operation of the compressor 10. cooling or heating performance. The compressor 10 may be a fixed capacity type, a variable capacity type, or a motor driven type with an on-off clutch. The throttling components (40, 45, 34) can be electromagnetic valves, which can adjust the opening degree of the throttling passages therein. In a preferred embodiment, the controller 100 controls the operating factors to keep the amount of liquid refrigerant flowing into the compressor 10 below a certain amount that is allowed by the compressor 10 . For example, the controller controls the valve 40 and the compressor 10 in order to keep the refrigerant on the suction port of the compressor 10 in a dry state or in a superheated state.

(Eighteenth Embodiment)

Fig. 22 is a diagram showing an example in which the ejector and the ejector cycle device of the present invention are applied to air-conditioning and refrigeration equipment for vehicles.

First, a refrigerant circulation channel 110 for circulating refrigerant is provided in the jet cycle device. In the refrigerant circulation passage 110, a compressor 111 sucks, compresses, and discharges refrigerant, and is rotated and driven by a vehicle drive engine (not shown) through an electromagnetic clutch 111a and a belt.

In this embodiment, a swash plate type variable capacity compressor in which the displacement is continuously controlled by a control signal from the outside is used. Here, the discharge volume means the geometric volume of the operation space where refrigerant is sucked and compressed, and means the cylinder volume between the upper dead center and the lower dead center of the piston stroke.

In the swash plate type variable capacity compressor, the pressure of the swirl chamber or swash chamber (not shown) is controlled by using the discharge pressure and the suction pressure to change the inclination angle of the swash plate and change the piston stroke, thereby Allows the excluded volume to be varied continuously from approximately 0% to 100%.

The compressor 111 has an electromagnetic displacement control valve 111b in order to control the pressure of the swirl chamber. A pressure reaction mechanism (not shown) that generates a force F1 by the pressure of the low-pressure refrigerant on the suction side of the compressor 111 and an electromagnetic mechanism (not shown) that generates an electromagnetic force F2 opposing the force F1 by the pressure of the low-pressure refrigerant Ps are provided. In this electromagnetic capacity control valve 111b.

The electromagnetic force F2 of this electromagnetic mechanism is determined by controlling the current output from the air conditioner control unit 122 (A/C ECU) which will be described later. The pressure of the swirl chamber is changed by changing the flow rate of high pressure refrigerant guided into the swirl chamber by a valve body (not shown) displaced according to force F1 and electromagnetic force F2 responsive to the pressure Ps of the low pressure refrigerant.

In addition, the discharge volume of the compressor 111 can be continuously changed approximately from 100% to 0% by controlling the pressure of the swirl chamber. Therefore, the compressor 111 can reach a state where the operation is substantially stopped by reducing the discharge volume to approximately 0%. Therefore, a clutchless structure in which the rotary shaft of the compressor 11 is always connected to the engine of the vehicle through the pulley and the belt V can be used.

The refrigerant radiator 112 is provided on the refrigerant discharge side of the compressor 111 . The radiator 112 is a heat exchanger for cooling the high-pressure refrigerant by exchanging heat between high-pressure refrigerant discharged from the compressor 111 and outside air (air outside the vehicle compartment) blown by the blower 112 a for the radiator 112 .

The blower 112a for the radiator 112 is driven by a driving motor 112b. And when the applied voltage is output from the air conditioner control unit 122 which will be described later, the driving motor 112b is rotated and driven. In addition, in this embodiment, a common Freon-based refrigerant is used as the refrigerant circulating in the cycle, and therefore, the ejector cycle device constitutes a subcritical pressure cycle with a high pressure not higher than the critical pressure of the refrigerant. Therefore, the radiator 112 functions as a condenser for condensing refrigerant.

The ejector 114 is connected to the downstream side of the radiator 112 through the refrigerant pipe 113 . The ejector 114 in this embodiment performs the function of a pressure reducing device for reducing the pressure of the refrigerant, and also performs a refrigerant cycle device for circulating the refrigerant by the suction effect (entrainment effect) of the refrigerant flow ejected at high speed function. In addition, the ejector 114 performs a function of a pressure reducing device that reduces the pressure of refrigerant flowing into a branch point of the branch passage 118 and the branch passage 118 that will be described later.

The structure of the injector 114 of this embodiment will be described using FIG. 23 . The injector 114 is composed of a housing 114 a , a nozzle portion 114 b , a diffuser portion 114 c , and a passage area control mechanism 115 .

The housing 114a functions to fix and protect the constituent parts of the injector 114 . The casing 114a has: a refrigerant inflow port 114d (first connecting portion) through which the refrigerant flowing out of the refrigerant pipe 113 flows into the injector 114; a refrigerant outflow port 114e (fourth connecting portion); and a refrigerant suction port 114f (third connecting portion) provided in communication with the refrigerant injection port 114h of the nozzle portion 114b and sucking refrigerant from the branch passage 118b.

The refrigerant pipe 113 is connected to the refrigerant inflow port 114d, the branch channel 118a is connected to the refrigerant suction port 114f, and the branch channel 118a is connected to the branch refrigerant outflow port 114e in a passing manner. These connection parts are connected by welding in order to prevent leakage of refrigerant.

The nozzle portion 114b reduces the area of the refrigerant passage of the refrigerant, and reduces the pressure of the refrigerant so that the refrigerant is isentropically expanded and fixed in the case 114a.

The nozzle portion 114b has: a refrigerant inflow port 114g that communicates the refrigerant inflow port 114d with the inside of the nozzle portion 114b so that the refrigerant flows into the nozzle portion 114b; to a refrigerant injection port 114h in a mixing portion 114j which will be described later; and a branch refrigerant outflow port which is provided on the upstream side of the refrigerant injection port 114h and communicates the inside of the nozzle portion 114b with the branch refrigerant outflow port 114e 114i.

In addition, the branch passage 118a passing through the branch refrigerant outflow port 114e is connected to the branch refrigerant outflow port 114i by welding or the like in order to prevent refrigerant leakage.

In addition, a mixing portion 114j is formed in the housing 114a on the downstream side of the refrigerant flow from the refrigerant injection port 114h. The mixing part 114j is provided to mix the refrigerant injected from the refrigerant injection port 114h with the refrigerant sucked in from the refrigerant suction part 114f.

The diverging portion 114c forming the pressure increasing portion is provided on the downstream side of the refrigerant flow from the mixing portion 114j. This diffusion portion 114c is formed into a shape that gradually increases the passage area of the refrigerant, and functions to decelerate the flow of the refrigerant to increase the pressure of the refrigerant. In other words, the diffusion portion 114c converts the velocity energy of the refrigerant into its pressure energy.

Further, the diffuser portion 114c has a diffuser outflow port 114l (second connection portion) through which the refrigerant passing through the diffuser portion 114c flows out. The diffusion portion 114c is also connected by welding or the like in order to prevent refrigerant leakage.

The passage area control mechanism 115 is fixed to the top (top side in FIG. 23 ) of the nozzle portion 114b of the housing 114a by using screws or the like through a seal or the like so as to prevent refrigerant leakage. The injector 114 and the passage area control mechanism 115 are integrally formed as a unitary structure.

The passage area control mechanism 115 is constituted by a needle 115a and a drive portion 115b. The needle 115a has an elongated pointed end portion approximately the same shape as the inner passage of the nozzle portion 114b and a shaft portion connected to the rotor 115c. The shaft portion of the needle 115a is connected to the rotor 115c by a screw-type connection portion, so that when the screw-type connection portion is rotated, the shaft portion of the needle 115a can be in the nozzle portion 115b along the lengthwise direction (shown by the arrow in FIG. 23 ). direction) to move.

The driving section 115b is constituted by a well-known stepping motor. When a control signal (pulse signal) is output from an air conditioner control unit 122 to be described later, the rotor 115c of the drive portion 115b rotates. As the rotor 115c rotates, the threaded connection portion of the rotor 115c rotates to move the needle 115a.

Here, control of the amount of refrigerant flowing through the refrigerant injection port 114h and the branch refrigerant outflow port 114i will be described with reference to FIGS. 24A and 24B. FIG. 24A shows a state in which the needle 115a moves in a direction approaching the refrigerant injection port 114h (direction indicated by arrow A in FIG. 24A).

First, the annular gap formed between the needle 115a and the upstream portion of the branch refrigerant outflow port 114i becomes the throttle passage C passing through the branch refrigerant outflow port 114i and the refrigerant injection port 114h. When the needle 115a moves in a direction close to the refrigerant injection port 114h, the area of this throttle passage C decreases.

At the same time, the annular gap formed between the refrigerant injection port 114h and the tip of the needle 115a becomes the throttle passage D passing through the branch refrigerant injection port 114h. When this needle 115a moves in a direction close to the refrigerant injection port 114h, the area of the throttle passage D decreases.

The refrigerant passing through the throttling passage C flows through the branch refrigerant outflow port 114i to reach the branch passage 118a. Meanwhile, the refrigerant that does not flow out to the branch passage 118a passes through the throttle passage D, and is discharged from the refrigerant injection port 114h. In other words, the refrigerant branches on the downstream side of the throttle passage C. As shown in FIG.

FIG. 24B shows a state where the needle 115a moves in a direction away from the refrigerant injection port 114h (the direction indicated by the arrow B in FIG. 24B ). When the needle 115a moves in this direction B, the area of the throttle passage C increases and the area of the throttle passage D also increases compared with FIG. 24A.

Therefore, when the needle 115a is moved by the driving portion 115b, the area of the refrigerant passage branched to the branch passage 118a and the passage area of the refrigerant injected from the refrigerant injection port 114h of the nozzle portion 114b are changed.

In summary, the needle 115a is the passage area control means in this embodiment, and the throttle passage C constituted by the nozzle portion 114a and the needle 115a becomes a variable throttle mechanism. Furthermore, in the embodiment, the structure in which the refrigerant branches off on the upstream side of the refrigerant injection port 114h of the ejector 114 includes the structure in which the refrigerant branches off on the upstream side of the nozzle portion 114b.

Second, the first evaporator 116 is connected to the downstream side of the refrigerant flow of the diffuser portion 114 c of the ejector 114 . The first evaporator 116 is disposed in a housing of a vehicle-mounted air conditioning unit (not shown), and performs an operation of cooling air used for air-conditioning a vehicle cabin.

Specifically, air for air conditioning the vehicle cabin is blown into the first evaporator 116 through the first evaporator blower 116a of the vehicle cabin air conditioning unit. Then, the low-pressure refrigerant whose pressure is lowered by the ejector 114 absorbs heat from the air for air-conditioning the vehicle cabin and evaporates, thereby cooling the air for air-conditioning the vehicle cabin, thereby applying cooling capacity.

The first evaporator blower 116a is driven by a driving motor 116b, and when the driving motor 116b has an applied voltage output from an air conditioner control unit 122 which will be described later, the driving motor 116b is rotated and driven.

An accumulator 117 for separating liquid-phase refrigerant from vapor-phase refrigerant is connected to the downstream side of the refrigerant flow of the first evaporator 116 . In addition, the downstream side of the vapor-phase refrigerant of the accumulator 117 is connected to the compressor 111 so that the vapor-phase refrigerant flowing out of the accumulator 117 is sucked by the compressor 111 and circulated in the refrigerant circulation passage 110 again.

The branch passage 118 is connected to the branch refrigerant outflow port 114e of the ejector 114 . This branch passage 118 is composed of a branch passage 118a connecting the branch refrigerant outflow port 114e of the ejector 114 to the inlet of the second evaporator 119, and a branch passage 118a connecting the outlet of the second evaporator 119 to the refrigerant suction port 114f of the ejector 114. The branch channel 118b constitutes.

The second evaporator 119 is provided in a refrigerator (not shown) installed in a vehicle compartment, and performs a cooling operation for cooling the inside of the refrigerator.

For example, air in the refrigerator is blown into the second evaporator 119 through the second evaporator blower 119a as air for cooling the inside of the refrigerator. Then, the low-pressure refrigerant whose pressure is reduced by the ejector 114 absorbs heat from the air used to cool the inside of the refrigerator and evaporates in the second evaporator 119 . The air used to cool the inside of the refrigerator is thereby cooled.

The second evaporator blower 119a is driven by a driving motor 119b, and when the driving motor 119b has an applied voltage output from an air conditioner control unit 122 which will be described later, the driving motor 119b is rotated and driven.

In addition, this embodiment is provided with a refrigerant guide passage 120 for connecting the liquid-phase refrigerant side of the accumulator 117 to the inlet of the second evaporator 119 . This refrigerant guide passage 120 is a refrigerant passage for guiding liquid-phase refrigerant in the accumulator 117 into the second evaporator 119 . A check valve 121 allowing only refrigerant to flow from the accumulator 117 to the second evaporator 119 is provided in the refrigerant guide passage 120 .

The air conditioner control unit 122 is constituted by a well-known microcomputer including a CPU, ROM, RAM, etc., and peripheral circuits thereof. The air conditioner control unit 122 performs various calculations and processes according to control programs stored in the ROM to control the operations of the above-mentioned various parts (111a, 111b, 112b, 115b, 116b, 119b).

Furthermore, detection signals from a group of various sensors and various operation signals from an operation panel (not shown) are input to the air-conditioning control unit 122 . Specifically, the group of sensors includes a temperature sensor 123 for detecting the temperature Ts2 of the refrigerant at the outlet of the second evaporator 119 , and a pressure sensor 124 for detecting the pressure Ps2 of the refrigerant at the outlet of the second evaporator 119 . Furthermore, the operation panel is provided with a temperature setting switch for setting the cooling temperature and the like of the space to be cooled.

Next, in the above structure, the operation of this embodiment will be described. When the compressor 111 is driven by a vehicle engine, refrigerant is sucked and compressed by the compressor 111, and enters a high temperature and high pressure state, and then is discharged. Then, the refrigerant discharged from the compressor 111 flows into the radiator 112 . In the radiator 112, the high-temperature refrigerant is cooled by external air, thereby condensing. The liquid-phase refrigerant flowing out of the radiator 112 flows through the refrigerant pipe 113, the refrigerant inflow port 114d of the ejector 114, and the refrigerant inflow port 114g, and enters the nozzle portion 114b.

The air conditioner control unit 122 calculates the degree of superheat of the refrigerant at the outlet of the second evaporator 119 according to the detection value Ts2 of the temperature sensor 123 and the detection value Ps2 of the pressure sensor 124 . The air conditioning control unit 122 changes the flow rate of the refrigerant supplied from the branch refrigerant outlet 114e of the ejector 114 to the second evaporator 119 so that the degree of superheat falls within a predetermined range.

Specifically, when the degree of superheat of the refrigerant at the outlet of the second evaporator 119 becomes higher than a prescribed value, the air conditioner control unit 122 outputs a control signal (pulse signal) to the drive portion 115b of the passage area control mechanism 115 so that The refrigerant flow rate at the branch refrigerant outflow port 114e becomes smaller to move the needle 115a in the A direction of FIG. 24A, thereby reducing the throttle passage C. FIG. On the contrary, when the degree of superheat of the refrigerant becomes lower than the specified value, the air conditioner control unit 122 outputs a control signal to the driving part 115b so that the refrigerant flow rate at the branch refrigerant outflow port 114e becomes large to be shown in B of FIG. 24B . direction to move the needle 115a, thereby increasing the throttle passage C.

In addition, when the needle 115a moves as described above, not only the flow rate of refrigerant supplied from the branch refrigerant outflow port 114e to the second evaporator 119 changes but also the flow rate of refrigerant sprayed out of the refrigerant injection port 114h changes.

Here, in the injection cycle device in which the refrigerant flowing out of the radiator 12 is branched on the upstream side of the nozzle portion 14b of the injector 14, the flow rate of refrigerant flowing out of the radiator 112 is equal to that injected out of the refrigerant injection port 114h and flowing into the first evaporator The sum of the refrigerant flow rate of the evaporator 116 and the refrigerant flow rate flowing into the second evaporator 119 from the branch refrigerant outlet 114e.

For this reason, the refrigerant flowing out of the evaporator 112 needs to be properly distributed to the first evaporator 116 and the second evaporator 119 in order to apply high cooling capacity throughout the cycle.

Therefore, the injection cycle device of this embodiment is set so that the refrigerant flow rate at the refrigerant injection port 114h and the refrigerant flow rate at the branch refrigerant outflow port 114e are changed in conjunction with each other. Therefore, the flow rate ratio between the evaporators 116, 119 can be set so that when the degree of superheat of the refrigerant at the outlet of the second evaporator 119 becomes a specified value, a high cooling capacity can be obtained in the whole cycle. This jet cycle device can be realized by appropriately designing the shapes of the branch refrigerant outlet 114e and the nozzle portion 114b and the size of the needle 115a.

The refrigerant having the flow rate determined in the above manner and injected out of the refrigerant injection port 114h absorbs heat from the air blown from the first evaporator blower 116a of the first evaporator 116 to apply cooling capacity. The refrigerant flowing out of the first evaporator 116 flows into the accumulator 117 and is separated into vapor-phase refrigerant and liquid-phase refrigerant. The separated vapor-phase refrigerant is sucked again through the compressor 111 .

The refrigerant flowing into the branch passage 118 a from the branch refrigerant outflow port 114 e flows through the second evaporator 119 . In addition, the liquid-phase refrigerant separated by the accumulator 117 is also drawn into the second evaporator 119 by the suction action of the ejector 114 .

In this way, the flow rate of refrigerant flowing through the second evaporator 119 can also be controlled by the liquid-phase refrigerant sucked by the accumulator 117 . Thus, the flow ratio between the evaporators 116, 119 can be closer to a value that increases the cooling capacity of the full cycle.

The refrigerant flowing into the second evaporator 119 absorbs heat from the air blown through the second evaporator blower 119a to apply cooling capacity. The vapor-phase refrigerant evaporated in the second evaporator 119 passes through the branch refrigerant passage 118b, is sucked by the ejector 114 from the refrigerant suction port 113d of the ejector 114, and is mixed with the liquid-phase refrigerant flowing through the nozzle portion 114b. Partially mixed and then flowed into the first evaporator 116.

As described above, in this embodiment, the refrigerant on the downstream side of the diffuser portion 114c of the ejector 114 is supplied to the first evaporator 116, and the refrigerant having a reduced pressure may also be supplied to the second evaporator from the branch refrigerant outflow port 114e. Evaporator 119. Accordingly, the first evaporator 116 and the second evaporator 119 may simultaneously apply a cooling operation.

In the cooling operation, the evaporation pressure of the refrigerant of the first evaporator 116 is the pressure of the refrigerant increased in pressure by the diffusion part 114c. Since the outlet of the second evaporator 119 is connected to the refrigerant suction port 114f, the lowest pressure of the refrigerant can be applied to the second evaporator 119 immediately after the pressure is lowered through the nozzle portion 113a.

Accordingly, the evaporator pressure (evaporator temperature) of the refrigerant in the second evaporator 119 can be made lower than the evaporator pressure (evaporator temperature) of the refrigerant in the first evaporator 116 . Accordingly, the first evaporator 116 may be used for air conditioning the vehicle compartment, and the second evaporator 119 may be used for a refrigerator installed in the vehicle compartment.

Since the suction pressure of the compressor 111 can be increased by the pressure-increasing action of the diffuser portion 114c of the ejector 114, the compression workload of the compressor 111 can be reduced by the increase of the suction pressure of the compressor 111, that is, savings can be generated. The effect of compressor 111 power.

In addition, in this embodiment, the variable nozzle portion that lowers the pressure of the refrigerant injected out of the refrigerant injection port 114h of the injector 114 to control the flow rate, and the one that lowers the pressure of the refrigerant flowing out of the branched refrigerant outflow port 114e to control the flow rate A variable throttle mechanism is integrally formed into injector 114 . Therefore, this eliminates the need to provide a throttling unit that reduces the pressure of the refrigerant to expand the refrigerant in the branch passage 118a, thereby reducing the size of the injection cycle device.

In addition, the throttling passages C and D can be controlled in linkage by moving the needle 115a (the passage area control device) through the driving part 115b. Therefore, it is possible to reduce fluctuations in the flow rate ratio between the flow rate of refrigerant flowing through the variable nozzle portion and the flow rate of refrigerant flowing through the variable throttle mechanism. As a result, this flow ratio can be easily controlled to an appropriate flow ratio between the evaporators 116, 119, and fluctuations in the flow ratio between the evaporators 116, 119 can be prevented.

(Nineteenth embodiment)

In the eighteenth embodiment described above, the injection cycle device is provided with the accumulator 117 , the refrigerant guide passage 120 , the check valve 121 , the temperature sensor 123 , and the pressure sensor 124 . However, in this embodiment, as shown in FIG. 25, there are no such parts, and the refrigerant pipe 113 on the downstream side of the radiator 112 is provided with a receiver 131 for separating vapor-phase refrigerant from liquid-phase refrigerant, detecting the first A temperature sensor 133 for refrigerant temperature Ts1 at the outlet of the evaporator 116 , and a pressure sensor 134 for detecting refrigerant pressure Ps1 at the outlet of the first evaporator 116 .

Since the accumulator 117 is absent, the compressor 111 is connected to the downstream side of the first evaporator 116 . Detection values of the temperature sensor 133 and the pressure sensor 134 are output to the air conditioning control unit 122 .

In addition, in the ejector 114 of the eighteenth embodiment described above, the variable throttle mechanism for lowering the pressure of the refrigerant is constituted by the throttle passage C, and the refrigerant flows out into the branch through the branch refrigerant outlet 114i constituted by the nozzle portion 114b. Refrigerant outlet 114e. However, in this embodiment, the injector 114 is not provided, and the injector 130 which does not have the above-mentioned variable throttle mechanism is provided.

Next, the structure of injector 130 of the nineteenth embodiment will be described with reference to FIG.

Like the eighteenth embodiment, the casing 130a has a refrigerant inflow port 130d (first connection portion) and a refrigerant suction port 130f (third refrigerant). In addition, the housing 130a has a refrigerant outflow port 130e (fourth connection portion) through which the refrigerant flowing in from the refrigerant inflow port 130d flows out to the branch passage 118a. In addition, the refrigerant pipe 113 is connected to the refrigerant inflow port 130, the branch channel 118b is connected to the refrigerant suction port 130f, and the branch channel 118a is connected to the branch refrigerant outflow port 130e.

The nozzle portion 130b has a refrigerant inflow port 130g and a refrigerant injection port 130h. In addition, the nozzle part 130b has the branch refrigerant outflow port 130i which communicates the inside of the nozzle part 130b with the branch refrigerant outflow port 130e. The branch refrigerant outlet 130i is provided at a position where the refrigerant flow rate of the branch refrigerant outlet 130e does not change even when a needle 132a of a passage area control mechanism 132 described later moves. Therefore, the injector 130 is not provided with a variable throttle mechanism.

Then, in order to reduce the pressure of the refrigerant flowing out from the inside of the nozzle portion 130b to the branch refrigerant outflow port 130e to expand the refrigerant, the housing 130a has a fixed throttle valve 130k provided therebetween. In this embodiment, the fixed throttle valve 130k is provided in the housing 130a, but of course, it may also be provided in the pipe of the branch passage 118a. In addition, the fixed throttle valve 130k in this embodiment is specifically composed of an orifice, but may also be composed of a capillary.

Next, the passage area control mechanism 132 is set to control the flow rate of refrigerant injected out of the refrigerant injection port 130h of the nozzle portion 130b. As in the eighteenth embodiment, the passage area control mechanism 132 is constituted by a needle 132a, a driving portion 132b, and a rotor 132c. The passage area control mechanism 132 changes the refrigerant flow rate of the refrigerant injection port 130h of the nozzle portion 130b by moving the needle 132a.

The control signal is output from the air conditioner control unit 122 to the driving part 132b. The nineteenth embodiment is the same as the eighteenth embodiment in other points.

The operation of this embodiment having this structure will be described below. Like the eighteenth embodiment, the refrigerant discharged from the compressor 111 is cooled by the radiator 112 and separated into a vapor-phase refrigerant and a refrigerant by a receiver 131. liquid refrigerant. The liquid-phase refrigerant flowing out of the receiver 131 flows into the nozzle part 130b through the refrigerant inflow port 130d and the refrigerant inflow port 130g of the ejector 130 .

The air conditioner control unit 122 calculates the degree of superheat of the refrigerant at the outlet of the first evaporator 116 according to the detection value Ts1 of the temperature sensor 133 and the detection value Ps1 of the pressure sensor 134 . Then, as in the eighteenth embodiment, the air conditioner control unit 122 moves the needle 132a to change the area of the throttle passage D so that the degree of superheat is within a predetermined range, thereby changing the refrigerant injection port 130h injected from the injector 130. flow of refrigerant.

Here, the refrigerant passage area of the fixed throttle valve 130k formed in the branch refrigerant outflow port 130e is pre-designed to a prescribed size in such a manner that when the degree of superheat of the refrigerant at the outlet of the first evaporator 116 becomes A specified value produces a flow ratio between the evaporators 116, 119 that can apply a high cooling capacity throughout the cycle.

The refrigerant flow rate of the refrigerant injection port 130h of the nozzle portion 130b and the refrigerant flow rate of the fixed throttle valve 130k are determined, and the refrigerant flowing through the refrigerant injection port 130h applies cooling capacity in the first evaporator 116 . The refrigerant flowing out of the first evaporator 116 is sucked through the compressor 111 again. The refrigerant at the outlet of the first evaporator 116 becomes vapor-phase refrigerant having a prescribed degree of superheat, and therefore, suction of liquid-phase refrigerant into the compressor 111 does not occur.

The refrigerant flowing through the fixed throttle valve 130 k flows through the branch passage 118 a, and flows into the second evaporator 119 . Then, the refrigerant applies cooling capacity in the second evaporator 119 and flows through the branch passage 118 b, and is sucked from the refrigerant suction port 130 d of the ejector 130 through the ejector 130 . Then, the refrigerant is mixed with the liquid-phase refrigerant flowing through the nozzle portion 130b at the mixing portion 130j, and then flows into the first evaporator 116.

As described above, as in the eighteenth embodiment, also in this embodiment, the cooling operation can be simultaneously performed in the first evaporator 116 and the second evaporator 119 , corresponding to the refrigerant evaporation pressure in the first evaporator 116 . ratio, the refrigerant evaporation pressure of the second evaporator 119 can be reduced. In addition, it is possible to reduce the compression workload of the compressor 111 and produce an effect of saving power.

In addition, in this embodiment, the pressure of the refrigerant injected out of the refrigerant injection port 130h of the injector 130 is lowered to control the variable nozzle portion of the flow rate, and the pressure of the refrigerant flowing through the branched refrigerant outlet 130e is lowered to control the flow rate of the refrigerant. A flow rate fixed throttle 130 k is integrally formed into the injector 130 . Therefore, there is no need to provide a fixed throttle valve for reducing the pressure of the refrigerant in the branch passage 118, and thus the size of the injection cycle device can be reduced.

In addition, the flow rate of refrigerant flowing through the variable nozzle portion is varied by the needle 132a and the driving portion 132b to control the flow ratio between the evaporators 116,119. Therefore, high cooling capacity can be applied in a full cycle with a simple structure.

(Twentieth Embodiment)

The ejector 114 of the eighteenth embodiment lowers the pressure of the refrigerant injected out of the refrigerant injection port 114h of the ejector 114 through the nozzle portion 114b and the needle 115a to control its flow rate, and reduces the flow out of the branch refrigerant outflow port 114e to the branch passage 118a. refrigerant pressure to control its flow. However, in the twentieth embodiment, the injector 114 is not provided, but the injector 140 is provided. Other points of this embodiment are the same as those of the eighteenth embodiment.

Next, an injector 140 of a twentieth embodiment will be described with reference to FIG. 27 . The injector 140 is composed of a housing 140 a , a nozzle portion 140 b , a diffuser portion 140 c , a passage area control mechanism 141 , a connecting pipe 142 , and a variable throttle mechanism 143 .

Like the nineteenth embodiment, the casing 140a has a refrigerant inflow port 140d (first connection portion) and a refrigerant suction port 140f (third refrigerant). In addition, the casing 140 a has a connection pipe outlet 140 e through which the refrigerant flowing in from the refrigerant inlet 140 d flows out to the connection pipe 142 . The refrigerant pipe 113 is connected to the refrigerant inflow port 140d, the branch passage 118b is connected to the refrigerant suction port 140f, and the connection pipe 142 is connected to the throttle mechanism outflow port 140e.

Like the nineteenth embodiment, the nozzle portion 140b has a refrigerant inflow port 140g and a refrigerant injection port 140h. Moreover, the nozzle part 140b has the connection pipe outlet 140i which connects the inside of the nozzle part 140b with the connection pipe outlet 140e. This connecting pipe outlet 140i is provided at a position where the flow rate of refrigerant flowing out of the connecting pipe outlet 140e is not changed by the passage area control mechanism 141 .

In addition, the diffusion portion 140c and the passage area control mechanism 141 are structurally the same as those of the nineteenth embodiment. The passage area control mechanism 141 is constituted by a needle 141a, a drive portion 141b, and a rotor 141c.

The connecting pipe 142 is a refrigerant pipe that connects the connecting pipe outlet 140e to a connecting pipe inlet 143d to be described later, and has a length of, for example, about 5 cm or less.

Next, the variable throttle mechanism 143 is composed of a variable throttle case 143a, a throttle portion 143b, and a passage area control mechanism 143c. The variable throttle case 143a has a connecting pipe inlet 143d through which refrigerant flowing out of the connecting pipe 142 flows out into the variable throttle mechanism 143, and a branch refrigerant flowing in from the connecting pipe inlet 143d flows out to the branch passage 118a. Outflow port 143e (fourth connection portion).

The connection pipe 142 is connected to the connection pipe inflow port 143d, and the branch passage 118a is connected to the branch refrigerant outflow port 143e, and the connection parts thereof are connected by welding so as to prevent refrigerant leakage.

The throttling portion 143b has a refrigerant inflow port 143f that communicates the connecting pipe inflow port 143d with the inside of the throttling portion 143b, and flows refrigerant into the throttling portion 143b, and reduces the amount of refrigerant flowing into the throttling portion from the refrigerant inflow port 143f. The refrigerant pressure of 143b is reduced by the refrigerant pressure of the expanded refrigerant through the port 143g.

Like the passage area control mechanism 141, the passage area control mechanism 143c is constituted by a needle 143h, a driving portion 143i, and a rotor 143j. The passage area control mechanism 143c changes the flow rate of the refrigerant flowing through the refrigerant pressure reducing port 143g by moving the needle 143h to reduce the refrigerant pressure, thereby expanding the refrigerant.

Here, the injector 140 and the passage area control mechanism 141 are integrated with each other as an integral structure. The casing 140a of the injector 140 and the variable throttle housing 143a of the variable throttle mechanism 143 are integrally connected to each other in a state in which they cannot be separated through a connecting pipe 142 having a length of 5 cm and less. The case 140a, the connection pipe 142, and the variable throttle case 143a may be connected to each other by screws through a seal or the like in a detachable state thereof.

The operation of this embodiment having this structure will be described below. Like the eighteenth embodiment, the refrigerant discharged from the compressor 111 is cooled by the radiator 112 and flows into the ejector 140 from the refrigerant inflow port 140d. 140. The refrigerant flowing into the ejector 140 is branched into the refrigerant flowing into the connection pipe 142 and the refrigerant injected from the refrigerant injection port 140h at the upstream side of the refrigerant injection port 140h of the nozzle portion 140b. The refrigerant flowing into the connecting pipe 142 flows into the throttle portion 143 b of the variable throttle mechanism 143 .

The air conditioner control unit 122 calculates the degree of superheat of the refrigerant at the outlet of the second evaporator 119 according to the detection value Ts2 of the temperature sensor 123 and the detection value Ps2 of the pressure sensor 124 . Then, the air-conditioning control unit 122 controls the refrigerant flow rate of the variable throttle mechanism 143 integrally formed with the ejector 140 so that the degree of superheat falls within a predetermined range. Specifically, the air conditioner control unit 122 outputs a control signal to the driving part 143j to move the needle 143h so as to change the flow rate of refrigerant flowing through the refrigerant pressure reducing port 143g.

In addition, as in the nineteenth embodiment, the air-conditioning control unit 122 changes the refrigerant flow rate injected from the refrigerant injection port 140h of the injector 140 in such a manner that the flow rate ratio between the evaporators 116, 119 can be adjusted throughout the cycle. Apply high cooling capacity.

As described above, the air conditioner control unit 122 determines the refrigerant flow rate of the refrigerant pressure lowering port 143g of the variable throttle mechanism 143 and the refrigerant flow rate of the refrigerant injection port 140h injected out of the nozzle portion 140b so that the refrigerant flowing through the nozzle portion 140b The agent exerts a high cooling capacity in the first evaporator 116 . The refrigerant flowing out of the first evaporator 116 is sucked through the compressor 111 again. The refrigerant flowing through the refrigerant pressure reducing port 143g and flowing out into the branch passage 118a applies cooling capacity in the second evaporator 119, and then is sucked by the refrigerant suction port 140f of the ejector 140 through the branch passage 118b

As in the eighteenth embodiment, even in this structure, the cooling action can be performed simultaneously in the first evaporator 116 and the second evaporator 119 . In addition, the refrigerant evaporation pressure of the second evaporator 119 may be lowered compared to the refrigerant evaporation pressure of the first evaporator 116 . In addition, it is possible to reduce the compression workload of the compressor 111 and produce an effect of saving power.

Furthermore, in this embodiment, the variable throttle mechanism 143 is integrated with the injector 140 . Therefore, this can eliminate the need to provide a throttle mechanism in the branch passage 118, and thus can reduce the size and weight of the injection cycle device.

Furthermore, in this embodiment, the flow rate of refrigerant flowing through the variable nozzle portion and the flow rate of refrigerant flowing through the variable throttle mechanism 143 can be changed independently. Accordingly, the flow rate of refrigerant flowing through the nozzle portion 140b and into the first evaporator 116, and the flow rate of refrigerant flowing through the branch passage 118 and into the second evaporator 119 may be controlled separately. Therefore, high cooling capacity can be applied throughout the cycle.

(Other implementations)

The present invention is not limited to the above-described embodiments, but may be variously modified in the following manner.

In the nineteenth embodiment, an injector 130 having a variable nozzle portion 130b and a fixed throttle 130k is used. However, the same effects as those of the nineteenth embodiment can be produced even with an injector having a variable throttle mechanism for reducing the pressure of refrigerant flowing out to the branch passage 118a with a fixed refrigerant passage area of the nozzle portion.

In the twentieth embodiment, the driving portion 141b of the variable nozzle portion 140b and the driving portion 143j of the variable throttle mechanism 143 are constituted separately. However, the needle 141a of the variable nozzle part 140b and the needle 143h of the variable throttle mechanism 143 may be connected to each other, and the two needles 141a, 143h may be controlled by a single driving part.

In the eighteenth to twentieth embodiments, examples in which the first evaporator 116 is used for air-conditioning the vehicle cabin and the second evaporator 119 is used for the refrigerator of the vehicle have been explained. However, the space cooled by the first evaporator 116 may be the same as the space cooled by the second evaporator 119 .

In the eighteenth to twentieth embodiments, a variable capacity compressor is used as the compressor 111 , but a fixed capacity compressor or an electrically driven compressor may also be used as the compressor 111 . In addition, in the case of a fixed-capacity compressor, it is also recommended to control the refrigerant discharge capacity by controlling the ratio of the operating state to the non-operating state (operation ratio) by an electromagnetic clutch. In addition, in the case of an electrically driven compressor, it is also recommended to control the refrigerant discharge amount by controlling the number of revolutions.

In the eighteenth to twentieth embodiments, examples of the subcritical pressure cycle in which the high pressure of the refrigeration cycle is not higher than the critical pressure of the refrigerant have been described, but the present invention can also be used in the case where the high pressure of the refrigeration cycle is higher than the refrigeration cycle. The supercritical pressure cycle of the agent's critical pressure.

In the eighteenth embodiment, the flow rate of the refrigerant is controlled according to the degree of superheat of the refrigerant at the outlet of the second evaporator 119 . In the nineteenth embodiment, the flow rate of the refrigerant is controlled according to the degree of superheat of the refrigerant at the outlet of the first evaporator 116 . However, the refrigerant passage area may be controlled according to the flow rate of refrigerant discharged from the compressor 111, the refrigerant pressure and temperature at the outlet of the radiator 112, the degree of subcooling, and the like.

For example, in a cycle in which the refrigerant has its pressure increased to a supercritical pressure state by the compressor 111, the refrigerant dissipating heat in the radiator 112 does not change into a liquid phase. Therefore, it is only necessary to control the refrigerant passage area of the nozzle portion of the ejector and the refrigerant passage area of the throttling unit of the branch passage according to the refrigerant pressure and temperature at the outlet of the radiator 112 .

In the eighteenth to twentieth embodiments, flow control valves controlled by stepping motors may be used as the passage area control mechanisms 115, 132, 141 and the variable throttle mechanism 143, but other flow control valves may also be used. For example, a variable throttle unit that converts to use multiple fixed throttle valves with different characteristics may be used. In addition, it is also recommended to use the mechanical variable throttle mechanism and the electrically variable throttle mechanism of each of the above-mentioned embodiments in combination.

For example, as shown in FIG. 28, the injector 114 of the eighteenth embodiment may be connected to the branch passage 118a through a fixed throttle valve 114k. An orifice or capillary can be used as the fixed throttle 114k.

In the eighteenth to twentieth embodiments, the first evaporator 116 and the second evaporator 119 are used, but the number of evaporators may be increased, for example, three or more evaporators may be used. A throttling unit (throttling device) that reduces the pressure of the refrigerant supplied to the added evaporator to expand the refrigerant may be integrally formed with the ejector. According to this, the size and weight of the injection cycle device can be further reduced.

For example, in the structures of the eighteenth to twentieth embodiments, there may be provided for connecting a portion between the outlet of the radiator 112 and the refrigerant inflow port 114d of the ejector 114 to the outlet of the first evaporator 116 and the outlet of the first evaporator 116. Part of the second branch channel between the reservoirs 117 . In addition, a throttling unit (throttling device) and a third evaporator may be provided in the second branch passage, and the throttling unit provided in the second branch passage may be integrally formed with the injector 114 .

In the above-described embodiments, the injector and the injection cycle device according to the present invention are applied to an air conditioner for a vehicle. However, the injector and injection cycle device according to the invention can also be used in heat pump cycles of refrigerators, stationary refrigerators, stationary freezers, air cooling units and water heaters for vehicles.

In the above-described embodiments, Freon-based refrigerants, carbon dioxide (CO ₂ )-based refrigerants, or hydrocarbon (HC)-based refrigerants may be used as refrigerants. Therefore, the term Freon means a general term for organic compounds including carbon, fluorine, chlorine, and hydrogen, and Freon is widely used as a refrigerant.

Freon-based refrigerants include HCFC (hydrochlorofluorocarbon/hydrochlorofluorocarbon)-based refrigerants and HFC (hydrofluorocarbon/hydrofluorocarbon)-based refrigerants. Because Freon-based refrigerants do not deplete the ozone layer, they are called Freon-based substitutes. Refrigerant.

In addition, HC (hydrocarbon)-based refrigerants are refrigerant substances that contain hydrogen and carbon and exist in nature. The HC-based refrigerants include R600a (isobutylene) and R290 (propane).

It should be understood that such changes and improvements are within the scope of the present invention as defined in the appended claims.

Claims (39)

1. ejector cycle device comprises:

The compressor (10) of suction and compressed refrigerant;

Distribute the radiator (20) of the heat of the high-pressure refrigerant of discharging from compressor;

Comprising that pressure with the high-pressure refrigerant in radiator downstream can be converted to speed can be with the nozzle segment of decompression and swell refrigeration agent, and is used for by the injector (30) of injection stream from the suction inlet of nozzle segment suction cold-producing medium;

From the coolant channel branch between the nozzle segment of radiator and injector, and be connected to the branched bottom (55) of the suction inlet of injector;

Be arranged in the branched bottom and the throttling unit (40) of reduced-pressure refrigerant; And

Be arranged in the branched bottom, the downstream of the cold-producing medium of throttling unit stream and the evaporimeter (50) of vaporized refrigerant.

2. ejector cycle device according to claim 1 also comprises:

Be arranged in the coolant channel between radiator and the injector, and the flow controlling unit (34) of control refrigerant flow.

3. ejector cycle device according to claim 1 also comprises:

Vapour/liquid/gas separator (60), this vapour/liquid/gas separator (60) and are separated into vapor phase refrigerant and liquid phase refrigerant with cold-producing medium between the outlet and compressor of injector, so that vapor phase refrigerant is supplied to compressor and gathers liquid phase refrigerant.

4. ejector cycle device according to claim 1 also comprises:

Between injector and compressor, regain unit (70) with the heat of exchanged heat between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucks by compressor.

5. ejector cycle device according to claim 3 also comprises:

Between vapour/liquid/gas separator and compressor, with the cold-producing medium that flows out radiator and flow out vapour/liquid/gas separator and the cold-producing medium that sucks by compressor between the heat of exchanged heat regain unit (70).

6. ejector cycle device according to claim 3 also comprises:

Between injector and vapour/liquid/gas separator, to regain unit (70) at the cold-producing medium and the outflow jet that flow out radiator and the heat that flows to exchanged heat between the cold-producing medium of vapour/liquid/gas separator.

7. ejector cycle device according to claim 3 also comprises:

A plurality of recuperation of heat parts (70A, 70B), these a plurality of recuperation of heat parts are between injector and compressor, and between the cold-producing medium that flows out radiator and outflow jet and the cold-producing medium that sucks by compressor exchanged heat, wherein vapour/liquid/gas separator is positioned between a plurality of low pressure refrigerant passages (72a, 72b) of recuperation of heat part.

8. according to any one described ejector cycle device of claim 4 to 7, the cold-producing medium that wherein flows to branched bottom is as flowing through the cold-producing medium that heat is regained the unit and flowed out radiator.

9. ejector cycle device according to claim 1 and 2 also comprises:

Vapour/liquid/gas separator between injector and compressor (60); And

Have by its cold-producing medium and flow to first coolant channel of branched bottom, and regain unit (70) by its heat of second coolant channel that flows out the vapor phase refrigerant inspiration compressor of vapour/liquid/gas separator from radiator.

10. ejector cycle device according to claim 3 also comprises:

Suck the liquid refrigerant feed path (65) of liquid phase refrigerant from vapour/liquid/gas separator; And

Be arranged in the liquid refrigerant feed path, and the backstop (80) that allows cold-producing medium to flow in the direction that flows out vapour/liquid/gas separator,

Wherein make the upstream side that flows to the cold-producing medium stream of evaporimeter from the liquid phase refrigerant of liquid refrigerant feed path supply.

11. ejector cycle device according to claim 10, wherein injector is the variable injecting device with the variable restrictor mechanism that can control refrigerant flow.

12. an ejector cycle device comprises:

The compressor of suction, compression and discharging refrigerant (10);

Be arranged on by it by the injector in the refrigerant circulation passage of compressor circulating refrigerant (30), wherein injector has the nozzle segment (31) that has the inlet that is used to introduce the high-pressure refrigerant before the decompression, cold-producing medium flows the suction inlet (33) that sucks from it by the injection of refrigerant from nozzle segment, and is used to eject the outlet from the cold-producing medium of nozzle and suction inlet;

Be connected to the branched bottom (55) of the suction inlet of the inlet of injector and injector;

Be arranged on the heat exchanger (50) in the branched bottom; And

Supply to the injector inlet at high-pressure refrigerant, and cold-producing medium supplies to outlet from first pattern and the high-pressure refrigerant that heat exchanger flows to suction inlet, and cold-producing medium flows to the passage converting unit of changing between second pattern of heat exchanger (160) from the suction inlet of injector.

13. ejector cycle device according to claim 12, wherein heat exchanger is arranged as first heat exchanger, also comprises:

Between the inlet and first heat exchanger of injector, and to make first heat exchanger in first pattern be low temperature, and to make first heat exchanger in second pattern be the throttling unit (40) of high temperature; And

Be arranged in the refrigerant circulation passage, and in first pattern, become high temperature and in second pattern, become second heat exchanger of low temperature.

14. ejector cycle device according to claim 13 also comprises:

Between injector and compressor, and the heat of heat exchange in first pattern between the cold-producing medium that flows out second heat exchanger and outflow jet and the cold-producing medium that sucked by compressor is regained unit (70).

15. ejector cycle device according to claim 14, the cold-producing medium that wherein flows to branched bottom is regained the cold-producing medium of unit as flowing through heat.

16., also comprise according to any one described ejector cycle device of claim 12 to 15:

Between injector and compressor, and the 3rd heat exchanger (51) of heat exchange between cold-producing medium and external fluid; And

In the suction inlet of injector and the second throttling unit (41) between first heat exchanger.

17. ejector cycle device according to claim 16, wherein first heat exchanger and the 3rd heat exchanger are whole forms.

18. ejector cycle device according to claim 12, wherein heat exchanger also comprises as first heat exchanger:

Be arranged on second injector (35) and second branched bottom (56) of the second heat exchanger side,

Wherein second injector has the inlet that flows into during in second pattern at the high-pressure refrigerant in the downstream of first heat exchanger by it,

Wherein second branched bottom will advance the suction inlet of second injector from the cold-producing medium stream guiding of the refrigerant circulation passage branch of first injector inlet upstream side, and

Wherein second heat exchanger is arranged in second branched bottom and vaporized refrigerant, thereby applies cooling capacity in second pattern.

19. according to any one described ejector cycle device of claim 12 to 15, wherein the pressure of the high-pressure refrigerant of discharging from compressor is critical pressure or higher.

20. according to any one described ejector cycle device of claim 12 to 15, wherein when the frost that needs heat exchanger was removed operation, the passage converting unit was transformed into as frost and removes second mode of operation.

21. according to any one described ejector cycle device of claim 12 to 15, wherein nozzle segment is set to interrupt cold-producing medium stream when making cold-producing medium flow out suction inlet.

22. an injector that is used for kind of refrigeration cycle comprises:

Reduce the pressure of cold-producing medium, thus the nozzle segment of swell refrigeration agent (114b, 130b, 140b);

High speed cold-producing medium suction wherein the suction part of cold-producing medium by spraying from nozzle segment;

Be used to mix the cold-producing medium that sprays from nozzle segment with supercharging and from the diffusion part that sucks the cold-producing medium that part sucks (114c, 130c, 140c)

The first pontes that is communicated with the upstream side of nozzle segment (114d, 130d, 140d);

Second coupling part that is communicated with the downstream of diffusion part (114l, 130l, 140l)

With suck partially communicating the 3rd coupling part (114f, 130f, 140f); And

The 4th coupling part that is communicated with the upstream side of nozzle segment (114e, 130e, 140e).

23. injector according to claim 22 also comprises:

The controlling organization (115,132,141) of the opening of control nozzle segment.

24. injector according to claim 23, wherein controlling organization (115) is set to control the opening of the coolant channel that passes the 4th coupling part.

25. injector according to claim 24,

Wherein controlling organization (115) has the pin (115a) in the coolant channel that is arranged on nozzle segment, and

An end of coolant channel that wherein passes the 4th coupling part in the coolant channel of nozzle segment with the side of pin opening relatively.

26., also comprise according to claim 22 or 23 described injectors:

The throttling unit (C, 130k, 143) of the cold-producing medium stream of the 4th coupling part is flow through in throttling.

27. injector according to claim 26, wherein the throttling unit (C, 130k) be positioned at the 4th coupling part (114e, 130e) and the first pontes (114d, 130d) between.

28. injector according to claim 26, wherein the throttling unit is arranged in the coolant channel that is connected to the 4th coupling part (114e).

29. an ejector cycle device comprises that the one end is connected to the 3rd coupling part according to the injector of claim 22, and its other end is connected to the heat exchanger (119) according to the 4th coupling part of the injector of claim 22.

30. ejector cycle device according to claim 29 comprises that also the one end is connected to other heat exchanger according to second coupling part of the injector of claim 22.

31. an injector that is used to have the kind of refrigeration cycle of evaporimeter comprises:

(114b, 130b 140b), and come suction inlet that the cold-producing medium of flash-pot is inhaled into partly (114f, spout part 130f) by it by the high speed cold-producing medium from nozzle ejection to have the decompression and the nozzle segment of swell refrigeration agent; And

With the whole upstream side branch that forms and be reduced in nozzle segment of injector, and flow out to the throttling unit (C, 130k, 143) of pressure of the cold-producing medium of vaporizer upstream side.

32. injector according to claim 31, wherein at least one in nozzle segment and the throttling unit constitutes the area that changes coolant channel.

33., also comprise according to claim 31 or 32 described injectors:

Hold nozzle segment housing (114a, 130a),

Wherein the throttling unit is contained in the housing.

34. injector according to claim 32,

Wherein nozzle segment is the variable-nozzle part (114b) that can change the coolant channel area,

Wherein the throttling unit is the variable restrictor mechanism (C) that can change the coolant channel area, and

Wherein the coolant channel area of the coolant channel area of variable-nozzle part and variable restrictor mechanism changes by common aisle spare control device.

35. injector according to claim 34, wherein the aisle spare control device shrinks simultaneously or increases the coolant channel area of variable-nozzle part and the coolant channel area of variable restrictor mechanism.

36., also comprise according to claim 31 or 32 described injectors:

Suck the refrigerant suction port (140f) of the cold-producing medium of vaporizer upstream side; And

The housing (114a) that holds nozzle segment,

Wherein the throttling unit is arranged on the outside of housing, and

Wherein the throttling unit is connected to housing by the refrigerant pipe integral body with about 5cm or shorter length.

37. injector according to claim 32,

Wherein nozzle segment is the variable-nozzle (114b) that can change the coolant channel area,

Wherein the throttling unit is the variable restrictor mechanism that can change the coolant channel area, and

Wherein variable-nozzle part and variable restrictor mechanism are by single drive part control.

38. according to claim 31 or 32 described injectors, also comprise the housing that is used to hold at least one nozzle (114a, 130a),

Wherein in cold-producing medium branch in housing of the upstream side branch of nozzle segment.

39. an ejector cycle device comprises:

Thereby comprise the pressure swell refrigeration agent that reduces cold-producing medium, and suck nozzle segment (114b, 130b, injector 140b) (114,130,140) of cold-producing medium by the high speed cold-producing medium that sprays from nozzle segment;

The evaporimeter (119) of the cold-producing medium that evaporation sucks in the upstream side branch of nozzle segment and by injector; And

Be reduced in the pressure of cold-producing medium of the upstream side branch of nozzle segment, thus swell refrigeration agent and cold-producing medium supplied to the throttling arrangement (C, 130k, 143) of evaporimeter,

Wherein throttling arrangement and injector are whole forms.

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