JP4539571B2 - Vapor compression cycle - Google Patents

Description

  The present invention relates to a vapor compression cycle using an ejector that serves as a refrigerant decompression unit and a refrigerant circulation unit, and is effective when applied to, for example, a domestic air conditioner, a vehicle air conditioner, and the like.

  Conventionally, as a vapor compression refrigeration cycle using an ejector, for example, one disclosed in Patent Document 1 is known. In other words, this refrigeration cycle includes a refrigerant compressor, an outdoor heat exchanger, an ejector, and a gas-liquid separator that are annularly connected, and a branch passage that connects the gas-liquid separator and the refrigerant suction port of the ejector to the first chamber. A heat exchanger is disposed, and a second indoor heat exchanger and a decompressor are disposed between the refrigerant compressor and the outdoor heat exchanger. A bypass passage is interposed at a predetermined portion of the refrigerant pipe.

In this refrigeration cycle, the following three operations are possible by changing the flow of the refrigerant by switching the bypass passage. That is, the cooling operation can be performed by absorbing heat with the first indoor heat exchanger and radiating heat with the outdoor heat exchanger, and the heating operation with absorbing heat with the outdoor heat exchanger and radiating heat with the second indoor heat exchanger. Furthermore, the dehumidifying and heating operation is enabled by absorbing heat with the outdoor heat exchanger and the first indoor heat exchanger and dissipating heat with the second indoor heat exchanger.
JP 200426004 A

  However, in the refrigeration cycle, during the cooling operation, the air mix door attached to the second indoor heat exchanger is closed so that heat exchange by the second indoor heat exchanger is not performed, and heating operation is performed. At times, the first indoor heat exchanger is not used by switching the bypass passage. Therefore, since not all heat exchangers are used in the entire system, the system is not efficient and is expensive.

  In view of the above problems, an object of the present invention is to provide a vapor compression cycle that can efficiently perform cooling, heating, and dehumidifying heating operations by effectively utilizing a plurality of arranged heat exchangers at all times. It is in.

  In order to achieve the above object, the present invention employs the following technical means.

  According to the first aspect of the present invention, in the vapor compression cycle, the compressor (110) that sucks and compresses the refrigerant, the outdoor heat exchanger (130) that exchanges heat between the refrigerant and the outdoor air, and the outdoor heat exchange. Ejector that is connected from the vessel (130) and decompresses and expands the high-pressure refrigerant by the nozzle (141) that allows the opening degree to be adjusted, and after the refrigerant is sucked from the refrigerant suction port (142), the pressure is increased by the pressure increasing unit (143) (140) and the first indoor heat exchanger (150) connected from the ejector (140) and exchanging heat between the refrigerant and the room air, and between the outdoor heat exchanger (130) and the ejector (140) And a decompressor (160) disposed in a branch channel (161) connected to the refrigerant suction port (142) to decompress and expand the refrigerant, and a decompressor (160) of the branch channel (161). ) And a second indoor heat exchanger (170) disposed between the refrigerant suction port (142) and exchanging heat between the refrigerant and room air, and a compressor (110) are connected to the first indoor heat exchanger (150). ) So that the refrigerant is sucked and discharged to the outdoor heat exchanger (130), or the refrigerant is sucked from the outdoor heat exchanger (130) and discharged to the first indoor heat exchanger (150). The branch channel (161) is disposed between the channel switching means (120) for switching the channel and the second indoor heat exchanger (170) and the refrigerant suction port (142) of the branch channel (161). And a variable diaphragm (180) that varies the degree of diaphragm.

  As a result, the cooling operation, the heating operation, and the dehumidifying heating operation using the three heat exchangers of the outdoor heat exchanger (130), the first indoor heat exchanger (150), and the second indoor heat exchanger (170) are always performed. It becomes possible.

  That is, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the first indoor heat exchanger (150) and discharges it to the outdoor heat exchanger (130). At the same time, the variable throttle (180) is fully opened to eliminate the throttle, so that the refrigerant discharged from the compressor (110) flows from the outdoor heat exchanger (130) through the ejector (140) and the branch flow path (161). . Then, the refrigerant flowing into the branch channel (161) is decompressed by the decompressor (160) and flows into the second indoor heat exchanger (170), and passes through the variable throttle (180) that is fully opened, It flows into the refrigerant suction port (142) of the ejector (140). The refrigerant flowing into the ejector (140) from the outdoor heat exchanger (130) is decompressed and expanded by the nozzle (141) and mixed with the refrigerant sucked from the refrigerant suction port (142). The pressure is increased and flows into the first indoor heat exchanger (150) and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the first and second indoor heat exchangers (150, 170) absorb heat from the indoor air, and the heat is radiated by the outdoor heat exchanger (130). Thus, the cooling operation in which the indoor air is cooled by the first and second indoor heat exchangers (150, 170) becomes possible.

  Further, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the outdoor heat exchanger (130) and discharges it to the first indoor heat exchanger (150). At the same time, the nozzle (141) of the ejector (140) is fully closed, and further, the variable throttle (180) is fully opened to eliminate the throttle degree, so that the refrigerant discharged from the compressor (110) is subjected to the first indoor heat exchange. Into the vessel (150). Then, the refrigerant passes through the refrigerant suction part (142) from the pressure raising part (143) of the ejector (140), passes through the variable throttle (180) that is fully opened, and flows into the second indoor heat exchanger (170). . The refrigerant flowing out of the second indoor heat exchanger (170) is decompressed by the decompressor (160), flows into the outdoor heat exchanger (130), and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the outdoor heat exchanger (130) absorbs heat from the outdoor air, and the heat is radiated by the first and second indoor heat exchangers (150, 170). Thus, the heating operation for heating the indoor air with the first and second indoor heat exchangers (150, 170) becomes possible.

  Further, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the first indoor heat exchanger (150) and discharges it to the outdoor heat exchanger (130). At the same time, the nozzle (141) of the ejector (140) is fully closed, and further, the variable throttle (180) is throttled to a predetermined throttle degree, so that the refrigerant discharged from the compressor (110) becomes the outdoor heat exchanger. (130) flows through the branch channel (161). Then, the refrigerant flowing into the branch flow path (161) is decompressed by the decompressor (160) and flows into the second indoor heat exchanger (170), and is decompressed by the variable restrictor (180) to be ejected by the ejector (140 ) Flows into the refrigerant suction port (142). The refrigerant that has flowed into the refrigerant suction port (142) of the ejector (140) flows into the first indoor heat exchanger (150) through the pressure increase unit (143) and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the first indoor heat exchanger (150) absorbs heat from the indoor air, and this heat is absorbed by the outdoor heat exchanger (130) and the second indoor heat exchanger (170). ), The indoor air is cooled by the first indoor heat exchanger (150), and the dehumidifying and heating operation in which the indoor air is heated by the second indoor heat exchanger (170) becomes possible.

  In the invention according to claim 2, the flow path switching means (120) includes the suction side of the compressor (110), the discharge side of the compressor (110), the outdoor heat exchanger (130) side, and the first indoor heat exchange. The four points on the side of the vessel (150) are connected to communicate with each other between two predetermined points, and the four-way valve (120) that enables switching of the combination of the communication is provided. A flow path switching means (120) can be configured.

  In the invention according to claim 3, heat is generated between the refrigerant flowing from the outdoor heat exchanger (130) to the decompressor (160) and the refrigerant flowing from the first indoor heat exchanger (150) to the compressor (110). An internal heat exchanger (195) for replacement is provided.

  Thereby, during cooling operation or dehumidifying heating operation, the heat-radiated refrigerant can be cooled by the heat-absorbed refrigerant, so that the enthalpy of the heat-radiated refrigerant can be reduced, and the inlet side on the heat absorption side can be reduced. The enthalpy difference from the outlet side can be increased to increase the heat absorption capacity. Moreover, since the refrigerant | coolant after heat absorption will be heated conversely and it can be set as the gaseous-phase refrigerant | coolant with a predetermined superheat degree, the liquid compression in a compressor (110) can be prevented reliably.

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

(First embodiment)
A first embodiment of the present invention is shown in FIG. In the first embodiment, the vapor compression cycle 100 according to the present invention is applied to a vehicle refrigeration cycle apparatus mounted on a vehicle such as a passenger car, a bus, or a truck. FIG. 1 is a schematic diagram showing the overall configuration of the vapor compression cycle 100, and the thin line arrows in FIG. 1 indicate the flow direction of the refrigerant during the cooling operation.

  In the vapor compression cycle 100, a compressor 110 that sucks and compresses refrigerant is rotationally driven by a vehicle travel engine (not shown) via an electromagnetic clutch 111, a belt, and the like. The on / off state of the electromagnetic clutch 111 is controlled by a control device (not shown).

  The compressor 110 may be a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or a fixed compressor that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by switching the electromagnetic clutch 111. Any of the capacity type compressors may be used. If an electric compressor is used as the compressor 110, the refrigerant discharge capacity can be adjusted by adjusting the rotation speed of the electric motor.

  On the refrigerant discharge side of the compressor 110, a four-way valve 120 as a flow path switching unit is disposed. The four-way valve 120 is a valve that has four connection portions, and that allows two predetermined connection portions to communicate with each other and switch the combination of the communication by, for example, an electric actuator mechanism provided therein.

  Specifically, a suction pipe 112, a discharge pipe 113, an outdoor pipe 131, and an indoor pipe 151 are connected to the four connecting portions of the four-way valve 120. As shown by the solid line in the four-way valve 120 in FIG. 1, the four-way valve 120 brings the discharge pipe 113 and the outdoor pipe 131 into communication and also connects the indoor pipe 151 and the suction pipe 112 with each other. As shown by the first pattern and the broken line in the four-way valve 120 in FIG. 1, the discharge pipe 113 and the indoor pipe 151 are in communication, and the outdoor pipe 131 and the suction pipe 112 are connected. It is possible to switch the second pattern to be in the communication state. The switching of the first and second patterns of the four-way valve 120 is controlled by a control device (not shown).

  For example, one end side of an outdoor heat exchanger 130 disposed in an engine room of the vehicle is connected to the anti-four-way valve side of the outdoor pipe 131. The outdoor heat exchanger 130 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the outdoor air.

In the present embodiment, carbon dioxide (CO ₂ ) is used as the refrigerant of the vapor compression cycle 100, and the high pressure discharged from the compressor 110 when the flow path is switched to the first pattern by the four-way valve 120. The pressure is set to a supercritical cycle exceeding the critical pressure. In this case, the outdoor heat exchanger 130 functions as a radiator (gas cooler) that releases the heat of the supercritical refrigerant to the outdoor air and cools the refrigerant. In addition, when the low-pressure refrigerant having a temperature lower than that of the outdoor air flows through the outdoor heat exchanger 130 by switching the flow path of the four-way valve 120, the outdoor heat exchanger 130 acts as a heat absorber that absorbs heat from the outdoor air.

  As the refrigerant, a normal chlorofluorocarbon refrigerant may be used. In this case, when the flow path is switched to the first pattern by the four-way valve 120, the high-pressure pressure discharged from the compressor 110 is the critical pressure. Since the subcritical cycle is not exceeded, the outdoor heat exchanger 130 acts as a condenser that condenses the refrigerant.

  Connected to the other end of the outdoor heat exchanger 130 is a variable ejector 140 that can adjust the opening degree of a nozzle portion (nozzle) 141 described later. The ejector 140 is a decompression means for decompressing the refrigerant, and is also a refrigerant circulation means (momentum transport type pump) that circulates the refrigerant (fluid transport) by suction action (contraction action) of the refrigerant flow ejected at high speed ( JIS Z 8126 number 2.1.2.3 etc.).

  The ejector 140 includes a nozzle portion 141 that reduces the passage area (opening degree) of the high-pressure refrigerant flowing from the outdoor heat exchanger 130 to an isentropic decompression expansion. The nozzle unit 141 is capable of switching to a fully closed state where the nozzle opening is zero with respect to a predetermined nozzle opening serving as a throttle. The nozzle opening degree of the nozzle portion 141 is controlled by a control device (not shown).

  The side wall of the ejector 140 is provided with a refrigerant suction port 142 that communicates with a space serving as a refrigerant outlet of the nozzle portion 141 and sucks a gas phase refrigerant from a second indoor heat exchanger 170 described later. Further, in the downstream part of the refrigerant flow of the nozzle part 141 and the refrigerant suction port 142, after the high-speed refrigerant flow from the nozzle part 141 and the suction refrigerant from the refrigerant suction port 142 are mixed, the pressure is increased to boost the mixed refrigerant. A portion 143 is provided.

  One end side of the first indoor heat exchanger 150 is connected to the booster 143 of the ejector 140, and the other end side of the first indoor heat exchanger 150 is connected to the indoor pipe 151. The first indoor heat exchanger 150 is a heat exchanger that exchanges heat between the refrigerant circulating in the interior and the room air. More specifically, when the low-pressure refrigerant having a temperature lower than the room air flows through the first indoor heat exchanger 150 by switching the flow path of the four-way valve 120, the first indoor heat exchanger 150 absorbs heat from the room air. It acts as a heat sink. In addition, when the high-pressure refrigerant having a temperature higher than the indoor air flows through the first indoor heat exchanger 150 by switching the flow path of the four-way valve 120, the first indoor heat exchanger 150 releases the heat of the refrigerant to the indoor air. Acts as a radiator.

  A branch pipe 161 as a branch flow path is connected between the nozzle part 141 side of the ejector 140 and the refrigerant suction part 142. That is, the branch pipe 161 is a pipe branched from between the outdoor heat exchanger 130 and the ejector 140, and the branched tip end side is connected to the refrigerant suction port 142. Note that Z in FIG. 1 indicates a branch point of the branch pipe 161.

  A throttle mechanism 160 is disposed in the branch pipe 161. The throttle mechanism 160 is a decompressor that decompresses and expands the refrigerant flowing through the branch pipe 161 by allowing the throttle opening to be adjusted. The aperture opening degree of the aperture mechanism 160 is controlled by a control device (not shown).

  A second indoor heat exchanger 170 is disposed between the throttle mechanism 160 of the branch pipe 161 and the refrigerant suction port 142 of the ejector 140. The second indoor heat exchanger 170 is a heat exchanger that exchanges heat between the refrigerant circulating in the interior and the room air. More specifically, as in the case of the first indoor heat exchanger 150, when a low-pressure refrigerant having a temperature lower than the room air flows through the second indoor heat exchanger 170 by switching the flow path of the four-way valve 120, The second indoor heat exchanger 170 acts as a heat absorber that absorbs heat from room air. In addition, when a high-pressure refrigerant having a temperature higher than the room air flows through the second indoor heat exchanger 170 by switching the flow path of the four-way valve 120, the second indoor heat exchanger 170 releases the heat of the refrigerant into the room air. Acts as a radiator.

  The second indoor heat exchanger 170 is housed in the air conditioning case 150B together with the first indoor heat exchanger 150 to form an air conditioning unit 150A. The air conditioning unit 150A is disposed, for example, in an instrument panel in the passenger compartment. In the air conditioning unit 150A, as indicated by a thick arrow in FIG. 1, indoor air (outdoor air taken into the vehicle interior) is transferred from the first indoor heat exchanger 150 side to the second indoor heat exchanger 170 side by a blower (not shown). Or the original indoor air) is supplied, and the first and second indoor heat exchangers 150 and 170 exchange the heat of the indoor air, and the heat-exchanged indoor air is blown into the vehicle interior.

  Further, a throttle mechanism 180 is disposed between the second indoor heat exchanger 170 of the branch pipe 161 and the refrigerant suction port 142 of the ejector 140. The throttle mechanism 180 is a variable throttle that decompresses and expands the refrigerant circulating through the branch pipe 161 by adjusting the throttle opening degree. The throttle opening of the throttle mechanism 180 can be adjusted to a fully open state that ensures a flow path area equivalent to that of the branch pipe 161. The throttle opening degree of the throttle mechanism 180 is controlled by a control device (not shown).

  An accumulator (gas-liquid separator) 190 that separates the refrigerant flowing therethrough into a gas-liquid two phase is disposed in the middle of the suction pipe 112. The accumulator 190 stores the liquid-phase refrigerant among the separated refrigerants, and distributes the gas-phase refrigerant.

  In the vapor compression cycle 100, the refrigerant flowing from the outdoor heat exchanger 130 to the expansion mechanism 160, more specifically, the refrigerant flowing from the outdoor heat exchanger 130 to the branch point Z, and the four-way valve 120 have a first pattern. An internal heat exchanger 195 for exchanging heat with the refrigerant flowing from the first indoor heat exchanger 150 to the compressor 110, more specifically with the refrigerant flowing from the accumulator 190 to the compressor 110, is provided. ing. The internal heat exchanger 195 has two flow paths inside and exchanges heat between the refrigerants flowing through both flow paths.

  Next, the operation of the first embodiment based on the above configuration will be described with reference to FIGS. 2 is a Mollier diagram showing the refrigerant state during the cooling operation, FIG. 3 is a schematic diagram showing the refrigerant flow during the heating operation of the vapor compression cycle 100, and FIG. 4 is a Mollier line showing the refrigerant state during the heating operation. FIG. 5 is a schematic diagram showing the refrigerant flow during the dehumidifying heating operation of the vapor compression cycle 100, and FIG. 6 is a Mollier diagram showing the refrigerant state during the dehumidifying heating operation.

1. Cooling operation (Figs. 1 and 2)
A control device (not shown) switches the four-way valve 120 to the first pattern, fully opens the throttle opening of the throttle mechanism 180, connects the electromagnetic clutch 111, and drives the compressor 110 by the vehicle running engine. . The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the outdoor heat exchanger 130 through the discharge pipe 113, the four-way valve 120, and the outdoor pipe 131. In the outdoor heat exchanger 130, the heat of the high-temperature refrigerant is released to the outdoor air and cooled (outdoor HE in FIG. 2).

  The refrigerant that has flowed out of the outdoor heat exchanger 130 flows through one flow path of the internal heat exchanger 195, flows out of an accumulator 190 described later, and flows through the other flow path of the internal heat exchanger 195 by low-temperature and low-pressure refrigerant. Further cooling is performed (the upper wavy portion in FIG. 2).

  The refrigerant flowing out from one flow path of the internal heat exchanger 195 is divided into a refrigerant flow toward the ejector 140 and a refrigerant flow toward the branch pipe 161 at the branch point Z.

  The refrigerant that has flowed into the ejector 140 is decompressed and expanded by the nozzle portion 141 to become a low-temperature and low-pressure refrigerant (ejector in FIG. 2). Accordingly, the pressure energy of the refrigerant is converted into velocity energy at the nozzle portion 141, and the refrigerant is ejected from the nozzle outlet of the nozzle portion 141 at a high speed. Due to the refrigerant pressure drop at this time, the refrigerant (gas phase refrigerant) after passing through the second indoor heat exchanger 170 of the branch pipe 161 is drawn from the refrigerant suction port 142. The refrigerant ejected from the nozzle part 141 and the refrigerant sucked into the refrigerant suction port 142 are mixed in the pressure-increasing part 143 on the downstream side of the nozzle part 141, and the speed (expansion) energy is converted into pressure energy to be pressurized. .

  Then, the refrigerant that has flowed out of the ejector 140 (the pressure increasing unit 143) flows into the first indoor heat exchanger 150. In the first indoor heat exchanger 150, the refrigerant absorbs heat from the indoor air in the direction of the thick arrow in FIG. 1 and evaporates (indoor HE1 in FIG. 2). The indoor air is cooled by the latent heat of vaporization when the refrigerant evaporates.

  On the other hand, the refrigerant flowing into the branch pipe 161 is decompressed and expanded by the throttle mechanism 160 to become a low-temperature and low-pressure refrigerant (throttle 160 in FIG. 2), and this low-temperature and low-pressure refrigerant flows into the second indoor heat exchanger 170. The second indoor heat exchanger 170 absorbs heat from the indoor air that has passed through the first indoor heat exchanger 150 and evaporates (room HE2 in FIG. 2). The indoor air is further cooled by the latent heat of evaporation when the refrigerant evaporates in the second indoor heat exchanger 170. The evaporated refrigerant passes through the throttle mechanism 180 controlled to be fully open, and is sucked into the ejector 140 from the refrigerant suction port 142.

  The evaporated refrigerant that has flowed out of the first indoor heat exchanger 150 is sucked into the accumulator 190 through the indoor pipe 151, the four-way valve 120, and the suction pipe 112. In the accumulator 190, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant flows through the other flow path of the internal heat exchanger 195. At this time, it is heated by the high-temperature and high-pressure refrigerant flowing through one flow path of the internal heat exchanger 195 to become a gas-phase refrigerant having a predetermined superheat degree (lower wavy portion in FIG. 2). It is sucked into the compressor 111 and compressed again.

  A control device (not shown) controls the throttle opening of the throttle mechanism 160 so that the temperature of the indoor air that has passed through the second indoor heat exchanger 170 becomes the set air temperature set by the vehicle occupant.

2. Heating operation (Figs. 3 and 4)
A control device (not shown) switches the four-way valve 120 to the second pattern, fully closes the nozzle portion 141 of the ejector 140, fully opens the throttle opening of the throttle mechanism 180, and puts the electromagnetic clutch 111 into a connected state. The compressor 110 is driven by a vehicle travel engine. The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the first indoor heat exchanger 150 through the discharge pipe 113, the four-way valve 120, and the indoor pipe 151.

  In first indoor heat exchanger 150, the refrigerant dissipates heat to indoor air in the direction of the thick arrow in FIG. 1 and is cooled (indoor HE1 in FIG. 4). That is, the room air is heated by heat dissipation from the refrigerant.

  The refrigerant cooled by the first indoor heat exchanger 150 flows from the booster 143 side of the ejector 140. Here, since the nozzle portion 141 of the ejector 140 is controlled to be fully closed, the refrigerant flowing into the pressure increasing portion 143 passes through the ejector 140 and flows out from the refrigerant suction port 142. Further, the refrigerant passes through the throttle mechanism 180 controlled to be fully opened and flows into the second indoor heat exchanger 170.

  In the second indoor heat exchanger 170, the refrigerant dissipates heat to the indoor air that has passed through the first indoor heat exchanger 150 and is cooled (indoor HE2 in FIG. 4). That is, the indoor air is further heated by the heat radiation from the refrigerant in the second indoor heat exchanger 170.

  The refrigerant that has flowed out of the second indoor heat exchanger 170 is decompressed and expanded by the throttle mechanism 160 to become a low-temperature and low-pressure refrigerant (throttle 160 in FIG. 2), and this low-temperature and low-pressure refrigerant is divided into the branch point Z, the internal heat exchanger. It passes through one flow path 195 and flows into the outdoor heat exchanger 130. Here, since the refrigerant flowing through both flow paths of the internal heat exchanger 195 is both a low-temperature and low-pressure refrigerant, heat exchange in the internal heat exchanger 195 during the cooling operation is not performed.

  In the outdoor heat exchanger 130, the refrigerant absorbs heat from the outdoor air and evaporates (outdoor HE in FIG. 4). The evaporated refrigerant that has flowed out of the outdoor heat exchanger 130 is sucked into the accumulator 190 through the outdoor pipe 131, the four-way valve 120, and the suction pipe 112. In the accumulator 190, as in the cooling operation, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant passes through the other flow path of the internal heat exchanger 195. Inhaled and compressed again.

  A control device (not shown) controls the throttle opening of the throttle mechanism 160 so that the temperature of the indoor air that has passed through the second indoor heat exchanger 170 becomes the set air temperature set by the vehicle occupant.

3. Dehumidification heating operation (Figs. 5 and 6)
A control device (not shown) switches the four-way valve 120 to the first pattern, fully closes the nozzle portion 141 of the ejector 140, and connects the electromagnetic clutch 111 to drive the compressor 110 by the vehicle travel engine. . The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the outdoor heat exchanger 130 through the discharge pipe 113, the four-way valve 120, and the outdoor pipe 131. In the outdoor heat exchanger 130, the heat of the high-temperature refrigerant is released to the outdoor air and cooled (outdoor HE in FIG. 6).

  The refrigerant that has flowed out of the outdoor heat exchanger 130 flows through one flow path of the internal heat exchanger 195, flows out of an accumulator 190 described later, and flows through the other flow path of the internal heat exchanger 195 by low-temperature and low-pressure refrigerant. Further cooling is performed (the upper wavy portion in FIG. 6).

  The refrigerant flowing out from one flow path of the internal heat exchanger 195 passes through the branch point Z and flows into the branch pipe 161 because the nozzle portion 141 of the ejector 140 is controlled to be fully closed.

  The refrigerant flowing into the branch pipe 161 is decompressed by a predetermined amount by the throttle mechanism 160 (throttle 160 in FIG. 6), and this refrigerant flows into the second indoor heat exchanger 170. In the second indoor heat exchanger 170, the indoor air cooled (dehumidified) through the first indoor heat exchanger 150 described later is heated by the heat radiation of the refrigerant (indoor HE2 in FIG. 6). The refrigerant that has flowed out of the indoor heat exchanger 170 is decompressed and expanded by the throttle mechanism 180 and flows into the ejector 140 from the refrigerant suction port 142.

  The refrigerant that has flowed into the ejector 140 passes through the pressure increasing unit 143 and flows into the first indoor heat exchanger 150. In the first indoor heat exchanger 150, the refrigerant absorbs heat from the indoor air in the direction of the thick arrow in FIG. 1 and evaporates (indoor HE1 in FIG. 6). The indoor air is cooled (dehumidified) by the latent heat of vaporization when the refrigerant evaporates. Here, the indoor air is cooled (dehumidified) by the first indoor heat exchanger 150 and further heated by the second indoor heat exchanger 170.

  The evaporated refrigerant that has flowed out of the first indoor heat exchanger 150 is sucked into the accumulator 190 through the indoor pipe 151, the four-way valve 120, and the suction pipe 112. In the accumulator 190, as in the cooling operation, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant flows through the other flow path of the internal heat exchanger 195. At this time, it is heated by the high-temperature and high-pressure refrigerant flowing through one flow path of the internal heat exchanger 195 to become a gas-phase refrigerant having a predetermined superheat degree (lower wavy portion in FIG. 6). It is sucked into the compressor 111 and compressed again.

  The control device (not shown) restricts the opening degree of the throttle mechanisms 160 and 180 so that the humidity and temperature of the indoor air that has passed through the second indoor heat exchanger 170 become the set air humidity and temperature set by the vehicle occupant. To control.

  As described above, in the vapor compression cycle 100 of the present embodiment, the outdoor heat exchanger 130, the variable ejector 140, the first and second indoor heat exchangers 150 and 170, the flow path switching unit 120, and the variable throttle Therefore, the flow path can be switched and the refrigerant can be depressurized at a predetermined location, and the outdoor heat exchanger 130, the first indoor heat exchanger 150, and the second indoor heat exchanger 170 can be switched. The cooling operation, the heating operation, and the dehumidifying heating operation using the three heat exchangers at all times are possible.

  Here, the flow path switching means (120) can be easily configured by using the four-way valve 120.

  Further, since the internal heat exchanger 195 is provided in the vapor compression cycle 100, the refrigerant after the heat release in the outdoor heat exchanger 130 is supplied to the first indoor chamber during the cooling operation or the dehumidifying heating operation. It is possible to cool with the refrigerant after absorbing heat in the heat exchanger 150, to reduce the enthalpy of the refrigerant after heat dissipation, and to reduce the enthalpy between the inlet side and the outlet side in the indoor heat exchanger (150 and 170 or 150). The enthalpy difference can be increased to increase the endothermic capacity. In addition, the refrigerant after the heat absorption in the first indoor heat exchanger 150 is heated in reverse, so that it can be a gas phase refrigerant having a predetermined superheat degree, so that the liquid compression in the compressor 110 is ensured. Can be prevented.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. In the second embodiment, the flow path switching means is changed with respect to the first embodiment. The flow path switching means in the second embodiment is formed by using a three-way valve 120A instead of the four-way valve 120 and adding electromagnetic valves 120B and 120C and a communication pipe 120D.

  The three-way valve 120A has three connecting portions, and a discharge pipe 113, an outdoor pipe 131, and an indoor pipe 151 are connected to each connecting section. The first pattern in which the discharge pipe 113 and the outdoor pipe 131 are in communication with each other, for example, by an electric actuator mechanism provided inside the three-way valve 120A, and the discharge pipe 113 and the indoor pipe 151 in communication with each other. The second pattern can be switched. The switching of the first and second patterns of the three-way valve 120A is controlled by a control device (not shown).

  An end portion of the suction pipe 112 on the compressor 110 side is connected to the outdoor pipe 131, and an electromagnetic valve 120B for opening and closing the suction pipe 112 is disposed in the vicinity of the connection portion. The opening and closing of the electromagnetic valve 120B is controlled by a control device (not shown).

  In addition, a communication pipe 120D is provided for connecting the vicinity of the first indoor heat exchanger 150 of the indoor pipe 151 and the vicinity of the accumulator 190 between the electromagnetic valve 120B and the accumulator 190 of the suction pipe 112, and the communication pipe 120D is connected to the communication pipe 120D. An electromagnetic valve 120C that opens and closes the pipe 120D is provided. The opening and closing of the solenoid valve 120C is controlled by a control device (not shown), similar to the solenoid valve 120B.

  In the above configuration, during the cooling operation, the control device (not shown) switches the three-way valve 120A to the first pattern, closes the solenoid valve 120B, and opens the solenoid valve 120C. Then, the throttle opening of the throttle mechanism 180 is fully opened, and the electromagnetic clutch 111 is connected, and the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by solid line arrows in FIG. 7, and a cycle in which heat is absorbed by the first and second indoor heat exchangers 150 and 170 and is radiated by the outdoor heat exchanger 130 as in the first embodiment. Thus, the indoor air can be cooled by the first and second indoor heat exchangers 150 and 170.

  During heating operation, the control device (not shown) switches the three-way valve 120A to the second pattern, opens the electromagnetic valve 120B, and closes the electromagnetic valve 120C. Then, the nozzle part 141 of the ejector 140 is fully closed, the throttle opening of the throttle mechanism 180 is fully opened, and the electromagnetic clutch 111 is connected, so that the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by broken line arrows in FIG. 7, and similarly to the first embodiment, the heat is absorbed by the outdoor heat exchanger 130 and is radiated by the first and second indoor heat exchangers 150 and 170. Thus, the indoor air can be heated by the first and second indoor heat exchangers 150 and 170.

  Further, during the dehumidifying heating operation, the three-way valve 120A is switched to the first pattern by a control device (not shown), the electromagnetic valve 120B is closed, and the electromagnetic valve 120C is opened. Then, the nozzle portion 141 of the ejector 140 is fully closed, and the electromagnetic clutch 111 is connected, and the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by a one-dot chain line arrow in FIG. 7, and similarly to the first embodiment, the refrigerant absorbs heat by the first indoor heat exchanger 150, and the outdoor heat exchanger 130 and the second indoor heat exchanger 170. Thus, the indoor air can be cooled by the first indoor heat exchanger 150 and the indoor air can be heated by the second indoor heat exchanger 170.

  As described above, also in the flow path switching means using the three-way valve 120A, the electromagnetic valves 120B and 120C, the communication pipe 120D, etc., the outdoor heat exchanger 130, the first indoor heat exchanger 150, and the second indoor heat exchanger 170 are used. The cooling operation, the heating operation, and the dehumidifying heating operation that always use these three heat exchangers are possible.

(Third embodiment)
A third embodiment of the present invention is shown in FIG. 3rd Embodiment changes the arrangement | positioning position of the internal heat exchanger 195 with respect to the said 1st Embodiment.

  Here, one flow path through which the high-temperature and high-pressure refrigerant circulates in the internal heat exchanger 195 during the cooling operation or the dehumidifying heating operation is disposed in the branch pipe 161, thereby the same as in the first embodiment. The effect of can be obtained.

(Other embodiments)
In each of the above embodiments, the vapor compression cycle 100 has been described as being applied to a vehicle refrigeration cycle apparatus. However, the vapor compression cycle 100 may be applied to a refrigeration cycle of a home air conditioner.

It is a schematic diagram which shows the vapor | steam compression-type cycle in 1st Embodiment (at the time of air_conditionaing | cooling operation). It is a Mollier diagram which shows the refrigerant | coolant state at the time of air_conditionaing | cooling operation. It is a schematic diagram which shows the vapor compression cycle in 1st Embodiment (at the time of heating operation). It is a Mollier diagram which shows the refrigerant | coolant state at the time of heating operation. It is a schematic diagram which shows the vapor | steam compression-type cycle in 1st Embodiment (at the time of dehumidification heating operation). It is a Mollier diagram which shows the refrigerant | coolant state at the time of a dehumidification heating operation. It is a schematic diagram which shows the vapor compression type cycle in 2nd Embodiment. It is a schematic diagram which shows the vapor | steam compression-type cycle in 3rd Embodiment.

Explanation of symbols

100 Vapor compression cycle 110 Compressor 120 Four-way valve (flow path switching means)
130 Outdoor Heat Exchanger 140 Ejector 141 Nozzle Part 142 Refrigerant Suction Port 143 Booster Part 150 First Indoor Heat Exchanger 160 Throttle Mechanism (Decompressor)
161 Branch piping (branch flow path)
170 Second indoor heat exchanger 180 Throttle mechanism (variable throttle)
195 Internal heat exchanger

Claims (3)

A compressor (110) for sucking and compressing refrigerant;
An outdoor heat exchanger (130) for exchanging heat between the refrigerant and outdoor air;
The high-pressure refrigerant is decompressed and expanded by a nozzle (141) connected from the outdoor heat exchanger (130) and adjustable in opening, and after the refrigerant is sucked from the refrigerant suction port (142), 143) an ejector (140) to be boosted;
A first indoor heat exchanger (150) connected from the ejector (140) to exchange heat between the refrigerant and room air;
The refrigerant branches from between the outdoor heat exchanger (130) and the ejector (140), and is disposed in a branch flow path (161) connected to the refrigerant suction port (142) to decompress and expand the refrigerant. A decompressor (160);
A second indoor heat exchanger (170) disposed between the decompressor (160) and the refrigerant suction port (142) of the branch channel (161) and exchanging heat between the refrigerant and the indoor air. )When,
The compressor (110) sucks the refrigerant from the first indoor heat exchange (150) and discharges it to the outdoor heat exchanger (130), or from the outdoor heat exchanger (130). A flow path switching means (120) for switching the flow path of the refrigerant so as to inhale and discharge to the first indoor heat exchanger (150),
A variable throttle (not shown) disposed between the second indoor heat exchanger (170) and the refrigerant suction port (142) of the branch channel (161) to vary the throttle degree of the branch channel (161). 180).   The flow path switching means (120) includes a suction side of the compressor (110), a discharge side of the compressor (110), the outdoor heat exchanger (130) side, and the first indoor heat exchanger (150). The vapor compression cycle according to claim 1, wherein the four points on the side are connected to communicate with each other between two predetermined points, and the four-way valve (120) is configured to switch the combination of the communication. . The refrigerant flowing from the outdoor heat exchanger (130) to the decompressor (160);
The internal heat exchanger (195) for exchanging heat with the refrigerant flowing from the first indoor heat exchanger (150) to the compressor (110) is provided. 2. A vapor compression cycle according to 2.

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