JP2014069639A - Refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To expand a temperature control range of blowing air to be blown to an air-conditioning target space during a dehumidification operation.SOLUTION: A cold storage agent container 21 filled with a cold storage agent is integrated with an indoor evaporator 20 of a refrigeration cycle device. In a cold storage mode, the cold storage agent stores cold so as to delay progress of frost formation on the indoor evaporator 20, and in a cold release mode, inflow of a low-pressure refrigerant to the indoor evaporator 20 is prevented so as to suppress frost formation on the indoor evaporator 20. Thus, even when a refrigerant evaporation temperature in an outdoor heat exchanger 15 is sufficiently lowered, while frost formation on the indoor evaporator 20 is easily suppressed, heating capacity of blowing air in an indoor condenser 12 is increased, so as to enable expansion of a temperature control range of blowing air during a dehumidification operation.

Description

  The present invention relates to a refrigeration cycle apparatus applied to an air conditioner that performs a dehumidifying operation.

  Conventionally, Patent Document 1 discloses an air conditioner for a vehicle that performs a dehumidifying operation in which blown air is cooled and dehumidified, and the dehumidified blown air is reheated and blown to an air-conditioning target space. More specifically, the air conditioner of Patent Document 1 includes a vapor compression refrigeration cycle device configured to be able to switch the refrigerant circuit, and dehumidifies by cooling the blown air with an indoor evaporator of the refrigeration cycle device. The dehumidifying operation is performed by reheating the dehumidified blown air with an indoor condenser.

  Furthermore, in the air conditioner of Patent Document 1, the indoor evaporator and the outdoor heat exchanger are connected in parallel to the refrigerant circuit of the refrigeration cycle apparatus during dehumidifying heating operation in which heating is performed together with dehumidification in the vehicle interior, which is the air conditioning target space. It is switched as follows. Then, the air is reheated by dissipating the heat absorbed from the blown air by the indoor condenser and the heat absorbed from the outside air by the outdoor heat exchanger to the blown air by the indoor condenser.

JP-A-6-341732

  However, in the refrigeration cycle apparatus of Patent Document 1, even if the dehumidifying heating operation is performed at a low outside air temperature, the blown air may not be reheated to a temperature required for vehicle interior heating. The reason is that, in the refrigerant circuit configuration in which the indoor evaporator and the outdoor heat exchanger are connected in parallel during the dehumidifying heating operation as in the refrigeration cycle apparatus of Patent Document 1, the refrigerant evaporation temperature and the outdoor heat exchanger in the indoor evaporator are used. It is because the refrigerant | coolant evaporation temperature in this will correspond.

  That is, if the refrigerant evaporation temperature in the indoor evaporator is adjusted to a temperature that can suppress the frost formation (frost) of the indoor evaporator, the refrigerant evaporation temperature in the outdoor heat exchanger is also adjusted to an equivalent temperature. Sometimes the temperature difference between the refrigerant evaporation temperature and the outside air temperature in the outdoor heat exchanger is reduced. As a result, the refrigerant cannot absorb sufficient heat from the outside air in the outdoor heat exchanger, and the blown air cannot be sufficiently reheated in the indoor condenser.

  In other words, in the air conditioner described in Patent Literature 1, the temperature adjustment range of the blown air blown to the air-conditioning target space during the dehumidifying heating operation is limited, and a comfortable dehumidifying heating operation in the passenger compartment may not be realized. .

  In view of the above points, an object of the present invention is to expand the temperature adjustment range of the blown air blown into the air-conditioning target space during the dehumidifying operation in the refrigeration cycle apparatus applied to the air conditioning apparatus that performs the dehumidifying operation.

  The present invention proposes a new utilization mode of the cold storage means applied to the refrigeration cycle apparatus in that the cold storage means is applied to the refrigeration cycle apparatus applied to the air conditioning apparatus that performs dehumidification heating of the air-conditioning target space. Is. Furthermore, the present invention has the problem of expanding the temperature adjustment range of the blown air that is blown to the air-conditioning target space during dehumidifying operation without effectively complicating the cycle by effectively utilizing existing refrigeration cycle components. A new refrigeration cycle apparatus to be solved is proposed.

  The invention according to claim 1 is a refrigeration cycle apparatus applied to an air conditioner, the compressor (11) compressing and discharging the refrigerant, and the high-pressure refrigerant discharged from the compressor (11) as a heat source. Heating the heat exchanger (12, 12a) for heating the blown air blown into the air-conditioning target space, the decompression means (14) for decompressing the high-pressure refrigerant, and the refrigerant and outside air flowing out from the decompression means (14) The outdoor heat exchanger (15) to be exchanged and the evaporator (20) that exchanges heat between the refrigerant flowing out of the outdoor heat exchanger (15) and the blown air before passing through the heating heat exchanger (12, 12a). ) And the cold heat of the low-pressure side refrigerant flowing through the refrigerant flow path from the outlet side of the decompression means (14) to the suction side of the compressor (11), and the heat exchanger (12, 12a) for heating with cold heat Cold storage means for cooling the blown air before passing 21), a bypass passage (17) for guiding the refrigerant flowing out of the outdoor heat exchanger (15) to the suction side of the compressor (11) by bypassing the evaporator (20), and the outdoor heat exchanger (15) Among the refrigerant that has flowed out of the refrigerant, the flow rate adjusting means (16, 18) for adjusting the flow rate of the refrigerant flowing into the evaporator (20) and the flow rate of the refrigerant flowing into the bypass passage (17) are provided.

  According to this, until the cold storage means (21) sufficiently stores cold heat, the flow rate adjustment means (16, 18) mainly causes the refrigerant flowing out of the outdoor heat exchanger (15) to the evaporator (20) side. By letting it flow in, the blowing air is cooled and dehumidified by the endothermic action when the refrigerant evaporates in the evaporator (20), and the dehumidified blowing air is reheated in the heating heat exchanger (12, 12a). Dehumidifying operation can be realized.

  At this time, the refrigerant evaporating temperature of the low-pressure side refrigerant in the outdoor heat exchanger (15) is frosted on the evaporator (20) so that the blown air can be sufficiently heated by the heating heat exchanger (12, 12a). Even if the temperature is lowered to a temperature at which it can be generated, the cold storage means (21) stores cold heat, so that the progress of frost formation of the evaporator (20) can be delayed.

  On the other hand, after the cold storage means (21) has sufficiently stored cold heat, the flow rate adjustment means (16, 18) mainly causes the refrigerant flowing out of the outdoor heat exchanger (15) to flow into the bypass passage (17) side. Thus, it is possible to realize a dehumidifying operation in which the blown air is cooled and dehumidified by the cold heat stored in the cold storage means (21), and the dehumidified blown air is reheated by the heating heat exchanger (12, 12a).

  At this time, the refrigerant evaporating temperature of the low-pressure side refrigerant in the outdoor heat exchanger (15) is frosted on the evaporator (20) so that the blown air can be sufficiently heated by the heating heat exchanger (12, 12a). Even if the temperature is lowered to a temperature at which it can be generated, the flow rate of refrigerant flowing into the evaporator (20) is small, or the refrigerant does not flow into the evaporator (20), so that frost formation occurs in the evaporator (20). Can be suppressed.

  In other words, according to the present invention, the refrigerant evaporation temperature of the low-pressure refrigerant in the outdoor heat exchanger (15) is increased in order to increase the heating capacity of the blown air in the heating heat exchanger (12, 12a). Even if the flow rate is sufficiently reduced, the flow rate adjusting means (16, 18) adjusts the refrigerant flow rate flowing into the evaporator (20) and the refrigerant flow rate flowing into the bypass passage (17). Generation | occurrence | production of frost formation can be suppressed.

  As a result, the heating capability of the blown air in the heating heat exchanger (12, 12a) can be increased, and the temperature adjustment range of the blown air during the dehumidifying operation can be expanded.

  Of the refrigerant that has flowed out of the outdoor heat exchanger (15), the flow rate adjusting means (16, 18) includes a refrigerant flow rate that flows into the evaporator (20) side and a refrigerant that flows into the bypass passage (17) side. Not only those that continuously adjust the flow rate ratio to the flow rate, but also those that allow the refrigerant flowing out of the outdoor heat exchanger (15) to flow into either the evaporator (20) side or the bypass passage (17) side, etc. Is also included.

  Therefore, in the refrigeration cycle apparatus according to claim 1, the flow rate adjusting means includes a refrigerant circuit and an outdoor heat exchanger (15) for causing the total flow rate of the refrigerant flowing out from the outdoor heat exchanger (15) to flow into the evaporator (20). ) May be configured by refrigerant circuit switching means (16, 18) for switching the refrigerant circuit that causes the entire flow rate of the refrigerant flowing out from the refrigerant to flow into the bypass passage (17), and the flow rate adjusting means may be the outdoor heat exchanger (15). ) Of the refrigerant passage from the refrigerant outlet side to the evaporator (20) and a flow rate adjusting valve (16) that changes at least one of the passage pressure loss of the bypass passage (17).

  Moreover, in invention of Claim 6, it is a refrigeration cycle apparatus applied to an air conditioner, Comprising: The compressor (11) which compresses and discharges a refrigerant | coolant, The high pressure refrigerant | coolant discharged from the compressor (11) Heating heat exchanger (12) for heating the air blown into the air-conditioning target space as a heat source, decompression means (14) for decompressing the high-pressure refrigerant, and refrigerant flowing out from decompression means (14) An evaporator (20) that exchanges heat with the blown air before passing through the exchanger (12) and evaporates; an outdoor heat exchanger (15) that exchanges heat between the refrigerant flowing out of the evaporator (20) and the outside air; The cold energy of the low-pressure side refrigerant flowing in the refrigerant flow path from the outlet side of the decompression means (14) to the suction side of the compressor (11) is stored, and the cold heat before passing through the heat exchanger (12, 12a) for heating. Cold storage means (21) for cooling the blown air, and reduction Among the refrigerant flowing out from the bypass passage (17) for guiding the refrigerant flowing out from the means (14) to the inlet side of the outdoor heat exchanger (15) by bypassing the evaporator (20), And a flow rate adjusting means (16, 18) for adjusting the flow rate of refrigerant flowing into the evaporator (20) and the flow rate of refrigerant flowing into the bypass passage (17).

  According to this, the flow rate adjusting means (16, 18) mainly causes the refrigerant flowing out from the pressure reducing means (14) to flow into the evaporator (20) side until the cold storage means (21) sufficiently stores cold heat. Thus, a dehumidifying operation is performed in which the blown air is cooled and dehumidified by an endothermic action when the refrigerant evaporates in the evaporator (20), and the dehumidified blown air is reheated in the heating heat exchanger (12). realizable.

  At this time, the refrigerant evaporating temperature of the low-pressure refrigerant in the outdoor heat exchanger (15) may be frosted in the evaporator (20) so that the blown air can be sufficiently heated by the heating heat exchanger (12). Even if the temperature is lowered to the temperature, the cold storage means (21) stores the cold heat, so that the frost formation of the evaporator (20) can be delayed.

  On the other hand, after the cold storage means (21) has sufficiently stored cold energy, the flow rate adjustment means (16, 18) causes the refrigerant flowing out from the decompression means (14) to flow mainly into the bypass passage (17) side. The dehumidifying operation can be realized in which the blown air is cooled and dehumidified by the cold heat stored in the cold storage means (21) and the dehumidified blown air is reheated by the heating heat exchanger (12).

  At this time, the refrigerant evaporating temperature of the low-pressure refrigerant in the outdoor heat exchanger (15) may be frosted in the evaporator (20) so that the blown air can be sufficiently heated by the heating heat exchanger (12). Even when the temperature is lowered, the flow rate of the refrigerant flowing into the evaporator (20) is small, or the refrigerant does not flow into the evaporator (20), so that the frost formation on the evaporator (20) is suppressed. it can.

  That is, according to the present invention, the refrigerant evaporation temperature of the low-pressure side refrigerant in the outdoor heat exchanger (15) is sufficiently increased in order to increase the heating capacity of the blown air in the heating heat exchanger (12). The flow rate adjusting means (16, 18) adjusts the flow rate of refrigerant flowing into the evaporator (20) and the flow rate of refrigerant flowing into the bypass passage (17), so that the evaporator (20) is frosted. Can be prevented from occurring.

  As a result, similar to the first aspect of the invention, the heating air heating capacity in the heating heat exchanger (12) can be increased, and the temperature adjustment range of the blowing air during the dehumidifying operation can be expanded. it can.

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

It is a whole lineblock diagram of the refrigerating cycle device of a 1st embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode (1st mode) of the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode (2nd mode) of the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode (3rd mode) of the refrigerating-cycle apparatus of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode (4th mode) of the refrigerating-cycle apparatus of 1st Embodiment. It is a flowchart which shows the control flow at the time of the 2nd dehumidification heating mode of the refrigerating-cycle apparatus of 1st Embodiment. It is explanatory drawing explaining the temperature adjustable range of blowing air at the time of the 1st, 2nd dehumidification heating mode of the refrigerating-cycle apparatus of 1st Embodiment. It is explanatory drawing for demonstrating the change of the evaporator temperature with time progress in the refrigerating-cycle apparatus of 1st Embodiment. It is explanatory drawing for demonstrating the change of the refrigerant | coolant flow volume and evaporator temperature with time passage in the refrigerating-cycle apparatus of 2nd Embodiment. It is a whole block diagram of the refrigerating-cycle apparatus of 3rd Embodiment. It is a whole refrigeration cycle apparatus block diagram of 4th Embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. In the present embodiment, the vapor compression refrigeration cycle apparatus 10 is applied to a vehicle air conditioner 1 mounted on a hybrid vehicle that obtains driving force for vehicle travel from an internal combustion engine (engine) and a travel electric motor. . The refrigeration cycle apparatus 10 fulfills the function of heating or cooling the blown air blown into the vehicle interior that is the air-conditioning target space in the vehicle air conditioner 1.

  Further, the refrigeration cycle apparatus 10 includes a cooling mode refrigerant circuit that cools the blown air to cool the vehicle interior, a heating mode refrigerant circuit that heats the blown air and heats the vehicle interior, and the cooled and dehumidified blown air The refrigerant circuit in the first dehumidifying and heating mode for performing dehumidifying and heating in the passenger compartment by heating the air and the outside air temperature is executed when the outside air temperature is extremely low (for example, 0 ° C. or less), and the blown air is heated more than in the first dehumidifying and heating mode. It is configured to be switchable to a refrigerant circuit in a second dehumidifying and heating mode that increases the capacity and performs dehumidifying and heating in the vehicle interior.

  In FIG. 1, the refrigerant flow in the cooling mode refrigerant circuit is indicated by solid arrows, the refrigerant flow in the heating mode refrigerant circuit is indicated by white arrows, and the refrigerant flow in the first dehumidifying and heating mode refrigerant circuit is shown. Is indicated by hatched arrows, and the flow of the refrigerant in the refrigerant circuit in the second dehumidifying and heating mode is indicated by hatched arrows.

  Further, in this refrigeration cycle apparatus 10, an HFC-based refrigerant (specifically, R134a) is adopted as the refrigerant, and a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure Pd does not exceed the critical pressure of the refrigerant. It is composed. Of course, you may employ | adopt HFO type refrigerant | coolants (for example, R1234yf). Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.

  The compressor 11 is disposed in the engine room, sucks refrigerant in the refrigeration cycle apparatus 10, compresses it, and discharges it. A fixed displacement type compression mechanism 11a having a fixed discharge capacity is fixed by an electric motor 11b. It is configured as an electric compressor to be driven. Specifically, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed as the compression mechanism 11a.

  The operation (rotation speed) of the electric motor 11b is controlled by a control signal output from an air conditioning control device to be described later, and either an AC motor or a DC motor may be adopted. And the refrigerant | coolant discharge capability of the compression mechanism 11a is changed by this rotation speed control. Therefore, in this embodiment, the electric motor 11b comprises the discharge capability change means of the compression mechanism 11a.

  The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port side of the compressor 11. The indoor condenser 12 is disposed in a casing 31 of an indoor air conditioning unit 30 to be described later, dissipates the refrigerant discharged from the compressor 11 (high-pressure refrigerant), and passes through the indoor evaporator 20 to be described later. It is a heat exchanger for heating which heats.

  The inlet side of the first expansion valve 14 is connected to the refrigerant outlet side of the indoor condenser 12. The first expansion valve 14 is a decompression unit that decompresses the high-pressure refrigerant discharged from the compressor 11 in the heating mode, the second dehumidifying heating mode, and the like, and a valve body configured to change the throttle opening degree. An electric variable throttle mechanism having an electric actuator composed of a stepping motor that changes the throttle opening by displacing the valve body.

  Further, the first expansion valve 14 of the present embodiment is configured by a variable throttle mechanism with a fully open function that functions as a simple refrigerant passage without exhibiting almost a refrigerant decompression action by fully opening the throttle opening. The operation of the first expansion valve 14 is controlled by a control signal output from the air conditioning control device.

  The refrigerant inlet side of the outdoor heat exchanger 15 is connected to the outlet side of the first expansion valve 14. The outdoor heat exchanger 15 is disposed on the vehicle front side in the engine room, and exchanges heat between refrigerant on the downstream side of the indoor condenser 12 that circulates inside and air outside the vehicle (outside air) blown from a blower fan (not shown). It is something to be made. The blower fan is an electric blower whose number of rotations (blowing capacity) is controlled by a control voltage output from the air conditioning control device.

  An indoor evaporator 20 is connected to the refrigerant outlet side of the outdoor heat exchanger 15 via the second expansion valve 16. The basic configuration of the second expansion valve 16 is the same as that of the first expansion valve 14. Furthermore, the second expansion valve 16 of the present embodiment not only has a fully open function for fully opening the refrigerant passage from the outdoor heat exchanger 15 to the indoor evaporator 20 when the throttle opening is fully opened, but also fully closes the throttle opening. In this case, it is composed of a variable throttle mechanism with a fully closing function that closes the refrigerant passage.

  The indoor evaporator 20 is arranged in the casing 31 of the indoor air conditioning unit 30 on the upstream side of the blower air flow from the indoor condenser 12. Further, the indoor evaporator 20 evaporates the refrigerant circulating through the interior in the cooling mode and the first and second dehumidifying and heating modes, etc. by exchanging heat with the blown air before passing through the indoor condenser 12, It is a heat exchanger for cooling which cools blowing air.

  Moreover, the indoor evaporator 20 of this embodiment is integrated with a plurality of cool storage agent containers 21 filled with a cool storage agent containing paraffin having a phase transition temperature of 0 ° C. or more and 10 ° C. or less. The cold storage agent container 21 stores cold heat stored in the low-pressure side refrigerant flowing in the refrigerant flow path from the outlet side of the first expansion valve 14 functioning as a pressure reducing means to the suction side of the compressor 11 at least in the second dehumidifying heating mode. Means.

  More specifically, the indoor evaporator 20 of the present embodiment collects or distributes a plurality of tubes that circulate the refrigerant and refrigerants that are arranged on both ends of the plurality of tubes and circulate through the tubes. A so-called tank and tube type heat exchanger structure having a pair of collective distribution tanks and the like is configured.

  And while forming the air path which distribute | circulates blowing air between adjacent tubes, the above-mentioned cool storage agent container 21 is joined to at least one part of these tubes. Thereby, the indoor evaporator 20 and the cool storage agent container 21 are integrated so that heat transfer is possible between the low-pressure side refrigerant flowing through the tube of the indoor evaporator 20 and the cool storage agent of the cool storage agent container 21.

  As is clear from the fact that the indoor evaporator 20 and the cool storage agent container 21 are integrated, the cool storage agent container 21 can cool the blown air before passing through the indoor condenser 12 by the cold storage. The inlet side of the accumulator 19 is connected to the refrigerant outlet side of the indoor evaporator 20.

  The accumulator 19 is a gas-liquid separator that separates the gas-liquid refrigerant flowing into the accumulator 19 and stores excess refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 19. Therefore, the accumulator 19 functions to prevent liquid phase refrigerant from being sucked into the compressor 11 and prevent liquid compression in the compressor 11.

  Furthermore, a bypass passage 17 is connected to the refrigerant outlet side of the outdoor heat exchanger 15 of the present embodiment to guide the refrigerant flowing out of the outdoor heat exchanger 15 to the inlet side of the accumulator 19 by bypassing the indoor evaporator 20. ing. The bypass passage 17 is provided with an on-off valve 18 that opens and closes the bypass passage 17. The on-off valve 18 is an electromagnetic valve whose operation is controlled by a control signal output from the air conditioning control device.

  Therefore, when the on-off valve 18 is open, among the refrigerant flowing out from the outdoor heat exchanger 15, the refrigerant flow rate flowing into the indoor evaporator 20 side and the refrigerant flow rate flowing into the bypass passage 17 side are the second expansion. It can be adjusted by the throttle opening of the valve 16. In other words, when the on-off valve 18 is open, the second expansion valve 16 can adjust the flow rate ratio between the refrigerant flow rate flowing into the indoor evaporator 20 side and the refrigerant flow rate flowing into the bypass passage 17 side. .

  Specifically, when the second expansion valve 16 is fully closed when the on-off valve 18 is open, the entire flow rate of the refrigerant flowing out of the outdoor heat exchanger 15 can be caused to flow into the bypass passage 17 side. . Further, by closing the on-off valve 18 and opening the second expansion valve 16, the entire flow rate of the refrigerant flowing out of the outdoor heat exchanger 15 can be caused to flow into the indoor evaporator 20 side via the second expansion valve 16. it can.

  Thereby, in this embodiment, the refrigerant flow rate flowing into the indoor evaporator 20 side and the refrigerant flow rate flowing into the bypass passage 17 side among the refrigerants flowing out from the outdoor heat exchanger 15 by the second expansion valve 16 and the on-off valve 18. The flow rate adjusting means for adjusting the flow rate is configured.

  Further, the second expansion valve 16 and the on-off valve 18 of the present embodiment allow the total flow rate of the refrigerant flowing out of the outdoor heat exchanger 15 to the indoor evaporator 20 side, as will be described in a second dehumidifying heating mode described later. It functions as a refrigerant circuit switching means for switching between a refrigerant circuit to be introduced and a refrigerant circuit to which the entire flow rate of the refrigerant that has flowed out of the outdoor heat exchanger 15 is caused to flow into the bypass passage 17 side.

  Next, the indoor air conditioning unit 30 will be described. The indoor air conditioning unit 30 is for blowing out the blown air whose temperature has been adjusted by the refrigeration cycle apparatus 10 into the vehicle interior, and is disposed inside the instrument panel (instrument panel) at the forefront of the vehicle interior. Furthermore, the indoor air conditioning unit 30 is configured by housing a blower 32, the indoor evaporator 20, the indoor condenser 12 and the like in a casing 31 forming an outer shell thereof.

  The casing 31 forms an air passage for blown air blown into the vehicle interior, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent in strength. On the most upstream side of the blast air flow in the casing 31, an inside / outside air switching device 33 is arranged as an inside / outside air switching means for switching and introducing the inside air (vehicle compartment air) and the outside air (vehicle compartment outside air) into the casing 31. ing.

  The inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port through which the inside air is introduced into the casing 31 and the outside air introduction port through which the outside air is introduced by the inside / outside air switching door, so that the air volume of the inside air and the air volume of the outside air are adjusted. The air volume ratio is continuously changed. The inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning control device.

  On the downstream side of the blown air flow of the inside / outside air switching device 33, a blower (blower) 32 is disposed as a blowing means for blowing the air sucked through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.

  On the downstream side of the blower air flow of the blower 32, the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the blown air. Further, a cold air bypass passage 35 is formed in the casing 31 to flow the blown air that has passed through the indoor evaporator 20 to the downstream side by bypassing the indoor condenser 12.

  On the downstream side of the blower air flow of the indoor evaporator 20 and on the upstream side of the blower air flow of the indoor condenser 12, the ratio of the amount of air passing through the indoor condenser 12 among the blown air after passing through the indoor evaporator 20 An air mix door 34 for adjusting the air pressure is disposed.

  In addition, the blast air heated by the indoor condenser 12 and the blast air not heated by the indoor condenser 12 through the cold air bypass passage 35 are mixed on the downstream side of the blast air flow of the indoor condenser 12. A mixing space is provided. Furthermore, the opening hole which blows off the ventilation air (air-conditioning wind) mixed in the mixing space to the vehicle interior which is an air-conditioning object space is arrange | positioned in the most downstream part of the ventilation air flow of the casing 31. FIG.

  Specifically, the opening hole includes a face opening hole that blows air-conditioned air toward the upper body of the passenger in the passenger compartment, a foot opening hole that blows air-conditioned air toward the feet of the passenger, and an inner surface of the front window glass of the vehicle. A defroster opening hole (both not shown) for blowing the conditioned air toward is provided. The air flow downstream of these face opening holes, foot opening holes, and defroster opening holes is connected to the face air outlet, foot air outlet, and defroster air outlet provided in the vehicle interior via ducts that form air passages, respectively. Neither is shown).

  Therefore, the air mix door 34 adjusts the air volume ratio between the air volume that passes through the indoor condenser 12 and the air volume that passes through the cold air bypass passage 35, thereby adjusting the temperature of the conditioned air mixed in the mixing space. The temperature of the blast air (air conditioned air) blown out from each outlet to the vehicle interior is adjusted.

  That is, the air mix door 34 constitutes a temperature adjusting means for adjusting the temperature of the conditioned air blown into the vehicle interior. The air mix door 34 is driven by an electric actuator for driving the air mix door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning control device.

  Further, on the upstream side of the air flow of the face opening hole, foot opening hole, and defroster opening hole, a face door for adjusting the opening area of the face opening hole, a foot door for adjusting the opening area of the foot opening hole, and a defroster opening, respectively. A defroster door (both not shown) for adjusting the opening area of the hole is disposed.

  These face doors, foot doors, and defroster doors constitute opening hole mode switching means for switching the opening hole mode, and are linked to an electric actuator for driving the outlet mode door via a link mechanism or the like. And rotated. The operation of this electric actuator is also controlled by a control signal output from the air conditioning control device.

  Specifically, as the air outlet mode switched by the air outlet mode switching means, a face mode in which the face air outlet is fully opened and air is blown out from the face air outlet toward the upper body of the passenger in the passenger compartment, the face air outlet and the foot air outlet The bi-level mode that opens both of the air outlets and blows air toward the upper body and feet of passengers in the passenger compartment, fully opens the foot outlet and opens the defroster outlet by a small opening, and mainly draws air from the foot outlet. There is a foot mode for blowing air, and a foot defroster mode for opening air from both the foot air outlet and the defroster air outlet by opening the foot air outlet and the defroster air outlet to the same extent.

  Furthermore, it can also be set as the defroster mode which fully opens a defroster blower outlet and blows air from a defroster blower outlet to the vehicle front window glass inner surface by a passenger's manual operation of the blowout mode changeover switch provided in the operation panel.

  Next, the electric control unit of this embodiment will be described. The air conditioning control device includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. Then, various calculations and processes are performed based on the air-conditioning control program stored in the ROM, the inverter for the compressor 11 connected to the output side, the second expansion valve 16 and the on-off valve constituting the flow rate adjusting means 18, controls the operation of various air conditioning control devices such as the blower 32 and the various electric actuators described above.

  Further, on the input side of the air conditioning control device, an inside air sensor as an inside air temperature detecting means for detecting the vehicle interior temperature (inside air temperature) Tr, and an outside air sensor as an outside air temperature detecting means for detecting the outside air temperature (outside air temperature) Tam. A solar radiation sensor as a solar radiation amount detecting means for detecting the solar radiation amount As irradiated into the passenger compartment, a discharge temperature sensor for detecting the refrigerant discharge temperature Td of the refrigerant discharged from the compressor 11, and a refrigerant discharge pressure (high pressure) of the refrigerant discharged from the compressor 11 Side refrigerant pressure), a discharge pressure sensor for detecting Pd, an evaporator temperature sensor for detecting the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 20, and a blown air temperature TAV blown from the mixing space into the vehicle interior. A detection signal of a sensor group for air conditioning control such as an air temperature sensor and an outdoor heat exchanger temperature sensor for detecting an outdoor temperature Ts of the outdoor heat exchanger 15 is input.

  In the cooling mode, the discharge refrigerant pressure (high-pressure side refrigerant pressure) Pd of the present embodiment is the high-pressure side refrigerant pressure of the cycle from the refrigerant discharge port side of the compressor 11 to the second expansion valve 16 inlet side, and the heating mode Etc., the high-pressure side refrigerant pressure of the cycle from the refrigerant discharge port side of the compressor 11 to the first expansion valve 14 inlet side is obtained. Moreover, in this embodiment, although the ventilation air temperature sensor which detects blowing air temperature TAV is provided, the value calculated based on evaporator temperature Tefin, discharge refrigerant temperature Td, etc. is employ | adopted as this blowing air temperature TAV. May be.

  Moreover, the evaporator temperature sensor of the present embodiment specifically detects the temperature of the heat exchange fins arranged in the air passage of the indoor evaporator 20. Of course, as the evaporator temperature sensor, temperature detecting means for detecting the temperature of other parts of the indoor evaporator 20 may be adopted, or temperature detecting means for detecting the temperature of the blown air blown out from the indoor evaporator 20. May be adopted. The same applies to the outdoor heat exchanger temperature sensor.

  Furthermore, operation signals from various air conditioning operation switches provided on an operation panel disposed near the instrument panel in the front part of the vehicle interior are input to the input side of the air conditioning control device. As various air conditioning operation switches provided on the operation panel, specifically, an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner 1, an A / C switch (air conditioner switch) for cooling the blown air, There are an air volume setting switch for manually setting the air volume of the blower 32, a temperature setting switch as a target temperature setting means for setting the target temperature Tset in the passenger compartment, and a blow mode switching switch for manually setting the blow mode.

  The air-conditioning control device is configured such that control means for controlling various air-conditioning components connected to the output side is integrally configured. And software) constitute control means for controlling the operation of each air conditioning component.

  For example, in this embodiment, the configuration (hardware and software) for controlling the operation of the compressor 11 constitutes the discharge capacity control means, and controls the operations of the second expansion valve 16 and the on-off valve 18 constituting the flow rate adjusting means. The configuration (hardware and software) that constitutes the refrigerant flow rate control means. Of course, the discharge capacity control means, the refrigerant flow rate control means, and the like may be configured as separate control devices for the air conditioning control device.

  Next, the operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described. As described above, the vehicle air conditioner 1 according to the present embodiment can be switched to the operation in the cooling mode, the heating mode, the first dehumidifying heating mode, and the second dehumidifying heating mode. Switching between these operation modes is performed by executing an air conditioning control program. This air conditioning control program is executed when the auto switch on the operation panel is turned on.

More specifically, in the main routine of the air conditioning control program, the detection signals of the above-described sensor group for air conditioning control and operation signals from various air conditioning operation switches are read. And based on the read detection signal and the value of the operation signal, the target blowing temperature TAO that is the target temperature of the blown air blown into the vehicle interior is calculated based on the following formula F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × As + C (F1)
Note that Tset is the vehicle interior set temperature set by the temperature setting switch, Tr is the vehicle interior temperature (inside air temperature) detected by the inside air sensor, Tam is the outside air temperature detected by the outside air sensor, and As is detected by the solar radiation sensor. The amount of solar radiation. Kset, Kr, Kam, Ks are control gains, and C is a correction constant.

  Further, when the A / C switch of the operation panel is turned on and the target blowing temperature TAO is lower than a predetermined cooling reference temperature α (for example, 25 ° C.), the operation in the cooling mode is performed. Execute. Further, when the A / C switch is turned on, the target outlet temperature TAO is equal to or higher than the cooling reference temperature α, and the outside air temperature Tam is higher than a predetermined dehumidifying heating reference temperature β (for example, 5 ° C.). If so, the operation in the first dehumidifying and heating mode is executed.

  On the other hand, when the target blowing temperature TAO is equal to or higher than the cooling reference temperature α and the outside air temperature Tam is equal to or lower than the dehumidifying heating reference temperature β with the A / C switch turned on, the second Run in heating mode. And when the A / C switch is not turned on, the operation in the heating mode is executed. The operation in each operation mode will be described below.

(A) Cooling mode In the cooling mode, the air-conditioning control device closes the on-off valve 18 and fully opens the throttle opening of the first expansion valve 14 to bring the second expansion valve 16 into a throttle state that exerts a pressure reducing action. Thereby, in the cooling mode, as indicated by the white arrow in FIG. 1, the compressor 11 → the indoor condenser 12 → (the first expansion valve 14) → the outdoor heat exchanger 15 → the second expansion valve 16 → the indoor evaporator. A vapor compression refrigeration cycle in which refrigerant is circulated in the order of 20 → accumulator 19 → compressor 11 is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of the various air conditioning control devices (control signals output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, based on the target blowing temperature TAO, the target evaporator blowing temperature TEO of the indoor evaporator 20 is determined with reference to a control map stored in advance in the air conditioning control device.

  Then, based on the deviation between the target evaporator outlet temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor, the evaporator temperature Tefin approaches the target evaporator outlet temperature TEO using a feedback control method. Further, a control signal output to the electric motor of the compressor 11 is determined so that frost (frost) does not occur in the indoor evaporator 20.

  As for the control signal output to the second expansion valve 16, the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 15 and flowing into the second expansion valve 16 is approximately the maximum coefficient of performance (COP) of the cycle. It is determined so as to approach the target degree of supercooling determined to be a value.

  For the control signal output to the servo motor of the air mix door 34, the air mix door 34 closes the air passage on the indoor condenser 12 side, and the total flow rate of the blown air after passing through the indoor evaporator 20 is the cold air bypass. It is determined to pass the passage 35 side.

  Then, the control signal determined as described above is output to various air conditioning control devices. After that, until the operation of the vehicle air conditioner is requested by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle → the target blowout temperature TAO is calculated → the operating states of various air conditioning control devices are determined -> Control routines such as control voltage and control signal output are repeated. Such a control routine is repeated in the other operation modes.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the air mix door 34 closes the air passage on the indoor condenser 12 side, the refrigerant flowing into the indoor condenser 12 flows out of the indoor condenser 12 with almost no heat exchange with the blown air. .

  The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 14. At this time, since the first expansion valve 14 is fully opened, the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 15 without being depressurized by the first expansion valve 14. The refrigerant flowing into the outdoor heat exchanger 15 radiates heat to the outside air blown from the blower fan in the outdoor heat exchanger 15.

  Since the on-off valve 18 is closed, the refrigerant flowing out of the outdoor heat exchanger 15 flows into the second expansion valve 16 and is decompressed until it becomes a low-pressure refrigerant at the second expansion valve 16. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the indoor evaporator 20 and evaporates. Thereby, the blowing air blown from the blower 32 and the cool storage agent in the cool storage agent container 21 are cooled.

  The refrigerant flowing out of the indoor evaporator 20 flows into the accumulator 19 and is separated into gas and liquid. The gas-phase refrigerant separated by the accumulator 19 is sucked from the suction side of the compressor 11 and compressed by the compressor 11 again.

  As described above, in the cooling mode, it is possible to achieve cooling of the vehicle interior by blowing the blown air cooled by the indoor evaporator 20 into the vehicle interior.

(B) Heating mode In the heating mode, the air conditioning control device opens the on-off valve 18, sets the first expansion valve 14 to a throttle state that exerts a pressure reducing action, and fully closes the second expansion valve 16. Thereby, in the heating mode, as indicated by the black arrows in FIG. 1, the refrigerant is circulated in the order of the compressor 11 → the indoor condenser 12 → the first expansion valve 14 → the outdoor heat exchanger 15 → the accumulator 19 → the compressor 11. A vapor compression refrigeration cycle is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of the various air conditioning control devices (control signals output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor 11b of the compressor 11 is determined as follows. First, the target condenser temperature TCO of the indoor condenser 12 is determined on the basis of the target outlet temperature TAO with reference to a control map stored in advance in the air conditioning controller.

  Then, based on the deviation between the target condenser temperature TCO and the discharge refrigerant temperature Td detected by the discharge temperature sensor, the discharge refrigerant temperature Td is further approximated to the target condenser temperature TCO using a feedback control method. A control signal output to the electric motor 11b of the compressor 11 is determined so that an abnormal increase in the high-pressure side refrigerant pressure Pd is suppressed.

  Regarding the control signal output to the first expansion valve 14, the degree of supercooling of the refrigerant flowing out from the indoor condenser 12 and flowing into the first expansion valve 14 is approximately the maximum value of the coefficient of performance (COP) of the cycle. It is determined so as to approach the target supercooling degree determined to be.

  As for the control signal output to the servo motor of the air mix door 34, the air mix door 34 closes the cold air bypass passage 35, and the total flow rate of the blown air after passing through the indoor evaporator 20 is on the indoor condenser 12 side. It is determined to pass through the air passage.

  Therefore, in the refrigeration cycle apparatus 10 in the heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. The refrigerant flowing into the indoor condenser 12 exchanges heat with the blown air that has been blown from the blower 32 and passed through the indoor evaporator 20 to dissipate heat. Thereby, blowing air is heated.

  The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 14 and is depressurized by the first expansion valve 14 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 14 flows into the outdoor heat exchanger 15 and absorbs heat from the outside air blown from the blower fan.

  The refrigerant that has flowed out of the outdoor heat exchanger 15 flows into the accumulator 19 through the bypass passage 17 and is separated into gas and liquid because the on-off valve 18 is opened and the second expansion valve 16 is fully closed. The gas-phase refrigerant separated by the accumulator 19 is sucked from the suction side of the compressor 11 and compressed by the compressor 11 again.

  As described above, in the heating mode, the blown air heated by the indoor condenser 12 can be blown out into the vehicle interior to realize heating of the vehicle interior.

(C) 1st dehumidification heating mode In 1st dehumidification heating mode, while an air-conditioning control apparatus closes the on-off valve 18, both the 1st expansion valve 14 and the 2nd expansion valve 16 are made into the throttle state which exhibits a pressure reduction effect | action. . As a result, in the first dehumidifying and heating mode, as indicated by the hatched arrows in FIG. 1, the compressor 11, the indoor condenser 12, the first expansion valve 14, the outdoor heat exchanger 15, the second expansion valve 16, and the indoor A vapor compression refrigeration cycle in which the refrigerant is circulated in the order of the evaporator 20 → the accumulator 19 → the compressor 11 is configured.

  In other words, in the 1st dehumidification heating mode, it switches to the refrigerant circuit which flows the refrigerant | coolant which flowed out from the indoor condenser 12 in order of the outdoor heat exchanger 15-> indoor evaporator 20 in order. Furthermore, with this refrigerant circuit configuration, the air conditioning control device operates based on the target blowout temperature TAO, the detection signal of the sensor group, etc., and the operating states of various control devices connected to the air conditioning control device (controls output to the various control devices). Signal).

  For example, the control signal output to the electric motor 11b of the compressor 11 is determined similarly to the cooling mode. As for the control signal output to the servo motor of the air mix door 34, the air mix door 34 closes the cold air bypass passage 35, and the total flow rate of the blown air after passing through the indoor evaporator 20 is on the indoor condenser 12 side. It is determined to pass through the air passage.

  Further, the first expansion valve 14 and the second expansion valve 16 are changed according to the target blowing temperature TAO. Specifically, the air conditioning control device decreases the throttle opening of the first expansion valve 14 and increases the throttle opening of the second expansion valve 16 as the target blowing temperature TAO increases. Thereby, in the 1st dehumidification heating mode, the mode of four steps from the 1st mode to the 4th mode is performed.

(C-1) 1st mode 1st mode is performed when the target blowing temperature TAO is more than the cooling reference temperature (alpha) and below the predetermined 1st reference temperature at the time of 1st dehumidification heating mode. .

  In the first mode, the air conditioning control device fully opens the throttle opening of the first expansion valve 14 and puts the second expansion valve 16 in the throttle state. Therefore, in the first mode, although the cycle configuration is exactly the same as that in the cooling mode, the air mix door 34 fully opens the air passage on the indoor condenser 12 side, so the cycle is performed as shown in the Mollier diagram of FIG. The state of the circulating refrigerant changes.

  That is, as shown in FIG. 2, the high-pressure refrigerant (point a1) discharged from the compressor 11 flows into the indoor condenser 12 and is heat-exchanged with the blown air cooled and dehumidified by the indoor evaporator 20. To dissipate heat (point a1 → point a2 in FIG. 2). Thereby, blowing air is heated. The refrigerant that has flowed out of the indoor condenser 12 flows into the first expansion valve 14. At this time, since the first expansion valve 14 is fully opened, the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 15 without being depressurized by the first expansion valve 14.

  And the refrigerant | coolant which flowed into the outdoor heat exchanger 15 heat-exchanges with the external air ventilated from the ventilation fan in the outdoor heat exchanger 15, and radiates it (a2 point-> a3 point of FIG. 2). Since the on-off valve 18 is closed, the refrigerant flowing out of the outdoor heat exchanger 15 flows into the second expansion valve 16 and is decompressed until it becomes a low-pressure refrigerant at the second expansion valve 16 (point a3 in FIG. 2). → a4 points).

  The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the indoor evaporator 20 and evaporates (point a4 → a5 in FIG. 2). Thereby, the blowing air blown from the blower 32 and the cool storage agent in the cool storage agent container 21 are cooled. Then, the refrigerant that has flowed out of the indoor evaporator 20 flows from the accumulator 19 to the suction side of the compressor 11 and is compressed again by the compressor 11 as in the cooling mode.

  As described above, in the first mode, the blown air cooled by the indoor evaporator 20 and dehumidified can be heated by the indoor condenser 12 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

(C-2) 2nd mode 2nd mode is performed when the target blowing temperature TAO is higher than 1st reference temperature and becomes below 2nd predetermined reference temperature at the time of 1st dehumidification heating mode. . In the second mode, the air conditioning control device places the first expansion valve 14 in the throttle state, and increases the throttle opening of the second expansion valve 16 as compared with that in the first mode. Therefore, in the second mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

  That is, as shown in FIG. 3, the high-pressure refrigerant (point b1) discharged from the compressor 11 flows into the indoor condenser 12 and is heat-exchanged with the blown air cooled and dehumidified by the indoor evaporator 20. To dissipate heat (b1 point → b2 point in FIG. 3). Thereby, blowing air is heated. The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 14 and is depressurized until it becomes an intermediate pressure refrigerant (b2 point → b3 point in FIG. 3).

  Then, the intermediate-pressure refrigerant decompressed by the first expansion valve 14 flows into the outdoor heat exchanger 15 and radiates heat by exchanging heat with the outside air blown from the blower fan (b3 point → b4 point in FIG. 3). ). The refrigerant flowing out of the outdoor heat exchanger 15 is depressurized by the second expansion valve 16 until it becomes a low-pressure refrigerant (b4 point → b5 point in FIG. 3).

  The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the indoor evaporator 20 and evaporates (b5 point → b6 point in FIG. 3). Thereby, the blowing air blown from the blower 32 and the cool storage agent in the cool storage agent container 21 are cooled. Then, the refrigerant that has flowed out of the indoor evaporator 20 flows from the accumulator 19 to the suction side of the compressor 11 and is compressed again by the compressor 11 as in the cooling mode.

  As described above, in the second mode, similarly to the first mode, the blown air cooled and dehumidified by the indoor evaporator 20 can be heated by the indoor condenser 12 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

  At this time, in the second mode, since the first expansion valve 14 is in the throttle state, the temperature of the refrigerant flowing into the outdoor heat exchanger 15 can be lowered compared to the first mode. Therefore, the temperature difference between the temperature of the refrigerant in the outdoor heat exchanger 15 and the outside air temperature can be reduced, and the amount of heat released from the refrigerant in the outdoor heat exchanger 15 can be reduced.

  As a result, the refrigerant pressure in the indoor condenser 12 can be increased without increasing the refrigerant circulation flow rate that circulates the cycle with respect to the first mode, and the temperature blown out from the indoor condenser 12 than in the first mode. Can be raised.

(C-3) Third Mode The third mode is executed when the target outlet temperature TAO is higher than the second reference temperature and lower than or equal to a predetermined third reference temperature in the first dehumidifying heating mode. . In the third mode, the air conditioning control device decreases the throttle opening of the first expansion valve 14 than in the second mode, and increases the throttle opening of the second expansion valve 16 than in the second mode. Therefore, in the third mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

  That is, as shown in FIG. 4, the high-pressure refrigerant (point c1) discharged from the compressor 11 flows into the indoor condenser 12 and is heat-exchanged with the blown air cooled and dehumidified by the indoor evaporator 20. To dissipate heat (point c1 → point c2 in FIG. 4). Thereby, blowing air is heated. The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 14 and is depressurized until it becomes an intermediate pressure refrigerant (point c2 → c3 in FIG. 4).

  The intermediate-pressure refrigerant decompressed by the first expansion valve 14 flows into the outdoor heat exchanger 15 and absorbs heat from the outside air blown from the blower fan (point c3 → point c4 in FIG. 4). The refrigerant that has flowed out of the outdoor heat exchanger 15 is depressurized by the second expansion valve 16 until it becomes a low-pressure refrigerant (point c4 → point c5 in FIG. 4).

  The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the indoor evaporator 20 and evaporates (point c5 → point c6 in FIG. 4). Thereby, the blowing air blown from the blower 32 and the cool storage agent in the cool storage agent container 21 are cooled. Then, the refrigerant flowing out of the indoor evaporator 20 flows from the accumulator 19 to the suction side of the compressor 11 and is compressed again by the compressor 11 as in the cooling mode.

  As described above, in the third mode, as in the first and second modes, the blown air cooled and dehumidified by the indoor evaporator 20 is heated by the indoor condenser 12 and blown out into the vehicle interior. it can. Thereby, dehumidification heating of a vehicle interior is realizable.

  At this time, in the third mode, the outdoor heat exchanger 15 is caused to function as an evaporator by reducing the throttle opening of the first expansion valve 14, so that it is blown out from the indoor condenser 12 than in the second mode. Temperature can be increased.

  As a result, the suction refrigerant density of the compressor 11 can be increased with respect to the second mode, and the refrigerant pressure in the indoor condenser 12 is increased without increasing the rotation speed (refrigerant discharge capacity) of the compressor 11. The temperature blown out from the indoor condenser 12 can be increased more than in the second mode.

(C-4) 4th mode 4th mode is performed when the target blowing temperature TAO becomes higher than 3rd reference temperature at the time of 1st dehumidification heating mode. In the fourth mode, the air conditioning control device decreases the throttle opening of the first expansion valve 14 as compared with the third mode, and opens the second expansion valve 16 fully. Therefore, in the fourth mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

  That is, as shown in FIG. 5, the high-pressure refrigerant (point d1) discharged from the compressor 11 flows into the indoor condenser 12 and is heat-exchanged with the blown air cooled and dehumidified by the indoor evaporator 20. To dissipate heat (d1 point → d2 point in FIG. 5). Thereby, blowing air is heated. The refrigerant flowing out of the indoor condenser 12 flows into the first expansion valve 14 and is depressurized until it becomes a low-pressure refrigerant (point d2 → point d3 in FIG. 5).

  And the low-pressure refrigerant decompressed by the first expansion valve 14 flows into the outdoor heat exchanger 15 and absorbs heat from the outside air blown from the blower fan (point d3 → point d4 in FIG. 5). The refrigerant that has flowed out of the outdoor heat exchanger 15 flows into the indoor evaporator 20 through the second expansion valve 16. At this time, in the fourth mode, since the second expansion valve 16 is fully opened, the refrigerant that has flowed out of the outdoor heat exchanger 15 is not decompressed by the second expansion valve 16 and is sent to the indoor evaporator 20. It flows and evaporates (point d4 → point d5 in FIG. 5).

  Thereby, the blowing air blown from the blower 32 and the cool storage agent in the cool storage agent container 21 are cooled. Then, the refrigerant that has flowed out of the indoor evaporator 20 flows from the accumulator 19 to the suction side of the compressor 11 and is compressed again by the compressor 11 as in the cooling mode.

  As described above, in the fourth mode, as in the first to third modes, the blown air cooled and dehumidified by the indoor evaporator 20 is heated by the indoor condenser 12 and blown out into the vehicle interior. it can. Thereby, dehumidification heating of a vehicle interior is realizable.

  At this time, in the fourth mode, as in the third mode, the outdoor heat exchanger 15 functions as an evaporator, and the throttle opening of the first expansion valve 14 is reduced compared to the third mode. The refrigerant evaporation temperature in the heat exchanger 15 can be lowered. Therefore, the temperature difference between the refrigerant temperature and the outside air temperature in the outdoor heat exchanger 15 can be increased more than in the third mode, and the heat absorption amount of the refrigerant in the outdoor heat exchanger 15 can be increased.

  As a result, the suction refrigerant density of the compressor 11 can be increased with respect to the third mode, and the refrigerant pressure in the indoor condenser 12 is increased without increasing the rotation speed (refrigerant discharge capacity) of the compressor 11. The temperature blown out from the indoor condenser 12 can be increased more than in the third mode.

  Thus, in 1st dehumidification heating mode, the aperture opening degree of the 1st expansion valve 14 and the 2nd expansion valve 16 is changed according to the target blowing temperature TAO, and the outdoor heat exchanger 15 is used as a radiator or an evaporator. By making it function, the temperature of the blown air blown into the passenger compartment can be adjusted.

(D) Second Dehumidifying Heating Mode In the second dehumidifying and heating mode, the air conditioning control device opens and closes the on-off valve 18 and sets the first expansion valve 14 in the throttle state, and further opens the second expansion valve 16 fully or completely. Closed. Thereby, in 2nd dehumidification heating mode, the cool storage mode operation | movement which cools cold energy to the cool storage agent of the cool storage agent container 21, and the cool cooling which cools ventilation air by cooling the cold energy stored in the cool storage agent to blowing air Switch between mode operation.

  Specifically, the cold storage mode and the cooling mode are switched as shown in the flowchart of FIG. 6 is a control flow executed as a subroutine of the main routine described above.

  First, in step S <b> 1, it is determined whether or not the temperature of the indoor evaporator 20 (that is, the evaporator temperature Tefin) is equal to or lower than the dew point temperature of the intake air sucked from the inside / outside air switching device 33. The dew point temperature of the intake air introduced from the inside / outside air switching device 313 is preliminarily set in the air conditioning control device based on the inside air temperature Tr, the outside temperature Tam, and a control signal output to the electric actuator for the inside / outside air switching door. It is determined with reference to the stored control map.

  If it is determined in step S1 that the evaporator temperature Tefin is equal to or lower than the dew point temperature, the process returns to the main routine without switching the operation mode. On the other hand, when it is determined in step S1 that the evaporator temperature Tefin is higher than the dew point temperature, the process proceeds to step S2 to switch to the cold storage mode. The reason is that if the evaporator temperature Tefin is higher than the dew point temperature, the condensed water is evaporated and the blown air is humidified.

  Subsequently, in step S3, it is determined whether or not the evaporator temperature Tefin is equal to or higher than the reference frost prevention temperature (1 ° C. in the present embodiment) determined to prevent the indoor evaporator 20 from frosting. . If it is determined in step S3 that the evaporator temperature Tefin is equal to or higher than the reference frost prevention temperature, the process returns to the main routine without switching the operation mode.

  On the other hand, if it is determined in step S3 that the evaporator temperature Tefin is lower than the reference frost prevention temperature, the process proceeds to step S4 to switch to the cooling mode in order to prevent the indoor evaporator 20 from forming frost. Return to the main routine. Next, detailed operations in the cold storage mode and the cool-down mode will be described.

(D-1) Cold storage mode In the cold storage mode, the air conditioning control device closes the on-off valve 18 and fully opens the second expansion valve 16. As a result, in the cold storage mode, as indicated by the hatched arrow (shaded hatched arrow) in FIG. 1, the compressor 11 → the indoor condenser 12 → the first expansion valve 14 → the outdoor heat exchanger 15 → the second expansion. A vapor compression refrigeration cycle similar to the first dehumidifying heating mode in which the refrigerant is circulated in the order of the valve 16 → the indoor evaporator 20 → the accumulator 19 → the compressor 11 is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of the various control devices as in the heating mode. For example, the throttle opening of the first expansion valve 14 is determined in the same manner as in the heating mode. Thereby, the throttle opening degree of the first expansion valve 14 is adjusted so that the refrigerant can sufficiently absorb the heat necessary for heating the vehicle interior from the outside air by the outdoor heat exchanger 15. Other basic operations in the cold storage mode are the same as those in the fourth mode of the first dehumidifying and heating mode.

  Therefore, in the cold storage mode, the blown air blown from the blower 32 is cooled by the endothermic action when the refrigerant evaporates in the indoor evaporator 20, and the cool storage agent container 21 integrated with the indoor evaporator 20 is cooled. The cold energy is stored in the cool storage agent. Furthermore, the dehumidifying heating in the vehicle interior can be realized by heating the blown air cooled and dehumidified by the indoor evaporator 20 and blowing it out to the vehicle interior.

(D-2) Cooling Mode In the cooling mode, the air conditioning control device opens the on-off valve 18 and fully closes the second expansion valve 16. Thereby, in the cooling mode, as indicated by the hatched arrow (black arrow) in FIG. 1, the compressor 11 → the indoor condenser 12 → the first expansion valve 14 → the outdoor heat exchanger 15 → the accumulator 19 → A vapor compression refrigeration cycle similar to the heating mode in which the refrigerant is circulated in the order of the compressor 11 is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of the various control devices (control signals to be output to the various control devices) as in the heating mode. Therefore, in the cooling mode, the blown air cooled and dehumidified by the cold stored in the regenerator of the regenerator container 21 is heated by the indoor condenser 12 and blown into the vehicle interior, thereby dehumidifying the vehicle interior. Heating can be realized.

  As described above, according to the vehicle air conditioner 1 of the present embodiment, appropriate air conditioning in the passenger compartment is realized by switching the operation in the cooling mode, the heating mode, the first dehumidifying heating mode, and the second dehumidifying heating mode. can do. Furthermore, in the 2nd dehumidification heating mode of this embodiment, as shown in FIG. 7, the temperature adjustment range of the ventilation air ventilated to air-conditioning object space at the time of a dehumidification heating operation can be expanded with respect to a prior art.

  More specifically, in the second dehumidifying and heating mode of the present embodiment, the throttle opening of the first expansion valve 14 is adjusted in the same manner as in the heating mode, and the refrigerant evaporation temperature in the outdoor heat exchanger 15 is adjusted to the indoor evaporator. 20 is lower than the refrigerant evaporation temperature determined so that frost formation does not occur, so that the heat absorption amount of the refrigerant in the outdoor heat exchanger 15 can be increased as compared with the prior art.

  Therefore, the heat dissipation amount of the refrigerant in the indoor condenser 12 can be increased to increase the heating capacity of the blown air. As a result, the temperature adjustment range of the blown air blown into the vehicle interior can be expanded, and the sufficiently heated blown air can be blown into the vehicle interior even when performing dehumidifying heating at a low outside temperature. it can.

  Further, in the second dehumidifying and heating mode, as described in the flowchart of FIG. 6, since the cold storage mode and the cooling mode are switched according to the evaporator temperature Tefin, the refrigerant evaporation temperature in the outdoor heat exchanger 15 is changed. Even if it reduces, it can suppress easily that frost formation will arise in the indoor evaporator 20. FIG.

  This will be described in detail with reference to FIG. 8. In the cold storage mode of the present embodiment, as shown in FIG. 8, since the cold heat of the low-pressure refrigerant is stored in the cold storage agent of the cold storage container 21, the cold storage means is provided. The temperature lowering rate of the indoor evaporator 20 (that is, the lowering rate of the evaporator temperature Tefin) is slower than the refrigeration cycle apparatus that is not, and the progress of frosting of the indoor evaporator 20 can be delayed.

  On the other hand, in the cooling mode of the present embodiment, the refrigerant is not allowed to flow into the indoor evaporator 20, so that frost formation on the indoor evaporator 20 can be suppressed. Further, since the blown air can be cooled by the cold heat stored in the cool storage agent of the cool storage agent container 21, the temperature rise rate of the indoor evaporator 20 (that is, the evaporator temperature Tefin is higher than that of the refrigeration cycle apparatus having no cool storage means). (Rising speed) becomes slow, and the time during which the blown air can be cooled and dehumidified becomes longer.

  That is, in the 2nd dehumidification heating mode of this embodiment, the cycle of the temperature change of the indoor evaporator 20 can be lengthened rather than the refrigeration cycle apparatus which does not have a cool storage means, and switches between cool storage mode and cool-down mode. Since the controllability of the control can be improved, it is possible to easily suppress frost formation in the indoor evaporator 20. Furthermore, since the frequency of switching between the cold storage mode and the cooling mode is less than that of the refrigeration cycle apparatus that does not have the cold storage means, the operating noise of the on-off valve 18 and the second expansion valve 16 when switching the refrigerant circuit is suppressed. be able to.

  Further, in the refrigeration cycle apparatus including the electric compressor as the compressor 11 as in the present embodiment, for example, the refrigerant discharge capacity of the compressor 11 is easily adjusted and required for the engine-driven compressor 11 or the like. Easy to produce cold heat in the temperature range. For this reason, in the refrigerating cycle apparatus provided with an electric compressor, there was little necessity of utilizing a cool storage means.

  On the other hand, in this embodiment, when performing dehumidification heating of the air-conditioning target space, a refrigeration cycle provided with an electric compressor is used in that the cold storage means is used to suppress frost formation of the indoor evaporator 20. A new utilization mode of the cold storage means applied to the apparatus is proposed.

(Second Embodiment)
In the first embodiment, in the second dehumidifying and heating mode, the on-off valve 18 and the second expansion valve 16 that are flow rate adjusting means function as the refrigerant circuit switching means, and the refrigerant storage mode and the cooling mode are switched by switching the refrigerant circuit. Although the example which switches is demonstrated, this embodiment demonstrates the example which switches cold storage mode and cool-down mode, without switching a refrigerant circuit.

  Specifically, in the second dehumidifying and heating mode of the present embodiment, the air conditioning control device opens the on-off valve 18, puts the first expansion valve 14 into a throttled state, and puts the second expansion valve 16 into a throttled state. . Therefore, in the second dehumidifying and heating mode of the present embodiment, as indicated by the hatched arrows in FIG. 1, the compressor 11 → the indoor condenser 12 → the first expansion valve 14 → the outdoor heat exchanger 15 → the second expansion. A vapor compression refrigeration cycle in which the refrigerant flows in the order of the valve 16 → the indoor evaporator 20 → the accumulator 19 → the compressor 11 and the refrigerant flows in the order of the outdoor heat exchanger 15 → the bypass passage 17 → the accumulator 19 → the compressor 11 is configured. Is done.

  Further, with the configuration of this refrigerant circuit, as shown in FIG. 9, in the cold storage mode, the refrigerant flow rate flowing from the outdoor heat exchanger 15 to the indoor evaporator 20 side through the second expansion valve 16 is increased from the outdoor heat exchanger 15. The throttle opening degree of the second expansion valve 16 is determined so as to be larger than the flow rate of the refrigerant flowing toward the bypass passage 17 side. On the other hand, in the cooling mode, the flow rate of the refrigerant flowing from the outdoor heat exchanger 15 to the indoor evaporator 20 side is smaller than the flow rate of the refrigerant flowing from the outdoor heat exchanger 15 to the bypass passage 17 side. The throttle opening is determined.

  That is, the second expansion valve 16 of the present embodiment is a flow rate adjustment valve that changes the passage pressure loss of the refrigerant passage from the refrigerant outlet side of the outdoor heat exchanger 15 to the suction side of the compressor 11 via the indoor evaporator 20. It is functioning. The passage pressure loss means a pressure loss caused when a predetermined flow rate of refrigerant flows through the refrigerant passage.

  Other configurations and operations are the same as those in the first embodiment. Therefore, also in the 2nd dehumidification heating mode of this embodiment, the driving | operation of the cool storage mode and cool-down mode which operate | move equivalent to 1st Embodiment can be performed. As a result, in the second dehumidifying and heating mode, it is possible to easily suppress frost formation in the indoor evaporator 20, and the temperature adjustment range of the blown air can be expanded.

(Third embodiment)
In the present embodiment, an example in which the configuration of the refrigeration cycle apparatus is changed as shown in the overall configuration diagram of FIG. 10 will be described. In the refrigeration cycle apparatus 10a of this embodiment, the indoor condenser 12 is abolished, and the high-pressure refrigerant discharged from the compressor 11 and the heat medium circulating in the heat medium circulation circuit 120 (in this embodiment, an ethylene glycol aqueous solution) are used. A water-refrigerant heat exchanger 13 for heat exchange is provided. In FIG. 10, the same reference numerals are given to the same or equivalent parts as in the first embodiment. The same applies to the following drawings.

  Furthermore, the heat medium circulation circuit 120 includes a heater core 12 a that is disposed in the casing 31 of the indoor air conditioning unit 30 and exchanges heat between the heat medium and the blown air that has passed through the indoor evaporator 20, and the heat medium circulation circuit 120. A water pump 12b that pumps the heat medium is disposed. The water pump 12b is an electric water pump whose operation is controlled by a control signal output from the air conditioning control device.

  In the present embodiment, the air conditioning controller operates the water pump 12b during the heating mode, the first dehumidifying heating mode, and the second dehumidifying heating mode. Thus, in the heat medium circulation circuit 120, the heat medium circulates in the order of the water pump 12b → the water passage of the water-refrigerant heat exchanger 13 → the heater core 12a → the water pump 12b.

  Therefore, in the heating mode, in the first dehumidifying heating mode, and in the second dehumidifying heating mode, the heat absorbed by the high-pressure refrigerant when the heat medium passes through the water passage of the water-refrigerant heat exchanger 13 is heated by the heater core 12a. The air can be heated by dissipating heat to the air. That is, the heater core 12a of this embodiment functions as a heat exchanger for heating that uses the high-pressure refrigerant discharged from the compressor 11 as a heat source and heats the blown air through the heat medium.

  Other configurations and operations are the same as those in the first embodiment. Therefore, also in the 2nd dehumidification heating mode of this embodiment, it can suppress easily that frost formation will arise in the indoor evaporator 20, and the temperature adjustment range of blowing air can be expanded. Of course, in the refrigeration cycle apparatus 10a of the present embodiment, the cold storage mode and the cooling mode may be switched as in the second embodiment.

(Fourth embodiment)
In the present embodiment, an example in which the configuration of the refrigeration cycle apparatus is changed as shown in the overall configuration diagram of FIG. 11 will be described. In FIG. 11, for clarity of illustration, the description of a part of the configuration of the indoor air conditioning unit 30 is omitted from FIG. 1, but the basic configuration of the indoor air conditioning unit 30 of the present embodiment is as follows. This is the same as the indoor air conditioning unit 30 of the first embodiment.

  The refrigeration cycle apparatus 10b of the present embodiment switches between a refrigerant circuit in a cooling mode (corresponding to the cooling mode of the first embodiment) and a refrigerant circuit in a dehumidifying heating mode (corresponding to the second dehumidifying heating mode of the second embodiment). It is configured to be possible.

  Moreover, the 1st three-way valve 23a is connected to the discharge outlet side of the compressor 11 of this embodiment. The first three-way valve 23a is an operation mode switching means for switching the refrigerant circuit in each operation mode, and is an electric three-way valve whose operation is controlled by a control signal output from the air conditioning control device.

  Specifically, the first three-way valve 23a switches to a refrigerant circuit that connects the discharge port side of the compressor 11 and one refrigerant inlet / outlet side of the outdoor heat exchanger 15 in the cooling mode, and in the dehumidifying heating mode, The refrigerant circuit is switched to connect the discharge port side of the compressor 11 and the refrigerant inlet side of the indoor condenser 12.

  Further, a branch passage 17a is connected between the first three-way valve 23a and the outdoor heat exchanger 15 to guide the refrigerant flowing out of the outdoor heat exchanger 15 to the second three-way valve 23b side in the dehumidifying heating mode. The basic configuration of the second three-way valve 23b is the same as that of the first three-way valve 23a.

  Specifically, the second three-way valve 23b switches to a refrigerant circuit that connects one refrigerant inlet / outlet side of the indoor evaporator 20 and the inlet side of the accumulator 19 in the cooling mode, and outdoor heat exchange in the dehumidifying heating mode. It switches to the refrigerant circuit which connects one refrigerant | coolant inflow / outlet side of the container 15, and the inlet side of the accumulator 19. FIG.

  Further, in the refrigeration cycle apparatus 10b of the present embodiment, the first expansion valve is configured so that the refrigerant flowing out of the indoor condenser 12 can be decompressed and flown into the bypass passage 17 or the indoor evaporator 20 in the dehumidifying heating mode. The outlet side of 14 is connected to the bypass passage 17 and the upstream side of the indoor evaporator 20 in the dehumidifying heating mode. Other configurations of the refrigeration cycle apparatus 10b are the same as those in the first embodiment.

  Next, the operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described. As described above, in the vehicle air conditioner 1 of the present embodiment, the operation can be switched to the cooling mode and the dehumidifying heating mode.

(A) Cooling Mode In the cooling mode, the air conditioning control device controls the operation of the first three-way valve 23a so as to connect the discharge port side of the compressor 11 and one refrigerant inlet / outlet side of the outdoor heat exchanger 15. The operation of the second three-way valve 23b is controlled so that the outlet side of the indoor evaporator 20 and the inlet side of the accumulator 19 are connected. Further, the air conditioning control device closes the on-off valve 18 and puts the second expansion valve 16 into a throttled state that exerts a pressure reducing action.

  Thereby, in the cooling mode, as indicated by the white arrow in FIG. 11, the compressor 11 → (first three-way valve 23 a →) outdoor heat exchanger 15 → second expansion valve 16 → indoor evaporator 20 → accumulator 19 → A vapor compression refrigeration cycle in which refrigerant is circulated in the order of the compressor 11 is configured. That is, a refrigeration cycle similar to the cooling mode of the first embodiment is configured. Other operations are the same as those in the first embodiment.

  Therefore, in the cooling mode of the present embodiment, the blown air cooled by the indoor evaporator 20 can be blown out into the vehicle interior to achieve cooling of the vehicle interior.

(B) Dehumidification heating mode In the dehumidification heating mode, the air conditioning control device controls the operation of the first three-way valve 23a so as to connect the discharge port side of the compressor 11 and the refrigerant inlet side of the indoor condenser 12, and the outdoor The operation of the second three-way valve 23b is controlled so that one refrigerant inlet / outlet side of the heat exchanger 15 and the inlet side of the accumulator 19 are connected.

  Further, the air-conditioning control device opens and closes the on-off valve 18 as in the first embodiment, sets the first expansion valve 14 in the throttle state, and further opens the second expansion valve 16 fully open or fully closed. Thereby, in dehumidification heating mode, the driving | operation of the cool storage mode similar to 1st Embodiment and the driving | operation in a cool-down mode are switched. Other operations are the same as those in the first embodiment. Next, the detailed operation of the cold storage mode and the cooling mode of the present embodiment will be described.

(B-1) Cold storage mode In the cold storage mode, the air conditioning controller closes the on-off valve 18 and fully opens the second expansion valve 16. Thus, in the cold storage mode, as indicated by the hatched arrow in FIG. 11, the compressor 11 → (first three-way valve 23a →) indoor condenser 12 → first expansion valve 14 → indoor evaporator 20 → second A vapor compression refrigeration cycle in which the refrigerant is circulated in the order of the expansion valve 16 → the outdoor heat exchanger 15 → (the branch passage 17a → the second three-way valve 23b →) accumulator 19 → the compressor 11 is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of various control devices, as in the heating mode of the first embodiment.

  Therefore, in the cold storage mode, the blown air blown from the blower 32 is cooled by the endothermic action when the refrigerant evaporates in the indoor evaporator 20, and the cool storage agent container 21 integrated with the indoor evaporator 20 is cooled. The cold energy is stored in the cool storage agent. Furthermore, the dehumidifying heating in the vehicle interior can be realized by heating the blown air cooled and dehumidified by the indoor evaporator 20 and blowing it out to the vehicle interior.

(B-2) Cooling Mode In the cooling mode, the air conditioning control device opens the on-off valve 18 and fully closes the second expansion valve 16. Thereby, in the cooling mode, as indicated by the hatched arrow in FIG. 11, the compressor 11 → (first three-way valve 23a →) indoor condenser 12 → first expansion valve 14 → (bypass passage 17 →). The same vapor compression refrigeration cycle as in the heating mode in which the refrigerant is circulated in the order of the outdoor heat exchanger 15 → accumulator 19 → compressor 11 is configured.

  Furthermore, with this refrigerant circuit configuration, the air conditioning control device determines the operating states of various control devices, as in the heating mode of the first embodiment. Therefore, in the cooling mode, the blown air cooled and dehumidified by the cold stored in the regenerator of the regenerator container 21 is heated by the indoor condenser 12 and blown into the vehicle interior, thereby dehumidifying the vehicle interior. Heating can be realized.

  That is, in the cold storage mode of the present embodiment, the indoor evaporator 20 is arranged upstream of the outdoor heat exchanger 15 among the indoor evaporator 20 and the outdoor heat exchanger 15 connected in series with the refrigerant flow. Although the point which is done is different from the cold storage mode of the first embodiment, other configurations and operations are the same as those of the first embodiment.

  Therefore, even in the dehumidifying and heating mode of the present embodiment, it is possible to easily suppress frost formation in the indoor evaporator 20 as in the first embodiment, and the temperature adjustment range of the blown air is expanded. be able to.

  In the configuration of the refrigeration cycle apparatus 10b of the present embodiment as well, as in the second embodiment, by controlling the opening degree of the second expansion valve 16 with the on-off valve 18 opened in the dehumidifying heating mode, The mode and the cooling mode may be switched.

  That is, in the cold storage mode, the refrigerant flow rate flowing from the indoor condenser 12 to the indoor evaporator 20 side via the first expansion valve 14 flows from the indoor condenser 12 to the bypass passage 17 side via the first expansion valve 14. What is necessary is just to determine the aperture opening degree of the 2nd expansion valve 16 so that it may increase more. On the other hand, in the cooling mode, the throttle valve of the second expansion valve 16 is opened so that the refrigerant flow rate flowing from the indoor condenser 12 to the indoor evaporator 20 side becomes smaller than the refrigerant flow rate flowing from the indoor condenser 12 to the bypass passage 17 side. The degree should be determined.

  Also in the refrigeration cycle apparatus 10b of the present embodiment, as in the third embodiment, the indoor condenser 12 is abolished, a water-refrigerant heat exchanger and a heat medium circulation circuit are provided, and a water-refrigerant heat exchanger is provided. It is good also as a structure which heats blowing air with the heater core 12a arrange | positioned in the casing 31 of the indoor air-conditioning unit 30 by using the heat medium heated in (3) as a heat source.

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

  (1) In the above-described embodiment, the example in which the refrigeration cycle apparatus 10 of the present invention is applied to the vehicle air conditioner 1 mounted on a hybrid vehicle has been described, but the application of the present invention is not limited to this. For example, the present invention may be applied to an ordinary vehicle air conditioner that obtains driving force for traveling from an internal combustion engine (engine), or an electric vehicle (fuel cell vehicle) that obtains driving force for traveling from an electric motor for traveling. Etc.) may be applied.

  Further, when applied to a vehicle having an internal combustion engine, auxiliary heating means for heating the blown air using engine cooling water as a heat source may be arranged in the indoor air conditioning unit 30. Furthermore, in the third embodiment or the like, the heat medium circulation circuit 120 may be circulated using the engine coolant as a heat medium. Further, in the electric vehicle, the heat medium circulation circuit 120 may be circulated using cooling water for cooling the battery or the electric device as a heat medium.

  The auxiliary heating means is not limited to the auxiliary heating heat exchanger (heater core) that heats the blown air by using cooling water as a heat source, and an electric heater made of a PTC heater or nichrome wire may be adopted. Moreover, the refrigeration cycle apparatus 10 of the present invention is not limited to a vehicle, and may be applied to a stationary air conditioner.

  (2) The configuration of the refrigeration cycle apparatus of the present invention is not limited to that disclosed in the above embodiment. For example, the accumulator 19 may be eliminated, and a receiver that separates the gas-liquid of the high-pressure refrigerant that has flowed out of the indoor condenser 12 or the outdoor heat exchanger 15 and stores excess liquid-phase refrigerant may be provided. Furthermore, the refrigeration cycle apparatus 10 only needs to be able to realize at least a refrigerant circuit configuration equivalent to the second dehumidifying heating mode described above, and is not limited to one configured to be able to switch the refrigerant circuit.

  (3) Although the above-described embodiment has described the example in which the cold storage agent container 21 in which the cold storage agent is sealed is used as the cold storage unit, the cold storage unit is not limited thereto. For example, you may employ | adopt a hydrate etc. as a cool storage agent. Moreover, in the above-mentioned embodiment, the cool storage agent which stores the cold heat of 0 degreeC or more and 10 degrees C or less is employ | adopted, However, It is more than the temperature which can prevent the frost of the indoor evaporator 20, and below the dew point temperature of general suction air You may employ | adopt the cool storage agent which stores cold heat. Furthermore, you may employ | adopt the magnetic cool storage means which accumulates cold using the entropy change of a magnetic material.

  (4) In the above-described embodiment, the example in which the indoor evaporator 20 and the cool storage agent container 21 are integrated has been described, but the indoor evaporator 20 and the cool storage agent container 21 may be configured separately. For example, a cold storage material tank filled with a cold storage material is connected to a refrigerant passage extending from the refrigerant outlet side of the outdoor heat exchanger 15 to the refrigerant inlet side of the indoor evaporator 20, and cold storage is performed by allowing the low-pressure side refrigerant to flow into the tank. You may make it store cold energy in a material.

  (5) In the above-described embodiment, the example in which the flow rate adjusting means is configured by the second expansion valve 16 and the on-off valve 18 has been described, but the flow rate adjusting means is not limited to this. For example, an opening / closing means having the same configuration as the opening / closing valve 18 may be provided in the refrigerant passage extending from the connection portion with the bypass passage 17 to the refrigerant inlet side of the indoor evaporator 20, and this may be used as the refrigerant circuit switching means. Further, a three-type flow rate adjusting valve may be arranged at the connection portion of the bypass passage 17 on the refrigerant inlet side, and this may be used as the flow rate adjusting valve.

  (6) In the second dehumidifying and heating mode of the second embodiment, by controlling the throttle opening degree of the second expansion valve 16, as shown in FIG. 9, the refrigerant flow rate that flows into the indoor evaporator 20 side in the cold storage mode However, the control mode of the throttle opening degree of the second expansion valve 16 is not limited to this. For example, even if the throttle opening degree of the second expansion valve 16 is continuously controlled so that the evaporator temperature Tefin approaches a predetermined reference evaporator temperature (for example, 5 ° C.) using a feedback control method or the like. Good.

  (7) In each of the above-described embodiments, the air-conditioning control device performs the air on the indoor condenser 12 (heater core 12a) side in each operation mode of the heating mode, the cooling mode, the first dehumidifying heating mode, and the second dehumidifying heating mode. Although the example which operates the air mix door 34 so that either one of a channel | path and the cold wind bypass channel 35 is obstruct | occluded was demonstrated, the operation | movement of the air mix door 34 is not limited to this.

  For example, the air mix door 34 may open both the air passage on the indoor condenser 12 (heater core 12a) side and the cold air bypass passage 35. Then, the temperature of the air blown into the passenger compartment may be adjusted by adjusting the air volume ratio between the air volume that passes through the air passage on the indoor condenser 12 side and the air volume that passes through the cold air bypass passage 35. Such temperature adjustment is effective in that the temperature of the blown air can be easily finely adjusted.

  (8) In each of the above-described embodiments, an example in which each operation mode is switched by executing an air conditioning control program has been described. However, switching of each operation mode is not limited to this. For example, an operation mode setting switch for setting each operation mode may be provided on the operation panel, and the heating mode, the cooling mode, and the second dehumidifying heating mode may be switched according to an operation signal of the operation mode setting switch.

DESCRIPTION OF SYMBOLS 11 Compressor 12 Indoor condenser 12a Heater core 14 1st expansion valve 15 Outdoor heat exchanger 16 2nd expansion valve (flow rate adjustment means)
17 Bypass passage 18 On-off valve (flow rate adjusting means)
20 Indoor evaporator

Claims (6)

A refrigeration cycle apparatus applied to an air conditioner,
A compressor (11) for compressing and discharging the refrigerant;
A heat exchanger for heating (12, 12a) for heating the blown air blown to the air-conditioned space using the high-pressure refrigerant discharged from the compressor (11) as a heat source;
Decompression means (14) for decompressing the high-pressure refrigerant;
An outdoor heat exchanger (15) for exchanging heat between the refrigerant flowing out of the decompression means (14) and the outside air;
An evaporator (20) for evaporating the refrigerant flowing out of the outdoor heat exchanger (15) by exchanging heat with the blown air before passing through the heating heat exchanger (12, 12a);
The cold heat of the low-pressure side refrigerant flowing through the refrigerant flow path from the outlet side of the decompression means (14) to the suction side of the compressor (11) is stored, and the heating heat exchanger (12, 12a) is stored by the cold heat. ) Cold storage means (21) for cooling the blown air before passing;
A bypass passage (17) for guiding the refrigerant flowing out of the outdoor heat exchanger (15) to the suction side of the compressor (11) by bypassing the evaporator (20);
Of the refrigerant flowing out from the outdoor heat exchanger (15), flow rate adjusting means (16, 18) for adjusting the flow rate of refrigerant flowing into the evaporator (20) and the flow rate of refrigerant flowing into the bypass passage (17); A refrigeration cycle apparatus comprising:   The flow rate adjusting means adjusts the total flow rate of the refrigerant flowing out of the outdoor heat exchanger (15) and the refrigerant circuit for flowing the total flow rate of the refrigerant flowing out of the outdoor heat exchanger (15) into the evaporator (20). The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is configured by refrigerant circuit switching means (16, 18) for switching a refrigerant circuit flowing into the bypass passage (17).   The flow rate adjusting means includes passage pressure loss of the refrigerant passage from the refrigerant outlet side of the outdoor heat exchanger (15) to the suction side of the compressor (11) through the evaporator (20) and the bypass passage (17 The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is configured by a flow rate adjustment valve (18) that changes at least one of the passage pressure loss of (1).   The refrigeration according to any one of claims 1 to 3, wherein the cold storage means (21) includes a cold storage agent having a phase transition temperature of 0 ° C or higher and 10 ° C or lower. Cycle equipment. The cold storage means (21) has a cold storage agent for storing cold energy,
The evaporator (20) and the cold storage means (21) are integrated so as to be capable of transferring heat between the low-pressure side refrigerant flowing through the evaporator (20) and the cold storage agent. The refrigeration cycle apparatus according to any one of claims 1 to 4. A refrigeration cycle apparatus applied to an air conditioner,
A compressor (11) for compressing and discharging the refrigerant;
A heating heat exchanger (12) for heating the blown air blown into the air-conditioned space using the high-pressure refrigerant discharged from the compressor (11) as a heat source;
Decompression means (14) for decompressing the high-pressure refrigerant;
An evaporator (20) for evaporating the refrigerant flowing out of the decompression means (14) by exchanging heat with the blown air before passing through the heating heat exchanger (12);
An outdoor heat exchanger (15) for exchanging heat between the refrigerant flowing out of the evaporator (20) and the outside air;
The cold heat of the low-pressure side refrigerant flowing through the refrigerant flow path from the outlet side of the decompression means (14) to the suction side of the compressor (11) is stored, and the heating heat exchanger (12, 12a) is stored by the cold heat. ) Cold storage means (21) for cooling the blown air before passing;
A bypass passage (17) for guiding the refrigerant flowing out from the decompression means (14) to the inlet side of the outdoor heat exchanger (15) by bypassing the evaporator (20);
Flow rate adjusting means (16, 18) for adjusting the flow rate of refrigerant flowing into the evaporator (20) and the flow rate of refrigerant flowing into the bypass passage (17) out of the refrigerant flowing out from the decompression means (14). A refrigeration cycle apparatus characterized by that.

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