JP2013024437A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner capable of securely performing a dehumidifying heating operation with no increase in an amount of enclosed refrigerant.SOLUTION: In an air conditioner 100, a control part 130 performs a dehumidifying heating operation such that conditioned air is dehumidified by an evaporator 116 and heated by a condenser 112 in a first mode in which an outdoor heat exchanger 114 is operated as a radiator with the condenser 112 or in a second mode in which the outdoor heat exchanger 114 is operated as a heat absorber with the evaporator 116. When an amount of refrigerant in the evaporator 116 becomes smaller than a predetermined amount, the opening degrees of a first throttle 113 and a second throttle 115 are changed. In the first mode, the state of the refrigerant flowed out from the outdoor heat exchanger 114 is controlled to be in a vapor liquid two-phase state. In the second mode, the state of the refrigerant flowed out from the condenser 112 is controlled to be in a vapor liquid two-phase state.

Description

  The present invention relates to a heat pump type air conditioner having a reheat dehumidifying type dehumidifying heating function.

  As a conventional air conditioner, for example, one disclosed in Patent Document 1 is known. In the air conditioner of Patent Document 1, a compressor, a condenser, an outdoor heat exchanger, and an evaporator are provided in a heat pump cycle, and the evaporator and the condenser are arranged in an air duct. A first throttle is provided between the condenser and the outdoor heat exchanger, and a second throttle is provided between the outdoor heat exchanger and the evaporator. As the first diaphragm and the second diaphragm, for example, variable diaphragms capable of adjusting the diaphragm opening are used.

  In the air conditioner of the cited document 1, the condenser and the outdoor heat exchanger are used as a radiator arranged in series, and the evaporator is used as a heat absorber, whereby the conditioned air is cooled (dehumidified) by the evaporator, and this cooling is performed. Dehumidification heating operation (dehumidification mode) is possible in which the conditioned air that has been (dehumidified) is heated by a condenser.

  During the dehumidifying heating operation, the rotation speed of the compressor is controlled so that the evaporator outlet temperature becomes the target outlet temperature Teo. In addition, combinations (ranks 1 to 5) of valve openings of the first throttle and the second throttle are determined in advance, and the two valve openings are set so that the condenser outlet temperature Tc becomes the target outlet temperature TAO. The combination (ranks 1 to 5) is changed according to the difference ΔT between the target outlet temperature Teo and the condenser outlet temperature Tc. The ranks 1 to 5 are changed from the first throttle ranks 1 to 5 which are changed from the small throttle opening degree to the large side, and the second throttle ranks are changed from the large throttle opening degree to the small side. The first diaphragm ranks 1 to 5 are formed to be a combination of 1 to 5 with each other.

Japanese Patent No. 3331765

  However, in the air conditioner of Patent Document 1, the refrigerant is condensed and liquefied by the condenser and the outdoor heat exchanger during the dehumidifying heating operation, so that the amount of liquid refrigerant held in the outdoor heat exchanger increases. If the required amount of refrigerant in the cycle at this time exceeds the actual amount of enclosed refrigerant, the evaporator is in a refrigerant shortage state, and the evaporator outlet side has an excessive degree of superheat and the dehumidifying capacity is reduced.

  In order to avoid this problem, it is necessary to enclose enough refrigerant in the cycle, but the amount of excess refrigerant under operating conditions with a small amount of refrigerant increases, and the basic amount of refrigerant to be encapsulated Therefore, it becomes necessary to enlarge the gas-liquid separator for storing the liquid refrigerant.

  In view of the above problems, an object of the present invention is to provide an air conditioner capable of performing a reliable dehumidifying and heating operation without increasing the amount of enclosed refrigerant.

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

In the invention described in claim 1, the compressor (111), the condenser (112), the first throttle (113), the outdoor heat exchanger (114), the second throttle (115), and the evaporator (116) are provided. A heat pump cycle (110) connected in a ring and circulated by a compressor (111);
The condenser (112) and the evaporator (116) are accommodated in the air duct (121), and the outdoor heat exchanger (114) is disposed outside the air duct (121).
In the air conditioner in which the throttle openings of the first throttle (113) and the second throttle (115) are controlled by the control unit (130),
The controller (130) controls the opening degree of the first throttle (113) and the second throttle (115), and causes the outdoor heat exchanger (114) to function as a radiator together with the condenser (112). Depending on the mode, or in the second mode in which the outdoor heat exchanger (114) functions as a heat absorber together with the evaporator (116), the evaporator (116) dehumidifies the conditioned air flowing in the air duct (121). When performing the dehumidifying and heating operation of heating in the condenser (112), when the refrigerant amount in the evaporator (116) is smaller than a predetermined amount, the first throttle (113) and the second throttle ( 115) by changing the throttle opening so that the state of the refrigerant flowing out of the outdoor heat exchanger (114) becomes a gas-liquid two-phase state in the case of the first mode, or in the case of the second mode. Clump Vessels of the refrigerant flowing out of the (112) state is characterized by controlling so that gas-liquid two-phase state.

  According to the present invention, when the amount of refrigerant in the evaporator (116) is smaller than a predetermined amount, the refrigerant flowing out of the outdoor heat exchanger (114) or the condenser (112) is gas-liquid. It is controlled to be in a two-phase state. Therefore, the state of the refrigerant flowing out from the outdoor heat exchanger (114) or the condenser (112) does not become a supercooled state in a liquid phase state, and the outdoor heat exchanger (114) or the condenser (112) It is suppressed that a large amount of refrigerant is held in the liquid phase state. Therefore, even if the amount of refrigerant sealed in the heat pump cycle (110) is not increased in the initial stage, the refrigerant shortage state in the evaporator (116) is suppressed, and the dehumidification capacity reduction in the evaporator (116) is suppressed. Therefore, it is possible to perform reliable dehumidifying and heating operation.

  In the second aspect of the invention, the control unit (130) causes the first throttle (113) and the second throttle (115) when the refrigerant amount in the evaporator (116) is smaller than a predetermined amount. ) To be increased so that the refrigerant flowing out of the outdoor heat exchanger (114) or the condenser (112) is in a gas-liquid two-phase state. It is a feature.

  According to the present invention, when the refrigerant amount in the evaporator (116) is smaller than a predetermined amount, in the case of the first mode, by increasing the opening of the second throttle (115), The amount of heat released from the outdoor heat exchanger (114) can be reduced to change the state of the refrigerant flowing out of the outdoor heat exchanger (114) into a gas-liquid two-phase state, and the refrigerant flowing out to the evaporator (116) The amount can be increased. Therefore, the dehumidifying ability in the evaporator (116) can be maintained. At this time, the amount of heat released by the outdoor heat exchanger (114) is reduced, so that the amount of heat released by the condenser (112) is increased and the heating capacity to the conditioned air is increased. By increasing the opening degree of 113), an increase in the heating capacity of the condenser (112) can be suppressed and the heating temperature of the conditioned air can be maintained.

  In the second mode, the amount of heat released from the condenser (112) can be reduced by increasing the opening of the first throttle (113) to reduce the amount of heat released from the condenser (112). It can be in a liquid two-phase state. And by increasing the opening of the second throttle (115), the amount of refrigerant flowing out from the outdoor heat exchanger (114) to the evaporator (116) can be increased. Dehumidification ability can be maintained.

In the third aspect of the present invention, the control unit (130) adjusts the predetermined combination of the throttle opening degrees of the first throttle (113) and the second throttle (115), thereby the condenser (112). The heating capacity control is executed so that the actual condenser temperature (TAV) at the temperature becomes the target condenser temperature (TAO) set as the target temperature,
The controller (130) changes the second throttle (115) so that the throttle opening becomes larger when the refrigerant amount in the evaporator (116) becomes smaller than a predetermined amount, After the amount of refrigerant flowing into (116) is increased, the opening of the second throttle (115) is changed by changing the throttle opening of the first throttle (113) to be larger in the heating capacity control. Adjustment is made to suppress an increase in the heating capacity of the condenser (112) due to the increase, and the state of the refrigerant flowing out of the outdoor heat exchanger (114) or the condenser (112) is a gas-liquid two-phase state. It is characterized by controlling to become.

  According to the present invention, as a result, since the apertures of the first aperture (113) and the second aperture (115) are both changed to be larger, the same effect as in claim 2 can be obtained. .

  In the invention according to claim 4, the control unit (130) determines that the refrigerant amount at the refrigerant outlet side of the evaporator (116) is smaller than the predetermined amount of refrigerant in the evaporator (116). It is characterized by determining when the degree of superheat (SH) is greater than a predetermined degree of superheat (SHa).

  According to the present invention, since the degree of superheat can be grasped by grasping the temperature of the refrigerant in the evaporator (116), the amount of refrigerant in the evaporator (116) is easily and reliably smaller than a predetermined amount. Can be determined.

In the invention according to claim 5, the gas-liquid separator (117) for separating the gas-liquid refrigerant and storing the liquid-phase refrigerant is provided between the evaporator (116) and the compressor (111).
The control unit (130) determines that the amount of refrigerant in the evaporator (116) is less than a predetermined amount, and the predetermined amount of liquid refrigerant in the gas-liquid separator (117) is predetermined. It is characterized by determining that the amount is less than the amount.

  According to the present invention, it is possible to grasp whether the amount of refrigerant on the low pressure side is large or small by detecting the amount of refrigerant in the gas-liquid separator (117). It can be determined that the amount is less than a predetermined amount.

In the invention described in claim 6, the compressor (111), the condenser (112), the first throttle (113), the outdoor heat exchanger (114), the second throttle (115), and the evaporator (116) are provided. A heat pump cycle (110) connected in a ring and circulated by a compressor (111);
The condenser (112) and the evaporator (116) are accommodated in the air duct (121), and the outdoor heat exchanger (114) is disposed outside the air duct (121).
In the air conditioner in which the throttle openings of the first throttle (113) and the second throttle (115) are controlled by the control unit (130),
A temperature type expansion valve (115A) connected in parallel to the second throttle (115) and having the throttle opening adjusted in accordance with the refrigerant temperature on the refrigerant outlet side of the evaporator (116),
The control unit (130) adjusts the combination of the throttle apertures of the first throttle (113) and the second throttle (115), so that the actual condenser temperature (TAV) in the condenser (112) is adjusted. However, the heating capacity control is executed so as to be the target condenser temperature (TAO) set as the target temperature,
The controller (130) controls the opening degree of the first throttle (113) and the second throttle (115), and causes the outdoor heat exchanger (114) to function as a radiator together with the condenser (112). Depending on the mode, or in the second mode in which the outdoor heat exchanger (114) functions as a heat absorber together with the evaporator (116), the evaporator (116) dehumidifies the conditioned air flowing in the air duct (121). In performing the dehumidifying and heating operation of heating in the condenser (112), when the temperature expansion valve (115A) is opened and the amount of refrigerant flowing into the evaporator (116) is increased, in the heating capacity control, Adjustment is made so as to suppress an increase in heating capacity in the condenser (112) when the temperature expansion valve (115A) is opened by changing the first throttle (113) so that the throttle opening is increased. Thus, in the first mode, the refrigerant flowing out of the outdoor heat exchanger (114) is in a gas-liquid two-phase state, or in the second mode, flowing out of the condenser (112). Control is performed so that the state of the refrigerant becomes a gas-liquid two-phase state.

  According to the present invention, the temperature type expansion valve (115A) adjusts the throttle opening according to the refrigerant temperature on the refrigerant outlet side of the evaporator (116), so the amount of refrigerant flowing into the evaporator (116) is always reduced. Maintaining it properly will not cause a refrigerant shortage condition.

  In the case of the first mode, the amount of heat released from the outdoor heat exchanger (114) is reduced by opening the temperature expansion valve (115A), and the amount of heat released from the condenser (112) is increased. As a result, the heating capacity of the conditioned air is increased, but since the opening of the first throttle (113) is increased, the increase in the heating capacity of the condenser (112) is suppressed, and the heating temperature of the conditioned air is reduced. Can be maintained. In the second mode, the amount of heat released from the condenser (112) can be reduced by increasing the opening of the first throttle (113) to reduce the amount of heat released from the condenser (112). It can be in a liquid two-phase state.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.

It is a block diagram which shows the whole structure of the air conditioner in 1st Embodiment. It is a control flowchart performed at the time of the dehumidification heating operation in 1st Embodiment. It is a map for determining the combination of the opening degree of a 1st aperture value and a 2nd aperture value. It is an operation diagram which shows the operating state 1 of a heat pump cycle. It is an operation diagram which shows the operating state 2 of a heat pump cycle. It is an operation diagram which shows the operating state 3 of a heat pump cycle. It is an operation diagram which shows the operation state 4 of a heat pump cycle. It is a map for determining the correction coefficient of aperture opening. It is an operation diagram which shows the refrigerant | coolant insufficient state in an evaporator. It is an operation diagram which shows the operation state after the aperture opening degree change of a 1st, 2nd aperture_diaphragm | restriction. It is a control flowchart performed at the time of dehumidification heating operation in 2nd Embodiment. It is a block diagram which shows the whole structure of the air conditioner in 3rd Embodiment. It is a control flowchart performed at the time of the dehumidification heating operation in 3rd Embodiment.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly indicate that the combination is possible in each embodiment, but also a combination of the embodiments even if they are not clearly specified unless there is a problem with the combination. It is also possible.

(First embodiment)
The air conditioner 100 in 1st Embodiment is demonstrated using FIGS. 1-10. FIG. 1 is a block diagram showing the overall configuration of the air conditioner 100, FIG. 2 is a control flowchart executed during the dehumidifying heating operation, and FIG. 3 is for determining a combination of opening degrees of the first throttle 113 and the second throttle 115. 4 to 7 are operation diagrams showing operating states 1 to 4 of the heat pump cycle 110, FIG. 8 is a map for determining a correction coefficient for the throttle opening, and FIG. 9 is a refrigerant shortage state in the indoor evaporator 116. FIG. 10 is an operation diagram showing an operation state after changing the apertures of the first aperture 113 and the second aperture 115. FIG.

  As shown in FIG. 1, the air conditioner 100 is a vehicle air conditioner mounted on a vehicle, for example. The air conditioner 100 includes a heat pump cycle 110, an indoor unit 120, a control device 130, and the like.

  The heat pump cycle 110 is a heat cycle for performing cooling, heating, or dehumidifying heating in the passenger compartment, and a compressor 111, an indoor condenser 112, a first throttle 113, an outdoor, and an annular refrigerant flow path 110a through which the refrigerant circulates. A heat exchanger 114, a second throttle 115, an indoor evaporator 116, an accumulator 117, and the like are provided, and a branch valve 118 is provided with an electromagnetic valve 119.

  Among the devices 111 to 119 constituting the heat pump cycle 110, the indoor condenser 112 and the indoor evaporator 116 are disposed in the vehicle interior (inside the instrument panel) as components of the indoor unit 120 described later, and others. The devices (111, 113 to 117, 119) are arranged in the engine room of the vehicle.

  The compressor 111 is an electric fluid machine that is driven by an electric motor (not shown) and compresses and discharges the refrigerant in the heat pump cycle 110 to a high temperature and a high pressure. The discharge amount of the refrigerant is adjusted according to the operating rotational speed. It has become so. The power supplied from a battery (not shown) is adjusted by the inverter 111a, so that the operating rotation speed and the refrigerant discharge amount of the compressor 111 are controlled. The operation of power adjustment by the inverter 111a is controlled by the control device 130.

  The indoor condenser 112 discharges the heat of the high-temperature and high-pressure refrigerant discharged from the compressor 111 to the air-conditioning air flowing through the air-conditioning case 121, and heats the air-conditioning air for heat dissipation. (Heat radiator) and corresponds to the condenser of the present invention. The indoor condenser 112 is disposed on the downstream side of the air flow for air conditioning in the air conditioning case 121.

  The first throttle 113 is a throttling section that allows the throttle opening to be adjusted from a fully open opening at which the flow passage cross-sectional area of the refrigerant flow passage 110a is equal to a predetermined throttle opening. The opening degree of the first diaphragm 113 is controlled by the control device 130.

  The outdoor heat exchanger 114 is a heat exchanger that exchanges heat between the refrigerant flowing out of the first throttle 113 and air outside the vehicle (hereinafter referred to as outside air). The outdoor heat exchanger 114 is disposed outside the air conditioning case 121 so as to overlap the front of a radiator (not shown) for cooling the engine, for example, in the engine room. An outdoor heat exchanger 114 and a radiator electric fan (not shown) for supplying outside air to the radiator are provided on the vehicle rear side of the radiator.

  During the cooling operation by the heat pump cycle 110, the throttle opening degree of the first throttle 113 is controlled to the fully opened opening degree, and the refrigerant flowing out from the indoor condenser 112 is not decompressed but remains at a high temperature and high pressure while being the outdoor heat exchanger. Inflow to 114. Therefore, the outdoor heat exchanger 114 functions as a heat dissipation heat exchanger (radiator) that releases the heat of the refrigerant to the outside air.

  Further, during the heating operation by the heat pump cycle 110, the throttle opening degree of the first throttle 113 is controlled to a predetermined throttle opening degree, and the refrigerant flowing out from the indoor condenser 112 is decompressed to a low temperature and a low pressure, and the outdoor heat. It flows into the exchanger 114. Therefore, the outdoor heat exchanger 114 functions as an endothermic heat exchanger (heat absorber) that absorbs heat from the outside air.

  In addition, during the dehumidifying and heating operation by the heat pump cycle 110, the opening degree of the first throttle 113 is controlled so that the size thereof is adjusted, and the refrigerant flowing out from the indoor condenser 112 is decompressed to some extent. In some cases, the air flows into the outdoor heat exchanger 114. In this case, the outdoor heat exchanger 114 functions as a heat dissipation heat exchanger (radiator) that releases the heat of the refrigerant to the outside air. Alternatively, during the dehumidifying and heating operation, the throttle opening of the first throttle 113 is controlled to a predetermined throttle opening, and the refrigerant flowing out of the indoor condenser 112 is decompressed to a low temperature and low pressure, and the outdoor heat exchanger 114. May flow into the In this case, the outdoor heat exchanger 114 functions as an endothermic heat exchanger (heat absorber) that absorbs heat from the outside air.

  The second throttle 115 is a decompression means that decompresses the refrigerant flowing out of the outdoor heat exchanger 114 with the throttle opening degree adjusted. The opening degree of the second diaphragm 115 is controlled by the control device 130.

  The indoor evaporator 116 exchanges heat between the refrigerant decompressed by the second throttle 115 and the air conditioning air flowing through the air conditioning case 121, absorbs heat from the air conditioning air to the refrigerant, and cools the air conditioning air. This is an endothermic heat exchanger (heat absorber) for cooling, which corresponds to the evaporator of the present invention. The indoor evaporator 116 is disposed in the air conditioning case 131 so as to cross the entire flow path. The indoor evaporator 126 is disposed in the air conditioning case 131 on the upstream side of the air flow for air conditioning with respect to the indoor condenser 112.

  The accumulator 117 corresponds to the gas-liquid separator of the present invention, and accepts the refrigerant flowing out from the indoor evaporator 116 or the refrigerant flowing through the branch flow path 118 described later, and separates the gas-liquid refrigerant. The liquid phase refrigerant is accumulated, and the gas phase refrigerant and a small amount of liquid phase refrigerant (oil is dissolved) near the bottom are sucked into the compressor 111.

  The branch flow path 118 is a flow path that connects between the outdoor heat exchanger 114 and the second throttle 115 and between the indoor evaporator 116 and the accumulator 117. The branch flow path 118 is a bypass flow path that bypasses the second throttle 115 and the indoor evaporator 116. An electromagnetic valve 119 that can open and close the branch flow path 118 is provided in the middle of the branch flow path 118. The opening and closing of the branch flow path 118 by the electromagnetic valve 119 is controlled by the control device 130.

  Next, the indoor unit 120 is a unit that adjusts the temperature of the air-conditioning air so as to be a set temperature set by the occupant and blows it out of one of the selected outlets (not shown) into the vehicle interior. is there. The indoor unit 120 is formed by providing a blower 122, an indoor evaporator 116, an indoor condenser 112, an air mix door 124, and the like in an air conditioning case 121.

  The blower 122 takes air-conditioning air into the air-conditioning case 121 from the inside air inlet 121a or the outside air inlet 121b formed on the air-conditioning air upstream side of the air-conditioning case 121, and the vehicle interior from the outlet on the most downstream side. It is the ventilation means which blows off. The operating rotational speed of the blower 122, that is, the amount of blown air is controlled by the control device 130. On the downstream side of the air flow for air conditioning of the blower 122, the indoor evaporator 116 and the indoor condenser 112 described above are sequentially arranged. Further, a bypass passage 123 is formed between the indoor condenser 112 and the air conditioning case 121 so that the air for air conditioning can flow through the indoor condenser 112.

  The air mix door 124 is an adjusting unit that adjusts the amount of air conditioning air that passes through the indoor condenser 112 and the bypass passage 123. The air mix door 124 is a rotary door that opens and closes the indoor condenser 112 (air conditioning air passage) or the bypass flow path 123. According to the opening degree of the air mix door 124, the flow rate ratio between the heated air that passes through the indoor condenser 112 and the cooling air that is cooled by the indoor evaporator 116 and flows through the bypass passage 123 is adjusted. Thus, the air-conditioning air temperature on the downstream side of the indoor condenser 112 is adjusted. The opening degree of the air mix door 124 is controlled by the control device 130.

  In the indoor unit 120, the downstream side of the indoor condenser 112 is connected to a plurality of outlets (a face outlet, a foot outlet, and a defroster outlet) toward the vehicle interior, and the temperature is adjusted by the air mix door 124. The air for air conditioning is blown into the vehicle interior from a selected outlet among the plurality of outlets.

  Between the indoor condenser 112 and the first throttle 113, a pressure sensor 131 that detects the pressure of the refrigerant flowing out of the indoor condenser 112 is provided. The pressure signal detected by the pressure sensor 131 is output to the control device 130.

  An inlet temperature sensor 132 that detects the temperature on the inlet side of the indoor evaporator 116 is provided on the refrigerant inlet side of the indoor evaporator 116. In addition, an outlet temperature sensor 133 that detects the temperature on the outlet side of the indoor evaporator 116 is provided on the refrigerant outlet side of the indoor evaporator 116. Each temperature sensor 132, 133 can be provided on the surface of the refrigerant tube of the indoor evaporator 116, the surface of the heat exchange fin, the surface of the header tank, or the like. The temperature signals detected by the temperature sensors 132 and 133 are output to the control device 130.

  The control device 130 is a control unit including a microcomputer and its peripheral circuits. In accordance with a preset program, the control device 130 is set by an occupant using an engine water temperature sensor (not shown), an outside air temperature sensor, various temperature signals from the inside air temperature sensor, a solar radiation signal from the solar radiation sensor, and an operation panel (not shown) Performs arithmetic processing for temperature signals and the like. Further, a calculation process is performed on the pressure signal from the pressure sensor 131 and the temperature signal from each of the temperature sensors 132 and 133. Further, the control device 130 controls the inverter 111a (compressor 111), the first throttle 113, the second throttle 115, the electromagnetic valve 119, the radiator electric fan, the blower 122, the air mix door 124, and the like based on the calculation result. Thus, the cooling operation, the heating operation, and the dehumidifying heating operation described below are performed.

  Next, the operation based on the above configuration will be described with reference to FIGS.

1. The cooling operation control device 130 calculates the required blowout temperature based on the outside air temperature obtained from the outside air temperature sensor, the inside air temperature obtained from the inside air temperature sensor, the amount of solar radiation obtained from the solar radiation sensor, and the set temperature set by the occupant. To do. And the control apparatus 130 selects the air conditioning air which should be taken in in the air conditioning case 121 according to required blowing temperature so that the temperature of the air conditioning air blown into the passenger compartment becomes the set temperature set by the occupant ( Whether inside air or outside air), the rotation speed (air flow rate) of the blower 122, the opening degree of the air mix door 124, the selection of the air outlet (whether face, foot or defroster) are performed.

  Further, in the heat pump cycle 110, the control device 130 sets the throttle opening of the first throttle 113 to the fully open opening, adjusts the throttle opening of the second throttle 115 to a predetermined throttle opening, closes the electromagnetic valve 119, The compressor 111 and the radiator electric fan are operated. Then, in the heat pump cycle 110, the refrigerant circulates in the order of the compressor 111, the indoor condenser 112, the first throttle 113, the outdoor heat exchanger 114, the second throttle 115, the indoor evaporator 116, the accumulator 117, and the compressor 111. To do.

  During the cooling operation, the air mixing door 124 is mainly rotated to close the indoor condenser 112 by the control device 130, and most of the air for air conditioning is controlled to flow through the bypass flow path 123. Therefore, the refrigerant flowing in the indoor condenser 112 is discharged from the indoor condenser 112 while maintaining high temperature and high pressure without radiating heat to the air for air conditioning. Further, since the first throttle 113 is fully opened, the high-temperature and high-pressure refrigerant that has flowed out of the indoor condenser 112 flows into the outdoor heat exchanger 114 without being depressurized in the first throttle 113. . Then, the heat of the refrigerant is released to the outside air by the outdoor heat exchanger 114, and the refrigerant is cooled.

  Further, the refrigerant cooled and flowing out of the outdoor heat exchanger 114 is decompressed to a low temperature and a low pressure by the second throttle 115 and flows into the indoor evaporator 116. Air-conditioning air in the indoor unit 130 is cooled by the refrigerant flowing in the indoor evaporator 116, becomes cooling air, passes through the bypass passage 123, and is blown out from the selected outlet to the vehicle interior. At this time, the temperature of the air for air conditioning is adjusted mainly by opening control of the air mix door 124. The refrigerant flowing out of the indoor evaporator 116 is gas-liquid separated by the accumulator 117, the liquid phase refrigerant is stored in the accumulator 117, and the gas phase refrigerant is sucked into the compressor 111.

2. The heating operation control device 130 calculates the necessary blowing temperature in the same manner as in the cooling operation. And the control apparatus 130 selects the air conditioning air which should be taken in in the air conditioning case 121 according to required blowing temperature so that the temperature of the air conditioning air blown into the passenger compartment becomes the set temperature set by the occupant ( Whether inside air or outside air), the rotation speed (air flow rate) of the blower 122, the opening degree of the air mix door 124, the selection of the air outlet (whether face, foot or defroster) are performed.

  Next, in the heat pump cycle 110, the control device 130 sets the throttle opening of the first throttle 113 to a predetermined throttle opening, fully closes the second throttle, opens the electromagnetic valve 119, and operates the compressor 111 and the radiator motor. Turn on the fan. Then, in the heat pump cycle 110, the refrigerant circulates in the order of the compressor 111, the indoor condenser 112, the first throttle 113, the outdoor heat exchanger 114, the branch flow path 118, the electromagnetic valve 119, the accumulator 117, and the compressor 111. .

  During the heating operation, the control device 130 causes the air mix door 124 to be rotated mainly to close the bypass flow path 123 so that most of the air for air conditioning passes through the indoor condenser 112. Therefore, the refrigerant flowing in the indoor condenser 112 dissipates heat to the air-conditioning air and heats the air-conditioning air. The refrigerant flowing out of the indoor condenser 112 is decompressed to low temperature and low pressure by the first throttle 113 and flows into the outdoor heat exchanger 114. In this case, the outdoor heat exchanger 114 functions as a heat absorber, and the refrigerant in the outdoor heat exchanger 114 absorbs heat from the outside air. As described above, during the heating operation, the air-conditioning air is heated by the indoor condenser 112 and blown out from the selected air outlet into the vehicle interior. At this time, the temperature of the air for air conditioning is adjusted mainly by opening control of the air mix door 124. The refrigerant flowing out of the outdoor heat exchanger 114 is gas-liquid separated by the accumulator 117 via the electromagnetic valve 119, the liquid phase refrigerant is stored in the accumulator 117, and the gas phase refrigerant is sucked into the compressor 111.

3. First, in the heat pump cycle 110, the dehumidifying and heating operation control device 130 closes the electromagnetic valve 119 and operates the compressor 111 and the radiator electric fan. Then, in the heat pump cycle 110, the refrigerant circulates in the order of the compressor 111, the indoor condenser 112, the first throttle 113, the outdoor heat exchanger 114, the second throttle 115, the indoor evaporator 116, the accumulator 117, and the compressor 111. To do.

  And the control apparatus 130 implements a dehumidification heating operation based on the flowchart shown in FIG. First, the control apparatus 130 performs dehumidification capability control by step S100. Specifically, the control device 130 calculates the target indoor evaporator temperature TEO in the indoor evaporator 116 in the dehumidifying heating operation so that the current indoor evaporator temperature TE becomes the calculated target indoor evaporator temperature TEO. Then, the target rotational speed IVO of the compressor 111 is determined, and the rotational speed of the compressor 111 is controlled.

  The target indoor evaporator temperature TEO is a target temperature required in the indoor evaporator 116 when performing the dehumidifying and heating operation. The control device 130 calculates a target indoor evaporator temperature TEO based on a predetermined target indoor evaporator temperature calculation map. The target indoor evaporator temperature calculation map is, for example, a map in which the outside air temperature obtained from the outside air temperature sensor and the target indoor evaporator temperature TEO are related in advance. Alternatively, the target indoor evaporator temperature calculation map is a map in which the required blowing temperature calculated during the cooling operation and the heating operation and the target indoor evaporator temperature TEO are related in advance. The current indoor evaporator temperature TE is a temperature obtained by the inlet temperature sensor 132.

  Next, the control apparatus 130 implements heating capacity control in step S110. Specifically, the control device 130 calculates the target indoor condenser temperature TAO in the indoor condenser 112 in the dehumidifying heating operation so that the current indoor condenser temperature TAV becomes the calculated target indoor condenser temperature TAO. In addition, the combination pattern of the apertures of the first aperture 113 and the second aperture 115 is adjusted, and the target aperture A of the first aperture 113 and the target aperture B of the second aperture 115 are determined. The target indoor condenser temperature TAV corresponds to the target condenser temperature of the present invention, and the current indoor condenser temperature TAV corresponds to the actual condenser temperature of the present invention.

  The target indoor condenser temperature TAO is a target temperature required in the indoor condenser 112 when performing the dehumidifying heating operation, and the control device 130 is provided in advance in the same manner as when calculating the target indoor evaporator temperature TEO. Based on the calculated target indoor condenser temperature calculation map, the target indoor condenser temperature TAO is calculated. The target indoor condenser temperature calculation map is, for example, a map in which the outside air temperature obtained from the outside air temperature sensor and the target indoor condenser temperature TAO are related in advance. Alternatively, the target indoor condenser temperature calculation map is a map in which the required blowing temperature calculated during the cooling operation and the heating operation and the target indoor condenser temperature TEO are related in advance. The current indoor condenser temperature TAV is calculated based on the refrigerant pressure value obtained by the pressure sensor 131, and the temperature value of the refrigerant corresponding to this pressure value is calculated and used. ing.

  In addition, the combination pattern of the opening degree of the first diaphragm 113 and the second diaphragm 115 is formed as follows. That is, as shown in FIG. 3, a plurality of opening levels in which the throttle opening of the first throttle 113 gradually decreases from the fully open side (large opening) to the fully closed side (small opening), A plurality of opening levels, in which the throttle opening of the second throttle 113 gradually increases from the fully closed side (small opening) to the fully open side (large opening), are combined with each other. The first aperture 113 and the second aperture 115 are formed as a combination pattern of aperture openings. Hereinafter, this is simply referred to as an opening combination pattern.

  When the combination pattern of the opening is changed from the left combination on the horizontal axis in FIG. 3 to the right combination, the heat pump cycle 110 can take the operation modes as shown in FIGS. That is, as the aperture of the first aperture 113 is increased and the aperture of the second aperture 115 is decreased, the pressure reduction at the second aperture 115 is increased. As shown in FIGS. The heat exchanger 114 functions as a radiator together with the indoor condenser 112, and the indoor evaporator 116 functions as a heat absorber. Hereinafter, this operation mode will be referred to as a first mode (FIGS. 4 and 5).

  Conversely, as the aperture of the first aperture 113 is decreased and the aperture of the second aperture 115 is increased, the pressure reduction at the first aperture 113 is increased. As shown in FIGS. The outdoor heat exchanger 114 functions as a heat absorber together with the indoor evaporator 116, and the indoor condenser 112 functions as a radiator. Hereinafter, this operation mode will be referred to as a second mode (FIGS. 6 and 7).

  The more the opening combination pattern is set to the left side of the horizontal axis in FIG. 3, the smaller the heat radiation in the indoor condenser 112 out of the indoor condenser 112 and the outdoor heat exchanger 114, and the indoor condenser 112. The current indoor condenser temperature TAV at becomes lower. Conversely, as the combination pattern of the opening degree is set to the combination on the right side of the horizontal axis in FIG. 3, the amount of heat absorbed by the outdoor heat exchanger 114 and the indoor evaporator 116 becomes larger, and the indoor condensation is balanced to this The heat radiation amount in the condenser 112 increases, and the current indoor condenser temperature TAV in the indoor condenser 112 increases. In step S110, the opening combination pattern is adjusted in this way, and the throttle opening of the first throttle 113 is determined as the target throttle opening A, and the throttle opening of the second throttle 115 is determined as the target throttle opening B. Thus, the heating capacity in the indoor condenser 112 is controlled.

  Next, in step S120, control device 130 determines whether or not the amount of refrigerant in indoor evaporator 116 is less than a predetermined amount. Here, specifically, the control device 130 grasps the refrigerant amount in the indoor evaporator 116 by using the superheat degree SH of the refrigerant on the refrigerant outlet side of the indoor evaporator 116.

  The control device 130 determines whether or not the superheat degree SH has exceeded a predetermined predetermined superheat degree SHa (for example, 5 ° C.). The control device 130 calculates the superheat degree SH using the refrigerant inlet temperature T1 obtained by the inlet temperature sensor 132 and the refrigerant outlet temperature T2 obtained by the outlet temperature sensor 133. That is, the refrigerant on the refrigerant inlet side of the indoor evaporator 116 is in a gas-liquid two-phase state in which the liquid-phase refrigerant is evaporated, and the refrigerant inlet temperature T1 becomes constant according to the pressure at that time, and the Mollier diagram of the refrigerant The temperature on the saturated vapor line is the same. On the other hand, the refrigerant on the refrigerant outlet side of the indoor evaporator 116 is in a vapor phase state where evaporation has been completed, and the refrigerant outlet temperature T2 rises as evaporation proceeds. Therefore, the superheat degree SH can be calculated as the refrigerant outlet temperature T2-the refrigerant inlet temperature T1.

  When determining that the calculated superheat degree SH has exceeded the predetermined superheat degree SHa in step S120, the control device 130 determines that the refrigerant amount in the indoor evaporator 116 is in an insufficient state, and in step S130, prevents the refrigerant shortage. Implement control. If NO is determined in step S120, the process returns to step S100. In step S130, when the operation mode of the heat pump cycle 110 is the first mode (FIGS. 4 and 5), the controller 130 determines that the state of the refrigerant flowing out of the outdoor heat exchanger 114 is the gas-liquid two-phase state. Or when the operation mode is the second mode (FIGS. 6 and 7), the first throttle 113 is set so that the state of the refrigerant flowing out of the indoor condenser 112 becomes a gas-liquid two-phase state. And the aperture of the second aperture 115 is changed.

  As described above, when the superheat degree SH exceeds the predetermined superheat degree SHa, in the first mode (FIGS. 4 and 5), the refrigerant is radiated (cooled) by the indoor condenser 112 and the outdoor heat exchanger 114. Is promoted and the amount of liquid-phase refrigerant retained in the outdoor heat exchanger 114 increases, so that the required amount of refrigerant in the indoor evaporator 116 is insufficient. Also in the second mode (FIGS. 6 and 7), the indoor condenser 112 promotes heat dissipation (cooling) of the refrigerant, the amount of liquid-phase refrigerant retained in the indoor condenser 112 increases, and the indoor evaporator 116 is increased. In this case, the required refrigerant amount is insufficient. Thus, when the refrigerant is insufficient in the indoor evaporator 116, the degree of cooling (dehumidification) of the air for air conditioning becomes insufficient, and the dehumidifying heating effect cannot be sufficiently obtained.

  Therefore, in step S130, in order to prevent the refrigerant shortage state in the indoor evaporator 116, the control device 130 corrects the throttle openings of the first throttle 113 and the second throttle 115 so that the superheat degree SH is equal to the predetermined superheat degree. It is made to become below SHa. For this purpose, the control device 130 determines a correction coefficient α for increasing both the target throttle opening A and the target throttle opening B determined in step S110.

  The control device 130 determines the correction coefficient α based on the map shown in FIG. That is, in the map, the horizontal axis represents superheat degree SH−predetermined superheat degree SHa, the vertical axis represents a correction coefficient α of 1 or more, and the relationship between the two is a positive linear function. That is, the correction coefficient α is determined as a larger value as the degree of superheat SH−the predetermined degree of superheat SHa increases. For example, as illustrated in FIG. 8, when the degree of superheat SH−the predetermined superheat degree SHa is obtained as C, the correction coefficient α is determined as D.

  After determining the correction coefficient α in step S130, the control device 130 determines the final throttle opening EVH of the first throttle 113 as the target throttle opening A × α in step S140, and the final throttle opening EV × of the second throttle 115. The throttle opening EVC is determined to be the target throttle opening B × α, and the throttle openings of the first throttle 113 and the second throttle 115 are changed to the final throttle opening EVH and the final throttle opening EVC, respectively. .

  As described above, in the present embodiment, in the dehumidifying and heating operation, when the refrigerant shortage state occurs in the indoor evaporator 116, the control device 130 sets the operation mode of the heat pump cycle 110 to the first mode (FIGS. 4 and 5). Therefore, when the state of the refrigerant flowing out of the outdoor heat exchanger 114 is a gas-liquid two-phase state or when the operation mode is the second mode (FIGS. 6 and 7), the indoor condenser 112 The throttle openings of the first throttle 113 and the second throttle 115 are changed so that the state of the refrigerant flowing out becomes a gas-liquid two-phase state.

  As a result, the state of the refrigerant flowing out of the outdoor heat exchanger 114 or the indoor condenser 112 does not become a supercooled state in the liquid phase state, and the inside of the outdoor heat exchanger 114 or the indoor condenser 112 is prevented. It is suppressed that a large amount of refrigerant is held in the liquid phase state. Therefore, without increasing the amount of refrigerant sealed in the heat pump cycle 110 in the initial stage, it is possible to suppress the refrigerant shortage state in the indoor evaporator 116 and suppress the dehumidification capacity decrease in the indoor evaporator 116, A reliable dehumidifying and heating operation can be performed.

  Specifically, in the present embodiment, when the apertures of the first aperture 113 and the second aperture 115 are changed, the apertures of both the apertures 113 and 115 are changed to be large. .

  Thereby, in the case of the first mode (FIGS. 4 and 5), for example, as shown in FIG. 9, the refrigerant is in a supercooled state on the refrigerant outflow side of the outdoor heat exchanger 114, and the refrigerant in the indoor evaporator 116 As shown in FIG. 10, by increasing the degree of opening of the second throttle 115, the amount of heat released from the outdoor heat exchanger 114 can be reduced by reducing the amount of heat released from the outdoor heat exchanger 114. The state of the refrigerant flowing out from the heat exchanger 114 can be changed to a gas-liquid two-phase state, and the amount of the refrigerant flowing out to the indoor evaporator 116 can be increased. Therefore, the dehumidifying ability in the indoor evaporator 116 can be maintained. At this time, the amount of heat released from the outdoor heat exchanger 114 is reduced, and the amount of heat released from the indoor condenser 112 is increased, increasing the heating capacity of the air for air conditioning. By increasing the degree, an increase in the heating capacity of the indoor condenser 112 can be suppressed and the heating temperature of the air-conditioning air can be maintained.

  In the case of the second mode (FIGS. 6 and 7), the amount of heat released from the indoor condenser 112 can be reduced by increasing the opening of the first throttle 113 to reduce the amount of heat released from the indoor condenser 112. The state can be changed to a gas-liquid two-phase state. And by increasing the opening degree of the second throttle 115, the amount of refrigerant flowing out from the outdoor heat exchanger 114 to the indoor evaporator 116 can be increased, and the dehumidifying ability in the outdoor evaporator 116 is maintained. Can do.

  Further, in the present embodiment, the refrigerant superheat degree SH on the refrigerant outlet side of the indoor evaporator 116 is determined by the predetermined superheat degree SHa that the refrigerant amount in the indoor evaporator 116 is smaller than the predetermined amount. Judgment is made when it becomes larger than the above.

  Thereby, since the superheat degree SH can be grasped by grasping the temperature of the refrigerant in the indoor evaporator 116, it is determined easily and reliably that the refrigerant amount in the indoor evaporator 116 is less than a predetermined amount. it can.

(Second Embodiment)
In the second embodiment, the configuration of the air conditioner 100 is the same as that of the first embodiment, but the control content during the dehumidifying heating operation is changed with respect to the first embodiment. A control flowchart executed during the dehumidifying and heating operation in the second embodiment is shown in FIG. The control flowchart (FIG. 11) of the second embodiment is obtained by changing steps S130 and S140 to steps S131 and S141, respectively, with respect to the control flowchart (FIG. 2) described in the first embodiment. It is said.

  As shown in FIG. 11, during the dehumidifying and heating operation, the control device 130 performs the refrigerant shortage prevention control in step S131 after step S100 to step S120. In step S131, first, the throttle opening of the second throttle 115 is corrected so that the superheat degree SH of the indoor evaporator 116 is equal to or less than the predetermined superheat degree SHa. The procedure for correcting the aperture opening degree of the second diaphragm 115 is the same as that in the first embodiment, and the correction coefficient α is determined based on the map shown in FIG.

  In step S141, the control device 130 determines the final throttle opening EVH of the first throttle 113 as the target throttle opening A set in step S110, and sets the final throttle opening EVC of the second throttle 115 as the target. The throttle opening is determined to be B × α, and the throttle opening of the second throttle 115 is increased.

  In the flowchart of FIG. 11, step S100 to step S141 are continuously repeated again after step S141. While this repetition is performed, in the heating capacity control of step S110, the control device 130 further changes (increases) the throttle opening of the first throttle 113.

  That is, in the case of the first mode (FIGS. 4 and 5), if the throttle opening of the second throttle 115 is increased in step S141, the amount of heat released from the outdoor heat exchanger 114 is reduced and flows out of the outdoor heat exchanger 114. As a result, the refrigerant state can be changed to a gas-liquid two-phase state and the amount of refrigerant flowing out to the indoor evaporator 116 can be increased. Therefore, the dehumidifying ability in the indoor evaporator 116 can be maintained. At this time, the amount of heat released from the indoor condenser 112 is increased by the amount of heat released from the outdoor heat exchanger 114, and the heating capacity of the air for air conditioning is increased. Therefore, in the heating capacity control in step S110, the control device 130 is changed so that the opening degree of the first diaphragm 113 is increased so as to suppress the increase in the heating capacity.

  In the case of the second mode (FIGS. 6 and 7), if the throttle opening of the second throttle 115 is increased in step S141, the amount of refrigerant flowing out from the outdoor heat exchanger 114 to the indoor evaporator 116 is increased. And the dehumidifying ability of the outdoor evaporator 116 can be maintained. At this time, the amount of heat dissipated in the indoor condenser 112 is increased so as to balance the amount of heat absorbed by the indoor evaporator 116, and the heating capacity of the air for air conditioning is increased. Therefore, in the heating capacity control in step S110, the control device 130 is changed so that the opening degree of the first diaphragm 113 is increased so as to suppress the increase in the heating capacity.

  In the second embodiment, the timing for changing (increasing) the opening degrees of the first throttle 113 and the second throttle 115 is different from that in the first embodiment, but the refrigerant amount in the indoor evaporator 116 is in an insufficient state. As a result, since the apertures of the first diaphragm 113 and the second diaphragm 115 are both changed so as to increase, the same effect as in the first embodiment can be obtained.

(Third embodiment)
FIG. 12 shows an air conditioner 100A according to the third embodiment. Moreover, the control flowchart performed at the time of the dehumidification heating operation in 3rd Embodiment is shown in FIG. In the third embodiment, the inlet temperature sensor 132 and the outlet temperature sensor 133 are eliminated and a temperature type expansion valve 115A is added to the first embodiment.

  A bypass passage 115B that bypasses the second throttle 115 is provided in the refrigerant passage 110a of the heat pump cycle 110A. The temperature type expansion valve 115A is disposed in the bypass flow path 115B, and automatically adjusts the opening degree of the bypass flow path 115B according to the degree of superheat SH of the refrigerant on the outlet side of the indoor evaporator 116. It is formed as. For example, when the degree of superheat SH exceeds a predetermined degree of superheat SHa, the temperature type expansion valve 115A changes the throttle opening of the temperature type expansion valve 115A to a larger side, and the amount of refrigerant flowing into the indoor evaporator 116 increases. Operates as On the contrary, the temperature type expansion valve 115A changes the throttle opening of the temperature type expansion valve 115A to a smaller side when the superheat degree SH becomes equal to or less than the predetermined superheat degree SH, and the amount of refrigerant flowing into the indoor evaporator 116 is reduced. Operates to be lowered. Thereby, the superheat degree SH is maintained at the predetermined superheat degree SHa.

  The control flowchart shown in FIG. 13 uses step S100 and step S110 described in the first embodiment as they are and adds step S142 after step S110.

  In step S100, the control device 130 determines the target rotational speed IVO of the compressor 111 for controlling the dehumidifying capacity, and controls the rotational speed of the compressor 111. Next, in step S110, the control device 130 determines the throttle openings (target throttle opening A, target throttle opening B) of the first throttle 113 and the second throttle 115 for heating capacity control (FIG. 3). ).

  In step S142, the control device 130 determines the final throttle opening EVH of the first throttle 113 as the target throttle opening A, and the final throttle opening EVC of the second throttle 115 as the target throttle opening B. decide. And the control apparatus 130 repeats step S100-step S142 continuously.

  Here, when a refrigerant shortage state occurs in the indoor evaporator 116 and the superheat degree SH exceeds the predetermined superheat degree SHa, the throttle opening degree of the temperature type expansion valve 115A is automatically changed to a larger side, The amount of refrigerant flowing into the evaporator 116 is increased.

  Then, when the throttle opening of the temperature type expansion valve 115A is changed to a larger side, the control device 130 in the heating capacity control of the next step S110 is performed while the steps S100 to S142 are repeated. The opening degree of the first diaphragm 113 is further changed (increased).

  Thereby, in the case of the first mode (FIGS. 4 and 5), the amount of heat released from the outdoor heat exchanger 114 is reduced by changing the throttle opening of the temperature type expansion valve 115A to the larger side. However, the heat dissipation amount in the indoor condenser 112 increases and the heating capacity to the air for air conditioning increases, but the controller 130 increases the opening of the first throttle 113 to increase the indoor condenser. The heating temperature of the air-conditioning air can be maintained while suppressing an increase in the heating capacity 112.

  In the case of the second mode (FIGS. 6 and 7), the control device 130 increases the opening degree of the first throttle 113 to reduce the amount of heat released from the indoor condenser 112, thereby reducing the amount of heat released from the indoor condenser 112. The state of the refrigerant flowing out can be changed to a gas-liquid two-phase state.

  In the third embodiment, the temperature type expansion valve 115A automatically adjusts the throttle opening according to the refrigerant temperature on the refrigerant outlet side of the indoor evaporator 116, so the amount of refrigerant flowing into the indoor evaporator 116 is always adjusted. Maintaining it properly will not cause a refrigerant shortage condition. And in 3rd Embodiment, since the temperature type expansion valve 115A is used, each temperature sensor 132 for detecting the superheat degree SH of the refrigerant | coolant of the exit side of the indoor evaporator 116 like the said 1st Embodiment, 133 can be made unnecessary.

(Other embodiments)
For example, a liquid level sensor is provided in the accumulator 117 to detect that the amount of refrigerant in the indoor evaporator 116 is less than a predetermined amount, and the amount of liquid refrigerant in the accumulator 117 is detected. The determination may be made when the refrigerant amount is smaller than a predetermined liquid phase refrigerant amount. Thereby, since it can be grasped whether the amount of refrigerant on the low pressure side of the heat pump cycle 110 is large or small, it can be easily and reliably determined that the amount of refrigerant in the indoor evaporator 116 is smaller than a predetermined amount.

100, 100A air conditioner 110, 110A heat pump cycle 111 compressor 112 indoor condenser (condenser)
113 First throttle 114 Outdoor heat exchanger 115 Second throttle 115A Thermal expansion valve 116 Indoor evaporator (evaporator)
117 Accumulator (gas-liquid separator)
121 Air conditioning case (air duct)
130 Control device (control unit)

Claims (6)

The compressor (111), the condenser (112), the first throttle (113), the outdoor heat exchanger (114), the second throttle (115), and the evaporator (116) are connected in an annular shape, and the compressor A heat pump cycle (110) in which the refrigerant is circulated by (111),
The condenser (112) and the evaporator (116) are accommodated in the air duct (121), and the outdoor heat exchanger (114) is disposed outside the air duct (121).
In the air conditioner in which the throttle openings of the first throttle (113) and the second throttle (115) are controlled by the control unit (130),
The control unit (130) controls the opening degree of the first throttle (113) and the second throttle (115) so that the outdoor heat exchanger (114) together with the condenser (112) is a radiator. The conditioned air flowing through the air duct (121) by the first mode that functions as a heat sink or the second mode in which the outdoor heat exchanger (114) functions as a heat absorber together with the evaporator (116). In performing dehumidification heating operation of dehumidifying with the evaporator (116) and heating with the condenser (112), when the amount of refrigerant in the evaporator (116) is less than a predetermined amount, By changing the opening degree of the first throttle (113) and the second throttle (115), the refrigerant flowing out of the outdoor heat exchanger (114) in the first mode is changed. Control is performed so that the state of the refrigerant flows out of the condenser (112) in the case of the second mode or the state of the refrigerant flowing out of the condenser (112). Air conditioner.   When the amount of refrigerant in the evaporator (116) is less than a predetermined amount, the control unit (130) opens the throttle openings of the first throttle (113) and the second throttle (115). And the refrigerant is controlled so that the state of the refrigerant flowing out of the outdoor heat exchanger (114) or the condenser (112) becomes a gas-liquid two-phase state. The air conditioner according to claim 1. The control unit (130) adjusts a predetermined combination of throttle openings of the first throttle (113) and the second throttle (115) to thereby adjust the actual condenser in the condenser (112). The heating capacity control is executed so that the temperature (TAV) becomes the target condenser temperature (TAO) set as the target temperature,
The controller (130) changes the throttle opening of the second throttle (115) to be larger when the refrigerant amount in the evaporator (116) becomes smaller than a predetermined amount. After the amount of refrigerant flowing into the evaporator (116) is increased, the second throttle is changed by changing the opening degree of the first throttle (113) in the heating capacity control. (115) is adjusted so as to suppress an increase in the heating capacity of the condenser (112) due to an increase in the opening degree, and is discharged from the outdoor heat exchanger (114) or the condenser (112). The air conditioner according to claim 1, wherein the state of the refrigerant is controlled to be a gas-liquid two-phase state.   The controller (130) determines that the amount of refrigerant in the evaporator (116) is less than a predetermined amount, and determines the degree of superheat (SH) of the refrigerant on the refrigerant outlet side of the evaporator (116). The air conditioner according to any one of claims 1 to 3, wherein the air conditioner is determined by being greater than a predetermined degree of superheat (SHA). Between the evaporator (116) and the compressor (111), a gas-liquid separator (117) that separates the gas-liquid of the refrigerant and stores a liquid-phase refrigerant is provided,
The controller (130) determines that the amount of refrigerant in the vaporizer (116) is less than a predetermined amount, and the amount of liquid-phase refrigerant in the gas-liquid separator (117) is predetermined. The air conditioner according to any one of claims 1 to 3, wherein the determination is made when the amount of liquid phase refrigerant is less than the amount. The compressor (111), the condenser (112), the first throttle (113), the outdoor heat exchanger (114), the second throttle (115), and the evaporator (116) are connected in an annular shape, and the compressor A heat pump cycle (110) in which the refrigerant is circulated by (111),
The condenser (112) and the evaporator (116) are accommodated in the air duct (121), and the outdoor heat exchanger (114) is disposed outside the air duct (121).
In the air conditioner in which the throttle openings of the first throttle (113) and the second throttle (115) are controlled by the control unit (130),
A temperature type expansion valve (115A) connected in parallel to the second throttle (115), the throttle opening degree of which is adjusted according to the refrigerant temperature on the refrigerant outlet side of the evaporator (116);
The control unit (130) adjusts a predetermined combination of throttle openings of the first throttle (113) and the second throttle (115) to thereby adjust the actual condenser in the condenser (112). The heating capacity control is executed so that the temperature (TAV) becomes the target condenser temperature (TAO) set as the target temperature,
The control unit (130) controls the opening degree of the first throttle (113) and the second throttle (115) so that the outdoor heat exchanger (114) together with the condenser (112) is a radiator. The conditioned air flowing through the air duct (121) by the first mode that functions as a heat sink or the second mode in which the outdoor heat exchanger (114) functions as a heat absorber together with the evaporator (116). When the dehumidifying and heating operation of dehumidifying with the evaporator (116) and heating with the condenser (112) is performed, the temperature expansion valve (115A) is opened and the refrigerant flows into the evaporator (116). When the amount is increased, in the heating capacity control, the temperature expansion valve (115A) is opened by changing the first throttle (113) so that the throttle opening is increased. In the case of the first mode, the state of the refrigerant flowing out of the outdoor heat exchanger (114) is a gas-liquid two-phase by adjusting so as to suppress the heating capacity increase in the condenser (112) accompanying The air conditioner is controlled so as to be in a state or in the second mode, the state of the refrigerant flowing out of the condenser (112) becomes a gas-liquid two-phase state.

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