Patent Publication Number: US-2020292218-A1

Title: Refrigeration cycle device

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     The present application is a continuation application of International Patent Application No. PCT/JP2018/041810 filed on Nov. 12, 2018, which designated the U.S. and claims the benefit of priority from Japanese Patent Application No. 2017-233196 filed on Dec. 5, 2017. The entire disclosures of all of the above applications are incorporated herein by reference. 
    
    
     TECHNICAL FIELD 
     The present disclosure relates to a refrigeration cycle device. 
     BACKGROUND ART 
     A refrigeration cycle device includes a compressor, an outside evaporator, an inside evaporator, and an evaporating pressure adjusting valve. The evaporating pressure adjusting valve is configured to adjust an evaporating pressure of a refrigerant in the inside evaporator as a value equal to or higher than a frost restriction pressure to restrict a frost from generating on the inside evaporator. The evaporating pressure adjusting valve is configured to adjust an opening degree of the valve with a mechanical means. 
     SUMMARY 
     A refrigeration cycle device includes a compressor, a heater, an inside evaporator, an outside evaporator, a first refrigerant passage, a first decompressor, a second refrigerant passage, a second decompressor, an evaporating pressure adjusting valve, a third refrigerant passage, an opening-closing member, a charging port, and a pressure change buffer. The compressor compresses and discharges a refrigerant. The heater heats a heat-exchange target fluid using the refrigerant, as a heat source, discharged from the compressor. The outside evaporator exchanges heat between an outside air and the refrigerant flowing out of the heater. The inside evaporator exchanges heat between the refrigerant flowing out of the outside evaporator and the heat-exchange target fluid. The refrigerant flowing out of the heater is guided toward an inlet of the outside evaporator through the first refrigerant passage. The first decompressor is disposed in the first refrigerant passage and configured to vary an opening area of the first refrigerant passage. The refrigerant flowing out of the outside evaporator flows through the inside evaporator toward a suction inlet of the compressor through the second refrigerant passage. The second decompressor is disposed in the second refrigerant passage between the outside evaporator and the inside evaporator and configured to vary an opening area of the second refrigerant passage. The evaporating pressure adjusting valve is disposed in the second refrigerant passage at a position downstream of the inside evaporator and configured to adjust an evaporating pressure of the refrigerant in the inside evaporator. The third refrigerant passage has an end fluidly connected to a portion of the second refrigerant passage between the evaporating pressure adjusting valve and the compressor. The refrigerant flowing out of the outside evaporator is guided toward the suction inlet of the compressor through the third refrigerant passage. The charging port through which the refrigerant is supplied is disposed in the second refrigerant passage at a position downstream of the evaporating pressure adjusting valve. The pressure change buffer is disposed in the second refrigerant passage between the evaporating pressure adjusting valve and the charging port and defines a buffer space to restrict an inner pressure in the second refrigerant passage from rapidly changing when the refrigerant is supplied through the charging port 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a diagram of an air conditioner including a refrigeration cycle device according to a first embodiment. 
         FIG. 2  is a diagram of an air conditioner including a refrigeration cycle device according to a second embodiment. 
         FIG. 3  is a diagram of an air conditioner including a refrigeration cycle device according to a third embodiment. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     To begin with, examples of relevant techniques will be described. 
     A refrigeration cycle device includes a compressor, an outside evaporator, an inside evaporator, and an evaporating pressure adjusting valve. The evaporating pressure adjusting valve is configured to adjust an evaporating pressure of a refrigerant in the inside evaporator as a value equal to or higher than a frost restriction pressure to restrict a frost from generating on the inside evaporator. The evaporating pressure adjusting valve is configured to adjust an opening degree of the valve with a mechanical means. 
     The refrigeration cycle device includes a high-pressure charging port at a position downstream of the compressor to supply the refrigerant before shipping the cycle device. The refrigeration cycle device includes a low-pressure charging port at a downstream of a low-pressure evaporator to supply the refrigerant after shipping the cycle device. 
     The evaporating pressure adjusting valve of the refrigeration cycle device varies the opening degree of the valve according to a pressure difference between the refrigerant upstream of the valve and the refrigerant downstream of the valve. When the pressure of the refrigerant downstream of the valve exceeds the pressure of the refrigerant upstream of the valve and thus a counter pressure is applied to the evaporating pressure adjusting valve, a durability of the evaporating pressure adjusting valve may be impaired. Thus, the low-pressure charging port is typically disposed at a position upstream of the evaporating pressure adjusting valve. 
     As described above, it is difficult to arrange the low-pressure charging port at a position downstream of the evaporating pressure adjusting valve, and therefore a flexibility of positions at which the low-pressure charging port is disposed is limited. Thus, there has been demand for a refrigeration cycle device that can keep a durability of the evaporating pressure adjusting valve even though the low-pressure charging port is positioned downstream of the evaporating pressure adjusting valve. 
     It is objective of the present disclosure to provide a refrigeration cycle device that has a high flexibility in positioning of a charging port without impairing a durability of an evaporating pressure adjusting valve. 
     According to one aspect of the present disclosure, a refrigeration cycle device includes a compressor, a heater, an inside evaporator, an outside evaporator, a first refrigerant passage, a first decompressor, a second refrigerant passage, a second decompressor, an evaporating pressure adjusting valve, a third refrigerant passage, an opening-closing member, a charging port, and a pressure change buffer. The compressor compresses and discharges a refrigerant. The heater heats a heat-exchange target fluid using the refrigerant, as a heat source, discharged from the compressor. The outside evaporator exchanges heat between an outside air and the refrigerant flowing out of the heater. The inside evaporator exchanges heat between the refrigerant flowing out of the outside evaporator and the heat-exchange target fluid. The refrigerant flowing out of the heater is guided toward an inlet of the outside evaporator through the first refrigerant passage. The first decompressor is disposed in the first refrigerant passage and configured to vary an opening area of the first refrigerant passage. The refrigerant flowing out of the outside evaporator flows through the inside evaporator toward a suction inlet of the compressor through the second refrigerant passage. The second decompressor is disposed in the second refrigerant passage between the outside evaporator and the inside evaporator and configured to vary an opening area of the second refrigerant passage. The evaporating pressure adjusting valve is disposed in the second refrigerant passage at a position downstream of the inside evaporator and configured to adjust an evaporating pressure of the refrigerant in the inside evaporator. The third refrigerant passage has an end fluidly connected to a portion of the second refrigerant passage between the evaporating pressure adjusting valve and the compressor. The refrigerant flowing out of the outside evaporator is guided toward the suction inlet of the compressor through the third refrigerant passage. The charging port through which the refrigerant is supplied is disposed in the second refrigerant passage at a position downstream of the evaporating pressure adjusting valve. The pressure change buffer is disposed in the second refrigerant passage between the evaporating pressure adjusting valve and the charging port and defines a buffer space to restrict an inner pressure in the second refrigerant passage from rapidly changing when the refrigerant is supplied through the charging port 
     The pressure change buffer can restrict the inner pressure in the second refrigerant passage, in which the evaporating pressure adjusting valve is disposed, from rapidly changing when the refrigerant is supplied to the refrigeration cycle device through the charging port. Thus, a pressure change at an outlet side of the evaporating pressure adjusting valve can be suppressed. As a result, a durability of the evaporating pressure adjusting valve can be restricted from deteriorating even though the charging port is disposed at a position downstream of the evaporating pressure adjusting valve. 
     According to the present disclosure, it is possible to flexibly select a position for the charging port without impairing a durability of the evaporating pressure adjusting valve. 
     Hereinafter, embodiments for implementing the present disclosure will be described with reference to drawings. In the respective embodiments, parts corresponding to matters already described in the preceding embodiments are given reference numerals identical to reference numerals of the matters already described. The same description is therefore omitted depending on circumstances. When only a part of a configuration is described in an embodiment, another preceding embodiment may be applied to the other parts of the configuration. The present disclosure is not limited to combinations of embodiments which combine parts that are explicitly described as being combinable. As long as no problem is present, the various embodiments may be partially combined with each other even if not explicitly described. 
     First Embodiment 
     An air conditioner  1  including a refrigeration cycle device  10  in a first embodiment will be described with reference to  FIG. 1 . The air conditioner  1  includes the refrigeration cycle device  10 , a heater  25 , and an inside air-conditioning unit  30 . In this embodiment, the refrigeration cycle device  10  is applied to the air conditioner  1  mounted in an electric vehicle that obtains a driving force from an electric motor for driving. The refrigeration cycle device  10  of the air conditioner  1  cools and heats a ventilation air conveyed to a vehicle cabin that is an air-conditioning target space. A heat-exchange target fluid in this embodiment is the ventilation air. 
     The refrigeration cycle device  10  is configured to switch the refrigerant circuit between a heating mode, a cooling mode, a serial dehumidification heating mode, and a parallel dehumidification heating mode. 
     The heating mode of the air conditioner  1  is an operating mode in which a ventilation air is heated and conveyed to the vehicle cabin that is the air-conditioning target space. The serial dehumidification heating mode and the parallel dehumidification heating mode are operating modes in which the ventilation air having been cooled and dehumidified is heated and conveyed into the vehicle cabin that is the air-conditioning target space. The cooling mode is an operating mode in which the ventilation air is cooled and conveyed to the vehicle cabin that is the air-conditioning target space. 
     In  FIG. 1 , a flow of a refrigerant in the refrigerant circuit of the heating mode is indicated by black arrows and a flow of the refrigerant in the refrigerant circuit of the parallel dehumidification heating mode is indicated by arrows with diagonal hatching. A flow of the refrigerant in the refrigerant circuit of the serial dehumidification heating mode and the cooling mode are indicated by white arrows. 
     The refrigeration cycle device  10  uses a hydrofluorocarbon type refrigerant (i.e., HFC type refrigerant and specifically, R134a) as a refrigerant and constitutes a vapor compression type subcritical refrigerant cycle in which a pressure of a high pressure side refrigerant Pd does not exceed a critical pressure of the refrigerant. However, a hydrofluoroolefin type refrigerant (i.e., HFO type refrigerant) such as R1234yf may be used as the refrigerant. In addition, the refrigerant contains a refrigerant oil to lubricate a compressor  11  and a part of the refrigerant oil circulates through the cycle together with the refrigerant. 
     The refrigeration cycle device  10  includes the compressor  11 , a condenser  12 , a first decompression valve  15   a  (a first decompressor), a second decompression valve  15   b  (a second decompressor), an outside evaporator  16 , a non-return valve  17 , an inside evaporator  18 , an evaporating pressure adjusting valve  19 , an accumulator  20  (a pressure change buffer), a first opening-closing valve  21  (an opening-closing member), a second opening-closing valve  22 , a low-pressure charging port  23 , and a high-pressure charging port  24 . 
     The compressor  11  sucks, compresses, and discharges the refrigerant in the refrigeration cycle device  10 . The compressor  11  is disposed in an engine compartment of the vehicle. The compressor  11  is configured as an electric compressor in which a fixed-displacement type compression mechanism is driven by an electric motor. The fixed-displacement type compression mechanism has a fixed discharging capacity and may apply various types of compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism. 
     The operation of the electric motor such as a rotational speed is controlled by control signals outputted from an air conditioning controller. The electric motor may be an alternate current motor or direct current motor. The air conditioning controller controls the rotational speed of the electric motor to alter a refrigerant discharging capacity of the compression mechanism. 
     A discharge outlet of the compressor  11  is fluidly connected to a refrigerant inlet of the condenser  12 . The condenser  12  is a heat exchanger for heating a cooling water through heat exchange between the high-temperature and high-pressure refrigerant discharged from the compressor  11  and the cooling water flowing through the heater  25  that is a heat-exchange target fluid. The high-pressure refrigerant is condensed when a heat of the high-pressure refrigerant is released to the cooling water. 
     The heater  25  includes the condenser  12 , a cooling water circulating circuit  26 , a heater core  27 , and a cooling water pump  28 . The heater  25  heats the ventilation air that is a heat-exchange target fluid using the high-pressure refrigerant, as a heat source, discharged from the compressor  11 . 
     The cooling water flowing through the cooling water circulating circuit  26  may be a liquid including at least ethylene glycol, dimethylpolysiloxane, or nano-fluid, or the cooling water may be an antifreeze. 
     The cooling water circulating circuit  26  is an annular passage through which the cooling water circulates between the condenser  12  and the heater core  27 . The condenser  12 , the heater core  27 , and the cooling water pump  28  are arranged in this order in the cooling water circulating circuit  26 . 
     The cooling water pump  28  circulates the cooling water through the cooling water circulating circuit  26  by drawing and discharging the cooling water toward the condenser  12 . The cooling water pump  28  is an electric pump and corresponds to a flow adjuster for the cooling water that adjusts a flow rate of the cooling water circulating through the cooling water circulating circuit  26 . 
     The heater core  27  is disposed in a casing  31 , as will be described later. The heater core  27  heats the ventilation air through heat exchange between the cooling water heated at the condenser  12  and the ventilation air that is a heat-exchange target fluid. The condenser  12  heats the ventilation air through the heater core  27 . 
     A refrigerant outlet of the condenser  12  is fluidly connected to one of three openings of a first three-way joint  13   a.  Such three-way joint may be formed by joining multiple pipes or by defining multiple refrigerant passages at a metal block or a resin block. The refrigeration cycle device  10  further includes second to fourth three-way joints  13   b  to  13   d  as described later. Basic structures of the second to fourth three-way joints  13   b  to  13   d  are similar to that of the first three-way joint  13   a.    
     Each of these three-way joints serves as a branching portion or joining portion. For example, the first three-way joint  13   a  in the parallel dehumidification heating mode uses one of the three openings as an inlet and the other two of the three openings as outlets. Accordingly, the first three-way joint  13   a  in the parallel dehumidification heating mode serves as a branching portion that divides a flow of the refrigerant flowing from the one inlet into two flows toward the two outlets. 
     The fourth three-way joint  13   d  in the parallel dehumidification heating mode uses two of the three openings as inlets and the other one of the three openings as an outlet. Accordingly, the fourth three-way joint  13   d  in the parallel dehumidification heating mode serves as a joining portion that joins refrigerants flowing into the fourth three-way joint  13   d  through the two inlets and discharges the joined refrigerant through the one outlet. 
     Another opening of the three openings of the first three-way joint  13   a  is fluidly connected to a first refrigerant passage  14   a.  The refrigerant flowing out of the condenser  12  is guided toward a refrigerant inlet of the outside evaporator  16  through the first refrigerant passage  14   a.  The other opening of the three openings of the first three-way joint  13   a  is fluidly connected to a fourth refrigerant passage  14   d,  and the refrigerant flowing out of the condenser  12  is guided toward an inlet of the second decompression valve  15   b  (specifically, one of openings of the third three-way joint  13   c ) through the fourth refrigerant passage  14   d.  The second decompression valve  15   b  is disposed in a second refrigerant passage  14   b  as described later. 
     The first decompression valve  15   a  is disposed in the first refrigerant passage  14   a.  The first decompression valve  15   a  can vary an opening area of the first refrigerant passage  14   a  and corresponds to the first decompressor that decompresses the refrigerant flowing out of the condenser  12  at least in the heating mode. The first decompression valve  15   a  is a variable throttle mechanism including a valve body configured to vary a throttle degree and an electric actuator including a stepper motor configured to control the throttle degree of the valve body. 
     The first decompression valve  15   a  is configured as a variable throttle mechanism with a full opening function in which the first decompression valve  15   a  serves as a refrigerant passage without decompressing the refrigerant by fully opening the valve body. An operation of the first decompression valve  15   a  is controlled by control signals (control pulse) outputted from the air conditioning controller. 
     An outlet of the first decompression valve  15   a  is fluidly connected to the refrigerant inlet of the outside evaporator  16 . The outside evaporator  16  exchanges heat between the refrigerant flowing out of the first decompression valve  15   a  (i.e., out of the condenser  12 ) and an outside air blown by a blowing fan (not shown). The outside evaporator  16  is disposed at a vehicle front side of the engine compartment. The blowing fan is an electric blower whose rotational speed (i.e., a blower performance) is controlled by a control voltage outputted from the air conditioning controller. 
     A refrigerant outlet of the outside evaporator  16  is fluidly connected to the second refrigerant passage  14   b.  The second refrigerant passage  14   b  is a passage through which the refrigerant flowing out of the outside evaporator  16  flows through the inside evaporator  18  and is guided toward a suction inlet of the compressor  11 . The second three-way joint  13   b,  the non-return valve  17 , the third three-way joint  13   c,  the second decompression valve  15   b,  the inside evaporator  18 , the evaporating pressure adjusting valve  19 , the fourth three-way joint  13   d,  the accumulator  20 , and the low-pressure charging port  23  are disposed in the second refrigerant passage  14   b  in this order along a flow direction of the refrigerant. An end of the second refrigerant passage  14   b  is fluidly connected to the suction inlet of the compressor  11 . 
     An opening of the second three-way joint  13   b  is fluidly connected to the third refrigerant passage  14   c  through which the refrigerant flowing out of the outside evaporator  16  is guided toward an inlet of the accumulator  20 , as will be described later (specifically, the refrigerant is guided to one of the openings of the fourth three-way joint  13   d ). The third three-way joint  13   c  is fluidly connected to the fourth refrigerant passage  14   d  as described above. 
     The non-return valve  17  allows the refrigerant to flow only from the second three-way joint  13   b  (i.e., from the outside evaporator  16 ) toward the inside evaporator  18 . 
     The second decompression valve  15   b  is disposed in the second refrigerant passage  14   b  between the outside evaporator  16  and the inside evaporator  18 . In this embodiment, the second decompression valve  15   b  is disposed in the second refrigerant passage  14   b  between the third three-way joint  13   c  and the inside evaporator  18 . The second decompression valve  15   b  is configured to vary an opening area of the second refrigerant passage  14   b  and corresponds to the second decompressor that decompresses the refrigerant flowing out of the outside evaporator  16  into the inside evaporator  18 . A basic structure of the second decompression valve  15   b  is the same as that of the first decompression valve  15   a.  Additionally, the second decompression valve  15   b  in this embodiment is configured as a variable throttle mechanism with a full-closing function in which the second refrigerant passage  14   b  is completely closed when a throttle of the valve is fully closed. 
     Accordingly, the refrigeration cycle device  10  in this embodiment can switch the refrigeration circuit by controlling the second decompression valve  15   b  to close the second refrigerant passage  14   b.  In other words, the second decompression valve  15   b  serves not only as a refrigerant decompressor but also as a refrigerant circuit switching device to switch a refrigerant circuit of the refrigerant circulating through the cycle. 
     In the cooling, the serial dehumidification heating, and the parallel dehumidification heating modes, the inside evaporator  18  serves as a heat exchanger for cooling that exchanges heat between the refrigerant flowing out of the second decompression valve  15   b  (i.e., out of the outside evaporator  16 ) and the ventilation air (i.e., a heat-exchange target fluid) before passing through the heater core  27 . The inside evaporator  18  cools the ventilation air by an endothermic action of evaporating the refrigerant decompressed by the second decompression valve  15   b.  The inside evaporator  18  is disposed at a position upstream of the heater core  27  in a flow direction of the ventilation air in the casing  31  of the inside air-conditioning unit  30 . 
     The refrigerant passage  14   b  is fluidly connected, at a position downstream of the inside evaporator  18  in the flow direction of the refrigerant, to an inlet of the evaporating pressure adjusting valve  19 . The evaporating pressure adjusting valve  19  adjusts an evaporating pressure Pe of the refrigerant in the inside evaporator  18  to be equal to or greater than a frost restricting pressure Ape so as to restrict a frost from generating on the inside evaporator  18 . In other words, the evaporating pressure adjusting valve  19  adjusts an evaporating temperature Te of the refrigerant in the inside evaporator  18  to be equal to or greater than a frost restricting temperature Ate. 
     In this embodiment, R134a is used as a refrigerant and the frost restricting temperature Ate is set to have a value slightly higher than 0° C. Accordingly, the frost restricting pressure APe is set to have a value slightly higher than 0.293 MPa that is a saturated pressure of R134a at 0° C. 
     The second refrigerant passage  14   b  at a position downstream of the evaporating pressure adjusting valve  19  is fluidly connected to the fourth three-way joint  13   d.  The fourth three-way joint  13   d  is fluidly connected to the third refrigerant passage  14   c  as described above. That is, the third refrigerant passage  14   c  has an end connected to the fourth three-way joint  13   d  that is a joining portion disposed in the second refrigerant passage  14   b  between the evaporating pressure adjusting valve  19  and the compressor  11 . 
     The other opening of the fourth three-way joint  13   d  is fluidly connected to an inlet of the accumulator  20 . That is, the accumulator  20  is disposed in the second refrigerant passage  14   b  between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . In this embodiment, the accumulator  20  is disposed at a position downstream of the fourth three-way joint  13   d  that is the joining portion of the third refrigerant passage  14   c  and the second refrigerant passage  14   b.    
     The accumulator  20  defines a buffer space  20   a  therein. The accumulator  20  is a gas-liquid separator that separates the refrigerant flowing therein into a gas-phase and a liquid-phase and reserves an excess amount of the refrigerant in the cycle in the buffer space  20   a.  The buffer space  20   a  of the accumulator  20  serves as a reservoir to reserve the excess amount of the refrigerant in the cycle. 
     The buffer space  20   a  of the accumulator  20  increases the capacity of a passage between the low-pressure charging port  23  and the evaporating pressure adjusting valve  19  as compared when the buffer space  20   a  is not formed. Thus, the buffer space  20   a  of the accumulator  20  serves as a pressure change buffer to restrict an inner pressure in the second refrigerant passage  14   b  from rapidly changing when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 . 
     The accumulator  20  has a gas-phase refrigerant outlet fluidly connected to the suction inlet of the compressor  11 . Accordingly, the accumulator  20  restricts the compressor  11  from sucking the liquid-phase refrigerant and prevents a liquid compression in the compressor  11 . 
     The first opening-closing valve  21  is disposed in the third refrigerant passage  14   c  that fluidly connects the second three-way joint  13   b  and the fourth three-way joint  13   d.  The first opening-closing valve  21  is an electromagnetic valve as a refrigerant circuit switching device that switches a refrigerant circuit, through which the refrigerant circulates, by selectively opening and closing the third refrigerant passage  14   c.  The first opening-closing valve  21  is an opening-closing member whose operation is controlled by control signals outputted from the air conditioning controller. 
     The second opening-closing valve  22  is disposed in the fourth refrigerant passage  14   d  that fluidly connects the first three-way joint  13   a  and the third three-way joint  13   c.  The second opening-closing valve  22  is an electromagnetic valve as a refrigerant circuit switching device that switches a refrigerant circuit, through which the refrigerant circulates, by selectively opening and closing the fourth refrigerant passage  14   d.  A basic structure of the second opening-closing valve  22  is the same as that of the first opening-closing valve  21 . 
     The low-pressure charging port  23  is located in the second refrigerant passage  14   b  at a position downstream of the evaporating pressure adjusting valve  19 . In this embodiment, the low-pressure charging port  23  is located in the second refrigerant passage  14   b  between the accumulator  20  and the compressor  11 . The low-pressure charging port  23  is used to supply the refrigerant into the refrigeration cycle device  10  while operating the compressor  11  after the vehicle (i.e., the refrigeration cycle device  10 ) is shipped. 
     The high-pressure charging port  24  is located in the first refrigerant passage  14   a  at a position downstream of the condenser  12 . In this embodiment, the high-pressure charging port  24  is located in the first refrigerant passage  14   a  between the first three-way joint  13   a  and the first decompression valve  15   a.  The high-pressure charging port  24  is used to supply the refrigerant into the refrigerant cycle device  10  before the vehicle (i.e., the refrigeration cycle device  10 ) is shipped. 
     Next, the inside air-conditioning unit  30  will be described. The inside air-conditioning unit  30  conveys the ventilation air temperature-adjusted by the refrigeration cycle device  10  into the vehicle cabin that is an air-conditioning target space. The inside air-conditioning unit  30  is disposed in an instrument panel that defines the most front side of the vehicle cabin. The inside air conditioning unit  30  includes a blower  32 , the inside evaporator  18 , and the heater core  27  in the casing  31  constituting an outer frame thereof. 
     The casing  31  is an air passage forming portion that defines a passage of the ventilation air conveyed to the vehicle cabin that is an air-conditioning target space. The casing  31  is made of resin such as polypropylene having a certain degree of an elasticity and great strength. An inside outside air switching device  33  is located at the most upstream side in the casing in the flow of the ventilation air. The inside outside air switching device  33 , as an inside outside switching portion, switches air introduced into the casing between an inside air (i.e., air inside the air-conditioning target space) and an outside air (i.e., air outside the air-conditioning target space). 
     The blower  32  is located at a position downstream of the inside outside air switching device  33  in the flow direction of the ventilation air. The blower  32  blows an air drawn through the inside outside air switching device  33  toward the air-conditioning target space. The blower  32  is an electric blower that drives a centrifugal multi blades fan (i.e., sirocco fan) by an electric motor. The rotational speed (i.e., a flow rate) of the blower  32  is controlled by a control voltage outputted from the air conditioning controller. 
     The inside evaporator  18  is disposed in the air passage defined by the casing  31  at a position downstream of the blower  32  in the flow direction of the ventilation air. A space downstream of the inside evaporator  18  in the air passage defined by the casing  31  is divided into two spaces so that an inside condenser passage  35  and a cooling air bypass passage  36  are formed in parallel with each other. 
     The heater core  27  is disposed in the inside condenser passage  35 . That is, the inside condenser passage  35  is a passage through which the ventilation air flows to exchange its heat with the refrigerant at the heater core  27 . The inside evaporator  18  and the heater core  27  are arranged in this order in the flow direction of the ventilation air. In other words, the inside evaporator  18  is located upstream of the heater core  27  in the flow direction of the ventilation air. 
     The cooling air bypass passage  36  is a passage through which the ventilation air that has passed through the inside evaporator  18  flows while bypassing the heater core  27 . 
     An air mix door  34  is disposed at a position downstream of the inside evaporator  18  and upstream of the heater core  27  in the flow direction of the ventilation air. The air mix door  34  is a flow ratio adjuster that adjusts an amount of the ventilation air passing through the heater core  27  that has passed through the inside evaporator  18  based on control signals outputted from the air conditioning controller. 
     A mixing passage  37  is defined in the casing  31  at a position downstream of the inside condenser passage  35  and the cooling air bypass passage  36 . The ventilation air heated at the heater core  27  is mixed with the ventilation air flowing through the cooling air bypass passage  36  without being heated at the heater core  27  in the mixing passage  37 . 
     Multiple openings are defined at the most downstream side of the casing  31  in the flow direction of the ventilation air. The ventilation air (i.e., conditioned air) mixed at the mixing passage  37  is conveyed toward the vehicle cabin through the multiple openings. 
     The air mix door  34  adjusts the ratio of an amount of air passing through the heater core  27  and an amount of air flowing through the cooling air bypass passage  36 , and therefore a temperature of the conditioned air mixed in the mixing passage  37  is adjusted. As a result, a temperature of the conditioned air conveyed into the vehicle cabin that is an air-conditioning target space is adjusted. 
     That is, the air mix door  34  serves as a temperature adjuster that adjusts a temperature of the conditioned air blown into the vehicle cabin that is an air-conditioning target space. The air mix door  34  is driven by an electric actuator for the air mix door  34 . The operation of the electric actuator is controlled by control signals outputted from the air conditioning controller. 
     The air mix door  34  causes the ventilation air to flow through the inside evaporator  18  and the heater core  27  in this order during the heating mode, the serial dehumidification heating mode, and the parallel dehumidification heating mode. The air mix door  34  causes the ventilation air to flow through the inside evaporator  18  and bypass the heater core  27  during the cooling mode. The air mix door  34  serves as an air passage switching device. 
     Next, an operation of the air conditioner  1  in this embodiment will be described. The air conditioner  1  in this embodiment can switch the operating mode between the heating mode, the cooling mode, the serial dehumidification heating mode, and the parallel dehumidification heating mode. These operating modes are selectively switched by executing air-conditioning control programs stored in the air conditioning controller in advance. 
     (a) Heating Mode 
     In the heating mode, the air conditioning controller opens the first opening-closing valve  21 , closes the second opening-closing valve  22 , controls the first decompression valve  15   a  to serve as a decompressor by reducing a throttle of the first decompression valve  15   a,  and fully closes the second decompression valve  15   b.    
     In the heating mode, as shown by the black arrows in  FIG. 1 , the refrigeration cycle device  10  constitutes the vapor compression type refrigeration cycle through which the refrigerant circulates through the compressor  11 , the condenser  12 , the first decompression valve  15   a,  the outside evaporator  16 , the first opening-closing valve  21 , the accumulator  20 , and the compressor  11  again in this order. 
     In this cycle, the air conditioning controller appropriately controls operations of air conditioning devices connected to an output portion of the air conditioning controller. The air conditioning controller determines control signals outputted to the electric actuator for the air mix door  34  such that the air mix door  34  completely closes the cooling air bypass passage  36 . That is, the control signals are determined such that all of the ventilation air that has passed through the inside evaporator  18  flows through the air passage in which the heater core  27  is disposed. 
     Accordingly, in the refrigeration cycle device  10  in the heating mode, the high-pressure refrigerant discharged from the compressor  11  flows into the condenser  12 . The refrigerant flowing through the condenser  12  exchanges heat with the cooling water flowing through the cooling water circulating circuit  26  and releases the heat. As a result, the cooling water flowing through the cooling water circulating circuit  26  is heated. The ventilation air that has been blown by the blower  32  and passed through the inside evaporator  18  is heated at the heater core  27  because the air mix door  34  opens the air passage in which the heater core  27  is disposed. 
     The refrigerant flowing out of the condenser  12  flows through the first three-way joint  13   a  toward the first refrigerant passage  14   a  because the second opening-closing valve  22  is closed. The refrigerant flowing through the first refrigerant passage  14   a  is decompressed to be a low-pressure refrigerant by the first decompression valve  15   a.  The low-pressure refrigerant decompressed by the first decompression valve  15   a  flows into the outside evaporator  16  and absorbs heat from an outside air blown by the blowing fan. 
     The refrigerant flowing out of the outside evaporator  16  flows through the second three-way joint  13   b  toward the third refrigerant passage  14   c  because the first opening-closing valve  21  is opened and the second decompression valve  15   b  is completely closed. The refrigerant flowing through the third refrigerant passage  14   c  flows through the fourth three-way joint  13   d  into the accumulator  20  and is separated into a gas-phase and a liquid-phase. The gas-phase refrigerant separated in the accumulator  20  is sucked by the compressor  11  through the suction inlet and compressed again by the compressor  11 . 
     Accordingly, in the heating mode, the ventilation air heated at the heater core  27  through the condenser  12  is blown into the vehicle cabin that is an air-conditioning target space to perform an air-heating in the vehicle cabin. 
     (b) Cooling Mode 
     In the cooling mode, the air conditioning controller closes the first opening-closing valve  21  and the second opening-closing valve  22 , fully opens the first decompression valve  15   a,  and reduces the throttle of the second decompression valve  15   b.    
     In the cooling mode, as shown by white arrows in  FIG. 1 , the refrigeration cycle device  10  constitutes a vapor compression type refrigeration cycle through which the refrigerant circulates through the compressor  11 , the condenser  12 , the first decompression valve  15   a,  the outside evaporator  16 , the non-return valve  17 , the second decompression valve  15   b,  the inside evaporator  18 , the evaporating pressure adjusting valve  19 , the accumulator  20 , and the compressor  11  again in this order. 
     In this cycle, the air conditioning controller appropriately controls the air conditioning devices connected to the output portion of the air conditioning controller. The control signals outputted to the electric actuator for the air mix door  34  from the air conditioning controller are set such that the air mix door  34  fully opens the cooling air bypass passage  36 . Thus, all amount of the ventilation air that has passed through the inside evaporator  18  flows through the cooling air bypass passage  36 . 
     Accordingly, in the refrigeration cycle device  10  in the cooling mode, the high-pressure refrigerant discharged from the compressor  11  flows into the condenser  12 . At this time, the air mix door  34  completely closes the air passage in which the heater core  27  is disposed, thus the cooling water flowing through the heater core  27  rarely exchanges heat with the ventilation air and flows out of the heater core  27 . 
     The refrigerant flowing out of the condenser  12  flows through the first three-way joint  13   a  toward the first refrigerant passage  14   a  because the second opening-closing valve  22  is closed. The refrigerant flowing through the first refrigerant passage  14   a  flows into the first decompression valve  15   a.  At this moment, the refrigerant flowing out of the condenser  12  is not decompressed by the first decompression valve  15   a  and flows into the outside evaporator  16  because the first decompression valve  15   a  is fully opened. 
     The refrigerant flowing through the outside evaporator  16  releases heat to the outside air blown by the blowing fan at the outside evaporator  16 . The refrigerant flowing out of the outside evaporator  16  flows through the second three-way valve  13   b  toward the second refrigerant passage  14   b  because the first opening-closing valve  21  is closed. The refrigerant flowing through the second refrigerant passage  14   b  is decompressed to be a low-pressure refrigerant by the second decompression valve  15   b.    
     The low-pressure refrigerant decompressed by the second decompression valve  15   b  flows into the inside evaporator  18  and evaporates by absorbing heat from the ventilation air blown by the blower  32 . Thus, the ventilation air is cooled. The refrigerant flowing out of the inside evaporator  18  flows through the evaporating pressure adjusting valve  19  into the accumulator  20  and is separated into a gas-phase and a liquid-phase in the accumulator  20 . The gas-phase refrigerant separated at the accumulator  20  is sucked by the compressor  11  through the suction inlet and compressed by the compressor  11  again. 
     Accordingly, in the cooling mode, the ventilation air cooled at the inside evaporator  18  is blown into the vehicle cabin that is an air-conditioning target space, thereby performing an air-cooling in the vehicle cabin. 
     (c) Serial Dehumidification Heating Mode 
     In the serial dehumidification heating mode, the air conditioning controller closes the first opening-closing valve  21  and the second opening-closing valve  22  and reduces throttles of the first decompression valve  15   a  and the second decompression valve  15   b.  The air conditioning controller displaces the air mix door  34  such that the air passage in which the heater core  27  is disposed is fully opened and the cooling air bypass passage  36  is fully closed. 
     The refrigeration cycle device  10  in the serial dehumidification heating mode constitutes a vapor compression type refrigeration cycle, as shown by white arrows in  FIG. 1 , in which the refrigerant circulates through the compressor  11 , the condenser  12 , the first decompression valve  15   a,  the outside evaporator  16 , the non-return valve  17 , the second decompression valve  15   b,  the inside evaporator  18 , the evaporating pressure adjusting valve  19 , the accumulator  20 , and the compressor  11  again in this order. That is, the outside evaporator  16  and the inside evaporator  18  is serially connected in the flow direction of the refrigerant. 
     The refrigeration cycle device  10  in the serial dehumidification heating mode constitutes a refrigeration cycle in which the condenser  12  serves as a radiator and the inside evaporator  18  serves as an evaporator. When a saturated temperature of the refrigerant in the outside evaporator  16  is higher than an outside temperature Tam, the outside evaporator  16  serves as a radiator. When the saturated temperature of the refrigerant in the outside evaporator  16  is lower than the outside temperature Tam, the outside evaporator  16  serves as an evaporator. 
     In this cycle, the air conditioning controller appropriately controls operations of the air conditioning devices connected to the output portion of the air conditioning controller. The control signals outputted to the electric actuator for the air mix door  34  from the air conditioning controller are set such that the air mix door  34  completely closes the cooling air bypass passage  36  as with in the heating mode. That is, the control signals are determined such that all amount of the air having passed through the inside evaporator  18  flows through the air passage in which the heater core  27  is disposed. 
     Accordingly, in the serial dehumidification heating mode, the ventilation air cooled and dehumidified at the inside evaporator  18  is heated at the heater core  27  and blown into the vehicle cabin that is an air-conditioning target space. Thus, air in the vehicle cabin is dehumidified and heated. Additionally, a heating capacity of the heater core  27  for the ventilation air can be adjusted by adjusting the throttle degrees of the first decompression valve  15   a  and the second decompression valve  15   b.    
     (d) Parallel Dehumidification Heating Mode 
     In the parallel dehumidification heating mode, the air conditioning controller opens the first opening-closing valve  21  and the second opening-closing valve  22  and reduces the throttles of the first decompression valve  15   a  and the second decompression valve  15   b.    
     As shown by arrows with diagonal hatching in  FIG. 1 , the refrigeration cycle device in the parallel dehumidification heating mode constitutes a vapor compression type refrigeration cycle in which the refrigerant circulates through the compressor  11 , the condenser  12 , the first decompression valve  15   a,  the outside evaporator  16 , the first opening-closing valve  21 , the accumulator  20 , and the compressor  11 , and the refrigerant also circulates through the compressor  11 , the condenser  12 , the second opening-closing valve  22 , the second decompression valve  15   b,  the inside evaporator  18 , the evaporating pressure adjusting valve  19 , the accumulator  20 , and the compressor  11  in this order. 
     That is, in the parallel dehumidification heating mode, the flow of the refrigerant flowing out of the condenser  12  is separated into two flows at the first three-way joint  13   a.  One of the two flows of the refrigerant flows through the first decompression valve  15   a,  the outside evaporator  16 , and the compressor  11  in this order, and the other one of the two flows of the refrigerant flows through the second decompression valve  15   b,  the inside evaporator  18 , the evaporating pressure adjusting valve  19 , and the compressor in this order. 
     In this cycle, the air conditioning controller appropriately controls operations of the air conditioning devices connected to the output portion of the air conditioning controller. For example, the control signals outputted to the electric actuator for the air mix door  34  from the air conditioning controller are set such that the air mix door  34  fully closes the cooling air bypass passage  36  as with in the heating mode. That is, the control signals are determined such that the all amount of the ventilation air having passed through the inside evaporator  18  flows through the air passage in which the heater core  27  is disposed. 
     Accordingly, in the refrigeration cycle device  10  in the parallel dehumidification heating mode, the high-pressure refrigerant discharged from the compressor  11  flows into the condenser  12 . The refrigerant flowing in the condenser  12  exchanges heat with and releases heat to the cooling water. The ventilation air that has been blown by the blower  32  and passed through the inside evaporator  18  is heated by the cooling water heated by the refregerant similarly to the heating mode because the air mix door  34  opens the air passage in which the heater core  27  is disposed. As a result, the ventilation air is heated. 
     The second opening-closing valve  22  is opened, thus the flow of the refrigerant flowing out of the condenser  12  is separated into the two flows at the first three-way joint  13   a.  One of the two flows of the refrigerant separated at the first three-way joint  13   a  flows through the first refrigerant passage  14   a.  The refrigerant flowing through the first refrigerant passage  14   a  is decompressed to be a low-pressure refrigerant at the first decompression valve  15   a.  The low-pressure refrigerant decompressed by the first decompression valve  15   a  flows into the outside evaporator  16  and absorbs heat from an outside air blown by the blowing fan. 
     The other one of the two flows of the refrigerant separated at the first three-way joint  13   a  flows through the fourth refrigerant passage  14   d.  The refrigerant flowing through the fourth refrigerant passage  14   d  is restricted from flowing back toward the outside evaporator  16  by the non-return valve  17  and flows through the second opening-closing valve  22  and the third three-way joint  13   c  into the second decompression valve  15   b.    
     The refrigerant flowing through the second decompression valve  15   b  is decompressed to be a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second decompression valve  15   b  flows into the inside evaporator  18  and evaporates by absorbing heat from the ventilation air blown by the blower  32 . As a result, the ventilation air is cooled. The refrigerant flowing out of the inside evaporator  18  is decompressed by the evaporating pressure adjusting valve  19  to have a value substantially equal to the pressure of the refrigerant flowing out of the outside evaporator  16 . 
     The refrigerant flowing out of the evaporating pressure adjusting valve  19  flows through the fourth three-way joint  13   d  and merges with the refrigerant flowing out of the outside evaporator  16 . The refrigerant merging at the fourth three-way joint  13   d  flows into the accumulator  20  and is separated into a gas-phase and a liquid-phase. The gas-phase refrigerant separated at the accumulator  20  is sucked by the compressor  11  through the suction inlet and compressed again by the compressor  11 . 
     In the parallel dehumidification heating mode, the ventilation air cooled and dehumidified at the inside evaporator  18  is heated at the heater core  27  and blown into the vehicle cabin that is an air-conditioning target space. As a result, air in the vehicle cabin is dehumidified and heated. 
     In addition, in the parallel dehumidification heating mode in this embodiment, the evaporating temperature of the refrigerant in the outside evaporator  16  can be lowered than the evaporating temperature in the inside evaporator  18 . Accordingly, a temperature difference between the evaporating temperature of the refrigerant in the outside evaporator  16  and the outside air can be increased, thereby increasing an amount of air absorbed by the refrigerant at the outside evaporator  16 . 
     As a result, the heating capacity of the heater core  27  for the ventilation air can be increased compared to a refrigeration cycle device in which the evaporating temperature of the refrigerant in the outside evaporator  16  is similar to the evaporating temperature of the refrigerant in the inside evaporator  18 . 
     As described above, the refrigeration cycle device  10  in this embodiment can perform a comfortable air-heating in the vehicle cabin by selectively switching the operating mode between the heating mode, the cooling mode, the serial dehumidification heating mode, and the parallel dehumidification heating mode. 
     Next, a method to supply the refrigerant into the refrigeration cycle device  10  will be described. Before the air conditioner  1  (i.e., the refrigeration cycle device  10 ) is shipped out, the first decompression valve  15   a  and the second decompression valve  15   b  are fully opened. The refrigeration cycle device  10  is vacuumed through the high-pressure charging port  24  and the low-pressure charging port  23  while opening the first opening-closing valve  21  and the second opening-closing valve  22 . 
     The refrigeration cycle device  10  is vacuumed to remove air in the refrigeration cycle device  10 . If air is remained in the refrigeration cycle device  10 , water vapor in the air would freeze in the refrigeration cycle device  10 , which prevents the refrigerant from circulating through the refrigeration cycle device  10 . 
     After the refrigeration cycle device  10  is vacuumed, the first decompression valve  15   a  and the second decompression valve  15   b  are fully opened. The refrigerant is supplied into the refrigeration cycle device  10  through the high-pressure charging port  24  while opening the first opening-closing valve  21  and the second opening-closing valve  22 . 
     After shipping out the air conditioner  1  (i.e., the refrigeration cycle device  10 ), the first decompression valve  15   a  and the second decompression valve  15   b  are fully opened. The refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23  while opening the first opening-closing valve  21  and the second opening-closing valve  22  and operating the compressor  11 . 
     As described above, the accumulator  20  is disposed in the second refrigerant passage  14   b  between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . The accumulator  20 , which is a pressure change buffer, restricts an inner pressure in the second refrigerant passage  14   b  from rapidly changing when the refrigerant is supplied through the low-pressure charging port  23 . 
     The accumulator  20  defines the buffer space  20   a,  thereby restricting the inner pressure in the second refrigerant passage  14   b  from rapidly changing when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23  and the second refrigerant passage  14   b.  The reason why the rapid change in the inner pressure is avoided is that the air in the buffer space  20   a  is compressed. Thus, it is possible to suppress a pressure change at an outlet side of the evaporating pressure adjusting valve  19 . In addition, even though the low-pressure charging port  23  is disposed at a position downstream of the evaporating pressure adjusting valve  19 , a durability of the evaporating pressure adjusting valve  19  is restricted from being impaired. 
     The refrigeration cycle device  10  in this embodiment can improve a flexibility of positions at which the charging port is mounted without impairing the durability of the evaporating pressure adjusting valve. 
     The buffer space  20   a  is defined by the accumulator  20  that is a reservoir to reserve an excess amount of the refrigerant. The buffer space  20   a  of the accumulator  20  that has been already installed as a reservoir in the refrigeration cycle device  10  is used as a pressure change buffer, thus an additional pressure change buffer is not needed. Therefore, a cost and a size of the refrigeration cycle device  10  are not increased. The refrigeration cycle device  10  that keeps the durability of the evaporating pressure adjusting valve  19  can be provided even though the low-pressure charging port  23  is located at a position downstream of the evaporating pressure adjusting valve  19 . 
     Second Embodiment 
     Hereinafter, a refrigeration cycle device  10  in a second embodiment will be described with reference to  FIG. 2  mainly at points different from the refrigeration cycle device  10  in the first embodiment. In the refrigeration cycle device  10  in the second embodiment, a muffler  51  is disposed in the second refrigerant passage  14   b  between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . In this embodiment, the muffler  51  is disposed in the second refrigerant passage  14   b  between the accumulator  20  and the low-pressure charging port  23 . 
     The muffler  51  defines a buffer space  51   a  that reduces a pressure pulsation generated when the compressor  11  discharges the refrigerant. The buffer space  51   a  also serves as a pressure change buffer that restricts the inner pressure in the second refrigerant passage  14   b  from changing when the refrigerant is supplied into the second refrigerant passage  14   b  through the low-pressure charging port  23 . 
     The buffer space  51   a  of the muffler  51  increases the capacity of a passage through which the refrigerant flows between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . Thus, air in the buffer space  51   a  is compressed when the refrigerant is supplied into the second refrigerant passage  14   b  through the low-pressure charging port  23 , thereby further restricting the inner pressure in the second refrigerant passage  14   b  from rapidly increasing. Thus, the pressure of the second refrigerant passage  14   b  at a position downstream of the evaporating pressure adjusting valve  19  is further restricted from changing. 
     As described above, the buffer space  51   a  is configured with the muffler  51  that reduces the pressure pulsation generated when the compressor  11  discharges the refrigerant. The refrigeration cycle device  10  including the muffler  51  does not need an additional member as a pressure change buffer. Thus, the refrigeration cycle device  10  can keep the durability of the evaporating pressure adjusting valve  19  without increasing a cost and a size of the refrigeration cycle device  10  even though the low-pressure charging port  23  is disposed at a position downstream of the evaporating pressure adjusting valve  19 . The pressure in the second refrigerant passage  14   b  at a position downstream of the evaporating pressure adjusting valve  19  is further restricted from changing when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 . 
     Third Embodiment 
     A refrigeration cycle device  10  in a third embodiment will be described with reference to  FIG. 3  mainly at different points from the first embodiment. The refrigeration cycle device  10  in the third embodiment includes a buffer space  52 , as a pressure change buffer, defined in a portion of the second refrigerant passage  14   b  between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . In this embodiment, the buffer space  52  is defined in a portion of the second refrigerant passage  14   b  between the accumulator  20  and the low-pressure charging port  23 . 
     The buffer space  52  is defined by repeatedly bending a pipe. The buffer space  52  increases a length of a passage through which the refrigerant flows between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23  and increases the capacity of the passage through which the refrigerant flows. 
     The buffer space  52  may be defined by branching multiple pipes and joining these multiple pipes to increase the capacity of the passage through which the refrigerant flows. 
     The buffer space  52  increases the capacity of the passage through which the refrigerant flows between the evaporating pressure adjusting valve  19  and the low-pressure charging port  23 . When the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23  and the second refrigerant passage  14   b,  air in the buffer space  52  is compressed. Thus, the inner pressure in the second refrigerant passage  14   b  is further restricted from rapidly changing. As a result, a pressure in the second refrigerant passage  14   b  downstream of the evaporating pressure adjusting valve  19  is further restricted from changing. 
     As described above, the buffer space  52  is defined by the pipe. Accordingly, a structure to restrict a pressure at the outlet side of the evaporating pressure adjusting valve  19  from changing can be achieved at a low cost. 
     The present disclosure is not limited to the embodiments described above, and can be variously modified in a range without departing from a gist of the present disclosure. 
     In the above embodiments, the refrigeration cycle device  10  in the present disclosure is applied to the vehicle, but the refrigeration cycle device  10  is not limited to a device for a vehicle and may be applied to a stationary refrigeration cycle device. 
     Components of the refrigeration cycle device  10  are not limited to those described in the embodiments. In the embodiments, the compressor  11  is an electric compressor, but not limited to this. When the compressor  11  is used for an engine for vehicle driving, the compressor  11  may be an engine driven compressor that is driven by a rotational driving force transmitted by the engine through a pulley and a belt. 
     Means disclosed in the above embodiments can be combined with each other in a practical range. For example, the air conditioner may be configured by combining the refrigeration cycle device  10  in the second embodiment and the refrigeration cycle device  10  in the third embodiment. 
     The low-pressure charging port  23  may include a throttle such as an orifice to further restrict a pressure at a position downstream of the evaporating pressure adjusting valve  19  from changing when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 . 
     A method to supply the refrigerant into the refrigeration cycle device  10  after the air conditioner  1  (i.e., the refrigeration cycle device  10 ) is shipped out is not limited to the method described above. Hereinafter, another method will be described. 
     At first, a predetermined amount of the refrigerant is supplied into the refrigeration cycle device  10  through the high-pressure charging port  24  while fully opening the first decompression valve  15   a  and the second decompression valve  15   b  and opening the first opening-closing valve  21  and the second opening-closing valve  22 . 
     Next, the refrigerant is further supplied into the refrigeration cycle device  10  through the low-pressure charging port  23  while completely closing the high-pressure charging port  24  and operating the compressor  11 . 
     After the predetermined amount of the refrigerant is supplied into the refrigeration cycle device  10  through the high-pressure charging port  24  as described above, the refrigerant is further supplied through the low-pressure charging port  23 . 
     In this case, when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 , the predetermined amount of the refrigerant has been already supplied into the refrigeration cycle device  10 . Accordingly, a pressure difference between the refrigerant supplied into the refrigeration cycle device  10  through the low-pressure charging port  23  and the refrigerant in the refrigeration cycle device  10  can be decreased. Thus, a counter pressure is not likely to act on the evaporating pressure adjusting valve  19  while the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 . 
     Therefore, a pressure at the outlet side of the evaporating pressure adjusting valve  19  is further restricted from rapidly changing when the refrigerant is supplied into the refrigeration cycle device  10  through the low-pressure charging port  23 . 
     The predetermined amount of the refrigerant supplied into the refrigeration cycle device  10  through the high-pressure charging port  24  is predetermined such that the pressure at a position downstream of the evaporating pressure adjusting valve  19  is restricted from rapidly changing when the refrigerant is supplied into the second refrigerant passage  14   b  through the low-pressure charging port  23 . 
     Although the present disclosure has been described in accordance with the examples, it is understood that the disclosure is not limited to such examples or structures. The present disclosure encompasses various modifications and variations within the scope of equivalents. In addition, it should be understood that various combinations or aspects, or other combinations or aspects, in which only one element, one or more elements, or one or less elements are added to the various combinations or aspects, also fall within the scope or technical idea of the present disclosure.