JP7330482B2 - heat pump system - Google Patents

Description

TECHNICAL FIELD The present invention relates to a heat pump system used for automobile air conditioning with ultra-low temperature specifications capable of coping with extremely low outside air temperatures.

Since cooling and heating for internal combustion engine vehicles can depend on exhaust heat, defrosters (hereinafter referred to as "dehumidifying heating") are used to ensure visibility by removing condensation that occurs along with heating, that is, fogging on the inner surface of the windshield. ) can also be constructed relatively easily. This is because it was easy to secure warm air by using waste heat during operation.

Air conditioners for vehicles that use only the internal combustion engine for driving power rely on a compressor that is driven by a belt attached to the engine for cooling, and exhaust heat is used for heating. Therefore, when the function is switched from cooling to heating to dehumidifying and heating, it is not necessary to reverse the direction of the refrigerant gas flowing through the refrigerant circuit. It was done.

In recent years, the drive system of passenger cars has changed from internal combustion engines to electric vehicles (EV), fuel cell vehicles (FCV), and the like. In the case of such a vehicle type, that is, a vehicle with a drive system in which the internal combustion engine is not always activated during operation, it is a natural trend to change the entire vehicle auxiliary system, including air conditioning, to an electric system.

In line with this trend, automobile air conditioner compressors that are driven by an electric motor instead of being driven by a belt have become quite popular. An electric vehicle (EV) includes a plug-in hybrid car, ie, a PHV (Plug-in Hybrid Vehicle) or a PHEV (Plug-in Hybrid Electric Vehicle). A PHEV is a hybrid car whose battery can be charged directly from an outlet using a plug.

In addition to the above-mentioned automobile air conditioners used for electric vehicles (EV), fuel cell vehicles (FCV), etc., in general residential cooling and heating air conditioners using a reversible heat pump cycle, switching between cooling and heating functions In this case, it is necessary to reverse the direction in which the refrigerant gas such as freon (hereinafter also simply referred to as "refrigerant") flows through the refrigerant circuit. On the other hand, a compressor for compressing a refrigerant and flowing it through a refrigerant circuit generally has a constant input/output direction. In other words, the general compressor cannot reverse the suction port and the discharge port. Therefore, in order to reverse the direction of the refrigerant gas flowing through the refrigerant circuit, it is necessary to switch the piping of the refrigerant circuit with a four-way valve.

On the other hand, in the case of an electric vehicle (EV), a fuel cell vehicle (FCV), etc., it is difficult to adopt heating by using exhaust heat because it is uncertain. In addition, a defroster (dehumidifying heating) is indispensable for automobile air conditioners, although it is unnecessary for residential air conditioners. This defroster has a condenser that generates low temperature for dehumidification and condensation, and a dehumidification valve that are placed in the immediate vicinity of the condenser that generates heat for indoor heating, and are activated by throttling the dehumidification valve.

Therefore, in addition to four-way valves and dehumidifying valves, air conditioners such as electric vehicles (EV) and fuel cell vehicles (FCV) include solenoid valves for switching them, piping to them (hereinafter referred to as "four-way valve peripheral part ) becomes considerably more complicated. Furthermore, a control function for controlling a large number of solenoid valves is also required.

In addition, since the air conditioner is considerably bulky and heavy even if it is not for a vehicle with a traction motor, there is a demand for a smaller size, lighter weight, and thinner thickness for a vehicle. In addition to this reduction in size, weight, and thickness, there is also a demand for excellent assembly workability, improved productivity, and reduced manufacturing costs. In order to meet such demands, the following techniques have been disclosed.

2. Description of the Related Art There is known a piping unit (hereinafter also simply referred to as a "piping unit") of a heat pump type refrigerator in which a refrigerant control member is integrally piped in advance (for example, Patent Literature 1). That is, the refrigerant control members of the refrigerating cycle (refrigerant circuit) in the heat pump type refrigerator (heat pump device) are preliminarily piped into a unit, and piping parts and piping welding points are reduced, resulting in excellent assembly workability and productivity. In addition to reducing the manufacturing cost by improving the performance, the size and thickness of the outdoor unit are reduced.

In the piping unit described in Patent Document 1, two side plates, which are bulged at places suitable for a predetermined refrigerant passage, are joined together to form a substrate, and the bulging portions of both side plates are attached to the substrate. A refrigerant passage is formed, a refrigerant control member is integrally attached to the substrate by piping in the refrigerant passage, and a pipe port connected to the refrigerating cycle is provided in the refrigerant passage.

JP-A-7-198229

However, the piping unit described in Patent Document 1 is not for vehicle use. Furthermore, when the outside air is extremely cold, sufficient heating and dehumidifying heating functions cannot be obtained.

The present invention has been made in view of such problems, and a heat pump system in which refrigerant control members are preliminarily piped together to form a unit, realizing cost performance through compactness, and particularly capable of sufficiently coping with extremely low temperatures. intended to provide

A heat pump system according to an aspect of the present invention is a heat pump system used for automotive air conditioning with cryogenic specifications, and includes two pairs of four refrigerant paths each corresponding to function switching between cooling, heating, and dehumidification. A four-way switching valve unit that can be freely switched to a path, a gas injection unit provided with a plurality of metal plates and a proportional control valve that are stacked in an airtight manner, and a liquid separation unit that separates the liquid, and are stacked in an airtight manner. A cooling/heating control unit for switching between cooling, heating and dehumidifying functions, a condenser for condensing a refrigerant, an evaporator for expanding the refrigerant, and a compressor for compressing the refrigerant. and, during heating and dehumidification heating, the four-way switching valve unit causes the refrigerant to flow from the cooling/heating control unit to the liquid separation unit and from the compressor to flow to the condenser; During cooling, the refrigerant flows from the condenser and flows out to the liquid separation unit, and flows from the compressor and flows out to the cooling/heating control unit. At times, it flows from the condenser and flows out to the compressor and the cooling/heating control unit through the proportional control valve, and flows out to the evaporator during dehumidification and heating, and flows from the evaporator to the condenser during cooling. The liquid separation unit flows the refrigerant from the four-way switching valve unit and flows out to the compressor during heating, dehumidifying heating, and cooling. The gas flows in from the gas injection unit and flows out to the four-way switching valve unit during heating and dehumidifying heating, and flows in from the four-way switching valve unit and flows out to the gas injection unit during cooling.

At this time, in one aspect of the present invention, the four-way switching valve unit and the liquid separation unit are integrated, and the pipe end of the compressor is configured such that the refrigerant is supplied to the gas injection unit and the liquid through the proportional control valve. It is composed of two pipe terminals that flow in from the separation unit and one pipe terminal that flows out to the four-way switching valve unit, and the gas injection unit injects the refrigerant from the condenser during heating and dehumidifying heating. The air may flow in and flow out to the compressor and the cooling/heating control unit by the proportional control valve, flow out to the evaporator during the dehumidification heating , and flow from the evaporator to the condenser during cooling .

At this time, in one aspect of the present invention, the four-way switching valve unit and the liquid separation unit are integrated, and the pipe end of the compressor is one pipe end into which the refrigerant flows from the liquid separation unit. and one pipe end that flows out to the four-way switching valve unit, the gas injection unit injects the refrigerant into the gas phase pipe end provided in the liquid separation unit, and the liquid separation unit is The refrigerant may flow through the gas injection unit to the cooling/heating control unit during heating and to the evaporator during dehumidifying and heating .

At this time, in one aspect of the present invention, the four-way switching valve unit and the liquid separation unit are separated, and the refrigerant flows from the gas injection unit and the liquid separation unit to the piping terminal of the compressor. and one pipe terminal flowing out to the four-way switching valve unit.

At this time, in one aspect of the present invention, the four-way switching valve unit includes a first connection port through which the refrigerant flows in and out, a cylinder to which the refrigerant is supplied from the first connection port, and a cylinder in the cylinder. a spool formed in a chevron shape that is movable in the axial direction of the cylindrical body so that two connection modes can be selected; and a second connection port through which the refrigerant flows in and out through the spool, A protrusion may be provided on the top surface of the spool, and a recess for receiving the protrusion may be provided on the inner surface of the cylindrical body.

At this time, in one aspect of the present invention, the spool may include a metal spool head formed in a chevron shape and a Teflon (registered trademark) pedestal for fixing the spool head.

At this time, in one aspect of the present invention, the second connection port is provided with a plurality of laminated metal plates, and the metal plates are composed of a lower plate, an intermediate plate and an upper plate, and the refrigerant can flow. The holes may be formed in the lower plate, the intermediate plate, and the upper plate so that the diameters of the holes are larger than the diameter of the second connection port.

At this time, in one aspect of the present invention, two or more metal plates are laminated on top of the plurality of airtightly laminated metal plates constituting the gas injection unit and the cooling/heating control unit. A segmented pedestal or integrally molded segmented pedestal may also be provided.

At this time, in one aspect of the present invention, a vertical check valve is further provided, and the check valve includes an outer cylinder, an inner cylinder provided inside the outer cylinder, and a bottom part of the inner cylinder. It may have a valve for allowing the refrigerant to flow in and not to flow out, and a port provided on the side surface of the inner cylinder for allowing the refrigerant to flow out.

At this time, in one aspect of the present invention, one or more of a heating expansion valve, a dehumidifying expansion valve, and a cooling expansion valve are further provided, and the heating expansion valve, the dehumidifying expansion valve, and the cooling expansion valve are provided. comprises a main body, a support provided in the main body, a magnet and a pulse motor fixed to the support and adapted to vertically move the support to adjust the flow rate of the refrigerant, and fixed to the main body. and a slicer, and an upper stopper and a lower stopper for preventing excessive vertical movement of the column, and the column may be formed with a groove for attaching the upper stopper and the lower stopper.

According to the present invention, it is possible to provide a heat pump system in which the refrigerant control member is preliminarily preliminarily piped into a unit, realizing cost performance due to compactness, and particularly capable of sufficiently coping with extremely low temperatures.

1 is a schematic diagram of a heat pump system according to an embodiment of the present invention, and is a schematic diagram of the heat pump system when a four-way switching valve unit and a liquid separation unit are combined; FIG. 1 is a schematic diagram of a heat pump system according to an embodiment of the present invention, and is a schematic diagram of the heat pump system when a four-way switching valve unit and a liquid separation unit are separated; FIG. FIG. 2 is an explanatory diagram of a refrigerant circuit during heating of type A of the heat pump system according to one embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating and dehumidification of type A of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during cooling of the A type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating of the B type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating and dehumidification of type B of the heat pump system according to the embodiment of the present invention; FIG. 2 is an explanatory diagram of a refrigerant circuit during cooling of type B of the heat pump system according to one embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating of the C type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating and dehumidification of the C type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during cooling of the C type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during heating of the D type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during dehumidification and heating of the D type of the heat pump system according to the embodiment of the present invention; FIG. 4 is an explanatory diagram of the refrigerant circuit during cooling of the D type of the heat pump system according to the embodiment of the present invention; 1 is a perspective view of a gas injection unit used in a heat pump system according to one embodiment of the present invention; FIG. 16(A) is a plan view of the metal plate and FIG. 16(B) is a cross-sectional view of the metal plate taken along line AA of the metal plate; FIG. , and FIG. 16C is a cross-sectional view taken along the line BB. FIG. 17A is a schematic view of an upper plate that constitutes a plurality of laminated metal plates provided in the gas injection unit, FIG. 17A is a plan view of the upper plate, and FIG. 17B is a side view of the upper plate; It is a diagram. FIG. 18A is a schematic diagram of a first intermediate plate that constitutes a plurality of laminated metal plates provided in the gas injection unit, FIG. 18A is a plan view of the first intermediate plate, and FIG. is a side view of the first intermediate plate; FIG. 19B is a schematic diagram of a second intermediate plate that constitutes a plurality of stacked metal plates provided in the gas injection unit, FIG. 19A being a plan view of the second intermediate plate; FIG. is a side view of the second intermediate plate; 20(A) is a plan view of the lower plate, and FIG. 20(B) is a side view of the lower plate; FIG. It is a diagram. 1 is a perspective view of a cooling/heating control unit used in a heat pump system according to one embodiment of the present invention; FIG. 22(A) is a plan view of the metal plate and FIG. 22(B) is a cross-sectional view of the metal plate taken along the line C--C. FIG. , and FIG. 22(C) is a sectional view taken along line DD. FIG. 23A is a perspective view of a four-way switching valve unit used in a heat pump system according to an embodiment of the present invention, and FIG. 23A is a four-way switching valve used when the four-way switching valve unit and a liquid separation unit are combined; FIG. 23(B) is a perspective view of the unit, and FIG. 23(B) is a perspective view of a plurality of laminated metal plates provided at the bottom of the four-way switching valve unit, and is a view from the bottom of FIG. 23(A). ) is a perspective view of a four-way switching valve unit used when the four-way switching valve unit and the liquid separation unit are separated, and shows a metal plate further laminated under the four-way switching valve unit. 24(A) is a perspective view of the cylinder, FIG. 24(B) is a side cross-sectional view of the cylinder, and FIG. FIG. 24B is a cross-sectional view taken along line AA of FIG. 24B; 25(A) is a schematic view of a four-way switching valve unit, FIG. 25(A) is a view from the bottom of FIG. 23(A), and FIG. 25(B) is a cross-sectional view taken along line AA of FIG. 25(A). FIG. 4 is a cross-sectional view of a proportional control valve provided in the gas injection unit; FIG. 4 is a cross-sectional view of a check valve; 3A and 3B are sectional views of a heating expansion valve, a dehumidifying expansion valve, and a cooling expansion valve; FIG.

A heat pump system 100 according to an embodiment of the present invention will be described below with reference to the drawings. A heat pump system 100 according to an embodiment of the present invention is a heat pump system used for automotive air conditioning with cryogenic specifications. As shown in FIG. 1, the heat pump system 100 includes a four-way switching valve unit 10 that can switch four refrigerant paths into two pairs of paths in accordance with function switching among cooling, heating, and dehumidification. a gas injection unit 20 provided with a plurality of airtightly stacked metal plates 25 and a proportional control valve 22; a liquid separation unit 30 for separating liquid; and a plurality of airtightly stacked metal plates. 45 is provided, a cooling and heating control unit 40 that switches functions between cooling, heating and dehumidification, a condenser 50 that condenses the refrigerant or an evaporator 60 that expands the refrigerant, a compressor 70 that compresses the refrigerant, Prepare.

According to the heat pump system 100 according to one embodiment of the present invention, as will be described later, the refrigerant control member is preliminarily piped to form a unit, and cost performance can be realized through compactness. Further, by means of the proportional control valve 22 provided in the gas injection unit 20, the medium-temperature medium-pressure refrigerant is further compressed by the compressor and sent to the condenser 50 to obtain hot air of even higher temperature. It will be possible to respond sufficiently. It is explained below.

In FIG. 1, the dashed arrow indicates the direction of refrigerant flow during heating, the dashed circle indicates the direction of refrigerant flow during dehumidification and heating, and the actual arrow indicates the direction of refrigerant flow during cooling. . The direction of flow of the refrigerant differs during heating, dehumidifying heating, and cooling. The same applies to FIG. 2 to be described later.

The flow of refrigerant from the four-way switching valve unit 10, the gas injection unit 20, the liquid separation unit 30, and the cooling/heating control unit 40 provided in the heat pump system 100 according to one embodiment of the present invention is controlled during heating, dehumidifying heating, and cooling. I will explain each.

In the four-way switching valve unit 10, during heating or dehumidifying heating, the refrigerant flows from the cooling/heating control unit 40, flows out to the liquid separation unit 30, flows from the compressor 70, and flows through the four-way switching valve unit 10 to the condenser. During cooling, the liquid flows from the condenser 50, flows through the four-way switching valve unit 10, flows out to the liquid separation unit 30, flows from the compressor 70, and flows out to the cooling/heating control unit 40.

In the gas injection unit 20, during heating or dehumidifying heating, the refrigerant flows from the condenser 50 and flows out to the compressor 70 and/or the cooling/heating control unit 40 or the evaporator 60 through the proportional control valve 22. . During cooling, the air flows from the evaporator 60 and flows out to the condenser 50 .

In the liquid separation unit 30, the refrigerant flows from the four-way switching valve unit 10 and flows out to the compressor 70 during heating, dehumidifying heating, and cooling.

In the cooling/heating control unit 40, the refrigerant flows from the gas injection unit 20 and flows out to the four-way switching valve unit 10 during heating or dehumidifying heating. During cooling, the gas flows from the four-way switching valve unit 10 and flows out to the gas injection unit 20 .

The four-way switching valve unit 10, the gas injection unit 20, the liquid separation unit 30, and the cooling/heating control unit 40 are provided with pipe ends. Refrigerant flows into and out of each device through the above piping terminals. By providing a manifold, it can also be unitized and made compact. 1 and 2, the gas injection unit 20 is preferably provided with a heating expansion valve 26, a dehumidifying expansion valve 23, a first check valve 24, and a second check valve 27, Used according to the refrigerant circuit during heating, dehumidifying heating, or cooling. Similarly, the cooling/heating control unit 40 is preferably provided with a check valve 41, a cooling expansion valve 42, and a battery expansion valve 43, which are used according to the refrigerant circuit during heating, dehumidifying heating, or cooling. They are connected through piping terminals and the refrigerant flows.

1 and 2, a heating expansion valve 26, a dehumidification expansion valve 23, a first check valve 24, a second check valve 27, a check valve 41, a cooling expansion valve 42, a battery The expansion valve 43 is a segmented pedestal formed by stacking two or more metal plates on top of the plurality of metal plates 25 and 45 that are stacked in an airtight manner and constitute the gas injection unit 20 and the cooling/heating control unit 40. 28, 48. In addition, the division pedestals 28 and 48, which are formed by laminating two or more metal plates, are also laminated so as to be airtight. The structure of the division pedestals 28, 48 will be described later.

The heat pump system 100 according to one embodiment of the present invention can be roughly classified into four A, B, C, and D types. Each type will be described later with reference to FIGS. 3-14, which are refrigerant circuit explanatory diagrams.

The A type is a heat pump system in which the four-way switching valve unit 10 and the liquid separation unit 30 as shown in FIG. 1 are combined. The piping terminals of the compressor 70 are composed of two piping terminals that flow in from the gas injection unit 20 and the liquid separation unit 30 through the proportional control valve 22 and one piping terminal that flows out to the four-way switching valve unit 10. , the pipe terminal of the compressor 70 has three ports. Also, the gas injection unit 20 is characterized in that the refrigerant flows in from the condenser 50 and flows out to the compressor 70 and the cooling/heating control unit 40 or the evaporator 60 through the proportional control valve 22 .

The B type is also a heat pump system in which the four-way switching valve unit 10 and the liquid separation unit 30 as shown in FIG. It is different from the A type in that it consists of one pipe terminal and one pipe terminal that flows out to the four-way switching valve unit 10, that is, the compressor 70 has two pipe terminals. In addition, the gas injection unit 20 causes the refrigerant to flow into the gas phase piping terminal provided in the liquid separation unit 30, and the liquid separation unit 30 sends the refrigerant through the gas injection unit 20 to the cooling/heating control unit 40 or the evaporator 60. Characterized by outflow.

The C type is a heat pump system in which the four-way switching valve unit 10 and the liquid separation unit 30 are separated as shown in FIG. The pipe terminals of the compressor 70 are composed of two pipe terminals into which the refrigerant flows from the gas injection unit 20 and the liquid separation unit 30 and one pipe terminal into which the refrigerant flows out to the four-way switching valve unit 10. The piping terminals of machine 70 are three-way. Further, the piping terminals of the compressor 70 are composed of two piping terminals into which the refrigerant flows from the gas injection unit 20 and the liquid separation unit 30 and one piping terminal into which the refrigerant flows out to the four-way switching valve unit 10. Characterized by

The D type is also a heat pump system in which the four-way switching valve unit 10 and the liquid separation unit 30 are separated as shown in FIG. In the D type, instead of using the cooling/heating control unit 40, the four-way switching valve unit 10 further includes a check valve and a cooling expansion valve (not shown in FIG. 1) to form a refrigerant circuit. A refrigerant circuit is mentioned later. The piping terminal of the compressor 70 is composed of one piping terminal into which the refrigerant flows from the liquid separation unit 30 and one piping terminal into which the refrigerant flows out to the four-way switching valve unit 10. is two mouths. Further, the gas injection unit 20 is characterized in that the refrigerant flows into the gas-phase pipe end provided in the liquid separation unit 30 .

Next, with reference to refrigerant circuit explanatory diagrams, the refrigerant circuits of types A, B, C, and D during heating, dehumidifying heating, and cooling will be described in order.

First, the A type refrigerant circuit will be described. FIG. 3 is an explanatory diagram of the refrigerant circuit during heating of type A of the heat pump system 100 according to one embodiment of the present invention. A solid line indicates a circuit through which the refrigerant passes, and a dashed line indicates a circuit through which the refrigerant does not pass. A solid line or a dashed line is used because the refrigerant circuits that flow during heating, dehumidifying heating, and cooling are different. The arrows indicate the direction of coolant flow. These also apply to the refrigerant circuit diagrams shown in FIGS. 4-14. Also, in the refrigerant circuit of the heating circuit in FIG. The pressure is high (as will be described later, the refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). Medium temperature and medium pressure are present from the outlet of the proportional control valve 22 to the compressor 70 . On the other hand, the refrigerant on the path from the heating expansion valve 26 of the gas injection unit 20 to the cooling/heating control unit 40, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 becomes low temperature and low pressure. In addition, the compressor 70 has three pipe ends.

As described above, in the A type, the four-way switching valve unit 10 and the liquid separation unit 30 are combined. By being united, it is possible to shorten the coolant flow path and reduce the piping resistance. In addition, cost can be reduced by reducing the number of suction pipes between the four-way switching valve unit 10 and the liquid separation unit 30, and space can also be saved by reducing the number of pipes.

As shown in FIG. 3 , the four-way switching valve unit 10 allows the refrigerant to flow from the cooling/heating control unit 40 through the outdoor condenser 110 and out to the liquid separation unit 30 . The four-way switching valve unit 10 also receives refrigerant from the compressor 70 and flows out to the condenser 50 .

The four-way switching valve unit 10 can distinguishably connect the four refrigerant paths U, V, W, and X into two pairs of paths. In addition, it is possible to freely switch between two types of connection forms UV and WX or WU and XV. For example, in the first embodiment, the coolant path U and the coolant path V are communicated, and the coolant path W and the coolant path X are communicated, as shown in FIG. 3 and the like. On the other hand, in the second embodiment, the coolant path W and the coolant path U are communicated as shown in FIG. 5 and the like, and the coolant path X and the coolant path V are communicated. The details of the structure of the four-way switching valve unit 10 will be described later.

The gas injection unit 20 receives refrigerant from the condenser 50 and does not all flow out to the heating/cooling control unit 40, and allows a portion of the refrigerant to flow through the proportional control valve 22 to the compressor 70 and at the same time a portion of the refrigerant. It flows out to the cooling/heating control unit 40 . The path from the compressor 70 through the four-way switching valve unit 10, the condenser 50, the gas injection unit 20, and back to the compressor 70 is high-temperature and high-pressure refrigerant. Instead, it is expanded to medium temperature and medium pressure by the proportional control valve 22 provided in the gas injection unit 20 and enters the compressor 70 again. The amount of refrigerant that has been made to flow out increases, the path from the compressor 70 to the four-way switching valve unit 10 and the condenser 50 becomes a higher temperature and pressure refrigerant, and the capacity of the condenser 50 increases. Therefore, by blowing the refrigerant to the condenser 50 by the air blower 120, hot air with a higher temperature can be obtained, and it is possible to cope particularly with very low temperatures.

Also, the proportional control valve 22 provided in the gas injection unit 20 adjusts the amount of refrigerant flowing out to the compressor 70 or the cooling/heating control unit 40 according to the temperature setting in the vehicle. For example, to increase the temperature inside the vehicle, the amount of refrigerant sent from the gas injection unit 20 to the compressor 70 should be increased, and to decrease the temperature, the amount of refrigerant sent to the compressor 70 should be reduced. good.

The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 . Cooling/heating control unit 40 receives refrigerant from gas injection unit 20 and flows out to four-way switching valve unit 10 through outdoor condenser 110 . The gas injection unit 20 and cooling/heating control unit 40 of the A type heating circuit, dehumidifying heating circuit, and cooling circuit are independent. Note that the liquid separation unit 30 is a unit provided with a function of separating gas and liquid, and has functions such as refrigerant recovery.

The gas injection unit 20 is provided with a dehumidifying expansion valve 23, a first check valve 24, a second check valve 27, and a heating expansion valve 26, and the cooling/heating control unit 40 is provided with a check valve 41 and a cooling expansion valve. It is preferable to provide a valve 42 and a battery expansion valve 43 to switch between heating, dehumidifying heating, and cooling. B, C and D types are the same.

FIG. 4 is an explanatory diagram of the refrigerant circuit during dehumidification and heating of the heat pump system 100 according to the embodiment of the present invention. In the refrigerant circuit of the dehumidifying and heating circuit in FIG. 4, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the expansion valve 23 for dehumidification has a high temperature and a high pressure. (The refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). Medium temperature and medium pressure are present from the outlet of the proportional control valve 22 to the compressor 70 . On the other hand, the refrigerant on the route from the dehumidifying expansion valve 23 of the gas injection unit 20 to the compressor 70 through the evaporator 60, the cooling/heating control unit 40, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 is low-temperature and low-pressure. Become.

The four-way switching valve unit 10 receives the refrigerant from the cooling/heating control unit 40 through the outdoor condenser 110 and flows out to the liquid separation unit 30 . The four-way switching valve unit 10 also receives refrigerant from the compressor 70 and flows out to the condenser 50 .

Gas injection unit 20 receives refrigerant from condenser 50 and out to compressor 70 via proportional control valve 22 . At the same time, it flows out to the cooling/heating control unit 40 through the evaporator 60 . In this way, the proportional control valve 22 provided in the gas injection unit 20 expands the refrigerant to medium temperature and medium pressure and enters the compressor 70 again. The outflow amount of the high-pressure refrigerant increases, and the path from the compressor 70 to the four-way switching valve unit 10 and the condenser 50 becomes a high-temperature and high-pressure refrigerant, and the capacity of the condenser 50 increases. On the other hand, the low-temperature refrigerant expanded by the dehumidifying expansion valve 23 flows into the (indoor) evaporator 60, and can quickly dehumidify the glass windows in the vehicle.

The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 . Cooling/heating control unit 40 receives refrigerant from gas injection unit 20 and flows out to four-way switching valve unit 10 through outdoor condenser 110 .

FIG. 5 is an explanatory diagram of the refrigerant circuit during cooling of type A of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the cooling circuit in FIG. 5, the refrigerant in the route from the compressor 70 to the four-way switching valve unit 10, the outdoor condenser 110, and the cooling/heating control unit 40 is at high temperature and high pressure. On the other hand, the refrigerant in the path from the cooling/heating control unit 40 through the evaporator 60, the gas injection unit 20, the condenser 50, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 has a low temperature and a low pressure.

The four-way switching valve unit 10 receives refrigerant from the condenser 50 and flows out to the liquid separation unit 30 . Also, the air flows in from the compressor 70 and flows out to the cooling/heating control unit 40 through the outdoor condenser 110 .

Gas injection unit 20 receives refrigerant from evaporator 60 and out to condenser 50 .

In the cooling/heating control unit 40 , the refrigerant flows from the four-way switching valve unit 10 through the outdoor condenser 110 and flows out to the gas injection unit 20 . Alternatively, a battery inverter cooler 130 may be provided as shown in FIG. By doing so, the cooling function is further improved.

In the case of the cooling circuit, the high-temperature and high-pressure refrigerant circuit from the outdoor condenser 110 is compact and improves workability by integrating the cooling expansion valve 42 and the battery expansion valve 43 provided in the cooling and heating control unit 40. can be made

Next, a B-type refrigerant circuit will be described. FIG. 6 is an explanatory diagram of the refrigerant circuit during heating of type B of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the heating circuit in FIG. 6, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the heating expansion valve 26 has a high temperature and high pressure ( The refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). From the outlet of the proportional control valve 22 through the liquid separation unit 30 to the compressor 70, medium temperature and medium pressure are present. On the other hand, the refrigerant on the path from the heating expansion valve 26 of the gas injection unit 20 to the cooling/heating control unit 40, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 becomes low temperature and low pressure.

In the heating circuit, the high temperature and high pressure refrigerant from the condenser 50 is expanded to medium temperature by the proportional control valve 22 and 100% wet gas flows into the liquid separation unit 30 . The gas (refrigerant) that has flowed in has a high specific gravity, and flows into the condenser 50 from the gas phase separated into two phases in the liquid separation unit 30 .

The refrigerant in the route shown in FIG. Therefore, a higher temperature and pressure refrigerant can be obtained. At this time, the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, and the proportional expansion valve 22 of the gas injection unit 20 becomes high temperature and high pressure (liquefaction). On the other hand, the refrigerant expanded by the proportional expansion valve 22 to medium temperature and medium pressure flows into the liquid separation unit 30 . The medium-temperature/medium-pressure refrigerant that has flowed into the liquid separation unit 30 is separated into a gas phase and a liquid phase due to the difference in specific gravity within the liquid separation unit 30. Since it flows into 70, the capacity of the condenser 50 is improved. On the other hand, the refrigerant (liquefied) in the liquid phase portion of the liquid separation unit 30 flows into the heating expansion valve 26 , expands again, and flows into the cooling/heating control unit 40 .

When medium-temperature and medium-pressure refrigerant is sent from the condenser 50 to the gas phase side of the liquid separation unit 30, the liquid separation unit 30 is not flowed vertically (directly below), but is directed against the wall surface of the liquid separation unit 30. It is preferable to provide internal piping. When the refrigerant is applied to the wall surface of the liquid separation unit 30, it is preferable to provide a socket for bending the refrigerant in a right angle direction at the portion of the liquid separation unit 30 where the refrigerant is sent to the gas phase side. In this way, since the refrigerant is prevented from being blown directly into the liquid phase within the liquid separation unit 30, the homing phenomenon (foaming) within the liquid separation unit 30 can be prevented.

The four-way switching valve unit 10 receives the refrigerant from the cooling/heating control unit 40 through the outdoor condenser 110 and flows out to the liquid separation unit 30 . Also, the air flows in from the compressor 70 and flows out to the condenser 50 .

The gas injection unit 20 receives refrigerant from the condenser 50 and out through the liquid separation unit 30 by the proportional control valve 22 to the compressor 70 and/or the heating expansion valve 26 to the cooling control unit 40 .

The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 . In addition, the medium-temperature medium-pressure refrigerant in the lower layer of the liquid separation unit 30 is re-expanded by the heating expansion valve 26 provided in the gas injection unit 20, passes through the check valve 41 provided in the cooling/heating control unit 40, and The refrigerant flows out to the liquid separation unit 30 through the condenser 110 .

Cooling/heating control unit 40 receives refrigerant from gas injection unit 20 and flows out to four-way switching valve unit 10 through outdoor condenser 110 . The gas injection unit 20 and cooling/heating control unit 40 of the B type heating circuit, dehumidifying heating circuit, and cooling circuit are independent.

FIG. 7 is an explanatory diagram of the refrigerant circuit during dehumidification and heating of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the dehumidifying and heating circuit in FIG. Refrigerant in the path to enter has a higher temperature and pressure). The refrigerant from the outlet of the dehumidifying expansion valve 23 of the proportional control valve 22 through the liquid separation unit 30 to the inlet of the dehumidifying expansion valve 23 of the gas injection unit 20 has medium temperature and medium pressure. On the other hand, the refrigerant from the outlet of the dehumidification expansion valve 23 of the gas injection unit 20 to the evaporator 60 and the cooling/heating control unit 40 becomes low temperature and low pressure.

In the B-type refrigerant circuit during dehumidification and heating, the gas injection unit 20 causes the refrigerant to flow in from the condenser 50 and flow out to the compressor 70 and/or the evaporator 60 through the proportional control valve 22, which is different from the refrigerant circuit during heating. different. Other points are the same as those of the B type refrigerant circuit during heating.

FIG. 8 is an explanatory diagram of the refrigerant circuit during cooling of the B type of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the cooling circuit in FIG. 8, the refrigerant in the route from the compressor 70 to the four-way switching valve unit 10, the outdoor condenser 110, and the cooling/heating control unit 40 is at high temperature and high pressure. On the other hand, the refrigerant in the path from the cooling/heating control unit 40 through the evaporator 60, the gas injection unit 20, the condenser 50, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 has a low temperature and a low pressure.

In the four-way switching valve unit 10, the refrigerant flows from the condenser 50 to the liquid separation unit 30, flows from the compressor 70, and flows to the cooling/heating control unit 40 through the outdoor condenser 110. FIG.

The gas injection unit 20 flows in from the evaporator 60 and out to the condenser 50 . The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 . The cooling/heating control unit 40 flows from the four-way switching valve unit 10 through the outdoor condenser 110 and flows out to the gas injection unit 20 .

Next, a C-type refrigerant circuit will be described. FIG. 9 is an explanatory diagram of the refrigerant circuit during heating of the C type of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the heating circuit in FIG. 9, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the heating expansion valve 26 has a high temperature and a high pressure ( The refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). Medium temperature and medium pressure are present from the outlet of the proportional control valve 22 to the compressor 70 . On the other hand, the refrigerant on the path from the heating expansion valve 26 of the gas injection unit 20 to the cooling/heating control unit 40, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 becomes low temperature and low pressure.

9 does not enter the heating/cooling control unit 40 from the condenser 50, but passes through the proportional control valve 22 and enters the compressor 70 again, resulting in a higher temperature and pressure refrigerant.

The four-way switching valve unit 10 receives the refrigerant from the cooling/heating control unit 40 through the outdoor condenser 110 and flows out to the liquid separation unit 30 . Also, the air flows in from the compressor 70 and flows out to the condenser 50 .

Gas injection unit 20 receives refrigerant from condenser 50 and out through proportional control valve 22 to compressor 70 and/or heating expansion valve 26 to cooling control unit 40 .

The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 .

In the cooling/heating control unit 40 , the refrigerant flows from the gas injection unit 20 and flows out to the four-way switching valve unit 10 and the liquid separation unit 30 through the outdoor condenser 110 .

The C type has a structure in which the four-way switching valve unit 10 and the liquid separation unit 30 are separated. The pipe terminals of the compressor 70 are composed of two pipe terminals into which the refrigerant flows from the gas injection unit 20 and the liquid separation unit 30 and one pipe terminal into which the refrigerant flows out to the four-way switching valve unit 10 . The gas injection unit 20 and cooling/heating control unit 40 of the C type heating circuit, dehumidifying heating circuit, and cooling circuit are independent.

FIG. 10 is an explanatory diagram of the refrigerant circuit during heating and dehumidification of type C of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the dehumidifying and heating circuit in FIG. 10, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the dehumidifying expansion valve 23 is at a high temperature. High pressure (the refrigerant in the path from the compressor 70 to the condenser 50 is at a higher temperature and pressure). Medium temperature and medium pressure are present from the outlet of the proportional control valve 22 to the compressor 70 . On the other hand, the refrigerant on the route from the dehumidifying expansion valve 23 of the gas injection unit 20 to the compressor 70 through the evaporator 60, the cooling/heating control unit 40, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 is low-temperature and low-pressure. Become.

In the C-type refrigerant circuit during dehumidification and heating, the gas injection unit 20 causes the refrigerant to flow in from the condenser 50 and flow out to the compressor 70 and/or the evaporator 60 through the proportional control valve 22, which is different from the refrigerant circuit during heating. different. Other points are the same as those of the C-type refrigerant circuit during heating.

FIG. 11 is an explanatory diagram of the refrigerant circuit during cooling of the C type of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the cooling circuit in FIG. 11, the refrigerant in the route from the compressor 70 to the four-way switching valve unit 10, the outdoor condenser 110, and the cooling/heating control unit 40 is at high temperature and high pressure. On the other hand, the refrigerant in the path from the cooling/heating control unit 40 through the evaporator 60, the gas injection unit 20, the condenser 50, the four-way switching valve unit 10, and the liquid separation unit 30 and entering the compressor 70 has a low temperature and a low pressure.

In the four-way switching valve unit 10, the refrigerant flows from the condenser 50 to the liquid separation unit 30, flows from the compressor 70, and flows to the cooling/heating control unit 40 through the outdoor condenser 110. FIG.

The gas injection unit 20 flows in from the evaporator 60 and out to the condenser 50 . The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 . The cooling/heating control unit 40 flows from the four-way switching valve unit 10 through the outdoor condenser 110 and flows out to the gas injection unit 20 .

Next, a D-type refrigerant circuit will be described. FIG. 12 is an explanatory diagram of the refrigerant circuit during heating of the D type of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the heating circuit in FIG. 12, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the heating expansion valve 26 has a high temperature and high pressure ( The refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). From the outlet of the proportional control valve 22 through the liquid separation unit 30 to the compressor 70, medium temperature and medium pressure are present. Moreover, it is preferable to provide a third check valve 31 in the path from the liquid separation unit 30 and the heating expansion valve 26 of the gas injection unit 20 . On the other hand, the refrigerant on the path from the heating expansion valve 26 of the gas injection unit 20 to the compressor 70 through the check valve 41, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 becomes low temperature and low pressure.

In the four-way switching valve unit 10 , the refrigerant flows from the gas injection unit 20 through the check valve 41 and the outdoor condenser 110 and flows out to the liquid separation unit 30 . Also, the air flows in from the compressor 70 and flows out to the condenser 50 .

In the gas injection unit 20, the refrigerant flows from the condenser 50 and flows through the liquid separation unit 30 through the proportional control valve 22, the compressor 70 and/or the heating expansion valve 26 through the check valve 41, and the outdoor condenser 110 through the four-way switching valve unit. Drain to 10.

In the D type, the cooling/heating control unit 40 is not used, and the four-way switching valve unit 10 is further provided with a check valve 41 and a cooling expansion valve 42 . When the battery inverter cooler 130 is used, it is preferable to further include the battery expansion valve 43 . The piping terminals of the compressor are composed of one piping terminal into which the refrigerant flows from the liquid separation unit 30 and one piping terminal into which the refrigerant flows out to the four-way switching valve unit 10 . Further, the gas injection unit 20 is characterized in that the refrigerant flows into the gas-phase pipe end provided in the liquid separation unit 30 . Also, in the D type, the four-way switching valve unit 10 and the liquid separation unit 30 are separated. The gas injection units 20 of the D-type heating circuit, dehumidifying heating circuit, and cooling circuit are independent.

FIG. 13 is an explanatory diagram of the refrigerant circuit during dehumidification and heating of the heat pump system 100 according to the embodiment of the present invention. In the refrigerant circuit of the dehumidifying and heating circuit in FIG. 13, the refrigerant in the path from the compressor 70 to the four-way switching valve unit 10, the condenser 50, the inlet of the proportional control valve 22 of the gas injection unit 20, and the expansion valve 23 for dehumidification has a high temperature and a high pressure. (The refrigerant in the path from the compressor 70 to the condenser 50 has a higher temperature and pressure). From the outlet of the proportional control valve 22 through the liquid separation unit 30 to the compressor 70, medium temperature and medium pressure are present. Further, it is preferable to provide a third check valve 31 in the path from the liquid separation unit 30 and gas injection unit 20 to the expansion valve 23 for dehumidification. On the other hand, the refrigerant on the path from the dehumidification expansion valve 23 of the gas injection unit 20 to the compressor 70 through the check valve 41, the outdoor condenser 110, the four-way switching valve unit 10, and the liquid separation unit 30 becomes low temperature and low pressure.

In the D-type refrigerant circuit for dehumidifying and heating, the gas injection unit 20 causes the refrigerant to flow in from the condenser 50 and flow out to the compressor 70 and/or the evaporator 60 through the liquid separation unit 30 by the proportional control valve 22 . Other points are the same as those of the D-type refrigerant circuit during heating.

FIG. 14 is an explanatory diagram of the refrigerant circuit during cooling of the D type of the heat pump system 100 according to one embodiment of the present invention. In the refrigerant circuit of the cooling circuit in FIG. 14, the four-way switching valve unit 10, the outdoor condenser 110, the cooling expansion valve 42 provided in the four-way switching valve unit 10, and the battery inverter cooler 130 are further provided from the compressor 70. In this case, the refrigerant in the route to the battery expansion valve 43 has a high temperature and a high pressure. On the other hand, the refrigerant on the route from the cooling expansion valve 42 provided in the four-way switching valve unit 10 to the compressor 70 through the evaporator 60, the gas injection unit 20, the condenser 50, the four-way switching valve unit 10, and the liquid separation unit 30 is Low temperature and low pressure.

In the four-way switching valve unit 10 , the refrigerant flows from the condenser 50 to the liquid separation unit 30 , flows from the compressor 70 , and flows to the cooling expansion valve 42 and the evaporator 60 through the outdoor condenser 110 .

The gas injection unit 20 flows in from the evaporator 60 and out to the condenser 50 . The liquid separation unit 30 receives refrigerant from the four-way switching valve unit 10 and flows out to the compressor 70 .

The above is the description of the schematic configuration and refrigerant circuit of the heat pump system 100 according to one embodiment of the present invention. Gas injection unit 20, cooling/heating control unit 40, four-way switching valve unit 10, proportional control valve 22, heating expansion valve 26, dehumidification expansion valve 23, and cooling, which are used in the heat pump system 100 according to one embodiment of the present invention, are described below. The configuration of the electronic expansion valve 230 such as the expansion valve 42 and the check valve will be described in detail.

FIG. 15 is a perspective view of the gas injection unit 20 used in the heat pump system 100 according to one embodiment of the invention. The gas injection unit 20 is provided with at least a plurality of metal plates 25 laminated in an airtight manner and a proportional control valve 22 . The plurality of metal plates 25 laminated in an airtight manner will be described in detail below.

16A and 16B are schematic diagrams of a plurality of stacked metal plates 25 provided in the gas injection unit 20. FIG. 16A is a plan view of the metal plates 25, and FIG. AA sectional view, and FIG. 16C is a BB sectional view. A proportional control valve 22 provided in the gas injection unit 20 is abutted on a plurality of metal plates 25 through a partition seat described below. This is for space saving. The dehumidification expansion valve 23, the check valve 24, and the heating expansion valve 26 are similarly abutted on a plurality of metal plates 25 through a sectioned pedestal, which will be described below.

The plurality of laminated metal plates 25 provided in the gas injection unit 20 are composed of at least an upper plate 251, a first intermediate plate 252, a second intermediate plate 253 and a lower plate 254 as shown in FIG. 16(C). It is The upper plate 251, the first and second intermediate plates 252 and 253, and the lower plate 254 are each provided with a hole. forming a part. Also, a check valve seat, a copper plate, a check valve top plate (not shown) for contacting the check valve, and a body for contacting the expansion valve may be provided.

Also, as shown in FIGS. 16(A), (B), and (C), it is preferable to provide a sectioning pedestal 28 . The partitioning pedestal 28 is provided on top of a plurality of airtightly laminated metal plates 25 constituting the gas injection unit 20 . The same applies to a cooling/heating control unit 40 shown in FIG. 22 which will be described later.

The partitioning pedestal 28 is configured by stacking two or more metal plates, and as shown in FIG. Constituent vent holes are formed.

The partitioning pedestal 28 serves as a pedestal for the proportional expansion valve 22, the dehumidifying expansion valve 23, the heating expansion valve 26, the cooling expansion valve 42, and the battery expansion valve 43 provided in the gas injection unit 40. Used.

By providing the partitioned pedestal 28, the control valves such as the proportional control valve 22, the dehumidifying expansion valve 23, and the heating expansion valve 26 throttle and expand the refrigerant, realizing a refrigerant compact space and improving the efficiency of passage resistance. is possible, and the occurrence of refrigerant noise can be prevented.

The number and thickness of the metal plates used for the division pedestal are not limited, and the number of metal plates may be two or more. The number of sheets and thickness may be appropriately changed according to the length of the circuit and the flow rate. On the other hand, the division pedestal may be integrally molded instead of stacking and combining a plurality of metal plates. At that time, it is molded by a Shibori press or the like.

17A and 17B are schematic diagrams of an upper plate 251 constituting a plurality of laminated metal plates 25 provided in the gas injection unit 20, FIG. ) is a side view of the upper plate 251. FIG. As shown in FIG. 17A, the upper plate 251 is formed with a through hole. Also, the thickness of the upper plate 251 is preferably 1.0 mm≦t≦2.0 mm (t is the thickness; the same shall apply hereinafter), and particularly preferably 1.5 mm.

FIG. 18 is a schematic diagram of a first intermediate plate 252 constituting a plurality of laminated metal plates 25 provided in the gas injection unit 20, and FIG. 18(A) is a plan view of the first intermediate plate 252. 18B is a side view of the first intermediate plate 252. FIG. As shown in FIG. 18(A), the first intermediate plate 252 is formed with a through hole. Also, the thickness of the first intermediate plate 252 is preferably 3.0 mm≦t≦4.0 mm, particularly preferably 3.5 mm.

FIG. 19 is a schematic diagram of a second intermediate plate 253 constituting a plurality of laminated metal plates 25 provided in the gas injection unit 20, and FIG. 19(A) is a plan view of the second intermediate plate 253. 19B is a side view of the second intermediate plate 253. FIG. As shown in FIG. 19(A), the second intermediate plate 253 is formed with a through hole. Also, the thickness of the second intermediate plate 253 is preferably 3.0 mm≦t≦4.0 mm, particularly preferably 3.5 mm.

20A and 20B are schematic diagrams of a lower plate 254 that constitutes a plurality of stacked metal plates 25 provided in the gas injection unit 20. FIG. 20A is a plan view of the lower plate 254. FIG. ) is a side view of the lower plate 254. FIG. As shown in FIG. 20(A), the lower plate 254 is formed with a through hole. Also, the thickness of the lower plate 254 is preferably 1.0 mm≦t≦2.0 mm, particularly preferably 1.5 mm.

The vent holes provided in the lower plate 254 shown in FIG. 20 are connected to the piping terminals of the gas injection unit 20, and the respective piping terminals are connected to the condenser 50, the evaporator 60, the four-way valve unit 10, the compressor 70, and the cooling/heating control. It is connected to the piping terminal of the unit 40, and the refrigerant flows. Moreover, as described above, the metal plates 25 are laminated so as to be airtight.

FIG. 21 is a perspective view of the cooling/heating control unit 40 used in the heat pump system 100 according to one embodiment of the present invention. The cooling/heating control unit 40 is provided with at least a plurality of metal plates 45 laminated in an airtight manner. A plurality of metal plates 45 laminated in an airtight manner will be described below.

22A and 22B are schematic diagrams of a plurality of laminated metal plates 45 provided in the cooling/heating control unit 40. FIG. 22A is a plan view of the metal plates 45, and FIG. CC sectional view, and FIG. 22C is a DD sectional view. When the check valve 41 , the cooling expansion valve 42 , and the battery expansion valve 43 are provided, they are in contact with a plurality of metal plates 45 . This is for space saving.

The plurality of laminated metal plates 45 provided in the cooling/heating control unit 40 are composed of at least an upper plate 451, a first intermediate plate 452, a second intermediate plate 453 and a lower plate 454 as shown in FIG. 22(C). It is The upper plate 451, the first and second intermediate plates 452 and 453, and the lower plate 454 are each provided with a hole. forming a part.

The cooling/heating control unit 40 may be provided with a check valve seat 455 and a copper plate 456 for contacting the check valve. As described above, the metal plates 45 are laminated so as to be airtight.

Next, the four-way switching valve unit 10 will be explained. FIG. 23 is a perspective view of the four-way switching valve unit 10 used in the heat pump system 100 according to one embodiment of the present invention, and FIG. FIG. 23B is a perspective view of a plurality of laminated metal plates 11 provided at the bottom of the four-way switching valve unit 10, and FIG. 23(C) is a perspective view of the four-way switching valve unit 10 used when the four-way switching valve unit 10 and the liquid separation unit 30 are separated. It is a figure provided with laminated metal plate 11'.

The A and B types described above use the four-way switching valve unit 10 shown in FIG. 23(A). In addition, a plurality of metal plates 11 laminated in an airtight manner as shown in FIG. 23B are provided in the lower portion of the unit shown in FIG. 23A. In the C and D types, a metal plate 11′ further laminated on the lower part of the laminated metal plate 11 shown in FIG. ' is used. In the A and B types, the four-way switching valve unit 10 and the liquid separation unit 30 are combined, so a metal plate 11 ′ further laminated below the laminated metal plate 11 shown in FIG. 23(B) is used. At least good.

Next, the configuration of the four-way switching valve unit 10 will be described. 24A and 24B are schematic diagrams of the cylindrical body 12 provided in the four-way switching valve unit 10. FIG. 24A is a perspective view of the cylindrical body 12, and FIG. FIG. 24(C) is a sectional view taken along the line AA of FIG. 24(B).

As shown in FIGS. 24A, 24B, and 24C, the four-way switching valve unit 10 includes a first connection port 13 through which the refrigerant flows in and out, and a tubular body 12 through which the refrigerant is supplied from the first connection port 13. , a spool 14 provided in the cylindrical body 12 and movable in the axial direction of the cylindrical body 12 so that two connection modes can be selected; three second connection ports 15 through which the refrigerant flows in and out through the spool 14; 16, 17.

The spool 14 is formed in a mountain shape, the top surface of the spool 14 is provided with a convex portion 18 , and the inner surface of the cylindrical body 12 is provided with a concave portion 19 for receiving the convex portion 18 . Preferably, two concave portions 19 are provided on the inner surface of the cylindrical body 12 so as to be bilaterally symmetrical. Moreover, the convex portion 18 may have a convex shape, and a projection such as a resin or metal ball is used. The concave portion 19 may have a concave shape that receives a convex shape, and a leaf spring bent into a concave shape is used. When cooling, heating, or dehumidification/heating is not used, the refrigerant will not flow through the four-way switching valve unit 10. I don't like it because it moves. For example, according to the position of the spool 14 as shown in FIG. 24(C), the refrigerant flows from the second connection port 16 to 17, but without the protrusion 18 and the recess 19 that serve as stoppers, the vibration of the vehicle would be reduced. etc., the spool 14 can be moved slightly to the left in the drawing, and the refrigerant can flow through all three of the second connection ports 15, 16, and 17. FIG. Also, if the four-way switching valve unit 10 is moved to an incomplete position, the differential pressure between chambers A and B shown in FIG. Therefore, the convex portion 18 and the concave portion 19 prevent the above point.

The spool 14 preferably has a metal chevron spool head 144 and a Teflon base 145 to which the spool head 144 is fixed. The spool 14 may be entirely made of resin, but in such a case, the resin must be thick in order to provide rigidity, while the space inside the cylindrical body 12 is limited. Therefore, by making the spool head 144 formed of metal into a mountain shape, the spool 14 can be thinned, the space in the cylindrical body 12 can be saved, and various flow rates and pressures can be handled. Further, when the spool 14 is entirely made of resin, the projections 18 are also made of resin for mounting problems. On the other hand, if the spool head 144 is made of metal and is formed in a mountain shape, the protrusion 18 can be made of metal, and the abrasion resistance is improved. SUS or the like is used as the metal, and the spool head 144 may be formed by press molding and integrated with the Teflon base 145 by molding.

The first connection port 13 corresponds to the refrigerant path X of the four-way switching valve unit, and the second connection ports 15, 16, 17 correspond to the refrigerant paths U, V, W of the four-way switching valve unit, respectively.

FIG. 25 is a schematic diagram of the four-way switching valve unit 10, FIG. 25(A) is a diagram viewed from the bottom of FIG. 23(A), and FIG. It is a cross-sectional view. As shown in FIG. 25(A), a plurality of metal plates 11 stacked on the tubular body 12 shown in FIG. 24(A) are provided so that the refrigerant can be kept airtight. 25(B), a plurality of metal plates 11 stacked on top of the cylindrical body 12 are provided. A plurality of stacked metal plates 11 are composed of a lower plate 111, an intermediate plate 112, and an upper plate 113. The lower plate 111, intermediate plate 112, and upper plate 113 are each formed by metal plates 11 so that the coolant can flow. through holes 115, 116 and 117 are provided. The through holes 115 , 116 , 117 of the metal plate 11 are connected and provided so as to match the second connection ports 15 , 16 , 17 .

The diameters of the holes 115 , 116 , 117 drilled in the lower plate 111 are preferably larger than the diameters of the second connection ports 15 , 16 , 17 . By doing so, the connectivity is improved and the airtightness can be further maintained.

Next, the structure of the proportional control valve 22 provided in the gas injection unit 20 will be described. 26 is a sectional view of the proportional control valve 22 provided in the gas injection unit 20. FIG.

As shown in FIG. 26, the proportional control valve 22 is fixed to a main body 221, a support 222 provided in the main body 221, and the support 222. The support 222 is vertically movable to adjust the flow rate of the refrigerant. a magnet 223 and a pulse motor 224, a slicer 225 fixed to the main body 221, and an upper stopper 226 and a lower stopper 227 for preventing excessive vertical movement of the column 222; It is characterized in that grooves are formed in which the stopper 226 and the lower stopper 227 can be attached.

When the pulse motor 224 rotates the magnet up and down, the post 222 moves up and down. At this time, since the upper stopper 226 and the lower stopper 227 are fixed to the pillars, they move up and down at the same time. The amount of vertical movement is used to adjust the flow rate of the refrigerant. When increasing the flow rate, the number of pulses can be increased to raise the strut 222 higher.

The slicer 225 is fixed to the body portion 221 . A groove 228 is formed in the column, and an upper stopper 226 is attached to the upper portion of the column 222 and a lower stopper 227 is attached to the lower portion of the column 222 in the groove. By attaching the slicer 225 , the upper stopper 226 and the lower stopper 227 , the slicer 225 fixed to the main body part 221 is caught by the upper stopper 226 and the lower stopper 227 when the post 222 tries to move in the vertical direction. and the lower stopper 227, the support 222 can move up and down. By doing so, it is possible to prevent excessive outflow of the refrigerant when the pulse motor malfunctions. For the upper stopper 226 and the lower stopper 227, for example, C-rings may be used. An electronic expansion valve described below has the same configuration.

Refrigerant flows through the proportional control valve 22 as indicated by arrows A to B. As shown in FIG. The flow rate of the refrigerant is adjusted by moving the valve seat 222' provided on the strut 222 of the proportional control valve 22 in the axial direction of the proportional control valve 22 (up and down in FIG. 26).

Further, by increasing the length of the valve seat 222' in the axial direction, it is possible to prevent blurring due to vibration or the like. Further, it is preferable that the upper portion 229 of the proportional control valve 22 be curved. By doing so, the resistance to internal pressure is improved.

FIG. 27 is a schematic diagram in cross section of a check valve. Preferably, the heat pump system 100 according to one embodiment of the present invention further includes a vertical check valve 41 as shown in FIG. The check valve 41 includes an outer cylinder 411 , an inner cylinder 412 provided inside the outer cylinder 411 , a valve 413 provided at the bottom of the inner cylinder 412 for allowing the refrigerant to flow in and not to flow out, and the inner cylinder 412 . It is characterized by having a port (hole) 414 provided on the side surface for discharging the coolant.

The refrigerant flows into and passes through the check valve 41 as indicated by solid line arrows in FIG. When the refrigerant pushes the valve 413 upward in FIG. 27, a gap is created between the valve 413 and the inner cylinder 412, and the refrigerant flows into the inner cylinder 412 through the gap. The refrigerant that has flowed in flows out from a port (hole) 414 provided on the side surface of the inner cylinder 412 and flows out through a gap provided between the outer cylinder 411 and the inner cylinder 412 . On the other hand, even if the refrigerant flows into the inner cylinder 413 through the port 414 from the left side of FIG.

A general check valve is of a horizontal type, but the check valve 41 used in the heat pump system 100 according to one embodiment of the present invention is of a vertical type. The structure of the check valve 41 can also be applied to the first check valve 24 and the second check valve 27 .

FIG. 28 is a sectional view of a heating expansion valve, a dehumidifying expansion valve, and a cooling expansion valve. Hereinafter, the heating expansion valve, the dehumidifying expansion valve, and the cooling expansion valve used in the heat pump system 100 according to one embodiment of the present invention will be collectively referred to as an electronic expansion valve 230 . As shown in FIG. 28, the electronic expansion valve 230 is fixed to a main body 231, a support 232 provided in the main body 231, and the support 232. The support 232 is vertically movable to adjust the flow rate of the refrigerant. a magnet 233 and a pulse motor 234, a slicer 235 fixed to the main body 231, and an upper stopper 236 and a lower stopper 237 for preventing excessive vertical movement of the column 232; A groove 238 is formed to allow attachment of a stopper 236 and a lower stopper 237 .

When the magnet is rotated up and down by the pulse motor 234, the column 232 moves up and down. At this time, since the upper stopper 236 and the lower stopper 237 are fixed to the pillars, they move up and down at the same time. The amount of vertical movement is used to adjust the flow rate of the refrigerant. When increasing the flow rate, the number of pulses can be increased to raise the strut 232 higher.

The slicer 235 is fixed to the body portion 231 . A groove 238 is formed in the column, and an upper stopper 236 is attached to the upper portion of the column 232 and a lower stopper 237 is attached to the lower portion of the column 232 in the groove. By attaching the slicer 235 , the upper stopper 236 and the lower stopper 237 , when the post 232 tries to move in the vertical direction, the slicer 235 fixed to the main body 231 is caught by the upper stopper 236 and the lower stopper 237 and the upper stopper 236 and the lower stopper 237, the support 232 can move vertically. By doing so, it is possible to prevent excessive outflow of the refrigerant when the pulse motor malfunctions.

As described above, according to the present invention, in addition to the reduction in size, weight, and thickness, the assembling workability is excellent. It is possible to provide a heat pump system that is unitized at the same time, realizes cost performance due to compactness, and is particularly capable of sufficiently coping with extremely low temperatures.

The piping unit for automobile air conditioning according to the present invention is adopted in a heat pump system mounted on a drive system automobile that does not always activate the internal combustion engine, such as an electric vehicle (EV), a fuel cell vehicle (FCV), etc. .

Although the embodiments and examples of the present invention have been described in detail as described above, it should be understood by those skilled in the art that many modifications are possible without substantially departing from the novel matters and effects of the present invention. , will be easily understood. Accordingly, all such modifications are intended to be included within the scope of the present invention.

For example, a term described at least once in the specification or drawings together with a different, broader or synonymous term can be replaced with the different term anywhere in the specification or drawings. Also, the configuration and operation of the heat pump system are not limited to those described in the embodiments of the present invention, and various modifications are possible.

10, 10' four-way switching valve unit, 11 stacked metal plates (of the four-way switching valve unit), 11' metal plate (provided under the plurality of metal plates provided in the four-way switching valve unit), 12 cylindrical body 13 first connection port 14 spool 15, 16, 17 second connection port 18 convex portion 19 concave portion 20 gas injection unit 22 proportional control valve 23 expansion valve for dehumidification 24 second One check valve 25 Stacked multiple metal plates (gas injection unit) 26 Heating expansion valve 27 Second check valve 28 Sectional seat 30 Liquid separation unit 31 Third check valve , 40 cooling and heating control unit, 41 check valve, 42 cooling expansion valve, 43 battery expansion valve, 45 laminated plural metal plates (cooling and heating control unit), 48 sectioned pedestal, 50 condenser, 60 evaporator, 100 heat pump system, 110 outdoor condenser, 120 blower, 130 battery inverter cooler,
111 lower plate, 112 intermediate plate, 113 upper plate, 115, 116, 117 holes in metal plate,
144 spool head, 145 Teflon base,
221 main body, 222 strut, 222' valve seat, 223 magnet, 224 pulse motor, 225 slicer, 226 upper stopper, 227 lower stopper, 228 groove, 229 upper portion of proportional control valve,
230 electronic expansion valve, 231 main body, 232 support, 233 magnet, 234 pulse motor, 235 slicer, 236 upper stopper, 237 lower stopper, 238 groove,
251 upper plate, 252 first intermediate plate, 253 second intermediate plate, 254 lower plate,
281, 282, 283, 284 metal plates (of section plinths),
411 outer cylinder, 412 inner cylinder, 413 valve, 414 port,
451 upper plate, 452 first intermediate plate, 453 second intermediate plate, 454 lower plate, 455 non-return valve seat, 456 copper plate, 481, 482, 483, 484 metal plate (of sectioned seat),
U, V, X, W Refrigerant path of the four-way switching valve unit,
A, B Cylindrical chamber provided in the four-way switching valve unit

Claims (10)

A heat pump system used for automotive air conditioning with cryogenic specifications,
a four-way switching valve unit that can switch four refrigerant paths into two pairs of paths in accordance with function switching among cooling, heating, and dehumidification;
a gas injection unit provided with a plurality of airtightly laminated metal plates and a proportional control valve;
a liquid separation unit that separates a liquid;
A cooling and heating control unit provided with a plurality of metal plates laminated in an airtight manner and performing function switching between cooling, heating and dehumidification;
a condenser for condensing the refrigerant;
an evaporator that expands the refrigerant;
a compressor for compressing the refrigerant;
with
The four-way switching valve unit allows the refrigerant to flow from the cooling/heating control unit to the liquid separation unit and from the compressor to flow to the condenser during heating and dehumidifying heating, and the refrigerant during cooling. from the condenser to the liquid separation unit and from the compressor to the cooling/heating control unit;
In the gas injection unit, the refrigerant flows from the condenser during heating and dehumidifying heating, flows out to the compressor and the cooling/heating control unit through the proportional control valve, and flows out to the evaporator during dehumidifying and heating. , during cooling, flows from the evaporator and flows out to the condenser;
The liquid separation unit flows the refrigerant from the four-way switching valve unit and flows out to the compressor during heating, dehumidifying heating, and cooling, and
The cooling/heating control unit allows the refrigerant to flow in from the gas injection unit and out to the four-way switching valve unit during heating and dehumidifying heating, and flow from the four-way switching valve unit to the gas injection unit during cooling. A heat pump system characterized by an outflow. The four-way switching valve unit and the liquid separation unit are combined,
The piping terminals of the compressor are composed of two piping terminals through which the refrigerant flows from the gas injection unit and the liquid separation unit through the proportional control valve, and one piping terminal through which the refrigerant flows out to the four-way switching valve unit. configured,
In the gas injection unit, the refrigerant flows from the condenser during heating and dehumidifying heating, flows out to the compressor and the cooling/heating control unit through the proportional control valve, and flows out to the evaporator during dehumidifying and heating. 2. The heat pump system according to claim 1, wherein the heat flows from the evaporator and flows out to the condenser during cooling. The four-way switching valve unit and the liquid separation unit are combined,
The piping terminals of the compressor are composed of one piping terminal into which the refrigerant flows from the liquid separation unit and one piping terminal into which the refrigerant flows out to the four-way switching valve unit,
The gas injection unit causes the refrigerant to flow into a gas-phase pipe terminal provided in the liquid separation unit,
2. The heat pump system according to claim 1, wherein the liquid separation unit causes the refrigerant to flow through the gas injection unit to the cooling/heating control unit during heating, and to the evaporator during dehumidifying and heating. The four-way switching valve unit and the liquid separation unit are separated,
The piping terminals of the compressor are composed of two piping terminals into which the refrigerant flows from the gas injection unit and the liquid separation unit, and one piping terminal into which the refrigerant flows out to the four-way switching valve unit. The heat pump system of claim 1, wherein the heat pump system is characterized by: The four-way switching valve unit is
a first connection port through which the refrigerant enters and exits;
a cylindrical body to which the refrigerant is supplied from the first connection port;
a spool provided in the cylindrical body and formed in a chevron shape movable in the axial direction of the cylindrical body so that two connection modes can be selected;
a second connection port through which the refrigerant enters and exits through the spool;
with
A protrusion is provided on the top surface of the spool,
The heat pump system according to any one of claims 1 to 4 , wherein a concave portion for receiving the convex portion is provided on the inner surface of the cylindrical body. 6. The heat pump system according to claim 5 , wherein the spool has a metal spool head formed in a chevron shape, and a Teflon base for fixing the spool head. A plurality of laminated metal plates are provided at the second connection port,
The metal plate is composed of a lower plate, an intermediate plate and an upper plate, and is provided with holes so that the coolant can flow,
6. The heat pump system according to claim 5 , wherein diameters of the punched holes in the lower plate, the intermediate plate, and the upper plate are larger than the diameter of the second connection port. A divided pedestal constructed by laminating two or more metal plates on top of the plurality of metal plates laminated in an airtight manner constituting the gas injection unit and the cooling/heating control unit, or a divided pedestal integrally molded 2. The heat pump system of claim 1, further comprising: In addition, it has a vertical check valve,
The check valve is
an outer cylinder;
an inner cylinder provided inside the outer cylinder;
a valve provided at the bottom of the inner cylinder to allow the refrigerant to flow in and prevent it from flowing out;
2. The heat pump system according to claim 1, further comprising a port provided on a side surface of said inner cylinder for discharging a refrigerant. Furthermore, one or more of a heating expansion valve, a dehumidifying expansion valve, and a cooling expansion valve are provided,
The heating expansion valve, the dehumidifying expansion valve, and the cooling expansion valve are
a main body;
a post provided in the main body;
a magnet and a pulse motor that are fixed to the support and adjust the flow rate of the refrigerant by moving the support in the vertical direction;
a slicer fixed to the main body;
The column has an upper stopper and a lower stopper that prevent excessive movement in the vertical direction,
2. The heat pump system according to claim 1, wherein grooves are formed in said struts so that said upper stoppers and lower stoppers can be attached.

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