JP2011235753A - Air conditioning device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning device for a vehicle which has an integral integrated valve integrating a three-way valve 30 and a valve unit 25 on the inlet side of an outdoor heat exchanger 21.SOLUTION: A refrigerant flow path change-over control valve 41 is formed of an integrated valve, which consists of a solenoid valve forming a valve unit 25 provided between an indoor condenser 12 and an inlet side of an outside heat exchanger 21, a heating throttle 26 provided in parallel to the valve unit 25 and a three-way valve 30 provided with a common flow path 50 on the outlet side of the outside heat exchanger 21, and accommodates the valve unit 25, heating throttle 26, three-way valve 30, first change-over flow path 55 and second change-over flow path 56 in the same body 40. The three-way valve 30 includes a differential pressure valve which changes over valve operation by changing pressure in accordance with the opening and closing of the valve unit 25. In this arrangement, easy piping, miniaturization and simple wiring work are achieved.

Description

  The present invention relates to a vehicle air conditioner that includes an indoor heat exchanger and an outdoor heat exchanger, and that integrates a valve mechanism that heats or cools a room and switches a path through which a refrigerant flows. In particular, the present invention relates to a vehicle air conditioner in which a valve mechanism is integrally attached to an outdoor heat exchanger.

  In vehicle air conditioning systems, it was common to use engine waste heat as a heat source for heating, but in recent years there has been development of hybrid vehicles and electric vehicles (hereinafter referred to as EV vehicles) with little waste heat that can be used for heating. The amount of waste heat that can be used for heating is very small, especially in EV cars. Therefore, the vehicle air conditioner using a heat pump system tends to increase.

  As a vehicle air conditioner using this heat pump system, an air conditioner described in Patent Document 1 is known. This known air conditioner relates to an automobile air conditioner that performs air conditioning in an automobile interior.

  This automotive air conditioner is used in a vehicle equipped with an engine in which engine coolant is not a sufficient heat source, or in a vehicle that does not have any surplus heat source such as an electric vehicle. It makes it possible to perform desirable air conditioning by skillfully utilizing the fluctuations in the above.

  And, by specifying the function of the heat exchanger arranged in the duct with the heater and the indoor evaporator, a single heat exchanger can function as a heater, or the indoor evaporator It does not perform the function as. In other words, the apparatus of Patent Document 1 is configured so that a large amount of moisture does not evaporate and cause fogging of the window glass even when switching the operating conditions of air conditioning.

  In addition, by driving the compressor with an electric motor, the compressor capacity can be variably controlled, and by appropriately controlling the compressor discharge capacity and the reheating of the air by the heater, air conditioning can be performed with low power. It is designed to be efficient.

  In addition, an outdoor heat exchanger is provided to complement the capabilities of the heater and indoor evaporator arranged in the duct, and the cooling or heating operation is made more efficient by controlling the refrigerant flow to the outdoor heat exchanger. I can do it.

  Furthermore, the air flow that bypasses the indoor evaporator and the heater disposed in the duct is variably controlled by a damper, so that the cooling operation and the heating operation can be performed more effectively.

  More specifically, as shown in a known refrigerant circuit diagram shown in FIG. 14, an indoor evaporator 11 constituting a refrigeration cycle is arranged in the duct 1. And the indoor condenser 12 which comprises the refrigerating cycle similarly is arrange | positioned in the downstream of this indoor evaporator 11. FIG.

  Note that the indoor evaporator 11 takes the heat of vaporization from the air during heat exchange with the conditioned air, cools the air, and operates as a cooler. On the other hand, the indoor condenser 12 releases the condensation heat into the air during heat exchange to heat the air and operates as a heater.

  The refrigeration cycle includes a compressor 20 that is driven by an electric motor (not shown) and compresses and discharges the refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 20 is condensed in the outdoor heat exchanger 21. The indoor condenser 12 in the duct 1 described above is connected to the outdoor heat exchanger 21 by a refrigerant pipe through a solenoid valve and a heating throttle 26 that form valve means 25.

  One of the refrigerant that has flowed out of the outdoor heat exchanger 21 is guided to the inlet of the indoor evaporator 11 in the duct 1 through a capillary tube that forms a cooling throttle 31, and the other through a downstream electromagnetic valve 32. It is guided to the outlet of the accumulator 35 and the indoor evaporator 11 in the duct 1.

  Further, the capacity of the indoor condenser 12 in the duct 1 is switched using the air mix damper 16. In other words, the air mix damper 16 causes air to flow into the indoor condenser 12 in the duct 1 during heating.

  On the other hand, as a general rule, the air mix damper 16 is closed as indicated by a broken line during cooling so that air does not flow to the indoor condenser 12. However, even during cooling, the air mix damper 16 operates as a damper that varies the blowing temperature, the opening degree of the air mixing damper 16 is controlled according to the necessary blowing temperature, and a part of the air is heated by the indoor condenser 12. Operates to

Japanese Patent No. 3538845

  The inventor has developed an air conditioner for an EV vehicle using this known vehicle air conditioner. In the development process, the air conditioner 31 between the outdoor heat exchanger 21 and the indoor evaporator 11 shown in FIG. 1 and the downstream solenoid valve 32 between the outdoor heat exchanger 21 and the accumulator 35 are replaced with a three-way valve 30 as shown in FIG.

  This is because, in consideration of thermal efficiency, it is desired to completely block the refrigerant leaking into the indoor evaporator 11 through the capillary tube that forms the cooling throttle 31 during heating.

  The air conditioner of FIG. 1 devised in the development process from the technique of Patent Document 1 requires a three-way valve 30, an electromagnetic valve forming valve means 25, and a heating throttle 26 around the outdoor heat exchanger 21. If these devices are mounted in a distributed manner, it takes time for mounting work and piping work, which is not preferable. Therefore, further ingenuity was required. Further, since the three-way valve 30 must be controlled together with the control of the electromagnetic valve constituting the valve means 25, the electrical wiring becomes complicated.

  The present invention has been made paying attention to such problems existing in the prior art, and its purpose is to reduce the number of pipes and to provide a vehicle air conditioner that can be easily installed and installed. It is to provide.

  Descriptions of patent documents listed as prior art can be introduced or incorporated by reference as explanations of technical elements described in this specification.

In order to achieve the above object, the present invention employs the following technical means. That is, in the invention described in claim 1, the air conditioning duct (1) includes the indoor evaporator (11) and the indoor condenser (12), and the indoor evaporator (11) and the indoor condenser (12). It is a vehicle air conditioner that performs heat exchange by a heat pump cycle in which refrigerant from the compressor (20) flows to the outdoor heat exchanger (21), and an inlet side of the outdoor heat exchanger (21) and an indoor condenser ( 12), and a heating throttle means (26) provided with a passage for restricting the flow of the refrigerant in parallel to the refrigerant passage opened and closed by the valve means (25). The three-way valve (30) provided with the common channel (50) communicating with the outlet side of the outdoor heat exchanger (21), and the refrigerant from the common channel (50) is cooled through the three-way valve (30). Refrigerant from first switching channel (55) and common channel (50) flowing during operation Comprises a three-way valve second switching flow path that flows during the heating operation through the (30) (56),
At least a part of the valve means (25), the heating throttle means (26), the three-way valve (30), the first switching flow path (55), and the second switching flow path (56) is accommodated in the body (40). The refrigerant flow switching control valve (41) comprising an integrated valve is configured.

  According to this invention, since at least three devices of the valve means (25), the heating throttle means (26), and the three-way valve (30) are housed and integrated in the body (40), the refrigerant pipe Can be connected to the body (40), and does not have to be connected to individual devices.

  The invention according to claim 2 is characterized in that the three-way valve (30) is constituted by a differential pressure valve whose valve operation is switched when the pressure changes in accordance with opening and closing of the valve means (25).

  Further, according to the present invention, since the three-way valve (30) is constituted by a differential pressure valve, the electric wiring for the three-way valve (30) becomes unnecessary, and the wiring work can be simplified.

  In the invention according to claim 3, the connection between the body (40) and the outdoor heat exchanger (21) is a connection provided on the body (40) side with a connection part mounted on the outdoor heat exchanger (21). A first joint part (71) on the inlet side of the outdoor heat exchanger (21) formed by fitting the concave and convex parts, and a second joint part (72) on the outlet side of the outdoor heat exchanger (21). The first joint portion (71) is provided on the valve means (25) side, and the second joint portion (72) is provided on the common flow path (50) side.

  According to this invention, piping is not required for the connection between the body (40) and the outdoor heat exchanger (21), and the body (40) may be simply joined directly to the outdoor heat exchanger (21). Therefore, piping connection is not necessary, and assembly work can be simplified.

  In the invention according to claim 4, the valve means inlet side flow path (44) through which the refrigerant from the indoor condenser (12) flows into the body (40), and the valve means through which the refrigerant flows into the outdoor heat exchanger (21). An outlet side flow path (45) is formed, and the valve means (25) is interposed between the valve means inlet side flow path (44) and the valve means outlet side flow path (45), and the valve means outlet side flow A three-way valve (30) having a common flow path (50) in the body (40) through which the refrigerant is led from the path (45) via the outdoor heat exchanger (21) and communicating with the common flow path (50). The common chamber (51) has a first switching channel (55) that connects the common channel (50) and the indoor evaporator (11) side on one side of the common chamber (51), and is compressed on the other side of the common chamber (51) It has the 2nd switching flow path (56) which comprises the flow path of the refrigerant | coolant which returns to the machine (20) side, It is characterized by the above-mentioned.

  According to this invention, the valve means (25) is interposed between the valve means inlet side flow path (44) and the valve means outlet side flow path (45) in the body (40), and the three-way valve (30). Has a common channel (50) in the body (40) through which the refrigerant is led from the valve means outlet side channel (45) via the outdoor heat exchanger (21), and communicates with the common channel (50). The first switching channel (55) for connecting the common channel (50) and the indoor evaporator (11) side is provided on one side of the common chamber (51) in the three-way valve (30). 51) Since the second switching channel (56) is provided on the other side of 51), the valve means (25) and the three-way valve (30) can be incorporated in the body (40) and the refrigerant channel can be switched.

  In the invention according to claim 5, the three-way valve (30) has a reciprocating valve body (60) that reciprocates between the first switching flow path (55) and the second switching flow path (56), In response to the movement of the reciprocating valve body (60), the three-way valve (30) causes the common flow path (50) to communicate with either the first switching flow path (55) or the second switching flow path (56). The valve (30) includes a pressure introduced from the valve means inlet side flow path (44) to one side of the reciprocating valve body (60) via the pressure introduction path (42) and a pressure of the common flow path (50). It is characterized by comprising a differential pressure valve that reciprocates with a differential pressure.

  According to this invention, the reciprocating valve body (60) is a differential pressure between the pressure introduced from the valve means inlet side flow path (44) to one side of the reciprocating valve body (60) and the pressure of the common flow path (50). To reciprocate. That is, the three-way valve (30) is composed of a differential pressure valve. For this reason, a dedicated electric wiring for controlling the three-way valve (30) is not required, and the wiring work is simplified.

  In the invention according to claim 6, the pressure introduced from the valve means inlet side flow path (44) to one side of the reciprocating valve body (60) is a pressure introduction path (42) formed in the body (40). It is introduced through this.

  According to the present invention, the pressure introduced into one side of the reciprocating valve body (60) from the valve means inlet-side flow path (44) for configuring the three-way valve (30) as a differential pressure valve is changed to the body (40). Since it is led by the pressure introduction path (42) formed in the inside, a dedicated electric wiring for controlling the three-way valve (30) becomes unnecessary, and compared with the case where the pressure introduction path (42) is separately provided on the pipe. It can be downsized.

  In the invention according to claim 7, the three-way valve (30) includes the pressure difference between the pressure introduced to one side of the reciprocating valve body (60) and the pressure of the common flow path (50), and the reciprocating valve body (60). ) By the elastic force of the spring member (63) provided on the other side, the reciprocating valve body (60) reciprocates, so that a part of the reciprocating valve body (60) becomes the first valve seat (65) and the second valve seat (65). It has a pair of poppet valve parts which contact | abut to a valve seat (66), It is characterized by the above-mentioned.

  According to this invention, the three-way valve (30) includes the differential pressure between the pressure introduced to one side of the reciprocating valve body (60) and the pressure of the common flow path (50), and the elastic force of the spring member (63). Therefore, the stroke of the reciprocating motion can be shortened and the three-way valve (30) portion can be made compact.

  In the invention according to claim 8, the pair of poppet valve portions includes one poppet valve portion of the pair of poppet valve portions and a connecting member (60c) having one end fixed to the one poppet valve portion. The other end of the connecting member (60c) is inserted into the other poppet valve portion of the pair of poppet valve portions, and the pair of poppet valve portions are interlocked in at least a predetermined direction via the connecting member (60c). It is characterized by.

  According to the present invention, the connecting member (60c) is inserted into the other poppet valve portion of the pair of poppet valve portions, and the pair of poppet valve portions are interlocked via the connecting member (60c). A pair of pressure difference between the pressure introduced to one side of the body (60) and the pressure of the common flow path (50) and the elastic force of the spring member (63) provided on the other side of the reciprocating valve body (60). The three-way valve (30) with which the poppet valve part of this is interlocked can be configured.

  In the invention described in claim 9, the heating throttle means (26) comprises a narrow-diameter channel formed in parallel with the valve means (25), and the narrow-diameter channel is a channel through which refrigerant flows in the valve means. It is characterized by comprising a flow path formed in a body (40) having a smaller diameter.

  According to this invention, the valve means (25) is interposed between the valve means inlet side flow path (44) and the valve means outlet side flow path (45), and the heating throttle means (26) is the body (40). ), The heating throttle means (26) can be formed in the body (40), and is smaller than the case where the heating throttle means is separately formed on the pipe. Can be

  In the invention according to claim 10, the heating throttle means (26) provided with the flow path for narrowing the flow of the refrigerant in parallel with the flow path of the refrigerant opened and closed by the valve means (25) includes the valve means ( 25) The valve means (25) which does not completely close but leaves a minute gap and performs a valve closing operation (25) is characterized by comprising a gap flow path after the valve is closed.

  According to this invention, since the heating throttle means (26) is formed from the gap flow path which becomes the leakage flow path after the valve means (25) is closed, the heating throttle means is specially provided for the valve means (25). Compared with the case of forming outside, it is easy to reduce the manufacturing cost.

  According to an eleventh aspect of the present invention, the valve means for closing the valve while leaving a minute gap comprises valve means for adjusting the opening degree of the valve after closing, which is the size of the minute gap.

  According to this invention, since the opening degree of the valve, which is the size of the minute gap, can be adjusted, the opening degree of the heating throttle means (26) can be set to an opening degree suitable for the operating state of the refrigerant cycle. .

  The twelfth aspect of the invention is characterized in that the valve means (25) capable of adjusting the opening degree of the valve after the valve closing operation is constituted by an electric valve.

  According to this invention, the throttle opening degree of the heating throttling means (26) can be easily set to the opening degree suitable for the operating state of the refrigerant cycle by the valve means (25) comprising the motor operated valve.

  In a thirteenth aspect of the present invention, the heat pump cycle further includes an accumulator (35), a cooling throttle (31), a first switching pipe (55a), and a second switching pipe (56a), and a common flow path ( The first switching flow path (55) for flowing the refrigerant from 50) during the cooling operation causes the refrigerant to flow to the indoor evaporator (11) through the first switching pipe (55a) and the cooling throttle (31), thereby heating the The second switching channel (56) for flowing the refrigerant during operation returns the refrigerant to the compressor (20) via the second switching pipe (56a) and the accumulator (35).

  According to this invention, the cooling operation can be performed via the first switching flow path (55), and the heating operation can be performed via the second switching flow path (56).

  In addition, the code | symbol in parentheses described in a claim and each said means is an example which shows the correspondence with the specific means as described in embodiment mentioned later easily, and limits the content of invention is not.

It is a refrigerant circuit figure in the air-conditioner for vehicles using the heat pump cycle for EV vehicles as a 1st embodiment of the present invention and a development stage. FIG. 2 is a substantial refrigerant piping diagram in which the refrigerant piping diagram of FIG. 1 is written in more detail. A part of a specific configuration of the refrigerant flow switching control valve in a cooling state including a solenoid valve forming valve means housed in the body shown in FIG. 2, a heating throttle forming throttle means, and a three-way valve It is sectional drawing. FIG. 4 is a partial cross-sectional view showing a specific configuration of a refrigerant flow switching control valve in a heating state in which the solenoid valve of FIG. 3 is closed and refrigerant from an outdoor heat exchanger is directed to an accumulator. It is a right view of the refrigerant flow path switching control valve of FIG. FIG. 4 is a partial cross-sectional view taken along line Z6-Z6 in FIG. 3. FIG. 4 is a partial cross-sectional view taken along line Z7-Z7 in FIG. 3. FIG. 6 is a partial cross-sectional view showing a specific configuration of a refrigerant flow switching control valve that employs a spool valve as a three-way valve showing a second embodiment of the present invention. FIG. 9 is a partial cross-sectional view showing a specific configuration of a refrigerant flow switching control valve employing a spool valve showing a state in which the reciprocating valve body has moved to the right from the state of FIG. 8. It is a partial cross section figure at the time of a motor operated valve full opening showing the concrete composition of the refrigerant channel change control valve which adopted the motor operated valve which shows a 3rd embodiment of the present invention. FIG. 11 is a partial cross-sectional view showing a state in which the motor-operated valve of FIG. 10 is closed while leaving a leak passage having a minute opening. It is the schematic diagram which showed typically the principal part of the three-way valve which shows other embodiment. It is a right view corresponding to FIG. 5 which shows other embodiment and shows the coupling | bonding state of an outdoor heat exchanger and a refrigerant | coolant flow path switching control valve. It is a refrigerant circuit figure in a publicly known vehicle air-conditioner.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration.

  Not only combinations of parts that clearly indicate that the combination is possible in each embodiment, but also a combination of the embodiments even if they are not clearly specified unless there is a problem with the combination. It is also possible.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. First, the entire configuration including the operation will be described, and then the operation will be described separately for cooling and heating. FIG. 1 is a refrigerant circuit diagram in a vehicle air conditioner using the heat pump cycle for an EV vehicle as the first embodiment (this refrigerant circuit diagram which is not detailed is the same as that in the development process). In FIG. 1, reference numeral 1 denotes a duct that forms an air passage, and is disposed in the passenger compartment.

  A fan case 2 is connected to one side of the duct 1, and a blower 4 including a sirocco fan 3 is disposed in the fan case 2. The blower 4 is rotationally driven by a blower motor 5 disposed at the center thereof. Furthermore, an inside / outside air switching unit 6 is connected to the fan case 2, and an inside air introduction port 7 and an outside air introduction port 8 are opened in the inside / outside air switching unit 6.

  An inside / outside air switching damper 9 is disposed in the inside / outside air switching unit 6, and the inside / outside air switching damper 9 can switch the air introduced into the duct 1 between the room air and the outside air. An air outlet (not shown) that blows out air-conditioned air toward the vehicle interior is formed above the duct 1 in FIG.

  This air outlet has a face air outlet that mainly blows cool air toward the head and chest of the occupant, a foot air outlet that mainly blows warm air toward the legs of the occupant, and a warm air mainly toward the window glass. A differential outlet for blowing wind is formed. Each air outlet is provided with a face damper, a foot damper, and a differential damper that control the air flow to the air outlet.

  An indoor evaporator 11 constituting a refrigeration cycle is disposed in the duct 1. And the indoor condenser 12 which comprises the refrigerating cycle similarly is arrange | positioned in the downstream of this indoor evaporator 11. FIG. Note that the indoor evaporator 11 takes the heat of vaporization from the air during heat exchange with the conditioned air, cools the air, and operates as a cooler.

  On the other hand, the indoor condenser 12 releases the heat of condensation into the air during heat exchange, heats the air, and operates as a heater. The indoor evaporator 11 and the indoor condenser 12 constitute indoor heat exchangers 11 and 12.

  A bypass passage 15 is disposed on the side of the indoor condenser 12 in the duct 1, and the ratio of the air volume flowing through the bypass path 15 and the air volume flowing through the indoor condenser 12 in the duct 1. An air mix damper 16 that continuously and variably controls is arranged so as to be rotatable around one end.

  The refrigeration cycle includes a compressor 20 that is driven by an electric motor (not shown) and compresses and discharges the refrigerant. Since the compressor 20 is disposed in a sealed case integrally with the electric motor, the installation location is not particularly limited.

  However, it is desired that the compressor 20 be disposed in a portion other than the passenger compartment of the automobile due to a request for maintenance and inspection. The outdoor heat exchanger 21 is disposed in front of the traveling direction of the automobile so that good heat exchange with outside air can be performed.

  That is, the outdoor heat exchanger 21 receives traveling wind when the vehicle is traveling, and can perform heat exchange between the refrigerant and the air satisfactorily. The indoor condenser 12 in the duct 1 is connected to the outdoor heat exchanger 21 and the refrigerant pipe through an electromagnetic valve and a heating throttle 26 that constitute valve means 25 composed of a pilot type electromagnetic valve.

  An operation panel (not shown) is disposed at a position where the passenger can easily see the vehicle interior. In the operation panel, a fan lever for controlling the rotation speed of the blower motor 5, a temperature adjusting lever for controlling the opening degree of the air mix damper 16, a mode switching lever for controlling each outlet damper, and an inside / outside air switching damper 9 are switched. There are provided an operation lever to be controlled, an air conditioner switch for starting the operation of the air conditioner, an economy switch for performing a power saving operation of the air conditioner, an off switch for stopping the operation of the air conditioner, and the like.

  Based on a signal from a temperature sensor (not shown) that detects the air temperature on the outlet side of the indoor evaporator 11, the rotational speed of the compressor 20 is controlled so that the temperature on the outlet side of the indoor evaporator 11 is 3 to 4 degrees. . However, when the economy switch is turned on, the rotational speed of the compressor 20 is variably controlled so that the air temperature at the outlet side of the indoor evaporator 11 becomes 10 to 11 degrees based on the signal from the temperature sensor.

  By turning on the air conditioner switch (not shown) and setting the fan switch to the LO, MID, or HI state, the compressor 20 starts rotating and the blower motor 5 rotates at the selected number of rotations.

  During the cooling of the passenger compartment, the high-temperature and high-pressure refrigerant discharged from the compressor 20 passes through the indoor condenser 12 and flows into the outdoor heat exchanger 21 from the valve means 25 and is condensed. The three-way valve 30 is switched so that the refrigerant flows to the cooling throttle 31 side, and the refrigerant condensed in the outdoor heat exchanger 21 passes through the indoor evaporator 11 in the duct 1 through the fixed throttle that forms the refrigerant throttle 31. After that, the gas and liquid are separated in the accumulator 35 and supplied to the compressor 20.

  The refrigerant which is adiabatically expanded by the cooling throttle 31 and becomes a low-temperature and low-pressure mist is supplied to the indoor evaporator 11. The indoor evaporator 11 exchanges heat with the air supplied from the blower 4. That is, it takes heat of vaporization from the air, and the refrigerant evaporates at a low pressure. The evaporated refrigerant is sucked into the compressor 20 again.

  The air mix damper 16 indicated by a broken line in FIG. 1 is a state in which the air mix damper 16 is fully closed. That is, no air flow is introduced into the indoor condenser 12 in this fully closed state. Therefore, the refrigerant is condensed in the outdoor heat exchanger 21.

  As indicated by the broken line, in the state where the air mix damper 16 is fully closed, the enthalpy loss due to the indoor condenser 12 can be ignored, so the cooling function of the indoor evaporator 11 can be used for cooling as it is. .

  Next, the air flow state at this time will be described. The air selectively supplied by the inside / outside air switching damper 9 is supplied from the blower 4 to the indoor evaporator 11. Here, the refrigerant is cooled by vaporization of the refrigerant when passing through the indoor evaporator 11, and goes to the bypass passage 15 and the indoor condenser 12 in a state where the outlet side air temperature becomes 3 to 4 degrees.

  This air flow is appropriately selected by the air mix damper 16. That is, in a state where maximum cooling is required, the air mix damper 16 closes the indoor condenser 12 and guides the cooled air as it is to the outlet.

  Cooling is too effective, so if you want to raise the temperature of the blown air, lower the compressor speed. If the temperature does not rise sufficiently even when the rotational speed of the compressor is lowered, the air mix damper 16 is opened and a part of the air is allowed to flow to the indoor condenser 12. The air that has flowed to the indoor condenser 12 is mixed with the cold air that has passed through the bypass passage 15 in the air mix chamber downstream of the indoor condenser 12.

  The mixed air is blown into the vehicle interior by switching between a known face damper, foot damper, and differential damper that controls the air flow to each outlet. When the mode switch on the operation panel (not shown) is in the face mode, only the face damper is opened and the other foot damper and differential damper are closed. Therefore, the cold air is blown mainly toward the passenger's head and chest.

  When the mode switch is set to the bi-level mode, the differential damper is closed and the face damper and the foot damper are opened.

  When the mode switch is set to the foot mode, only the foot damper is opened, and the other face damper and differential damper are closed. As a result, the air that has passed through the indoor condenser 12 is blown out from the foot outlet to the feet of the passenger.

  When the mode switch is set to the differential mode, only the differential damper is opened and the other face dampers and foot dampers are closed. As a result, air is blown out from the differential outlet toward the window glass of the automobile.

  In the above-described example, the opening degree of the air mix damper 16, the rotational speed of the blower motor 5, and the rotational speed of the compressor 20 may be manually operated by the occupant or may be automatically operated.

  When the discharge capacity of the compressor 20 is decreased, the capacity of the vehicle air conditioner as the refrigeration device is excessive as in the case where the actual temperature is lower than the target temperature. The frequency of the inverter is lowered, the rotational speed for driving the compressor 20 is lowered, and the discharge capacity of the compressor 20 is reduced.

  As shown in FIG. 1, in the first embodiment, the refrigeration cycle is an accumulator cycle. That is, an accumulator 35 for collecting refrigerant is installed on the outlet side of the indoor evaporator 11 on the suction side of the compressor 20, while a capillary tube serving as a cooling throttle 31 is used as the pressure reducing means.

  Hereinafter, the control valve in the air conditioner will be mainly described in the vehicle air conditioner of the first embodiment mounted on the EV vehicle capable of switching between cooling and heating. Hereinafter, an example in which the refrigerant flow switching control valve 41 in which the valve means 25 including a pilot electromagnetic valve and the differential pressure valve forming the three-way valve 30 are arranged in the same body 40 will be described as a control valve.

  FIG. 2 is an actual refrigerant piping diagram in which the refrigerant piping diagram of FIG. In FIG. 2, the indoor condenser 12 in the duct 1 is connected by refrigerant piping through an outdoor heat exchanger 21, valve means 25 including a solenoid valve, and a heating throttle 26. A three-way valve 30 is also provided.

  In FIG. 2, the valve means 25 including the electromagnetic valve, the heating throttle 26, and the three-way valve 30 are housed in the same or common body 40. That is, the valve means 25 between the outdoor heat exchanger 21 and the indoor condenser 12, the heating throttle 26 which constitutes the heating throttle means in which the flow path is provided in parallel to the valve means 25, and the outdoor heat exchange The three-way valve 30 connected to the vessel 21 is integrally stored in a body 40 made of the same metal. As an example of the valve means 25, a solenoid valve, particularly a pilot solenoid valve is employed.

  The three-way valve 30 is formed from a differential pressure valve whose valve operation is switched in accordance with opening and closing of the valve means 25 composed of an electromagnetic valve. As will be described in detail later, when the valve means 25 composed of an electromagnetic valve is closed, the pressure of the pressure introduction passage 42 which is one pressure of the valve body of the three-way valve 30 and the other pressure of the valve body in the three-way valve 30 The valve body is driven in relation to the differential pressure and the spring force, and the three-way valve 30 operates.

  A valve means inlet side flow path 44 through which refrigerant from the indoor condenser 12 flows and a valve means outlet side flow path 45 through which refrigerant flows to the outdoor heat exchanger 21 are formed in the body 40. The valve means 25 is interposed between the valve means inlet side flow path 44 and the valve means outlet side flow path 45.

  The heating restrictor 26 is composed of a small-diameter channel that bridges between the valve unit inlet-side channel 44 and the valve unit outlet-side channel 45 without using the valve unit 25. The heating restrictor 26 composed of the small diameter channel is formed in the body 40 with a smaller diameter than the valve means inlet side channel 44 and the valve means outlet side channel 45.

  The body 40 has a common flow path 50 of the three-way valve 30 through which the refrigerant is guided from the valve means outlet side flow path 45 via the outdoor heat exchanger 21. A first switching channel 55 and a second switching channel 56 are provided in the same body 40 on one side and the other side of the common chamber 51 in the three-way valve 30 communicating with the common channel 50. A first switching pipe 55a and a second switching pipe 56a are connected to the first switching path 55 and the second switching path 56, respectively.

  FIG. 3 shows a refrigerant flow switching control valve 41 comprising a valve means 25 housed in the body 40 shown in FIG. 2, a heating throttle 26 (not visible in FIG. 3) forming a throttle means, and a three-way valve 30. It is a partial sectional view showing the concrete composition of.

  In FIG. 3, the valve means 25 is in particular a pilot type electromagnetic valve. The three-way valve 30 moves the common channel 50 between the first switching channel 55 and the second switching channel according to the movement of the reciprocating valve body 60 that reciprocates between the first switching channel 55 and the second switching channel 56. Communicate with one of the paths 56.

  The reciprocating valve body 60 is configured such that the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 from the valve means inlet side passage 44 via the pressure introduction passage 42 and the pressure of the common chamber 51 communicating with the common passage 50. It reciprocates with the differential pressure. That is, the three-way valve 30 is composed of a differential pressure valve.

  The three-way valve 30 includes a differential pressure between the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 and the pressure of the common flow path 50 or the common chamber 51, and the spring housing chamber 62 on the other side of the reciprocating valve body 60. The reciprocating valve body 60 is reciprocated by the elastic force of a single coil spring 63 serving as a spring member provided on the reciprocating member.

  The starting end of the first switching channel 55 and the starting end of the second switching channel 56 exist in a direction orthogonal to the reciprocating motion direction of the reciprocating valve body 60. The reciprocating valve body 60 includes a pair of first reciprocating valve body portion 60a and second reciprocating valve body portion 60b, and a connecting member 60c comprising a connecting rod that bridges between the first and second reciprocating valve body portions 60a and 60b. It consists of and.

  A common chamber 51 that communicates with the common flow path 50 is formed with a first protrusion that forms a cylindrical first valve seat 65 and a second protrusion that forms a second valve seat 66. Due to the movement of the reciprocating valve body 60, the first reciprocating valve body portion 60a faces the first valve seat 65, the seal portion 60a1 of the first reciprocating valve body portion 60a is pressed against the first valve seat 65, and the common flow path 50 And the communication state between the first switching channel 55 and the first switching channel 55 can be blocked.

  On the other hand, the movement of the reciprocating valve body 60 causes the second reciprocating valve body portion 60b to face the second valve seat 66 as shown in FIG. 3, and the seal portion 60b1 of the second reciprocating valve body portion 60b is pressed against the second valve seat 66. Thus, the communication state between the common channel 50 and the second switching channel 56 can be blocked.

  As described above, the three-way valve 30 constituting the differential pressure valve moves to a predetermined position in accordance with ON / OFF of the valve means 25 formed of an electromagnetic valve, thereby switching between the cooling circuit and the heating circuit. A pair of poppet valve portions 60a, 60b, 65, 66 is constituted by the first reciprocating valve body portion 60a, the second reciprocating valve body portion 60b, the first valve seat 65, and the second valve seat 66 of the reciprocating valve body 60. Yes.

  The pair of poppet valve portions 60a, 60b, 65, 66 is a connecting rod that constitutes the connecting member 60c fixed to one of the pair of poppet valve portions 60a, 60b, 65, 66. However, since the other poppet valve portions 60b and 66 are inserted, the one and the other poppet valve portions are connected to each other via the connecting member 60c.

  By using the pair of poppet valve portions 60a, 60b, 65, 66 in this way, a flow path with a large opening area can be opened and closed even when the reciprocating valve body 60 has a small sliding distance, and the valve can be downsized. It becomes possible. Moreover, since a high sealing performance can be ensured, the refrigerant does not leak into the unselected flow path.

  In FIG. 2, the outdoor heat exchanger 21 and the body 40 are connected via a first joint portion 71 and a second joint portion 72. The valve means inlet side flow path 44 in the body 40 and the valve means inlet pipe 44 a as the refrigerant pipe are connected by a third joint portion 73.

  Further, the first switching flow passage 55 in the body 40 and the first switching piping 55 a as the refrigerant piping are connected by a fourth joint portion 74. The second switching flow path 56 in the body 40 and the second switching pipe 56 a as the refrigerant pipe are connected by a fifth joint portion 75.

  As described above, the body 40 is provided with the five joint portions (piping connection ports) 71, 72, 73, 74, 75, and is roughly divided into the joint portion 71 of the valve means 25 portion comprising the upper electromagnetic valve, 73 and joint portions 72, 74, 75 of the lower three-way valve 30 portion.

  FIG. 4 is a partial cross-sectional view showing a specific configuration in a state where the refrigerant flow path switching control valve 41 in FIG. 3 blocks the common flow path 50 and the first switching flow path 55. In FIG. 4, the valve means 25 comprising an electromagnetic valve is OFF (closed).

  When the valve means 25 composed of an electromagnetic valve is turned off (closed), the pressure on the downstream side (secondary side) of the valve means 25 decreases, and the pressure in the pressure chamber 61 and the pressure in the common chamber 51 flowing through the pressure introduction path 42. The first reciprocating valve body portion 60a abuts on the first valve seat 65 and the communication state between the common flow path 50 and the first switching flow path 55 is shut off. On the other hand, the second reciprocating valve body 60 b is separated from the second valve seat 66 to form a communication state between the common flow path 50 and the second switching flow path 56.

  In FIG. 4, the refrigerant that has entered the valve means 25 comprising the electromagnetic valve from the valve means inlet-side flow path 44 passes through the valve means outlet-side flow path 45 in the body 40 and passes through the first joint portion 71 of FIG. It flows into the outdoor heat exchanger 21. FIG. 5 is a right side view of the refrigerant flow path switching control valve 41 of FIG. As shown in FIG. 5, a heating throttle 26 is provided as a throttle means provided in parallel with the valve means 25 between the outdoor heat exchanger 21 and the indoor condenser 12 in FIG. 2.

  The heating restrictor 26 is formed of a small-diameter channel through which a minute amount of refrigerant flows even if the valve means 25 composed of an electromagnetic valve is completely closed. As shown in FIG. 5, the small-diameter flow path forming the heating restrictor 26 is formed in the body 40, and bypasses the refrigerant leaking from the upstream side of the valve seat of the valve means 25 made of an electromagnetic valve to the valve means outlet-side flow path 45 side. This constitutes a gap flow path.

  Further, as shown in FIG. 5, the body 40 is provided with a first joint portion 71 and a second joint portion 72, and the first joint portion 71 and the second joint portion 72 are provided with FIG. 2. As shown in FIG. 2, the outdoor heat exchanger 21 is directly attached without a pipe.

  That is, only the female joint is shown in the first joint portion 71 and the second joint portion 72 in FIG. 5, but a male joint (not shown) integrated with the outdoor heat exchanger 21 is directly connected to the female joint. Combined. This reduces the number of pipes.

  The operation of the above embodiment will be described below. The flow of the refrigerant will be described for each of cooling and heating.

<When cooling>
In FIG. 2, the high-temperature and high-pressure refrigerant discharged from the compressor 20 flows into the indoor condenser 12. However, since the air mix damper 16 in the duct 1 constituting the HVAC is held at the MAX COOL position, which is the position of the broken line, heat exchange between the air in the duct 1 and the indoor condenser 12 is not performed.

  The refrigerant from the indoor condenser 12 flows into the pipe connection port forming the third joint portion 73 of the refrigerant flow switching control valve 41 forming the integrated valve. Since the valve means 25 is driven by a signal from a control circuit (not shown) so that the valve means 25 composed of an electromagnetic valve is opened during cooling, the refrigerant remains in the first joint from the valve means outlet side flow path 45 as a high-temperature and high-pressure refrigerant. It passes through the section 71 and flows into the outdoor heat exchanger 21.

The high-pressure liquid refrigerant condensed in the outdoor heat exchanger 21 flows into the refrigerant flow switching control valve 41 from the second joint portion 72 again. Here, a rightward force F1 = S1 (P1-P2) and a leftward force F2 = kΔX are applied to the reciprocating valve body 60 of the three-way valve 30 including the differential pressure valve in FIG.
(S1: pressure receiving area of the reciprocating valve body 60, P1: pressure per unit area applied to the left side of the first reciprocating valve body part 60a, P2: per unit area applied to the right side of the first reciprocating valve body part 60a Pressure, k: spring constant of the coil spring 63, and ΔX: deflection length of the coil spring 63). The second reciprocating valve body 60b is provided with a pressure equalizing hole 67 which will be described later, so that the pressure applied from the left and right sides of the second reciprocating valve body 60b is substantially equal.

  Here, since the coil spring 63 is selected so that F1 <F2 when the valve means 25 composed of the electromagnetic valve is open as described above, the reciprocating valve body 60 has a left side as shown in FIG. Has moved to.

  Therefore, the high-pressure liquid refrigerant flowing from the outdoor heat exchanger 21 in FIG. 2 to the common flow path 50 in FIG. 3 passes through the first switching flow path 55 and the first switching pipe 55a in FIG. 2 as indicated by an arrow Y3. And flows to the cooling diaphragm 31.

  The low-pressure two-phase refrigerant depressurized by the cooling throttle 31 including the fixed throttle evaporates in the indoor evaporator 11. The refrigerant that has passed through the indoor evaporator 11 flows from the accumulator 35 to the compressor 20.

<When heating>
The high-temperature and high-pressure refrigerant discharged from the compressor 20 flows into the indoor condenser 12. The heat of the indoor condenser 12 exchanges heat with the blower air from the blower 4. The refrigerant from the indoor condenser 12 flows into the pipe connection port forming the third joint portion 73 of the refrigerant flow switching control valve 41 including the integrated valve in FIG.

  During heating, the valve means 25 is controlled by a control signal from a control device (not shown) so that the valve means 25 comprising an electromagnetic valve is closed, so that the refrigerant is decompressed by the heating throttle 26 and becomes a low-pressure two-layer refrigerant. , Flows through the first joint portion 71 and flows into the outdoor heat exchanger 21. Then, the low-pressure gas refrigerant evaporated in the outdoor heat exchanger 21 flows again into the refrigerant flow switching control valve 41 including an integrated valve from the second joint portion 72.

  As described above, when the valve means 25 made of an electromagnetic valve is closed, the pressure on the downstream side of the valve means 25 in FIG. 4 decreases, and the unit area applied to the left side of the first reciprocating valve body 60a is reduced. The pressure difference between the pressure P1 and the pressure P2 per unit area applied to the right side of the first reciprocating valve body 60a is the rightward force F1> the leftward force F2, and the reciprocating valve body 60 moves to the right.

  Therefore, the low-pressure gas refrigerant flowing from the outdoor heat exchanger 21 in FIG. 2 passes through the second switching channel 56 and the second switching pipe 56a in FIG. 2 from the common channel 50 in FIG. It flows from the accumulator 35 to the compressor 20.

  As described above, it is possible to switch between the cooling circuit and the heating circuit by the control signal to the valve means 25 composed of one electromagnetic valve. The three-way valve 30 composed of a differential pressure valve has two poppet valve portions (first reciprocating valve body portion 60a, second reciprocating valve body portion 60b, connecting member 60c, first valve seat 65, and second valve seat 66 in FIG. 4). With this configuration, even when the slide distance of the reciprocating valve body 60 (stroke through which the valve body moves) is small, opening and closing can be performed with a large channel opening area. Therefore, in the first embodiment, the body 40 of the refrigerant flow switching control valve 41 including an integrated valve can be made smaller than the embodiment using a spool valve described later. Next, the dimensions and structure of each part will be further described.

(1) Integration of heating throttle As shown in FIG. 5, a heating throttle 26 comprising a small-diameter channel having a diameter of 0.8 mm to 1.0 mm is provided in the body 40 outside the valve means 25 consisting of an electromagnetic valve. It is composed. During the heating, when the valve means 25 comprising the electromagnetic valve serving as the main valve is closed, the refrigerant is depressurized by the heating throttle 26 and flows from the valve means outlet side flow path 45 to the outdoor heat exchanger 21. By integrating the heating restrictor 26 into the body 40, the number of pipe connections is reduced, and the system can be simplified and the cost can be reduced.

(2) Structure in which refrigerant flow path switching control valve is directly attached to the outdoor heat exchanger As shown in FIGS. 2 and 5, the body 40 is provided with a first joint portion 71 and a second joint portion 72. The first joint part 71 and the second joint part 72 form the valve means outlet side flow path 45 and the common flow path 50 in FIG. 5 in a pair of male joints (not shown) integral with the outdoor heat exchanger 21. A pair of female joints are combined to integrate the body 40 and the outdoor heat exchanger 21.

  With this structure, space saving and connection piping can be reduced. The male joint is fitted and joined to the female joint, and the fitting portion is sealed with an O-ring.

(3) Regarding the structure of the slide valve portion (a pair of poppet valve portions) As shown in FIG. 3, for example, the first and second valve seats 65, 66 and the first, The second reciprocating valve body portions 60a and 60b are arranged to form a cylindrical common chamber 51 in which the first and second reciprocating valve body portions 60a and 60b slide. A first switching passage 55 and a second switching passage 56 serving as a refrigerant passage are provided from the common chamber 51 to the outside of the body 40.

  6 is a partial cross-sectional view taken along line Z6-Z6 in FIG. 3, and FIG. 7 is a partial cross-sectional view taken along line Z7-Z7 in FIG. As can be understood from FIGS. 6 and 7, a cylindrical first valve seat 65 and a second valve seat 66 are provided in the common chamber 51, and the first valve seat 65 and the second valve seat 66 are provided in the common chamber 51. The connecting member 60c extends. Further, the common flow path 50 communicating with the common chamber 51, the first switching flow path 55, and the second switching flow path 56 are rotated by 90 degrees.

  In the reciprocating valve body 60 having the first and second reciprocating valve body portions 60a and 60b in FIG. 3, the second reciprocating valve body portion 60b is closed with respect to the second valve seat 66 by a coil spring 63 serving as a spring member. Although force is generated in the direction, the spring force of the coil spring 63 can be easily changed by the adjusting screw 64.

(4) Structure in which the pressure equalizing hole 67 made of a minute through hole is formed in the second reciprocating valve body 60b The refrigerant is pushed into the spring housing chamber 62 where the coil spring 63 exists by the pressure equalizing hole 67 made of the minute through hole. The valve operation, which is the operation of the reciprocating valve body 60, is prevented from becoming unstable due to an increase in the internal pressure of the spring storage chamber 62.

  In addition, when the valve means 25 composed of an electromagnetic valve is switched from OFF to ON, vibration and noise due to switching of the valve operation, which is the operation of the reciprocating valve body 60 forming the differential pressure valve, can be reduced. The reciprocating valve body 60 is provided with valve seat seal portions 60a1 and 60b1 and piston rings 60a2 and 60b2.

  Further, the reciprocating valve body 60 constituting the movable valve body is mainly composed of two parts, a first reciprocating valve body 60a and a second reciprocating valve body 60b, and a connecting member 60c made of a rod is an integral part of one valve body 60a. The other valve body 60b employs a structure in which a hole for receiving the connecting member 60c is provided. With this shape, the first and second reciprocating valve bodies 60a and 60b and the connecting member 60c, which are components of the differential pressure valve, can be inserted into the body 40.

  As described above, the refrigerant flow path switching control valve 41 serving as an integrated valve in this embodiment selects the flow path to the outdoor heat exchanger 21 (passes through the valve means 25 including a large-diameter electromagnetic valve or performs heating. Selection of whether or not to pass through the throttle 26 and the selection of the flow path on the outlet side of the outdoor heat exchanger 21 (cooling and flow path from the cooling throttle 31 to the indoor evaporator 11 or during heating) And the operation of selecting the flow path to the accumulator 35) is incorporated in the body 40 for a single valve.

  As described above, the refrigerant flow switching control valve 41 having the three-way valve 30 and the valve means 25 is housed in the same body 40 and integrated into an integrated valve. And branching is reduced. For this reason, the structure of the system is simplified, and cost reduction and space saving can be achieved.

  There are two types of solenoid valves, the direct acting type and the pilot type. In the direct acting type, the operation is switched only by the attractive force of the electromagnet, but the drive current is large because the large valve is moved against the spring. Thus, instead of a direct-acting solenoid valve that opens and closes the refrigerant passage by the electromagnetic force of the solenoid directly, an opening and closing state of a small passage called a pilot passage is switched by the electromagnetic force of the solenoid, whereby a large valve body for opening and closing the refrigerant passage A pilot-type solenoid valve for driving is well known.

  In this embodiment, a pilot type electromagnetic valve is used as the valve means 25 composed of an electromagnetic valve. By doing so, the valve means 25 can be reduced in size. Examples of this pilot type solenoid valve are disclosed in Japanese Patent Laid-Open Nos. 2003-254467 and 9-264449.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. In the following embodiments, the same components as those in the first embodiment described above are denoted by the same reference numerals, description thereof will be omitted, and different configurations and features will be described.

  FIG. 8 is a partial cross-sectional view showing a specific configuration of the refrigerant flow switching control valve 41 that employs a spool valve as the three-way valve 30 showing the second embodiment of the present invention. In FIG. 8, 25 is a pilot type solenoid valve which constitutes valve means.

  In response to the movement of the reciprocating valve body 60 that reciprocates between the first switching channel 55 and the second switching channel 56, the three-way valve 30 is connected to the common channel 50 from the outdoor heat exchanger 21 in FIG. The refrigerant is communicated with either the first switching channel 55 or the second switching channel 56.

  The difference between the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 via the pressure introduction path 42 from the valve means inlet side flow path 44 of FIG. 8 and the pressure of the common chamber 51 communicating with the common flow path 50. The reciprocating valve body 60 reciprocates using the pressure. That is, the three-way valve 30 is composed of a differential pressure valve.

  The three-way valve 30 is a reciprocating valve based on the differential pressure between the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 and the pressure in the common chamber 51 and the elastic force of a single coil spring 63 serving as a spring member. The body 60 reciprocates.

  The starting end of the first switching channel 55 and the starting end of the second switching channel 56 exist in a direction orthogonal to the reciprocating motion direction of the reciprocating valve body 60. The reciprocating valve body 60 includes a pair of first reciprocating valve body 60a and second reciprocating valve body 60b, and a connecting member 60c that bridges the first and second reciprocating valve bodies 60a and 60b. ing.

  The connecting member 60c is formed by cutting a part of the outer periphery of the cylindrical valve body, and the refrigerant flowing from the outdoor heat exchanger 21 through the common flow path 50 is connected to the inside of the common chamber 51 that also serves as the spring storage chamber and the second member. It consists of the part which passed the inside of 2 reciprocating valve body part 60b, and was able to blow out a refrigerant | coolant to all directions.

  In FIG. 8, the movement of the reciprocating valve body 60 causes the second reciprocating valve body portion 60 b to face the second switching flow path 56 and close the second switching flow path 56. At this time, the first reciprocating valve body 60a does not block the first switching flow path 55, and the refrigerant from the common flow path 50 flows through the first switching flow path 55 as indicated by an arrow Y8.

  FIG. 9 is a partial cross-sectional view showing a specific configuration of the refrigerant flow switching control valve 41 that employs a spool valve showing a state in which the reciprocating valve body 60 has moved rightward from the state of FIG.

  In this way, the valve means 25 composed of an electromagnetic valve is closed, the pressure on the downstream side of the valve means 25 decreases, and the second reciprocating valve body portion 60b is moved by the reciprocating valve body 60 moving in the right direction in FIG. Opens the second switching channel 56 and the first reciprocating valve body 60a closes the first switching channel 55, the common channel 50 and the first switching channel 55 from the outdoor heat exchanger 21 of FIG. And the common flow path 50 and the second switching flow path 56 communicate with each other.

  As described above, the reciprocating valve body 60 constituting the spool valve of the three-way valve 30 constituting the differential pressure valve moves to a predetermined position in accordance with ON / OFF of the valve means 25 composed of an electromagnetic valve, so that the cooling circuit and the heating circuit Switch to

(Third embodiment)
Next, a third embodiment of the present invention will be described. In the following embodiments, the same components as those in the first embodiment described above are denoted by the same reference numerals, description thereof will be omitted, and different configurations and features will be described.

  FIG. 10 shows a third embodiment of the present invention. In the third embodiment, an electric valve is employed as the valve means. FIG. 10 is a partial cross-sectional view showing the specific configuration of the refrigerant flow switching control valve 41 when the motor-operated valve is fully opened. FIG. 11 is a partial cross-sectional view showing a state in which the motor-operated valve of FIG. 10 is closed leaving a leak passage having a minute opening. 10 and 11, reference numeral 25 denotes a motor-operated valve that serves as valve means, and employs a step motor for the motor portion.

  From the valve means inlet side passage 44, for example, a refrigerant having a pressure of about 1.7 MPa is guided into the refrigerant flow switching control valve 41. Between the valve means inlet side passage 44 and the valve means outlet side flow path 45 toward the outdoor heat exchanger 21 in FIG. 2, the valve body and valve seat of the valve means 25 comprising an electric valve for opening and closing the refrigerant passage are provided. Have.

  The stroke of the movement of the valve body is controlled by the rotation angle of the step motor in the valve means 25 comprising an electric valve. Therefore, the valve body and the valve seat of the valve means 25 composed of a motorized valve form a variable stroke valve, and the opening degree of the motorized valve constituting the valve means 25 can be set to an ideal point corresponding to the operating state of the refrigeration cycle. .

  FIG. 11 shows a state in which the valve body of the valve means 25 is stopped at a position close to the valve seat until the refrigerant flow switching control valve 41 employing the valve means 25 comprising the motorized valve of FIG. FIG. The valve means 25 comprising this electric valve is also called an electronic expansion valve with a fully open function, and has a diameter of about 10 mm as a valve diameter through which the refrigerant flows.

  The valve means 25 comprising this electric valve is fully opened as shown in FIG. 10 during cooling, and allows the refrigerant from the indoor condenser 12 shown in FIG. 2 to flow to the outdoor heat exchanger 21 with a minimum pressure drop. At this time, the pressure on the downstream side of the valve means 25 increases. On the other hand, the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 from the valve means inlet side flow path 44 via the pressure introduction path 42 does not change much when the valve means 25 is opened and closed.

  Further, the set pressure of the coil spring 63 that constitutes the spring means is set in the vicinity of 0.3 to 0.2 MPa. For this reason, the reciprocating valve body 60 moves to the left as shown in FIG. Thus, the refrigerant that has passed through the outdoor heat exchanger 21 in FIG. 2 flows through the first switching flow path 55 and travels toward the indoor evaporator 11 in FIG. 2.

  On the other hand, during heating, the valve means 25 composed of an electric valve is configured such that the internal step motor adjusts the valve opening to a very small opening and decompresses the high-pressure refrigerant from the indoor condenser 12 in FIG. To the outdoor heat exchanger 21.

  In this state, as shown in FIG. 11, the heating restrictor 26 is formed from the leakage flow path when the valve means 25 including the motor-operated valve is closed. That is, in FIG. 11, the valve body of the valve means 25 composed of an electric valve does not completely contact the valve seat and stops at an approached position, so that a leakage passage similar to the small-diameter flow path forming the heating throttle 26 is formed. It can be formed.

  When the valve means 25 composed of an electric valve is closed while leaving a leak passage similar to the small-diameter flow path forming the heating restrictor 26, the pressure on the downstream side of the valve means 25 composed of the electric valve decreases. The three-way valve 30 comprising the differential pressure valve at this time communicates with the pressure introduced into the pressure chamber 61 on one side of the reciprocating valve body 60 from the valve means inlet side passage 44 via the pressure introduction passage 42 and the common passage 50. The differential pressure from the pressure of the common chamber 51 increases.

  Therefore, the reciprocating valve body 60 moves to the right. Thus, the refrigerant that has passed through the outdoor heat exchanger 21 in FIG. 2 flows through the common chamber 51 and the second switching channel 56 that communicate with the common channel 50, and travels from the second switching pipe 56 a in FIG. 2 to the accumulator 35.

  As described above, the motor-operated valve constituting the valve means 25 that closes the minute gap constituting the heating throttle 26 can adjust the opening of the valve, which is the size of the minute gap. Further, since the opening degree of the valve, which is the size of the minute gap, can be adjusted, the heating throttle 26 can be set to an opening degree suitable for the operating state of the refrigerant cycle by an electric valve constituting the valve means 25.

  For this reason, the heating throttle 26 can be configured as a variable throttle. In this way, by providing a structure that can control the size of the minute gap of the heating throttle 26 to an optimum value according to various operating conditions, air conditioning can be performed as compared with the fixed heating throttle as in the first and second embodiments. Performance can be improved.

  The vehicle air conditioner has a large heating load when the vehicle interior temperature is considerably lower than the set temperature and the deviation between the vehicle interior temperature and the set temperature is large. In the fixed heating restrictor, when the heating load is high, the minute gap is too small, the subcooling in the indoor condenser 12 becomes maximum, the required input of the air conditioner increases, and the energy efficiency deteriorates.

  On the other hand, when the heating load is low, in the case of the fixed heating throttle, the minute gap is too large, and the refrigerant cannot be sufficiently evaporated by the outdoor heat exchanger, so that the refrigerant accumulates in the accumulator 35. Problems such as performance degradation due to the subcool being minimized. However, such a problem can be solved and the air conditioning performance can be improved by configuring the heating throttle 26 as a variable throttle as described above.

(Other embodiments)
The present invention is not limited to the above-described embodiments, and can be modified or expanded as follows. FIG. 12 is a schematic view schematically showing a main part of a three-way valve showing another embodiment.

  In FIG. 12, one end side of a connecting member 60c composed of a connecting rod that bridges between the first and second reciprocating valve body portions 60a and 60b is manufactured from a material integral with the first reciprocating valve body portion 60a, and is a stopper. The part 60d is also integrally formed.

  The stopper 60d limits the movement of the first reciprocating valve body 60a so that the first reciprocating valve body 60a does not go too far to the left and close the outlet of the pressure introduction path 42. In this case, the first reciprocating valve body 60a is located at the position (a) in FIG. 12 during cooling.

  Even if the first reciprocating valve body 60a moves to the leftmost side during cooling, the other end of the connecting member 60c is a hole in the second reciprocating valve body 60b as shown in FIG. 12 (b). The stopper portion 60d limits the movement of the first reciprocating valve body portion 60a so that the outlet of the pressure introduction path 42 is not closed.

  Next, during heating, the first reciprocating valve body 60a abuts on the first valve seat 65 and the second reciprocating valve body 60b is moved from the second valve seat 66 as shown in FIG. Separate. This separation dimension Ls may be about 3 mm to 4 mm.

  Next, in FIGS. 5 to 7, the first switching channel 55 and the second switching channel 56 that form the refrigerant passage are configured to extend downward in the figure. Centering on the center of the connecting member 60c in FIG. 7, the first switching channel 55 and the second switching channel 56 are rotated counterclockwise in FIG. 6 and clockwise in FIG. May be extended.

  Next, as described in FIG. 5 showing the first embodiment, the body 40 is provided with the first joint portion 71 and the second joint portion 72, and the first joint portion 71 and the second joint portion 72 are provided. The outdoor heat exchanger 21 is coupled by a direct mounting structure without a pipe.

  FIG. 13 is a side view showing another embodiment of the direct mounting structure and showing a coupling state between the outdoor heat exchanger 21 and the refrigerant flow switching control valve 41. That is, FIG. 13 shows the refrigerant flow switching control valve 41 and the outdoor heat exchange in a state where the refrigerant flow switching control valve 41 is coupled to the outdoor heat exchanger 21 via the first joint portion 71 and the second joint portion 72. FIG.

  The female joints 23f, 24f are joined to the male joints 23m, 24m welded or brazed to the inlet and outlet of the outdoor heat exchanger 21, and are screwed with the through bolts 22 for attachment. With this structure, space saving and connection piping can be reduced. The male joints 23m and 24m are fitted and joined to the female joints 23f and 24f, and the fitting portions are sealed with O-rings. By adopting such a structure, the number of pipes can be reduced.

DESCRIPTION OF SYMBOLS 1 Duct 11 Indoor evaporator 12 Indoor condenser 11, 12 Indoor heat exchanger 15 Bypass passage 16 Air mix damper 20 Compressor 21 Outdoor heat exchanger 23m, 24m Male joint 23f, 24f Female joint 25 Valve means 26 For heating Restrictor 30 Three-way valve 31 Cooling restrictor 35 Accumulator 40 Body 41 Refrigerant flow path switching control valve 42 Pressure introduction path 44 Valve means inlet side flow path 45 Valve means outlet side flow path 50 Common flow path 51 Common chamber 55 First switching flow path 56 2nd switching flow path 55a 1st switching piping 56a 2nd switching piping 60 Reciprocating valve body 61 Pressure chamber 62 Spring storage chamber 63 Coil spring 60a 1st reciprocating valve body 60a, 60b, 65, 66 A pair of poppet valve 60a , 65 One poppet valve portion 60b, 66 The other poppet valve portion 60b Second reciprocating valve Parts 60c connecting member 60d stopper 64 adjustment screw 65 fourth joint portion 75 fifth joint portion first valve seat 66 second valve seat 67 pressure equalizing hole 71 first joint portion 72 second joint 73 third joint portion 74

Claims (13)

The air conditioning duct (1) includes an indoor evaporator (11) and an indoor condenser (12), and the indoor evaporator (11), the indoor condenser (12), and an outdoor heat exchanger (21). A vehicle air conditioner that performs heat exchange by a heat pump cycle in which the refrigerant from the compressor (20) flows through
Valve means (25) provided between the inlet side of the outdoor heat exchanger (21) and the indoor condenser (12),
The heating throttle means (26) provided with a flow path for narrowing the flow of the refrigerant in parallel with the refrigerant flow path opened and closed by the valve means (25),
A three-way valve (30) provided with a common flow path (50) communicating with the outlet side of the outdoor heat exchanger (21),
The refrigerant from the common flow path (50) flows through the three-way valve (30) during cooling operation, the first switching flow path (55), and the refrigerant from the common flow path (50) A second switching channel (56) that flows through the three-way valve (30) during heating operation;
At least a part of the valve means (25), the heating throttle means (26), the three-way valve (30), the first switching flow path (55), and the second switching flow path (56) are disposed in the body. (40) A vehicle air conditioner comprising a refrigerant flow switching control valve (41) housed in an integrated valve.   2. The vehicle air conditioner according to claim 1, wherein the three-way valve (30) is a differential pressure valve whose valve operation is switched when the pressure changes with the opening and closing of the valve means (25).   The connection between the body (40) and the outdoor heat exchanger (21) is performed by fitting a connection portion mounted on the outdoor heat exchanger (21) and a connection portion provided on the body (40) side into an uneven shape. The first joint portion (71) on the inlet side of the outdoor heat exchanger (21) formed by combining the second joint portion (72) on the outlet side of the outdoor heat exchanger (21), The first joint part (71) is provided on the valve means (25) side, and the second joint part (72) is provided on the common flow path (50) side. The vehicle air conditioner according to 2. Valve means inlet side flow path (44) through which the refrigerant from the indoor condenser (12) flows into the body (40), and valve means outlet side flow path through which the refrigerant flows into the outdoor heat exchanger (21). (45) is formed,
The valve means (25) is interposed between the valve means inlet side flow path (44) and the valve means outlet side flow path (45),
The body (40) has the common channel (50) through which the refrigerant is guided from the valve means outlet side channel (45) via the outdoor heat exchanger (21),
The first channel connecting the common channel (50) and the indoor evaporator (11) side to one side of the common chamber (51) in the three-way valve (30) communicating with the common channel (50). It has a switching flow path (55), and has the 2nd switching flow path (56) which constitutes the flow path of the refrigerant which returns to the compressor (20) side on the other side of the common room (51). The vehicle air conditioner according to any one of claims 1 to 3. The three-way valve (30) has a reciprocating valve body (60) that reciprocates between the first switching channel (55) and the second switching channel (56),
Depending on the movement of the reciprocating valve body (60), the three-way valve (30) moves the common flow path (50) between the first switching flow path (55) and the second switching flow path (56). Communicate with
The three-way valve (30) includes the pressure introduced from the valve means inlet side flow path (44) to one side of the reciprocating valve body (60) via the pressure introduction path (42) and the common flow path (50). The vehicle air conditioner according to claim 4, comprising a differential pressure valve that reciprocates at a pressure difference from the pressure of (5).   The pressure introduced from the valve means inlet side flow path (44) to one side of the reciprocating valve body (60) is introduced through the pressure introduction path (42) formed in the body (40). The vehicle air conditioner according to claim 5.   The three-way valve (30) has a differential pressure between the pressure introduced to one side of the reciprocating valve body (60) and the pressure of the common flow path (50), and the other side of the reciprocating valve body (60). Due to the elastic force of the provided spring member (63), the reciprocating valve body (60) reciprocates, whereby a part of the reciprocating valve body (60) becomes a first valve seat (65) and a second valve seat ( 66. The vehicular air conditioner according to claim 6, further comprising a pair of poppet valve portions that abut against the inner wall 66).   The pair of poppet valve portions includes one of the pair of poppet valve portions, and a connecting member (60c) having one end fixed to the one poppet valve portion, and the pair of poppet valves. The other end of the connecting member (60c) is inserted into the other poppet valve portion of the valve portions, and the pair of poppet valve portions are interlocked in at least a predetermined direction via the connecting member (60c). The vehicle air conditioner according to claim 7.   The heating throttle means (26) is composed of a small diameter channel formed in parallel with the valve means (25), and the narrow diameter channel is smaller in diameter than the channel through which the refrigerant flows in the valve means. The vehicle air conditioner according to any one of claims 1 to 8, characterized by comprising a flow path formed in the body (40).   The heating throttle means (26) provided with a flow path for restricting the flow of the refrigerant in parallel with the refrigerant flow path opened and closed by the valve means (25) is configured to completely connect the valve means (25). The vehicle according to any one of claims 1 to 8, characterized in that the valve means (25) which closes the valve without closing the valve and closes the valve is operated to close the valve. Air conditioner.   11. The vehicle according to claim 10, wherein the valve means for closing the valve while leaving the minute gap includes valve means for adjusting an opening degree of the valve after the valve closing, which is the size of the minute gap. Air conditioner.   The vehicle air conditioner according to claim 11, wherein the valve means (25) capable of adjusting the opening degree of the valve after the valve closing operation comprises an electric valve.   The heat pump cycle further includes an accumulator (35), a cooling throttle (31), a first switching pipe (55a), and a second switching pipe (56a), and the refrigerant from the common flow path (50). The first switching channel (55) that flows during the cooling operation causes the refrigerant to flow to the indoor evaporator (11) through the first switching pipe (55a) and the cooling throttle (31), thereby heating operation. The second switching flow path (56) for flowing the refrigerant sometimes returns the refrigerant to the compressor (20) via the second switching pipe (56a) and the accumulator (35). Item 13. The vehicle air conditioner according to any one of Items 1 to 12.

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