JP2012086723A - Three-way valve and vehicular air conditioner using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a three-way valve enabling automatic switching of passages in a valve housing without using an electromagnetic force or the like.SOLUTION: A first equalizing chamber is formed on one axial end in the valve housing, a second equalizing chamber is formed on the other end, an energizing means for energizing a valve element in a closing direction of a passage running from an inlet port to a second outlet port is disposed within the first equalizing chamber, and an equalizing introduction passage for introducing part of a fluid flowing in from the inlet port is coupled to the second equalizing chamber, so that when the pressure of the fluid flowing in from the inlet port is lower than a predetermined pressure, a passage through which the fluid flowing in from the inlet port flows out from a first outlet port is formed in the valve housing, and when the pressure of the fluid flowing in from the inlet port is higher than the predetermined pressure, a passage through which the fluid flowing in from the inlet port flows out from the second outlet port is formed in the valve housing.

Description

  The present invention relates to a three-way valve and a vehicle air conditioner using the three-way valve, and more specifically, a three-way valve configured to automatically switch a flow path in a valve housing in accordance with a fluid pressure, and the three-way valve The present invention relates to a vehicle air conditioner using a valve.

  Conventionally, in an air conditioner for a vehicle such as an engine-equipped automobile, a vapor compression refrigeration cycle is used for the cooling system, and engine exhaust heat is used for the heating system. However, in recent years, along with the development and popularization of electric vehicles and the like that cannot use engine exhaust heat, a vehicle air conditioner that uses a vapor compression refrigeration cycle to cool and heat the vehicle has been developed. It has become widespread.

When air-conditioning is performed using a heat pump type air conditioner, in a general air-conditioning apparatus, switching between a cooling operation and a heating operation is performed by switching a refrigerant flow using a four-way valve.
However, in the case of a vehicle air conditioner such as an automobile, in order to avoid an increase in the size of the air conditioner, instead of using a four-way valve, an electromagnetic valve is disposed so as to bypass the expansion valve, and cooling is performed by opening and closing the electromagnetic valve. Switching between operation and heating operation is performed (for example, Patent Documents 1 and 2).

  FIG. 10 is a system configuration diagram showing a vehicle air conditioner 100 ′ in which an electromagnetic valve is disposed so as to bypass the expansion valve as disclosed in Patent Documents 1 and 2. In addition, the arrow H in the figure indicates the refrigerant flow during the heating operation, and the arrow C in the figure indicates the refrigerant flow during the cooling operation.

  As shown in FIG. 10, the vehicle air conditioner 100 ′ includes a refrigerant compressor 110 that sucks and compresses a refrigerant, a heating heat exchanger 120 connected to the downstream side of the refrigerant compressor 110, The outdoor heat exchanger 140 connected to the downstream side of the heating heat exchanger 120 and the cooling heat exchanger 130 connected to the downstream side of the outdoor heat exchanger 140 are connected in a ring shape. ing.

  A first expansion valve 150a is arranged between the heating heat exchanger 120 and the outdoor heat exchanger 140, and a bypass flow formed so as to bypass the first expansion valve 150a. A first electromagnetic valve 160a is disposed in the path 162.

  Further, a branch point A where the flow path branches into two is formed downstream of the outdoor heat exchanger 140. A second electromagnetic valve 160b is disposed in the flow path 164 on the downstream side of the branch point A, and is connected to the refrigerant compressor 110 downstream of the second electromagnetic valve 160b. . Further, a third electromagnetic valve 160c and a second expansion valve 150b are disposed in the other flow path 166 downstream of the branch point A, and the cooling heat is downstream of the second expansion valve 150b. Connected to the exchanger 130. The other channel 166 is connected to the channel 166 at a junction B downstream of the cooling heat exchanger 130.

  The high-pressure refrigerant discharged from the refrigerant compressor 110 first flows into the heating heat exchanger 120. At this time, during the heating operation, heat exchange with indoor air blown by a fan (not shown) and passing through the heat exchanger for heating 120 causes heat to flow in the refrigerant flowing in and heat the air passing therethrough. It has become. And as shown in FIG. 10, the heated air flows in into a room | chamber interior from the open door 122 (code | symbol 122H). On the other hand, during the cooling operation, the door 122 is closed (reference numeral 122C) and the above-described fan (not shown) is stopped so that heat is not exchanged between the refrigerant and the indoor air.

  The high-pressure refrigerant that has passed through the heating heat exchanger 120 then flows into the outdoor heat exchanger 140. At this time, the first electromagnetic valve 160a is closed during the heating operation, and the high-pressure refrigerant passes through the first expansion valve 150a. Then, the high-pressure refrigerant that has passed through the first expansion valve 150 a is decompressed and expanded here, becomes low-pressure refrigerant, and flows into the outdoor heat exchanger 140. Then, heat exchange is performed between the inflowing low-pressure refrigerant and the outdoor air, so that the inflowing low-pressure refrigerant absorbs heat and is heated.

  On the other hand, the first electromagnetic valve 160a is opened during the cooling operation, and the high-pressure refrigerant that has passed through the first electromagnetic valve 160a flows into the outdoor heat exchanger 140 without being decompressed and expanded. Then, heat exchange is performed between the inflowing high-pressure refrigerant and the outdoor air, so that the inflowing high-pressure refrigerant dissipates heat and is cooled.

  The refrigerant that has passed through the outdoor heat exchanger 140 then flows into the branch point A via the flow path 168. As described above, the low-pressure refrigerant flows into the branch point A during the heating operation, and the high-pressure refrigerant flows during the cooling operation. At this time, during the heating operation, the second electromagnetic valve 160b is opened and the third electromagnetic valve 160c is closed, so that the low-pressure refrigerant flowing into the branch point A flows on one side. It flows through the path 164 and flows into the refrigerant compressor 110. On the other hand, during the cooling operation, the second electromagnetic valve 160b is closed and the third electromagnetic valve 160c is opened, so that the high-pressure refrigerant that has flowed into the branch point A flows through the flow path on the other side. It flows through 166 and passes through the second expansion valve 150b, where it is decompressed and expanded to become a low-pressure refrigerant and flows into the cooling heat exchanger 130. Then, heat exchange is performed between the inflowing low-pressure refrigerant and the indoor air, so that the inflowing low-pressure refrigerant absorbs heat and the indoor air is cooled. The low-pressure refrigerant that has passed through the cooling heat exchanger 130 flows into the flow path 164 on one side at the junction B, and flows into the refrigerant compressor 110.

  As described above, in the vehicle air conditioner 100 ′ in which the electromagnetic valve 160 a is arranged so as to bypass the first expansion valve 150 a instead of using the four-way valve, the heating is performed like the branch point A described above. There is a branch point configured to flow the low-pressure refrigerant flowing in to the one-side flow path 164 during the operation and to flow the high-pressure refrigerant flowing in to the other-side flow path 166 during the cooling operation. In the vehicle air conditioner 100 ′ shown in FIG. 10, as described above, the switching of the refrigerant flow path at the branch point A is performed by connecting the two solenoid valves, the second solenoid valve 160 b and the third solenoid valve 160 c. It is done by opening and closing.

  However, switching the refrigerant flow path at the branch point A with two solenoid valves not only complicates the system but also hinders the downsizing of the air conditioner. Under such a background, Patent Document 3 discloses a three-way valve that can be suitably used for switching the refrigerant flow path at the branch point A described above.

  The three-way valve of Patent Document 3 moves the valve body by electromagnetic force so that when the refrigerant flowing in is a low-pressure refrigerant, the low-pressure refrigerant flowing from the inlet port flows out from the first outlet port and flows in. When the refrigerant to be performed is a high-pressure refrigerant, the high-pressure refrigerant that has flowed from the inlet port is configured to flow out from the second outlet port. Therefore, the three-way valve of Patent Document 3 is arranged at the branch point A described above, the first outlet port is connected to the one-side flow path 164, and the second outlet port is connected to the other-side flow path 166. Thus, the refrigerant flow path at the branch point A described above can be switched.

JP 2000-16072 A JP 2004-142646 A Japanese Patent Laid-Open No. 2006-97761

  However, although the three-way valve of Patent Document 3 switches the flow path in the valve housing by electromagnetic force, it is required to suppress power consumption as much as possible in an electric vehicle or the like. Therefore, it has been desired to develop a three-way valve that can automatically switch the flow path in the valve housing without using electromagnetic force.

Further, in the three-way valve of Patent Document 3, since it is necessary to provide an electromagnetic part or the like that is a magnetic driving means, the cost is increased and it is difficult to reduce the size.
The present invention has been made in view of the above problems, and a three-way valve capable of automatically switching a flow path in a valve housing without using electromagnetic force or the like, and a vehicle using the three-way valve The purpose is to provide an air conditioner for a vehicle.

The present invention has been invented to achieve the above-described object,
The three-way valve of the present invention is
An inlet port that is a fluid inflow port, and a valve housing in which a first outlet port and a second outlet port that are fluid outflow ports are formed, and is accommodated in the valve housing so as to be movable in the axial direction thereof A valve body,
The valve body moves in the valve casing in the axial direction, so that the fluid flowing in from the inlet port flows out of either the first outlet port or the second outlet port. A three-way valve configured to automatically switch the flow path,
A first pressure equalizing chamber is defined at one end of the valve casing in the axial direction, and a flow path from the inlet port to the second outlet port is provided inside the first pressure equalizing chamber. Urging means for urging the valve body in the direction of closing the valve is formed,
A second pressure equalization chamber is defined at the other axial end of the valve casing, and a pressure equalization for introducing a part of the fluid flowing from the inlet port into the second pressure equalization chamber. The introduction path is in communication, and the second pressure equalization chamber is configured to open the flow path from the inlet port to the second outlet port by the pressure of the fluid introduced from the pressure equalization introduction path. It is configured to press the valve body,
When the pressure of the fluid flowing in from the inlet port is lower than a predetermined pressure, the valve body moves in a direction to close the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path is formed in the valve housing so that the inflowing fluid flows out from the first outlet port,
When the pressure of the fluid flowing in from the inlet port is higher than a predetermined pressure, the valve body moves in a direction to open the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path through which the inflowing fluid flows out from the second outlet port is formed in the valve housing.

  Thus, the valve body is pivoted by the biasing force of the biasing means accommodated in the first pressure equalizing chamber and the pressing force of the second pressure equalizing chamber interlocked with the pressure of the fluid flowing in from the inlet port. Since it is configured to move in the direction, the flow path in the valve housing can be automatically switched according to the pressure of the fluid flowing from the inlet port without using electromagnetic force or the like.

Further, since no magnetic driving means such as an electromagnetic part is required, the three-way valve can be reduced in size.
In the above invention,
It is desirable that the first pressure equalizing chamber and the second pressure equalizing chamber are defined by a pressure sensitive member in the valve casing.

  As described above, when the first pressure equalizing chamber and the second pressure equalizing chamber are defined by the pressure-sensitive member in the valve casing, the fluid flowing through the flow path in the valve casing is Intrusion into the chamber or the second pressure equalizing chamber can be reliably prevented, and the operation accuracy of the three-way valve of the present invention can be improved.

In the above invention,
It is desirable that the urging means is constituted by an urging member disposed at least in the first pressure equalizing chamber.

In this way, if the urging means is constituted by the urging member, the urging means can be easily formed inside the first pressure equalizing chamber.
The three-way valve of the present invention is
An inlet port that is a fluid inflow port, and a valve housing in which a first outlet port and a second outlet port that are fluid outflow ports are formed, and is accommodated in the valve housing so as to be movable in the axial direction thereof A valve body,
The valve body moves in the valve casing in the axial direction, so that the fluid flowing in from the inlet port flows out of either the first outlet port or the second outlet port. A three-way valve configured to automatically switch the flow path,
A pressure equalizing chamber is defined at one end of the valve housing in the axial direction, and the valve element is disposed in the pressure equalizing chamber in a direction to close a flow path from the inlet port to the second outlet port. And a pressure equalizing passage for introducing a part of the fluid flowing in from the inlet port into the pressure equalizing chamber is communicated with the pressure equalizing chamber. Is configured to press the valve body in a direction to open the flow path from the inlet port to the second outlet port by the pressure of the fluid introduced from the pressure equalization introduction path,
The axial force acting on the valve body by the pressure of the fluid flowing through the flow path in the valve housing is configured to act in both axial directions.
When the pressure of the fluid flowing in from the inlet port is lower than a predetermined pressure, the valve body moves in a direction to close the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path is formed in the valve housing so that the inflowing fluid flows out from the first outlet port,
When the pressure of the fluid flowing in from the inlet port is higher than a predetermined pressure, the valve body moves in a direction to open the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path through which the inflowing fluid flows out from the second outlet port is formed in the valve housing.

  Thus, the valve body is moved in the axial direction by the biasing force of the biasing member housed in the pressure equalizing chamber and the pressing force of the pressure equalizing chamber interlocked with the pressure of the fluid flowing in from the inlet port. Since it is configured, the flow path in the valve housing can be automatically switched according to the pressure of the fluid flowing from the inlet port without using electromagnetic force or the like.

Further, since the pressure equalizing chamber defined in the valve casing is one, it is easy to reduce the size of the valve casing.
The vehicle air conditioner of the present invention uses the above-described three-way valve of the present invention.

In the vehicle air conditioner using such a three-way valve of the present invention, the refrigerant flow path can be easily switched.
The vehicle air conditioner of the present invention is
A vehicle air conditioner using a refrigeration cycle in which high-pressure refrigerant discharged from a refrigerant compressor is depressurized by an expansion valve, becomes low-pressure refrigerant, and flows into the refrigerant compressor again.
While using the above-described three-way valve of the present invention,
The first pressure equalizing chamber of the three-way valve is communicated with a low pressure introduction path for introducing a low pressure refrigerant decompressed by the expansion valve.

  If such a low pressure introduction path is communicated with the first pressure equalizing chamber, the valve is caused by pressure fluctuations of the low pressure refrigerant flowing in the state where the low pressure refrigerant lower than the predetermined pressure flows into the three-way valve. It is possible to reliably prevent the body from moving.

  According to the present invention, a three-way valve configured to automatically switch the flow path in the valve housing according to the pressure of the fluid flowing from the inlet port without using electromagnetic force or the like, and the three-way valve The used vehicle air conditioner can be provided.

FIG. 1 is a schematic diagram for explaining a three-way valve according to a first embodiment of the present invention. FIG. 2 is a schematic diagram for explaining a three-way valve according to a second embodiment of the present invention. FIG. 3 is a schematic diagram for explaining a three-way valve according to a third embodiment of the present invention. FIG. 4 is a schematic diagram for explaining a three-way valve according to a fourth embodiment of the present invention. 4A is a schematic diagram for explaining a process in which the valve body moves from the state shown in FIG. 4A to the state shown in FIG. 4B. FIG. 5 is a schematic diagram for explaining a three-way valve according to a fifth embodiment of the present invention. FIG. 6 is a schematic diagram for explaining a three-way valve according to a sixth embodiment of the present invention. FIG. 7 is a sectional view showing an optimum embodiment of the three-way valve of the present invention. FIG. 8 is a sectional view showing an optimum embodiment of the three-way valve of the present invention. FIG. 9 is a system configuration diagram of a vehicle air conditioner using the three-way valve of the present invention. FIG. 10 is a system configuration diagram of a vehicle air conditioner in which an electromagnetic valve is disposed so as to bypass the expansion valve as disclosed in Patent Documents 1 and 2.

Hereinafter, embodiments of the present invention will be described in more detail with reference to the drawings.
In the following description, the terms “upper side”, “upper surface”, “lower side”, and “lower surface” refer to “upper side”, “upper surface”, “lower side”, and “lower surface” in the figure. And

<First Embodiment>
FIG. 1 is a schematic diagram for explaining a three-way valve according to a first embodiment of the present invention.
As shown in FIG. 1, the three-way valve 1 of the present embodiment includes a valve housing 10 and a valve body 20 accommodated in the valve housing 10.

  The valve casing 10 has a hollow cylindrical shape. As shown in FIG. 1, the valve casing 10 includes an inlet port 12 that is a fluid inlet and a first outlet port that is a fluid outlet. 14a and a second outlet port 14b are formed. These positional relationships in the present embodiment are such that a first outlet port 14a is formed on one end side in the axial direction, a second outlet port 14b is formed on the other end side in the axial direction, and the inlet port 12 is It is formed between the first outlet port 14a and the second outlet port 14b.

  A first pressure equalizing chamber 16a is defined at one end of the valve casing 10 in the axial direction, and a second pressure equalizing chamber 16b is defined at the other end of the valve casing 10 in the axial direction. It is made. The first pressure equalizing chamber 16a and the second pressure equalizing chamber 16b are defined by a diaphragm 36a and a diaphragm 36b, which are pressure-sensitive members, respectively, and are partitioned from other portions of the valve housing 10.

  As will be described later, in the three-way valve 1 of the present embodiment, the diaphragm 36a and the diaphragm 36b are not essential components. However, if the first pressure equalizing chamber 16a and the second pressure equalizing chamber 16b are defined by the diaphragms 36a and 36b in the valve casing 10, the fluid flowing in the valve casing 10 is allowed to flow through the first casing. The pressure equalizing chamber 16a and the second pressure equalizing chamber 16b can be reliably prevented from entering, and the operation accuracy of the three-way valve 1 of the present invention can be improved, which is preferable.

  The valve body 20 is accommodated in the above-described valve housing 10 so as to be movable in the axial direction thereof. As shown in FIG. 1, the valve body 20 includes a valve body 22 that closes the first outlet port 14a or the second outlet port 14b, and a first body connected to the valve body 22 by a rod-shaped member 26a. And a second flange portion 24b connected to the valve body 22 by a rod-like member 26b. The first flange portion 24a is joined to the above-described diaphragm 36a on its upper surface, and similarly, the second flange portion 24b is joined to the above-described diaphragm 36b on its lower surface.

  Further, as shown in FIG. 1, a spring member 30 is arranged in the first pressure equalizing chamber 16a described above as a biasing means for biasing the valve body 20 toward the other end side in the axial direction. Yes. The spring member 30 has one end fixed to the upper surface of the valve housing 10 and the other end joined to the first flange portion 24a. As shown by the arrow F1 in FIG. It arrange | positions in the state biased to the other end side of the axial direction of the valve housing 10 (namely, the direction which closes the 2nd exit port 14b).

  Further, as shown in FIG. 1, a pressure equalization introduction path 32 communicates with the second pressure equalization chamber 16b described above. The pressure equalization introduction path 32 communicates with the upstream side of the inlet port 12 of the valve housing 10 and introduces a part of the fluid flowing into the valve housing 10 from the inlet port 12 into the second pressure equalizing chamber 16b. It can be done. That is, the pressure equalization introduction path 32 communicates with the second pressure equalization chamber 16b, so that the pressure inside the second pressure equalization chamber 16b flows into the valve housing 10 from the inlet port 12. It is comprised so that it may become equal to the pressure of.

  Therefore, the pressing force F2 due to the pressure inside the second pressure equalizing chamber 16b acts on the second flange portion 24b of the valve body 20 described above via the diaphragm 36b. That is, the second pressure equalizing chamber 16b opens the valve body 20 to one end side in the axial direction of the valve housing 10 (that is, opens the second outlet port 14b) by the pressure of the fluid introduced from the pressure equalizing introduction path 32. It is configured to press (in the direction to do).

  Further, a stopper portion 17 for controlling the movement of the valve body 20 in the axial direction is formed inside the valve housing 10 and above the first outlet port 14a in FIG. The stopper portion 17 is formed at a place where the valve body 22 stops at an appropriate position when the valve body 20 moves in the axial direction.

The operation of the three-way valve of the present invention configured as described above will be described in detail based on (a) and (b) of FIG.
1A is a cross-sectional view showing a state in which a low-pressure fluid lower than a predetermined pressure flows into the valve housing 10 from the inlet port 12, and FIG. 1B shows a predetermined pressure. FIG. 6 is a cross-sectional view showing a state in which a higher pressure fluid is flowing from the inlet port 12 into the valve housing 10. Note that arrows F1 to F4 in FIGS. 1A and 1B indicate the axial force acting on the valve body 20, the direction of the arrow indicates the direction in which the force is applied, and the size of the arrow is The relative magnitude of the acting force is shown.

  In the state shown in FIG. 1A, the valve body 20 includes an urging force F <b> 1 of the spring member 30, a pressing force F <b> 2 of the second pressure equalizing chamber 16 b, and the first flange portion 24 a and the valve body 22. The fluid pressing forces F3 and F4 due to the pressure of the low-pressure fluid passing between them act in the axial direction, respectively. Similarly, in the state shown in FIG. 1 (b), the valve body 20 includes an urging force F1 of the spring member 30, a pressing force F2 of the second pressure equalizing chamber 16b, and a second flange portion 24b. Fluid pressing forces F3 and F4 due to the pressure of the high-pressure fluid passing between the valve main body 22 act in the axial direction.

  Here, the fluid pressing force F3 acts on the valve body 20 on one end side, and the fluid pressing force F4 acts on the valve body 20 on the other end side in the moving direction. Is formed in a cylindrical shape, and the lower surface of the first flange portion 24a and the upper surface of the valve body 22 have the same pressure receiving area with respect to the pressure of the fluid flowing through the flow path inside the valve housing 10. Yes. Similarly, as shown in FIG. 1B, the upper surface of the second flange portion 24 b and the lower surface of the valve body 22 correspond to the pressure of the fluid flowing through the flow path inside the valve housing 10. The same pressure receiving area.

  That is, in the state shown in FIGS. 1A and 1B, among the four axial forces acting on the valve body 20, the fluid pressing forces F3 and F4 cancel each other, so the valve body 20 Therefore, it can be considered that two forces of the biasing force F1 of the spring member 30 and the pressing force F2 of the second pressure equalizing chamber 16b are acting.

  Further, as described above, the pressure equalization introduction path 32 is configured so that the pressure inside the second pressure equalization chamber 16 b becomes equal to the pressure of the fluid flowing into the valve housing 10 from the inlet port 12. Yes. Therefore, the pressing force F2 of the second pressure equalizing chamber is linked to the pressure of the fluid flowing into the valve housing 10 from the inlet port 12, and when the fluid is high pressure, the pressing force of the second pressure equalizing chamber is F2 also increases, and when the fluid is low pressure, the pressing force F2 of the second pressure equalizing chamber is also reduced.

  Therefore, as shown in FIG. 1A, when the pressure of the fluid flowing from the inlet port 12 is a low pressure fluid lower than a predetermined pressure, the pressing force of the second pressure equalizing chamber 16b is the spring member. Thus, the valve body 20 moves inside the valve housing 10 toward the other end side in the axial direction. Then, the valve body 20 is stopped at a position where the first flange portion 24a contacts the stopper portion 17, and the second outlet port 14b is closed by the valve body 22, so that the fluid flowing in from the inlet port 12 is the first. A flow path that flows out from the outlet port 14 a is formed inside the valve housing 10.

  Further, as shown in FIG. 1B, when the pressure of the fluid flowing from the inlet port 12 is a high pressure fluid higher than a predetermined pressure, the pressing force of the second pressure equalizing chamber 16b is the spring member. As a result, the valve body 20 moves inside the valve housing 10 toward one end in the axial direction. Then, the valve body 20 stops at a position where the valve main body 22 abuts against the stopper portion 17, and the first outlet port 14 a is closed by the valve main body 22, so that the fluid flowing from the inlet port 12 is allowed to flow into the second outlet port. A flow path that flows out from 14 b is formed inside the valve housing 10.

  As described above, the three-way valve 1 of the present invention is configured such that the flow path inside the valve housing 10 can be automatically switched according to the pressure of the fluid flowing from the inlet port 12. Therefore, unlike the conventional three-way valve, electromagnetic force is not used to drive the valve body, and no magnetic driving means such as an electromagnetic part is required, so that the three-way valve 1 can be downsized. It is like that.

  In the three-way valve 1 of the present embodiment, the fluid pressing forces F3 and F4 are configured to cancel each other, but the three-way valve 1 of the present invention is not limited to this. For example, the pressure receiving area of the valve main body 22, the pressure receiving area on the lower side of the first flange portion 24a, and the pressure receiving area on the upper side of the second flange portion 24b may be formed in different pressure receiving areas. Even in this case, if the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the biasing force F1 of the spring member 30 than the absolute value of the difference between the fluid pressing forces F3 and F4, FIG. The valve body 20 moves to the other end side in the axial direction as shown in FIG. 5 and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out from the first outlet port 14a. . On the other hand, if the pressing force F2 of the second pressure equalizing chamber 16b is larger than the biasing force F1 of the spring member 30 than the absolute value of the difference between the fluid pressing forces F3 and F4, it is shown in FIG. Thus, the valve body 20 moves to one end side in the axial direction, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out from the second outlet port 14b.

  In the three-way valve 1 of the present embodiment, as described above, the first pressure equalizing chamber 16a and the second pressure equalizing chamber 16b are defined by the diaphragms 36a and 36b, which are pressure-sensitive members, inside the valve housing 10. It is made. However, the three-way valve 1 of the present invention is not limited to this. For example, the first pressure equalizing chamber 16a and the second pressure equalizing chamber are defined by the first flange portion 24a and the second flange portion 24b of the valve body 20, for example. 16b may be defined.

<Second Embodiment>
FIG. 2 is a schematic diagram for explaining the three-way valve according to the second embodiment of the present invention. FIG. 2A shows a low-pressure fluid having a pressure lower than a predetermined pressure from the inlet port 12 to the valve housing 10. FIG. 2B is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows into the valve housing 10 from the inlet port 12.

  The three-way valve 1 of the second embodiment shown in FIG. 2 has basically the same configuration as the three-way valve 1 of the first embodiment described above, and the same reference numerals are assigned to the same components. A detailed description thereof will be omitted.

  In the three-way valve 1 of the second embodiment, the spring member 30 is not disposed inside the first pressure equalizing chamber 16a, and instead, pressure introduction that introduces fluid into the first pressure equalizing chamber 16a. The point which the path 38 is connected is different from the first embodiment described above.

  In the three-way valve 1 of the second embodiment, the fluid pressure of the fluid introduced into the first pressure equalizing chamber 16a acts on the first flange portion 24a of the valve body 20 via the diaphragm 36a. The valve body 20 is configured to be urged toward the other end side in the axial direction by an urging force F1 ′. That is, in the three-way valve 1 of the second embodiment, the pressure introduction path 38 communicating with the first pressure equalizing chamber 16a has a biasing means for biasing the valve body 20 toward the other end side in the axial direction. It is composed.

  In the three-way valve 1 of the present invention, the pressure of the fluid introduced by the pressure introduction path 38 is not particularly limited. However, in the case of the three-way valve 1 in which the pressure receiving area of the upper surface of the first flange portion 24a is equal to the pressure receiving area of the lower surface of the second flange portion 24b as in this embodiment, the pressure introduction path 2 is higher in pressure than the low-pressure fluid flowing into the valve housing 10 from the inlet port 12 in the state shown in FIG. 2A, and in FIG. In the state shown, the pressure needs to be lower than the high-pressure fluid flowing from the inlet port 12 into the valve housing 10.

  If such a pressure introduction path 38 communicates with the first pressure equalizing chamber 16a, the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the biasing force F1 ′ of the biasing means described above. As shown in FIG. 2 (a), the valve body 20 moves to the other end side in the axial direction, and a flow path through which the fluid flowing in from the inlet port 12 flows out from the first outlet port 14a is formed in the valve housing. 10 is formed inside. When the pressing force F2 of the second pressure equalizing chamber 16b is larger than the fluid pressure F1 ′, the valve body 20 moves to one end side in the axial direction as shown in FIG. A flow path is formed in the valve housing 10 so that the fluid flowing in from the port 12 flows out from the second outlet port 14b.

  As described above, in the three-way valve 1 of the present invention, the urging means formed in the first pressure equalizing chamber 16a is not limited to the urging member such as the spring member 30, and the second As in the embodiment, the pressure introduction path 38 for introducing a low-pressure fluid into the first pressure equalizing chamber 16a may be used.

<Third Embodiment>
FIG. 3 is a schematic diagram for explaining the three-way valve according to the third embodiment of the present invention. FIG. 3A shows a low-pressure fluid having a pressure lower than a predetermined pressure from the inlet port 12 to the valve housing 10. FIG. 3B is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows into the valve housing 10 from the inlet port 12.

  The three-way valve 1 of the third embodiment shown in FIG. 3 has basically the same configuration as the three-way valve 1 of the first embodiment described above, and the same reference numerals are given to the same components. A detailed description thereof will be omitted.

  The three-way valve 1 according to the third embodiment is different from the three-way valve 1 according to the first embodiment described above, and as shown in FIG. 3, the valve body 20 includes the first valve body 22a and the first valve body 22a. The first valve main body 22a and the second valve main body 22b connected by a rod-shaped member 26 are included. The first valve body 22a is joined on its upper surface to a diaphragm 36a that defines the first pressure equalizing chamber 16a. Similarly, the second valve body 22b has a second surface on its lower surface. The pressure equalizing chamber 16b is joined to a diaphragm 36b.

  Further, in the three-way valve 1 of the third embodiment, the positional relationship between the first outlet port 14a and the second outlet port 14b is opposite to that of the first embodiment described above. That is, as shown in FIG. 3, in the three-way valve 1 of the third embodiment, the second outlet port 14b is formed on one end side in the axial direction, and the second outlet port 14b is formed on the other end side in the axial direction. An outlet port 14a is formed.

Even in such a three-way valve 1, when the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the urging force F1 of the spring member 30, the valve body 20 as shown in FIG. Is moved to the other end side in the axial direction, the first valve body 22a closes the second outlet port 14b, and the fluid flowing in from the inlet port 12 flows out from the first outlet port 14a. Is formed inside the valve housing 10. When the pressing force F2 of the second pressure equalizing chamber 16b is larger than the urging force F1 of the spring member 30, the valve body 20 moves to one end side in the axial direction as shown in FIG. The second valve body 22b closes the first outlet port 14a, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out of the second outlet port 14b. .
Thus, in the three-way valve 1 of the present invention, the valve body 20 can be configured to include the two valve bodies 22a and 22b.

<Fourth Embodiment>
FIG. 4 is a schematic diagram for explaining a three-way valve according to a fourth embodiment of the present invention. FIG. 4A shows a low-pressure fluid having a pressure lower than a predetermined pressure from the inlet port 12 to the valve housing 10. FIG. 4B is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows into the valve housing 10 from the inlet port 12.

  The three-way valve 1 of the fourth embodiment shown in FIG. 4 has basically the same configuration as the three-way valve 1 of the first embodiment described above, and the same reference numerals are given to the same components. A detailed description thereof will be omitted.

  The three-way valve 1 of the fourth embodiment is different from the three-way valve 1 of the first embodiment described above, and as shown in FIG. 4, the valve body 20 is connected to the first outlet port 14a or the second outlet port 14a. The valve main body 22 is configured to close the outlet port 14b, and the first main flange portion 24a is connected to the valve main body 22 by a rod-shaped member 26a. Further, the lower surface of the valve body 22 is not joined to the diaphragm 36b, and is in contact with the diaphragm 36b in a detachable state in the state shown in FIG.

  Even in such a three-way valve 1, when the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the urging force F1 of the spring member 30, the valve body 20 as shown in FIG. Is moved to the other end side in the axial direction, the valve body 22 closes the second outlet port 14b, and a flow path in which the fluid flowing in from the inlet port 12 flows out of the first outlet port 14a is formed in the valve housing. 10 is formed inside. When the pressing force F2 of the second pressure equalizing chamber 16b is larger than the biasing force F1 of the spring member 30, the valve body 20 moves to one end side in the axial direction as shown in FIG. The valve body 22 closes the first outlet port 14a, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out of the second outlet port 14b.

Here, the process in which the valve body 20 moves from the state shown in FIG. 4A to the state shown in FIG. 4B will be described in detail with reference to FIG. 4A.
When the fluid flowing into the valve housing 10 from the inlet port 12 is switched from the low pressure fluid to the high pressure fluid, the pressing force F2 of the second pressure equalizing chamber 16b becomes larger than the biasing force F1 of the spring member 30, and FIG. As shown in FIG. 4A (c), the diaphragm 36b expands to move the valve body 20 to one end side in the axial direction. And if the valve body 20 moves to the state shown to (d) of FIG. 4A, the high pressure fluid which flows in from the inlet port 12 will flow in between the valve main body 22 and the diaphragm 36b. Then, the valve main body 22 is further moved to one end side in the axial direction by the fluid pressing force F3 due to the pressure of the fluid that has flowed in, so that the state shown in FIG.

  Thus, in the three-way valve 1 of the present invention, as described above, the valve main body 22 that closes the first outlet port 14a or the second outlet port 14b, the valve main body 22 and the rod-shaped member 26a. It is also possible to constitute the valve body 20 from the connected first flange portion 24a.

  In the three-way valve 1 of the fourth embodiment, the diaphragm 36b that defines the second pressure equalizing chamber 16b is omitted as in the three-way valve 1 of the first embodiment described above. Can not. This is because if the diaphragm 36b is omitted, the fluid flowing into the valve housing 10 from the inlet port 12 circulates through the pressure equalization introduction path 32 in the state shown in FIG.

<Fifth Embodiment>
FIG. 5 is a schematic diagram for explaining a three-way valve according to a fifth embodiment of the present invention. FIG. 5A shows a low-pressure fluid having a pressure lower than a predetermined pressure from the inlet port 12 to the valve housing 10. FIG. 5B is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows from the inlet port 12 into the valve housing 10.

  The three-way valve 1 of the fifth embodiment shown in FIG. 5 has basically the same configuration as the three-way valve 1 of the first embodiment described above, and the same reference numerals are assigned to the same components. A detailed description thereof will be omitted.

  Unlike the three-way valve 1 of the first embodiment described above, the three-way valve 1 of the fifth embodiment is different from the three-way valve 1 of the first embodiment described above in that the valve body 20 is connected to the first outlet port 14a or the second It consists only of the valve body 22 that closes the outlet port 14b. A diaphragm 36 a is joined to the upper surface of the valve body 22. Further, the spring member 30 is in contact with the upper surface of the valve main body 22, whereby the valve body 20 is urged toward the other end side in the axial direction. Furthermore, the lower surface of the valve main body 22 is not joined to the diaphragm 36b, and is in contact with the diaphragm 36b in a detachable state in the state shown in FIG.

  Even in such a three-way valve 1, in the state shown in FIG. 5A, the fluid pressing forces F3 and F4 cancel each other through the diaphragm 36a joined to the valve main body 22. Act on. Therefore, when the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the urging force F1 of the spring member 30, the valve body 20 is in the other end side in the axial direction as shown in FIG. The valve body 22 closes the second outlet port 14b, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out of the first outlet port 14a. It is like that. When the pressing force F2 of the second pressure equalizing chamber 16b is larger than the urging force F1 of the spring member 30, the valve body 20 moves to one end side in the axial direction as shown in FIG. Then, the valve body 22 closes the first outlet port 14a, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out from the second outlet port 14b.

In addition, about the process in which the valve body 20 moves from the state shown to (a) of FIG. 5 to the state shown to (b) of FIG. 5, it is the same as that of 4th Embodiment mentioned above.
Thus, in the three-way valve 1 of the present invention, as described above, the valve body 20 is composed only of the valve body 22 that closes the first outlet port 14a or the second outlet port 14b. Is also good.

  In the three-way valve 1 of the fifth embodiment, like the three-way valve 1 of the first embodiment described above, the diaphragm 36a that defines the first pressure equalizing chamber 16a, and the second The diaphragm 36b that defines the pressure equalizing chamber 16b cannot be omitted. This is because if the diaphragm 36a is omitted, the urging force F1 of the spring member 30, the pressing force F2 of the second pressure equalizing chamber 16b, and the fluid pressing force are applied to the valve body 20 in the state shown in FIG. Although the pressure F4 is applied, the pressing force F2 and the fluid pressing force F4 act so as to cancel each other, so that the valve body 20 is biased to the other end side in the axial direction by the spring member 30. Become. In this state, even if the fluid flowing from the inlet port 12 into the valve housing 10 is switched from the low pressure fluid to the high pressure fluid, the fluid pressure F4 increases as the pressure F2 in the second pressure equalizing chamber 16b increases. Therefore, the pressing force F2 and the fluid pressing force F4 cancel each other, and the valve body 20 remains biased to the other end side in the axial direction by the biasing force F1 of the spring member 30 and does not move.

  If the diaphragm 36b is omitted, as in the above-described fourth embodiment, the fluid flowing into the valve housing 10 from the inlet port 12 in the state shown in FIG. It is because it will circulate through.

  In short, as in the three-way valve 1 of the first to fifth embodiments described above, in the three-way valve 1 in which pressure equalizing chambers are formed at one end and the other end of the valve housing 10, respectively, The valve housing 20 moves in the axial direction inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out of either the first outlet port 14a or the second outlet port 14b. As long as it is configured to be able to switch the flow path inside 10, the shape of the valve body 20 is not particularly limited.

<Sixth Embodiment>
FIG. 6 is a schematic diagram for explaining a three-way valve according to a sixth embodiment of the present invention. FIG. 6A shows a low-pressure fluid having a pressure lower than a predetermined pressure from the inlet port 12 to the valve housing 10. FIG. 6B is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows from the inlet port 12 into the valve housing 10.

  The three-way valve 1 of the sixth embodiment shown in FIG. 6 has basically the same configuration as the three-way valve 1 of the first embodiment described above, and the same reference numerals are assigned to the same components. A detailed description thereof will be omitted.

  The three-way valve 1 according to the sixth embodiment is different from the three-way valve 1 according to the first to fifth embodiments described above, as shown in FIG. A chamber 16 is formed. The spring member 30 ′ disposed inside the pressure equalizing chamber 16 is different from the spring member 30 of the above-described embodiment in that the valve body 20 is placed on one end side in the axial direction (that is, the second outlet port 14 b). (In the direction of closing).

  Further, as shown in FIG. 6, the pressure equalization chamber 16 is connected to the pressure equalization introduction path 32, and a part of the fluid flowing into the valve housing 10 from the inlet port 12 is in the pressure equalization chamber 16. It has been introduced inside.

  In the three-way valve 1 of the sixth embodiment, the positional relationship between the first outlet port 14a and the second outlet port 14b is reversed, as in the third embodiment described above. That is, as shown in FIG. 6, in the three-way valve 1 of the sixth embodiment, the second outlet port 14b is formed on one end side in the axial direction, and the second outlet port 14b is formed on the other end side in the axial direction. An outlet port 14a is formed.

  Even in such a three-way valve 1, the fluid pressing forces F3 and F4 act so as to cancel each other. For this reason, when the pressing force F2 of the pressure equalizing chamber 16 is smaller than the urging force F1 of the spring member 30 ′, the valve body 20 moves to one end side in the axial direction as shown in FIG. The valve body 22 closes the second outlet port 14b, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out of the first outlet port 14a. Further, when the pressing force F2 of the pressure equalizing chamber 16 is larger than the biasing force F1 of the spring member 30 ′, the valve body 20 moves to the other end side in the axial direction as shown in FIG. The valve body 22 closes the first outlet port 14a, and a flow path is formed inside the valve housing 10 so that the fluid flowing in from the inlet port 12 flows out from the second outlet port 14b.

  As described above, in the three-way valve 1 of the present invention, the pressure equalizing chamber 16 is defined only at one end portion in the axial direction of the valve housing 10, and the valve body 20 is disposed in this pressure equalizing chamber 16 at one end side in the axial direction. It is also possible to arrange the urging member (spring member 30 ′) that urges the pressure equalizing chamber 16 and communicate the pressure equalizing chamber 16 with the pressure equalizing chamber 16.

  In the three-way valve 1 of the sixth embodiment, the valve body 20 having the shape as in the fourth embodiment and the fifth embodiment described above cannot be employed. Because, for example, in the three-way valve 1 of the sixth embodiment, if the valve body 20 as in the fourth embodiment is adopted, in the state shown in FIG. The urging force F1 of the spring member 30 ′, the pressing force F2 of the pressure equalizing chamber 16, and the fluid pressing force F3 are in a state of acting, but the pressing force F2 and the fluid pressing force F3 act so as to cancel each other. Therefore, the valve body 20 is biased to one end side in the axial direction by the spring member 30 '. In this state, even if the fluid flowing from the inlet port 12 into the valve housing 10 is switched from a low pressure fluid to a high pressure fluid, the fluid pressure F3 increases as the pressure F2 in the pressure equalizing chamber 16 increases. This is because the pressing force F2 and the fluid pressing force F3 cancel each other, and the valve body 20 remains biased toward one end side in the axial direction by the biasing force F1 of the spring member 30 ′ and does not move.

  That is, in the three-way valve 1 in which the pressure equalizing chamber is defined only at one end in the axial direction like the three-way valve 1 of the sixth embodiment, the fluid flowing through the flow path inside the valve housing 10 The axial force acting on the valve body 20 due to the pressure of the valve must be configured to act simultaneously in both the axial direction and the other end direction.

<Vehicle air conditioner 100>
In the first to sixth embodiments described above, the three-way valve 1 of the present invention has been described based on a schematic cross-sectional view. Next, the vehicle air conditioner 100 using the three-way valve 1 of the present invention will be described with reference to FIGS.

  7 and 8 are cross-sectional views showing an optimum embodiment of the three-way valve of the present invention. FIG. 7 shows a state in which a low-pressure fluid lower than a predetermined pressure flows into the valve housing from the inlet port. FIG. 8 is a cross-sectional view showing a state in which a high-pressure fluid higher than a predetermined pressure flows from the inlet port into the valve housing.

  The three-way valve 1 shown in FIGS. 7 and 8 has basically the same configuration as the three-way valve 1 shown in the first embodiment described above. Therefore, the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

  However, in the three-way valve 1 shown in FIGS. 7 and 8, a valve chamber 10A is formed at a substantially central portion in the axial direction of the valve housing 10, and the valve main body 22 is located inside the valve chamber 10A. Further, the valve body 20 is accommodated in the valve housing 10. When the pressing force F2 of the second pressure equalizing chamber 16b is smaller than the biasing force F1 of the spring member 30, the valve body 20 moves to the other end side in the axial direction as shown in FIG. The valve body 22 and the second valve seat surface 11b formed on the other end side in the axial direction of the valve chamber 10A come into contact with each other, and the flow path to the second outlet port 14b is closed. The fluid that has flowed in flows out from the first outlet port 14a. When the pressing force F2 of the second pressure equalizing chamber 16b is larger than the urging force F1 of the spring member 30, the valve body 20 moves to one end side in the axial direction as shown in FIG. The main body 22 and the first valve seat surface 11a formed on one end side of the valve chamber 10A come into contact with each other and close the flow path to the first outlet port 14a. The second outlet port 14b flows out.

  In the three-way valve 1 shown in FIGS. 7 and 8 configured as described above, the valve main body 22 has the first valve seat surface 11a or the second valve seat surface formed in the axial direction of the valve chamber 10A. Since it is configured to close the flow path to the first outlet port 14a or the second outlet port 14b by contacting with 11b, the valve main body 22 on which the axial force is applied acts to The flow path to one outlet port 14a or the second outlet port 14b is securely closed. Therefore, in the three-way valve 1 shown in FIGS. 7 and 8, it is difficult for the fluid to leak into the closed flow path, and a refrigerant having a maximum pressure of about 3 Mpa is used as the fluid. It can be suitably used also in an air conditioner or the like.

  Further, in the three-way valve 1 shown in FIGS. 7 and 8, the low pressure introduction path 34 communicates with the first pressure equalizing chamber 16a, and a low pressure fluid is introduced into the first pressure equalizing chamber 16a. It has become so. The effect of the low pressure introduction path 34 will be described later.

Such a three-way valve 1 shown in FIGS. 7 and 8 can be suitably used for the vehicle air conditioner 100 of the present invention.
FIG. 9 is a system configuration diagram of a vehicle air conditioner using the three-way valve of the present invention.

  In the vehicle air conditioner 100 shown in FIG. 9, the same components as those of the conventional vehicle air conditioner 100 ′ shown in FIG. 10 are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the vehicle air conditioner 100 shown in FIG. 9, switching of the refrigerant flow path at the branch point A is performed by two electromagnetic valves 160b and 160c as compared with the conventional vehicle air conditioner 100 ′ shown in FIG. Instead, the difference is that the three-way valve 1 described above is used.

  That is, in the vehicle air conditioner 100 shown in FIG. 9, the inlet port 12 is connected to the flow path 168 on the outdoor heat exchanger 140 side, and the first outlet port 14 a is on one side downstream of the branch point A. The three-way valve 1 is arranged so that the second outlet port 14 b is connected to the flow path 164 and the flow path 166 on the other side.

  With such a vehicle air conditioner 100, the flow path of the low-pressure refrigerant flowing into the branch point A during the heating operation is automatically switched inside the valve casing 10 of the three-way valve 1, and the first outlet It flows out from the port 14a to the flow path 164 on one side. In addition, the flow path of the high-pressure refrigerant flowing into the branch point A during the cooling operation is automatically switched inside the valve housing 10 of the three-way valve 1, and then flows from the second outlet port 14 b to the flow path 166 on the other side. And leaked.

  Further, the low-pressure introduction path 34 described above is connected between the junction B of the flow path 164 and the refrigerant compressor 110 as shown in FIG. 9. Since the low-pressure refrigerant that has been decompressed and expanded always flows in the downstream of the junction B of the flow path 164 during both the heating operation and the cooling operation, the introduction of the first pressure equalization chamber 16a from the low-pressure introduction path 34. The refrigerant to be used is always a low-pressure refrigerant.

  In the state shown in FIG. 7, the low-pressure refrigerant flowing out from the first outlet port 14 a is introduced into the first pressure equalizing chamber 16 a through the low-pressure introduction path 34. Therefore, as in the three-way valve 1 shown in FIGS. 7 and 8, if the pressure receiving area on the upper surface of the first flange portion 24a and the pressure receiving area on the lower surface of the second flange portion 24b are formed to be equal. The pressing force F2 of the second pressure equalizing chamber 16b and the fluid pressing force F5 due to the low-pressure refrigerant introduced into the first pressure equalizing chamber 16a via the low pressure introduction passage 34 described above always act to cancel each other. Therefore, only the urging force F1 of the spring member 30 acts on the valve body 20 on the other end side in the axial direction.

  Therefore, even if the pressure of the low-pressure refrigerant flowing from the inlet port 12 fluctuates, the urging force F1 of the constant spring member 30 always acts on the valve element 20, and therefore the valve element 20 is caused by fluctuations in the pressure of the low-pressure refrigerant flowing. In the state shown in FIG. 7, the flow path to the second outlet port 14b is reliably closed.

  In the state shown in FIG. 8, the fluid pressing force F5 described above acts in a direction to open the flow path to the first outlet port 14a. However, the pressure difference between the low-pressure refrigerant and the high-pressure refrigerant in the automotive air conditioner 100 is large, and in the state shown in FIG. 8, the pressing force F2 of the second pressure equalizing chamber 16b is larger than the fluid pressing force F5. Because it is much larger, it is not a problem.

  As described above, in the vehicle air conditioner 100 of the present invention, unlike the conventional vehicle air conditioner 100 ′, it is not necessary to switch the refrigerant flow path at the branch point A by the two electromagnetic valves 160b and 160c. As a result, the air conditioner can be downsized.

  Further, since the refrigerant flow path at the branch point A is switched by the pressure of the refrigerant flowing in instead of the electromagnetic force, it can be suitably used in a vehicle air conditioner that is required to suppress power consumption as much as possible, such as an electric vehicle. .

  As mentioned above, although preferable embodiment of this invention was described, this invention is not limited to the said embodiment. Various modifications can be made without departing from the object of the present invention.

1 three-way valve 10 valve housing 10A valve chamber 11a first valve seat surface 11b second valve seat surface 12 inlet port 14a first outlet port 14b second outlet port 16 pressure equalizing chamber 16a first pressure equalizing chamber 16b Second pressure equalizing chamber 17 Stopper portion 20 Valve body 22 Valve body 22a First valve body 22b Second valve body 24a First flange portion 24b Second flange portion 26 Rod member 26a First rod member 26b First Two rod-shaped members 30 Spring member 32 Equal pressure introduction path 34 Low pressure introduction path 36a First diaphragm 36b Second diaphragm 38 Pressure introduction path 100 Vehicle air conditioner 110 Refrigerant compressor 120 Heating heat exchanger 122 Door 130 For cooling Heat exchanger 140 Outdoor heat exchanger 150a First expansion valve 150b Second expansion valve 160a First solenoid valve 160b Second solenoid valve 160c Third solenoid valve 16 The flow path 168 flow path A branch point B junction of the flow path 166 the other side of the bypass passage 164 on one side

Claims (7)

An inlet port that is a fluid inflow port, and a valve housing in which a first outlet port and a second outlet port that are fluid outflow ports are formed, and is accommodated in the valve housing so as to be movable in the axial direction thereof A valve body,
The valve body moves in the valve casing in the axial direction, so that the fluid flowing in from the inlet port flows out of either the first outlet port or the second outlet port. A three-way valve configured to automatically switch the flow path,
A first pressure equalizing chamber is defined at one end of the valve casing in the axial direction, and a flow path from the inlet port to the second outlet port is provided inside the first pressure equalizing chamber. Urging means for urging the valve body in the direction of closing the valve is formed,
A second pressure equalization chamber is defined at the other axial end of the valve casing, and a pressure equalization for introducing a part of the fluid flowing from the inlet port into the second pressure equalization chamber. The introduction path is in communication, and the second pressure equalization chamber is configured to open the flow path from the inlet port to the second outlet port by the pressure of the fluid introduced from the pressure equalization introduction path. It is configured to press the valve body,
When the pressure of the fluid flowing in from the inlet port is lower than a predetermined pressure, the valve body moves in a direction to close the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path is formed in the valve housing so that the inflowing fluid flows out from the first outlet port,
When the pressure of the fluid flowing in from the inlet port is higher than a predetermined pressure, the valve body moves in a direction to open the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. 3. A three-way valve, characterized in that a flow path through which inflowing fluid flows out from the second outlet port is formed in the valve housing.   The three-way valve according to claim 1, wherein the first pressure equalizing chamber and the second pressure equalizing chamber are defined by a pressure sensitive member in the valve casing.   3. The three-way valve according to claim 1, wherein the urging unit is configured by an urging member disposed at least in the first pressure equalizing chamber. An inlet port that is a fluid inflow port, and a valve housing in which a first outlet port and a second outlet port that are fluid outflow ports are formed, and is accommodated in the valve housing so as to be movable in the axial direction thereof A valve body,
The valve body moves in the valve casing in the axial direction, so that the fluid flowing in from the inlet port flows out of either the first outlet port or the second outlet port. A three-way valve configured to automatically switch the flow path,
A pressure equalizing chamber is defined at one end of the valve housing in the axial direction, and the valve element is disposed in the pressure equalizing chamber in a direction to close a flow path from the inlet port to the second outlet port. And a pressure equalizing passage for introducing a part of the fluid flowing in from the inlet port into the pressure equalizing chamber is communicated with the pressure equalizing chamber. Is configured to press the valve body in a direction to open the flow path from the inlet port to the second outlet port by the pressure of the fluid introduced from the pressure equalization introduction path,
The axial force acting on the valve body by the pressure of the fluid flowing through the flow path in the valve housing is configured to act simultaneously in both axial directions,
When the pressure of the fluid flowing in from the inlet port is lower than a predetermined pressure, the valve body moves in a direction to close the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. A flow path is formed in the valve housing so that the inflowing fluid flows out from the first outlet port,
When the pressure of the fluid flowing in from the inlet port is higher than a predetermined pressure, the valve body moves in a direction to open the flow path from the inlet port to the second outlet port, and thereby, from the inlet port. 3. A three-way valve, characterized in that a flow path through which inflowing fluid flows out from the second outlet port is formed in the valve housing.   A vehicle air conditioner using the three-way valve according to any one of claims 1 to 3. A vehicle air conditioner using a refrigeration cycle in which high-pressure refrigerant discharged from a refrigerant compressor is depressurized by an expansion valve, becomes low-pressure refrigerant, and flows into the refrigerant compressor again.
6. The vehicle air conditioner according to claim 5, wherein the first pressure equalizing chamber of the three-way valve is in communication with a low pressure introduction path for introducing the low pressure refrigerant decompressed by the expansion valve.   An air conditioner for vehicles, wherein the three-way valve according to claim 4 is used.

Images