JP6809706B2 - Six-way switching valve - Google Patents

Description

The present invention relates to a six-way switching valve that switches the flow path by moving the valve body, and is particularly suitable for use as a flow path switching valve that switches the flow path in a heat pump type heating / cooling system or the like. Regarding.

In general, heat pump air-conditioning systems such as room air conditioners and car air conditioners have a flow path switching valve as a flow path (flow direction) switching means in addition to a compressor, an outdoor heat exchanger, an indoor heat exchanger, and an expansion valve. It has.

As a flow path switching valve of this type, a four-way switching valve is well known, but it is considered to use a six-way switching valve instead.

An example of a heat pump type heating / cooling system provided with a six-way switching valve will be briefly described below with reference to FIGS. 8A and 8B. In the heat pump type heating / cooling system 100 of the illustrated example, the operation mode (cooling operation and heating operation) is switched by the six-way switching valve 180, and basically, the compressor 110, the outdoor heat exchanger 120, and the indoor heat exchanger 120 are used. A six-way switching valve 180 provided with a heat exchanger 130, an expansion valve 150 for cooling, and an expansion valve 160 for heating, and having six ports pA, pB, pC, pD, pE, and pF is arranged between them. There is.

Each of the devices is connected by a flow path formed by a conduit (pipe) or the like, and when the cooling operation mode is selected, the high temperature discharged from the compressor 110 is as shown in FIG. 8 (A). The high-pressure refrigerant is guided from the port pA of the six-way switching valve 180 to the outdoor heat exchanger 120 via the port pB, where it exchanges heat with the outdoor air and condenses to become a high-pressure two-phase refrigerant, which expands for cooling. Introduced to valve 150. The high-pressure refrigerant is depressurized by the cooling expansion valve 150, and the depressurized low-pressure refrigerant is introduced into the indoor heat exchanger 130 from the port pE of the hexagonal switching valve 180 via the port pF, where indoor air and heat are introduced. After exchanging (cooling) and evaporating, the low-temperature low-pressure refrigerant is returned from the indoor heat exchanger 130 from the port pC of the hexagonal switching valve 180 to the suction side of the compressor 110 via the port pD.

On the other hand, when the heating operation mode is selected, as shown in FIG. 8B, the high-temperature and high-pressure refrigerant discharged from the compressor 110 enters the room from the port pA of the hexagonal switching valve 180 via the port pF. It is guided to the heat exchanger 130, where it exchanges heat (heating) with the room air, condenses it, becomes a high-pressure two-phase refrigerant, and is introduced into the expansion valve 160 for heating. The high-pressure refrigerant is depressurized by the heating expansion valve 160, and the depressurized low-pressure refrigerant is introduced into the outdoor heat exchanger 120 from the port pC of the hexagonal switching valve 180 via the port pB, where the outdoor air and heat are generated. After exchanging and evaporating, the low-temperature low-pressure refrigerant is returned from the outdoor heat exchanger 120 from the port pE of the hexagonal switching valve 180 to the suction side of the compressor 110 via the port pD.

As a six-way switching valve incorporated in the heat pump type heating / cooling system as described above, a sliding type as described in Patent Document 1 is known. This slide-type six-way switching valve has a valve body (main valve housing) incorporating a slide-type main valve body and an electromagnetic pilot valve (four-way pilot valve), and the ports pA to pF are provided in the main valve housing. Is provided, and the sliding main valve body is slidably arranged in the left-right direction. On the left and right sides of the sliding main valve body in the main valve housing, a pair of left and right piston type packings connected to the compressor discharge side and the compressor suction side via a pilot valve, respectively, are connected to the sliding main valve body. Two defined operating chambers are provided, and high-pressure fluid (refrigerant) is selectively introduced and discharged into these two operating chambers by the pilot valve, and the pressure difference between the two operating chambers is used. The flow path is switched by sliding the sliding main valve body in the left-right direction.

Japanese Unexamined Patent Publication No. 8-170864

The conventional flow path switching valve as described above has the following problems to be solved.

That is, in the slide-type six-way switching valve described in Patent Document 1, five ports pB to pF out of the six ports pA to pF are provided side by side in the axial direction. The valve seat surface and the sliding main valve seat of the main valve seat and the sliding main valve body on which the ports pB to pF are provided become longer (in the axial direction) and the sliding main valve body is slidably brought into contact with each other. It is difficult to ensure the surface accuracy (flatness) of the sealing surface of the valve body, and there is a risk that initial leakage and leakage due to durability deterioration (valve leakage) will increase.

Further, in the main valve housing having a relatively small internal volume, the high-pressure fluid (refrigerant) collides with the inner wall surface or the like, and the flow direction thereof changes greatly in a crank shape, so that the pressure loss is disliked to increase.

In addition to the above, in the conventional flow path switching valve, particularly the flow path switching valve used in the heat pump type heating / cooling system described above, a high temperature and high pressure refrigerant (port pA to port pB, port pA to port) is used in the main valve housing. The refrigerant flowing to pF) and the low-temperature low-pressure refrigerant (refrigerant flowing from port pC to port pD and from port pE to port pD) are flowed in close proximity to each other. Specifically, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant flow through the main valve seat to the adjacent ports pB and pC during the cooling operation, and to the adjacent port pF via the main valve seat during the heating operation. The main valve seat provided with each port is generally made of a metal having high thermal conductivity, so that the amount of heat exchange (that is, heat loss) between them becomes large. There is also the problem that the efficiency of the system deteriorates.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a six-way switching valve capable of preventing valve leakage and effectively suppressing pressure loss.

Another object of the present invention is a heat pump type heating / cooling system that can reduce heat loss when used in an environment where a high temperature / high pressure fluid and a low temperature / low pressure fluid flow, such as a heat pump type heating / cooling system. It is an object of the present invention to provide a six-way switching valve capable of improving the efficiency of the above.

In order to achieve the above object, the six-way switching valve according to the present invention basically includes a tubular main valve housing that defines the main valve chamber, and a total of six ports provided in the main valve housing. A sliding main valve body movably arranged in the main valve chamber in the axial direction is provided, and a plurality of communication passages for selectively communicating between the ports are provided in the main valve body. By moving the main valve body, it is possible to switch between the ports that communicate with each other, and three ports are opened side by side in the axial direction in the main valve chamber, and the three ports are in different positions around the axis, another three port is made to open aligned in the axial direction, said main valve body, the 1U to the two ports of the previous SL three ports selectively communicating A first slide valve body having a turn passage and a second slide valve body having a second U-turn passage for selectively communicating two of the other three ports are provided in the main valve chamber. By moving the main valve body, two of the three ports are communicated with each other through the first U-turn passage, and two of the other three ports are connected. Communicated through the second U-turn passage, the other one of the three ports and the other one of the other three ports pass through the main valve housing. A plurality of communication states that can be communicated with each other can be selectively taken , and the first slide valve body and the second slide valve body have the first U-turn passage and the second U-turn passage in opposite directions. The first slide valve body and the second slide valve body are integrally movable in the axial direction and are arranged in a back-to-back state so as to open, and in a direction perpendicular to the axis. It is characterized by being slidable with each other.

In a more specific preferred embodiment, the three ports are the first port, the second port, and the third port , and the other three ports are the fourth port, the fifth port, and the sixth port. The first U-turn passage is a port , and the first U-turn passage selectively communicates two ports of the first to third ports, and the second U-turn passage is two of the fourth to sixth ports. the number of ports not selectively communicating, by moving the main valve body in the main valve chamber, said second port and said first port is made to communicate with each other through the first 1U turn passage, the fourth The first communication state in which the port and the fifth port are communicated with each other through the second U-turn passage, and the third port and the sixth port are communicated with each other through the main valve housing, and the second port and the said The third port is communicated through the first U-turn passage, the fifth port and the sixth port are communicated through the second U-turn passage, and the first port and the fourth port are the main. a second communication state is caused to communicate through the valve housing, Ru is to obtain selective to take.

In a further preferred embodiment, the first port, second port, and a third port and the fourth port, fifth port, and a sixth port Ru provided at a position opposed.

In a more preferred embodiment, the tubular portion provided on one of the first slide valve body and the second slide valve body is fitted with the other of the first slide valve body and the second slide valve body. The convex portion is slidably fitted inside to be integrated.

In another preferred embodiment, an urging member that urges the first slide valve body and the second slide valve body in opposite directions between the first slide valve body and the second slide valve body. Are distributed.

In another preferred embodiment, a pressure chamber into which the high pressure fluid is introduced is provided between the first slide valve body and the second slide valve body.

In a more preferred embodiment, a relatively high pressure fluid is introduced into one of the first U-turn passage and the second U-turn passage, and a relatively low pressure fluid is introduced into the other of the first U-turn passage and the second U-turn passage. At the same time as being introduced, a part of the high-pressure fluid introduced into one of the first U-turn passage and the second U-turn passage is introduced into the pressure chamber.

In a more preferred embodiment, when viewed in a direction perpendicular to the axis, the pressure receiving area on the pressure chamber side of one of the first slide valve body and the second slide valve body is the first port, the second port, and the second port. It is made larger than the pressure receiving area on the main valve seat side where the third port is provided.

In another preferred embodiment, in the first communication state, the third port and the sixth port are communicated via the main valve chamber, and in the second communication state, the first port and the fourth port. Is communicated through the main valve chamber.

In a more preferred embodiment, a sealing material is provided to seal between the main valve chamber and the pressure chamber.

In another preferred embodiment, in the first communication state, the third port and the sixth port are communicated with each other through a lower gangway provided so as to penetrate the main valve body, and the second communication state is provided. In, the first port and the fourth port are communicated with each other through an upper gangway provided so as to penetrate the main valve body.

In a more preferred embodiment, the lower gangway and / or the upper gangway is composed of a straight passage having a constant passage diameter.

In a more preferred embodiment, the lower through-passage and / or the upper through-passage is a split passage that straddles the first slide valve body and the second slide valve body, and is among the split passages. A large-diameter portion is formed on one of the end portion on the first slide valve body side and the end portion on the second slide valve body side, and a fitting insertion tube portion to be inserted into the large-diameter portion is extended to the other. A sealing material is interposed between the large diameter portion and the fitting / inserting cylinder portion.

In a more preferred embodiment, the main valve chamber and the pressure chamber are always in communication with each other.

In another preferred embodiment, the capacity at which the high pressure fluid is selectively introduced and discharged, defined by a pair of first and second pistons, on one end side and the other end side of the main valve chamber in the main valve housing. Variable first and second operating chambers are provided, and the main valve body is arranged so as to be movable in the axial direction in conjunction with the first and second pistons, and the first and second operating chambers are provided. The introduction / discharge of the high-pressure fluid into the main valve chamber is controlled to move the first and second pistons, so that the main valve body is moved in the main valve chamber.

In a more preferred embodiment, the first piston and the second piston are integrally movably connected by a main connecting body, and the main valve body is reciprocated to the main connecting body to move the first and second pistons. It is connected, fitted, or engaged so that it moves with it.

In another preferred embodiment, one end side lid member which also serves as a stopper for preventing the movement of the first piston in the one end direction is fixed to one end of the main valve housing, and the second end of the main valve housing is fixed. The other end side lid member that also serves as a stopper that prevents the piston from moving in the other end direction is fixed.

In another preferred embodiment, the control of the introduction / discharge of the high-pressure fluid into the first and second operating chambers is controlled by the ports provided in the first and second operating chambers and the high-pressure portion of the six-way switching valve. It is done by a single four-way pilot valve connected to the low pressure section.

In the six-way switching valve according to the present invention, three ports are opened side by side in the axial direction in the main valve chamber, and three other ports are arranged at different positions around the axis from the three ports. The first U-turn passage, which is opened side by side in the axial direction and selectively communicates at least two of the three ports in the main valve body, and two of the other three ports. A second U-turn passage for selectively communicating the ports is provided, and by moving the main valve body in the main valve chamber, two of the three ports can be communicated through the first U-turn passage. Two of the other three ports are communicated through the second U-turn passage, and the other one of the three ports and the other three ports. It is possible to selectively take a plurality of communication states (flow paths) in which the other one port is communicated through the main valve housing. More specifically, the first port, the second port, and the third port are opened side by side in the main valve chamber in the axial direction, and the first port, the second port, and the third port are around the axis. The 4th port, the 5th port, and the 6th port are opened side by side in the axial direction at different positions in the main valve body, and at least two ports of the 1st to 3rd ports are selectively selected in the main valve body. A 1st U-turn passage and a 2nd U-turn passage for selectively communicating two of the 4th to 6th ports are provided, and by moving the main valve body in the main valve chamber, the first U-turn passage is provided. The 1st port and the 2nd port are communicated through the 1st U-turn passage, the 4th port and the 5th port are communicated through the 2nd U-turn passage, and the 3rd port and the 6th port are in the main valve housing. The first communication state in which the main valve chamber or the lower through path provided through the main valve body is communicated, and the second port and the third port are communicated through the first U-turn passage, and the first The 5th port and the 6th port are communicated with each other through the 2nd U-turn passage, and the 1st port and the 4th port are connected through the main valve chamber in the main valve housing or the upper through passage provided through the main valve body. It is possible to selectively take the second communication state and the communication state. Therefore, the main valve seat and main valve body provided with the port can be shortened (in the axial direction) as compared with the conventional six-way switching valve using the sliding main valve body, so that the valve seat surface and main valve of the main valve seat can be shortened. It becomes easier to secure the surface accuracy (flatness) of the sealing surface of the body, valve leakage can be suppressed, and fluid (for example, high-pressure fluid (refrigerant)) is flowed through the U-turn passage, so that pressure loss should be reduced. You can also.

In addition to the above, when the six-way switching valve according to the present invention is used in an environment such as a heat pump type heating / cooling system in which a high-temperature high-pressure refrigerant and a low-temperature low-pressure refrigerant flow, a U-turn passage through which the high-temperature high-pressure refrigerant flows and a low temperature Since the U-turn passages through which the low-pressure refrigerant flows are provided relatively far apart without passing through, for example, a metal main valve seat, the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant form a metal main valve seat. The amount of heat exchange (that is, heat loss) between them can be significantly reduced as compared with the conventional ones that are flowed in close proximity to each other, and therefore the efficiency of the system can be improved.

Further, in the six-way switching valve according to the present invention, the main valve body is arranged such that the first slide valve body having the first U-turn passage and the second slide valve body having the second U-turn passage are back-to-back. Since a pressure chamber into which the high-pressure fluid is introduced is provided between the first slide valve body and the second slide valve body, the first slide valve body and the second slide valve are provided by the high-pressure fluid introduced into the pressure chamber. The body is pressed (press-contacted) against the main valve seats provided with ports, and as mentioned above, the U-turn passage through which the high-temperature and high-pressure refrigerant flows and the U-turn passage through which the low-temperature and low-pressure refrigerant flows are even larger. Since they are provided apart from each other, valve leakage can be suppressed and the amount of heat exchange (that is, heat loss) between the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant can be further significantly reduced.

Issues, configurations, and effects other than those described above will be clarified by the following embodiments.

The vertical sectional view which shows the 1st communication state (during the cooling operation) of the 1st Embodiment of the 6-way switching valve which concerns on this invention. The vertical sectional view which shows the 2nd communication state (during the heating operation) of the 1st Embodiment of the 6-way switching valve which concerns on this invention. An enlarged vertical sectional view of a main part of the hexagonal switching valve shown in FIG. 1 in an enlarged manner. It is an enlarged view which shows the four-way pilot valve used for the six-way switching valve which concerns on this invention, (A) is the 1st communication state (during cooling operation) (when energization is OFF), (B) is a 2nd communication state. A vertical sectional view showing (during heating operation) and (when energization is ON). The vertical sectional view which shows the 1st communication state (during the cooling operation) of the 2nd Embodiment of the 6-way switching valve which concerns on this invention. The vertical sectional view which shows the 2nd communication state (during heating operation) of the 2nd Embodiment of the 6-way switching valve which concerns on this invention. FIG. 5 is a cross-sectional view taken along the line of sight of the UU arrow in FIG. In an example of a heat pump type heating / cooling system in which a six-way switching valve is used as a flow path switching valve, (A) is a schematic configuration diagram showing a cooling operation and (B) a schematic configuration diagram showing a heating operation.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

<First Embodiment>
1 and 2 are vertical cross-sectional views showing a first embodiment of the six-way switching valve according to the present invention, FIG. 1 is a first communication state (during cooling operation), and FIG. 2 is a second communication state (during cooling operation). It is a figure which shows (during heating operation).

In this specification, the description indicating the position and direction of up / down, left / right, front / back, etc. is added for convenience according to the drawings in order to avoid complicated explanation, and is actually incorporated into a heat pump type heating / cooling system or the like. It does not always point to the position or direction in the state of being struck.

Further, in each drawing, the gap formed between the members, the separation distance between the members, etc. are larger than the dimensions of each constituent member in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn small.

The six-way switching valve 1 of the illustrated embodiment is, for example, a slide type used as a six-way switching valve 180 in the heat pump type heating / cooling system 100 shown in FIGS. 8A and 8B described above, and is basically a cylinder type. The hexagonal valve main body 10 and a single electromagnetic four-way pilot valve 90 as a pilot valve are provided. The six ports provided in the six-way switching valve 1 of the present embodiment have the same reference numerals corresponding to the ports pA to pF of the six-way switching valve 180.

[Structure of hexagonal valve body 10]
The hexagonal valve main body 10 has a tubular main valve housing 11 made of metal such as brass or stainless steel, and the first operating chamber 31 and the first operating chamber 31 and the first operating chamber 31 are sequentially connected to the main valve housing 11 from one end side (upper end side). One piston 21, a main valve chamber 12, a second piston 22, and a second operating chamber 32 are arranged. Each of the first and second pistons 21 and 22 is provided with a spring-loaded packing whose outer peripheral portion is in pressure contact with the inner peripheral surface of the main valve housing 11 in order to airtightly partition the main valve housing 11. ..

An umbrella-shaped upper end side lid member 11A that also serves as a stopper that prevents the first piston 21 that defines the variable capacity first operating chamber 31 from moving upward is airtightly fixed to the upper end of the main valve housing 11. At the lower end of the main valve housing 11, there is an inverted umbrella-shaped lower end side lid member 11B that also serves as a stopper that prevents the second piston 22 that defines the variable capacity second operating chamber 32 from moving downward. It is airtightly fixed. Ports p11 and p12 for introducing and discharging a high-pressure fluid (refrigerant) into the first operating chamber 31 and the second operating chamber 32 are attached to the upper end side lid member 11A and the lower end side lid member 11B, respectively.

The main valve housing 11 (main valve chamber 12) is provided with a total of six ports.

Specifically, in the center of the left portion of the main valve chamber 12, for example, a metal first main valve seat (valve seat) 13 having a flat valve seat surface (right surface) is brazed to the main valve. Three ports (port pB, sequentially from the upper end side) consisting of pipe joints that are airtightly fixed to (inner circumference) of the housing 11 and extend to the left on the valve seat surface of the first main valve seat 13. Port pA, port pF) are vertically arranged (arranged in the axis O direction) and opened at approximately equal intervals.

Further, on the right center of the main valve chamber 12 (a position facing the first main valve seat 13, in other words, a position opposite to the axis O of the first main valve seat 13), the surface (left surface) thereof. ) Is a flat valve seat surface, for example, a metal second main valve seat (valve seat) 14 is airtightly fixed to (inner circumference) of the main valve housing 11 by brazing or the like, and the second main valve thereof. On the valve seat surface of the seat 14, three ports (port pC, port pD, port pE in order from the upper end side) consisting of pipe joints extending to the right are arranged vertically (arranged in the axis O direction). It is opened at equal intervals.

Each port (port pB, port pA, port pF) provided on the first main valve seat 13 and each port (port pC, port pD, port pE) provided on the second main valve seat 14 face each other. It is set at the position (opposite to the axis O), and in this example, the diameters of the ports pA to pF provided on the first main valve seat 13 and the second main valve seat 14 are set to substantially the same diameter. Has been done.

In the main valve chamber 12, both side surfaces (left surface and right surface) are slidably brought into contact with the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14, respectively, in a race track type. A sliding main valve body 15 having an annular sealing surface and a rectangular cross section is arranged so as to be movable in the axis O direction (vertical direction).

The main valve body 15 is made of, for example, synthetic resin, and has a first slide valve body 15A on the first main valve seat 13 side (left side) and a second slide valve body 15B on the second main valve seat 14 side (right side). And are arranged in a back-to-back state.

On the left side of the first slide valve body 15A (opposite to the side of the second slide valve body 15B), two adjacent ports of the three ports opened on the valve seat surface of the first main valve seat 13 A first U-turn passage (communication passage) 16A is provided, which is composed of a bowl-shaped depression having a size capable of selectively communicating ports (port pB and port pA, or port pA and port pF). Further, on the right side of the second slide valve body 15B (the side opposite to the side of the first slide valve body 15A), two adjacent ports of the three ports opened on the valve seat surface of the second main valve seat 14 are adjacent to each other. A second U-turn passage (communication passage) 16B having a bowl-shaped depression having a size capable of selectively communicating the ports (port pC and port pD, or port pD and port pE) is opened.

On the other hand, on the left surface of the second slide valve body 15B (the surface facing the first slide valve body 15A), a tubular portion 15b having substantially the same shape as the outer shape of the second slide valve body 15B is extended (to the left). On the right side of the first slide valve body 15A (the surface facing the second slide valve body 15B), a cylinder slightly smaller than the outer shape of the first slide valve body 15A (in other words, the outer shape of the second slide valve body 15B). The shape-shaped fitting convex portion 15a is projected (to the right). The fitting convex portion 15a is slidably fitted into the tubular portion 15b (with an O-ring 18 sandwiched between them) so that the first slide valve body 15A and the second slide valve body 15B can be separated from each other. Left-right direction (direction perpendicular to the axis O and provided on the first main valve seat 13 (port pB, port pA, port pF) and each port provided on the second main valve seat 14 (port pB, port pA, port pF) Port pC, port pD, port pE) are slightly movable to each other (in the direction opposite to each other), and are integrally movable in the vertical direction (axis O direction).

The arrangement relationship between the fitting convex portion 15a of the first slide valve body 15A and the tubular portion 15b of the second slide valve body 15B may be reversed. That is, the first slide valve body 15A is provided with a tubular portion, the second slide valve body 15B is provided with a fitting convex portion, and the tubular portion of the first slide valve body 15A is provided with a fitting convex portion of the second slide valve body 15B. The first slide valve body 15A and the second slide valve body 15B may be integrated by fitting the portion internally.

Further, in the illustrated example, between the right surface of the first slide valve body 15A (the portion inside the fitting convex portion 15a) and the left surface of the second slide valve body 15B (the portion inside the fitting convex portion 15a). In addition to forming a slight gap, the first slide valve body 15A (the bottom of the first U-turn passage 16A in the first slide valve body 15A) is provided with a communication hole 16a formed of a lateral hole for communicating the first U-turn passage 16A and the gap. An O-ring 18 as a sealing material is provided between the fitting convex portion 15a and the tubular portion 15b (specifically, in an annular groove provided on the outer periphery of the fitting convex portion 15a). It is being mediated.

Therefore, the portion inside the O-ring 18 including the gap is a pressure chamber 17 into which a high-pressure fluid (refrigerant) is introduced from the port (discharge side high-pressure port) pA through the first U-turn passage 16A and the communication hole 16a. Has been done. The pressure chamber 17 and the main valve chamber 12 are sealed (sealed) by the O-ring 18 arranged between them.

Here, as can be easily understood by referring to FIG. 3 together with FIGS. 1 and 2, the pressure chamber 17 side (right side side) of the first slide valve body 15A is viewed in the left-right direction (direction perpendicular to the axis O). ) Is larger than the pressure receiving area Sa on the first main valve seat 13 side (left side).

More specifically, it is the projected area of the pressure chamber 17 with respect to a plane perpendicular to the left-right direction, and the first slide valve body 15A (right side) is in the left direction due to the high-pressure refrigerant introduced into the pressure chamber 17. The projected area of the surface receiving pressure (pressure receiving area Sb) is the projected area of the annular sealing surface on the first main valve seat 13 side with respect to the plane perpendicular to the left-right direction, and the port (inside the annular sealing surface). The first slide valve body 15A (left surface) is made larger than the projected area (pressure receiving area Sa) of the surface receiving the pressure in the right direction by the high pressure refrigerant flowing in the first slide valve body 15A.

As a result, the high-pressure refrigerant is introduced into the first U-turn passage 16A via the port (discharge side high-pressure port) pA, and a part of the high-pressure refrigerant introduced into the first U-turn passage 16A is pressured through the communication hole 16a. When the chamber 17 is filled, the pressure received from the pressure chamber 17 (high pressure refrigerant) (more specifically, the pressure received from the pressure chamber 17 (high pressure refrigerant) and the refrigerant flowing through the second U-turn passage 16B (low pressure refrigerant)). The right surface (annular seal surface) of the second slide valve body 15B is pressed against the valve seat surface of the second main valve seat 14 by the pressure difference from the pressure received from the pressure chamber 17 (high pressure refrigerant). The left surface (annular seal surface) of the first slide valve body 15A is pressed against the valve seat surface of the first main valve seat 13 by the differential pressure between the pressure and the pressure received from the refrigerant (high pressure refrigerant) flowing through the first U-turn passage 16A. It is supposed to be.

Further, in this example, a plurality of spring receiving holes 19a and 19b are formed on the right surface of the first slide valve body 15A and the left surface of the second slide valve body 15B, respectively, and the first spring receiving holes 19a and 19b are formed in the spring receiving holes 19a and 19b. A compression coil spring (biasing member) 19 that urges the slide valve body 15A and the second slide valve body 15B in opposite directions (pulling directions) is contracted (in the illustrated example, the first slide valve body). Compression coil springs 19 are loaded in two upper and lower positions between the right side of the 15A and the left side of the second slide valve body 15B), which also causes the left side (annular seal surface) of the first slide valve body 15A to be. While being pressed (pressed) against the valve seat surface of the first main valve seat 13, the right surface (annular seal surface) of the second slide valve body 15B is pressed against the valve seat surface of the second main valve seat 14 (pressed). Pressed).

In this example, reinforcing pins 15c and 15d for maintaining the shape are located in the front-rear direction at substantially the center of the first U-turn passage 16A of the first slide valve body 15A and the second U-turn passage 16B of the second slide valve body 15B. It is erected toward.

As described above, in the main valve body 15, the first slide valve body 15A and the second slide valve body 15B are integrally moved in the axial direction O direction, and the port pF is provided as shown in FIG. The port pB and the port pA are opened and communicated with each other through the first U-turn passage 16A of the first slide valve body 15A, and the port pE is opened and the port pC and the port pD are connected to the second U-turn of the second slide valve body 15B. The cooling position (upper end position) communicating via the passage 16B and the port pB are opened and the port pA and the port pF are connected via the first U-turn passage 16A of the first slide valve body 15A as shown in FIG. It is possible to selectively take a heating position (lower end position) in which the port pC is opened and the port pD and the port pE are communicated with each other via the second U-turn passage 16B of the second slide valve body 15B. ..

The first slide valve body 15A of the main valve body 15 is located directly above two of the three ports (port pB and port pA, or port pA and port pF) except when moving. The second slide valve body 15B of the main valve body 15 is located directly above two of the three ports (port pC and port pD, or port pD and port pE) except when moving. At this time, the pressure from the pressure chamber 17 (high pressure refrigerant introduced into) provided between the first slide valve body 15A and the second slide valve body 15B and the urging force of the compression coil spring 19 cause the left and right sides, respectively. It is pressed and pressed against the valve seat surfaces of the first main valve seat 13 and the second main valve seat 14.

The first piston 21 and the second piston 22 are integrally movably connected by, for example, a vertically long rectangular plate-shaped main connecting body 25. The first slide valve body 15A and the second slide valve body 15B of the main valve body 15 are slidably fitted to the main connecting body 25 from the left and right sides (more specifically, the second slide valve body). (The tubular portion 15b of the 15B is fitted so as to be slidably inscribed) For example, a rectangular main opening 25a with rounded corners is formed, and the main valve body 15 is formed of the first and second pistons 21 and 22. Along with the reciprocating movement, it is pushed by the main opening 25a portion of the main connecting body 25 (here, the tubular portion 15b portion of the second slide valve body 15B is pressed) and the cooling position (upper end position) and heating. It is designed to go back and forth between the position (lower end position).

Further, the main connecting body 25 has a port pF and a second main valve on the lower side of the first main valve seat 13 when the main valve body 15 takes a cooling position (upper end position) above and below the main opening 25a. A circular opening 25b is formed in a portion located substantially beside the port pE on the lower side of the seat 14, and a port on the upper side of the first main valve seat 13 when the main valve body 15 takes a heating position (lower end position). A circular opening 25c is formed at a portion located substantially right beside the pB and the port pC on the upper side of the second main valve seat 14.

[Operation of hexagonal valve body 10]
Next, the operation of the hexagonal valve main body 10 having the above-described configuration will be described.

When the main valve body 15 arranged in the main valve housing 11 is in the heating position (lower end position) (second communication state as shown in FIG. 2), the first is via the four-way pilot valve 90 described later. When the 2 working chamber 32 is communicated with the port pA which is the discharge side high pressure port and the 1st working chamber 31 is communicated with the port pD which is the suction side low pressure port, a high temperature and high pressure refrigerant is introduced into the 2nd working chamber 32. At the same time, the high temperature and high pressure refrigerant is discharged from the first operating chamber 31. Therefore, the pressure of the second operating chamber 32 on the other end side (lower end side) of the main valve chamber 12 becomes higher than the pressure of the first operating chamber 31 on the one end side (upper end side) of the main valve chamber 12, which is shown in FIG. As described above, the first and second pistons 21, 22 and the main valve body 15 move upward, the first piston 21 is abutted and locked to the upper end side lid member 11A, and the main valve body 15 is in the cooling position (upper end). Position) (first communication state as shown in FIG. 1) is taken.

As a result, the port pA and the port pB are communicated with each other (via the first U turn passage 16A), the port pC and the port pD are communicated with each other (via the second U turn passage 16B), and the port pE and the port pF are communicated with each other. Since the and are communicated (via the main valve chamber 12), the cooling operation is performed in the heat pump type heating / cooling system 100 as shown in FIGS. 8A and 8B.

When the main valve body 15 is in the cooling position (upper end position) (first communication state as shown in FIG. 1), the first operating chamber 31 is connected to the discharge side high pressure port via the four-way pilot valve 90 described later. When the second operating chamber 32 is communicated with the port pD which is the suction side low pressure port while communicating with a certain port pA, a high temperature and high pressure refrigerant is introduced into the first operating chamber 31 and the temperature is high from the second operating chamber 32. High pressure refrigerant is discharged. Therefore, the pressure of the first operating chamber 31 on one end side (upper end side) of the main valve chamber 12 is higher than the pressure of the second operating chamber 32 on the other end side (lower end side) of the main valve chamber 12, which is shown in FIG. The first and second pistons 21, 22 and the main valve body 15 move downward, the second piston 22 is abutted and locked to the lower end side lid member 11B, and the main valve body 15 is in the heating position (lower end). Position) (second communication state as shown in FIG. 2) is taken.

As a result, the port pA and the port pF are communicated (via the first U turn passage 16A), the port pE and the port pD are communicated (via the second U turn passage 16B), and the port pC and the port pB are communicated with each other. Since the and are communicated (via the main valve chamber 12), the heating operation is performed in the heat pump type heating / cooling system 100 as shown in FIGS. 8A and 8B.

[Structure of four-way pilot valve 90]
The structure of the four-way pilot valve 90 as a pilot valve is well known, and as shown in the enlarged drawings of FIGS. A valve case 92 made of a cylindrical straight pipe to which a coil 91 is externally fitted and fixed is provided, and a suction element 95, a compression coil spring 96, and a plunger 97 are sequentially arranged in the valve case 92 from the base end side. Being present.

The left end of the valve case 92 is hermetically sealed to the flange-shaped portion (outer terrace portion) of the attractor 95 by welding or the like, and the attractor 95 is attached to the cover case 91A that covers the outer periphery of the electromagnetic coil 91 for energization excitation. It is fastened and fixed by the bolt 92B.

On the other hand, a lid member 98 with a filter having a thin tube insertion port (high pressure introduction port a) for introducing a high pressure refrigerant is airtightly attached to the right end opening of the valve case 92 by welding, brazing, caulking or the like. The area surrounded by the lid member 98, the plunger 97, and the valve case 92 is the valve chamber 99. The valve chamber 99 is entered from the port (discharge side high pressure port) pA via a flexible high pressure thin tube #a that is airtightly inserted into the thin tube insertion port (high pressure introduction port a) of the lid member 98. High temperature and high pressure refrigerants are being introduced.

Further, a valve seat 93 whose inner end surface is a flat valve seat surface is airtightly joined between the plunger 97 and the lid member 98 in the valve case 92 by brazing or the like. On the valve seat surface (inner end surface) of the above, ports b and ports (low pressure on the suction side) are sequentially connected to the first operating chamber 31 of the hexagonal valve main body 10 described above via a thin tube # b from the tip side (right end side). Port) The port c connected to the pD via the thin tube #c and the port d connected to the second operating chamber 32 via the thin tube #d are spaced apart from each other along the longitudinal direction (left-right direction) of the valve case 92. It is opened side by side and opened.

The plunger 97 arranged to face the suction element 95 is basically cylindrical, and is slidably arranged in the valve case 92 in the axial direction (direction along the center line L of the valve case 92). .. At the end of the plunger 97 opposite to the suction element 95 side, a valve body holder 94A that holds the valve body 94 slidably in the thickness direction on the free end side holds the base end portion together with the fitting 94B. It is attached and fixed by press fitting, caulking, etc. A leaf spring 94C that urges the valve body 94 in the direction of pressing the valve body 94 against the valve seat 93 (thickness direction) is attached to the valve body holder 94A. The valve body 94 is in contact with the valve seat surface of the valve seat 93 in order to switch the communication state between the ports b, c, and d that open on the valve seat surface of the valve seat 93. The valve seat surface slides as the plunger 97 moves in the left-right direction.

Further, the valve body 94 has a size such that the adjacent ports bc and cd of the three ports b to d opened on the valve seat surface of the valve seat 93 can be selectively communicated with each other. A recess 94a is provided.

Further, the compression coil spring 96 is compressed between the suction element 95 and the plunger 97 to urge the plunger 97 in the direction of pulling it away from the suction element 95 (to the right in the figure). In the example, the valve seat 93 (the left end portion of the valve seat 93) is used as a stopper that prevents the plunger 97 from moving to the right. Needless to say, other configurations can be adopted as the configuration of this stopper.

The four-way pilot valve 90 is attached to an appropriate position such as the back side of the six-way valve main body 10 via the attachment 92A.

[Operation of four-way pilot valve 90]
In the four-way pilot valve 90 having the above-described configuration, when the electromagnetic coil 91 is energized and turned off, the plunger 97 is subjected to the urging force of the compression coil spring 96 as shown in FIGS. 1 and 4 (A). The right end is pushed to a position where it contacts the valve seat 93. In this state, the valve body 94 is located on the port b and the port c, and the port b and the port c communicate with each other by the recess 94a, and the port d and the valve chamber 99 communicate with each other. ) The high-pressure fluid flowing into pA is introduced into the second working chamber 32 via the high-pressure thin tube #a → valve chamber 99 → port d → thin tube # d → port p12, and the high-pressure fluid in the first working chamber 31 is ported. It flows from p11 → thin tube # b → port b → recess 94a → port c → thin tube # c → port (low pressure port on the suction side) pD and is discharged.

On the other hand, when the energization of the electromagnetic coil 91 is turned on, as shown in FIGS. 2 and 4B, the position where the left end of the plunger 97 comes into contact with the suction element 95 due to the suction force of the suction element 95. Is attracted to (against the urging force of the compression coil spring 96). At this time, the valve body 94 is located on the port c and the port d, and the port c and the port d communicate with each other by the recess 94a, and the port b and the valve chamber 99 communicate with each other. Therefore, the port (discharge side high pressure port) The high-pressure fluid flowing into pA is introduced into the first working chamber 31 via the high-pressure thin tube #a → valve chamber 99 → port b → thin tube # b → port p11, and the high-pressure fluid in the second working chamber 32 is introduced into the port p12. → Thin tube # d → Port d → Recessed 94a → Port c → Thin tube # c → Port (low pressure port on the suction side) pD is discharged.

Therefore, when the energization of the electromagnetic coil 91 is turned off, the main valve body 15 of the hexagonal valve main body 10 shifts from the heating position (second communication state) to the cooling position (first communication state), and the flow path as described above. While the switching is performed, when the energization of the electromagnetic coil 91 is turned on, the main valve body 15 of the hexagonal valve main body 10 shifts from the cooling position (first communication state) to the heating position (second communication state), and is described above. The flow path is switched as described above.

As described above, in the six-way switching valve 1 of the present embodiment, the high-pressure fluid (port pA which is a high-pressure portion) circulating in the six-way switching valve 1 is switched by switching the energization of the electromagnetic four-way pilot valve 90 by ON / OFF. The main valve is moved by moving the main valve body 15 constituting the hexagonal valve main body 10 in the main valve chamber 12 by utilizing the differential pressure between the flowing fluid) and the low pressure fluid (the fluid flowing through the port pD which is the low pressure portion). The communication state between the six ports provided in the housing 11 is switched, and in the heat pump type heating / cooling system 100 as shown in FIGS. 8A and 8B, the heating operation is switched to the cooling operation, and the operation is switched. , It is possible to switch from cooling operation to heating operation.

[Action and effect of hexagonal switching valve 1]
As can be understood from the above description, in the hexagonal switching valve 1 of the present embodiment, the port pB, the port pA, and the port pF are opened side by side in the axis O direction in the main valve chamber 12, and the port pB is opened. Port pC, port pD, and port pE are opened side by side in the axis O direction at different positions around the axis O from the port pA and the port pF, and the first U-turn passage 16A and the port pF are formed in the main valve body 15. A second U-turn passage 16B is provided, and by moving the main valve body 15 in the main valve chamber 12, port pA and port pB are communicated with each other via the first U-turn passage 16A, and port pC and port pD are connected. The first communication state in which the port pE and the port pF are communicated via the main valve chamber 12 and the port pA and the port pF are communicated via the first U-turn passage 16A. The second communication state, in which the port pE and the port pD are communicated with each other through the second U-turn passage 16B and the port pC and the port pB are communicated with each other via the main valve chamber 12, can be selectively taken. Has been done. Therefore, as compared with the six-way switching valve using the conventional sliding main valve body, the main valve seats (first main valve seat 13 and second main valve seat 14) and the main valve body 15 (axis line O) provided with ports are provided. Since it can be shortened (in the direction), it becomes easier to secure the surface accuracy (flatness) of the valve seat surface of the main valve seats (first main valve seat 13 and second main valve seat 14) and the sealing surface of the main valve body 15. Since valve leakage can be suppressed and a fluid (for example, high-pressure fluid (refrigerant)) is flowed through the first U-turn passage 16A, pressure loss can be reduced.

Further, in the present embodiment, the fluid (for example, low-pressure refrigerant) flowing in the hexagonal valve main body 10 is flowed through the second U-turn passage 16B, and the fluid (for example, medium-pressure refrigerant) flows in the main valve chamber 12 in the left-right direction. Since the fluid is flowed (straight), this also makes it possible to reduce the pressure loss.

In addition to the above, when the six-way switching valve 1 according to the present invention is used in an environment where a high-temperature high-pressure refrigerant and a low-temperature low-pressure refrigerant flow, such as a heat pump type heating / cooling system, a first U-turn passage through which the high-temperature and high-pressure refrigerant flows. Since the second U-turn passage 16B through which the 16A and the low-temperature low-pressure refrigerant flow are provided relatively far apart without passing through, for example, a metal main valve seat, the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant are made of metal. The amount of heat exchange (that is, heat loss) between them can be significantly reduced compared to the conventional one that flows in close proximity through the main valve seat of the, and therefore the efficiency of the system can be improved. can get.

Further, in the six-way switching valve 1 according to the present invention, the main valve body 15 has a first slide valve body 15A having a first U-turn passage 16A and a second slide valve body 15B having a second U-turn passage 16B in a first U-turn. The passage 16A and the second U-turn passage 16B are arranged so as to open in opposite directions (in other words, so that the annular sealing surfaces which are sliding surfaces are opposite to each other) so as to be back-to-back. Since the pressure chamber 17 into which the high-pressure fluid is introduced is provided between the slide valve body 15A and the second slide valve body 15B, the high-pressure fluid introduced into the pressure chamber 17 provides the first slide valve body 15A and the second slide valve body 15A. The slide valve body 15B is pressed (press-contacted) against the first main valve seat 13 and the second main valve seat 14 provided with ports, respectively, and as described above, the first U-turn passage through which the high-temperature and high-pressure refrigerant flows. Since the second U-turn passage 16B through which the 16A and the low-temperature low-pressure refrigerant flow are provided further apart (only for the pressure chamber 17 minutes), valve leakage can be suppressed, and the high-temperature high-pressure refrigerant and the low-temperature low-pressure refrigerant can also be suppressed. The amount of heat exchange between the refrigerants (that is, heat loss) can be further significantly reduced.

<Second Embodiment>
5 and 6 are vertical cross-sectional views showing a second embodiment of the six-way switching valve according to the present invention, FIG. 5 is a first communication state (during cooling operation), and FIG. 6 is a second communication state (during cooling operation). It is a figure which shows (during heating operation).

The six-way switching valve 2 of the second embodiment shown in the drawing is different from the six-way switching valve 1 of the first embodiment described above in the configuration of the main valve body mainly constituting the hexagonal valve main body, and other configurations are omitted. Since they are the same, the parts corresponding to the respective parts of the hexagonal switching valve 1 are designated by a common reference numeral to omit the duplicate description, and the differences will be mainly described below.

The six-way switching valve 2 of the illustrated embodiment is used as the six-way switching valve 180 in the heat pump type heating / cooling system 100 shown in FIGS. 8 (A) and 8 (B) described above, as in the case of the six-way switching valve 1 of the first embodiment. Although it is a slide type, in this example, it is fixed to the main valve housing 11 (main valve chamber 12) and the main valve housing 11 constituting the hexagonal valve main body 10 as compared with the hexagonal switching valve 1 of the first embodiment. The first main valve seat 13, the second main valve seat 23, and the sliding main valve body 15 and the like movably arranged in the main valve chamber 12 are formed slightly longer in the vertical direction (axis O direction). ing.

The main valve body 15 is the same as the hexagonal switching valve 1 of the first embodiment, that is, the first slide valve body 15A on the first main valve seat 13 side (left side) and the second main valve seat 14 side (right side). The second slide valve body 15B and the second slide valve body 15B have a two-divided structure arranged in a back-to-back state, and the first U-turn passage 16A is opened in the center on the left side of the first slide valve body 15A, and the second A second U-turn passage 16B is provided in the center on the right side of the slide valve body 15B.

In addition to the above, in the present embodiment, the first U-turn passage 16A and the second U-turn passage 16B in the main valve body 15 are sandwiched below and above (in other words, the first U-turn passage 16A and the second U-turn passage 16B). In), the lower through-passage (communication passage) 52 that can communicate the port pE and the port pF when the cooling position (upper end position) is taken as shown in FIG. 5, and the heating position as shown in FIG. An upper through-passage (communication passage) 51 capable of communicating the port pC and the port pB when the (lower end position) is taken is provided.

The upper gangway 51 and the lower gangway 52 are provided so as to penetrate the main valve body 15 in the left-right direction (direction perpendicular to the axis O), and here, the passage diameter (inner diameter) is constant. Moreover, it is a straight passage having substantially the same diameter as each port pA to pE.

Specifically, the first slide valve body 15A constituting the left portion of the main valve body 15 has a diameter substantially the same as the diameter of each port pA to pE in the vertical direction above and below the first U turn passage 16A. 1 Upper through-passage portion 51A and first lower through-passage portion 52A are established, respectively. When the main valve body 15 (the first slide valve body 15A) is in the cooling position (upper end position), the left side opening of the first upper through-passage portion 51A is in contact with the first main valve seat 13 (upper part). The first U-turn passage 16A is located right beside the port pB and the port pA, the left side opening of the first lower gangway portion 52A is located right beside the port pF, and the main valve body 15 (of the main valve body 15) is closed. When the first slide valve body 15A) is in the heating position (lower end position), the left side opening of the first lower through-passage portion 52A is brought into contact with the first main valve seat 13 (lower portion) and closed. The dimensions and shape of each part are set so that the first U-turn passage 16A is located right beside the port pA and the port pF, and the left side opening of the first upper gangway portion 51A is located right beside the port pB. ..

Further, in the second slide valve body 15B constituting the right portion of the main valve body 15, the first upper through-passage portion 51A and the first lower through-passage are provided above and below the second U-turn passage 16B in the left-right direction. A second upper through-passage portion 51B and a second lower through-passage portion 52B having the same diameter (same passage diameter) as the portion 52A are opened, respectively. The second upper through-passage section 51B and the second lower through-passage section 52B are located right next to the first upper through-passage section 51A and the first lower through-passage section 52A of the first slide valve body 15A. .. When the main valve body 15 (the second slide valve body 15B) is in the cooling position (upper end position), the right side opening of the second upper through-passage portion 51B is in contact with the second main valve seat 14 (upper part). The second U-turn passage 16B is located right beside the port pC and the port pD, the right side opening of the second lower gangway portion 52B is located right beside the port pE, and the main valve body 15 (of the main valve body 15) is closed. When the second slide valve body 15B) is in the heating position (lower end position), the right side opening of the second lower through-passage portion 52B is brought into contact with the second main valve seat 14 (lower portion) and closed. The dimensions and shape of each part are set so that the second U-turn passage 16B is located right next to the port pD and the port pE, and the right side opening of the second upper gangway portion 51B is located right next to the port pC. ..

A linear upper gangway (communication passage) composed of a first upper gangway portion 51A and a second upper gangway portion 51B by combining the two members of the first slide valve body 15A and the second slide valve body 15B. A linear lower gangway (communication passage) 52 composed of 51, a first lower gangway portion 52A, and a second lower gangway portion 52B is formed.

Further, as described above, the upper gangway 51 and the lower gangway 52 are split passages straddling the first slide valve body 15A and the second slide valve body 15B of the main valve body 15. The following measures have been taken to ensure the sealing performance. That is, to explain on behalf of the upper gangway 51, a large diameter portion 54 is provided at the left end portion (inner peripheral portion) of the second upper gangway portion 51B of the second slide valve body 15B constituting the upper gangway 51. Along with the formation, a cylindrical fitting / inserting cylinder portion 53 slidably inserted into the large diameter portion 54 is extended at the right end portion of the first upper through-passage portion 51A of the first slide valve body 15A. An O-ring 55 as a sealing material (in a compressed state) is interposed between the large diameter portion 54 and the fitting / inserting cylinder portion 53 (specifically, an annular groove provided on the outer periphery of the fitting / inserting cylinder portion 53). Has been done. The lower gangway 52 has the same configuration.

In the present embodiment, in the upper through-passage 51 provided in the upper part of the main valve body 15 and the lower through-passage 52 provided in the lower part of the main valve body 15, the fitting / inserting cylinder portion 53 becomes the large-diameter portion 54. By being slidably fitted (with an O-ring 55 sandwiched between them), the first slide valve body 15A and the second slide valve body 15B are slidably fitted in the left-right direction (axis line O) as in the first embodiment. It is said that it is slightly movable with respect to each other (in the direction perpendicular to the vertical direction) and is integrally movable in the vertical direction (axis O direction).

The arrangement relationship between the fitting insertion tube portion 53 of the first slide valve body 15A and the large diameter portion 54 of the second slide valve body 15B may be reversed. That is, the first slide valve body 15A is provided with a large diameter portion, the second slide valve body 15B is provided with a cylindrical fitting / inserting cylinder portion, and the large diameter portion of the first slide valve body 15A is provided with the second slide valve body 15B. The first slide valve body 15A and the second slide valve body 15B may be integrated by fitting the fitting insertion tube portion internally.

Further, in the present embodiment, the center of the right surface of the first slide valve body 15A (the portion between the upper and lower fitting / inserting cylinder portions 53) and the center of the left surface of the second slide valve body 15B (the portion between the upper and lower large diameter portions 54). ), A slight gap is formed, and the first slide valve body 15A (the bottom of the first U-turn passage 16A in the) communicates with a lateral hole that communicates the first U-turn passage 16A and the gap. The hole 16a is provided, and the portion including the gap (that is, the central portion of the main valve body 15) is a high-pressure fluid (that is, a high-pressure fluid (that is, a central portion of the main valve body 15) from the port (discharge side high-pressure port) pA via the first U-turn passage 16A and the communication hole 16a. The pressure chamber 17 into which the refrigerant) is introduced is provided, but as can be clearly seen with reference to FIG. 7, the pressure chamber 17 and the main valve chamber 12 are always in communication with each other.

That is, in the first embodiment, the pressure chamber 17 is sealed from the main valve chamber 12 by the O-ring 18, and the main valve chamber 12 is filled with the medium pressure fluid (refrigerant) introduced from the port pE or the port pC. However, in the second embodiment, the pressure chamber 17 and the main valve chamber 12 are always in communication with each other, and the main valve chamber 12 is filled with the high-pressure fluid (refrigerant) introduced through the pressure chamber 17. Will be.

In this example as well, as in the first embodiment, the pressure receiving area Sb on the pressure chamber 17 side (right side) in the first slide valve body 15A is the first when viewed in the left-right direction (direction perpendicular to the axis O). A compression coil spring that is larger than the pressure receiving area Sa on the main valve seat 13 side (left side) and urges them between the first slide valve body 15A and the second slide valve body 15B in opposite directions. 19 is reduced, whereby the left surface (annular seal surface) of the first slide valve body 15A is pressed (pressed) against the valve seat surface of the first main valve seat 13, and the second slide valve is pressed. The right side (annular seal surface) of the body 15B is pressed (pressed) against the valve seat surface of the second main valve seat 14. However, in this example, the main valve chamber 12 is filled with the high-pressure fluid (refrigerant) introduced through the pressure chamber 17, and the first slide valve body 15A and the second slide valve body 15B are entirely covered (mainly). Since the surface exposed to the valve chamber 12) receives high pressure, the left surface (annular sealing surface) of the first slide valve body 15A is strongly pressed against the valve seat surface of the first main valve seat 13, and the first The right surface (annular seal surface) of the two-slide valve body 15B is strongly pressed against the valve seat surface of the second main valve seat 14.

As described above, the main valve body 15 has the first slide valve body 15A and the second slide valve body 15B integrally moved in the axis O direction, and has the port pB as shown in FIG. The port pA is communicated with the first slide valve body 15A via the first U turn passage 16A, the port pC and the port pD are communicated with each other via the second U turn passage 16B of the second slide valve body 15B, and the port pF. And the port pE are communicated via the lower gangway 52 (the first lower gangway 52A of the first slide valve body 15A and the second lower gangway 52B of the second slide valve 15B). (Upper end position) and port pA and port pF as shown in FIG. 6 are communicated with each other via the first U-turn passage 16A of the first slide valve body 15A, and port pD and port pE are connected to each other through the second slide valve. The port pB and the port pC are communicated with each other through the second U-turn passage 16B of the body 15B, and the upper through-passage 51 (the first upper through-passage portion 51A of the first slide valve body 15A and the second slide valve body 15B). 2 It is possible to selectively take a heating position (lower end position) to communicate with each other via the upper through-passage portion 51B).

The first slide valve body 15A of the main valve body 15 is located directly above the three ports (port pB, port pA, port pF), and the second slide valve body 15B of the main valve body 15 has three ports. From the pressure chamber 17 (high pressure refrigerant introduced into) located directly above the ports (port pC, port pD, port pE) and provided between the first slide valve body 15A and the second slide valve body 15B. The valve seat surfaces of the first main valve seat 13 and the second main valve seat 14 are pressed to the left and right by the pressure of the compression coil spring 19, the urging force of the compression coil spring 19, and the pressure from the main valve chamber 12 (the high-pressure refrigerant introduced into). It is pressed against.

In this example, when the main valve body 15 takes the cooling position (upper end position), the lower port pF of the first main valve seat 13 and the lower port pE of the second main valve seat 14 are the main valves. It communicates through the lower through-passage 52 provided in the body 15, and when the main valve body 15 takes the heating position (lower end position), the upper port pB and the second main valve seat of the first main valve seat 13 Since the port pC on the upper side of the 14 is communicated with the upper port pC provided in the main valve body 15 via the upper through-passage 51, in the main connecting body 25 connecting the first piston 21 and the second piston 22, the first The circular openings 25b and 25c in the embodiment are omitted.

In the hexagonal valve main body 10 having the above-described configuration, when the main valve body 15 arranged in the main valve housing 11 is in the heating position (lower end position) (second communication state as shown in FIG. 6). In, when the four-way pilot valve 90 having the same configuration as that of the first embodiment is controlled (that is, the energization of the four-way pilot valve 90 to the electromagnetic coil 91 is turned off), the main valve body 15 is placed in the cooling position (upper end). Position) (first communication state as shown in FIG. 5) is taken.

As a result, the port pA and the port pB are communicated with each other (via the first U turn passage 16A), the port pC and the port pD are communicated with each other (via the second U turn passage 16B), and the port pE and the port pF are communicated with each other. Since the and are communicated (via the lower through passage 52), the cooling operation is performed in the heat pump type heating / cooling system 100 as shown in FIGS. 8A and 8B.

On the other hand, when the main valve body 15 is in the cooling position (upper end position) (first communication state as shown in FIG. 5), the four-way pilot valve 90 having the same configuration as that of the first embodiment is controlled ( That is, when the four-way pilot valve 90 turns on the electromagnetic coil 91), the main valve body 15 takes a heating position (lower end position) (second communication state as shown in FIG. 6).

As a result, the port pA and the port pF are communicated with each other (via the first U turn passage 16A), the port pE and the port pD are communicated with each other (via the second U turn passage 16B), and the port pC and the port pB are communicated with each other. Is communicated (via the upper through-passage 51), so that the heating operation is performed in the heat pump type heating / cooling system 100 as shown in FIGS. 8A and 8B.

As described above, also in the six-way switching valve 2 of the present embodiment, similarly to the six-way switching valve 1 of the first embodiment, the six-way switching valve 2 is switched by switching the energization of the electromagnetic four-way pilot valve 90 by ON / OFF. The main valve body 15 constituting the hexagonal valve main body 10 by utilizing the differential pressure between the high-pressure fluid (fluid flowing through the port pA which is the high-pressure portion) and the low-pressure fluid (the fluid flowing through the port pD which is the low-pressure portion) flowing inside. By moving the above in the main valve chamber 12, the communication state between the six ports provided in the main valve housing 11 is switched, and the heat pump type heating and cooling as shown in FIGS. 8 (A) and 8 (B) is switched. In the system 100, it is possible to switch from the heating operation to the cooling operation and from the cooling operation to the heating operation.

As can be understood from the above description, in the six-way switching valve 2 of the present embodiment, in addition to obtaining the same action and effect as the six-way switching valve 1 of the first embodiment, the cooling position (first communication). In the state), a straight lower through-passage 52 (in other words, consisting of a straight passage having a constant passage diameter in the left-right direction) provided with the port pE and the port pF penetrating the main valve body 15 is provided. In the heating position (second communication state), the port pC and the port pB are linear (in other words, the passage diameter is constant in the left-right direction) provided through the main valve body 15. It is communicated through an upper gangway 51 (consisting of a straight passage). Therefore, the flow path diameters of the medium pressure fluid (refrigerant) flowing from the port pE to the port pF in the cooling position (first communication state) and the medium pressure fluid (refrigerant) flowing from the port pC to the port pB in the heating position (second communication state). Is constant, so that the pressure loss of the medium pressure fluid (refrigerant) can be further reduced.

Further, in the present embodiment, the main valve chamber 12 and the pressure chamber 17 are always communicated with each other, and the main valve chamber 12 and the pressure chamber 17 are introduced into the pressure chamber 17 from the port (discharge side high pressure port) pA via the first U turn passage 16A and the communication hole 16a. Since the high-pressure fluid (refrigerant) is also filled in the main valve chamber 12, the first slide valve body 15A and the second slide valve body 15B constituting the main valve body 15 are also used by the high-pressure refrigerant introduced into the main valve chamber 12. And are pressure-welded to the first main valve seat 13 and the second main valve seat 14 provided with the ports, respectively. Therefore, the pressing load on the first main valve seat 13 and the second main valve seat 14 increases, and valve leakage can be suppressed more effectively.

In the hexagonal switching valves 1 and 2 of the first and second embodiments, the ports (port pB, port pA, port pF) provided on the first main valve seat 13 are used in order to simplify the configuration. Each port (port pC, port pD, port pE) provided on the second main valve seat 14 is arranged to face each other, but the arrangement configuration (direction, positional relationship, etc.) of the six ports pA to pF is different. Of course, it is not limited to the illustrated example. For example, each port (port pB, port pA, port pF) provided in the first main valve seat 13 and each port (port pC, port pD, port pE) provided in the second main valve seat 14 are Positions separated by an angular interval of 90 degrees around the axis O (in the circumferential direction of the main valve housing 11), in other words, with each port (port pB, port pA, port pF) provided on the first main valve seat 13. Each port (port pC, port pD, port pE) provided on the second main valve seat 14 may be provided so as to be orthogonal to each other.

Further, in the six-way switching valves 1 and 2 of the first and second embodiments, the configuration in which the main valve body 15 is driven in the main valve chamber 12 by using the four-way pilot valve 90 has been described. For example, the four-way pilot valve 90 has been described. Instead of, a motor may be used to drive the main valve body 15 in the main valve chamber 12.

Further, it goes without saying that the six-way switching valves 1 and 2 of the first and second embodiments can be incorporated not only in the heat pump type heating / cooling system but also in other systems, devices and devices.

1 Six-way switching valve (first embodiment)
2 Six-way switching valve (second embodiment)
10 Hexagonal valve body 11 Main valve housing 11A Upper end side lid member 11B Lower end side lid member 12 Main valve chamber 13 First main valve seat (valve seat)
14 Second main valve seat (valve seat)
15 Main valve body 15A 1st slide valve body 15B 2nd slide valve body 15a Fitting convex part 15b of 1st slide valve body Cylindrical part 16A 1st U turn passage (continuous passage) of 2nd slide valve body
16B 2nd U-turn passage (continuous passage)
16a Communication hole 17 Pressure chamber 18 O-ring (sealing material)
19 Compression coil spring (urging member)
21 1st piston 22 2nd piston 25 Main connecting body 25a Main opening 25b Circular opening 25c Circular opening 31 1st operating chamber 32 2nd operating chamber 51 Upper gangway (communication passage)
51A 1st upper gangway part 51B 2nd upper gangway part 52 Lower gangway (continuous passage)
52A 1st lower through-passage 52B 2nd lower through-passage 53 Fitting insertion tube 54 Large diameter 55 O-ring (sealing material)
90 four-way pilot valve pA, pB, pC, pD, pE, pF port

Claims (18)

A tubular main valve housing that defines the main valve chamber, a total of six ports provided in the main valve housing, and a sliding main valve body that is movable in the main valve chamber in the axial direction. In the main valve body, a plurality of communication passages for selectively communicating between the ports are provided, and by moving the main valve body, the communication ports can be switched. It is a six-way switching valve,
Three ports are opened side by side in the axial direction in the main valve chamber, and three other ports are opened side by side in the axial direction at different positions around the axis from the three ports. ,
Said main valve body, before SL two of the three ports three first slide valve having a first 1U turn passage for selectively communicating the two ports of the port and of the further A second slide valve body having a second U-turn passage for selectively communicating ports is provided .
By moving the main valve body in the main valve chamber, two of the three ports are communicated with each other through the first U-turn passage, and the other three ports are communicated with each other. The two ports are communicated through the second U-turn passage, and the other one of the three ports and the other one of the other three ports are said. It is possible to selectively take multiple communication states that can be communicated through the main valve housing .
The first slide valve body and the second slide valve body are arranged in a back-to-back state so that the first U-turn passage and the second U-turn passage open in opposite directions.
The hexagonal feature is that the first slide valve body and the second slide valve body are integrally movable in the axial direction and slidable with each other in the direction perpendicular to the axis. Switching valve. The three ports, a first port, a second port, and a third port,
The further three ports, the fourth port, a fifth port and a sixth port,
The first U-turn passage selectively communicates two ports out of the first to third ports, and the second U-turn passage connects two ports out of the fourth to sixth ports. selectively communicated,
By moving the main valve body in the main valve chamber,
The first port and the second port are communicated with each other through the first U-turn passage, the fourth port and the fifth port are communicated with each other through the second U-turn passage, and the third port and the said port are communicated with each other. The first communication state in which the sixth port communicates through the main valve housing,
The second port and the third port are communicated with each other through the first U-turn passage, the fifth port and the sixth port are communicated with each other through the second U-turn passage, and the first port and the said port are communicated with each other. The six-way switching valve according to claim 1, wherein the fourth port can selectively take a second communication state in which communication is performed through the main valve housing. The six-way switching according to claim 2 , wherein the first port, the second port, and the third port are provided at positions where the fourth port, the fifth port, and the sixth port face each other. valve. A fitting convex portion provided on the other side of the first slide valve body and the second slide valve body slides on a tubular portion provided on one of the first slide valve body and the second slide valve body. The six-way switching valve according to any one of claims 1 to 3, wherein the hexagonal switching valve is freely fitted and integrated. An urging member for urging the first slide valve body and the second slide valve body in opposite directions is arranged between the first slide valve body and the second slide valve body. The six-way switching valve according to any one of claims 1 to 4, wherein the six-way switching valve is characterized in that. The six sides according to any one of claims 1 to 5 , wherein a pressure chamber into which a high-pressure fluid is introduced is provided between the first slide valve body and the second slide valve body. Switching valve. A relatively high-pressure fluid is introduced into one of the first U-turn passage and the second U-turn passage, and a relatively low-pressure fluid is introduced into the other of the first U-turn passage and the second U-turn passage. The six- way switching valve according to claim 6 , wherein a part of the high-pressure fluid introduced into one of the first U-turn passage and the second U-turn passage is introduced into the pressure chamber. When viewed in a direction perpendicular to the axis, the pressure receiving area on the pressure chamber side of one of the first slide valve body and the second slide valve body is provided with the first port, the second port, and the third port. The six-way switching valve according to claim 7 , wherein the pressure receiving area on the main valve seat side is larger than the pressure receiving area. In the first communication state, the third port and the sixth port communicate with each other through the main valve chamber, and in the second communication state, the first port and the fourth port connect the main valve chamber. The six- way switching valve according to any one of claims 6 to 8 , wherein the six- way switching valve is communicated with each other. The six-way switching valve according to claim 9 , wherein a sealing material for sealing between the main valve chamber and the pressure chamber is arranged. In the first communication state, the third port and the sixth port are communicated with each other through a lower gangway provided through the main valve body, and in the second communication state, the first port. The six- way switching valve according to any one of claims 6 to 8 , wherein the fourth port is communicated with each other through an upper through-passage provided so as to penetrate the main valve body. The six-way switching valve according to claim 11 , wherein the lower gangway and / or the upper gangway is composed of a straight passage having a constant passage diameter. The lower through-passage and / or the upper through-passage is a split passage that straddles the first slide valve body and the second slide valve body, and the first slide valve in the split passage. A large-diameter portion is formed on one of the end portion on the body side and the end portion on the second slide valve body side, and a fitting insertion tube portion to be inserted into the large-diameter portion is extended to the other, and the large-diameter portion The six-way switching valve according to claim 11 or 12 , wherein a sealing material is interposed between the fitting and inserting cylinder portion. The six-way switching valve according to any one of claims 11 to 13 , wherein the main valve chamber and the pressure chamber are always in communication with each other. A variable-capacity first and first valve housing, which is defined by a pair of first and second pistons on one end side and the other end side of the main valve chamber, and in which a high-pressure fluid is selectively introduced and discharged. Two operating chambers are provided, and the main valve body is movably arranged in the axial direction in conjunction with the first and second pistons.
The introduction and discharge of the high-pressure fluid into the first and second operating chambers are controlled to move the first and second pistons, so that the main valve body is moved in the main valve chamber. The six-way switching valve according to any one of claims 1 to 14 , wherein the six-way switching valve is characterized. The first piston and the second piston are integrally movably connected by a main connecting body, and the main valve body moves to the main connecting body as the first and second pistons reciprocate. The six-way switching valve according to claim 15 , wherein the six-way switching valve is connected to, fitted to, or engaged with. One end side lid member that also serves as a stopper that prevents the first piston from moving toward one end is fixed to one end of the main valve housing, and the other end of the main valve housing is directed toward the other end of the second piston. The six-way switching valve according to claim 15 or 16 , wherein a lid member on the other end side which also serves as a stopper for preventing the movement of the lid member is fixed. The control of the introduction and discharge of the high-pressure fluid into the first and second operating chambers is connected to the ports provided in the first and second operating chambers and the high-pressure portion and the low-pressure portion of the six-way switching valve. The six-way switching valve according to any one of claims 15 to 17 , wherein the six-way switching valve is provided by a single four-way pilot valve.

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