JP5881451B2 - Compound valve - Google Patents

Description

  The present invention relates to a composite valve suitable for use in a heat pump air conditioning system and the like, and more particularly, to a composite valve including a pilot-type large flow control valve and a small flow control valve.

  As a heat pump type air conditioning system, a system including a compressor, a condenser, an evaporator, an expansion valve, and a refrigerant flow path switching (reversal) four-way valve is known.

  On the other hand, as a heat pump type air conditioning system for vehicles (for example, for electric vehicles), as shown in FIG. 1 of Patent Document 1, for example, the refrigerant flow is not reversed and the cooling expansion valve and the heating expansion valve are individually provided. A system has been proposed.

  In such a system, since the refrigerant flow is not reversed, for example, when attention is paid to the heating expansion valve (reference numeral 24) shown in FIG. 1 of the same document, a cooling electromagnetic valve (reference numeral) is provided in parallel with the heating expansion valve. 26), the cooling solenoid valve is closed during heating and the refrigerant is throttled by the heating expansion valve. During cooling, the cooling electromagnetic valve is opened to bypass the inlet / outlet of the heating expansion valve, and the refrigerant is supplied to the expansion valve. The configuration is such that no aperture is performed.

  By the way, if these expansion valves and bypass solenoid valves are provided for cooling and heating, respectively, the system becomes large, the piping assembly cost increases, and the power consumption may increase. .

  Therefore, it is conceivable to achieve these functions with a single motor-operated valve. That is, for example, the refrigerant may be throttled by the electric valve during heating, and the electric valve may be fully opened during cooling.

Here, an example of a conventional electric valve will be described with reference to FIG.
The illustrated motor-operated valve 1 'includes a valve shaft 25 having a lower shaft portion 25a and an upper small-diameter shaft portion 25b, a valve body 40 having a valve chamber 41, and a lower end portion of the valve body 40 hermetically sealed. A can 60, a rotor 30 (rotation axis O) disposed with a predetermined gap α on the inner periphery of the can 60, and a stator 50 </ b> A externally fitted to the can 60 for rotationally driving the rotor 30. It is equipped with.

  The valve shaft 25 is integrally provided with a valve body portion 44 having a specific shape (two-stage inverted truncated cone shape each having a predetermined center angle) at the lower end portion of the lower shaft portion 25a. In 1 ', the flow volume of a refrigerant | coolant is controlled by changing the lift amount of this valve body part 44. As shown in FIG.

  The valve chamber 41 of the valve body 40 is provided with a valve seat 42 with a valve port (orifice) 43 to which the valve body portion 44 contacts and separates at a lower portion thereof, and a first inlet / outlet 5 ′ is opened at a side portion thereof. In addition, a second inlet / outlet 6 ′ is provided at the lower portion of the valve body 40 so as to continue to the valve port 43.

  The stator 50A includes a yoke 51, a bobbin 52, a stator coil 53, a resin mold cover 56, and the like. A stepping motor 50 includes the rotor 30 and the stator 50A. The stepping motor 50 and a feed screw (described later) An elevating drive mechanism for adjusting the lift amount (= opening degree) of the valve body 44 with respect to the valve port 43 is constituted by the female screw portion 38, the male screw portion 48) and the like.

  A support ring 36 is integrally coupled to the rotor 30, and an upper protrusion of a cylindrical valve shaft holder 32 is provided on the support ring 36 with a lower opening disposed on the outer periphery of the guide bush 46. The rotor 30, the support ring 36, and the valve shaft holder 32 are integrally connected by caulking and fixing.

  A lower end portion 46a of a cylindrical guide bush 46 is press-fitted and fixed in a fitting hole 49 provided in the upper portion of the valve body 40, and the valve shaft 25 (lower shaft portion 25a) is fixed to the guide bush 46. Is slidably inserted. In addition, a male thread portion 48 is formed on the outer periphery of the guide bush 46 in order to raise and lower the valve shaft 25 (valve body portion 44) using the rotation of the rotor 30, and on the inner periphery of the valve shaft holder 32. A female screw portion 38 is formed, and the male screw portion 48 and the female screw portion 38 constitute a feed screw.

  The upper small diameter portion 46b of the guide bush 46 is inserted into the upper portion of the valve shaft holder 32, and the upper small diameter shaft portion 25b of the valve shaft 25 is formed at the center of the ceiling portion of the valve shaft holder 32 (through hole formed therein). Has been inserted. A push nut 33 is press-fitted and fixed to the upper end portion of the upper small-diameter shaft portion 25b of the valve shaft 25.

  The valve shaft 25 is extrapolated to the upper small-diameter shaft portion 25b of the valve shaft 25, and between the ceiling portion of the valve shaft holder 32 and the upper end terrace surface of the lower shaft portion 25a of the valve shaft 25. The valve closing spring 34 composed of a compressed compression coil spring is always urged downward (in the valve closing direction). A coil for returning the push nut 33 to the outer periphery of the push nut 33 on the ceiling of the valve shaft holder 32 when the valve shaft 25 moves in the valve opening direction and the female screw portion 38 and the male screw portion 48 are disengaged. A return spring 35 made of a spring is provided.

  The guide bush 46 has a lower stopper body (fixed stopper) that constitutes one of rotation lowering stopper mechanisms for preventing further rotation lowering when the rotor 30 is rotated downward to a predetermined valve closing position. 47 is fixed, and an upper stopper body (moving stopper) 37 constituting the other of the stopper mechanism is fixed to the valve shaft holder 32.

  The valve closing spring 34 obtains a required sealing pressure in the valve closing state in which the valve body portion 44 is seated on the valve opening 43 (leakage prevention), and the valve body portion 44 comes into contact with the valve opening 43. Deployed to mitigate impact.

  In the motor-operated valve 1 ′ having such a configuration, the motor 50 (stator 50 </ b> A) is supplied with energizing excitation pulses in the first mode, so that the rotor is made to the guide bush 46 fixed to the valve body 40. 30 and the valve shaft holder 32 are rotated in one direction, and, for example, the valve shaft holder 32 is moved downward by the screw feed of the screw portions 48 and 38, and the valve body portion 44 is pressed against the valve seat 42, thereby opening the valve port 43. Is closed.

  At the time when the valve port 43 is closed, the upper stopper body 37 is not yet in contact with the lower stopper body 47, and the rotor 30 and the valve shaft holder 32 are further rotated and lowered while the valve body portion 44 closes the valve port 43. To do. In this case, the valve shaft 25 (the valve body portion 44) does not descend, but the valve shaft holder 32 descends, so that the valve closing spring 34 is compressed by a predetermined amount. As a result, the valve body portion 44 is strongly against the valve seat 43. The upper stopper body 37 comes into contact with the lower stopper body 47 by the lowering of the rotation of the valve shaft holder 32 and the lowering of the valve shaft holder 32 is forcibly stopped even if the pulse supply to the stator 50A is continued thereafter. (Fully closed).

  On the other hand, when the energization excitation pulse is supplied to the stator 50A in the second mode from this fully closed state, the rotor 30 and the valve shaft holder 32 are rotated in the opposite direction to the guide bush 46 fixed to the valve body 40. The valve shaft holder 32 is now moved upward by the screw feed of the screw portions 48 and 38. In this case, since the valve closing spring 34 is compressed by a predetermined amount as described above at the time when the rotation of the valve shaft holder 32 starts to rise (when pulse supply starts), until the valve closing spring 34 is extended by the predetermined amount. The valve body portion 44 does not leave the valve seat 42 and remains in the closed state (lift amount = 0). Then, after the valve closing spring 34 is extended by the predetermined amount, when the valve shaft holder 32 is further rotated up, the valve body portion 44 is separated from the valve seat 42, the valve port 43 is opened, and the refrigerant is supplied to the valve port. Pass through 43.

  In this case, the lift amount of the valve body 44, in other words, the effective opening area (= opening degree) of the valve port 43 can be arbitrarily finely adjusted according to the rotation amount of the rotor 30, and the rotation amount of the rotor 30 is determined by the supply pulse. Since it is controlled by the number, the refrigerant flow rate can be controlled with high accuracy.

  Therefore, when the motor-operated valve 1 ′ having such a configuration is employed as a motor-operated valve having both functions of the expansion valve and the bypass solenoid valve disclosed in Patent Document 1 described above, for example, during the cooling operation, the bypass solenoid valve In order to reduce the pressure loss as much as possible, the maximum opening (maximum lift) is adjusted. During heating operation, the opening (lift) is adjusted to function as an expansion valve. The refrigerant flow rate is finely controlled.

  However, in the motor-operated valve 1 ', improvement in flow rate control accuracy in the small flow rate region and increase in controllable flow rate are contradictory. That is, in order for the motor-operated valve 1 'to function as an expansion valve, it is necessary to ensure high flow control accuracy in a small flow region, which requires a high flow control resolution. It is necessary to make (effective opening area) as small as possible. On the other hand, since it is required to suppress pressure loss as much as possible in order to function as a bypass solenoid valve, the valve diameter cannot be reduced so much (less than the effective passage cross-sectional area of the piping system). In other words, if the valve diameter is reduced, the flow control accuracy in the small flow area can be increased. However, if the flow rate of refrigerant flowing through the system (controllable flow rate) is increased, the valve opening is maximized even if the valve opening is maximized. The part becomes resistance and pressure loss increases. Conversely, if the valve diameter is increased, the controllable flow rate can be increased (reduction of pressure loss), but the flow rate control accuracy in the small flow rate region is reduced. In addition, the valve body and the like must be enlarged according to the valve diameter, and a large torque is required for driving the valve body, which may lead to an increase in size, an increase in power consumption, and the like.

  Furthermore, if the resolution is increased to improve the flow rate control accuracy in the small flow rate region (for example, the valve lift amount per rotation of the rotor is reduced), it will take a long time from the small flow rate control state to the fully open state (flow channel bypass state). It takes time, and the opening gap (gap between the valve body and the valve port wall surface) at the time of small flow control becomes very narrow, and there is a possibility that foreign matter or the like is caught in the gap and becomes clogged.

  Therefore, it is compatible with improvement of flow control accuracy and increase of controllable flow rate (reduction of pressure loss) in the small flow rate region, reduction of required time from the small flow control state to the fully open state, and power consumption. In order to achieve a reduction or the like, the following Patent Document 2 describes a pilot-type first control valve for large flow rate (first valve body, first valve port) and a second control valve for small flow rate (second valve body, More specifically, the piston-type first valve body is used to open and close the large-diameter first valve opening, and the valve shaft (25) is separate from the first valve body. The needle-type second valve body provided in the lower part opens and closes the small-diameter second valve port, and the small flow rate second control valve can be used as a pilot valve for the large flow rate first control valve. A composite valve adapted to work is disclosed.

  In this composite valve, when the lift amount of the valve shaft (second valve body) is not more than a predetermined amount (when the second control valve opening is not more than a predetermined value), the first valve body closes the first valve port. The second valve body is in the small flow rate control state in which the small flow rate second control valve opening degree is controlled. At this time, an amount of refrigerant corresponding to the lift amount (second control valve opening) of the second valve body is between the inlet → the first valve chamber → the first valve body outer peripheral surface and the first valve chamber wall surface. The gap flows between the sliding surface formed at the back side, the back pressure chamber, the pilot passage, the second valve chamber, the second valve port, the outflow passage, and the outlet. When the lift amount of the valve shaft (second valve body) exceeds the predetermined amount, the amount of refrigerant flowing out from the back pressure chamber via the second valve port increases from the time of the small flow control, and the back pressure chamber When the pressure drops, the valve opening force eventually becomes larger than the valve closing force acting on the first valve body, the first valve body opens the first valve port, and the refrigerant flows into the inlet → first valve chamber → first valve. A large flow rate control state flows from the mouth to the outlet.

  In this way, the first valve body opens and closes the large-diameter first valve port, the second valve body opens and closes the small-diameter second valve port, and the second valve body is used for the large flow rate. By making it work as a pilot valve for one control valve, it is possible to improve the flow control accuracy in the small flow rate region and increase the controllable flow rate (reducing pressure loss) and reduce power consumption. Can be achieved.

  However, in the composite valve described in Patent Document 2, a single small flow rate second control valve serves as a small flow rate control valve and a pilot valve for the large flow rate first control valve. Therefore, the following problems may occur. That is, in order to switch from the small flow control to the large flow control, it is necessary to significantly increase the refrigerant flow rate passing through the small flow rate second control valve as compared with the small flow control, so the diameter of the second valve port (effective opening) It is necessary to set the area) to be considerably larger than the diameter required for the small flow control. For this reason, it becomes easy to cause an increase in operating load, increase the size of the drive unit (motor part) and the valve body, and the size and shape of the second control valve for small flow rate cannot be set optimal for small flow control. There was a problem that the flow rate control accuracy at the time of small flow rate control could not be increased so much.

  Further, since the opening and closing of the first control valve for large flow rate depends on the lift amount of the second valve body that changes slightly, the opening and closing of the first control valve for large flow rate may not be performed at a desired timing. There are not a few cases, and at the time of small flow control, since the refrigerant flows through the sliding surface gap of the first valve body → the back pressure chamber → the pilot passage, malfunction due to minute foreign matters mixed in the refrigerant (for example, There is also a problem that the first valve element is likely to be locked due to a minute foreign matter being caught in the sliding surface gap.

  Therefore, the inventors of the present application have previously proposed a composite valve as described in Patent Document 3 in order to solve the above problem. This composite valve utilizes a piston-type first valve body, a valve shaft provided with a needle-type second valve body, a lifting drive means for moving the valve shaft up and down, and a lifting operation of the valve shaft. And a valve main body provided with an inlet and an outlet, and the first valve body slides between the inlet and the outlet of the valve body. An insertion chamber that is freely inserted and partitioned by the first valve body into a back pressure chamber and a first valve chamber, a first valve port that opens to the first valve chamber, the pilot valve body, A second valve chamber in which a second valve body is disposed so as to be movable up and down; a second valve port communicating the inflow port or the first valve chamber and the second valve chamber; the back pressure chamber; A pilot passage communicating with the valve chamber, and when the lift amount of the second valve body is less than a predetermined amount, the pilot valve body While the pilot passage is closed, the first valve port is closed by the first valve body, and the second valve body is in a small flow rate control state in which the flow rate is controlled according to the lift amount of the second valve body. When the lift amount exceeds the predetermined amount, the pilot valve body is raised as the valve shaft rises to open the pilot passage, and accordingly, the first valve body opens the first valve port. It is configured to take a large flow rate control state.

  In the proposed composite valve, the second valve body for small flow rate is separated from the pilot valve body for opening and closing the first valve body for large flow rate. Until the fixed lift, a small flow rate control is performed by the second valve body. When the second valve body is lifted by a predetermined amount or more, the pilot valve body is pulled up and the pilot passage is opened, thereby the first valve body is opened. Therefore, the size and shape of the second control valve for small flow rate can be set to be optimal for the small flow control, and the opening and closing of the first control valve for large flow rate can be performed at a desired timing. It is possible to reliably perform the operation, and it is possible to obtain an excellent effect such that it is difficult to cause malfunction.

Japanese Patent No. 3799732 Japanese Patent No. 4416528 Japanese Patent Application No. 2011-68451

However, the previously proposed composite valve has the following problems to be improved.
First, a specific configuration example of the main part of such a composite valve is shown in FIG. As shown in the drawing, a pilot valve having a convex cross-sectional outer shape provided with a large-diameter cylindrical portion 127b having a flat annular lower end surface 127s and a small-diameter cylindrical portion 127a above the second valve body 124 in the valve shaft 125. An upper side portion 127c (a central insertion hole 127d thereof) of the body 127 is slidably inserted.

  The pilot valve body 127 is provided so as to slide on the inner wall of the second valve chamber 121 formed in the valve body 110, and the bush holding body 128 corresponding to the upper part of the valve body 40 shown in FIG. Is screwed and fixed to the valve body 40 so as to cover the second valve chamber 121. The bush holding body 128 holds the lower end portion 46 a of the guide bush 46.

  The pilot valve body 127 has its annular lower end surface 127s separated from the bottom surface 121b of the second valve chamber 121 (the upper end opening edge of the pilot passage 119) in order to open and close the first valve body not shown in the drawing. By making contact, the pilot passage 119 (the upper end opening thereof) communicating with the back pressure chamber 116 and the second valve chamber 121 formed behind the first valve body is opened and closed. The cylindrical portion 127b is slidably inserted and urged downward by a pilot valve closing spring 126 made of a compression coil spring. The pilot valve element 127 has a lift amount of the valve shaft 125 that is raised and lowered while being rotated by a stepping motor (not shown), as can be understood with reference to FIGS. 9 (A) and 10 (A). , The hook-shaped hook portion 125g provided on the valve shaft 125 comes into contact with the upper side portion 127c, and when the lift amount of the valve shaft 125 exceeds a predetermined amount Tc, as shown in FIG. The pilot valve body 127 is lifted against the urging force of the pilot valve closing spring 126 by the hook-shaped hook portion 125 g of the valve shaft 125 so as to open the pilot passage 119.

  As described above, in the previously proposed composite valve, the flat annular lower end surface 127s of the pilot valve element 127 is separated from and contacted with the flat bottom surface 121b of the second valve chamber 121 (the upper end opening edge of the pilot passage 119). The pilot passage 119 (the upper end opening thereof) is opened and closed. Therefore, in the closed state, the pressure in the back pressure chamber of the control valve for large flow rate is concentrated on a part of the annular lower end surface 127s of the pilot valve body 127 through the pilot passage 119, and the pilot valve When the body 127 is easily tilted and the pilot valve body 127 is tilted, a gap β is formed between the annular lower end surface 127s of the pilot valve body 127 and the bottom surface 121b of the second valve chamber 121 as shown in FIG. And the pressure in the back pressure chamber is released to the second valve chamber 121 side through the pilot passage 119, and the first valve body is undesirably opened.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to achieve both improvement in flow rate control accuracy in a small flow rate region and increase in controllable flow rate (reduction in pressure loss). A pilot-type first control valve for large flow rate, a second control valve for small flow rate, and a pilot valve for the first control valve for large flow rate. In addition to being able to be set optimally for control, the first control valve for large flow rate can be reliably opened and closed at a desired timing, and the sealing performance of the pilot passage by the pilot valve can be improved. Another object of the present invention is to provide a composite valve that can surely prevent the pilot passage from being undesirably opened, thereby improving reliability.

  In order to achieve the above object, one composite valve according to the present invention basically includes a piston-type first valve body, a valve shaft provided with a needle-type second valve body, and the valve shaft. Elevating drive means for elevating and lowering, a pilot valve body that is driven to open and close using the elevating operation of the valve shaft, and a valve body provided with an inflow port and an outflow port, and the inflow port in the valve body The first valve body is slidably inserted between the first outlet and the outlet, and the insertion chamber is partitioned into a back pressure chamber and a first valve chamber by the first valve body, and the first A first valve port that opens into the valve chamber, a second valve chamber in which the pilot valve body and the second valve body are arranged so as to be movable up and down, and the inlet or the first valve chamber and the second valve chamber. A pilot passage having an upper end opened to a bottom surface of the second valve chamber so as to communicate the second valve port communicating with the back pressure chamber and the second valve chamber When the lift amount of the second valve body is a predetermined amount or less, the pilot passage is closed by the pilot valve body, and the first valve port is closed by the first valve body, When the small flow rate control state in which the flow rate is controlled according to the lift amount of the second valve body is taken and the lift amount of the second valve body exceeds the predetermined amount, the pilot valve body is raised along with the rise of the valve shaft. Is lifted to open the pilot passage, and accordingly, the first valve body is configured to take a large flow rate control state in which the first valve port is opened, and the pilot valve body opens the second valve chamber. When slidably housed in the inner wall of the covering member, urged downward by a spring member to close the pilot passage, and the lift amount of the second valve body is further increased from the predetermined amount, Installed on the valve stem It is characterized in that by being hooked portion is thus pulled against the biasing force of the spring member.

  Another composite valve according to the present invention basically includes a piston-type first valve body, a valve shaft provided with a needle-type second valve body, and a lift drive means for raising and lowering the valve shaft. And a pilot valve body that is driven to open and close using the raising / lowering operation of the valve shaft, and a valve body provided with an inlet and an outlet, and between the inlet and the outlet in the valve body In addition, the first valve body is slidably inserted, a fitting insertion chamber partitioned by the first valve body into a back pressure chamber and a first valve chamber, and a first opening opened to the first valve chamber. A first valve port, a second valve chamber in which the pilot valve body and the second valve body are arranged so as to be movable up and down, and a communication passage communicating the inlet or the first valve chamber and the second valve chamber; A second valve port that communicates the second valve chamber and the outlet, and a pilot passage that communicates the back pressure chamber and the outlet. When the lift amount of the second valve body is less than or equal to a predetermined amount, the pilot passage is closed by the pilot valve body, the first valve port is closed by the first valve body, and the lift of the second valve body is When a small flow rate control state in which the flow rate is controlled according to the amount is taken and the lift amount of the second valve body exceeds the predetermined amount, the pilot valve body is raised with the rise of the valve shaft, and the A pilot passage is opened, and the first valve body is configured to take a large flow rate control state in which the first valve port is opened, and the pilot valve body slides on the inner wall of a member covering the second valve chamber. When the piston member is movably accommodated, biased downward by a spring member to close the pilot passage, and when the lift amount of the second valve body is further increased from the predetermined amount, the valve shaft is provided. Hook It is characterized by being so lifted against the urging force of more the spring member.

  In a preferred aspect, the pilot valve body includes a valve body member that can close a pilot passage that opens to a bottom surface of the second valve chamber, and a valve body pressing member that presses the valve body member. The pressing member is slidably accommodated on the inner wall of the member that covers the second valve chamber.

In this case, the valve body member, said sealing surface approaching and moving away from the opening edge portion of the pilot passage spherical, ellipsoidal surface, or composed of a curved surface in line contact against the opening edge portion of the conical surface.

  In this case, the valve body member includes a ball that is brought into contact with and separated from the opening edge of the pilot passage and a holding body that holds the ball.

  In another preferred aspect, the member that covers the second valve chamber is a bush holding body that holds a guide bush constituting a feed screw mechanism of the valve shaft.

  In another preferred embodiment, the valve shaft and the second valve body and the valve seat to which the second valve body contacts and separates are made of the same metal material.

  In this case, preferably, the valve shaft, the second valve body, and the valve seat to which the second valve body contacts and separates are made of stainless steel, and the valve main body is made of aluminum.

In another preferred embodiment, the first valve body is disposed sideways and the second valve body is disposed vertically.
In another preferred embodiment, the first valve body and the second valve body are both arranged vertically and are separated from each other by a predetermined distance.

  In the composite valve according to the present invention, in addition to the first control valve for large flow rate (first valve body, first valve port) and the second control valve for small flow rate (second valve body, second valve port), Since the pilot valve body is provided separately from the second valve body, and this pilot valve body is driven to open and close by using the raising and lowering operation of the valve shaft, the second control valve for small flow rate (second valve) Body, second valve port) can be set to the optimal size for small flow control, and the first control valve for large flow rate can be reliably opened and closed at a desired timing. At the time of small flow rate control, the refrigerant is made to flow without passing through a narrow part such as a sliding surface gap like the conventional one, so that it is difficult to cause malfunction, and as a result, the operation load increases and the drive unit (motor Part) and increase in flow control accuracy in the small flow area and control without increasing the size of the valve body It is possible to achieve both the increase in the flow rate (reduction of pressure loss).

  In addition, in the composite valve of the present invention, the pilot valve body or the valve body pressing member constituting the pilot valve body is slidably accommodated on the inner wall of the member covering the second valve chamber. Even if high pressure is introduced from the pilot passage, the pilot valve body or the valve body pressing member is less likely to be inclined, and the sealing performance of the pilot passage may be reduced. In addition, it is possible to reliably prevent the pilot passage from being undesirably opened, thereby improving the reliability.

The notch longitudinal cross-sectional view which shows the 1st operation state (fully closed state) in one Example of the compound valve which concerns on this invention. (A) is XX arrow sectional drawing of FIG. 1, (B) is YY arrow sectional drawing of FIG. FIG. 3 is an enlarged detail view around a second control valve for small flow rate and a pilot valve in FIG. 1. (A) is an enlarged view of the A part in FIG. 3, (B) is BB arrow sectional drawing of (A). The notch longitudinal cross-sectional view which shows the 2nd operation state (small flow control state) in one Example of the compound valve which concerns on this invention. The expanded sectional view around the pilot valve which shows the 3rd operation state (state just before switching from small flow control to large flow control) in one example of the compound valve concerning the present invention. The notch longitudinal cross-sectional view which shows the 4th operation state (large flow control state) in one Example of the compound valve which concerns on this invention. The expanded sectional view around the pilot valve which shows the 4th operation state (large flow control state) in one example of the compound valve concerning the present invention. (A) is sectional drawing which shows the principal part (The 2nd control valve for small flow rate and pilot valve periphery) of the composite valve of a proposal previously, (B) is the Z section enlarged view of (A). FIG. 10A is a diagram for explaining the operation and problem of the composite valve shown in FIG. 9, and (A) is a diagram showing a state in which the valve shaft 125 is raised and the hook-shaped hook portion 125 g is in contact with the pilot valve body 127. (B) is a figure which shows a mode that the valve stem 125 raised further, and the pilot valve body 127 raised. The longitudinal cross-sectional view which shows an example of the conventional motor operated valve.

Embodiments of the present invention will be described below with reference to the drawings.
1, 5 and 7 are cutaway longitudinal sectional views showing an embodiment of the composite valve according to the present invention, and each drawing shows different operating states. 2 (A) is a cross-sectional view taken along the line XX of FIG. 1 (first control valve for large flow rate: closed state), and FIG. 2 (B) is FIG. 7 (first control valve for large flow rate: It is a YY arrow sectional drawing of an open state. Since the internal configuration of the stepping motor 50 portion of the composite valve 1 of the illustrated embodiment is substantially the same as that of the conventional motor-operated valve 1 ′ shown in FIG. 11, this portion represents only the outer shape. Moreover, in each figure, the code | symbol same as FIGS. 9-11 has shown the same or equivalent part.

  The composite valve 1 of the first embodiment shown in the figure is a valve of the motor-operated valve 1 ′ of the conventional example in order to achieve both improvement in flow rate control accuracy at a small flow rate and increase in controllable flow rate (reduction in pressure loss). A rectangular parallelepiped valve body 10 larger than the main body 40, a pilot-type first control valve 4A for large flow rate (first valve body 15, first valve port 13), and a second control valve 4B for small flow rate (second valve body). 24, a second valve port 23), and a pilot valve 4C (pilot valve body 60, pilot passage 19) for opening and closing the first control valve 4A for large flow rate. The small flow rate second control valves 4B are arranged in the vertical direction.

  Specifically, the valve main body 10 has an inflow port 5 (shown by a virtual line in FIG. 1 and a cross-section (solid line) in FIG. 2) in the vicinity of the center in the left-right direction on the front (front) side and slightly in the vertical direction. Is provided in the lower part on the right side when viewed in the left-right direction, and a stepped recessed hole 7 having a female thread part on the upper surface opening is provided slightly on the upper side. A stepped lateral hole 8 having a threaded portion 8a and an annular stepped portion 8b is provided below the concave hole 7 so that the left side is open in a horizontal direction. A first valve port with a first valve seat 12 is disposed laterally at the bottom on the right end side of the horizontal hole 8 so that the horizontal hole 8 (first valve chamber 11 described later) communicates with an outlet passage 29 and an outlet 6 described later. 13 is provided.

  A bush holding body 28 corresponding to the upper part of the valve body 40 in the conventional motor-operated valve 1 ′ (see FIG. 11) is screwed and fixed to the upper half of the stepped recess hole 7. A second valve chamber 21 is defined below the cylindrical portion 28b with the ceiling surface 28a provided in the lower half of the body 28, and is driven up and down by the motor 50 at the center of the bottom of the recessed hole 7. A second valve port 23 having a small diameter that is opened and closed by a second valve body 24 provided at a lower portion of the valve shaft 25 is provided. A valve seat member 22 formed with a valve seat 22a with which the second valve body 24 contacts and separates is fixed to the upper end portion of the second valve port 23 by, for example, caulking. Moreover, the 2nd valve port 23 is extended in the vertical direction, and the lower part is connected to the 1st valve chamber 11 mentioned later.

  The bush holding body 28 is provided with the fitting hole 49 described above with reference to FIG. 11, and the lower end portion 46 a of the cylindrical guide bush 46 is press-fitted and fixed to the fitting hole 49.

  A male screw portion is formed on the outer periphery of the guide bush 46, and a female screw portion is formed on the inner periphery of the valve shaft holder (reference numeral 32 in FIG. 11). The valve shaft 25 is moved up and down by the male screw portion and the female screw portion. A feed screw mechanism is configured.

  In addition, an upper end of an outflow passage 29 that communicates the second valve chamber 21 and the outlet 6 is opened at the bottom right corner of the recessed hole 7, and a left side of the second valve port 23 at the bottom of the recessed hole 7 is opened. A valve body guide hole 19D into which a valve body member 61 in a pilot valve body 60 having a divided configuration, which will be described later, is slidably inserted is provided.

  A large-diameter first valve seat 12 with a first valve port 13 is provided on the right side of the first valve chamber 11 in the stepped lateral hole 8, and further, the outflow passage 29 and the outlet port 6 connected thereto are formed. Yes.

  A lid-like mounting body 9 having a cylindrical guide portion 9c with a ceiling surface 9a is screwed and fixed to the female screw portion 8a of the stepped lateral hole 8. The cylindrical guide portion 9c is provided with an annular terrace portion 9b that comes into contact with the annular terrace portion 8b of the stepped lateral hole 8, and around the terrace portion 9b of the cylindrical guide portion 9c and the stepped lateral hole 8b. The area around the terrace 8b is sealed with an O-ring 81. Further, the right side from the ceiling surface 9a of the lid-like mounting body 9 on the left side of the bottom portion (first valve seat 12 side) in the lateral hole 8 is an insertion chamber 14, and the cylindrical guide portion 9c in the insertion chamber 14 is connected to the cylindrical guide portion 9c. The piston-type first valve body 15 (the large diameter portion 15a) is slidably inserted, and the back of the first valve body 15 (the large diameter portion 15a) in the insertion chamber 14 is on the left side. The pressure chamber 16 is defined, and the first valve chamber 11 is defined on the right side of the first valve body 15 (the large diameter portion 15a).

  The first valve body 15 has a bobbin shape having a large-diameter portion 15a, a small-diameter portion 15b, and a medium-diameter portion 15c in order from the left side, and is separated from and in contact with the first valve seat 12 at the right end thereof. An annular sealing material 15d made of rubber or Teflon (registered trademark) is fixed by an appropriate method such as caulking, and the left end surface of the sealing material 15d contacts the ceiling surface 9a of the insertion chamber 14. A stopper 15g with a short cylindrical side hole 15i that defines the leftward movement limit of the first valve body 15 is projected, and a sealing material (piston ring) 15f is mounted on the outer periphery of the large diameter portion 15a. .

  Further, in order to urge the first valve body 15 to the right (valve closing direction), the bottom surface of the spring receiving hole 15 h provided in the center on the left end side of the first valve body 15 and the ceiling surface 9 a of the insertion chamber 14. In the meantime, a first valve closing spring 18 formed of a compression coil spring is mounted.

  Further, the large diameter portion 15 a of the first valve body 15 is provided with a pressure equalizing hole 17 including a through passage for communicating the first valve chamber 11 and the back pressure chamber 16.

  In addition to the above configuration, a pilot passage 19 having an upper end opened to the bottom surface 21b of the second valve chamber 21 is provided in order to communicate the back pressure chamber 16 and the second valve chamber 21. The pilot passage 19 includes four through-holes 19a provided radially, for example, at 90 ° intervals so as to penetrate through the cylindrical guide portion 9c of the lid-like mounting body 9 near the ceiling surface 9a in the thickness direction. An annular space 19b airtightly defined on the inner peripheral side of the stepped lateral hole 8 on the outer peripheral side of the guide portion 9c, one end opening in the space 19b, and the other end of the valve element guide hole 19D described above The ball 65 of the pilot valve body 60 described later contacts and separates from the upper end opening edge 19e of the vertical hole 19c. The passage 19 is opened and closed.

  On the other hand, the pilot valve body 60 of the pilot valve 4C includes a valve body member 61 slidably fitted in the valve body guide hole 19D, and the valve body member 61 at the opening edge 19e of the pilot passage 19e. A valve body pressing member that is extrapolated to the lower shaft portion 25a of the valve shaft 25 so that the valve shaft 25 is lifted by the valve shaft 25 when the lift amount exceeds a predetermined amount Tc. 62.

  When the valve shaft 25 is lifted over a predetermined amount Tc, the valve shaft 25 is formed with a hook-shaped locking portion 25g so that the valve body pressing member 62 is pulled up by the valve shaft 25. A thrust bearing (ball bearing) 70 is extrapolated and held on the hook-shaped locking portion 25g in a state where the inner peripheral portion is sandwiched between the annular locking plate 71 and the E-type retaining ring 72.

  As can be understood with reference to FIG. 3, the valve body pressing member 62 includes a ceiling portion 62 a in which an insertion hole 62 b to be externally inserted into the lower shaft portion 25 a of the valve shaft 25 is provided, and the bush The cylindrical portion 62c is slidably fitted into a cylindrical portion 28b with a ceiling surface 28a provided in the lower half of the holding body 28. An annular spring receiving hole 62d having an upper surface opening is provided in the cylindrical portion 62c. A compression coil spring 26 that urges the valve body pressing member 62 downward (in the direction to close the pilot passage 19) is mounted between the bottom surface of the spring receiving hole 62d and the ceiling surface 28a. The hole diameter of the insertion hole 62b is set larger than the outer diameter of the E-type retaining ring 72, and when the valve shaft 25 is lifted beyond a predetermined amount Tc, the outer peripheral portion of the upper surface of the thrust bearing 70 Is in contact with the lower surface of the ceiling 62a.

  The bush holding body 28 covers the second valve chamber 21 so as to fit inside the upper portion of the second valve chamber 21. And the said valve body pressing member 62 is provided so that the inner wall of this bush holding body 28 may slide.

As shown in FIG. 4 in addition to FIG. 3, the valve body member 61 includes a ball 65 that is brought into contact with and separated from the opening edge 19 e of the pilot passage 19, and a holding body 64 that holds the ball 65. It consists of More specifically, the holding body 64 has an upper small diameter portion 64a, an intermediate large diameter portion 64b, and a lower small diameter whose top surface portion 64s made of, for example, a spherical surface contacts the lower surface of the cylindrical portion 62c of the valve body pressing member 62 in order from the top. The intermediate large-diameter portion 64b includes parallel chamfered portions 67 and 67 as shown in FIG. 4B, and includes a parallel chamfered portion 67 and 67 as shown in FIG. Between the chamfered portions 67 and 67 and the inner peripheral surface of the valve element guide hole 19D is a flow passage 19f (a part of the bypass passage 19). Further, a sideways L-shaped hole 64f is formed in the lower small diameter portion 64c to communicate the caulking portion 64d with the outside. In FIG. 4, the main body member 61 is inclined with respect to the central axis of the valve element guide hole 19D. Even in such a state, the opening edge portion 19e can be satisfactorily sealed by the action of the ball 65. it can.
The caulking portion 64d may hold the ball 65 in a rotatable state.

  A compression coil spring 66 that biases the valve body member 61 upward (in the direction of opening the pilot passage 19) is mounted between the lower surface of the intermediate large diameter portion 64b and the bottom surface of the valve body guide hole 19D. . By this coil spring 66, the top surface portion 64 s of the valve body member 61 is always brought into contact with the lower surface of the cylindrical portion 62 c of the valve body pressing member 62.

Here, in the composite valve 1 of this embodiment, the pressure in the first valve chamber 11 is P1, the pressure in the back pressure chamber 16 is P2, the pressure in the first valve port 13 is P3, and the horizontal cross-sectional area of the back pressure chamber 16 ( The pressure receiving area of the first valve body 15 is Ap, the horizontal sectional area of the first valve port 13 is Av, the urging force of the main valve opening spring 18 is Pf, and the force that pushes up the first valve body 15 is the valve opening force. If the force that pushes down the valve body 15 is the closing force, the opening condition of the first control valve for large flow rate
Valve closing force = P2 x Ap + Pf <valve opening force = P1 x (Ap-Av) + P3 x Av
It becomes.

  In this embodiment, the valve shaft 25 (valve body 24) is made of stainless steel, and the valve seat 22a (valve seat member 22) is used to improve the sealing performance and durability by reducing wear of the contact portion and sliding portion. Is made of the same stainless steel as the valve shaft 25 (valve element 24). The lid-like mounting body 9 is also made of stainless steel. On the other hand, the valve body 10 can be made of aluminum.

  In the composite valve 1 having such a configuration, as shown in FIG. 1, when all of the first valve body 15, the second valve body 24, and the pilot valve body 27 are in the closed state, The high-pressure refrigerant introduced into the one valve chamber 11 is introduced into the back pressure chamber 16 through the pressure equalizing hole 17, and the pressure in the back pressure chamber 16 becomes high, so that the first valve body 15 is moved to the first valve seat. 12 is strongly pressed.

  From this state, when the motor 50 is supplied with pulses to raise the valve shaft 25 and the second valve body 24 while rotating, the second valve body 24 moves away from the second valve seat 22a as shown in FIG. The second valve port 23 is opened. In this case, when the lift amount of the valve shaft 25 and the second valve body 24 is less than a predetermined amount Tc (see FIGS. 1 and 3), the outer peripheral portion of the upper surface of the thrust bearing 70 has not reached the lower surface of the ceiling portion 62a. Accordingly, the valve body pressing member 62 and the valve body member 61 constituting the pilot valve body 60 remain in the state shown in FIG. 1. At this time, the pilot passage 19 is formed by the balls 65 of the pilot valve body 60. A small flow rate control state in which the first valve port 13 is closed by the first valve body 15 and the refrigerant flow rate (second control valve opening) is controlled according to the lift amount of the second valve body 24 while being closed. It becomes. In this small flow rate control state, an amount of refrigerant corresponding to the lift amount of the second valve body 24 flows into the inlet 5 → the first valve chamber 11 → the second valve port 23 → the second valve chamber 21 → the outlet passage 29 → flow. Flows to exit 6.

  When the lift amount of the valve shaft 25 and the second valve body 24 reaches the predetermined amount Tc, as shown in FIG. 6, the outer peripheral portion of the upper surface of the thrust bearing 70 comes into contact with the lower surface of the ceiling portion 62a. Subsequently, when the valve shaft 25 and the second valve body 24 are further raised while rotating and the lift amount exceeds the predetermined amount Tc, as shown in FIGS. 62 is hooked on the outer peripheral portion of the upper surface of the thrust bearing 70 and pulled up against the urging force of the valve closing spring 26, and accordingly, the valve body member 61 has its top surface portion 64 s due to the urging force of the coil spring 66. The ball 65 is moved away from the upper end opening edge 19e of the vertical hole 19c, and the pilot passage 19 is opened. The refrigerant from the chamber 16 is introduced into the second valve chamber 21 through the pilot passage 19 and is guided from here to the outlet 6 through the outlet passage 29. As a result, the pressure in the back pressure chamber 16 decreases, and eventually the valve opening force becomes larger than the valve closing force that acts on the first valve body 15, the first valve body 15 opens the first valve port 13, and the refrigerant flows. A large flow rate control state flows from the inlet 5 to the first valve chamber 11 to the first valve port 13 to the outlet 6.

  As understood from the above description, in the composite valve 1 of the present embodiment, the first control valve 4A for the large flow rate (the first valve body 15 and the first valve port 13) and the second control valve 4B for the small flow rate ( In addition to the second valve body 24 and the second valve port 23), the pilot valve body 60 is provided separately from the second valve body 24, and the pilot valve body 60 is moved up and down using the valve shaft 25. Since it is configured to open and close, the size and shape of the second control valve 4B for small flow rate (second valve body 24, second valve port 23) can be set to be optimal for small flow control. The first flow control valve 4A for large flow rate can be reliably opened and closed at a desired timing. Further, when the small flow rate control is performed, the refrigerant is allowed to flow without passing through a narrow portion such as a sliding surface gap like the conventional one. As a result, it is difficult to cause malfunctions. Part (a motor portion) and the valve without increasing the size of the body, it is possible to achieve both an increase of the control flow rate and increase of the flow rate control accuracy in the small flow rate area (reduction of pressure loss).

  Further, the pilot valve body 60 is divided into a valve body member 61 having a sealing surface of a ball 65 and a valve body pressing member 62 separate from the valve body member 61, and these are biased by spring members 26 and 66. Therefore, even if the valve body pressing member 62 is inclined, the inclination is hardly transmitted to the valve body member 61, and the sealing performance of the pilot passage by the valve body member 61 is improved. In addition, since the portion (seal portion) that contacts and separates from the opening edge portion 19e of the pilot passage 19 is formed of a spherical surface (ball 65), even if the valve body member 61 is inclined, Thus, an undesired gap β (see FIG. 9B) does not occur, and since the seal portion is not a surface contact but a line contact unlike the conventional one, the contact pressure increases, Sealed by Is remarkably improved, without much increasing the spring load of the valve closing spring 26, also without much increasing the machining accuracy of the seal portion, it is possible to reliably suppress the leakage.

  In addition, since the thrust bearing 70 as a hook-like hooking portion is provided on the valve shaft 25, when the valve shaft 25 and the second valve body 24 are further lifted while rotating beyond the predetermined amount Tc, The valve body pressing member 62 is hooked by the outer peripheral portion of the upper surface of the thrust bearing 70 and pulled up against the urging force of the valve closing spring 26. In this case, the lower surface side of the thrust bearing 70 is integrated with the valve shaft 25. However, since the upper surface side of the thrust bearing 70 and the valve body pressing member 62 that contacts the thrust bearing 70 do not rotate, there is no rotational sliding friction resistance between the valve shaft 25 and the pilot valve body 60 as in the prior art. Almost no occurrence occurs, and therefore the rotation of the valve shaft 25 is not hindered, and malfunction can be reliably prevented.

  Of course, the composite valve according to the present invention is not limited to the configuration of the composite valve 1 of the first embodiment described above, and various modifications can be made.

  For example, in the composite valve 1 of the above embodiment, the second valve port 23 communicates the first valve chamber 11 and the second valve 21 chamber, but the following configuration may be slightly different from that. Good. That is, the second valve port is communicated with the outlet, and a separate communication path is provided for communicating the first valve chamber and the second valve chamber, and the high pressure of the first valve chamber is provided via the communication path to the second valve. By introducing into the chamber, high pressure is not applied to the closed second valve body. As a result, the second valve element opens undesirably without increasing the spring load of the valve closing spring (reference numeral 34 in FIG. 11) that urges the second valve element (valve shaft) in the valve closing direction. Can be surely prevented, and restrictions on the diameter of the second valve port can be relaxed. As a result, cost reduction, size reduction, power consumption reduction, etc. can be achieved (Japanese Patent Application No. 2011 by the applicant of the present invention). -273975).

  Further, in the above embodiment, the valve member 61 has the ball 65 at the portion that contacts and separates from the opening edge 19e of the pilot passage 19, but it is not always necessary to use the ball, and the sealing surface is spherical, elliptical. What is necessary is just to be comprised by the curved surface which carries out a line contact substantially with respect to opening edge part 19e, such as a spherical surface and a conical surface.

  In the above embodiment, the first valve body is disposed sideways and the second valve body is disposed vertically, but the first valve body and the second valve body are both disposed vertically, etc. Of course, it may be a form.

  Moreover, in the said Example, since the valve shaft 25 which pulls up the valve body pressing member 62 raises rotating, it demonstrates that the thrust bearing 70 is interposed between the hook-shaped latching | locking part 25g and the valve body pressing member 62. However, when the valve shaft rises without rotating, the bearing 70 can be omitted.

  Further, in the above embodiment, the valve body pressing member 62 is described as being slidably provided on the inner wall of the bush holding body 28 that fits inside the second valve chamber 21 and covers it, but the present invention is only this. The valve body pressing member 62 may be slidably provided on the inner wall of the member that does not hold the guide bush 46 as long as it is a member that fits inside the second valve chamber 21 and covers it. It is natural.

  Furthermore, in the above embodiment, an electric type (stepping motor 50) is used as the raising / lowering driving means for raising and lowering the valve shaft. The present invention is equally applicable.

  Moreover, it cannot be overemphasized that the compound valve of this invention is applicable not only to a heat pump type | formula air conditioning system but to another system.

  Furthermore, in the above embodiment, since the valve body pressing member 62 is provided so as to slide on the inner wall of the bush holding body 28, the valve body pressing member 62 is provided in the second valve chamber provided in the valve body 10. The sliding area of the valve body pressing member 62 can be increased as compared with the case where the inner wall 21 is configured to slide. As a result, when the valve body pressing member 62 is pulled up by the lift of the valve shaft 25, the inclination of the valve body pressing member 62 is reduced.

  Therefore, instead of configuring the pilot valve body 60 with the valve body member 61 and the valve body pressing member 62, the valve body member 61 is omitted, and the pilot passage 19 (vertical hole 19c) is opened and closed with only the valve body pressing member 62. It is also possible to do. In this case, the valve body pressing member 62 functions as a pilot valve body.

DESCRIPTION OF SYMBOLS 1 Compound valve 4A 1st control valve 4B for large flow rates 2nd control valve 4C for small flow rates Pilot valve 5 Inlet 6 Outlet 10 Valve body 11 First valve chamber 12 First valve seat 13 First valve port 14 Insertion chamber 15 First valve body 16 Back pressure chamber 17 Pressure equalizing hole 18 First valve closing spring 19 Pilot passage 19D Valve body guide hole 21 Second valve chamber 23 Second valve port 24 Second valve body 25 Valve shaft 26 Pilot valve closing spring 30 Rotor 50 Stepping motor 50A Stator 60 Pilot valve body 61 Valve body member 62 Valve body pressing member 64 Holding body 65 Ball 66 Coil spring 70 Thrust bearing

Claims (10)

A valve shaft provided with a piston-type first valve body, a needle-type second valve body, an elevating drive means for elevating the valve shaft, and a pilot driven to open and close using the elevating operation of the valve shaft A valve body and a valve body provided with an inlet and an outlet,
The first valve body is slidably inserted between the inlet and the outlet in the valve body, and the back valve chamber and the first valve chamber are partitioned by the first valve body. An insertion chamber, a first valve opening that opens to the first valve chamber, a second valve chamber in which the pilot valve body and the second valve body are arranged to be movable up and down, and the inflow port to the first valve chamber, A second valve port communicating with the second valve chamber; and a pilot passage having an upper end opened to a bottom surface of the second valve chamber to communicate the back pressure chamber and the second valve chamber. And
When the lift amount of the second valve body is equal to or less than a predetermined amount, the pilot passage is closed by the pilot valve body, the first valve port is closed by the first valve body, and the second valve body When a small flow rate control state in which the flow rate is controlled in accordance with the lift amount is taken and the lift amount of the second valve body exceeds the predetermined amount, the pilot valve body is raised as the valve shaft rises. A composite valve configured to take a large flow rate control state in which the pilot passage is opened and the first valve body opens the first valve port with the pilot passage;
The pilot valve body is slidably accommodated in an inner wall of a member that covers the second valve chamber, and is biased downward by a spring member to close the pilot passage, and the lift of the second valve body A composite valve characterized in that when the amount is further increased from the predetermined amount, it is pulled up against the urging force of the spring member by a hooking portion provided on the valve shaft. A valve shaft provided with a piston-type first valve body, a needle-type second valve body, an elevating drive means for elevating the valve shaft, and a pilot driven to open and close using the elevating operation of the valve shaft A valve body and a valve body provided with an inlet and an outlet,
The first valve body is slidably inserted between the inlet and the outlet in the valve body, and the back valve chamber and the first valve chamber are partitioned by the first valve body. An insertion chamber, a first valve opening that opens to the first valve chamber, a second valve chamber in which the pilot valve body and the second valve body are arranged to be movable up and down, and the inflow port to the first valve chamber, A communication passage communicating the second valve chamber, a second valve port communicating the second valve chamber and the outflow port, and a pilot passage communicating the back pressure chamber and the outflow port. And
When the lift amount of the second valve body is equal to or less than a predetermined amount, the pilot passage is closed by the pilot valve body, the first valve port is closed by the first valve body, and the second valve body When a small flow rate control state in which the flow rate is controlled in accordance with the lift amount is taken and the lift amount of the second valve body exceeds the predetermined amount, the pilot valve body is raised as the valve shaft rises. A composite valve configured to take a large flow rate control state in which the pilot passage is opened and the first valve body opens the first valve port with the pilot passage;
The pilot valve body is slidably accommodated in an inner wall of a member that covers the second valve chamber, and is biased downward by a spring member to close the pilot passage, and the lift of the second valve body A composite valve characterized in that when the amount is further increased from the predetermined amount, it is pulled up against the urging force of the spring member by a hooking portion provided on the valve shaft. The pilot valve body is composed of a valve body member that can close a pilot passage that opens to the bottom surface of the second valve chamber, and a valve body pressing member that presses the valve body member,
The composite valve according to claim 1 or 2, wherein the valve body pressing member is slidably accommodated in an inner wall of a member covering the second valve chamber. Wherein said valve body member, characterized in that the sealing surface approaching and moving away from the opening edge portion of the pilot passage is spherical, ellipsoidal surface, or that for the opening edge portion of the conical surface formed by a curved surface in line contact Item 4. The composite valve according to Item 3.   5. The composite valve according to claim 4, wherein the valve body member includes a ball that is brought into contact with and separated from an opening edge of the pilot passage and a holding body that holds the ball. The second valve chamber cover member is combined valve according to claim 1, any one of 5, which is a bushing holder that holds a guide bush which constitutes the feed screw mechanism of the valve shaft . And the valve shaft and the second valve body, the composite according to any one of claims 1 from the valve seat that the second valve body and moving away, characterized in that it is made of the same metal material 6 valve.   8. The composite valve according to claim 7, wherein the valve shaft, the second valve body, and the valve seat to which the second valve body contacts and separates are made of stainless steel, and the valve main body is made of aluminum. . The composite valve according to any one of claims 1 to 8, wherein the first valve body is disposed sideways, and the second valve body is disposed vertically. Wherein with the first valve body and the second valve body are both Zaisa distribution vertically, according to any one of mutually the preceding claims, characterized in that are brought apart by a predetermined distance 8 Composite valve.

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