JP6367164B2 - Pressure operated valve and refrigeration cycle - Google Patents

Description

  The present invention relates to a pressure operating valve that operates a valve member in accordance with the pressure of a fluid on a primary side and a refrigeration cycle.

  Conventionally, as a pressure-actuated valve, for example, there is one disclosed in JP-A-6-229481 (Patent Document 1). This pressure-actuated valve is designed to cause the ball valve to separate from the valve seat and flow out of the outflow pipe when a fluid whose pressure exceeds the set pressure set by the adjusting screw and the adjusting spring flows into the inflow pipe. is there. Further, a guide blade material is slidably disposed in a cylinder above the valve chamber to prevent hunting.

JP-A-6-229481

  In a conventional pressure-actuated valve, fluid flows between a valve port inside the valve seat and a ball valve (valve member), but the valve member slightly vibrates due to the disturbance of the refrigerant flow after passing through the valve port. This vibration may be transmitted to the operating shaft or the like to generate abnormal noise. In particular, when the valve member is a needle part, the fine vibration may cause the needle part to repeatedly collide with the valve port and wear the valve port (valve seat). Such vibration of the valve member is also caused by the flow of the refrigerant.

  An object of the present invention is to provide a pressure-actuated valve and a refrigeration cycle that can suppress vibration of the valve member and prevent the valve member from repeatedly colliding with the valve port and generating abnormal noise.

The pressure-actuated valve according to claim 1 is a pressure-actuated valve having a diaphragm larger than a diameter of the valve port, wherein the diaphragm is actuated in accordance with a pressure of a fluid on a primary side, and actuates a valve member. at least a portion of said valve member for opening and closing the valve port to flow is located downstream of the valve port, the valve member, on one side with respect to the axis of the valve port by the force of fluid flowing from said valve port An urging means for urging is provided.

  The pressure-actuated valve according to claim 2 is the pressure-actuated valve according to claim 1, wherein the biasing means is configured by an asymmetrical shape portion that is non-rotationally symmetric about the axis of the valve member. Features.

The pressure-actuated valve according to claim 3 is the pressure-actuated valve according to claim 2, wherein the valve member is opposed to the valve port and has a needle portion whose diameter decreases from the upstream side to the downstream side of the fluid, A boss portion connected to the downstream side of the needle portion, and the asymmetrical shape portion is formed in the boss portion.

  The pressure-actuated valve according to claim 4 is the pressure-actuated valve according to claim 2, wherein the valve member has a needle portion that is opposed to the valve port and has a diameter that decreases from the upstream side to the downstream side of the fluid. The asymmetric shape part is formed in the needle part.

  The pressure-actuated valve according to claim 5 is the pressure-actuated valve according to claim 1, wherein the biasing means is a non-rotationally symmetric asymmetric shape around the axis formed in a valve seat around the valve port. It is comprised by the part.

  The pressure-actuated valve according to claim 6 is the pressure-actuated valve according to claim 5, wherein the asymmetrical shape portion is formed in a valve seat around the valve port and is biased to one side with respect to the axis. It is the counterbore part formed in this.

  The pressure-actuated valve according to claim 7 is the pressure-actuated valve according to claim 1, wherein the urging means has an asymmetric shape portion that is disposed downstream of the valve port and is non-rotationally symmetric about the axis. It is characterized by comprising a ring-shaped member.

  The refrigeration cycle of claim 8 includes a compressor that compresses a refrigerant that is a fluid, a condenser, an evaporator, and an expansion valve that expands the refrigerant between the condenser and the evaporator to decompress the refrigerant. The pressure actuated valve according to any one of claims 1 to 7, wherein the pressure actuated valve is connected between a discharge side pipe of the compressor and a secondary side pipe of the expansion valve.

  According to the pressure actuated valve of claim 1, the biasing means causes the force due to the flow of the fluid after passing through the valve port to act asymmetrically with respect to the both sides of the axis of the valve port with respect to the valve member. Is urged in a direction crossing the axis of the valve port, and vibration of the valve member can be suppressed. As a result, it is possible to prevent the valve member from repeatedly colliding with the valve port (or the valve seat), so that no abnormal noise (collision noise) is generated and quietness is obtained. Further, the valve port can be prevented from being worn.

  According to the pressure actuated valve of the second, third, and fourth aspects, the same effect as that of the first aspect can be obtained by setting the shape of the valve member.

  According to the pressure actuated valves of claims 5 and 6, the same effect as in claim 1 can be obtained by setting the shape of the valve seat.

  According to the pressure actuated valve of claim 7, the same effect as that of claim 1 can be obtained by arranging the ring-shaped member.

  According to the refrigeration cycle system of the eighth aspect, the same effects as those of the first to seventh aspects can be obtained.

It is a longitudinal section of the pressure operation valve of a 1st embodiment of the present invention. It is a figure which shows the valve member in 1st Embodiment. It is a side view which shows the modification of the valve member in 1st Embodiment. It is a longitudinal cross-sectional view of the pressure actuated valve of 2nd Embodiment of this invention. It is an expanded sectional view and bottom view which show the valve seat part in 2nd Embodiment. It is a longitudinal cross-sectional view of the pressure actuated valve of 3rd Embodiment of this invention. It is an expanded sectional view and a top view showing a ring member in a 3rd embodiment. It is a schematic block diagram of the refrigerating cycle which concerns on embodiment of this invention.

  Next, an embodiment of a pressure operated valve of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of a pressure-actuated valve according to the first embodiment, and FIG. 2 is a view showing a valve member according to the first embodiment. 2A is a side view of the valve member, and FIG. 2B is a bottom view of the valve member.

  The pressure operating valve 10 of this embodiment is an example of a pressure adjusting valve that adjusts the high pressure on the discharge side of the compressor of the refrigeration cycle as will be described later. This pressure-actuated valve 10 has a metal valve body 1. In the valve body 1, a pipe connection hole 11, a pipe connection hole 12, a valve port 13, a valve chamber 14, a primary side port 15, a spring chamber 16, a pressure equalizing hole 17 and a guide hole 18 are formed. Has been. A primary side joint 11a into which a fluid flows is attached to the pipe connection hole 11 as shown by an arrow, and a secondary side joint 12a from which a fluid flows out is attached to the pipe connection hole 12 as shown by an arrow. The primary side joint 11a and the secondary side joint 12a are assembled integrally with the valve body 1 by brazing or the like.

  The primary side joint 11 a is communicated with the valve chamber 14 via the primary side port 15, and the secondary side joint 12 a is communicated with the valve chamber 14 via the valve port 13. Further, the primary side port 15 communicates with the spring chamber 16 through the pressure equalizing hole 17. The valve port 13 is a cylindrical hole (hole having a circular cross section) centered on the axis L, and the periphery of the valve port 13 is a valve seat 13a.

  The valve member 2 is disposed in the valve port 13, the valve chamber 14 and the guide hole 18. The valve member 2 includes a needle portion 21, a valve rod 22, a cylindrical portion 23, and a boss portion 24. The needle portion 21 has a shape that is opposed to the valve port 13 and is reduced in diameter from the upstream side to the downstream side. Then, the needle portion 21 of the valve member 2 is advanced and retracted into the valve port 13 by the action of a diaphragm portion 4 described later, and the valve port 13 is opened and closed. At least a part of the valve member 2 (the cylindrical portion 23 and the boss portion 24) is located on the downstream side with respect to the valve port 13.

  The spring chamber 16 is formed as a ring-shaped deep groove around the guide hole 18, and the coil spring 3 is disposed in the spring chamber 16. A hook-shaped spring receiver 22a is fixed to the end of the valve rod 22 of the valve member 2, and the coil spring 3 is compressed between the bottom of the spring chamber 16 and the spring receiver 22a. As a result, the coil spring 3 biases the valve member 2 toward the later-described diaphragm 43, and presses the valve rod 22 against the diaphragm 43. The guide hole 18 has a cylindrical shape aligned with the valve stem 22, and the valve stem 22 can slide accurately in the direction of the axis L within the guide hole 18.

  A diaphragm portion 4 is attached to the upper portion of the valve body 1. Diaphragm part 4 comprises a case body with upper lid 41 and lower lid 42, and this case body is fitted to annular rib 1 a at the upper part of valve body 1 at mounting hole 42 a of lower lid 42. By being attached, the valve body 1 is fixed. Further, a diaphragm 43 is provided between the upper lid 41 and the lower lid 42, and the diaphragm 43 and the lower lid 42 define a pressure chamber 44 that communicates with the spring chamber 16. In the upper lid 41, a contact 45 that contacts the diaphragm 43 is disposed, and a ball 55 of the pressure adjusting unit 5 described later contacts the contact 45.

  The pressure in the pressure chamber 44 is made equal to the refrigerant pressure in the primary port 15 introduced by the spring chamber 16 and the pressure equalizing hole 17, and when the refrigerant pressure becomes equal to or higher than the set pressure, the diaphragm 43 is activated, The valve member 2 is separated from the valve seat 13a by an amount corresponding to the pressure of the refrigerant in the side port 15, and the valve is opened. As will be described later, when the high-pressure pressure on the discharge side of the compressor rises above a certain value, the primary side joint 11a has a refrigeration cycle when it is used for bypassing the refrigerant to the inlet side of the evaporator. The secondary side joint 12a is connected to the inlet side of the evaporator.

  A pressure adjusting unit 5 is attached to the upper part of the diaphragm unit 4. The pressure adjustment unit 5 includes a substantially cylindrical spring box 51, a spring receiver 52, an adjustment screw 53, a coil spring 54, and a ball 55. The ball 55 is inserted into the insertion hole 41 a of the upper lid 41 of the diaphragm portion 4.

  A female screw portion 41 a is formed on the upper inner peripheral surface of the spring box 51, and a male screw portion 53 a is formed on the outer periphery of the adjustment screw 53. Then, the adjustment screw 53 is attached to the spring box 51 by screwing the male screw portion 53a with the female screw portion 51a. The adjustment screw 53 has an engagement groove 53b at the top, and a jig or the like is engaged with the engagement groove 53a and the adjustment screw 53 is rotated to move the adjustment screw 53 in the axis L direction. . The coil spring 54 is fitted into the boss portion 521 of the spring receiver 52 and the boss portion 531 of the adjustment screw 53, and is disposed in a compressed state between the spring receiver 52 and the adjustment screw 53. The spring receiver 52 is urged toward the ball 55 by the spring force of the coil spring 54, and the abutment 45 urges the diaphragm 43 in the valve closing direction via the ball 55.

  As described above, in the pressure adjustment unit 5, the adjustment screw 53 can be turned to adjust the compression amount of the coil spring 54 by the amount of thrust of the adjustment screw 53 in the axis L direction. The applied urging force can be adjusted. Therefore, the pressure (set pressure) at which valve opening is started by the increase in the fluid pressure in the valve chamber 14 can be accurately set to a desired pressure. After setting, the adjustment screw 53 is fixed by caulking or bonding.

  The boss portion 24 of the valve member 2 has a D-cut surface 241 cut at a part thereof in a plane parallel to the axis L. That is, the portion of the D-cut surface 241 of the valve member 2 is a non-rotationally symmetric asymmetric shape portion around the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 1). In this way, the boss portion 24 constitutes “biasing means”.

  In this embodiment, since the flow rate of the refrigerant passing through the D-cut surface 241 side increases, a pressure difference is generated in the fluid pressure in the left-right direction at the asymmetric portion of the boss portion 24, and one side with respect to the valve member 2. A force acts in the direction intersecting the axis L. Thereby, the vibration of the valve member 2 can be suppressed. As a result, it is possible to prevent the valve member 2 from repeatedly colliding with the valve seat 13a, so that no abnormal noise is generated and quietness is obtained. Further, it is possible to prevent the valve port 13 from being worn.

  FIG. 3 is a side view showing a modification of the valve member 2. The valve member 2 of this modified example includes a needle portion 25 and a valve stem 26, and a notch 251 is formed at the tip of the needle portion 25. The notch 251 is formed only on one side of the axis L. That is, the needle portion 25 having the notch portion 251 of the valve member 2 is an asymmetric shape portion that is non-rotationally symmetric about the axis L. Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 (needle valve 25) to act asymmetrically on both sides of the axis L of the valve port 13. Thus, the notch 251 at the tip of the needle portion 25 constitutes an “urging means”.

  In this modification, since the flow rate of the refrigerant passing through the notch portion 251 side increases, a pressure difference occurs in the fluid pressure in the left-right direction at the asymmetrical portion of the needle portion 25, and one side with respect to the valve member 2. A force acts in the direction intersecting the axis L. Thereby, the vibration of the valve member 2 can be suppressed and the effect similar to 1st Embodiment is acquired.

  FIG. 4 is a longitudinal sectional view of the pressure operated valve according to the second embodiment, and FIG. 5 is an enlarged sectional view of a main part of the pressure operated valve according to the second embodiment. FIG. 5B is a view taken in the direction of arrows AA in FIG. The major difference between the second embodiment and the first embodiment is the configuration of the valve member and the valve seat 13a. Hereinafter, in 2nd and 3rd embodiment, the same code | symbol is attached | subjected to the same element and corresponding element as 1st Embodiment, and the overlapping description is abbreviate | omitted.

  The valve member 2 according to the second embodiment has substantially the same shape as the valve member 2 of the modified example. That is, the valve member 2 has a shape in which the notch portion 251 of the needle portion valve 25 in the modified example is eliminated, and has a needle portion 27 having a normal shape. In the valve main body 1 according to the second embodiment, a counterbore 131 that is partially cylindrical is formed at a position shifted from the axis L of the valve port 13 on the secondary joint 12 a side of the valve seat 13. That is, the counterbore 131 in the valve seat 13 is formed at a position that is biased to one side with respect to the axis L on the downstream side of the valve port 13. The counterbore portion 131 is an asymmetric shape portion that is non-rotationally symmetric about the axis L.

  Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides of the axis L of the valve port 13 (left and right sides in FIG. 4). In this manner, the counterbore 131 constitutes “biasing means”. And in this 2nd Embodiment, since the flow volume of the refrigerant | coolant which passes the counterbore part 131 side increases, a pressure difference arises in the fluid pressure in the left-right direction in the asymmetrical part of the downstream of the valve port 13, and a valve member The force acts on one side (direction intersecting the axis L) with respect to 2 (needle portion 27). Thereby, the vibration of the valve member 2 can be suppressed and the effect similar to 1st Embodiment is acquired.

  FIG. 6 is a longitudinal sectional view of a pressure-actuated valve according to the third embodiment, and FIG. 7 is a view showing a ring-shaped member according to the third embodiment. FIG. 7A is a cross-sectional view of the ring-shaped member, and FIG. 7B is a plan view of the ring-shaped member. In FIG. 7A, the valve member 2 is shown by a one-dot chain line. The third embodiment is different from the second embodiment in that a ring-shaped member 6 is provided between the valve seat 13a and the secondary side joint 12a. The valve member 2 is the same as in the second embodiment.

  As shown in FIG. 7, the ring-shaped member 6 has an opening 61 whose maximum diameter is larger than that of the valve port 13. The opening 61 has a horseshoe shape, and has a wall portion 62 that bulges toward the axis L in a portion corresponding to the straight line of the horseshoe shape. The wall portion 62 of the ring-shaped member 6 is formed at a position deviated to one side with respect to the axis L on the downstream side of the valve port 13, and the ring-shaped member 6 has a non-rotationally symmetric asymmetric shape around the axis L. Has become a department.

  Thereby, the force by the flow of the refrigerant that has passed through the valve port 13 causes the valve member 2 to act asymmetrically on both sides (left and right sides in FIG. 6) of the axis L of the valve port 13. Thus, the ring-shaped member 6 constitutes “biasing means”. And in this 3rd Embodiment, since the flow volume of the refrigerant | coolant which passes the opening 61 of the ring-shaped member 6 increases on the opposite side to the wall part 62, it is set to fluid pressure in the left-right direction in the part which becomes asymmetric of the ring-shaped member 6. A pressure difference is generated, and a force acts on one side (direction intersecting the axis L) with respect to the valve member 2 (needle portion 27). Thereby, the vibration of the valve member 2 can be suppressed and the effect similar to 1st Embodiment is acquired.

  FIG. 8 is a schematic configuration diagram of a refrigeration cycle according to the embodiment. The refrigeration cycle 100 is used for an air conditioner such as a room air conditioner. In FIG. 8, 10 is a pressure operation valve of each embodiment, 20 is an evaporator (indoor heat exchanger), 30 is a condenser (outdoor heat exchanger), 40 is an expansion valve that throttles the refrigerant, and 50 is a compressor. . The refrigerant compressed by the compressor 50 flows into the condenser 30, is throttled by the expansion valve 40, and is circulated in the order of the compressor 50 through the evaporator 20. As a result, the room is cooled.

  A primary side joint 11 a of the pressure operating valve 10 is connected to the discharge side pipe 50 a of the compressor 50, and a secondary side joint 12 a of the pressure operating valve 10 is connected to the secondary side joint 40 a of the expansion valve 40. . And if the pressure of the refrigerant | coolant which flows out out of the compressor 50 becomes more than preset pressure, the pressure action valve 10 will act | operate and a high pressure refrigerant | coolant will be bypassed to the secondary side joint 40a of the expansion valve 40. FIG.

  In each of the above embodiments, the pressure regulating valve that regulates the high pressure on the discharge side of the compressor of the refrigeration cycle has been described as an example. However, the pressure actuated valve of the present invention controls the flow of other fluids. It can also be applied to. For example, the present invention can also be used in a case where the fluid is provided in a pipe that is a liquid and the pipe is prevented from being sealed.

  As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention.

DESCRIPTION OF SYMBOLS 1 Valve body 11 Piping connection hole 12 Piping connection hole 13 Valve port 13a Valve seat 14 Valve chamber 16 Spring chamber 17 Pressure equalizing hole 18 Guide hole 2 Valve member 21 Needle part 22 Valve rod 23 Column part 24 Boss part (biasing means)
241 D-cut surface 25 Needle part 251 Notch part (biasing means)
6 Ring-shaped member (biasing means)
61 Opening 62 Wall 10 Pressure Actuating Valve 20 Evaporator 30 Outdoor Heat Exchanger (Condenser)
40 Expansion valve 40a Secondary side piping 50 Compressor 50a Discharge side piping 100 Refrigeration cycle L Axis

Claims (8)

A pressure actuated valve having a diaphragm larger than the diameter of the valve port, the diaphragm being actuated according to the pressure of the fluid on the primary side, and actuating the valve member;
At least a portion of said valve member for opening and closing the valve port to flow the fluid, located downstream of the valve port, a valve member, relative to the axis of the valve port by the force of fluid flowing from said valve port And a biasing means for biasing to one side.   2. The pressure-actuated valve according to claim 1, wherein the urging means is formed of an asymmetrical shape portion that is non-rotationally symmetric about the axis of the valve member. The valve member has a needle portion that is opposed to the valve port and has a diameter that decreases from the upstream side to the downstream side of the fluid, and a boss portion that is connected to the downstream side of the needle portion, and the asymmetrical shape portion is The pressure actuated valve according to claim 2, wherein the pressure actuated valve is formed in the boss portion.   3. The valve member has a needle portion that is diameter-reduced from an upstream side to a downstream side of a fluid so as to face the valve port, and the asymmetrical shape portion is formed in the needle portion. The pressure-actuated valve described in 1.   2. The pressure-actuated valve according to claim 1, wherein the biasing means is configured by an asymmetrical shape portion that is non-rotationally symmetric about the axis formed in a valve seat around the valve port.   6. The pressure-actuated valve according to claim 5, wherein the asymmetrical shape portion is a counterbore portion formed in a valve seat around the valve port and formed at a position biased to one side with respect to the axis. .   2. The pressure-actuated valve according to claim 1, wherein the urging means is configured by a ring-shaped member that is disposed on the downstream side of the valve port and has a non-rotationally symmetric asymmetric shape around the axis. .   A compressor that compresses a refrigerant that is a fluid, a condenser, an evaporator, an expansion valve that expands and depressurizes the refrigerant between the condenser and the evaporator, and a discharge side pipe of the compressor A refrigeration cycle comprising: the pressure operating valve according to any one of claims 1 to 7 connected between a secondary side pipe of the expansion valve.

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