JP6697975B2 - Expansion valve - Google Patents

Description

  The present invention relates to an expansion valve with a built-in temperature sensing mechanism used in a refrigeration cycle.

  BACKGROUND ART Conventionally, for a refrigeration cycle used for an air conditioner mounted on an automobile, a temperature expansion valve with a built-in temperature sensing mechanism that adjusts the amount of refrigerant passing according to temperature has been used. The valve body of such an expansion valve has an inlet port into which high pressure refrigerant is introduced and a valve chamber communicating with the inlet port, and a valve element drive mechanism called a power element is provided at the top of the valve body. To be done.

  The spherical valve element arranged in the valve chamber is arranged so as to face the valve seat of the valve hole that opens in the valve chamber. The valve body is supported by a support member arranged in the valve chamber, and is urged toward the valve seat by a coil spring installed between an adjusting screw attached to the valve body and the support member. The valve element is operated by the valve rod driven by the power element to control the opening degree of the throttle passage between the valve element and the valve seat. Further, the refrigerant having passed through the valve hole is sent from the outlet port to the evaporator side.

  Here, the high-pressure refrigerant flowing from the inlet port passes through the valve chamber, but the high-pressure refrigerant sent to the expansion valve may have a pressure fluctuation on the upstream side in the refrigeration cycle. When transmitted, it may cause a problem of destabilizing the operation of the valve body. This pressure fluctuation causes the valve body to vibrate, resulting in abnormal noise.

  In order to prevent such vibration, there has been conventionally proposed a configuration in which a vibration-proof spring that elastically supports the valve body is provided in the valve chamber (see Patent Documents 1 and 2).

JP, 2005-156046, A JP, 2013-68368, A

  Although the structure of the conventional anti-vibration spring has a certain anti-vibration effect, it also has the following problems.

That is, in Patent Document 1, a support member that supports the valve body is provided with a vibration-proof spring having a plurality of elastic arms (legs), and the tips of the legs are elastically brought into contact with the inner wall of the valve chamber. Accordingly, a configuration is disclosed in which the support member is stably supported from its periphery toward the center in the direction.
However, in Patent Document 1, since the leg portion of the anti-vibration spring directly collides with the refrigerant flowing into the valve chamber through the inlet port, turbulence may occur in the high-pressure refrigerant introduced into the valve chamber. .. This point will be described with reference to FIGS.

  As shown in FIG. 7, the high-pressure refrigerant delivered by the compressor (not shown) enters the inlet port 320 as indicated by arrow A, is introduced into the valve chamber 324 through the inlet hole 320a. Here, the conventional vibration-proof spring 300 includes an annular plate-shaped portion 301 sandwiched between a support member 400 of a valve body and a coil spring 344 that biases the support member 400 toward the valve body, and the plate-shaped portion 301. It is composed of a plurality of leg portions 302 that are bent and formed radially from the portion 301 and are inclined in the direction of the central axis of the valve stem. Then, the plurality of legs 302 extend to the lower side wall 324b of the valve chamber 324 below the inlet hole 320a. Here, the leg portion 302 forms various flow passage shapes with respect to the inlet hole 320a according to the angle at which the anti-vibration spring 300 is attached (rotation angle about the center point of the anti-vibration spring 300). It will be.

8 to 10 show examples of the shape of the inlet passage formed by the inlet hole 320a and the leg portion 302 viewed from the inlet port 320 side. FIG. 8 shows a case in which the leg portion 302 is located vertically in the center of the inlet hole 320a, and the facing flow channel is divided into two. FIG. 9 shows a case where the leg portion 302 blocks one side of the inlet hole 320a. FIG. 10 shows a case in which the leg portions 302 are located on both sides of the inlet hole 320a and form a gate-shaped flow path. As described above, the leg portion 302 blocks a part of the inlet hole 320a in various modes, and the inlet flow path has a shape corresponding to the leg portion 302. Therefore, turbulent flow may occur depending on the orientation of the vibration-proof spring 300. Due to the turbulent flow, a noise passing through the refrigerant is generated, and there is a concern that abnormal noise may occur due to bursting of bubbles containing bubbles. Further, there is a concern that the flow rate of the introduced refrigerant will decrease.
On the other hand, Patent Document 2 discloses a technique for shortening the length of the leg portion in the direction of the central axis by making the leg portion of the anti-vibration spring extend radially around the central axis of the valve rod. However, in this case, if the vibration-proof spring is not inserted into the valve body while being twisted, there is a concern that a load is applied to the leg portion, especially the root portion thereof, and the vibration-proof spring is deformed.

  Then, the objective of this invention is suppressing the vibration of a valve body, and suppressing the deformation|transformation of an anti-vibration spring, and providing the expansion valve provided with the anti-vibration spring which reduced the passing noise of a refrigerant|coolant.

In order to solve the above problems, one of the typical expansion valves of the present invention is a valve main body having an inlet hole through which a refrigerant flows into a valve chamber and a valve hole through which the refrigerant flows out of the valve chamber,
A valve body for adjusting the amount of refrigerant flowing through the valve hole,
A power element attached to the valve body to drive the valve body via a valve rod;
A support member for supporting the valve body,
A coil spring for pressing the valve element in the valve closing direction via the support member,
A vibration-proof spring for preventing vibration of the valve body,
The support member includes a main body portion that is fitted into the coil spring,
The vibration-proof spring has an annular base portion arranged between the support member and the coil spring, and a plurality of leg portions radially extending from the base portion,
Each of the plurality of legs includes an upper portion formed radially on the same surface as the base portion, a bending portion that bends from the upper portion to the coil spring side, and a side portion that extends downward from the bending portion. ,
Each of the plurality of legs is in contact with the side of the valve chamber closer to the valve hole than the inlet hole,
In the direction along the central axis of the coil spring and the end portion of the inlet hole side of the leg portion, the end portion of the inlet hole side of the main body of the support member, of the valve hole side edge of the inlet aperture Located in the vicinity, at least one of the legs is arranged on the opposite side of the inlet hole with the coil spring interposed therebetween .

In one embodiment of the expansion valve according to the present invention, the plurality of leg portions may further include a connecting portion between leg portions that are adjacent to each other on the same plane as the base portion.

  Since the expansion valve according to the present invention is configured as described above, it is possible to suppress the vibration of the valve element and the deformation of the vibration-proof spring to reduce the passing noise of the refrigerant.

1 is a vertical sectional view showing a first embodiment of an expansion valve according to the present invention. It is a longitudinal cross-sectional view of the main part of the expansion valve of the first embodiment. It is a perspective view which shows the vibration-proof spring of 1st Example. It is a top view which shows the vibration-proof spring of 1st Example. It is a side view which shows the vibration-proof spring of 1st Example. It is a top view which shows the vibration-proof spring of 2nd Example. It is a longitudinal cross-sectional view showing an example of a conventional expansion valve. It is a figure which shows the shape example of the inlet flow path of the conventional expansion valve. It is a figure which shows the shape example of the inlet flow path of the conventional expansion valve. It is a figure which shows the shape example of the inlet flow path of the conventional expansion valve.

<First embodiment>
FIG. 1 is a vertical sectional view showing a first embodiment of an expansion valve according to the present invention. FIG. 2 is a vertical cross-sectional view of the main part of the expansion valve of the first embodiment.

  As shown in FIG. 1, the expansion valve 10 includes a valve body 11, a power element 70, a valve body 40, a valve rod 60, an O-ring 36, a support member 100, a vibration-proof spring 140, a coil spring 44, and an adjusting screw 120. There is.

  The valve body 11 is made of, for example, an aluminum alloy, and can be obtained, for example, by extrusion-molding an aluminum alloy or the like with the X direction in FIG. 1 as the extrusion direction and subjecting this to machining. The valve body 11 includes a power element mounting portion 12, which is a female screw formed on an upper surface portion and screwed into a male screw 72a of the power element 70 to fix the male screw 72a, an inlet port 20 into which high-pressure refrigerant is introduced, and an inlet port. The refrigerant outlet port 28 through which the refrigerant flowing in from 20 flows out, the refrigerant return passage 30, the hole 33 for mounting the O-ring 36, the female screw 11a formed on the bottom surface of the valve body 11, and the valve body 11 It has a mounting hole (or a female screw for mounting) 80 for mounting on an evaporator (not shown), other components, and the like.

  The power element mounting portion 12 is formed as a bottomed cylindrical hole having a circular opening on the upper surface of the valve body 11 and having an internal thread on its inner wall surface. At the center of the bottom of this hole, an opening 32 is formed (communicating) with the return passage 30. Here, the direction of the central axis of the power element attachment portion 12 is a direction (Y direction) substantially orthogonal to the passage direction (X direction) of the refrigerant passing through the return passage 30.

  The female screw 11a is formed so as to open on the lower surface of the valve body 11, and an insertion hole 11b is formed in the upper portion thereof. The valve chamber 24 is formed inside the valve body 11 by closing the opening of the female screw 11a with the adjusting screw 120. The valve chamber 24 has a cylindrical side wall surface, and an upper wall surface 24a is above the upper end of the inlet hole 20a and a lower wall surface 24b is below the lower end of the inlet hole 20a. The upper wall surface 24a secures a vertical length required for sliding the vibration-proof spring 140 described later. Further, the portion between the upper end of the insertion hole 11b and the inlet hole 20a may have a thickness necessary for strength.

  The inlet port 20 is formed so as to communicate with the valve chamber 24 from the side of the valve chamber 24 via an inlet hole 20a having a smaller diameter than the inlet port 20. Further, a narrowed portion 28 a having a smaller diameter than the outlet port 28 is provided at the back of the outlet port 28, and the narrowed portion 28 a is arranged above the valve chamber 24. The narrowed portion 28a communicates with the upper end portion of the valve chamber 24 via the valve hole 26 serving as an orifice. A valve seat 25 is formed on the valve chamber 24 side of the valve hole 26. A through hole 29 is formed in the valve body 11 in the vertical direction (Y direction in FIG. 1) so as to connect the return passage 30 and the narrowed portion 28a. The valve hole 26, the through hole 29, the opening 32, and the valve chamber 24 are arranged such that their central axes are on the same straight line. The return passage 30 is formed further above the outlet port 28 in the valve body 11 and penetrates the valve body 11 in the lateral direction (X direction in FIG. 1 ). A hole 33 coaxial with the through hole 29 and having a larger inner diameter than the through hole 29 is formed below the return passage 30.

  In addition, in FIG. 1, the inlet port 20 and the outlet port 28 are opened to the left and right of the valve body 11, and the return passage 30 is also formed so as to penetrate right and left of the valve body 11. Both openings of the outlet port and the return passage can be variously changed depending on the layout of the refrigeration cycle in which the expansion valve is arranged. For example, the left side openings of the outlet port 28 and the return passage 30 are opened to the front side or the back side of the paper of FIG. 1 (that is, the inlet port and the outlet port are orthogonal to each other when viewed from the center line of the valve rod 60). Similarly, both openings of the return passage may be formed so as to be orthogonal to each other.

  The power element 70 includes an upper lid member 71 made of, for example, stainless steel and a receiving member 72 having a through hole 72b in a central portion, a diaphragm 73 sandwiched between the upper lid member 71 and the receiving member 72, and this diaphragm. It is composed of a stopper member 90 and the like arranged between 73 and the receiving member 72. Then, the upper lid member 71, the diaphragm 73, and the receiving member 72 are integrated by circumferentially welding the overlapped end portions. A pressure working chamber 75 is formed between the upper lid member 71 and the diaphragm 73. The pressure working chamber 75 is filled with a working gas and then sealed with a sealing plug 65. The lower part of the receiving member 72 is cylindrical, and a male screw 72a is formed on the periphery thereof, and by being screwed with a female screw of the power element mounting portion 12 (a female screw opened on the upper surface of the valve body 11) via the packing 35, The power element 70 is attached to the valve body 11.

  The valve body 40 is a spherical member arranged so as to face the valve seat 25, and is provided inside the valve chamber 24. The valve rod 60 is provided so as to be inserted into each of the valve hole 26, the through hole 29, and the opening 32 of the valve body 11, and the upper end of the valve rod 60 is below the stopper member 90 of the power element 70. It abuts on the receiving portion 92 provided, and its lower end is arranged so as to come into contact with the valve body 40. The O-ring 36 is attached to the hole 33, and the stopper member 37 attached to the upper portion prevents the O-ring 36 from coming off.

  The support member 100 is a member that supports the valve body 40 in the direction of the valve seat 25 (direction of the valve rod 60). Although the valve body 40 is fixed to the support member 100, the support member 100 is always biased by the coil spring 44 toward the valve seat 25 and the valve rod 60, so that the support member 100 abuts on the valve body 40. It may be a simple structure. The support member 100 includes a main body 103, an upper surface 101, and a flange 102. The upper surface of the cylindrical main body portion 103 is an upper surface portion 101 having a conical recess and supporting the lower surface of the valve body 40. Further, the support member 100 is provided with a flange portion 102 projecting from the main body portion 103 to the side surface (outer peripheral side), and the lower surface of the flange portion 102 receives the vibration-proof spring 140 and one end of the coil spring 44. .. At this time, the outer diameter of the body portion 103 below the flange portion 102 is smaller than the inner diameter of the coil spring 44, and is located inside the coil spring 44.

  The coil spring 44 is installed between the lower surface of the flange portion 102 provided on the support member 100 and the recess 125 formed on the adjusting screw 120. The valve body 40 is biased toward the valve seat 25 via the support member 100 by the elastic force of the coil spring 44. An anti-vibration spring 140 is installed between the lower surface of the flange portion 102 and the coil spring 44, and details of this configuration will be described later.

The adjusting screw 120 includes a main body 121, a hexagonal hole 122, an insertion portion 123, a tip portion 124, and a recess 125. The insertion portion 123 is provided on the upper portion of the main body portion 121 with a smaller outer diameter than the main body portion 121, and the tip portion 124 is provided on the upper portion of the insertion portion 123 with a smaller outer diameter than the insertion portion 123. There is. Further, the outer circumference of the main body portion 121 is a female screw 11 that opens to the lower surface of the valve main body 11.
It is a male screw part 121a for screwing into a. Furthermore, a recess 125 having a cylindrical space with an open top is provided at the top of the adjusting screw 120. The recess 125 is formed to a depth reaching the vicinity of the main body 121. Further, the inner diameter of the recess 125 is slightly larger than the outer diameter of the coil spring 44 so that the coil spring 44 can be stably arranged in the recess 125. In addition, the adjusting screw 120 (main body 121) is provided below the adjusting screw 120.
A hexagonal hole 122 for inserting a hexagonal wrench (not shown) for turning is provided.

  FIG. 3 is a perspective view showing the vibration-proof spring 140 of the first embodiment. FIG. 4 is a plan view showing the vibration-proof spring 140 of the first embodiment. FIG. 5 is a side view showing the vibration damping spring of the first embodiment. The vibration-proof spring 140 includes a base 141 and legs 142. The vibration-proof spring 140 can be press-molded from an elastic plate material such as stainless steel or its alloy.

  The base portion 141 is an annular plate-shaped member that forms an upper portion of the vibration-proof spring 140, and has a mounting hole 141a at the center.

  A plurality of legs 142 extend from the outer peripheral side of the base 141 in a direction perpendicular to the tangential line in the circumferential direction, in other words, radially. In the first embodiment, eight leg portions 142 having the same length are provided at equal angular intervals. The leg portion 142 includes an upper portion 142a, a bent portion 142b, a side portion 142c, and a protruding portion 142d. The leg portion 142 is bent downward at the bent portion 142b.

  The upper portion 142a is formed in substantially the same plane as the base portion 141. Therefore, in the root portion of each leg portion 142, a cutout 145 having a predetermined shape is secured in the surface having the base portion 141. In FIG. 4, the length C is the length of the upper portion 142a. Since the leg portion 142 includes the upper portion 142a, the leg portion 142 is formed closer to the center of the base portion 141 than the bent portion on the same plane as the base portion 141. Further, in the vicinity of the connecting portion of the upper portion 142a to the base portion 141 (near the root of the leg portion 142), the notch 145 formed between the side surfaces in the width direction of the adjacent upper portions 142a has the same curvature from the root side surface of the upper portion 142a. Are continuously connected to form an arc shape, whereby the upper portions 142a (leg portions 142) are smoothly connected. Of course, the notch 145 may be formed in a shape other than an arc shape by connecting the root side surface of the upper portion 142a with different curvatures.

  The bent portion 142b is formed so as to be continuously bent outward from the upper portion 142a and directed downward (to the coil spring 44 side). The bent portion 142b may have a constant radius of curvature. The bent portion 142b is formed by bending (90-θ) degrees.

  The side portion 142c is linearly formed continuously below the bent portion 142b. The angle of the side portion 142c is θ degrees downward and outward with respect to the vertical direction.

  The protrusion 142d is formed outward in the vicinity of the lower end of the side portion 142c. For example, the protrusion 142d can be formed by a part of the spherical surface such as a hemisphere. When the protrusion 142d is mounted in the valve body 11, the protrusion 142d elastically contacts the upper portion (upper wall surface 24a) of the opening of the inlet hole 20a, but even when the valve body 40 is at the lowest position. The dimensions of each part are set so that the protrusion 142d does not enter the opening of the inlet hole 20a.

  The length of the leg portion 142 in the vertical direction is set to an appropriate length as long as the lower end portion of the leg portion 142 does not fall into the opening of the inlet hole 20a at the lowest end within the range of vertical movement of the vibration-proof spring 140. However, in order not to hinder the flow of the refrigerant introduced from the inlet port 20, it is desirable that the lower end portion of the leg portion 142 does not reach the opening portion of the inlet hole 20a. Further, in the present embodiment, the width of each leg 142 is formed to have a constant width in all of the upper portion 142a, the bent portion 142b, and the side portion 142c, but the present invention is not limited thereto. However, it is possible to narrow the width of the tip, widen the width of the tip, or change the shape to the most suitable shape for suppressing the vibration of the valve body. Further, the thickness of the leg portion 142 (the thickness of the vibration-proof spring 140 when the vibration-proof spring 140 is formed by pressing from one elastic plate material) is also a thickness suitable for suppressing the vibration of the valve body. .

  The vibration-proof spring 140 has a gap D (FIG. 4) between the adjacent leg portions 142 for the refrigerant to pass therethrough. The outer diameter of the vibration-proof spring 140 connected at the tip of the protrusion 142d is larger than the inner diameter of the upper wall surface 24a in the valve chamber 24, and elastic force acts when the valve chamber 24 is attached. The projection 142d is adapted to be pressed against the wall surface 24a. Further, the size in which the coil spring 44 is arranged inside the leg portion 142 is secured.

  As shown in FIGS. 1 and 2, when mounting the vibration-proof spring 140, first, the main body 103 of the support member 100 is passed through the mounting hole 141a of the vibration-proof spring 140 from the lower side, and the base 141 of the vibration-proof spring 140 is inserted. The upper surface of the above is brought into contact with the lower surface of the flange portion 102 of the support member 100. Next, the coil spring 44 is attached from below the vibration-proof spring 140. At this time, the main body 103 of the support member 100 is arranged inside the coil spring 44, and the upper surface of the coil spring 44 contacts the lower surface of the base 141 of the vibration-proof spring 140. As a result, the vibration-proof spring 140 is installed inside the valve chamber 24.

  In the expansion valve 10 to which the vibration-proof spring 140 is attached, the base portion 141 of the vibration-proof spring 140 is urged by the coil spring 44 from the lower side. It is attached by being sandwiched. Then, in the vibration-proof spring 140, the elastic force of the leg portion 142 pushes the protrusion 142d toward the upper wall surface 24a of the valve chamber 24 with a predetermined force, and a sliding resistance is generated according to the movement of the valve body 40. To do.

  Next, the operation will be described. In the expansion valve 10 of the first embodiment of the present invention, the high-pressure refrigerant discharged from the compressor (not shown) flows from the inlet port 20 into the valve chamber 24 through the inlet hole 20a, and the valve hole 26 Through the outlet port 28 and expanded to an evaporator (not shown). Further, the refrigerant sent out from this evaporator passes through the return passage 30 so as to enter from the left inlet and exit to the right outlet, and then return to the compressor. At this time, part of the refrigerant passing through the return passage 30 flows into the lower portion of the power element 70 from the opening 32. Then, the pressure of the working gas in the pressure working chamber 75 is changed according to the temperature change of the refrigerant flowing into the lower portion of the power element 70. At this time, the stopper member 90 moves up and down in response to the movement of the diaphragm 73 deformed according to the change of the internal pressure in the pressure working chamber 75. Then, the movement of the stopper member 90 is transmitted to the valve body 40 via the valve rod 60, and the flow rate of the expanded refrigerant is controlled.

  When the valve body 40 moves in the opening/closing direction (vertical direction), the vibration-proof spring 140 behaves together with the valve body 40 and the support member 100. At this time, since the vibration-proof spring 140 presses the upper wall surface 24a of the valve chamber 24 of the valve body 11 with a predetermined force, when the vibration-proof spring 140 slides, the projection 142d of the leg portion 242 and the valve chamber 24d. A frictional force is generated between the upper wall surfaces 24 a of 24. As a result, the valve body 40 and the support member 100 do not sensitively react in the vertical direction with respect to the pressure fluctuation of the high-pressure refrigerant from the inlet port 20, and the vertical vibration can be prevented or reduced. Further, since the vibration-proof spring 140 presses the upper wall surface 24a of the valve chamber 24 at a plurality of places by the plurality of legs 142, the valve body 40 and the support are supported against the pressure fluctuation of the high-pressure refrigerant from the inlet port 20. The member 100 does not easily move laterally against the pressing force, and exhibits an effect of preventing lateral vibration. At the same time, the vertical movement of the valve body 40 and the support member 100 is guided.

  Further, since the anti-vibration spring 140 is in contact with the upper wall surface 24a of the valve chamber 24 above the inlet hole 20a, the leg portion 142 does not contact the inlet hole 20a, and the generation of the refrigerant flow rate and the turbulent flow is suppressed. Then, the passing sound of the refrigerant can be reduced. Further, since the vibration-proof spring 140 is composed of the radially extending legs 142, the vibration-proof spring 140 can be easily attached to the inside of the valve body 11 simply by inserting it from the opening of the female screw 11a formed at the bottom of the valve body 11. You can Furthermore, since the vibration-proof spring 140 has a constant notch depth (notch 145) on the surface having the base 141, the length of the leg 142 can be made longer than the height of the vibration-proof spring. Therefore, the spring constant of the leg portion 142 can be reduced, the change in force due to the deformation of the leg portion 142 can be reduced, and more stable sliding resistance can be obtained. Further, by making the widths of the legs 142 the same, it becomes easy to calculate the spring constant, that is, to design the first anti-vibration spring 140. Further, since the leg portions 142 are formed in a direction perpendicular to the tangent line of the base portion 141 in the circumferential direction (radially), sliding resistance is generated without applying a circumferential twisting force of the base portion 141. You can

<Second embodiment>
FIG. 6 is a plan view showing the vibration damping spring of the second embodiment. The second embodiment has a structure in which the vibration-proof spring 140 of the first embodiment is replaced with a vibration-proof spring 240, and the other parts are common to those shown in the first embodiment, and therefore common parts are duplicated. The description is omitted.

  The vibration-proof spring 240 includes a base portion 241 and a leg portion 242. The vibration-proof spring 240 can be press-molded from an elastic plate material such as stainless steel or its alloy.

  The base 241 is an annular plate-shaped member that forms the upper portion of the vibration-proof spring 240, and has a mounting hole 141a at the center similar to the first embodiment.

  A plurality of legs 242 extend from the outer peripheral side of the base 241 in a direction perpendicular to the tangential line in the circumferential direction, that is, radially. In the second embodiment, eight leg portions 242 are provided at equal angular intervals. The leg portion 242 includes an upper portion 242a, a bent portion 142b, a side portion 142c, and a protruding portion 142d. The bent portion 142b, the side portion 142c, and the protruding portion 142d are the same as those in the first embodiment.

  Here, the first embodiment has the arcuate notch 145, but the second embodiment is different in that it has the substantially triangular notch 245. Therefore, the length E of the upper portion 242a of the second embodiment is longer than the length C of the upper portion 142a of the first embodiment. Then, the length of the leg portion 242 of the second embodiment becomes longer by that amount. The outer circumference of the base 241 of the second embodiment is smaller than the outer circumference of the base 141 of the first embodiment. The side surfaces in the width direction of the adjacent upper portions 242a may be formed with a small arc-shaped portion in consideration of strength and stress concentration.

  In the second embodiment, by forming the substantially triangular notch 245, the length of the vibration-proof spring 240 can be further increased. Therefore, the spring constant of the leg portion 242 can be further reduced, the change in force due to the deformation of the leg portion 242 can be further reduced, and more stable sliding resistance can be achieved.

  As described above, although the first embodiment and the second embodiment have been shown with respect to the embodiment of the present invention, the present invention is not limited to the above-mentioned embodiments, and various modifications are included. For example, the present invention is not limited to those having all the configurations (structures) provided in the above-described embodiments. It is also possible to delete a part of the configuration of a certain embodiment, replace it with the configuration of another embodiment, or add the configuration of another embodiment to the configuration of a certain embodiment.

  For example, in the above embodiment, the leg portions 142 and 242 are shown to have eight leg portions 142 having the same length at equal angular intervals. If the number of legs 142 and 242 is eight, stability of behavior and sliding resistance can be secured, and the balance of the gap between the legs can be maintained, but the invention is not limited to this. For example, the number of legs may be two or more, and the legs are not limited to have the same length and equal angular intervals. Further, even if the width of the leg portion shown in the above embodiment changes in the middle, it can be adopted.

  Further, although the power element 70 shown in the above-mentioned embodiment is shown to be attached by screws, in addition to this, a cylindrical portion formed on the upper part of the valve body is provided, and the power element 70 is inserted inside this cylindrical portion. The power element 70 may be attached by caulking the cylindrical portion inside.

10 expansion valve 11 valve body 20 inlet port 20a inlet hole 24 valve chamber 24a upper wall surface 25 valve seat 26 valve hole 28 outlet port 30 return passage 40 valve body 44 coil spring 60 valve rod 70 power element 100 support member 120 adjusting screw 140, 240 Anti-vibration springs 141, 241 Bases 142, 242 Legs

Claims (7)

A valve body having an inlet hole through which the refrigerant flows into the valve chamber, and a valve hole through which the refrigerant flows out of the valve chamber;
A valve body for adjusting the amount of refrigerant flowing through the valve hole,
A power element attached to the valve body to drive the valve body via a valve rod;
A support member for supporting the valve body,
A coil spring for pressing the valve element in the valve closing direction via the support member,
A vibration-proof spring for preventing vibration of the valve body,
The support member includes a main body portion that is fitted into the coil spring,
The vibration-proof spring has a ring-shaped base portion arranged between the support member and the coil spring, and a plurality of leg portions radially extending from the base portion,
Each of the plurality of legs includes an upper portion formed radially on the same surface as the base portion, a bending portion that bends from the upper portion to the coil spring side, and a side portion that extends downward from the bending portion. ,
Each of the plurality of legs is in contact with the valve hole side with respect to the inlet hole in the side wall surface of the valve chamber,
In the direction along the central axis of the coil spring and the end portion of the inlet hole side of the leg portion, the end portion of the inlet hole side of the main body of the support member, of the valve hole side edge of the inlet aperture An expansion valve that is located in the vicinity and at least one of the legs is arranged on the opposite side of the inlet hole with the coil spring interposed therebetween .   The expansion valve according to claim 1, wherein the upper portion is defined by a notch formed between the plurality of leg portions in the same plane as the base portion.   The expansion valve according to claim 2, wherein the notch has an arc shape.   The expansion valve according to claim 2, wherein the notch has a substantially triangular shape.   The expansion valve according to claim 1, wherein in each of the plurality of legs, the upper portion, the bent portion, and the side portion have a constant width. Each of the plurality of legs further has a protrusion provided near the lower end of the side portion,
The expansion valve according to any one of claims 1 to 5, wherein the protrusion is in contact with a side wall surface of the valve chamber closer to the valve hole than the inlet hole.   The expansion valve according to any one of claims 1 to 6, wherein each of the plurality of legs further has a connecting portion between adjacent legs on the same surface as the base.