CN116336703A - Expansion valve - Google Patents

Abstract

The expansion valve of the present invention comprises: a valve 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 spool that adjusts an amount of refrigerant flowing through the valve hole; a power element that is attached to the valve body and drives the valve element via a valve stem; a support member that supports the valve body; a coil spring that presses the valve element in a valve closing direction via the support member; and an anti-vibration spring that prevents vibration of the valve body, the anti-vibration spring having an annular base portion disposed between the support member and the coil spring, and a plurality of leg portions radially extending from the base portion, the leg portions being bent toward the coil spring and being in contact with a portion of a side wall surface of the valve chamber that is closer to the valve hole than the inlet hole.

Description

Expansion valve

This application is a divisional application of the following application:

Filing date of the original application: July 21, 2017

The application number of the original application: 201780048788.5

Invention title of the original application: expansion valve

technical field

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

Background technique

Conventionally, a temperature expansion valve with a built-in temperature sensing mechanism that adjusts the passage amount of refrigerant according to temperature has been used in a refrigeration cycle used in an air conditioner mounted on an automobile or the like. The valve main 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 driving mechanism of a valve element called a power element is provided on the top of the valve main body.

The spherical valve element arranged in the valve chamber is arranged facing the valve seat of the valve hole opened to the valve chamber. The valve element is supported by a supporting member arranged in the valve chamber, and is biased toward the valve seat by a coil spring provided between an adjusting screw attached to the valve main body and the supporting member. In addition, the valve core is operated by a valve rod driven by a power element, and controls the opening degree of the throttle passage between the valve core and the valve seat. In addition, the refrigerant passing through the valve hole is sent from the outlet port to the evaporator side.

Here, the high-pressure refrigerant flowing in from the inlet port passes through the valve chamber. However, in the high-pressure refrigerant sent to the expansion valve, there may be a pressure fluctuation on the upstream side in the refrigeration cycle. There is a problem that the operation of the spool becomes unstable. This pressure fluctuation causes the vibration of the spool, resulting in abnormal noise.

In order to prevent such vibration, conventionally, a structure in which an anti-vibration spring elastically supporting the valve element is provided in the valve chamber has been proposed (see Patent Documents 1 and 2).

prior art literature

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2005-156046

Patent Document 2: Japanese Patent Laid-Open No. 2013-68368

The problem to be solved by the invention

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

That is, Patent Document 1 discloses a structure in which an anti-vibration spring having a plurality of elastic arm portions (leg portions) is provided on a support member supporting the valve element, and the tip ends of the leg portions elastically abut against the valve body. The interior wall stably supports the support member from the periphery of the support member toward the center.

However, in Patent Document 1, the leg portion of the anti-vibration spring collides directly with the refrigerant flowing into the valve chamber from the inlet port, so there is a possibility of turbulent flow in the high-pressure refrigerant introduced into the valve chamber. This point will be described using FIGS. 7 to 10 .

As shown in FIG. 7 , high-pressure refrigerant sent from a compressor (not shown) enters the inlet port 320 as indicated by arrow A, and is introduced into the valve chamber 324 through the inlet hole 320 a. Here, the conventional anti-vibration spring 300 is formed by an annular plate-shaped portion 301 and a plurality of leg portions 302. The plate-shaped portion 301 is sandwiched between the support member 400 of the valve element and the support member 400 is positioned toward the valve element. Between the biasing coil springs 344, the plurality of leg portions 302 are formed by bending radially from the plate portion 301 obliquely toward the center axis of the stem. And, the plurality of leg portions 302 extend to the lower side wall 324b of the valve chamber 324 on the lower side of the inlet hole 320a. Here, the legs 302 form various flow path shapes with respect to the inlet hole 320 a according to the angle at which the anti-vibration spring 300 is attached (rotation angle around the center point of the anti-vibration spring 300 ).

8 to 10 show shape examples of the inlet flow path formed by the inlet hole 320 a and the leg portion 302 viewed from the inlet port 320 side. FIG. 8 shows a case where the leg portion 302 is arranged in the vertical direction at the center of the inlet hole 320a to divide the opposing flow path 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 where the legs 302 are positioned on both sides of the inlet hole 320a to form a gate-shaped flow path. Since the leg portion 302 blocks a part of the inlet hole 320 a in various forms, and the inlet flow path has a corresponding shape, turbulent flow may occur depending on the orientation of the anti-vibration spring 300 . Refrigerant passage sound due to turbulent flow may cause abnormal noise due to bubble collapse of the bubble mixture. In addition, there is also a concern that the flow rate of the introduced refrigerant may decrease.

In this regard, Patent Document 2 discloses a technique in which the legs of the anti-vibration spring are bent in the radial direction around the center axis of the valve rod to shorten the length of the legs in the direction of the center axis. , If the anti-vibration spring is not inserted into the valve body when the anti-vibration spring is twisted, a load may be applied to the foot, especially the root, or the anti-vibration spring may be deformed.

Contents of the invention

Therefore, an object of the present invention is to provide an expansion valve including an anti-vibration spring that suppresses vibration of a valve body, prevents deformation of the anti-vibration spring, and reduces passing noise of refrigerant.

means to solve the problem

In order to solve the above-mentioned problems, a typical expansion valve of the present invention includes: a valve main body having an inlet hole through which the refrigerant flows into the valve chamber and a valve hole through which the refrigerant flows out from the valve chamber; , the valve core adjusts the amount of refrigerant flowing through the valve hole; the power element is installed on the valve main body and drives the valve core through the valve stem; the support component is for the The spool is supported; the coil spring presses the spool toward the valve closing direction via the support member; and the anti-vibration spring prevents the spool from vibrating. The vibrating spring has an annular base disposed between the supporting member and the coil spring, and a plurality of legs extending radially from the base, and each of the plurality of legs has The upper portion formed radially in the surface of the upper portion, the bent portion bent from the upper portion to the side of the coil spring, and the side portion extending downward from the bent portion, the plurality of leg portions are respectively connected to the valve chamber The part of the side wall surface of the valve hole that is closer to the valve hole side than the inlet hole is in contact with.

In one embodiment of the expansion valve of the present invention, the plurality of leg portions may have a connecting portion that connects adjacent leg portions on the same plane as the base portion.

Invention effect

The expansion valve of the present invention is configured as described above, so that the vibration of the valve body is suppressed, and the deformation of the anti-vibration spring can be prevented to reduce the passing sound of the refrigerant.

Description of drawings

Fig. 1 is a longitudinal sectional view showing a first embodiment of an expansion valve of the present invention.

Fig. 2 is a longitudinal sectional view of main parts of the expansion valve of the first embodiment.

Fig. 3 is a perspective view showing the anti-vibration spring of the first embodiment.

Fig. 4 is a plan view showing the anti-vibration spring of the first embodiment.

Fig. 5 is a side view showing the anti-vibration spring of the first embodiment.

Fig. 6 is a plan view showing an anti-vibration spring of a second embodiment.

Fig. 7 is a longitudinal sectional view showing an example of a conventional expansion valve.

FIG. 8 is a diagram showing an example of the shape of an inlet flow path of a conventional expansion valve.

9 is a diagram showing an example of the shape of an inlet flow path of a conventional expansion valve.

Fig. 10 is a diagram showing an example of the shape of an inlet flow path of a conventional expansion valve.

Detailed ways

<First embodiment>

Fig. 1 is a longitudinal sectional view showing a first embodiment of an expansion valve of the present invention. Fig. 2 is a longitudinal sectional view of main parts of the expansion valve of the first embodiment.

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

The valve main body 11 is made of, for example, an aluminum alloy, and can be obtained, for example, by extruding an aluminum alloy or the like with the X direction in FIG. 1 as an extrusion direction, and applying machining to this. The valve main body 11 has a power element mounting part 12 which is an internal thread formed on the upper surface and is screwed with the external thread 72a of the power element 70 to fix it, an inlet port 20 through which high-pressure refrigerant is introduced, and an inlet port through which a high-pressure refrigerant is introduced. The refrigerant outlet port 28 through which the inflowing refrigerant flows out, the refrigerant return passage 30, the hole 33 for installing the O-ring 36, the female thread 11a formed on the bottom surface of the valve body 11, and the valve body 11 It is installed in the mounting hole (or internal thread for mounting) 80 etc. of the evaporator which is not shown in figure, and other components.

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

The internal thread 11a is formed so as to open on the lower surface of the valve main body 11, and the insertion hole 11b is formed in the upper part of the internal thread 11a. The valve chamber 24 is formed inside the valve body 11 by closing the opening portion of the internal thread 11 a with the adjustment screw 120 . The valve chamber 24 has cylindrical side wall surfaces, an upper wall surface 24a above the upper end of the inlet hole 20a, and a lower wall surface 24b below the lower end of the inlet hole 20a. The upper wall surface 24a secures the length in the vertical direction required for the vibration-proof spring 140 to be described later to slide. In addition, the portion between the upper end of the insertion hole 11b and the inlet hole 20a may have a thickness sufficient for strength.

The inlet port 20 is formed to communicate with the valve chamber 24 from the side of the valve chamber 24 through an inlet hole 20 a smaller in diameter than the inlet port 20 . In addition, a narrow portion 28 a smaller in diameter than the outlet port 28 is provided deep in the outlet port 28 , and the narrow portion 28 a is arranged above the valve chamber 24 . The narrow portion 28 a communicates with the upper end portion of the valve chamber 24 via the valve hole 26 as an orifice. In addition, a valve seat 25 is formed on the valve chamber 24 side of the valve hole 26 . In the valve main body 11 , a through hole 29 is formed in the up-down direction (Y direction in FIG. 1 ) to communicate the return passage 30 with the narrow portion 28 a. Furthermore, the valve hole 26 , the through hole 29 , the opening 32 , and the valve chamber 24 are arranged so that their central axes are on the same straight line. The return passage 30 is formed above the outlet port 28 in the valve main body 11 , and is formed so as to penetrate the valve main body 11 in the lateral direction (X direction in FIG. 1 ). In addition, a hole portion 33 coaxial with the through hole 29 and having a larger inner diameter than the through hole 29 is formed on the lower side of the return passage 30 .

In addition, in FIG. 1 , the inlet port 20 and the outlet port 28 are opened on the left and right sides of the valve main body 11. Similarly, the return passage 30 is also formed to pass through the left and right sides of the valve main body 11, but these inlet ports, outlet ports and return passages The two openings of the expansion valve can be variously changed according to the design 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 can also be opened to the outside of the paper surface or the inside of the paper surface of FIG. Formed, likewise, the two openings of the return passage are also formed in an orthogonal manner).

The power element 70 includes, for example, an upper cover member 71 formed of stainless steel, a receiving member 72 having a through-hole 72b in the center, a diaphragm 73 sandwiched between the upper cover member 71 and the receiving member 72, and a The stopper member 90 and the like between the receiving member 72 and the like. In addition, the upper cover member 71 , the diaphragm 73 , and the receiving member 72 are overlapped and welded around their ends to integrate them. A pressure chamber 75 is formed between the upper cover member 71 and the diaphragm 73 , and the working gas is sealed in the pressure chamber 75 by the sealing plug 65 . The lower part of the receiving member 72 has a cylindrical shape and an external thread 72a is formed around it, and is screwed with the internal thread of the power element mounting part 12 (the internal thread opening to the upper surface of the valve body 11 ) via the gasket 35 , Thus, the power element 70 is mounted on the valve main body 11 .

The valve element 40 is a spherical member arranged to face the valve seat 25 , and is installed in the valve chamber 24 . The valve stem 60 is provided in the form of respectively inserting the valve hole 26 , the through hole 29 and the opening 32 of the valve body 11 , and the upper end of the valve stem 60 abuts against the receiving portion 92 provided on the lower side of the stopper member 90 of the power element 70 . The lower end thereof is configured to be in contact with the spool 40 . The O-ring 36 is attached to the hole portion 33 , and the stop member 37 attached to the upper portion is used to prevent 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 (the direction of the valve stem 60 ). The spool 40 is in close contact with the support member 100, but since the support member 100 is always biased toward the valve seat 25 and the valve stem 60 by the coil spring 44, the support member 100 may only be in contact with the spool 40. The support member 100 includes a main body portion 103 , an upper surface portion 101 , and a flange portion 102 . The upper surface of the cylindrical main body portion 103 is provided with a conical recess to form an upper surface portion 101 that supports the lower surface of the valve element 40 . Further, the supporting member 100 includes a flange portion 102 protruding toward the side surface (outer peripheral side) of the main body portion 103 , and the lower surface of the flange portion 102 has a structure for receiving the anti-vibration spring 140 and one end of the coil spring 44 . At this time, the outer diameter of the main body portion 103 on the lower side than the flange portion 102 is configured to be smaller than the inner diameter of the coil spring 44 so as to enter the inside of the coil spring 44 .

The coil spring 44 is provided between the lower surface of the flange part 102 provided on the support member 100 and the recessed part 125 formed on the adjustment screw 120 . The valve element 40 is urged toward the valve seat 25 via the support member 100 by the elastic force of the coil spring 44 . The anti-vibration spring 140 is provided between the lower surface of the flange part 102 and the coil spring 44, but the detail of this structure is mentioned later.

The adjustment screw 120 includes a main body portion 121 , a hexagonal hole 122 , an insertion portion 123 , a tip portion 124 , and a concave portion 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 . Moreover, the outer periphery of the main body part 121 becomes the external thread part 121a for screwing with the internal thread 11a opened to the lower surface of the valve main body 11. As shown in FIG. In addition, a concave portion 125 having an open upper portion and having a cylindrical space is provided on the upper portion of the adjusting screw 120 . The concave portion 125 is formed to a depth reaching the vicinity of the main body portion 121 . In addition, the inner diameter of the recessed portion 125 is slightly larger than the outer diameter of the coil spring 44 so that the coil spring 44 is stably arranged in the recessed portion 125 . In addition, a hexagonal hole 122 into which an unillustrated hexagonal wrench for turning the adjusting screw 120 is inserted is provided at a lower portion of the adjusting screw 120 (main body portion 121 ).

FIG. 3 is a perspective view showing the anti-vibration spring 140 of the first embodiment. FIG. 4 is a plan view showing the anti-vibration spring 140 of the first embodiment. Fig. 5 is a side view showing the anti-vibration spring of the first embodiment. The anti-vibration spring 140 includes a base portion 141 and a leg portion 142 . The anti-vibration spring 140 can be obtained by stamping elastic plate materials such as stainless steel and its alloys.

The base 141 is an annular plate-shaped member forming the upper portion of the anti-vibration spring 140, and has an attachment hole 141a in the center.

The leg part 142 extends from the outer peripheral side of the base part 141 in the direction perpendicular to the tangent to the circumferential direction, in other words, a plurality of leg parts extend radially. In the first embodiment, eight leg portions 142 of 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. In addition, 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 portion of the base of each leg portion 142 , a cutout 145 of a predetermined shape is ensured on the surface having the base portion 141 . In FIG. 4 the length C is the length of the upper portion 142a. The leg part 142 is provided with the upper part 142a, and the leg part 142 is formed from the center side of the base part 141 rather than the bending part on the same surface as the base part 141. As shown in FIG. In addition, in the vicinity of the connection part of the upper part 142a to the base part 141 (near the root of the leg part 142), the notch 145 formed between the side surfaces in the width direction of the adjacent upper part 142a is formed from the base side of the upper part 142a at the same distance. Curvatures are continuously connected to form an arc shape, whereby upper parts 142 a (leg parts 142 ) are smoothly connected. Of course, the notch 145 may be formed in a shape other than the arc shape by being connected with different curvatures from the base side of the upper portion 142a.

The bent portion 142b is formed by bending continuously outward from the upper portion 142a downward (coil spring 44 side). The bent portion 142b may also have a certain radius of curvature. The bent portion 142b is formed by bending (90-θ) degrees.

The side part 142c is continuously formed in a straight line from the bottom of the bent part 142b. The angle of the side portion 142c has θ degrees toward the lower outer side with respect to the up-down direction.

The protruding portion 142d is formed toward the outside near the lower end of the side portion 142c. For example, the protruding portion 142d may be formed by a part of a spherical surface such as a hemisphere or the like. The protrusion 142d is dimensioned in such a manner that when installed in the valve main body 11, it comes into elastic contact with the portion (upper wall surface 24a) above the opening of the inlet hole 20a, but even if the valve body 40 is at the lowest lowered position In this case, the protrusion 142d does not enter the opening of the inlet hole 20a.

As for the length in the vertical direction of the leg portion 142, 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 lowermost end within the range of the vertical movement of the anti-vibration spring 140, an appropriate length can be used. However, in order not to obstruct the flow of the refrigerant introduced from the inlet port 20, it is desirable that the lower end of the leg portion 142 does not reach the opening of the inlet hole 20a. In addition, in this embodiment, with regard to the width of each leg portion 142, the upper portion 142a, the bent portion 142b, and the side portion 142c are all formed with a fixed width, but this is not particularly limited in the present invention, and the width of the top end can be made In addition to narrowing the width or conversely widening it, it can be changed to a shape most suitable for suppressing the vibration of the spool. In addition, the thickness of the leg portion 142 (thickness of the anti-vibration spring 140 when the anti-vibration spring 140 is formed by pressing from a single elastic plate) is also adopted as a thickness suitable for suppressing the vibration of the spool.

In the anti-vibration spring 140, there is a gap D ( FIG. 4 ) for passage of refrigerant between adjacent leg portions 142 . In addition, the outer diameter of the anti-vibration spring 140 connected at the top end of the protrusion 142d is larger than the inner diameter of the upper wall surface 24a in the valve chamber 24, so that an elastic force acts on the upper wall surface of the valve chamber 24 when mounting. 24a presses the protrusion 142d. In addition, a size sufficient to arrange the coil spring 44 is ensured inside the leg portion 142 .

As shown in Figures 1 and 2, when installing the anti-vibration spring 140, at first, the installation hole 141a of the anti-vibration spring 140 is passed through the main body portion 103 of the support member 100 from the lower side, and the base portion 141 of the anti-vibration spring 140 is The upper surface is in contact with the lower surface of the flange portion 102 of the support member 100 . Next, the coil spring 44 is attached from the lower side of the anti-vibration spring 140 . At this time, the main body portion 103 of the support member 100 is arranged inside the coil spring 44 , and the upper surface of the coil spring 44 is in contact with the lower surface of the base portion 141 of the anti-vibration spring 140 . Accordingly, the anti-vibration spring 140 is installed in the valve chamber 24 .

In the expansion valve 10 to which the anti-vibration spring 140 is mounted, the base portion 141 of the anti-vibration spring 140 is biased from the lower side by the coil spring 44, and thus is clamped with a predetermined force and is attached to the flange portion 102 of the support member 100 and the Between the coil springs 44. Furthermore, the protrusion 142d of the anti-vibration spring 140 is pressed toward the upper wall surface 24a of the valve chamber 24 with a predetermined force by the elastic force of the leg portion 142 , and generates sliding resistance corresponding to the movement of the valve body 40 .

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 into the valve chamber 24 through the inlet hole 20a from the inlet port 20, and expands through the valve hole 26. And it is sent out to the evaporator (not shown) from the outlet port 28. In addition, the refrigerant sent from the evaporator enters from the left inlet of the return passage 30, passes through the right outlet, and returns 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 . And, the pressure of the working gas in the pressure working chamber 75 changes 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 under the influence of the movement of the diaphragm 73 deformed according to the fluctuation of the internal pressure in the pressure working chamber 75 . And, the movement of the stopper member 90 is transmitted to the valve element 40 via the valve stem 60, thereby controlling the flow rate of the expanded refrigerant.

When the valve body 40 moves in the opening and closing direction (vertical direction), the anti-vibration spring 140 acts together with the valve body 40 and the supporting member 100 . At this time, the anti-vibration spring 140 presses the upper wall surface 24a of the valve chamber 24 of the valve main body 11 with a predetermined force, so when the anti-vibration spring 140 slides, there is a gap between the protrusion 142d of the leg portion 142 and the upper wall surface 24a of the valve chamber 24. friction between them. Accordingly, the valve body 40 and the support member 100 do not respond sensitively in the vertical direction to the pressure fluctuation of the high-pressure refrigerant from the inlet port 20 , and vertical vibration can be prevented or reduced. In addition, the upper wall surface 24a of the valve chamber 24 is pressed from the anti-vibration spring 140 to the upper wall surface 24a of the valve chamber 24 at a plurality of places by the plurality of legs 142, so the valve body 40 and the support member 100 do not respond to the pressure fluctuation of the high-pressure refrigerant from the inlet port 20. It can easily move in the lateral direction against the pressing force, and exerts the effect of preventing lateral vibration. At the same time, the vertical movement of the valve body 40 and the supporting member 100 is guided.

In addition, the anti-vibration spring 140 is in contact with the upper wall surface 24a above the inlet hole 20a in the valve chamber 24, so the leg portion 142 does not fall into the inlet hole 20a, and the refrigerant flow rate and turbulent flow can be suppressed to make the refrigeration The passing sound of the agent decreases. In addition, the anti-vibration spring 140 is constituted by radially extending leg portions 142 , and thus can be easily installed in the valve body 11 simply by being inserted through an opening of the female thread 11 a formed at the bottom of the valve body 11 . In addition, since the anti-vibration spring 140 has a certain notch depth (notch 145 ) in the surface having the base portion 141 , the length of the leg portion 142 can be extended to be equal to or greater than the height of the anti-vibration spring. Therefore, the spring constant of the leg portion 142 can be reduced, the change in force with respect to the deformation of the leg portion 142 can be reduced, and more stable sliding resistance can be obtained. In addition, the calculation of the spring constant, that is, the design of the first anti-vibration spring 140 is facilitated by making the width of the leg portions 142 the same. In addition, the legs 142 are formed in a direction perpendicular to a tangent to the circumferential direction of the base 141 (radially), so that sliding resistance can be generated without applying a torsional force in the circumferential direction of the base 141 .

<Second Embodiment>

Fig. 6 is a plan view showing an anti-vibration spring of a second embodiment. The second embodiment is a structure in which the anti-vibration spring 140 of the first embodiment is replaced by the anti-vibration spring 240 . Other than that, it is the same as the structure shown in the first embodiment, so further description of the common parts will be omitted.

The anti-vibration spring 240 includes a base portion 241 and a leg portion 242 . The anti-vibration spring 240 can be obtained by stamping an elastic plate material such as stainless steel and its alloy.

The base part 241 is an annular plate-shaped member forming the upper part of the anti-vibration spring 240, and has the same mounting hole 141a as in the first embodiment in the center.

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

Here, the point of difference is that, in the first embodiment, there is an arc-shaped notch 145 , but in the second embodiment, it is a 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. Also, the length of the leg portion 242 of the second embodiment is longer by a corresponding amount. In addition, the outer circumference of the base 241 of the second embodiment is smaller than that of the base 141 of the first embodiment. In addition, the side surfaces in the width direction of adjacent upper portions 242a may be formed as small arc-shaped portions in consideration of strength and stress concentration.

In the second embodiment, the length of the anti-vibration spring 240 can be further extended by forming the substantially triangular cutout 245 . Therefore, the spring constant of the leg portion 242 can be further reduced, the change in force with respect to the deformation of the leg portion 242 can be further reduced, and more stable sliding resistance can be generated.

As mentioned above, although the 1st Example and the 2nd Example were shown as embodiment of this invention, this invention is not limited to the said Example, Various modification examples are included. For example, it is not limited to the form including all the structures (structures) provided in the above-mentioned embodiments. In addition, a part of the structure of the example may be deleted, or may be replaced with a structure of another example, or may be added to the structure of the example.

For example, in the embodiment described above, the legs 142 , 242 are shown to have eight legs 142 having the same length at equal angular intervals. If the number of the legs 142 and 242 is eight, the stability of movement and the sliding resistance can be ensured, and the balance of the gap between the legs can be ensured, but the present invention is not limited thereto. For example, there may be two or more legs, and they are not limited to the same length and equal angular intervals. In addition, even the structure in which the width of the leg part changes midway as shown in the above-mentioned embodiment can be adopted.

In addition, the power element 70 shown in the above-mentioned embodiment shows installation based on a thread, but other than that, the following structure is also possible: a cylindrical part formed on the upper part of the valve main body is provided, and the power element 70 is inserted into this The inner side of the cylindrical part is riveted to the inner side of the cylindrical part to install the power element 70 .

Symbol Description

10 expansion valve

11 valve body

20 entry ports

20a entrance hole

24 valve chamber

24a upper wall

25 seat

26 valve holes

28 egress ports

30 return access

40 spool

44 coil spring

60 stem

70 power components

100 supporting parts

120 adjusting screw

140, 240 anti-vibration spring

141, 241 base

142, 242 feet

Claims (9)

1. An expansion valve, characterized in that, possesses: a valve body having an inlet hole for refrigerant to flow into the valve chamber and a valve hole for the refrigerant to flow out of the valve chamber; a spool, the spool adjusts the amount of refrigerant flowing through the valve hole; a power element, the power element is installed on the valve body and drives the valve core through the valve stem; a supporting part, the supporting part supports the valve core; a coil spring that presses the valve core in a valve closing direction via the support member; and anti-vibration spring, the anti-vibration spring prevents the vibration of the spool, The anti-vibration spring has an annular base disposed between the support member and the coil spring, and a plurality of legs extending radially from the base, Each of the plurality of leg portions has an upper portion formed on the same plane as the base portion and extending linearly, a bent portion bent from the upper portion toward the coil spring side, and a downward direction from the bent portion. The side extending linearly, One end of the upper portion on the side of the bent portion is disposed outside the coil spring in a direction in which the upper portion extends, The plurality of upper portions of the plurality of leg portions are formed in a radially extending shape, Each of the plurality of leg portions is in contact with a portion of a side wall surface of the valve chamber that is closer to the valve hole than the inlet hole. 2. The expansion valve of claim 1, wherein: In each of the plurality of leg portions, widths of the upper portion, the bent portion, and the side portion are constant. 3. The expansion valve of claim 1, wherein: The vertical length of each of the plurality of legs is at the lowermost end within the vertical movement range of the anti-vibration spring, and the length of the legs does not reach the inlet hole. 4. The expansion valve of claim 1, wherein: Each of the plurality of leg portions further has a protrusion provided near a lower end of the side portion, The protrusion is in contact with a portion of the side wall surface of the valve chamber that is closer to the valve hole than the inlet hole. 5. The expansion valve of claim 4, wherein: The protrusion is in contact with a portion of the side wall surface of the valve chamber that is closer to the valve hole than the inlet hole at a lowermost position within a vertically moving range of the anti-vibration spring. 6. The expansion valve of claim 1, wherein: The upper portion is delimited by a cutout formed between the plurality of feet in the same plane as the base portion. 7. The expansion valve of claim 6, wherein: The cutout is arc-shaped or roughly triangular-shaped. 8. The expansion valve of claim 1, wherein: The plurality of leg portions further have a connecting portion that connects adjacent leg portions to each other on the same plane as the base portion. 9. An expansion valve according to any one of claims 1 to 8, characterized in that, The support member has a main body disposed inside the coil spring, In the direction along the central axis of the coil spring, the end of the foot portion on the inlet hole side and the end portion of the body portion on the inlet hole side are located at the inlet hole side. At least one of the legs is disposed on the side opposite to the inlet hole via the coil spring in the vicinity of the edge on the side of the valve hole.

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