JP6943379B2 - Expansion valve - Google Patents

Description

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

Conventionally, a temperature expansion valve with a built-in temperature sensing mechanism has been used for a refrigerating cycle used in an air conditioner or the like mounted on an automobile to adjust the amount of refrigerant passing through according to the temperature. The valve body of such an expansion valve has an inlet port into which a high-pressure refrigerant is introduced and a valve chamber that communicates with the inlet port, and the top of the valve body is equipped with a valve body drive mechanism called a power element. Will be done.

The spherical valve body 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 the adjusting screw attached to the valve body and the support member. Then, the valve body is operated by a valve rod driven by a power element to control the opening degree of the throttle passage between the valve body and the valve seat. Further, the refrigerant that has passed through the valve hole is sent from the outlet port to the evaporator side.

Here, the high-pressure refrigerant sent to the inlet port of the expansion valve may cause pressure fluctuation (pulsation) due to the operation of the compressor, which may cause the valve body to vibrate and generate an abnormal noise.

In order to prevent such vibration, a configuration in which a vibration-proof spring for suppressing vibration of the valve body is provided has been conventionally proposed (see, for example, Patent Documents 1 and 2).

The expansion valve described in Patent Document 1 elastically holds a support member provided in the valve chamber for supporting the spherical valve body in the valve chamber by using a plurality of elastic bodies, whereby the valve body is outside the valve body. Since it is elastically pressed and supported toward the valve seat side (that is, in a direction substantially orthogonal to the vertical direction, which is the movement direction of the valve body), vibration of the valve body can be effectively suppressed. It is possible.

Further, the expansion valve described in Patent Document 2 has a valve body in which the valve stem is inserted in order to give a desired sliding resistance to the valve stem for transmitting the operation of the power element to the spherical valve body. An anti-vibration spring is placed in the pores, and the tip of this spring is brought into contact with the valve stem. With such a configuration, unnecessary minute vibrations in the vertical direction of the valve stem can be suppressed, and this also causes the valve. It is possible to effectively suppress the vibration of the body.

Japanese Unexamined Patent Publication No. 2005-1506046 Japanese Unexamined Patent Publication No. 2006-3056

Although the structure of the conventional expansion valve has a certain anti-vibration effect, it also has the following problems. That is, in order to achieve both the miniaturization and weight reduction of the refrigeration cycle arranged inside an automobile or the like and its high functionality and efficiency, the miniaturization of various devices including the expansion valve arranged in the refrigeration cycle is also required. Higher performance and higher performance are required.
However, various types of research and development have been continuously carried out on expansion valves, and the reality is that their miniaturization is almost reaching its limit.

In such an expansion valve, if a plurality of legs of the anti-vibration spring in the valve chamber are in contact with the side wall of the valve chamber as disclosed in Patent Document 1, the shape and material of the anti-vibration spring, etc. Even if various adjustments are made, sufficient vibration suppression of the valve body cannot be obtained depending on the degree of pressure fluctuation of the high-pressure refrigerant introduced into the inlet port of the expansion valve (that is, the pressure difference and the degree of the fluctuation cycle). was there.

The same applies to the structure in which the valve stem is brought into contact with the ring anti-vibration spring as disclosed in Patent Document 2.

Therefore, an object of the present invention is to provide an expansion valve capable of effectively suppressing vibration of a valve body due to the influence of a high-pressure refrigerant.

In order to solve the above problems, one of the typical expansion valves of the present invention includes a valve body having an inlet hole for the refrigerant to flow into the valve chamber, a valve hole for the refrigerant to flow out from the valve chamber, and the valve body. A valve body that adjusts the amount of refrigerant flowing through the valve hole, a support member that supports the valve body, a coil spring that presses the valve body in the valve closing direction via the support member, and a valve body attached to the valve body. A power element for driving the valve body via a valve rod and an anti-vibration spring for preventing vibration of the valve body are provided, and the support member includes a main body portion fitted into the coil spring to prevent the valve body from vibrating. The oscillating spring has an annular base arranged between the support member and the coil spring, and a plurality of legs extending radially from the base, and each of the plurality of legs has the base. It is provided with an upper portion formed radially on the same surface as the above, a bent portion that bends from the upper portion to the coil spring side, and a side portion that extends downward from the bent portion, and the width of the upper portion and the side portion is substantially reduced. Equally, in the direction along the central axis of the coil spring, the end on the inlet side of the leg and the end on the inlet side of the main body of the support member are on the valve hole side of the inlet. Located near the edge.

Since the expansion valve according to the present invention is configured as described above, vibration of the valve body due to the influence of the high-pressure refrigerant can be effectively suppressed.

It is a vertical sectional view which shows the 1st Example of the expansion valve by this invention. It is a vertical cross-sectional view of the main part of the expansion valve of 1st Example. It is a perspective view which shows the 1st vibration isolation spring of 1st Example. It is a top view which shows the 1st vibration isolation spring of 1st Example. It is a side view which shows the 1st vibration isolation spring of 1st Example. It is a perspective view which shows the 2nd vibration isolation spring of 1st Example. It is a partial explanatory view (a) and the main part side view (b) of the 2nd vibration isolation spring of 1st Example. The plan view which shows the state which attached the valve stem to the 2nd vibration isolation spring of 1st Example. It is a top view which shows the 1st vibration isolation spring of 2nd Example. It is a vertical sectional view which shows the 3rd Example of the expansion valve by this invention. It is a perspective view which shows the 2nd vibration isolation spring of 3rd Example. It is a vertical sectional view which shows 4th Example of the expansion valve by this invention.

<First Example>
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 a 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, a support member 100, a first anti-vibration spring 140, a coil spring 44, an adjusting screw 120, and a second anti-vibration. It is equipped with a spring 500.

The valve body 11 is made of, for example, an aluminum alloy, and can be obtained by, for example, extruding an aluminum alloy or the like with the X direction in FIG. 1 as the extrusion direction and machining the valve body 11. The valve body 11 has a power element mounting portion 12, which is a female screw formed on the upper surface of the power element 70 and screwed onto the male screw 72a of the power element 70 to fix the power element 70, an inlet port 20 into which a high-pressure refrigerant is introduced, and an inlet port. The outlet port 28 of the refrigerant from which the refrigerant flowing in from 20 flows out, the return passage 30 of the refrigerant, the hole 33 to which the second anti-vibration spring 500 is attached, the female screw 11a formed on the bottom surface of the valve body 11, and the valve. It has a mounting hole (or mounting female screw) 80 or the like for mounting the main body 11 on an evaporator or other parts (not shown).

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 a female screw on the inner wall surface thereof. An opening 32 leading to (communication with) the return passage 30 is formed in 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 orthogonal to the passing 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 portion of the female screw 11a with the adjusting screw 120. The valve chamber 24 has a cylindrical side wall surface, and the upper wall surface 24a is above the upper end of the inlet hole 20a and the lower wall surface 24b is below the lower end of the inlet hole 20a. The upper wall surface 24a has a vertical length required for the first anti-vibration spring 140, which will be described later, to slide. Further, the portion between the upper end of the insertion hole 11b and the inlet hole 20a may have a thickness required 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 diameter smaller than that of the inlet port 20. Further, a narrowed portion 28a having a diameter smaller than that of the outlet port 28 is provided at the back of the outlet port 28, and the narrowed portion 28a is arranged above the valve chamber 24. The narrowed portion 28a communicates with the upper end portion of the valve chamber 24 via a 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 communicate 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 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 body 11 and is formed so as to penetrate the valve body 11 in the lateral direction (X direction in FIG. 1). Further, a hole portion 33 coaxial with the through hole 29 and having an inner diameter larger than that of the through hole 29 is formed on the lower side of the return passage 30.

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 similarly, the return passage 30 is also formed so as to penetrate the left and right 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 opening of the exit port 28 and the return passage 30 is opened on the front side or the back side of the paper surface in FIG. 1 (that is, the inlet port and the exit port are orthogonal to each other when viewed from the center line of the valve stem 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 stainless steel or the like, a receiving member 72 having a through hole 72b at the center thereof, a diaphragm 73 sandwiched between the upper lid member 71 and the receiving member 72, and the diaphragm. It is composed of a stopper member 90 or the like arranged between the 73 and the receiving member 72. Then, the upper lid member 71, the diaphragm 73, and the receiving member 72 are integrated by peripheral welding at the overlapped end portion. A pressure actuating chamber 75 is formed between the upper lid member 71 and the diaphragm 73, and after the working gas is sealed in the pressure actuating chamber 75, it is sealed with a sealing plug 65. The lower part of the receiving member 72 is cylindrical, and a male screw 72a is formed around it, and by screwing with the female screw (the female screw opened on the upper surface of the valve body 11) of the power element mounting portion 12 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 in the valve chamber 24. The valve stem 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 stem 60 is below the stopper member 90 of the power element 70. The receiving portion 92 is provided, and the lower end thereof is arranged so as to be in contact with the valve body 40. The second anti-vibration spring 500 is arranged in the hole 33 and elastically supports the valve stem 60. Details of the second anti-vibration spring 500 will be described later.

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 stem 60). The valve body 40 is fixed to the support member 100, but since the support member 100 is always urged in the direction of the valve seat 25 and the valve stem 60 by the coil spring 44, the support member 100 comes into contact with the valve body 40. It may be a configuration of only. 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 columnar main body 103 is an upper surface 101 having a conical recess to support the lower surface of the valve body 40. Further, the support member 100 includes a flange portion 102 protruding from the main body portion 103 to the side surface (outer peripheral side), and the lower surface of the flange portion 102 has a structure in which one end of the first anti-vibration spring 140 and the coil spring 44 is received. ing. At this time, the outer diameter of the main body 103 below the flange 102 is smaller than the inner diameter of the coil spring 44, and is 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 in the adjusting screw 120. Due to the elastic force of the coil spring 44, the valve body 40 is urged toward the valve seat 25 via the support member 100. A first anti-vibration spring 140 is installed between the lower surface of the flange portion 102 and the coil spring 44, and the details of this configuration will be described later.

The adjusting screw 120 includes a main body portion 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 an outer diameter smaller than that of the main body portion 121, and the tip portion 124 is provided on the upper portion of the insertion portion 123 with an outer diameter smaller than that of the insertion portion 123. There is. Further, the outer circumference of the main body portion 121 is a male screw portion 121a for screwing into the female screw 11a opening on the lower surface of the valve main body 11. Further, a recess 125 is provided in the upper portion of the adjusting screw 120 so that the upper portion is open and has a columnar space. The recess 125 is formed to a depth that reaches 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 is stably arranged in the recess 125. Further, a hexagonal hole 122 for inserting a hexagon wrench (not shown) for turning the adjusting screw 120 is provided in the lower portion of the adjusting screw 120 (main body portion 121).

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

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

A plurality of leg portions 142 extend from the outer peripheral side of the base portion 141 in the direction perpendicular to the tangent line in the circumferential direction, in other words, radially. In the first embodiment, eight legs 142 having the same length are provided at equal intervals. The leg portion 142 is composed of an upper portion 142a, a bent portion 142b, a side portion 142c, and a protruding portion 142d. Further, 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 base portion of each leg portion 142, a notch 145 having a predetermined shape is secured on the surface having the base portion 141. In FIG. 4, the length C is the length of the upper portion 142a. When the leg portion 142 includes the upper portion 142a, the leg portion 142 is formed on the same surface as the base portion 141 from the central side of the base portion 141 rather than the bent portion. Further, in the vicinity of the connection portion of the upper portion 142a to the base portion 141 (near the base of the leg portion 142), the notch 145 formed between the lateral side surfaces of the adjacent upper portions 142a has the same curvature from the root side surface of the upper portion 142a. The upper parts 142a (legs 142) are smoothly connected to each other by forming an arc shape by connecting them continuously with. Of course, the notch 145 may be formed in a shape other than the arc shape by connecting the notch 145 from the root side surface of the upper portion 142a with a different curvature.

The bent portion 142b is formed so as to be continuously bent outward from the upper portion 142a toward the lower side (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 formed continuously and linearly below the bent portion 142b. The angle of the side portion 142c has a θ degree toward the lower outer side with respect to the vertical direction.

The protrusion 142d is formed in the vicinity of the lower end of the side portion 142c toward the outside. For example, the protrusion 142d can be formed by a spherical surface such as a hemisphere, a part of another curved surface, or the like. When the protrusion 142d is mounted inside the valve body 11, it 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 lowermost position. The dimensions of each part are set so that the protrusion 142d does not enter the opening of the inlet hole 20a.

The vertical length of the leg portion 142 is 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 lowermost end within the range of vertical movement of the first anti-vibration spring 140. Although it can be set, the lower end of the leg portion 142 is formed in the inlet hole 20a so as not to obstruct the flow of the refrigerant introduced from the inlet port 20 and to prevent a decrease in flow rate or turbulence due to the flow rate. It is desirable not to reach the opening. Further, in the present embodiment, the width of each leg portion 142 is formed to have a constant width in each of the upper portion 142a, the bent portion 142b, and the side portion 142c, but the present invention is particularly limited to that. It is possible to narrow the width of the tip, widen it, or change the shape to be most suitable for suppressing the vibration of the valve body. Further, the thickness of the leg portion 142 (the thickness of the first anti-vibration spring 140 when the first anti-vibration spring 140 is formed by pressing from one elastic plate material) is also a thickness suitable for suppressing the vibration of the valve body. Is adopted.

The first anti-vibration spring 140 has a gap D (FIG. 4) for the refrigerant to pass between the adjacent legs 142. Further, the outer diameter of the first anti-vibration 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 an elastic force acts when the first anti-vibration spring 140 is attached to the valve chamber 24. The protrusion 142d presses against the upper 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 first anti-vibration spring 140, first, the first anti-vibration spring 140 is first passed through the main body 103 of the support member 100 from below through the mounting hole 141a of the first anti-vibration spring 140. The upper surface of the base portion 141 of the oscillating spring 140 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 the lower side of the first anti-vibration 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 comes into contact with the lower surface of the base 141 of the first anti-vibration spring 140. As a result, the first anti-vibration spring 140 is installed in the valve chamber 24.

In the expansion valve 10 to which the first anti-vibration spring 140 is attached, since the base 141 of the first anti-vibration spring 140 is urged by the coil spring 44 from below, it is between the flange portion 102 of the support member 100 and the coil spring 44. It is attached by being sandwiched by a predetermined force. Then, in the first anti-vibration spring 140, the protrusion 142d is pushed by the elastic force of the leg 142 toward the upper wall surface 24a of the valve chamber 24 with a predetermined force, and the sliding resistance is increased according to the movement of the valve body 40. Occurs.

FIG. 6 is a perspective view showing the second anti-vibration spring 500 of the first embodiment. FIG. 7 is a front view (a) of a deployment main part and a cross-sectional view (b) of the main part of the second vibration-proof spring of the first embodiment. FIG. 8 is a cross-sectional view showing a state in which the valve stem is attached to the second anti-vibration spring of the first embodiment. The second anti-vibration spring 500 bends a plate-shaped member into a cylindrical shape as shown in FIG. 6, and has a first elastic piece 520, a second elastic piece 530, and a third elastic piece 540 inward. It is constructed by folding.

The first elastic piece 520, the second elastic piece 530, and the third elastic piece 540 are bent inward, but the first convex contact portion 522, the second convex contact portion 532, and the third elastic piece 520. The convex contact portion 542 is designed so that the circumference is divided into three equal parts. The diameter of the circle connecting the tops of the first convex contact portion 522, the second convex contact portion 532, and the third convex contact portion 542 is smaller than the diameter dimension of the valve stem 60. Is formed in.

The second anti-vibration spring 500 can be formed from an elongated elastic metal plate by press working.
One end of the elastic metal plate in the longitudinal direction has a tongue piece 512, and the other end has a tongue piece receiving portion 514 that receives the tongue piece 512 when the elastic metal plate is curved into a cylindrical shape. It is formed. The convex portion 516 is used when the elastic metal plate is curved into a cylindrical shape.

FIG. 7 is a partial explanatory view (a) and a side view (b) of a main part showing a state before bending of the first elastic piece 520 of the second anti-vibration spring 500. The second anti-vibration spring 500 punches out a U-shaped first notch 528 from a strip-shaped metal plate 500a having elasticity, thereby forming a first elastic piece 520 and at the tip thereof. A first convex contact portion 522, which is a hemispherical spherical portion, is formed. Similarly, the second elastic piece 530 and the third elastic piece 540 form the second notch portion 538 and the third notch portion 548 to form the second elastic piece 530 and the third elastic piece 540. A second convex contact portion 532 and a third convex contact portion 542, which are hemispherical spherical portions, are formed at the tip thereof.
Then, the roots of the first to third elastic pieces 520, 530, and 540 are bent from one direction, and then, as shown in FIG. 6, the first to third convex contact portions 522, 532, and 542 are formed. The first to third elastic pieces 520, 530, and 540 are bent from the root so as to face inward.

FIG. 8 is a plan view showing a state in which the valve rod 60 is attached to the second anti-vibration spring 500 of the first embodiment. The valve rod 60 is supported and supported by contacting and supporting the convex contact portions formed at the tips of the three elastic pieces at three points around the valve rod 60 so as to contact the side peripheral surfaces of the valve rod 60 at equal intervals. NS. The number of elastic pieces can be set to an appropriate number of two or more.

Next, the action 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 from the inlet port 20 through the inlet hole 20a, and flows into the valve chamber 24. It is expanded through 26 and delivered from the outlet port 28 to an evaporator (not shown). Further, the refrigerant sent out from the evaporator enters from the left inlet of the return passage 30 and passes through to the right outlet, and returns to the compressor. At this time, a part of the refrigerant passing through the return passage 30 flows into the lower part 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 part 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 fluctuation of the internal pressure in the pressure operating 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 first anti-vibration spring 140 behaves together with the valve body 40 and the support member 100. At this time, since the first anti-vibration spring 140 presses the upper wall surface 24a of the valve chamber 24 of the valve body 11 with a predetermined force, when the first anti-vibration spring 140 slides, the protruding portion of the leg portion 242 A frictional force is generated between the 142d and the upper wall surface 24a of the valve chamber 24. As a result, the valve body 40 and the support member 100 do not react sensitively to the pressure fluctuation of the high-pressure refrigerant from the inlet port 20 in the vertical direction, and vibration in the vertical direction can be prevented or reduced. Further, since the first anti-vibration spring 140 presses the upper wall surface 24a of the valve chamber 24 at a plurality of locations by the plurality of legs 142, the valve body 40 responds to the pressure fluctuation of the high-pressure refrigerant from the inlet port 20. The support member 100 does not easily move laterally against the pressing force, and has an effect of preventing lateral vibration. At the same time, it guides the vertical movement of the valve body 40 and the support member 100.

Further, since the first anti-vibration spring 140 is in contact with the upper wall surface 24a above the inlet hole 20a in the valve chamber 24, the leg portion 142 does not come into contact with the inlet hole 20a, and a refrigerant flow rate and turbulent flow are generated. Can be suppressed and the passing noise of the refrigerant can be reduced. Further, since the first anti-vibration spring 140 is composed of the legs 142 extending radially, it can be easily inserted into the valve body 11 simply by inserting it through the opening of the female screw 11a formed at the bottom of the valve body 11. Can be installed. Further, since the first anti-vibration spring 140 has a constant notch depth (notch 145) on the surface having the base portion 141, the length of the leg portion 142 can be made longer than the height of the anti-vibration spring. .. Therefore, the spring constant of the leg portion 142 can be reduced, the change in the force with respect to the deformation of the leg portion 142 can be reduced, and a 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, by forming the leg portion 142 in the direction perpendicular to the tangent line in the circumferential direction of the base portion 141 (radially), sliding resistance is generated without applying a twisting force in the circumferential direction of the base portion 141. Can be done.

Further, in this embodiment, in addition to the first anti-vibration spring 140, a second anti-vibration spring 500 that elastically supports the valve rod 60 is arranged, and the second anti-vibration spring 500 is the valve rod 60. It is configured to further impart a predetermined sliding resistance in the driving direction of the. That is, even when the vibration of the valve body 40 cannot be completely suppressed by the first anti-vibration spring 140 alone, it is possible to effectively suppress the vibration of the valve body 40 by arranging the second anti-vibration spring 500. Is.

<Second Example>
FIG. 9 is a top view showing the first anti-vibration spring of the second embodiment. The second embodiment has a configuration in which the first anti-vibration spring 140 of the first embodiment is replaced with the first anti-vibration spring 240, and other than that, it is the same as that shown in the first embodiment, and is therefore common. The part is omitted from the explanation again.

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

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

A plurality of leg portions 242 extend in the direction perpendicular to the tangent line in the circumferential direction, that is, radially from the outer peripheral side of the base portion 241. In the second embodiment, eight legs 242 are provided at equal intervals. The leg portion 242 is composed of 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 in the first embodiment.

Here, the first embodiment has an arc-shaped notch 145, but the second embodiment is different in that it has 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. Then, the length of the leg portion 242 of the second embodiment is increased by that amount. Further, the outer circumference of the base portion 241 of the second embodiment is smaller than the outer circumference of the base portion 141 of the first embodiment. The side surfaces of the adjacent upper portions 242a in the width direction may form a small arcuate portion in consideration of strength and stress concentration.

In the second embodiment, the length of the first anti-vibration spring 240 can be further increased by forming a substantially triangular notch 245. Therefore, the spring constant of the leg portion 242 can be made smaller, the change in the force with respect to the deformation of the leg portion 242 can be made smaller, and the sliding resistance can be made more stable.

<Third Example>
FIG. 10 is a vertical cross-sectional view showing a third embodiment of the expansion valve according to the present invention. FIG. 11 is a perspective view showing the second anti-vibration spring of the third embodiment. The third embodiment has a configuration in which the second anti-vibration spring 500 (three elastic pieces, one column) of the first embodiment is replaced with the second anti-vibration spring 600 (three elastic pieces, two columns). Other than that, it is the same as that shown in the first embodiment, so the common parts are omitted again.

The second anti-vibration spring 600 can be formed from an elongated elastic metal plate by press working. One end of the elastic metal plate in the longitudinal direction has a tongue piece 612, and the other end has a tongue piece receiving portion 614 that receives the tongue piece 612 when the elastic metal plate is curved into a cylindrical shape. It is formed. The convex portion 616 is used when the elastic metal plate is curved into a cylindrical shape.

At the tip of each elastic piece (620, 624, 630, 634, 640, 644), each convex contact portion (622, 626, 632, 636, 642, 646) which is a hemispherical spherical portion is formed. Notches (628, 638, 648) are formed in the longitudinal direction. Then, each elastic piece (620, 624, 630, 634, 640, 644) is bent inward.

In the third embodiment, a total of six elastic pieces (620, 624, 630, 634, 640, 644) are supported more firmly and stably by the spring force, and in addition to the anti-vibration action by the first anti-vibration spring. It is possible to exert a more effective anti-vibration effect.

In the above-described embodiment, an example in which three elastic pieces are formed in two columns is shown, but if a plurality of elastic pieces in each stage are arranged at equal intervals on the side peripheral surface of the valve stem 60, The number of elastic pieces can be selected from two or more as appropriate. Further, it may be a multi-column set of 3 or more columns.

<Fourth Example>
FIG. 12 is a vertical cross-sectional view showing a fourth embodiment of the expansion valve according to the present invention. The fourth embodiment has a configuration in which the first anti-vibration spring 140 of the first embodiment is replaced with the first anti-vibration spring 740, and other than that, it is the same as that shown in FIG. 1 of the first embodiment. , The common part is omitted from the explanation again.

Like the first anti-vibration spring 140, the first anti-vibration spring 740 has a base and eight legs having the same length, but the legs are longer than the first anti-vibration spring 140. That is, the leg of the first anti-vibration spring 140 is in contact with the upper wall surface 24a above the inlet hole 20a in the valve chamber 24, while the leg of the first anti-vibration spring 740 is in contact with the lower wall surface 24b. .. Then, the protrusion of the first anti-vibration spring 740 is pushed by the elastic force of the leg toward the lower wall surface 24b of the valve chamber 24 with a constant force, and the sliding resistance is increased according to the movement of the valve body 40. appear.

The vertical length of the lower wall surface 24b is the length required for the strength between the upper portion of the insertion hole 11b and the inlet hole 20a, and the vertical length required for the first anti-vibration spring 740 to slide. It suffices if the length in the direction is secured.

In the above-described embodiment, an example is shown in which all eight legs of the first anti-vibration spring 740 are in contact with the lower wall surface 24b, but the lengths of the legs alternate between long and short. There may be. That is, long ones in contact with the lower wall surface 24b and short ones in contact with the upper wall surface 24a may alternate, for example.

As described above, the first embodiment, the second embodiment, the third embodiment, and the fourth embodiment have been shown with respect to the embodiment of the present invention, but the present invention is not limited to the above-described embodiment. , Various variants are included. For example, the present invention is not limited to the one having all the configurations (structures) provided in the above-described embodiment. It is also possible to delete a part of the configuration of one embodiment, replace it with the configuration of another embodiment, or add the configuration of another embodiment to the configuration of one embodiment.

For example, in the above embodiment, the legs 142 and 242 show that eight legs 142 of the same length are provided at equal intervals. If the number of legs 142 and 242 is 8, stability of behavior and sliding resistance can be ensured, and the balance of the gap between the legs can be maintained, but the present invention is not limited to this. For example, the number of legs may be two or more, and the legs may not be limited to the same length and equiangular spacing. Further, even if the width of the leg portion shown in the above embodiment changes in the middle, it can be adopted.

Further, the power element 70 shown in the above embodiment is shown to be attached by a screw, but 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 the 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 screws 140, 240 , 740 1st anti-vibration spring 141, 241 Base 142, 242 Leg 500, 600 2nd anti-vibration spring

Claims (2)

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 that adjusts the amount of refrigerant flowing through the valve hole,
A support member that supports the valve body and
A coil spring that presses the valve body in the valve closing direction via the support member, and
A power element attached to the valve body and driving the valve body via a valve stem,
A vibration-proof spring for preventing vibration of the valve body is provided.
The support member includes a main body portion that fits into the coil spring.
The anti-vibration spring has an annular base arranged between the support member and the coil spring, and a plurality of legs extending radially from the base.
Each of the plurality of legs includes an upper portion radially formed on the same surface as the base portion, a bent portion that bends from the upper portion to the coil spring side, and a side portion that extends downward from the bent portion. , The width of the upper part and the width of the side part are almost equal,
In the direction along the central axis of the coil spring, the end on the inlet side of the leg and the end on the inlet side of the main body of the support member are the side edges of the valve hole of the inlet. Expansion valve located in the vicinity. At least one of the legs is arranged on the side opposite to the inlet hole with the coil spring in between.
The expansion valve according to claim 1.

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