JP2013142506A - Expansion valve and vibrationproof spring - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a simple and low-cost vibrationproof spring suitable for preventing the vibration of a working part of an expansion valve.SOLUTION: An expansion valve 1 of a certain embodiment includes a first passage 13 that penetrates a body 2 and has an intake port of a refrigerant at one end and a discharge port of the refrigerant at the other end, a valve hole 16 formed at an intermediate part of the first passage 13, a valve disc 18 to open and close the valve hole 16, a power element 3 to generate a driving force to actuate the valve disc 18, a shaft 33 that is supported by the body 2 and transmits the driving force of the power element 3 to the valve disc 18, and the vibrationproof spring 50 that is installed between the body 2 and the shaft 33 and energizes the shaft 33 to give sliding resistance. The vibrationproof spring 50 is formed by bending an elastic plate strip at a plurality of locations in the longitudinal direction thereof.

Description

  The present invention relates to an expansion valve, and more particularly to a structure of a vibration isolation spring suitable for vibration isolation of an operation portion of the expansion valve.

  The refrigeration cycle of an automotive air conditioner generally includes a compressor that compresses the circulating refrigerant, a condenser that condenses the compressed refrigerant, a receiver that separates the condensed refrigerant into gas and liquid, and the separated liquid refrigerant is squeezed and expanded. There are provided an expansion valve that is sent in the form of a mist, and an evaporator that evaporates the mist-like refrigerant and cools the air in the passenger compartment by the latent heat of evaporation.

  The expansion valve controls the flow rate of the refrigerant sent to the evaporator by sensing the temperature and pressure of the refrigerant on the outlet side of the evaporator and opening and closing the valve so that the refrigerant derived from the evaporator has a predetermined degree of superheat. A temperature expansion valve is used. In the body of the expansion valve, there are formed a first passage through which the refrigerant from the receiver to the evaporator passes and a second passage through which the refrigerant returned from the evaporator passes and is led to the compressor. A valve hole is formed in an intermediate portion of the first passage, and a valve body that adjusts the flow rate of the refrigerant toward the evaporator by being attached to and detached from the valve hole is disposed. A power element that senses the temperature and pressure of the refrigerant flowing through the second passage and controls the opening of the valve portion is provided at the end of the body. The driving force of the power element is transmitted to the valve body through a long shaft. The shaft extends across the second passage so as to reach the first passage. The shaft slides in an insertion hole provided in a partition portion that divides the first passage and the second passage in the body. It is supported movably.

  By the way, in such an expansion valve, pressure fluctuation may occur on the upstream side of the valve portion into which the high-temperature refrigerant is introduced, and if left untreated, the valve body may vibrate and generate noise. Therefore, in many cases, a method of stabilizing the operation of the valve body by applying an urging force by a spring to the shaft from the side so that the valve body does not respond sensitively to the pressure fluctuation. For example, there exists a thing which cuts out a plate-shaped body inside from several places of the annular part of a support ring, and uses it as a vibration-proof spring (for example, refer patent document 1). Moreover, there exists what forms a vibration-proof spring by bending the wire for springs (for example, refer patent document 2). Further, there is a type in which a vibration-proof spring is formed by bending a plate material punched radially by press working (see, for example, Patent Document 3).

Japanese Unexamined Patent Publication No. 2004-293779 (FIG. 2 etc.) JP-A-8-145505 (FIG. 6 etc.) Japanese Patent Laid-Open No. 2008-14628 (FIGS. 3, 4, etc.)

  However, since the support ring described in Patent Document 1 is configured to cut out the plate-like body from the annular portion, the width of the annular portion must be made larger than the width of the plate-like body. For this reason, if the width of the plate-like body is increased in order to increase the sliding load to be applied to the shaft, the entire support ring becomes larger, which may cause a problem in space. Moreover, since the anti-vibration spring of patent document 2 is formed by bending a wire, its rigidity is small and it is easy to bend in the axial direction of a shaft. For this reason, it is difficult to give a sufficient sliding load to the shaft. Furthermore, the vibration-proof spring described in Patent Document 3 has a problem in that since the plate material used as the material of the vibration-proof spring is formed radially, the yield of the material when cutting it from a larger plate material is low and the material cost increases. There is.

  The present invention has been made in view of such problems, and it is an object of the present invention to provide a vibration isolation spring suitable for vibration isolation of an operating portion of an expansion valve in a simple and low cost manner.

  In order to solve the above-described problem, an aspect of the present invention provides an expansion valve that allows a refrigerant introduced from an upstream side of a refrigeration cycle to be expanded by being passed through a valve portion in the body and led to a downstream side. A refrigerant introduction port provided on one end side of the refrigerant passage and a refrigerant outlet port provided on the other end side thereof, a valve hole provided in an intermediate portion of the refrigerant passage, A valve element that opens and closes the valve part by contacting and separating from the valve hole, a drive part that generates a driving force for opening and closing the valve element, an operation rod that is supported by the body and transmits the driving force of the drive part to the valve element; And an anti-vibration spring that is interposed between the body and the actuating rod and biases the actuating rod to provide sliding resistance. The anti-vibration spring is formed by bending a single strip-shaped plate material having elasticity at a plurality of locations along the extending direction.

  According to this aspect, the vibration of the valve body connected to the operating rod can be suppressed by giving an appropriate sliding resistance to the operating rod by the vibration-proof spring. In particular, the vibration-proof spring is realized by a simple process of bending a single strip-shaped plate material at a plurality of locations along its extending direction. That is, since it is formed by bending a plate instead of a wire, it can have sufficient rigidity and appropriate elasticity, and a sufficient sliding load can be applied to the operating rod. In addition, since a strip-shaped plate material is adopted as the material of the vibration-proof spring, even if the plate material is cut out from a larger plate material, the yield of the material can be maintained high, and the material cost can be suppressed. Become. Furthermore, since the spring is configured with the entire plate width, the vibration-proof spring as a whole can be configured compactly in the plate width direction. That is, it is possible to provide a vibration isolation spring suitable for vibration isolation of the operating portion of the expansion valve easily and at low cost.

  Another aspect of the present invention is a vibration-proof spring. This anti-vibration spring is formed by bending a single strip-shaped plate material having elasticity at a plurality of locations along the extending direction thereof, and both side portions of the plate material are folded back symmetrically so that one side portion side is opened. In each of the pair of folded portions, the inner portion constitutes a first spring portion, the outer portion constitutes a second spring portion, and a direction perpendicular to the extending direction The urging force of at least one of the first spring portion and the second spring portion is adjusted by partially changing the plate width of the first spring portion and the second spring portion.

  According to this aspect, the anti-vibration spring is realized by a simple process of bending a single strip-shaped plate material at a plurality of locations along its extending direction. Moreover, since it forms by bending a board | plate material instead of a wire, it can have sufficient rigidity and moderate elasticity. In addition, since a strip-shaped plate material is adopted as the material of the vibration-proof spring, even if the plate material is cut out from a larger plate material, the yield of the material can be maintained high, and the material cost can be suppressed. Become. Further, by partially changing the plate width of the plate material along the extending direction, the respective spring loads can be adjusted appropriately for the inner first spring portion and the outer second spring portion. . As a result, the sliding load can be adjusted according to the object of vibration isolation, and the versatility becomes high. In addition, although the plate width partially changes, since the spring is configured with the entire plate width, the vibration-proof spring as a whole can be configured compactly in the plate width direction. And by applying the said vibration-proof spring to the expansion valve mentioned above, the vibration-proof of the action | operation part can be implement | achieved favorably.

  ADVANTAGE OF THE INVENTION According to this invention, it becomes possible to provide the anti-vibration spring suitable for anti-vibration of the action | operation part of an expansion valve simply and at low cost.

It is sectional drawing of the expansion valve which concerns on embodiment. It is a figure which shows the structure of an anti-vibration spring. It is a figure which shows the structure of the vibration isolator spring which concerns on the modification of 1st Embodiment. It is a figure which shows the structure of the vibration isolating spring which concerns on the other modification of 1st Embodiment. It is a figure which shows the structure of the vibration isolator spring which concerns on 2nd Embodiment. It is a figure which shows the structure of the anti-vibration spring which concerns on the modification of 2nd Embodiment. It is a figure which shows the structure of the vibration isolator spring which concerns on the other modification of 2nd Embodiment. It is a figure which shows the structure of the vibration isolator spring which concerns on the other modification of 2nd Embodiment. It is a figure which shows the structure of the vibration isolator spring which concerns on 3rd Embodiment. It is a figure which shows the structure of the vibration isolating spring which concerns on 4th Embodiment. It is a figure which shows the structure of the anti-vibration spring which concerns on the modification of 4th Embodiment. It is a figure which shows the structure of the vibration isolator spring which concerns on 5th Embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for the sake of convenience, the positional relationship between the structures may be expressed based on the illustrated state. In the following embodiments and modifications thereof, substantially the same components are denoted by the same reference numerals, and the description thereof may be omitted as appropriate.

[First Embodiment]
In this embodiment, the expansion valve of the present invention is embodied as a temperature type expansion valve applied to a refrigeration cycle of an automobile air conditioner. In this refrigeration cycle, a compressor that compresses the circulating refrigerant, a condenser that condenses the compressed refrigerant, a receiver that separates the condensed refrigerant into gas and liquid, and the separated liquid refrigerant is squeezed and expanded into a mist. An expansion valve and an evaporator that evaporates the mist-like refrigerant and cools the air in the passenger compartment by the latent heat of vaporization are provided, but detailed description other than the expansion valve is omitted.

FIG. 1 is a cross-sectional view of an expansion valve according to an embodiment.
The expansion valve 1 has a body 2 formed by subjecting a member obtained by extruding a material made of an aluminum alloy to a predetermined cutting process. The body 2 has a prismatic shape, and a valve portion is provided in the body 2 for performing expansion and expansion of the refrigerant. A power element 3 that functions as a temperature sensing unit is provided at an end of the body 2 in the longitudinal direction.

  An introduction port 6 for introducing high-temperature / high-pressure liquid refrigerant from the receiver side (capacitor side) to the side portion of the body 2, and a derivation for deriving low-temperature / low-pressure refrigerant expanded by the expansion valve 1 toward the evaporator. A port 7, an introduction port 8 for introducing the refrigerant evaporated by the evaporator, and a lead-out port 9 for leading the refrigerant that has passed through the expansion valve 1 to the compressor side are provided. A screw hole 10 is formed between the introduction port 6 and the lead-out port 9 so that a stud bolt for pipe attachment (not shown) can be implanted.

  In the expansion valve 1, a first passage 13 is constituted by the introduction port 6, the outlet port 7, and the refrigerant passage connecting them. The first passage 13 is provided with a valve portion at an intermediate portion thereof, and the refrigerant introduced from the introduction port 6 is squeezed and expanded at the valve portion to form a mist, and is led out from the lead-out port 7 toward the evaporator. To do. On the other hand, a second passage 14 (corresponding to a “return passage”) is constituted by the introduction port 8, the outlet port 9, and the refrigerant passage connecting them. The second passage 14 extends straight, introduces the refrigerant from the introduction port 8, and guides it from the outlet port 9 toward the compressor.

  That is, a valve hole 16 is provided in an intermediate portion of the first passage 13 in the body 2, and a valve seat 17 is formed by an opening edge of the valve hole 16 on the introduction port 6 side. A valve body 18 is disposed so as to face the valve seat 17 from the introduction port 6 side. The valve body 18 is configured by joining a spherical ball valve body that attaches and detaches to the valve seat 17 to open and close the valve portion, and a valve body receiver that supports the ball valve body from below.

  A communication hole 19 is formed in the lower end portion of the body 2 so as to communicate the inside and the outside so as to be orthogonal to the first passage 13, and a valve chamber 40 for accommodating the valve body 18 is formed by the upper half portion thereof. . The valve chamber 40 communicates with the valve hole 16 at the upper end portion thereof and communicates with the introduction port 6 through the small hole 42 at the side portion, and constitutes a part of the first passage 13. The small hole 42 is formed by locally narrowing the passage section of the first passage 13 and opens to the valve chamber 40.

  An adjustment screw 20 (corresponding to an “adjusting member”) is screwed into the lower half of the communication hole 19 so as to seal the communication hole 19 from the outside. A spring 23 that biases the valve body 18 in the valve closing direction is interposed between the valve body 18 (more precisely, the valve body receiver) and the adjusting screw 20. By adjusting the screwing amount of the adjustment screw 20 into the body 2, the load of the spring 23 can be adjusted. An O-ring 24 is interposed between the adjusting screw 20 and the body 2 to prevent refrigerant leakage.

  On the other hand, a communication hole 25 is formed in the upper end portion of the body 2 so as to communicate between the inside and the outside so as to be orthogonal to the second passage 14, and the power element 3 (“temperature sensitive”) is sealed to seal the communication hole 25. Corresponding to the “part”). The power element 3 is configured such that a diaphragm 28 made of a thin metal plate is interposed between an upper housing 26 and a lower housing 27, and a disk 29 is disposed on the lower housing 27 side. A temperature-sensitive gas is enclosed in a sealed space surrounded by the upper housing 26 and the diaphragm 28. An O-ring 30 is interposed between the power element 3 and the body 2 to prevent refrigerant leakage. The pressure and temperature of the refrigerant passing through the second passage 14 are transmitted to the lower surface of the diaphragm 28 through the communication hole 25 and the groove provided in the disk 29.

  A stepped hole 34 for connecting the first passage 13 and the second passage 14 is provided in the central portion of the body 2, and a long shaft 33 ( Functioning as an “actuating rod” is slidably inserted. The shaft 33 is interposed between the disk 29 and the valve body 18. Thereby, the driving force due to the displacement of the diaphragm 28 is transmitted to the valve body 18 through the disk 29 and the shaft 33, and the valve portion is opened and closed.

  The upper half portion of the shaft 33 crosses the second passage 14, and the lower half portion slidably penetrates the small diameter portion 44 of the stepped hole 34. An anti-vibration spring for applying a biasing force in a direction perpendicular to the axial direction to the shaft 33, that is, a lateral load (sliding load), is applied to the large-diameter portion 46 (corresponding to the “hole”) of the stepped hole 34. 50 is arranged. When the shaft 33 receives a lateral load of the vibration-proof spring 50, vibrations of the shaft 33 and the valve body 18 due to fluctuations in the refrigerant pressure are suppressed. Details of the structure of the vibration-proof spring 50 will be described later.

  In the expansion valve 1 configured as described above, the power element 3 senses the pressure and temperature of the refrigerant returned from the evaporator via the introduction port 8, and the diaphragm 28 is displaced. The displacement of the diaphragm 28 becomes a driving force and is transmitted to the valve body 18 through the disk 29 and the shaft 33 to open and close the valve portion. On the other hand, the liquid refrigerant supplied from the receiver is introduced from the introduction port 6 and is squeezed and expanded by passing through the valve portion to become a low-temperature / low-pressure mist refrigerant. The refrigerant is led out from the lead-out port 7 toward the evaporator.

  Next, a specific structure of the vibration isolation spring 50 will be described. FIG. 2 is a view showing the structure of the vibration-proof spring. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows the state by which the vibration-proof spring was penetrated by the stepped hole, (C) is a top view which shows the no-load state of a vibration-proof spring.

  As shown in FIGS. 2 (A) and 2 (B), the anti-vibration spring 50 is formed by bending a strip-shaped plate material made of a metal having high elasticity, for example, stainless steel, at a plurality of locations along the extending direction. Is formed. Specifically, a so-called forming process provides a circular shape with a circular arc in the middle of a long rectangular plate, and is symmetrical with respect to the bisector (see the alternate long and short dash line) of the intermediate portion 52. It is formed so that both ends are folded inward.

  That is, as shown in FIGS. 2B and 2C, the anti-vibration spring 50 includes an intermediate portion 52 having substantially the same curvature as the large-diameter portion 46 of the stepped hole 34 and both sides of the intermediate portion 52. The outer spring portion 54 extends linearly, and a folded portion 56 is formed by folding the distal end of the outer spring portion 54 inside thereof. A linear inner spring portion 58 is connected to the folded portion 56. As shown in FIG. 2C, the anti-vibration spring 50 has a substantially straight line as shown in FIG. 2C in a no-load state before being inserted into the large-diameter portion 46.

  When the anti-vibration spring 50 is inserted into the large-diameter portion 46, for example, the tip of a tool 60 such as tweezers is inserted inside the pair of folded portions 56 and a load is applied so that both folded portions 56 are brought closer (in the drawing). (Refer to the arrow), and insert it after making it close to a ring as shown by the dotted line in the figure. In other words, the pair of folded portions 56 functions as a grip portion when the vibration-proof spring 50 is inserted into the large-diameter portion 46. At this time, since the tip of the tool 60 is arranged inside the circumscribed circle of the vibration isolating spring 50, that is, it is not necessary to grasp from the outside of the vibration isolating spring 50, the tool is inserted into the large diameter portion at the time of insertion. The work becomes very easy without being caught by the edge of 46. At this time, the pair of inner spring portions 58 are substantially parallel to each other.

  Since the anti-vibration spring 50 is inserted into the large-diameter portion 46 in a state of being elastically deformed from an unloaded state, a lateral load in a direction in which the pair of inner spring portions 58 sandwich the shaft 33 as shown in FIG. Is generated. On the other hand, the outer spring portion 54 is also slightly bent, and generates a load that presses a part of the folded portion 56 against the inner surface of the large diameter portion 46. The anti-vibration spring 50 thus contacts the shaft 33 at two points and applies a sliding load, while being firmly fixed to the large-diameter portion 46 (that is, the body 2) by its elastic reaction force. .

  As described above, in the expansion valve 1 of the present embodiment, an appropriate sliding resistance can be given to the shaft 33 by the anti-vibration spring 50, and as a result, the shaft 33 and the valve body accompanying the pressure fluctuation of the refrigerant. 18 vibrations can be suppressed. In particular, since the vibration-proof spring 50 can be obtained by a simple process of bending a strip-shaped plate material along the extending direction, even if the plate material is cut out from a larger plate material, Is less likely to occur and manufacturing costs can be reduced. Further, since the outer spring portion 54 and the inner spring portion 58 are formed by the entire plate width of the vibration-proof spring 50, it is possible to form a compact structure in the width direction. Furthermore, since the pair of folded portions 56 are provided so that the tip of the tool 60 can be disposed inside the vibration-proof spring 50, the attaching operation to the body 2 becomes very easy. In particular, when the expansion valve 1 is downsized, both the large-diameter portion 46 and the vibration isolating spring 50 are reduced. Therefore, the vibration isolating spring 50 can be easily grasped and the work can be performed in a small space, so that the working efficiency is remarkably improved. To do.

[Modification 1]
FIG. 3 is a diagram illustrating a structure of a vibration-proof spring according to a modification of the first embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole. However, illustration of the stepped hole and the shaft is omitted.

  In this modification, the pair of inner spring portions 158 are each provided with a hemispherical bulging portion 70 at the center of the inner side surface (opposing surface) thereof. When the anti-vibration spring of this modification is inserted into the large-diameter portion 46, the pair of bulging portions 70 come into point contact with the shaft 33. With such a configuration, even if the shaft 33 may be slightly inclined, the point contact state between the bulging portion 70 and the shaft 33 is always ensured, and the smooth support state by the vibration isolating spring is maintained. . The details of the bulging portion 70 will be described in a second embodiment described later.

[Modification 2]
FIG. 4 is a diagram illustrating a structure of a vibration-proof spring according to another modification of the first embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole.

  In this modification, a claw portion 72 (corresponding to a “locking portion”) is formed at the edge of the portion that contacts the large-diameter portion 46 of the vibration-proof spring. That is, the claw portion 72 is formed by partially cutting out the upper edges of the pair of folded portions 156 and bending them outward. With such a configuration, when the vibration-proof spring is inserted into the large-diameter portion 46, the claw portion 72 is hooked on the inner wall of the large-diameter portion 46, and the vibration-proof spring can be prevented from falling off. In this modification, the claw portion 72 is provided at the upper edge of the folded portion 156, but may be provided at the lower edge of the folded portion 156. Or you may provide in both those upper end edges and lower end edges. Further, the claw portion 72 may be provided on one or both of the upper end edge and the lower end edge of the intermediate portion 52.

[Second Embodiment]
The expansion valve of the present embodiment has the same configuration as that of the first embodiment except that a partial load adjustment is performed on the vibration-proof spring. FIG. 5 is a diagram illustrating the structure of the vibration-proof spring according to the second embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows the state by which the anti-vibration spring was penetrated by the stepped hole. (C) is an expanded view which shows the structure of the bulging part vicinity of the vibration isolator spring which concerns on this embodiment, (D) is the modification.

  As shown in FIGS. 5 (A) and 5 (B), the vibration-proof spring 250 of this embodiment is attached to the shaft 33 by partially changing the plate width in the direction perpendicular to the extending direction. The power is adjusted. That is, the plate width is made smaller than that of the outer spring portion 54 from the middle of the folded portion 256 to the tip of the inner spring portion 258. As in the first modification of the first embodiment, the pair of inner spring portions 258 are each provided with a hemispherical bulging portion 70 at the center of the inner surface thereof. For this reason, when the vibration-proof spring 250 is inserted into the large-diameter portion 46, the pair of bulging portions 70 come into point contact with the shaft 33.

  As shown in the left side of FIG. 5C, the vibration-proof spring 250 has a reduced plate width at both ends at the stage of cutting out the strip-shaped plate material. And the hemispherical bulging part 70 is formed by press molding from the one side of the board | plate material so that the side view of the narrow part may be shown in the right stage of the figure. After forming the plate material in this way, the vibration-proof spring 250 is obtained by bending the plate material at a plurality of locations in the extending direction by forming.

  According to the present embodiment, by reducing the inner spring portion 258 and the plate width in the vicinity thereof, the load applied to the shaft 33 is made smaller than in the case of the first embodiment, and an appropriate sliding load is applied to the shaft 33. To give. With such a configuration, the vibration of the shaft 33 and the valve body 18 is suppressed as in the first embodiment, while the operation responsiveness of the valve body 18 is ensured. Note that the bulging portion 70 is not limited to the hemispherical shape illustrated in FIG. 5C, and may be appropriately selected, for example, an arched shape like the bulging portion 270 illustrated in FIG. 5D. it can.

[Modification 1]
FIG. 6 is a diagram illustrating a structure of a vibration-proof spring according to a modification of the second embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole.

  In this modification, a rectangular hole 160 is formed at the center of each of the pair of outer spring portions 154, so that the plate width of the outer spring portion 154 is substantially reduced. With such a configuration, the reaction force to the body 2 generated when the vibration-proof spring is inserted into the large-diameter portion 46 is made smaller than that in the first embodiment, and the support strength of the vibration-proof spring in the body 2 is reduced. Can be adjusted moderately.

[Modification 2]
FIG. 7 is a diagram illustrating a structure of a vibration-proof spring according to another modification of the second embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole.

  In this modification, a hole 162 is further provided at the boundary between the folded portion 262 and the inner spring portion 58. Thereby, the load applied to the shaft 33 is made smaller than that in the first embodiment, and an appropriate sliding load is applied to the shaft 33. Thus, by providing an appropriate number of holes in the extending direction of the vibration-proof spring, both the urging force applied to the shaft 33 and the reaction force to the body 2 may be adjusted.

[Modification 3]
FIG. 8 is a diagram illustrating the structure of a vibration-proof spring according to another modification of the second embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole.

  In this modification, the plate | board width is made small, without providing a hole in the outer side spring part 254. FIG. Specifically, the plate width is reduced in such a manner that the upper and lower edges of the outer spring portion 254 are cut out. Even with such a configuration, the same effects as those of the first and second modifications can be obtained.

  In another modification, in the vibration-proof spring shown in FIGS. 6 and 8, for example, the plate width of the inner spring portion 258 and the plate width of the intermediate portion 52 may be substantially the same. Further, without providing the hole 160 in the anti-vibration spring shown in FIG. 7, at least one of the upper end edge and the lower end edge of the outer spring portion 154 may be cut out to reduce the plate width.

[Third Embodiment]
The expansion valve of the present embodiment is slightly different from the second embodiment in the load adjustment structure of the vibration-proof spring. FIG. 9 is a diagram illustrating the structure of the vibration-proof spring according to the third embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows the state by which the anti-vibration spring was penetrated by the stepped hole.

  In the vibration-proof spring 350 of this embodiment, an intermediate part 352 and a pair of outer spring parts 354 are connected in an annular shape. A hole 360 is formed in the intermediate portion 352. On the other hand, the plate width of the folded portion 356 and the inner spring portion 358 is smaller than that of the outer spring portion 354. With such a configuration, the spring load of the intermediate portion 352 can be adjusted.

[Fourth Embodiment]
The expansion valve of the present embodiment is different from the first embodiment in the structure of the vibration-proof spring. FIG. 10 is a diagram illustrating the structure of the vibration-proof spring according to the fourth embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows the state by which the anti-vibration spring was penetrated by the stepped hole.

  In the vibration-proof spring 450 of this embodiment, a pair of inner spring portions 458 are connected to the intermediate portion 452. And the front end side of the pair of inner spring portions 458 is folded outward to form a folded portion 456, and an outer spring portion 454 is connected to the distal end. As described above, although the manner of the folded portion is different from that of the first embodiment, the pair of folded portions 456 function as gripping portions when the vibration-proof spring 450 is inserted into the large-diameter portion 46.

  Further, by forming a rectangular hole 460 at the center of each of the pair of inner spring portions 458, the plate width of the inner spring portion 458 is substantially reduced. With such a configuration, it is possible to adjust the urging force applied to the shaft 33 that is generated when the vibration-proof spring is inserted into the large-diameter portion 46. Further, the plate width of the pair of outer spring portions 454 is reduced. With such a configuration, the reaction force to the body 2 generated when the vibration-proof spring is inserted into the large-diameter portion 46 is made smaller than that in the first embodiment, and the support strength of the vibration-proof spring in the body 2 is reduced. Can be adjusted moderately.

[Modification 1]
FIG. 11 is a diagram illustrating a structure of a vibration-proof spring according to a modification of the fourth embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows a state when a vibration-proof spring is inserted in the stepped hole. However, illustration of the stepped hole and the shaft is omitted.

  In this modification, the pair of inner spring portions 459 has a reduced plate width in such a manner that the upper and lower edges thereof are cut out. On the other hand, by forming a rectangular hole 461 at the center of each of the pair of outer spring portions 455, the plate width of the outer spring portion 455 is substantially reduced. With such a configuration, the biasing force to the shaft 33 and the reaction force to the body 2 that are generated when the vibration-proof spring is inserted into the large-diameter portion 46 are adjusted.

  In another modification, the anti-vibration spring 450 illustrated in FIG. 10 may be configured not to include the hole 460, for example. Further, the plate width of the outer spring portion 454 and the plate width of the inner spring portion 458 may be the same.

[Fifth Embodiment]
The expansion valve of the present embodiment is different from the first embodiment in the structure of the vibration-proof spring. FIG. 12 is a diagram illustrating the structure of the vibration-proof spring according to the fifth embodiment. (A) is a perspective view which shows the whole structure of an anti-vibration spring. (B) is a top view which shows the state by which the anti-vibration spring was penetrated by the stepped hole.

  The anti-vibration spring 550 of the present embodiment has a triangular cross section by bending a strip-shaped plate material at two locations along its extending direction. In the anti-vibration spring 550, three side surfaces forming the triangular shape constitute a first spring portion 551, a second spring portion 552, and a third spring portion 553. A bulging portion 70 is formed on the inner surface of each spring portion. That is, the anti-vibration spring 550 supports the shaft 33 at three points. At both ends in the extending direction of the plate material, that is, at the tip of the first spring portion 551 and the tip of the third spring portion 553, a complementary notch 560 that can intersect is formed, and the vibration-proof spring 550 is assembled. The degree of freedom is improved. In another modification, the notch 560 may not be provided.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the specific embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Nor. For example, some components may be combined in the above-described embodiment and modification, or some components may be deleted from each embodiment and modification.

  Although not described in the above embodiment, a seal member such as an O-ring is provided between the stepped hole 34 and the shaft 33 shown in FIG. 1, and refrigerant leaks from the first passage 13 to the second passage 14. May be prevented or suppressed. Specifically, the depth of the large diameter portion 46 of the stepped hole 34 may be increased, an O-ring may be disposed on the bottom side of the large diameter portion 46, and an anti-vibration spring may be disposed above the O ring. In that case, the anti-vibration spring can function as a stopper for locking the O-ring from above by the bottom surface of the folded portion.

  The expansion valve of the above embodiment is suitably applied to a refrigeration cycle that uses an alternative chlorofluorocarbon (HFC-134a) or the like as a refrigerant. However, the expansion valve of the present invention uses a refrigerant having a high operating pressure such as carbon dioxide. It is also possible to apply to a cycle. In that case, an external heat exchanger such as a gas cooler is disposed in place of the condenser in the refrigeration cycle. At this time, in order to supplement the strength of the diaphragm constituting the power element 3, for example, a metal disc spring or the like may be arranged in an overlapping manner. Alternatively, a disc spring or the like may be disposed instead of the diaphragm. Moreover, although the example which comprised the expansion valve as a temperature type expansion valve was given in the said embodiment, it can also be comprised as an expansion valve which does not sense temperature. For example, you may comprise as an electromagnetic expansion valve which uses a solenoid as a drive part. Or you may comprise as an electric expansion valve which uses electric motors, such as a stepping motor, as a drive part.

  DESCRIPTION OF SYMBOLS 1 Expansion valve, 2 Body, 3 Power element, 13 1st channel | path, 14 2nd channel | path, 16 Valve hole, 17 Valve seat, 18 Valve body, 33 Shaft, 34 Stepped hole, 46 Large diameter part, 52 Middle Part, 54 outer spring part, 56 folding part, 58 inner spring part, 70 bulging part, 72 claw part, 154 outer spring part, 156 folding part, 158 inner spring part, 160, 162 hole, 254 outer spring part, 256 Folded part, 258 inner spring part, 260 hole, 262 folded part, 270 bulge part, 352 intermediate part, 354 outer spring part, 356 folded part, 358 inner spring part, 452 intermediate part, 454, 455 outer spring part, 456 Folded part, 458, 459 Inner spring part, 460, 461 hole, 551 1st Spring portion, 552 a second spring portion, 553 the third spring part.

Claims (10)

In the expansion valve that squeezes and expands the refrigerant introduced from the upstream side of the refrigeration cycle by passing it through the valve part in the body and leads it to the downstream side,
A refrigerant passage formed so as to penetrate the body, provided with a refrigerant introduction port on one end side thereof, and provided with a refrigerant outlet port on the other end side;
A valve hole provided in an intermediate portion of the refrigerant passage;
A valve body that opens and closes the valve portion in contact with and apart from the valve hole;
A drive unit that generates a drive force for opening and closing the valve body;
An actuating rod supported by the body and transmitting the driving force of the driving unit to the valve body;
An anti-vibration spring interposed between the body and the actuating rod and biasing the actuating rod to provide sliding resistance;
With
The anti-vibration spring is formed by bending a single belt-like plate material having elasticity at a plurality of locations along its extending direction.   The expansion valve according to claim 1, wherein the vibration-proof spring contacts the outer peripheral surface of the operating rod at two or more points.   The expansion valve according to claim 2, wherein the anti-vibration spring contacts at two points symmetrical with respect to the axis of the operating rod.   The anti-vibration spring is configured to adjust at least one of an urging force applied to the operating rod and a reaction force to the body by partially changing a plate width in a direction perpendicular to the extending direction. The expansion valve according to claim 1, wherein the expansion valve is provided.   The expansion valve according to claim 4, wherein the vibration-proof spring partially changes the plate width by opening a hole in a predetermined portion of the plate material. The vibration-proof spring is
By being inserted into the hole formed concentrically with the operating rod in the body, positioning with respect to the operating rod is performed,
In an unloaded state where the hole is not inserted, the outer shape is formed to be larger than the hole,
It is inserted into the hole in a state of being elastically deformed under a load in a direction to reduce its outer shape, and is fixed to the body by being pressed against the inner peripheral surface of the hole by the elastic reaction force. The expansion valve according to any one of claims 1 to 5.   The expansion valve according to claim 6, wherein the vibration-proof spring includes a locking portion that is hooked on an inner peripheral surface of the hole portion.   The anti-vibration spring is formed such that both side portions of the plate member are folded back symmetrically to open one side portion, and a predetermined tool is inserted inside the pair of folded portions to narrow the opening portion. The expansion valve according to claim 6 or 7, wherein an outer diameter of the expansion valve can be reduced by applying a load in a direction. A temperature at which the refrigerant expanded and passed through the valve part is led out from the outlet port and supplied to the evaporator, and the pressure and temperature of the refrigerant returned from the evaporator is sensed to control the opening degree of the valve part. Configured as an expansion valve,
A return passage that is formed so as to penetrate the body separately from the refrigerant passage, and allows the refrigerant returned from the evaporator to pass through,
It is provided as the drive unit, operates by sensing the temperature and pressure of the refrigerant flowing through the return passage, and transmits the drive force to the valve body through the operating rod to change the opening of the valve unit. A power element for controlling the flow rate of the refrigerant supplied to the evaporator;
The expansion valve according to claim 1, comprising: Bending a single strip-like plate material having elasticity at a plurality of locations along its extending direction, and forming both sides of the plate symmetrically folded so that the side piece side is opened,
In each of the pair of folded portions, the portion located on the inner side constitutes the first spring portion, the portion located on the outer side constitutes the second spring portion, and the plate width in the direction perpendicular to the extending direction An anti-vibration spring configured to adjust an urging force of at least one of the first spring portion and the second spring portion by partially changing.

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