JP2017204245A - Press mechanism and pressure-reducing valve having the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a press mechanism capable of suppressing an abrasion accompanied with a slide of a piston and a pressure-reducing valve having the press mechanism.SOLUTION: A press mechanism 6 of a pressure-reducing valve includes: a bottomed cylindrical cylinder 51; a piston 52 slidably stored inside a cylinder 51; and a coil spring 53 arranged in a compressed state between a bottom part 62 of the cylinder 51 and the piston 52 and energizing the piston 52. Sit surfaces 82 and 84 on which end surfaces 81 and 83 of the coil spring 53 in the cylinder 51 and the piston 52 sit are in parallel with each other and formed inclined toward an orthogonal surface S orthogonal to an axial line L2 of the cylinder 51. The end surfaces 81 and 83 of the coil spring 53 are formed in a flat surface state orthogonal to the center axis L1. Each of inclined angles β and γ for the orthogonal flat surface S of the sit surfaces 82 and 84 is set so as to be equal to an orthogonal angle α between a resultant force Fc of the coil spring 53 and the center axis L1.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a pressing mechanism and a pressure reducing valve including the pressing mechanism.

  Conventionally, as a pressure reducing valve (regulator) used for pressure adjustment of high pressure hydrogen gas for fuel cell vehicles, a valve mechanism provided between a primary port and a secondary port, and a valve body of the valve mechanism are pressed to Some include a pressing mechanism that adjusts the opening (opening) (for example, Patent Document 1). Such a pressing mechanism includes a piston slidably accommodated in the cylinder, and a coil spring that is arranged coaxially with the cylinder and biases the piston. Then, the piston slides based on the pressure of the high-pressure gas flowing in from the primary port, and the opening amount of the valve mechanism is changed, whereby the high-pressure gas is decompressed and sent out from the secondary port.

JP 2014-115820 A JP 2008-273294 A

  By the way, even if the coil spring is uniformly compressed (parallel compressed) along its central axis, the center other than the axial force along the central axis of the coil spring depends on the effective number of turns, shape, etc. A lateral force in a direction perpendicular to the axis is generated. Therefore, the direction of the entire urging force (the combined force of the axial force and the lateral force) generated when the coil spring is compressed is slightly inclined with respect to the central axis of the coil spring. As a result, in the conventional configuration described above, the piston is biased in a direction intersecting the cylinder axis, and a part of the piston strongly hits the inner peripheral surface of the cylinder, so that wear occurs when the piston slides. It tends to occur.

  Such a problem is not limited to the pressure reducing valve, and may occur in the same manner in a configuration including a pressing mechanism that biases the piston by a coil spring, such as a rack guide (for example, Patent Document 2).

  An object of the present invention is to provide a pressing mechanism capable of suppressing wear caused by sliding of a piston and a pressure reducing valve provided with the pressing mechanism.

  A pressing mechanism that solves the above problem includes a cylinder, a piston that is slidably accommodated in the cylinder, a coil spring that is disposed between the cylinder and the piston, and biases the piston. At least one of the cylinder and the seating surfaces of the piston, on which the end surfaces of the coil springs are seated, is formed so as to be inclined with respect to an orthogonal plane orthogonal to the axis of the cylinder.

  According to the above configuration, since at least one of the seating surfaces is inclined with respect to the orthogonal plane, the relative circumferential position (phase) between the cylinder, the piston and the coil spring is changed when the pressing mechanism is assembled. The direction of the combined force of the coil spring changes. Therefore, the coil spring can be assembled so as to reduce the deviation between the direction of the combined force of the coil spring and the axial direction of the cylinder. Thereby, it can reduce that a part of piston slides in the state pressed strongly to the internal peripheral surface of a cylinder, and can suppress wear of a piston and a cylinder.

  In the pressing mechanism, it is preferable that the seat surface of the cylinder and the seat surface of the piston are parallel to each other, and each end surface of the coil spring is formed to be orthogonal to the central axis of the coil spring.

  According to the above configuration, since the coil spring is compressed substantially uniformly along its central axis, the amount of compression of the coil spring is suppressed from greatly changing according to the circumferential position, and the piston is allowed to slide within the cylinder. It can be stabilized.

  In the pressing mechanism, an inclination angle between each seat surface and the orthogonal plane is such that an axial force in a central axis direction and a lateral direction in a direction orthogonal to the central axis direction when the coil spring is compressed along the central axis. It is preferably set to be equal to the intersection angle between the force synthesis force and the central axis.

According to the said structure, this coil spring can be assembled | attached so that the direction of the synthetic force of a coil spring and the axial direction of a cylinder may correspond substantially.
A pressure reducing valve that solves the above problem includes a valve mechanism provided between a primary port and a secondary port, and a pressing mechanism having any one of the above-described configurations that presses the valve body of the valve mechanism.

  According to the said structure, since abrasion of a piston and a cylinder can be suppressed, durability can be improved, for example.

  According to the present invention, it is possible to suppress wear associated with the sliding of the piston.

The partial cross section figure of a pressure-reduction valve. The schematic diagram which shows the synthetic | combination force at the time of compressing a coil spring uniformly along an axis. The schematic cross section which shows the press mechanism vicinity in the pressure-reduction valve of 1st Embodiment. The schematic cross section which shows the press mechanism vicinity in the pressure-reduction valve of 2nd Embodiment. The schematic cross section which shows the press mechanism vicinity in the pressure-reduction valve of 3rd Embodiment. The schematic cross section which shows the coil spring of 4th Embodiment. The schematic cross section which shows the press mechanism vicinity in the pressure-reduction valve of 4th Embodiment.

(First embodiment)
Hereinafter, a pressing mechanism and a first embodiment of a pressure reducing valve including the pressing mechanism will be described with reference to the drawings.
A pressure reducing valve (regulator) 1 shown in FIG. 1 is provided in the middle of a fluid circuit connecting a hydrogen tank mounted on a fuel cell vehicle and a fuel cell, and decompresses high-pressure hydrogen gas and sends it to the fuel cell side. The pressure reducing valve 1 includes a housing 4 in which a primary port 2 and a secondary port 3 are formed, a valve mechanism 5 provided between the primary port 2 and the secondary port 3 in the housing 4, and an opening of the valve mechanism 5. And a pressing mechanism 6 that adjusts the amount (opening).

  The housing 4 is formed with a circular hole-shaped accommodation hole 11 that communicates with the primary port 2 and the secondary port 3 and opens to the outside. The supply flow path 12 extending from the primary port 2 opens at the center of the bottom surface 11 a of the accommodation hole 11, and the delivery flow path 13 extending to the secondary port 3 opens at an eccentric position on the bottom surface of the accommodation hole 11. An opening portion on the side of the accommodation hole 11 in the supply flow path 12 is set to have a larger inner diameter than other portions so as to accommodate the valve mechanism 5. Specifically, the opening portion of the supply flow path 12 is continuous with the cylindrical first storage portion 14 and the first storage portion 14 in order from the upstream side (lower side in FIG. 1) of the supply flow path 12. It has the cylindrical 2nd accommodating part 15 opened to the bottom face 11a. The first and second accommodating portions 14 and 15 are formed so that the inner diameters thereof increase in this order and are arranged coaxially with the accommodating hole 11. The delivery channel 13 is provided with a relief valve and a joint (both not shown).

  The valve mechanism 5 is disposed in the plug 23, the valve body 21 accommodated in the supply flow path 12, the valve seat 22 accommodated in the first accommodating part 14, the plug 23 accommodated in the second accommodating part 15, and the plug 23. The valve stem 24 is provided.

  The valve body 21 has a substantially cylindrical main body 31 with a bottom, and a tapered portion whose outer shape gradually decreases from the bottom of the main body 31 toward the downstream side (upper side in FIG. 1), and the tip of the valve body 21 is outside. A contact portion 33 having a substantially constant diameter. The outer diameter of the valve body 21 (main body portion 31) is set to be slightly smaller than the inner diameter of the supply flow path 12, and can move in the axial direction within the supply flow path 12. A biasing member 34 such as a coil spring is accommodated in the main body 31. The valve body 21 is urged downstream by compressing the urging member 34 between a rod-like support member 35 disposed on the upstream side of the supply flow path 12 and the valve body 21.

  The valve seat 22 is formed in an annular shape having a valve port 36 and is press-fitted into the first accommodating portion 14. The inner diameter of the valve port 36 is formed to be substantially equal to the outer diameter at the midway position of the tapered portion of the contact portion 33. The valve seat 22 is made of an elastically deformable hard resin such as a polyimide resin.

  The plug 23 is formed in a cylindrical shape, and is screwed onto the inner periphery of the second accommodating portion 15 while compressing the valve seat 22, and a part of the plug 23 projects into the accommodating hole 11. A through hole 37 that penetrates in the axial direction is formed coaxially with the valve port 36 at the center of the plug 23. The upstream portion of the through hole 37 has a smaller diameter than the other portions, and the inner diameter thereof is set to be substantially equal to the inner diameter of the valve port 36. Further, a flow passage hole 39 that extends in the radial direction and communicates the through hole 37 and the accommodation hole 11 is formed in the protruding portion 38 that projects into the accommodation hole 11 in the plug 23.

  The valve stem 24 includes a cylindrical portion 41 formed in an elongated cylindrical shape, a downstream end portion 42 that protrudes downstream from the cylindrical portion 41, and an upstream end portion 43 that protrudes upstream from the cylindrical portion 41. ing. The outer diameter of the cylindrical portion 41 is set slightly smaller than the inner diameter of the through hole 37 and can move in the axial direction within the through hole 37. A plurality of flow passage holes 44 extending in the axial direction are formed in the cylindrical portion 41 at equiangular intervals around the central axis. The outer diameter of the downstream end portion 42 is formed in a columnar shape having a smaller diameter than the columnar portion 41. The outer diameter of the upstream end portion 43 is set to be substantially equal to the outer diameter of the tip portion of the contact portion 33 of the valve body 21, and the upstream end portion 43 and the contact portion 33 are inserted into the valve port 36 and the through hole 37. Are in contact with each other.

  The pressing mechanism 6 includes a cylinder 51 fixed in the receiving hole 11, a piston 52 slidably received in the cylinder 51, and a coil spring 53 disposed in a compressed state between the cylinder 51 and the piston 52. I have.

  The cylinder 51 is formed in a bottomed cylindrical shape. The cylinder 51 is fixed to the housing 4 by the outer peripheral portion of the cylindrical portion 61 being screwed to the inner periphery of the receiving hole 11 and the lock nut 63 being screwed to the outer peripheral portion of the bottom portion 62. A seal member 64 such as an O-ring is attached to the outer periphery of the opening of the cylindrical portion 61 to ensure airtightness between the accommodation hole 11 and the outside. On the inner bottom surface of the bottom portion 62, a round hole-shaped spring installation hole 65 is formed.

  The piston 52 is formed in a bottomed cylindrical shape, and the outer diameter of the piston 52 is set substantially equal to the inner diameter of the cylindrical portion 61. The piston 52 is accommodated in the cylindrical portion 61 so as to be slidable in the axial direction, and divides the inside of the cylindrical portion 61 into a decompression chamber 71 and a pressure adjustment chamber 72. Note that a ring member 73 such as a wear ring or a lip seal is attached to the outer periphery of the piston 52 to ensure airtightness between the decompression chamber 71 and the pressure adjustment chamber 72. A spring installation hole 74 is formed on the surface of the piston 52 that faces the inner bottom surface of the cylinder 51. The piston 52 is in contact with the downstream end portion 42 of the valve stem 24. As a result, the valve stem 24 and the valve body 21 move together as the piston 52 slides.

  The coil spring 53 is accommodated in a compressed state in the spring installation holes 65 and 74 of the cylinder 51 and the piston 52. Specifically, the compression is performed in a state in which one end surface 81 of the coil spring 53 is in contact with the seating surface 82 which is the bottom surface of the spring installation hole 65 and the other end surface 83 is in contact with the seating surface 84 which is the bottom surface of the spring installation hole 74. Has been placed. The coil spring 53 urges the piston 52 so that the valve body 21 is separated from the valve seat 22, that is, the opening amount (opening degree) of the valve mechanism 5 is increased.

  In the pressure reducing valve 1 configured as described above, the piston 52 slides in the cylindrical portion 61 according to the differential pressure between the pressure reducing chamber 71 and the pressure adjusting chamber 72 and the biasing force of the biasing member 34 and the coil spring 53. Then, the opening amount of the valve mechanism 5 is adjusted according to the position of the piston 52 in the axial direction so that the pressure on the secondary port 3 side (pressure in the decompression chamber 71) does not exceed a predetermined pressure.

  As shown in FIG. 2, the coil spring 53 has a central axis L1 other than the axial force Fl along the central axis L1 even when it is uniformly compressed (parallel compressed) along the central axis L1. Lateral force Fs in the direction orthogonal to the direction is generated. Therefore, the direction of the entire biasing force (the combined force Fc of the axial force Fl and the lateral force Fs) generated when the coil spring 53 is compressed is slightly inclined at the crossing angle α with respect to the central axis L1. Note that the direction of the lateral force Fs in a plane orthogonal to the axial force Fl is substantially uniquely determined according to the spring specifications such as the effective number of turns. Further, in FIG. 2, for convenience of explanation, the crossing angle α is exaggerated larger than actual.

  Considering this point, as shown in FIG. 3, the seating surfaces 82 and 84 of the cylinder 51 and the piston 52 of the present embodiment are inclined with respect to the orthogonal plane S orthogonal to the axis L <b> 2 of the cylinder 51 (cylindrical portion 61). It is formed so that it can be assembled. Thus, considering that the direction of the resultant force Fc of the coil spring 53 changes according to the relative circumferential position (phase) between the cylinder 51, the piston 52, and the coil spring 53, the coil spring 53 has the direction of the resultant force Fc. It is assembled so as to reduce the deviation from the direction of the axis L2. In FIG. 3, for convenience of explanation, the inclination of the seating surfaces 82 and 84 with respect to the orthogonal plane S is exaggerated more than actual.

  Specifically, the inclination angle β of the seating surface 82 of the cylinder 51 with respect to the orthogonal plane S is set substantially equal to the crossing angle α (α = β). At the opening end of the cylindrical portion 61, a mark such as coloring or notch at the position where the seating surface 82 is lowered (the position where the depth of the spring installation hole 65 is deepest) (shown with dots in the drawing for convenience) 85 is provided.

  In the state where the seat surface 84 of the piston 52 is housed in the cylinder 51, the inclination angle γ with respect to the orthogonal plane S is set substantially equal to the crossing angle α (α = γ). At the opening end of the spring installation hole 74 of the piston 52, a mark 86 such as coloring or notch is provided at a position where the seat surface 84 is high (position where the depth of the spring installation hole 74 is the shallowest). . And the piston 52 is assembled | attached to the cylinder 51 so that the circumferential direction position of the marks 85 and 86 may correspond, and the seat surfaces 82 and 84 are parallel.

  The end faces 81 and 83 of the coil spring 53 are formed in a planar shape orthogonal to the central axis L1 and are parallel to each other. The end surfaces 81 and 83 of the coil spring 53 are colored or notched at circumferential positions opposite to the direction in which the lateral force Fs viewed from the central axis L1 acts when compressed uniformly along the central axis L1. Etc. are provided. It is to be noted that a coil spring that is a model of the same standard (the number of effective windings and the shape is the same) is preliminarily compressed along the central axis by an experiment using a well-known 6-component force load cell or the like. The force is measured, and a mark 87 is provided based on the measurement result.

  The coil spring 53 is assembled so that the circumferential positions of the marks 86 and 87 coincide with each other, and the central axis L1 of the coil spring 53 has an intersection angle δ that is substantially equal to the intersection angle α with respect to the axis L2 of the cylinder 51. While intersecting, the direction of the resultant force Fc is substantially parallel to the axis L2. That is, in the coil spring 53, the direction of the component force mapped on the orthogonal plane S of the axial force Fl is opposite to the direction of the component force mapped on the orthogonal plane S (the phase on the orthogonal plane S is the same). 180 °), and the direction of the resultant force Fc is assembled so as to substantially coincide with the direction of the axis L2.

  The pressing mechanism 6 is assembled after the coil spring 53 is accommodated so that the circumferential positions of the marks 86 and 87 coincide with the spring installation hole 74 of the piston 52, and the marks 85 and 86 are positioned on the cylindrical portion 61 of the cylinder 51. The piston 52 and the coil spring 53 are assembled so that the circumferential positions match. The cylinder 51, the piston 52, and the coil spring 53 are kept in phase, and the cylinder 51 is screwed into the housing hole 11 of the housing 4 and the lock nut 63 is screwed.

Next, effects of the pressing mechanism 6 and the pressure reducing valve 1 of the present embodiment will be described.
(1) Since the seating surfaces 82 and 84 are inclined with respect to the orthogonal plane S, the coil spring 53 is changed by changing the relative phase between the cylinder 51, the piston 52 and the coil spring 53 when the pressing mechanism 6 is assembled. The direction of the axial force Fl and the lateral force Fs acting on the piston 52 changes from that to the direction of the resultant force Fc. Since the seating surfaces 82 and 84 are inclined with respect to the orthogonal plane S at inclination angles β and γ substantially equal to the crossing angle α, respectively, and the end surfaces 81 and 83 of the coil spring 53 are orthogonal to the central axis L1, respectively. As a result, the direction of the resultant force Fc of the coil spring 53 can be substantially matched with the direction of the axis L2 of the cylinder 51 so that the coil spring 53 can be assembled. Thereby, it can reduce effectively that a part of piston 52 slides in the state pressed strongly to the internal peripheral surface of the cylindrical part 61, and wear of a cylinder 51 and piston 52 is suppressed, for example, pressure reducing valve 1 durability can be improved.

  (2) Since the seat surfaces 82 and 84 are parallel and the end surfaces 81 and 83 are respectively orthogonal to the central axis L1, the coil spring 53 is compressed substantially uniformly along the central axis L1. Therefore, it is possible to suppress the amount of compression of the coil spring 53 from greatly changing according to the position in the circumferential direction, and to stabilize the sliding of the piston 52 in the cylinder 51.

  (3) Since the coil spring 53 is provided with the mark 87 indicating the direction of the lateral force Fs, and the cylinder 51 and the piston 52 are provided with the marks 85 and 86 indicating the inclined state of the seating surfaces 82 and 84 with respect to the orthogonal plane S, the coil spring is easily provided. The coil spring 53 can be assembled so as to reduce the deviation between the resultant force Fc of 53 and the axis L2 of the cylinder 51.

(Second Embodiment)
Next, a second embodiment will be described with reference to the drawings. For convenience of explanation, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 4, the seating surface 82a of the cylinder 51 of the present embodiment is formed in parallel with the orthogonal plane S, and no mark is provided. In FIG. 4, for convenience of explanation, the inclination of the seating surface 84 of the piston 52 with respect to the orthogonal plane S is exaggerated more than actual. And the coil spring 53 is assembled | attached with respect to the cylinder 51 and the piston 52 so that the circumferential direction position of the marks 86 and 87 may correspond similarly to the said 1st Embodiment.

In this embodiment, in addition to the effect of (3) of the said 1st Embodiment, there exist the following effects.
(4) Since the seat surface 84 is inclined with respect to the orthogonal plane S, the relative phase between the cylinder 51, the piston 52, and the coil spring 53 is changed when the pressing mechanism 6 is assembled. The directions of the axial force Fl and the lateral force Fs acting on the force change and the direction of the resultant force Fc changes. Thereby, the coil spring 53 can be assembled so as to reduce the deviation between the direction of the combined force Fc of the coil spring 53 and the direction of the axis L2.

(Third embodiment)
Next, a third embodiment will be described with reference to the drawings. For convenience of explanation, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 5, the seating surface 84a of the piston 52 is formed in parallel with the orthogonal plane S, and no mark is provided. In FIG. 5, for convenience of explanation, the inclination of the seating surface 82 of the cylinder 51 with respect to the orthogonal plane S is exaggerated more than actual.

  Each end face 81, 83 of the coil spring 53 is provided with a mark 87a based on a lateral force measured by an experiment or the like performed in the following manner. Specifically, first, compression is performed under the same situation as when the coil spring 53 is sandwiched between the cylinder 51 and the piston 52, that is, between a plane orthogonal to the central axis L1 and a plane inclined by an inclination angle β with respect to the plane. The lateral force Fs generated when the Thereafter, the coil spring 53 is rotated around the central axis L1 by a predetermined angle (changing the phase), and the same measurement is performed a plurality of times. The compression amount of the coil spring 53 is the phase where the lateral force is the smallest among the measurement results. A mark 87a is provided at a position in the circumferential direction that is the largest.

And the coil spring 53 is assembled | attached with respect to the cylinder 51 and the piston 52 so that the circumferential direction position of the marks 85 and 87a may correspond.
In this embodiment, in addition to the effect of (3) of the said 1st Embodiment, there exist the following effects.

  (5) The seat surface 84 a is parallel to the orthogonal plane S and the seat surface 82 is inclined with respect to the orthogonal plane S. Therefore, by changing the relative phase between the cylinder 51, the piston 52, and the coil spring 53 when the pressing mechanism 6 is assembled, the circumferential portion of the coil spring 53 where the amount of compression increases (decreases) changes, and each end face 81, As the load distribution changes at 83, the direction of the resultant force Fc changes with the magnitude of the lateral force Fs. Thereby, the coil spring 53 can be assembled so as to reduce the deviation between the direction of the combined force Fc of the coil spring 53 and the direction of the axis L2.

(Fourth embodiment)
Next, a fourth embodiment will be described with reference to the drawings. For convenience of explanation, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 6, the end surfaces 81a and 83a of the coil spring 53 are set such that the inclination angle ε with respect to the plane S1 orthogonal to the central axis L1 is substantially equal to the crossing angle α. A mark 87b is provided on each end face 81a, 83a of the coil spring 53 by the same method as in the second embodiment or the third embodiment. As shown in FIG. 7, the coil spring 53 is assembled to the cylinder 51 and the piston 52 so that the circumferential positions of the marks 85, 86, and 87b coincide. In FIGS. 6 and 7, for convenience of explanation, the inclination of the seating surfaces 82 and 84 and the end surfaces 81 and 83 with respect to the orthogonal plane S is exaggerated more than actual.

In the present embodiment, the same effects as (3) of the first embodiment and (4) of the second embodiment or (5) of the third embodiment are obtained according to the setting method of the mark 87b. .
In addition, each said embodiment can also be implemented in the following aspects which changed this suitably.

  In the first embodiment, the pressing mechanism 6 is assembled with the circumferential positions of the marks 85, 86, 87 matched, but if the deviation between the direction of the resultant force Fc and the direction of the axis L 2 becomes small, the mark 85, The pressing mechanism 6 may be assembled in a state where the circumferential positions of 86 and 87 are slightly shifted. The same applies to the second to fourth embodiments.

  In the first embodiment, the inclination angles β and γ of the seating surfaces 82 and 84 with respect to the orthogonal plane S may be set other than the intersection angle α. Alternatively, the inclination angle β and the inclination angle γ may be set to be different from each other so that the seating surface 82 and the seating surface 84 are not parallel to each other, and the end surfaces 81 and 83 of the coil spring 53 are arranged with respect to the orthogonal plane S. May be inclined. In short, it is sufficient that at least one of the seat surfaces 82 and 84 is inclined with respect to the orthogonal plane S, and the settings of the seat surfaces 82, 82a, 84, and 84a and the end surfaces 81, 81a, 83, and 83a can be changed as appropriate. is there.

  In each of the above embodiments, the cylinder 51 is fixed to the accommodation hole 11 of the housing 4. However, the invention is not limited to this. For example, a disc-shaped cover is fixed to the accommodation hole 11 and the piston 52 is slid into the accommodation hole 11. It may be accommodated as possible. That is, the cylinder may be constituted by a part of the cover and the housing.

  In each of the above embodiments, the cylinder 51, the piston 52, and the coil spring 53 are provided with the marks 85, 86, 87, 87a, 87b in the circumferential direction and the lateral force for providing the marks 85, 86, 87, 87a, 87b. The measuring method can be changed as appropriate. Further, the marks 85, 86, 87, 87a, 87b may not be provided.

In each of the embodiments described above, the pressure reducing valve 1 is used for the purpose of reducing the pressure of the high-pressure hydrogen gas.
In each of the above embodiments, the pressing mechanism 6 is applied to the configuration for pressing the valve body 21 of the pressure reducing valve 1. However, the present invention is not limited thereto, and for example, for pressing a rack bar in a rack and pinion type steering device. You may apply to other apparatuses, such as a structure.

Next, technical ideas that can be understood from the above embodiments and other examples will be described below together with their effects.
(A) The coil spring is provided with a mark based on a lateral force generated when the coil spring is compressed, and the cylinder and the piston are provided with a mark based on an inclined state of each seating surface with respect to the orthogonal plane. Pressing mechanism. According to the above configuration, since the mark is provided, the coil spring can be easily assembled so as to reduce the deviation between the combined force of the coil spring and the axis of the cylinder.

  DESCRIPTION OF SYMBOLS 1 ... Pressure reducing valve, 2 ... Primary port, 3 ... Secondary port, 5 ... Valve mechanism, 6 ... Pressing mechanism, 21 ... Valve body, 22 ... Valve seat, 23 ... Plug, 24 ... Valve stem, 51 ... Cylinder, 52 ... piston, 53 ... coil spring, 81, 81a, 83, 83a ... end face, 82, 82a, 84, 84a ... seating face, 85, 86, 87, 87a, 87b ... mark, α, δ ... crossing angle, β, γ , Ε ... inclination angle, S ... orthogonal plane, Fc ... synthetic force, Fl ... axial force, Fs ... lateral force, L1 ... central axis, L2 ... axis.

Claims (4)

A cylinder,
A piston slidably accommodated in the cylinder;
A coil spring disposed between the cylinder and the piston and energizing the piston;
A pressing mechanism formed such that at least one of the cylinder and piston seating surfaces on which the end surfaces of the coil springs are seated is inclined with respect to an orthogonal plane perpendicular to the axis of the cylinder. The pressing mechanism according to claim 1,
A pressing mechanism formed such that a seating surface of the cylinder and a seating surface of the piston are parallel to each other, and each end surface of the coil spring is orthogonal to a central axis of the coil spring. The pressing mechanism according to claim 2,
The inclination angle between each seating surface and the orthogonal plane is the combined force of the axial force in the central axis direction and the lateral force in the direction orthogonal to the central axis direction when the coil spring is compressed along the central axis. A pressing mechanism that is set to be equal to the crossing angle with the central axis. A valve mechanism provided between the primary port and the secondary port;
The pressure-reduction valve provided with the press mechanism as described in any one of Claims 1-3 which presses the valve body of the said valve mechanism.

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