JP2007092936A - Spring load adjusting device of hydraulic shock absorber - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spring load adjusting device for a hydraulic shock absorber including a stopper supporting a spring support, capable of decreasing the number of component parts and the man-hours for processing and enhancing the reliability in its service. <P>SOLUTION: The spring load adjusting device of the hydraulic shock absorber is configured so that a piston rod 12 is inserted in a cylinder 11 slidably, and a stationary member 61 is installed on the cylinder 11 side or the piston rod 12 side, and a cylindrical member 62 is supported on the periphery of the stationary member 61 in a whirl stop condition, while the stopper 63 is installed on the periphery of the cylindrical member 62, and a plurality of engagement parts 64A to engage selectively with the stopper 63 are provided on the spring support 64 fitted rotatably on the periphery of the cylindrical member 62, wherein the stopper 63 is integrally formed with the cylindrical member 62. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a spring load adjusting device for a hydraulic shock absorber.

As a spring load adjusting device for a hydraulic shock absorber, as described in Patent Document 1, a piston rod is slidably inserted into a cylinder, a fixing member is provided on the cylinder side or the piston rod side, and a cylindrical member is provided on the outer periphery of the fixing member. Supporting in a non-rotating state, providing a stopper on the outer periphery of the cylindrical member, and providing a plurality of engaging portions that selectively engage the stopper on a spring support that is rotatably fitted on the outer periphery of the cylindrical member There is.
Real registration 2507350

  In the spring load adjusting device of Patent Document 1, a stopper is welded to the cylindrical member, and there are the following problems.

  (1) It is necessary to prepare a stopper as a separate part for the cylindrical member.

  (2) A stopper welding process is required.

  (3) There is a risk that the welded part of the stopper may come off and be damaged during use.

  SUMMARY OF THE INVENTION An object of the present invention is to reduce the number of parts and the number of processing steps and improve the reliability in use of a stopper for supporting a spring support in a spring load adjusting device for a hydraulic shock absorber.

  According to the first aspect of the present invention, a piston rod is slidably inserted into a cylinder, a fixing member is provided on the cylinder side or the piston rod side, and the cylindrical member is supported on the outer periphery of the fixing member in a non-rotating state. In the spring load adjusting device for a hydraulic shock absorber, the cylinder is provided with a stopper, and a spring support that is rotatably fitted on the outer periphery of the cylinder member is provided with a plurality of engaging portions that selectively engage the stopper. The stopper is integrally formed with the member.

  According to a second aspect of the present invention, in the first aspect of the present invention, a notch extending in the cylinder axial direction is further provided on the outer periphery of the fixed member, and the non-rotating convex portion protruding from the inner periphery of the cylindrical member is provided in the notch. And a retaining ring is provided on the outer periphery of the fixed member, and the end of the cylinder member in the cylinder axial direction is latched to the retaining ring.

  According to a third aspect of the present invention, in the first aspect of the present invention, the fixing member can be engaged with or disengaged from the mounting member on the cylinder side or the piston rod side from the outside, and a protrusion protruding in the cylinder radial direction is provided on the outer periphery of the fixing member. The rotation stop notch provided in the cylinder member is engaged with the projection, and the end of the cylinder member in the cylinder axial direction is engaged with the upper surface of the fixed member.

  According to a fourth aspect of the present invention, in the first aspect of the present invention, the stopper of the cylindrical member is provided by bulging.

(Claim 1)
(a) The number of parts can be reduced by integrally forming the stopper on the cylindrical member.

  (b) The stopper can be integrally formed at the same time as the cylindrical member is formed, and the number of processing steps can be reduced.

  (c) The stopper is not peeled off from the cylindrical member even under a heavy load, and the load resistance is improved and the reliability in use is improved.

(Claim 2)
(d) By providing the fixing member with a notch and a retaining ring and providing the cylindrical member with a non-rotating projection, it is possible to improve the detachability of the cylindrical member and improve maintainability such as spring replacement.

(Claim 3)
(e) The fixing member can be engaged and disengaged, the protrusion is provided on the fixing member, and the non-rotating notch is provided on the cylindrical member, thereby improving the detachability of the cylindrical member and improving maintainability such as spring replacement.

(Claim 4)
(f) Since the stopper of the cylindrical member is provided by bulging, the protruding stopper can be bulged and formed outward at the axial intermediate portion of the cylindrical member. There is no inconvenience that the cylindrical member formed with this stopper cannot be tilted in the axial direction after forming.

  1 is a sectional view showing a hydraulic shock absorber, FIG. 2 is a sectional view showing a spring load adjusting device, FIG. 3 is a side view of FIG. 2, FIG. 4 is a bottom view of FIG. (A) is a cross-sectional view, (B) is a side view, (C) is a bottom view, FIG. 6 shows a cylindrical member, (A) is a top view, and (B) is a cross section taken along line BB in (A). 7 is a sectional view showing a modification of the spring load adjusting device, FIG. 8 is a side view of FIG. 7, FIG. 9 is a mounting member, (A) is a front view, (B) is a top view, and FIG. Shows a fixing member, (A) is a top view, (B) is a sectional view taken along line BB in (A), FIG. 11 shows a cylindrical member, (A) is a sectional view, and (B) is a side view. FIG.

Example 1 (FIGS. 1 to 6)
As shown in FIG. 1, the hydraulic shock absorber 10 has a hollow piston rod 12 inserted into a cylinder 11, and a suspension spring 13 is interposed between the cylinder 11 and the piston rod 12.

  The cylinder 11 includes a vehicle body side mounting member 14, and the piston rod 12 includes an axle side mounting member 15 together with a lock nut 16. A spring support 17 is provided on the outer periphery of the cylinder 11, and a spring receiver 65 of a spring load adjusting device 60, which will be described later, is provided on the piston rod 12 side. A suspension spring is provided between the spring support 17 and the spring receiver 65. 13 is interposed. The elastic force of the suspension spring 13 absorbs the impact force that the vehicle receives from the road surface.

  The cylinder 11 includes a rod guide 21 through which the piston rod 12 passes. The rod guide 21 is liquid-tightly attached to the cylinder 11 via an O-ring 22 and allows the piston rod 12 to slide in a liquid-tight manner on an inner diameter portion including an oil seal 23, a bush 24 and a dust seal 25. The cylinder 11 is provided with a pressure side bumper 26 outside the rod guide 21, and at the time of maximum compression, the pressure side bumper 26 is abutted against a bumper stopper 27 provided in the piston rod 12 so that the maximum compression stroke can be regulated. The cylinder 11 includes a washer 28 </ b> A and an extension-side bump rubber 28 inside the rod guide 21.

  The hydraulic shock absorber 10 has a piston valve device (pressure side and extension side damping force generation device) 30 and a base valve device (pressure side damping force generation device) 50. The hydraulic shock absorber 10 suppresses expansion and contraction vibration of the cylinder 11 and the piston rod 12 due to the absorption of the impact force by the suspension spring 13 by the damping force generated by the piston valve device 30 and the base valve device 50.

  The piston valve device 30 has a valve stopper 31, a pressure side valve 32, a piston 33, an expansion side valve 34, and a valve stopper 35 mounted on the end of the piston rod 12 inserted into the cylinder 11, and these are fixed with nuts 36. is there.

  The piston 33 is in fluid-tight sliding contact with the inside of the cylinder 11 and divides the inside of the cylinder 11 into a piston-side oil chamber 38A in which the piston rod 12 is not accommodated and a rod-side oil chamber 38B in which the piston rod 12 is accommodated. The piston 33 includes a pressure side valve 32 and a pressure side passage 39 (not shown) that allows the piston side oil chamber 38A and the rod side oil chamber 38B to communicate with each other. The piston 33 includes an expansion side valve 34 and the piston side oil chamber 38A. The expansion side flow path 40 which enables communication with the rod side oil chamber 38B is provided.

The piston valve device 30 has a damping force adjusting device 41.
The damping force adjusting device 41 forms a bypass oil passage 42 that allows the piston-side oil chamber 38A and the rod-side oil chamber 38B to communicate with the Pillton rod 12, and a vertical hole that opens the bypass oil passage 42 into the piston-side oil chamber 38A. And a lateral hole opening in the rod side oil chamber 38B. The damping force adjusting device 41 is provided with a valve seat at the open end of the vertical hole of the bypass oil passage 42, and a push rod 43 formed with a needle valve 43 </ b> A facing the valve seat at the tip thereof is axially advanced and retracted in the hollow portion of the piston rod 12. It is freely and liquid-tightly inserted through an O-ring, and the opening area of the valve seat can be adjusted by the needle valve 43A.

  The push rod 43 has a base end portion extending from the piston rod 12 to the mounting member 15 side. The push rod 43 is protruded in a direction in which its base end is in contact with the adjustment rod 44 by a thrust force based on the hydraulic pressure of the piston-side oil chamber 38A.

  The adjusting rod 44 is provided on the mounting member 15 fixed to the outer end portion of the piston rod 12, and is screwed into a mounting hole drilled in a direction intersecting the axial direction of the push rod 43 and is externally screwed. The push rod 43 is supported so that it can be operated directly and abuts directly on the base end of the push rod 43 to advance and retract in the axial direction. The needle valve 43A of the push rod 43 adjusts the opening area of the valve seat of the bypass oil passage 42. The extension side damping force can be adjusted.

  The base valve device 50 connects the reservoir 51 to the cylinder 11, partitions the interior of the reservoir 51 into a pressurized gas chamber and an oil chamber by a partition member, and connects the piston side oil chamber 38 </ b> A of the cylinder 11 and the oil chamber of the reservoir 51. A compression-side damping force generation mechanism is provided in the communication area between the two.

Therefore, the hydraulic shock absorber 10 performs a damping action as follows.
(When compressed)
The oil in the piston side oil chamber 38A flows into the rod side oil chamber 38B through the pressure side flow path 39, and this oil deflects and deforms the pressure side valve 32 to obtain a pressure side damping force. At the same time, the oil corresponding to the volume of the piston rod 12 entering the cylinder 11 is discharged from the piston-side oil chamber 38A to the oil chamber of the reservoir 51, and is provided between the piston-side oil chamber 38A and the oil chamber of the reservoir 51. The compression side damping force generating mechanism that generates the compression side damping force generates the compression side damping force.

(When stretched)
When the relative speed between the cylinder 11 and the piston rod 12 is low, the oil in the rod side oil chamber 38B passes through the bypass passage 42 of the piston rod 12 whose opening is adjusted by the needle valve 43A of the adjustment rod 43, and the piston side oil. It flows into the chamber 38A, and the expansion side damping force is obtained by the throttle resistance by the needle valve 43A during this period. Further, when the relative speed between the cylinder 11 and the piston rod 12 is medium to high, the oil in the rod side oil chamber 38B passes through the extension side flow path 40 and bends and deforms the extension side valve 34 to flow into the piston side oil chamber 38A. Get the extension damping force. At this time, the oil corresponding to the retracted volume of the piston rod 12 retracting from the cylinder 11 is insufficient, and this insufficient oil is quickly supplied from the oil chamber of the reservoir 51 to the piston-side oil chamber 38A.
The expansion and contraction vibration of the hydraulic shock absorber 10 is suppressed by the damping force on the compression side and the extension side.

  When the hydraulic shock absorber 10 is most compressed, a buffering action at the time of the most compression is achieved by a collision between the bumper 26 on the cylinder 11 side and the bumper stopper 27 on the piston rod 12 side. When the hydraulic shock absorber 10 is fully extended, the bumper bar 28 on the cylinder 11 side and the valve stopper 31 on the piston rod 12 side abut against each other to provide a buffering action when fully extended.

  Hereinafter, the spring load adjusting device 60 for the suspension spring 13 provided in the hydraulic shock absorber 10 will be described.

  2 to 4, the spring load adjusting device 60 uses the upper end flange of the mounting member 15 of the piston rod 12 as a fixed member 61, and supports the cylindrical member 62 on the outer periphery of the fixed member 61 in a non-rotating state. The stoppers 63 are provided at two circumferential positions on the outer periphery of the member 62, and selectively engage with the stoppers 63 in the two circumferential regions on the lower surface of the spring support 64 that is rotatably mounted on the outer periphery of the cylindrical member 62. A plurality of engaging portions 64A are provided. The plurality of engaging portions 64A have a cam shape in which their heights are sequentially changed.

  The spring support 64 is provided with a separate (or integrated) spring receiver 65 on the flat surface of the upper surface, and the suspension spring 13 is supported by the spring receiver 65. A plurality of locking recesses 64B having a predetermined interval are provided on the outer periphery near the upper surface of the spring support 64, and the rotary operation tool can be locked to the locking recesses 64B.

  As shown in FIG. 5, the fixing member 61 includes a notch 61A extending in the axial direction at one location on the outer periphery, and an annular groove 61B continuous in the circumferential direction on the outer periphery. 66 can be disengaged. On the other hand, as shown in FIG. 6, the cylindrical member 62 includes an anti-rotation convex portion 62A that protrudes at one location on the inner periphery on the lower end side, and an annular retaining portion 62B that has an enlarged inner diameter at the lowermost end portion. And As a result, the spring load adjusting device 60 supports the cylindrical member 62 in a non-rotating state by locking the rotation preventing projection 62A on the inner periphery of the cylindrical member 62 to the notch 61A on the outer periphery of the fixing member 61. Further, the retaining portion 62 </ b> B at the lowermost end of the cylindrical member 62 is engaged with a retaining ring 66 provided on the outer periphery of the fixing member 61.

  Further, the spring load adjusting device 60 is integrally formed so that the above-described stopper 63 bulges radially outward at two locations on the outer periphery of the cylindrical member 62. The cylindrical member 62 integrally molds the stopper 63 together with the anti-rotation convex portion 62A and the annular retaining portion 62B by press-molding a circular tubular material. The stopper 63 is bulged and formed by bulging so as to form a protruding shape outward in the axial intermediate portion of the cylindrical member 62.

  In order to adjust the spring load in the spring load adjusting device 60, the spring support 64 is rotated with respect to the cylindrical member 62, and the engaging portion 64A of the spring support 64 that engages with the stopper 63 of the cylindrical member 62 is changed. The spring load corresponding to the height of the selected engaging portion 64A is obtained.

  In order to replace the spring in the spring load adjusting device 60, the suspension spring 13 is slightly contracted so that no spring force acts on the spring support 64, and the cylindrical member 62 is slightly raised in the axial direction with respect to the fixed member 61 and stopped. The ring 66 is removed, and then the cylinder member 62 is removed downward from the fixing member 61 and the mounting member 15 while the rotation preventing projection 62A of the cylinder member 62 is moved downward along the notch 61A of the fixing member 61. The support body 64 is removed, and the suspension spring 13 can be removed.

According to the present embodiment, the following operational effects can be obtained.
(a) By integrally forming the stopper 63 on the cylindrical member 62, the number of parts can be reduced.

  (b) The stopper 63 can be integrally formed at the same time as the cylindrical member 62 is formed, and the number of processing steps can be reduced.

  (c) The stopper 63 is not peeled off from the cylindrical member 62 even under a heavy load action, and the load resistance is improved and the reliability in use is improved.

  (d) By providing the fixing member 61 with the notch 61A and the retaining ring 66 and providing the cylindrical member 62 with the anti-rotation convex portion 62A, it is possible to improve the detachability of the cylindrical member 62 and improve the maintainability such as spring replacement. .

  (e) Since the stopper 63 of the cylindrical member 62 is provided by bulge processing, the protruding stopper 63 can be bulged and formed outward at the axial intermediate portion of the cylindrical member 62. There is no inconvenience that the cylindrical member 62 formed with the stopper 63 cannot be inclined in the axial direction after forming.

Example 2 (FIGS. 7 to 11)
In the hydraulic shock absorber 10, the second embodiment is substantially different from the first embodiment in that a spring load adjusting device 70 is used instead of the spring load adjusting device 60. The adjusting rod 44 constituting the damping force adjusting device 41 of the second embodiment is substantially the same as the first embodiment although the form is different from that of the first embodiment.

  As shown in FIGS. 7 and 8, the spring load adjusting device 70 is provided with a fixing member 71 at the upper end portion of the mounting member 15 of the piston rod 12, and supports the cylindrical member 72 on the outer periphery of the fixing member 71 in a non-rotating state. Stoppers 73 are provided at two circumferential positions on the outer periphery of the cylindrical member 72, and each stopper 73 is selectively engaged with two circumferential areas on the lower surface of the spring support 74 fitted rotatably on the outer periphery of the cylindrical member 72. A plurality of engaging portions 74A are provided. The plurality of engaging portions 74A have a cam shape in which their heights are sequentially changed.

  The spring support 74 is provided with a separate spring receiver 75 on the flat surface of the upper surface, and the suspension spring 13 is supported by the spring receiver 75. A plurality of locking recesses 74B having a predetermined interval are provided on the outer periphery near the upper surface of the spring support 74, and the rotary operation tool can be locked in the locking recesses 74B.

  As shown in FIG. 10, the fixing member 71 has a disk shape and has a narrow slit 71B in a part of the center hole 71A. The central hole 71 </ b> A has a slightly larger diameter than the lock nut 16 of the mounting member 15, and the slit 71 </ b> B is wider than the piston rod 12 and narrower than the lock nut 16. With the mounting member 15 and the lock nut 16 fixed to the piston rod 12, the fixing member 71 is moved laterally from the radial direction of the piston rod 12 above the lock nut 16, and the slit 71B of the fixing member 71 is formed around the piston rod 12. The central hole 71A is positioned via. Next, the fixing member 71 is moved downward along the axial direction of the piston rod 12, the center hole 71A of the fixing member 71 is loaded around the lock nut 16 of the piston rod 12, and the lower surface of the disk of the fixing member 71 is attached to the mounting member. 15 is placed on the longitudinal seating surface 15B (FIG. 9) on both sides of the locknut seating surface 15A, and as a result, the fixing member 71 can be engaged with and disengaged from the mounting member 15 from the outside. The bumper stopper 27 is supported on the upper surface of the disk of the fixing member 71.

  As shown in FIG. 10, the fixing member 71 is provided with detents 71C on both sides in a direction perpendicular to the diameter passing through the slit 71B of the central hole 71A. The detents 71C are arranged on the upper surface of the disk of the fixing member 71. It protrudes below the lower surface of the disk of the fixing member 71 without projecting to the side. When the fixing member 71 is engaged with the mounting member 15, the front end surface of the detents 71 C on both sides engages with both side surfaces 15 C in the direction perpendicular to the diameter of the longitudinal seating surface 15 B of the mounting member 15, and the fixing member 71 is attached. The member 15 is prevented from rotating.

  As shown in FIG. 10, the fixing member 71 includes a protrusion 71 </ b> D that protrudes in the radial direction at one location on the outer periphery. On the other hand, as shown in FIG. 11, the cylindrical member 72 includes an annular retaining portion 72B having an enlarged inner periphery at the lower end portion, and a non-rotating notch 72A at one location on the outer periphery of the annular retaining portion 72B. . As a result, the spring load adjusting device 70 supports the cylindrical member 72 in a non-rotating state by locking the non-rotating notch 72A on the inner periphery of the cylindrical member 72 to the protrusion 71D on the outer periphery of the fixing member 71. Further, the lower end portion of the cylindrical member 72 is locked so that the lower end portion of the cylindrical member 72 is placed on the upper surface of the fixing member 71 while the annular retaining portion 72 </ b> B at the lower end portion of the cylindrical member 72 is put on the outer periphery of the fixing member 71.

  Further, the spring load adjusting device 70 is integrally formed so that the stopper 73 is bulged outward in the radial direction at two locations on the outer periphery of the cylindrical member 72. The cylindrical member 72 is integrally formed with a stopper 73 together with a non-rotating notch 72A and an annular retaining portion 72B by press-molding a circular tubular material.

  In the spring load adjusting device 70, in order to adjust the spring load, the spring support 74 is rotated with respect to the cylindrical member 72, and the engaging portion 74A of the spring support 74 engaged with the stopper 73 of the cylindrical member 72 is changed. The spring load corresponding to the height of the selected engaging portion 74A is obtained.

  In order to replace the spring in the spring load adjusting device 70, the suspension spring 13 is slightly contracted so that no spring force acts on the spring support 74, the cylindrical member 72 is separated upward from the fixing member 71, and then the fixing member. 71 is lifted above the lock nut 16 of the mounting member 15, and the fixing member 71 is moved laterally outward in the radial direction of the piston rod 12 and removed. Further, the cylindrical member 72 is removed downward from the attachment member 15, and at the same time, the spring support 74 is removed so that the suspension spring 13 can be removed.

According to the present embodiment, the following operational effects can be obtained.
(a) By integrally forming the stopper 73 on the cylindrical member 72, the number of parts can be reduced.

  (b) The stopper 73 can be integrally formed at the same time as the cylindrical member 72 is formed, and the number of processing steps can be reduced.

  (c) The stopper 73 is not peeled off from the cylindrical member 72 even under a high load action, and the load resistance is improved and the reliability in use is improved.

  (d) The fixing member 71 can be engaged and disengaged, the protrusion 71D is provided on the fixing member 71, and the cylindrical member 72 is provided with a non-rotating cutout 72A, thereby improving the detachability of the cylindrical member 72 and maintaining spring replacement and the like. Can be improved.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention. The fixing members 61 and 71 of the spring load adjusting devices 60 and 70 may be provided on the cylinder 11 side.

FIG. 1 is a sectional view showing a hydraulic shock absorber. FIG. 2 is a sectional view showing the spring load adjusting device. FIG. 3 is a side view of FIG. FIG. 4 is a bottom view of FIG. FIG. 5 shows a fixing member, (A) is a cross-sectional view, (B) is a side view, and (C) is a bottom view. 6A and 6B show a cylindrical member, where FIG. 6A is a top view and FIG. 6B is a cross-sectional view taken along line BB in FIG. FIG. 7 is a sectional view showing a modification of the spring load adjusting device. FIG. 8 is a side view of FIG. FIG. 9 shows an attachment member, (A) is a front view, and (B) is a top view. 10A and 10B show a fixing member, FIG. 10A is a top view, and FIG. 10B is a cross-sectional view taken along line BB in FIG. FIG. 11 shows a cylindrical member, (A) is a cross-sectional view, and (B) is a side view.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Hydraulic buffer 11 Cylinder 12 Piston rod 60, 70 Spring load adjustment apparatus 61, 71 Fixing member 61A Notch 71D Protrusion 62, 72 Cylindrical member 62A Non-rotation convex part 72A Non-rotation notch 63, 73 Stopper 64, 74 Spring support Body 64A, 74A Engaging portion 66 Retaining ring

Claims (4)

Insert the piston rod slidably into the cylinder,
A fixing member is provided on the cylinder side or piston rod side,
A cylindrical member is supported on the outer periphery of the fixed member in a non-rotating state,
A stopper is provided on the outer periphery of the cylindrical member,
In a spring load adjusting device for a hydraulic shock absorber, wherein a plurality of engaging portions that selectively engage with the stopper are provided on a spring support that is rotatably fitted on the outer periphery of a cylindrical member.
A spring load adjusting device for a hydraulic shock absorber, wherein a stopper is integrally formed with the cylindrical member. A notch extending in the cylinder axial direction is provided on the outer periphery of the fixing member, and the non-rotating convex portion protruding from the inner periphery of the cylindrical member is locked to the notch.
The spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein a retaining ring is provided on an outer periphery of the fixed member, and an end of the cylindrical member in the cylinder axial direction is engaged with the retaining ring. The fixing member can be engaged and disengaged from the outside to the mounting member on the cylinder side or the piston rod side,
Protrusion projecting in the cylinder radial direction is provided on the outer periphery of the fixing member, and the non-rotating notch provided in the cylindrical member is locked to the protrusion,
2. The spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein an end of the cylindrical member in the cylinder axial direction is locked to an upper surface of the fixed member.   The spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein the stopper of the cylindrical member is provided by bulging.

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