JP2009180355A - Hydraulic shock absorber - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a self-leveling type hydraulic shock absorber for preventing the mixture of foreign matters into an oil liquid and deformation caused by welding heat during welding sputtering. <P>SOLUTION: Into a cylinder 3 filled with the oil liquid, a piston 24 is fitted to which a piston rod 27 is connected. For vehicle height control, a damping force is generated by elongation and shrinkage side disc valves 31, 32 and an orifice 33 and the oil liquid is given and received between the cylinder 3 and an oil tank 10 by a self-leveling mechanism S. A bladder 12 of an oil tank 10 is clamped between an outside flange member 9 of a partition member 8 and a case 2. The partition member 8 is constituted by joining the annular outside flange member 9 pressed into a cylindrical body member 8A. The oil tank 10 is formed without depending on welding, thereby preventing the mixture of foreign matters and the deformation caused by heat during welding sputtering. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a hydraulic shock absorber provided with a vehicle height automatic adjustment mechanism mounted on a suspension device of a vehicle such as an automobile.

  In general, in a vehicle such as an automobile, a hydraulic shock absorber is mounted between a spring and an unsprung part of a suspension system so as to damp vibrations on the spring and unsprung so as to improve riding comfort and driving stability. I have to. However, in vehicles with relatively large loading weight, such as vans and wagons, the ride height and the loading / unloading of passengers greatly change the vehicle height and reduce ride comfort and handling stability. There are things to do. Furthermore, since the vehicle height on the rear wheel side is lowered due to the loading of the luggage (lowering the bottom), the optical axis of the headlight faces upward. For this reason, there is a demand for a suspension device that can automatically maintain a constant vehicle height regardless of the load capacity.

Therefore, as described in Patent Document 1, for example, pump means for supplying the oil in the oil tank into the cylinder by expansion and contraction of the piston rod, and from the pump means and the cylinder to the oil tank according to the expansion and contraction position of the piston rod. A return means for returning the pressure oil, and operating the pump means and the return means by utilizing the vibration of the suspension device during traveling to appropriately adjust the pressure in the cylinder and adjust the extension length of the piston rod to be constant. Thus, a so-called self-leveling hydraulic shock absorber that automatically maintains a certain standard vehicle height has been proposed.
JP-A-9-144801

  Further, in the self-leveling hydraulic shock absorber described in Patent Document 1, the oil tank separates the oil chamber and the gas chamber with a flexible film to reliably prevent gas from being mixed into the oil liquid. On the other hand, by reducing the height direction dimension and disposing it below the suspension spring on the outer periphery of the outer cylinder (case), the necessary volume is ensured by using dead space.

  However, the self-leveling hydraulic shock absorber described in Patent Document 1 has the following problems. In the oil tank, the annular member for holding the bladder that partitions the gas chamber and the oil chamber of the reservoir is fixed by welding, so there is a risk that foreign matter will be mixed into the oil liquid due to the occurrence of spatter during welding, Further, the annular member may be deformed by heat at the time of welding and the sealing performance may be reduced.

  The present invention has been made in view of the above points, and while reducing the number of parts while increasing the space efficiency and ensuring the necessary capacity of the reservoir and the oil tank, the foreign matter into the oil liquid by welding It is an object of the present invention to provide a self-leveling hydraulic shock absorber capable of preventing deformation due to mixing of heat and welding heat.

In order to solve the above-described problems, the present invention provides a cylinder in which oil is sealed, a piston slidably fitted in the cylinder, one end connected to the piston, and the other end connected to the cylinder. A piston rod extended outside, a damping force generating mechanism for generating a damping force by controlling the flow of the oil liquid generated by the movement of the piston, and the oil liquid and the gas sealed by being connected to the cylinder A reservoir, an oil tank that stores the oil liquid, and a self-leveling mechanism that adjusts the extension length of the piston rod by exchanging the oil liquid between the cylinder and the oil tank by expansion and contraction of the piston rod. In the hydraulic shock absorber
An outer cylinder is provided on the outer periphery of the cylinder to form a chamber between the cylinder and the outer cylinder, and the chamber is partitioned into an upper chamber and a lower chamber by a partition member, and one of the upper chamber and the lower chamber The reservoir is disposed on the other side, the oil tank is disposed on the other side, the interior of the lower chamber is partitioned into an oil chamber and a gas chamber by a flexible film, and the lower end of the cylinder communicates with the reservoir. An oil passage; a second oil passage communicating with the self-leveling mechanism and the oil tank; and the partition member is an annular outer flange member fitted to an inner peripheral portion of the outer cylinder, and the outer flange. It is comprised from the cylindrical main body member press-fit in the inner peripheral part of a member, It is characterized by the above-mentioned.

  According to the hydraulic shock absorber according to the present invention, in the hydraulic shock absorber provided with the self-leveling mechanism, the partition member that partitions the reservoir and the oil tank is configured by connecting the outer flange member and the main body member by press-fitting. Therefore, welding is not necessary, and there is no problem of spatter generation during welding and deformation due to heat.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.
As shown in FIG. 1, the hydraulic shock absorber 1 has a double cylinder structure in which a cylinder 3 is inserted into a substantially bottomed cylindrical case 2 (outer cylinder), and a seal is provided at the opening of the case 2. A member 4 is mounted and an annular chamber is formed between the case 2 and the cylinder 3. In the case 2, the lower end side is expanded by a bulge process or the like to form an expanded diameter portion 5, and a portion above the expanded diameter portion 5 is slightly expanded to form a spring support portion 6. . The bottom of the case 2 is closed by a cap member 7 being welded. A partition member 8 is inserted between the enlarged diameter portion 5 of the case 2 and the cylinder 3, and an outer flange member 9 formed at the upper end of the partition member 8 is fitted into the case 2, so that the case 2 An annular chamber between the cylinder 3 and the cylinder 3 is partitioned into an oil tank 10 in the lower chamber facing the expanded diameter portion 5 and a reservoir 11 in the upper chamber.

  The oil tank 10 is divided into an oil chamber 13 on the inner peripheral side and a gas chamber 14 on the outer peripheral side by a flexible bladder 12 (flexible film). An oil liquid is sealed in the oil chamber 13 of the cylinder 3 and the oil tank 10, a low pressure gas is sealed in the gas chamber 14 of the oil tank 10, and an oil liquid and a high pressure gas are sealed in the reservoir 11. Yes.

  An annular holding member 15 is interposed between the lower end portion of the partition member 8 and the cap member 7. A base guide 16 is fitted to the inner periphery of the holding member 15, and an oil chamber 17 is formed between the cap member 7 and the base guide 16. A base member 18 is interposed between the base guide 16 and the lower end portion of the cylinder 3, and an oil chamber 19 is formed between the base guide 16 and the base member 18. An annular member 20 is fitted between the lower end portion of the case 2 and the partition member 8. The annular member 20 is sandwiched and fixed by the edge portion of the cap member 7 and the step portion 8B on the outer periphery of the partition member 8. The bladder 12 of the oil tank 10 is clamped by the outer flange member 9 and the annular member 20 of the partition member 8.

  The oil chamber 17 between the cap member 7 and the base guide 16 is communicated with the oil chamber 13 of the oil tank 10 by an oil passage 21 provided in the annular member 20. The oil chamber 19 between the base guide 16 and the base member 18 communicates with the reservoir 11 via an annular oil passage 22 (first oil passage) formed between the cylinder 3 and the partition member 8. Further, the cylinder 3 and the oil chamber 19 (that is, the reservoir 11 through the annular oil passage 22) are communicated with each other by an orifice 23 (described later) formed by the base member 18.

  An annular piston 24 is slidably fitted in the cylinder 3, and the inside of the cylinder 3 is defined by the piston 24 as two chambers, a cylinder upper chamber 3A and a cylinder lower chamber 3B. One end of a hollow piston rod 27 is connected to the piston 24 by a piston bolt 25 and a nut 26. The other end side of the piston rod 27 is inserted through the rod guide 28 and the seal member 4 attached to the upper ends of the case 2 and the cylinder 3 and extends to the outside of the cylinder 3 and the case 2.

  The piston 24 is provided with an expansion side passage 29 and a contraction side passage 30 that allow the cylinder upper chamber 3A and the cylinder lower chamber 3B to communicate with each other, and controls the flow of oil in the extension side passage 29 and the contraction side passage 30. A damping force generation mechanism is provided that includes an extension side disk valve 31 that generates a damping force, a contraction side disk valve 32, and an orifice 33.

The piston rod 27 incorporates a sele-leveling mechanism S that adjusts the vehicle height by exchanging oil between the cylinder 3 and the reservoir 11 and the oil tank 10.
Next, the self-leveling mechanism S will be described. Inside the hollow piston rod 27, a pump tube 34 is inserted and fixed by a piston bolt 25 and a spring 35. A tubular pump rod 36 is disposed in the cylinder 3 along its axis, and the base end portion of the pump rod 36 is inserted into the opening of the base member 18 and connected to the base guide 16. A slight gap is provided between the pump rod 36 and the opening of the base member 18, and the orifice 23 that connects the cylinder lower chamber 3 </ b> B and the oil chamber 19 (that is, the reservoir 11) is formed by this gap. The tip of the pump rod 36 is slidably fitted into the pump tube 34 to form a pump chamber 37 in the pump tube 34. The oil passage 38 in the pump rod 36 is connected to the oil chamber 17 (therefore, the oil chamber 13 of the oil tank 10 via the oil passage 21) via an oil passage 38 </ b> A (second oil passage) provided in the base guide 16. It is communicated.

  The pump chamber 37 communicates with an oil passage 38 in the pump rod 36 via a check valve 39 provided at the tip of the pump rod 36, and the check valve 39 communicates from the oil passage 38 to the pump chamber 37. Only fluid flow is allowed. The pump chamber 37 is communicated with an annular oil passage 41 formed between the hollow piston rod 27 and the pump tube 34 via a check valve 40 provided at the end of the pump tube 34. In addition, the oil passage 41 communicates with the cylinder upper chamber 3A. The check valve 40 allows only the fluid flow from the pump chamber 37 to the oil passage 41.

  A groove 42 extending along the axial direction from the tip portion is formed in the side surface portion of the pump rod 36. Normally, the pump chamber 37 is communicated with the cylinder lower chamber 3B via the groove 42, When the piston rod 27 is shortened to a predetermined position, the pump tube 34 blocks communication between the groove 42 and the cylinder lower chamber 3B. A relief port 43 is formed in the side wall of the pump rod 36, and the relief port 43 is normally closed by the pump tube 34. When the piston rod 27 extends to a predetermined position, the relief port 43 extends from the pump tube 34. The cylinder lower chamber 3B is exposed and the oil passage 38 in the pump rod 36 is communicated.

  When the pressure on the oil chamber 19 (that is, on the high-pressure cylinder 3 and reservoir 11 side) rises excessively, the base guide 16 is opened and this pressure is opened to the chamber 17 side (that is, the low-pressure oil tank 10). A normally closed relief valve 44 is provided. An annular spring receiver 45 for receiving the lower end portion of a suspension spring (not shown) is fitted and fixed to the outer periphery of the spring support portion 6 of the case 2. And the hydraulic shock absorber 1 connects the front-end | tip part of the piston rod 27 to the vehicle body side (not shown), and connects the attachment eye 46 attached to the lower end part of the case 2 to the wheel side (not shown). The lower end of the suspension spring is received by a spring receiver 45 that is mounted on the suspension device of the vehicle.

Next, the structure of the oil tank 10 will be described in more detail.
The upper end of the bladder 12 is formed in a shape that fits into the outer peripheral groove 47 formed in the outer flange member 9 of the partition member 8, and is clamped between the outer peripheral groove 47 and the inner peripheral surface of the case 2. The space between the reservoir 11 and the oil chamber 13 and the gas chamber 14 of the oil tank 10 is sealed. Further, the outer flange member 9 of the partition member 8 is extended in the axial direction toward the reservoir 11 to form an outer peripheral groove 48, and an O-ring 49 is fitted into the outer peripheral groove 48, and the O-ring 49 causes the case to 2 and the outer flange member 9 are sealed. The lower end portion of the bladder 12 is formed in a shape that fits into the outer peripheral groove 50 formed in the annular member 20, and is clamped between the outer peripheral groove 50 and the inner peripheral surface of the case 2, and the oil chamber 13 and the gas. The space between the chambers 14 is sealed.

  As shown in FIG. 2, the partition member 8 includes a cylindrical main body member 8 </ b> A and an outer flange member 9, and the main body member is formed on the inner periphery of the cylindrical press-fit portion 51 formed at the lower end portion of the outer flange member 9. The upper end of 8A is press-fitted and integrated. On the inner peripheral surface of the intermediate portion of the outer flange member 9, an abutting portion 52 having a diameter reduced to the same diameter as the inner diameter of the main body member 8A is formed, and the front end portion of the main body member 8A is brought into contact with the end surface of the abutting portion 52. By making contact, the press-fitting allowance of the main body member 8A is defined. The main body member 8 </ b> A has a chamfered tip outer peripheral portion to form a tapered seal surface 53. An O-ring 54 (seal member) is interposed between the inner peripheral surface of the press-fit portion 51 of the outer flange member 9 and the end surface of the abutting portion 52 and the seal surface 53 of the main body member 8A. The outer flange member 9 and the coupling portion are sealed.

  As shown in FIGS. 3 to 6, the annular member 20 has a total of four notched portions 55 having a diameter increased every 90 degrees on the inner peripheral surface into which the cylindrical portion 8 </ b> A of the partition member 8 is inserted. The four arc-shaped oil passages 21 are formed by the gap between the notch 55 and the cylindrical portion 8A. In the four portions into which the cylindrical portion 8A between the cutout portions 55 of the annular member 20 is inserted, there are two (four in total) leaving both ends and the center in the circumferential direction on the inner peripheral portion of each end face. ) Recess 56 is formed. The annular member 20 can be made of a synthetic resin, for example, a polyamide reinforced with glass fibers.

Next, the operation of the present embodiment configured as described above will be described.
The sliding of the piston 24 in the cylinder 3 accompanying the expansion and contraction of the piston rod 27 generates an oil liquid flow between the cylinder upper and lower chambers 3A, 3B through the expansion side and contraction side oil passages 29, 30. Is controlled by the expansion and contraction side disk valves 31 and 32 and the orifice 33 to generate a damping force. At this time, the volume change in the cylinder 3 due to the entry and withdrawal of the piston rod 27 is compensated by the compression and expansion of the gas in the reservoir 11.

Next, the vehicle height adjustment function of the hydraulic shock absorber 1 will be described.
Normally, when the vehicle is empty, the extension length of the piston rod 27 is within a predetermined standard range. In this state, since the pump chamber 37 is communicated with the cylinder lower chamber 3B by the groove 42 of the pump rod 36, the pumping operation is not performed even if the piston rod 27 expands and contracts, and the vehicle height is maintained.

  When the vehicle height decreases due to an increase in the loaded load and the extension length of the piston rod 27 becomes shorter than a predetermined standard range, the groove 42 is blocked from the cylinder lower chamber 3B by the pump tube 34. In this state, when the piston rod 27 expands and contracts during traveling, the pump rod 36 is retracted and the pump chamber 37 is expanded and depressurized during the extension stroke, the check valve 39 is opened, and the oil chamber 13 of the oil tank 10 is opened. The oil liquid is introduced into the pump chamber 37 through the oil passage 21, the oil chamber 17, the oil passage 38 </ b> A, and the oil passage 38. During the contraction stroke, the pump rod 36 moves forward, the pump chamber 37 is contracted and pressurized, the check valve 40 is opened, and oil is supplied from the pump chamber 37 through the oil passage 41 to the cylinder lower chamber 3B. The rod 27 is extended. In this way, by repeating the pumping operation by the expansion and contraction of the piston rod 27 during traveling, the piston rod 27 is extended to raise the vehicle height. When the vehicle height reaches a predetermined standard range, the pump chamber 37 is communicated with the cylinder lower chamber 3A by the groove 42 as described above, and the pumping operation is released.

  Further, when the vehicle height rises due to a decrease in the loaded load and the extension length of the piston rod 27 exceeds a predetermined standard range, the relief port 43 of the pump rod 36 is exposed from the pump tube 34, and the relief port 43 By this, the cylinder lower chamber 3B and the oil passage 38 are communicated. As a result, the oil in the cylinder lower chamber 3B is returned to the oil chamber 13 of the oil tank 10, and the piston rod 27 is shortened to lower the vehicle height. When the vehicle height decreases and the extension length of the piston rod 27 is shortened to a predetermined standard range, the relief port 43 is blocked by the pump tube 34 and the vehicle height is maintained.

  In this way, by using the expansion and contraction of the piston rod 27 during traveling, the pumping operation and the returning operation are repeated as appropriate, so that the extension length of the piston rod 27 is adjusted to a predetermined standard range and the load is affected. The vehicle height can be automatically adjusted to a constant value.

  The oil tank 10 is supported by the spring receiver 45 with the oil chamber 13 and the gas chamber 14 separated from each other by the bladder 12 to reduce the size in the height direction while reliably preventing gas from being mixed into the oil liquid. It can be arranged below the suspension spring. Further, by forming the enlarged diameter portion 5 in the case 2, the volume can be sufficiently increased. Thereby, space efficiency can be improved by effectively using dead space. Since the reservoir 11 is disposed above the oil tank 10 and communicates with the cylinder 3 via the annular oil passage 22, the liquid level can be made sufficiently high, and the gas to the oil liquid can be taken. Can be prevented. Further, since the gas chamber 14 of the oil tank 10 is sealed by the bladder 12, the manufacturing process can be simplified by sealing the atmosphere as low-pressure gas during assembly.

  By forming the oil tank 10 with the expanded diameter portion 5 of the case 2, the number of parts can be reduced, and the number of manufacturing steps and the manufacturing cost can be reduced as compared with the conventional example described in Patent Document 1. it can. Further, the oil tank 10 is formed by clamping the bladder 12 by the partition member 8 and the annular member 20, not by welding. Therefore, the oil tank 10 is caused by mixing of foreign matter into the oil liquid due to the occurrence of welding spatter and welding heat. There is no problem of deformation.

  Since the oil tank 10 and the reservoir 11 are sealed by the O-ring 49 in addition to the upper end portion of the bladder 12, the pressure of the reservoir 11 that is increased by pumping does not directly act on the upper end portion of the bladder 12. It is possible to ensure sealing performance and to prevent the bladder 12 from coming off due to high pressure.

  Since the partition member 8 is configured by press-fitting the main body member 8A and the outer flange member 9, the shape of the press-fit portion is simple compared to the case where these are welded, and the manufacturing is easy. Further, there is no problem of spattering during welding and deformation due to heat. Further, the pressure of the high-pressure reservoir 11 acts on the outer flange member 9 of the partition member 8 from above, and the pressure of the low-pressure oil tank 10 acts. There is no problem of the omission of the press-fit portion between the main body member 8A and the outer flange member 9A.

  The annular member 20 does not need to be made of solid metal since high rigidity is not required because only the force due to the pressure of the low-pressure oil tank 10 acts on the outer circumferential groove 50 that holds the bladder 12. Further, it can be formed of a material having relatively low rigidity such as a synthetic resin or a hollow press-molded material.

  In the above embodiment, the reservoir 11 is disposed in the upper chamber on the outer periphery of the cylinder 3 and the oil tank 10 is disposed in the lower chamber. However, the oil tank is disposed in the upper chamber and the reservoir is disposed in the lower chamber. It is good also as a structure. In this case, the reservoir in the lower chamber is connected to the lower portion of the cylinder 3 via the oil passage 21 of the annular member 20, and the oil tank in the upper chamber is connected to the oil passage 38 of the pump rod 36 via the annular oil passage 22. In addition, an oil liquid passage may be formed at the bottom of the case 2.

1 is a longitudinal sectional view of a hydraulic shock absorber according to an embodiment of the present invention. It is a longitudinal cross-sectional view which expands and shows the partition member of the hydraulic shock absorber of FIG. It is a longitudinal cross-sectional view by the AA line in FIG. 5 which expands and shows the annular member of the hydraulic shock absorber of FIG. It is a longitudinal cross-sectional view by the AB line in FIG. 5 which expands and shows the annular member of the hydraulic shock absorber of FIG. It is a top view which expands and shows the annular member of the hydraulic shock absorber of FIG. It is a bottom view which expands and shows the annular member of the hydraulic shock absorber of FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Hydraulic shock absorber, 2 Case (outer cylinder), 3 Cylinder, 8 Partition member, 8A Main body member, 9 Outer flange member, 10 Oil tank, 11 Reservoir, 12 Bladder (flexible film), 13 Oil chamber, 14 Gas chamber , 22 Annular oil passage (first oil passage), 24 piston, 27 piston rod, 31 disc valve (damping force generating mechanism), 32 disc valve (damping force generating mechanism), 33 orifice (damping force generating mechanism), 38 oil Passage (second oil passage), 49 O-ring (sealing means), S self-leveling mechanism

Claims (6)

A cylinder filled with oil, a piston slidably fitted in the cylinder, a piston rod having one end coupled to the piston and the other end extending outside the cylinder, and the piston A damping force generation mechanism that generates a damping force by controlling the flow of the oil liquid generated by the movement of the oil, a reservoir that is connected to the cylinder and encloses the oil liquid and gas, an oil tank that stores the oil liquid, In a hydraulic shock absorber provided with a self-leveling mechanism that adjusts the extension length of the piston rod by exchanging oil between the cylinder and the oil tank by expansion and contraction of the piston rod,
An outer cylinder is provided on the outer periphery of the cylinder to form a chamber between the cylinder and the outer cylinder, and the chamber is partitioned into an upper chamber and a lower chamber by a partition member, and one of the upper chamber and the lower chamber The reservoir is disposed on the other side, the oil tank is disposed on the other side, the interior of the lower chamber is partitioned into an oil chamber and a gas chamber by a flexible film, and the lower end of the cylinder communicates with the reservoir. An oil passage; a second oil passage communicating with the self-leveling mechanism and the oil tank; and the partition member is an annular outer flange member fitted to an inner peripheral portion of the outer cylinder, and the outer flange. A hydraulic shock absorber comprising a cylindrical main body member press-fitted into an inner peripheral portion of the member. On the inner peripheral surface of the outer flange member, an abutting portion with which the front end portion of the press-fitted main body member abuts is formed, and on the outer peripheral portion of the front end of the main body member, a tapered seal surface is formed, 2. The hydraulic shock absorber according to claim 1, wherein a seal member is interposed between an inner peripheral surface and a butting portion of the outer flange member and a seal surface of the main body member. The hydraulic shock absorber according to claim 1 or 2, wherein the reservoir is disposed in the upper chamber, and the oil tank is disposed in the lower chamber. An annular member that is fitted between the outer cylinder and the main body member of the partition member and clamps one end of the flexible film, the annular member having a notch formed on an inner peripheral surface thereof; 4. The hydraulic shock absorber according to claim 3, wherein the oil chamber and the second oil passage are communicated with each other through a gap between a portion and a main body member of the partition member. The hydraulic shock absorber according to claim 1 or 2, wherein the oil tank is disposed in the upper chamber, and the reservoir is disposed in the lower chamber. An annular member that is fitted between the outer cylinder and the main body member of the partition member and clamps one end of the flexible film, the annular member having a notch formed on an inner peripheral surface thereof; The hydraulic shock absorber according to claim 5, wherein the oil chamber and the first oil passage are communicated with each other through a gap between a portion and a main body member of the partition member.

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