JP6990141B2 - Hydraulic equipment - Google Patents

Description

The present invention relates to an improvement of a hydraulic device.

Conventionally, some hydraulic devices such as shock absorbers and hydraulic cylinders are provided with a partition member that forms a chamber separated from the liquid chamber in the liquid chamber formed inside the hydraulic chamber. For example, such a partition member includes a first member including a bottomed tubular socket portion and a disk-shaped second member inserted into the socket portion, and is between the first member and the second member. It forms a room (Patent Documents 1 and 2).

Then, in the partition wall member, the second member is directly press-fitted into the inner circumference of the socket portion of the first member (Patent Document 1), or an O-ring is attached to the outer periphery of the second member and press-fitted into the inner circumference of the socket portion. (Patent Document 2) seals between the first member and the second member.

Japanese Unexamined Patent Publication No. 2016-173140 Japanese Unexamined Patent Publication No. 2013-133896

However, when the second member is directly press-fitted into the first member to seal between them, it is necessary to strictly control the dimensional tolerance of the press-fitting portion, which increases the manufacturing cost of the hydraulic device.

Further, when sealing between the first member and the second member with the O-ring, it is necessary to insert the second member into the socket portion of the first member while compressing the O-ring mounted on the outer periphery of the second member. be. That is, the O-ring has a tightening allowance (crushing allowance) with respect to the socket portion. Furthermore, the O-ring is generally made of a rubber material or the like, and has a high coefficient of friction in a dry state.

Therefore, if the second member to which the O-ring is attached is to be inserted into the socket portion of the first member in a dry state, the surface of the O-ring may be damaged or the O-ring may be twisted and adhere to the inner circumference of the socket portion. It may be difficult to do. Therefore, when inserting the second member equipped with the O-ring into the socket part of the first member, it is necessary to apply a lubricant, and the application equipment and human resources are required, and the hydraulic pressure is also required in this case. The manufacturing cost of the equipment will increase.

Therefore, the present invention was devised to solve such a problem, and the partition wall member forming a room inside the hydraulic pressure device is configured to have a first member and a second member. Even in this case, the purpose is to provide hydraulic equipment that can reduce the manufacturing cost.

A hydraulic device that solves the above problems is configured to have a first member and a second member, and includes a partition wall member that forms a room between them, and the second member is elastically adhered to the first member. It includes an annular sealing member and a synthetic resin holding member in which a part of the sealing member is embedded.

According to the above configuration, when forming a room with the first member and the second member inside the hydraulic pressure device, it is only necessary to elastically deform the seal member of the second member and abut it against the first member. For this reason, strict control of dimensional tolerances is not required, and no lubricant application equipment or human resources are required.

Further, since the sealing member and the holding member are integrated, the number of parts of the hydraulic device does not increase and the assembling property can be improved. In addition, the holding member is made of synthetic resin, and a part of the sealing member is embedded in the holding member. Therefore, since the second member can be formed by insert molding or the like, the second member can be easily formed.

Therefore, according to the above configuration, even when the partition wall member forming the room inside the hydraulic pressure device has the first member and the second member, the manufacturing cost of the hydraulic pressure device is reduced. can.

Further, in the hydraulic device, it is preferable that the sealing member has an annular disc spring portion, and the disc spring portion is brought into close contact with the first member. According to this configuration, even when the size of the room changes, it is easy to maintain the disc spring portion in close contact with the first member with a pressing force (load) equal to or higher than a predetermined value.

Further, in the hydraulic device, it is preferable that the second member is laminated on the first member and the seal member is arranged so as to be compressed in the stacking direction of the first member and the second member. According to this configuration, even when the first member and the second member are displaced in the direction orthogonal to the stacking direction, the entire circumference of the seal member can be easily brought into close contact with the first member, and the hydraulic device can be easily manufactured. Can be done.

Further, in the hydraulic device, it is preferable that a bent portion is formed in a portion of the seal member embedded in the holding member. According to this configuration, it is possible to reliably prevent the sealing member from coming off the holding member.

Further, when the hydraulic pressure device includes a main valve body formed in the first member to open and close the main passage leading to the room, and a sub valve body formed in the second member and opening and closing the sub passage leading to the room. good. According to this configuration, the first member, the second member, the main valve body, and the sub-valve body form a damping valve, and the damping valve gives resistance to the flow of liquid generated during expansion and contraction of the hydraulic device to provide liquid. The pressure device can exert the damping force due to its resistance.

According to the hydraulic device of the present invention, even when the partition wall member forming the room inside thereof is configured to have the first member and the second member, the manufacturing cost can be reduced.

It is a vertical sectional view which showed the shock absorber which is the hydraulic pressure apparatus which concerns on one Embodiment of this invention. It is a vertical sectional view showing a part of FIG. 1 enlarged. It is a vertical sectional view showing a part of FIG. 2 in a further enlarged view. (A) is a partially enlarged vertical sectional view showing a first modification of a sealing member in a shock absorber which is a hydraulic device according to an embodiment of the present invention. (B) is a partially enlarged vertical sectional view showing a second modification of the seal member. (C) is a partially enlarged vertical sectional view showing a third modification of the seal member.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The same reference numerals, given throughout several drawings, indicate the same part or the corresponding part.

As shown in FIG. 1, the hydraulic device according to the embodiment of the present invention is the shock absorber D. The shock absorber D is interposed between the vehicle body of a vehicle such as an automobile and the axle. In the following description, for convenience of explanation, the upper and lower parts of the shock absorber D shown in FIG. 1 are simply referred to as "upper" and "lower" unless otherwise specified.

The mounting target of the shock absorber D is not limited to the vehicle and can be changed as appropriate. Of course, the top and bottom of the shock absorber D in the mounted state can be appropriately changed according to the mounting target. Specifically, the shock absorber D of the present embodiment may be attached to the vehicle in the same orientation as in FIG. 1, or may be attached to the vehicle upside down.

Subsequently, the specific structure of the shock absorber D will be described. As shown in FIG. 1, the shock absorber D has a bottomed cylindrical cylinder 1, a piston 2 slidably inserted into the cylinder 1, a lower end connected to the piston 2, and an upper end outside the cylinder 1. It is provided with a piston rod 3 that protrudes toward.

A bracket (not shown) is provided at the upper end of the piston rod 3, and the piston rod 3 is connected to one of the vehicle body and the axle via the bracket. On the other hand, a bracket (not shown) is also provided on the bottom portion 1a of the cylinder 1, and the cylinder 1 is connected to the other of the vehicle body and the axle via the bracket.

In this way, the shock absorber D is interposed between the vehicle body and the axle. When the wheels vibrate up and down with respect to the vehicle body, such as when the vehicle travels on an uneven road surface, the piston rod 3 moves in and out of the cylinder 1, the shock absorber D expands and contracts, and the piston 2 moves inside the cylinder 1. Move up and down (axial direction).

Further, the shock absorber D includes an annular cylinder head 10 that closes the upper end of the cylinder 1 and slidably supports the piston rod 3. On the other hand, the lower end of the cylinder 1 is closed by the bottom portion 1a. In this way, the inside of the cylinder 1 is a closed space. The free piston 11 is slidably inserted on the side opposite to the piston rod 3 when viewed from the piston 2 in the cylinder 1.

A liquid chamber L is formed on the upper side of the free piston 11 in the cylinder 1, and a gas chamber G is formed on the lower side. Further, the liquid chamber L is divided into an extension side chamber L1 on the piston rod 3 side and a compression side chamber L2 on the piston 2 side by the piston 2, and liquids such as hydraulic oil are contained in the extension side chamber L1 and the compression side chamber L2, respectively. It is filled. On the other hand, the gas chamber G is filled with a gas such as air or nitrogen gas in a compressed state.

Then, when the piston rod 3 retracts from the cylinder 1 when the shock absorber D is extended and the internal volume of the body-integrated cylinder of the retracted piston rod 3 increases, the free piston 11 moves upward in the cylinder 1 and the gas chamber G To expand. On the contrary, when the piston rod 3 invades the cylinder 1 when the shock absorber D contracts and the internal volume of the body-integrated cylinder of the invaded piston rod 3 decreases, the free piston 11 moves downward in the cylinder 1. Reduce the gas chamber G.

Instead of the free piston 11, a bladder, a bellows, or the like may be used to partition the liquid chamber L and the gas chamber G, and the configuration of the movable partition wall serving as the partition can be appropriately changed.

Further, in the present embodiment, the shock absorber D is a single rod, single cylinder type, and when the shock absorber D expands and contracts, the gas chamber G is expanded or contracted by the free piston (movable partition wall) 11 to enter and exit the cylinder 1. The volume of the piston rod 3 is compensated. However, the configuration for this volume compensation can also be changed as appropriate.

For example, the free piston (movable partition wall) 11 and the gas chamber G are eliminated, an outer shell is provided on the outer periphery of the cylinder 1 to make the shock absorber a double cylinder type, and liquid is stored between the cylinder 1 and the outer shell. A reservoir chamber may be formed and volume compensation may be performed in this reservoir chamber. Further, the reservoir chamber may be formed in a tank separately placed from the cylinder 1.

Further, piston rods may be provided on both sides of the piston to make the shock absorber a double rod type. In such a case, the volume compensation itself of the piston rod can be eliminated.

Subsequently, the piston 2 is configured to have a first member 4 and a second member 5 held by a nut 30 on the outer periphery of the piston rod 3. Then, a room R partitioned from the liquid chamber L is formed between the first member 4 and the second member 5. As described above, in the present embodiment, the piston 2 functions as a partition member for forming the room R inside the shock absorber D.

Further, in the present embodiment, the first member 4 is a main valve case in which the main valve bodies 6 and 7 described later are laminated, and the second member 5 is a sub valve case in which the sub valve body 8 described later is attached. .. As described above, the piston 2 of the present embodiment also functions as a valve case to which a valve body such as a main valve body 6 or 7 or a sub valve body 8 is attached, and constitutes a damping valve V together with the valve body or the like. ing. Hereinafter, the configuration of the damping valve V will be described.

As shown in FIG. 2, the first member 4 includes an annular main body portion 4a and a cylindrical skirt portion 4b protruding downward from the lower end outer peripheral portion of the main body portion 4a. The main body portion 4a is formed with main passages 4c and 4d on the extension side and the compression side which are opened on the inner peripheral side of the skirt portion 4b and penetrate the main body portion 4a in the axial direction. Further, on the lower side (compression side chamber L2 side) of the main body portion 4a, the extension side main valve body 6 that opens and closes the outlet of the extension side main passage 4c is laminated, and the upper side of the main body portion 4a (extension side chamber). On the L1 side), the main valve body 7 on the compression side that opens and closes the outlet of the main passage 4d on the compression side is laminated.

The main valves 6 and 7 on the extension side and the compression side are laminated leaf valves in which a plurality of elastically deformable leaf valves are laminated. The extension-side main valve body 6 opens when the shock absorber D is extended and the piston speed is in the medium-high speed range, and the extension-side main passage 4c is a liquid that goes from the extension-side chamber L1 to the compression-side chamber L2. Gives resistance to the flow of. On the other hand, the main valve body 7 on the compression side is opened when the shock absorber D is contracted and the piston speed is in the medium-high speed range, and the main passage 4d on the compression side is a liquid flowing from the compression side chamber L2 to the extension side chamber L1. Give resistance to the flow.

Further, among the plurality of leaf valves constituting the main valve bodies 6 and 7 on the extension side and the compression side, the outer peripheral portion of the first leaf valve located on the first member 4 side has notches 6a, respectively. 7a is formed. When the piston speed is in the low speed range and the main valve bodies 6 and 7 on the extension side and the compression side are closed, the liquid passes through the orifice formed by the notches 6a and 7a and the extension side chamber L1 and the compression side chamber L1 and the compression side chamber. Go back and forth with L2. Resistance is provided to the flow of the liquid by the orifices (notches 6a, 7a).

The orifice formed by the notches 6a and 7a allows bidirectional flow of the liquid. Therefore, one of the notches 6a and 7a formed in the main valve bodies 6 and 7 on the extension side and the compression side may be omitted. Further, the method of forming the orifice can be appropriately changed. For example, a stamp may be formed on the valve seat on which the main valve bodies 6 and 7 on the extension side or the compression side are taken off and seated, and an orifice may be formed by this stamp. Further, the orifice may be replaced with a choke. Further, the main valves 6 and 7 attached to the first member 4 which is the main valve case and for generating the damping force in the middle and high speed range in the shock absorber D may be other than the laminated leaf valve, for example, a poppet valve or the like. May be.

Subsequently, the second member 5 is laminated on the lower side (compression side chamber L2 side) of the main valve body 6 on the extension side. Further, the second member 5 has a holding member 50 made of synthetic resin and a metal or synthetic resin sealing member 51 integrated with the holding member 50 by insert molding, and is a part of the sealing member 51. Is embedded in the holding member 50.

More specifically, the holding member 50 includes an annular disk portion 50a, an annular boss portion 50b projecting upward from the upper end inner peripheral portion of the disk portion 50a, and an annular surface projecting downward from the lower end outer peripheral portion of the disk portion 50a. 50c, and an annular facing portion 50d projecting radially inward (center side of the shock absorber D) from the tip of the case portion 50c.

A communication hole 50e that opens to the inner peripheral side of the case portion 50c and penetrates the disc portion 50a in the axial direction is formed on the outer peripheral side of the disc portion 50a from the boss portion 50b. Further, the valve stopper 80 is housed in the case portion 50c, and the auxiliary valve body 8 is laminated on the lower side of the valve stopper 80.

In the present embodiment, the auxiliary valve body 8 is configured to have three laminated leaf valves and can be elastically deformed. The outer diameter of the central leaf valve 8a among these three leaf valves is larger than the outer diameter of the other leaf valves. The spacers 81 and 82 are interposed between the sub-valve body 8 and the valve stopper 80, and between the sub-valve body 8 and the nut 30, respectively.

In the present embodiment, each of the spacers 81 and 82 is an annular plate whose outer diameter is smaller than the outer diameter of each leaf valve constituting the auxiliary valve body 8, and the auxiliary valve body 8 has an inner peripheral portion thereof as a spacer. It is fixed to the second member 5 in a state of being sandwiched between 81 and 82. On the other hand, the outer peripheral side of the spacer 81, 82 of the auxiliary valve body 8 can move up and down (axially) with the outer peripheral edge of the contact portion between the spacer 81, 82 and the auxiliary valve body 8 as a fulcrum.

As described above, in the present embodiment, the end (inner peripheral end) on the inner peripheral side of the sub-valve body 8 mounted on the second member 5 which is the sub-valve case is a fixed end which does not move with respect to the second member 5. It is 8b. Further, the outer peripheral surface of the central leaf valve 8a located at the outer peripheral end (outer peripheral end) of the auxiliary valve body 8 becomes a free end 8c that can move up and down (both sides in the axial direction) with respect to the second member 5. ing.

Then, in an extremely low speed region where the piston speed is close to 0 (zero), such as when the shock absorber D starts to move, the auxiliary valve body 8 does not bend and is maintained in the initial mounting state (FIG. 2). As described above, in the state where the sub-valve body 8 is not bent, the free end 8c of the sub-valve body 8 faces the facing surface 50f formed on the inner circumference of the facing portion 50d with a predetermined gap P. The gap P becomes very narrow. More specifically, the opening area of the gap P in the initial mounting state of the auxiliary valve body 8 is larger than the opening area of all the orifices formed by the notches 6a and 7a formed in the main valve bodies 6 and 7 described above. Is also small.

On the other hand, when the piston speed is in the low speed range or the medium and high speed range, the outer peripheral portion of the auxiliary valve body 8 bends upward or downward, and the free end 8c shifts up and down from the facing surface 50f. Then, the opening area of the gap formed between the free end 8c of the auxiliary valve body 8 displaced vertically and the facing surface 50f becomes larger than the opening area of the orifice formed by the notches 6a and 7a.

Hereinafter, the sub-valve 8 opens so that the sub-valve 8 moves in a direction of increasing the opening area of the gap between the free end 8c and the facing surface 50f, and conversely, the sub-valve 8 has the free end 8c. It is assumed that the auxiliary valve body 8 closes when it moves in the direction of reducing the opening area of the gap between the facing surface 50f. Then, in the present embodiment, the communication hole 50e and the sub-passage 50g having the inner peripheral portions of the case portion 50c and the facing portion 50d and communicating with each other above and below the second member 5 are configured, and the sub-valve body 8 is configured. Although the sub-passage 50g is not completely closed, the sub-passage 50g can be opened and closed.

The configuration of the auxiliary valve body 8 is not limited to the above, and can be changed as appropriate. For example, the number of leaf valves constituting the sub-valve 8 is not limited to three, and the sub-valve may be detached and seated on the valve seat formed on the second member 5 which is the sub-valve case. .. Further, the auxiliary valve body 8 may be a valve other than the leaf valve, and may be, for example, a poppet valve or the like.

Subsequently, a room R is formed between the disc portion 50a of the second member 5 facing each other and the main body portion 4a of the first member 4 on the inner peripheral side of the skirt portion 4b. Then, the seal member 51 of the second member 5 is pressed against the lower end of the skirt portion 4b, whereby the lower end of the skirt portion 4b and the outer peripheral portion of the upper end of the disc portion 50a facing the lower end are sealed. ..

Further, the main passages 4c and 4d on the extension side and the compression side and the sub-passage 50g can communicate with each other in the room R, respectively. In other words, the extension side main passage 4c and the sub-passage 50g, and the compression side main passage 4d and the sub-passage 50g are communicated with each other via the room R, respectively.

As shown in FIG. 3, the seal member 51 of the present embodiment is formed by bending an annular thin plate, and has an annular disc spring portion 51a and an annular flat plate shape connected to the inner circumference of the annular disc spring portion 51a. Includes the base 51b of. Then, the base portion 51b is embedded in the holding member 50, whereby the sealing member 51 is held by the holding member 50.

In the present embodiment, the disc spring portion 51a is an annular flat plate-shaped contact portion 51c, and the tapered cone portion 51d which is connected to the inner circumference of the contact portion 51c and is gradually reduced in diameter toward the base portion 51b. And include.

Then, in a state where the first member 4 and the second member 5 are sandwiched and fixed between the step 3a of the piston rod 3 and the nut 30, the disc spring portion 51a is compressed and elastically deformed, and the tapered portion 51d. The tilt angle with respect to the contact portion 51c and the base portion 51b changes. At this time, the contact portion 51c (FIG. 3) of the seal member 51 is elastically pressed against the lower end of the skirt portion 4b to be in close contact with the skirt portion 4. Therefore, the space between the skirt portion 4b and the holding member 50 is closed by the sealing member 51, and the liquid in the room R is prevented from leaking.

Hereinafter, the operation of the shock absorber (hydraulic pressure device) D according to the present embodiment will be described.

When the shock absorber D is extended, the piston 2 moves upward in the cylinder 1 to compress the extension side chamber L1, and the liquid in the extension side chamber L1 passes through the extension side main valve body 6 and the auxiliary valve body 8 to the compression side. Move to room L2. Resistance is applied to the flow of the liquid by the extension side main valve body 6, the orifice formed by the notches 6a, 7a of each main valve body 6, 7 or the auxiliary valve body 8, so that the extension is performed. The pressure in the concubine L1 rises, and the shock absorber D exerts an extension damping force that hinders the extension operation.

On the contrary, when the shock absorber D contracts, the piston 2 moves downward in the cylinder 1 to compress the compression side chamber L2, and the liquid in the compression side chamber L2 passes through the auxiliary valve body 8 and the compression side main valve body 7. And move to the extension side chamber L1. Resistance is provided to the flow of the liquid by the main valve body 7 on the compression side, the orifice formed by the notches 6a and 7a of the main valve bodies 6 and 7, or the auxiliary valve body 8, so that the compression side chamber is provided. The pressure of L2 rises, and the shock absorber D exerts a compression side damping force that hinders the contraction operation.

Then, in the present embodiment, the main valve bodies 6 and 7 on the extension side and the compression side are opened according to the piston speed, and the outer peripheral portion (end portion on the free end 8c side) of the sub valve body 8 is flexed up and down. Therefore, the shock absorber D can generate a speed-dependent damping force depending on the piston speed.

More specifically, when the piston speed is in the extremely low speed range close to 0, the main valve bodies 6 and 7 on the extension side and the compression side are closed, and the auxiliary valve body 8 does not bend and its free end 8c faces the facing surface 50f. I'm letting you.

When the piston speed is in the extremely low speed region when the shock absorber D is extended, the liquid flows from the extension side chamber L1 into the chamber R through the notches 6a and 7a of the main valve bodies 6 and 7 on the extension side and the compression side. Then, the communication hole 50e and the inner peripheral portion of the case portion 50c flow downward in the middle of FIG. 2, and from the gap P formed between the free end 8c of the auxiliary valve body 8 facing each other and the facing surface 50f to the compression side chamber L2. And leak.

On the contrary, when the piston speed is in the extremely low speed region when the shock absorber D contracts, the case portion is formed from the gap P formed between the free end 8c of the auxiliary valve body 8 facing each other from the compression side chamber L2 and the facing surface 50f. It flows into the 50c, flows upward in the communication hole 50e and the chamber R in FIG. 2, and flows out from the notches 6a and 7a of the main valve bodies 6 and 7 on the extension side and the compression side to the extension side chamber L1.

As described above, the opening area of the gap P formed between the free ends 8c of the opposing auxiliary valve bodies 8 and the facing surface 50f is very small. Therefore, when the piston speed is in the extremely low speed range, the shock absorber D is used. , The damping force in the extremely low speed region due to the resistance when the liquid flows through the gap P can be exhibited.

Further, when the piston speed increases and the piston speed is high and the vehicle is in the low speed region after deviating from the extremely low speed region, the main valve bodies 6 and 7 on the extension side and the compression side are closed, but the outer peripheral portion of the sub valve body 8 (on the free end 8c side). The end) bends downward when it expands and upwards when it contracts, and the free end 8c of the auxiliary valve body 8 and the facing surface 50f shift up and down. Then, the opening area of the gap formed between them becomes larger than the opening area of the orifice formed by the notches 6a and 7a.

Therefore, when the piston speed is in the low speed range, the shock absorber D exerts a damping force in the low speed range due to the resistance of the orifice formed by the notches 6a and 7a of the main valve bodies 6 and 7 on the extension side and the compression side. It will be demonstrated. Then, when the piston speed shifts from the extremely low speed region to such a low speed region, the damping coefficient of the shock absorber D becomes smaller.

Further, when the piston speed is further increased and the sub-valve body 8 escapes from the low-speed range and is in the medium-high speed range, the outer peripheral portion of the auxiliary valve body 8 is of course bent upward or downward, and the main valve body 6 on the extension side is not only bent upward or downward. Opens, and when contracted, the main valve body 7 on the compression side opens.

In the present embodiment, when the extension side main valve body 6 is opened, the outer peripheral portion of the main valve body 6 bends downward, and the liquid can pass through the gap formed between the outer peripheral portion and the first member 4. It will be like. Similarly, when the main valve body 7 on the compression side is opened, the outer peripheral portion of the main valve body 7 bends upward, and the liquid can pass through the gap formed between the outer peripheral portion and the first member 4.

Therefore, when the piston speed is in the medium-high speed range, the shock absorber D exerts a damping force in the medium-high speed range due to the resistance of the gap created by opening the main valves 6 and 7 on the extension side or the compression side. become. Then, when the piston speed shifts from the low speed range to such a medium and high speed range, the damping coefficient of the shock absorber D becomes small.

In the middle of the medium and high speed range, the amount of deflection of the main valve bodies 6 and 7 on the extension side and the compression side may be restricted. In such a case, the damping coefficient increases again at the speed at which the amount of deflection of the main valve bodies 6 and 7 on the extension side and the compression side becomes maximum.

Hereinafter, the action and effect of the shock absorber (hydraulic pressure device) D according to the present embodiment will be described.

The shock absorber (hydraulic device) D according to the present embodiment includes a piston (partition wall member) 2 having a first member 4 and a second member 5, and the first member 4 and the second member. A room R is formed between 5 and 5. Then, the ring-shaped sealing member 51 in which the second member 5 is elastically adhered to the first member 4 and the holding member 50 made of synthetic resin in which a part (base 51b) of the sealing member 51 is embedded are included.

According to the above configuration, when the room R is formed by the first member 4 and the second member 5 inside the shock absorber D, the seal member 51 of the second member 5 is elastically deformed and abutted against the first member 4. Just need it. For this reason, strict control of dimensional tolerances is not required, and no lubricant application equipment or human resources are required.

Further, since the seal member 51 and the holding member 50 are integrated, the number of parts of the shock absorber D does not increase and the assembling property can be improved. In addition, the holding member 50 is made of synthetic resin, and a part of the sealing member 51 is embedded in the holding member 50. Therefore, since the second member 5 can be formed by insert molding or the like, the second member 5 can be easily formed.

Therefore, according to the above configuration, the piston (partition wall member) 2 forming the room R inside the shock absorber (hydraulic device) D is configured to have the first member 4 and the second member 5. Even if there is, the manufacturing cost of the shock absorber (hydraulic pressure device) D can be reduced.

Further, in the present embodiment, the shock absorber (hydraulic device) D is formed in the first member 4 and leads to the room R, and the main passages 4c and 4d and the main valve bodies 6 and 6 that open and close the main passages 4c and 4d. A sub-passage 50g formed in the second member 5 and leading to the room R, and a sub-valve 8 for opening and closing the sub-passage 50g are provided.

According to the above configuration, the first member 4, the second member 5, the main valve bodies 6, 7, and the sub-valve body 8 form a damping valve V, and the liquid generated when the shock absorber (hydraulic device) D expands and contracts. The damping valve V gives resistance to the flow of the buffer D, and the shock absorber D can exert the damping force due to the resistance.

Further, in the shock absorber D of the present embodiment, the main valve bodies 6 and 7 are used for generating the damping force in the medium and high speed range, and the sub valve body 8 is used for generating the damping force in the extremely low speed range. .. In this way, when the auxiliary valve body 8 is used for generating the damping force in the extremely low speed range, even if the liquid leaks from the room R in the medium and high speed range, it does not affect the damping force in the medium and high speed range. The adhesion of 51 to the first member 4 can be reduced.

However, the purpose of use of the main valve bodies 6 and 7 and the sub valve body 8 is not limited to the above, and can be changed as appropriate. Further, the second member 5 may be laminated on either the upper or lower side of FIG. 2 of the first member 4, and the main passage opened and closed by the main valve bodies 6 and 7 is formed in the second member 5 and the auxiliary valve body is formed. The sub-passage opened and closed by 8 may be formed in the first member 4.

Further, in the above description, in the region of piston speed, the sub-valve body 8 does not bend and the main valve bodies 6 and 7 are maintained in a closed state, which is an extremely low speed region, and the sub-valve body 8 bends mainly. The valve bodies 6 and 7 are divided into a low speed region which is a closed region and a medium and high speed region which is a region where the main valve bodies 6 and 7 open while the sub valve body 8 bends. However, the region of the piston speed may be divided in any way, and the threshold value of each region can be arbitrarily set.

Further, in the present embodiment, the seal member 51 has an annular disc spring portion 51a, and the disc spring portion 51a is brought into close contact with the first member 4. According to this configuration, for example, the size of the room R (length in the vertical direction in FIG. 2) can be increased by changing the number of stacked leaf valves or the plate thickness constituting the main valve bodies 6 and 7 or the sub valve body 8. Even if it changes, it is easy to bring the disc spring portion 51a into close contact with the first member 4 with a pressing force (load) equal to or higher than a predetermined value, and it is easy to maintain the sealed state.

Further, in the present embodiment, the second member 5 is laminated on the first member 4, and the seal member 51 is arranged so as to be compressed in the stacking direction of the first member 4 and the second member 5. The stacking direction is the stacking direction, and in the present embodiment, it corresponds to the axial direction (vertical direction in FIG. 2) of the piston rod 3 on which the first member 4 and the second member 5 are mounted. According to the above configuration, even when the first member 4 and the second member 5 are displaced in a direction orthogonal to the stacking direction due to a dimensional tolerance or the like, the entire circumference of the annular seal member 51 is in close contact with the first member 4. It is easy to make the shock absorber D easy to manufacture.

However, the configuration of the seal member 51 is not limited to the above and can be changed as appropriate. For example, the shape of the disc spring portion 51a may be changed as in the seal member 51A shown in FIG. 4A. Further, as in the seal members 51B and 51C shown in FIGS. 4B and 4C, the disc spring portion 51a may be compressed in a direction orthogonal to the stacking direction of the first member 4 and the second member 5.

Further, as in the seal members 51B and 51C shown in FIGS. 4B and 4C, the bent portion 51e may be formed in the base portion (the portion embedded in the holding member 50). In such a case, the bent portion 51e may be formed. , It is possible to surely prevent the seal members 51B and 51C from coming off from the holding member 50. And, of course, such a configuration may be applied to the base portion 51b of the seal members 51, 51A shown in FIGS. 3 and 4 (a).

Further, as long as the sealing members 51, 51A, 51B, 51C have a structure in which the sealing members 51, 51A, 51B, and 51C are elastically adhered to the first member 4, the portion in which the sealing members 51, 51A, 51B, and 51C are in close contact with each other does not necessarily have to be the disc spring portion 51a having a disc spring structure. Specifically, for example, a portion that is elastically brought into close contact with the first member 4 may be formed into a flat plate annular leaf spring portion, and the leaf spring portion may be flexed and deformed to be brought into close contact with the first member 4.

Further, in the present embodiment, the piston 2 functions as a partition member that forms a room R inside the shock absorber D. However, a partition member may be provided in addition to the piston 2. For example, as described above, when the shock absorber D is configured to have a tank separately from the cylinder, a partition wall member is provided in the tank, and the partition wall member is used to connect the room R and the reservoir chamber. It may be partitioned.

Further, in the present embodiment, the partition wall member separates the liquid chamber L and the chamber R formed inside the shock absorber D, but the partition wall member is a liquid other than the shock absorber (for example, a hydraulic cylinder or the like). It may be used for pressure equipment.

Although the preferred embodiments of the present invention have been described in detail above, they can be modified, modified, and modified as long as they do not deviate from the claims.

D ... shock absorber (hydraulic pressure device), R ... room, 2 ... piston (partition member), 4 ... first member, 4c ... extension side main passage (main passage), 4d ... Main passage on the compression side (main passage), 5 ... Second member, 6 ... Main valve body on the extension side (main valve body), 7 ... Main valve body on the compression side (main valve body) ), 8 ... Sub valve body, 50 ... Holding member, 50 g ... Sub passage, 51, 51A, 51B, 51C ... Seal member, 51a ... Belleville spring part, 51b ... Base (Part embedded in the holding member), 51e ... Bending part

Claims (5)

It is configured to have a first member and a second member, and includes a partition wall member in which a room is formed between the first member and the second member.
The second member is a hydraulic device including an annular sealing member that is elastically adhered to the first member and a holding member made of synthetic resin in which a part of the sealing member is embedded. The hydraulic device according to claim 1, wherein the seal member has an annular disc spring portion, and the disc spring portion is brought into close contact with the first member. The second member is laminated on the first member.
The hydraulic device according to claim 1 or 2, wherein the sealing member is arranged so as to be compressed in the stacking direction of the first member and the second member. The hydraulic device according to any one of claims 1 to 3, wherein a bent portion is formed in a portion of the seal member embedded in the holding member. A main valve body formed in the first member and opening and closing the main passage leading to the room,
The hydraulic device according to any one of claims 1 to 4, further comprising an auxiliary valve body formed on the second member and opening and closing an auxiliary passage leading to the room.

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