JP7032979B2 - Valves and shock absorbers - Google Patents

Description

The present invention relates to a valve and an improvement of a shock absorber provided with the valve.

Conventionally, the main valve case, the sub-valve case facing the main valve case, the main valve body for opening and closing the main passage formed in the main valve case, and the sub-valve case formed in the sub-valve case have been included in the valve. Some have a sub-valve body that opens and closes the passage, and the main passage and the sub-valve body are communicated with each other through a gap formed between the main valve case and the sub-valve case (for example, Patent Document 1, 2).

Then, in such a valve, a disk-shaped sub-valve case is press-fitted into the tubular socket portion provided in the main valve case to form a gap, and the sub-valve case is directly placed on the inner circumference of the socket portion. Some of them are brought into close contact with each other to seal between them (Patent Document 1). In addition, an O-ring is attached to the outer circumference of the sub-valve case that is inserted into the socket of the main valve case, and the O-ring is brought into close contact with both the main valve case and the sub-valve case to seal between them. There is (Patent Document 2).

According to the above configuration, for example, the distance between the main valve case and the sub valve case is changed by changing the number of stacked leaf valves or the plate thickness constituting the main valve body or the sub valve body, and the size of the void is increased. Even if it changes, it is possible to maintain a direct or indirect close contact state between the main valve case and the sub valve case via an O-ring or the like.

Japanese Unexamined Patent Publication No. 2016-173140 Japanese Unexamined Patent Publication No. 7-355185

However, when the main valve case and the sub-valve case are brought into close contact with each other by press-fitting, it is necessary to strictly control the dimensional tolerance of the press-fitting portion, which increases the manufacturing cost of the valve and the shock absorber provided with the valve.

When the O-ring mounted on the outer circumference of the sub-valve case is brought into close contact with both the main valve case and the sub-valve case, the sub-valve case is attached to the main valve case while compressing the O-ring mounted on the outer circumference of the sub-valve case. It is necessary to insert it into the socket part. 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 sub-valve case equipped with the O-ring is to be inserted into the socket part of the main valve case 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 part. It may be difficult to do. Therefore, when inserting the sub-sub disk equipped with the O-ring into the socket part of the main disk, it is necessary to apply a lubricant, and the application equipment and human resources are required. In this case, the valve and the valve are also required. The manufacturing cost of the shock absorber equipped with the above will increase.

Therefore, the present invention has been devised to solve such a problem, and even if the valve includes a main valve case and a sub-valve case, a valve and a valve that can reduce the manufacturing cost are provided. The purpose is to provide a equipped shock absorber.

The valve that solves the above problems is sandwiched between the main valve case and the sub-valve case facing the main valve case in an elastically deformed state, and is on the outer peripheral side of the gap formed between the main valve case and the sub-valve case. It is provided with a partition member having an annular flat spring portion that is pressed against both the main valve case and the sub valve case to seal between the main valve case and the sub valve case .

According to the above configuration, in order to maintain the close contact state between the main valve case and the sub valve case via the partition wall member, it is only necessary to elastically deform and interpose the disc spring portion between the main valve case and the sub valve case. good. Therefore, strict control of dimensional tolerances is not required, and no lubricant application equipment or human resources are required, so that the valve manufacturing cost can be reduced.

Further, in the above valve, it is preferable that the sub-valve case is laminated on the main valve case and the disc spring portion is arranged so as to be compressed in the laminating direction of the main valve case and the sub-valve case. According to this configuration, the disc spring portion can be easily brought into close contact with both the main valve case and the sub valve case, and the valve can be easily manufactured.

Further, in the above valve, the main valve case and the sub valve case are each formed in an annular shape and mounted on the outer periphery of the mounting shaft, and the partition wall member includes the annular mounting portion, and the outer periphery of the mounting shaft is provided via the mounting portion. It should be fixed to. According to this configuration, the main valve case, the sub-valve case, and the partition wall member can be prevented from being displaced in the direction orthogonal to the mounting shaft by the mounting shaft, so that the assembling property of the valve can be improved.

Further, the valve may be configured to have a plurality of disc springs in which disc spring portions are laminated. According to this configuration, the stroke length of the disc spring portion can be secured and the adjustment allowance for the size of the gap can be increased.

Further, the shock absorber includes a cylinder, a rod that is movably inserted into the cylinder in the axial direction, and the valve. It is good to give resistance with a valve. According to this configuration, when the shock absorber expands and contracts and the cylinder and the rod move relative to each other in the axial direction, the damping force due to the resistance of the valve can be exerted. Further, the shock absorber comprises a cylinder, a rod movably inserted into the cylinder, and a valve, the valve facing the main valve case and the main valve case, between the main valve case. A sub-valve case with a gap formed in the main valve case, a main valve body formed in the main valve case to open and close the main passage leading to the gap, and a sub-valve formed in the sub-valve case to open and close the sub-passage leading to the gap. A partition member having an annular flat spring portion that is sandwiched between the body and the main valve case and the sub-valve case in an elastically deformed state and pressed against both the main valve case and the sub-valve case on the outer peripheral side of the gap. The main valve case and sub-valve case are connected to the rod to form a piston by giving resistance to the flow of liquid generated when the cylinder and the rod move relative to each other in the axial direction. The sub-valve body is set to open at a piston speed lower than the piston speed when the body opens, and the partition wall between the main valve case and the sub-valve case while the sub-valve body is closed. It may be configured to be sealed with a member.

According to the valve of the present invention and the shock absorber provided with the valve, the manufacturing cost can be reduced even when the main valve case and the sub valve case are provided.

It is a vertical sectional view which showed the shock absorber provided with the damping valve which is the valve which concerns on one Embodiment of this invention. It is a vertical sectional view showing a part of FIG. 1 enlarged. (A) is a sectional view taken along line XX of (b). (B) is a plan view which showed the partition wall member of the damping valve which is a valve which concerns on one Embodiment of this invention. It is a partially enlarged vertical sectional view which showed the 1st modification of the partition wall member in the damping valve which is a valve which concerns on one Embodiment of this invention. It is a partially enlarged vertical sectional view which showed the 2nd modification of the partition wall member in the damping valve which is a valve which concerns on one Embodiment of this invention.

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 valve according to the embodiment of the present invention is a damping valve V embodied in the piston portion of 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 buffer D shown in FIG. 1 are simply referred to as "upper" and "lower" unless otherwise specified.

The attachment target of the shock absorber provided with the valve according to the present invention is not limited to the vehicle and can be appropriately changed. Of course, the top and bottom of the shock absorber 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 two valve cases held by nuts 30 on the outer periphery of the mounting shaft 3a provided at the tip of the piston rod 3. Hereinafter, in order to distinguish between the two valve cases, the valve case in which the main valve bodies 6 and 7 described later are laminated is the main valve case 4, and the other valve case to which the sub valve body 8 described later is attached is the sub valve case 5. And.

As described above, the piston 2 of the present embodiment 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. There is. Hereinafter, the configuration of the damping valve V will be described.

As shown in FIG. 2, the main valve case 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 (extension side chamber) of the main body portion 4a is laminated. 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 side of the main valve case 4 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 main valve case 4 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. ..

Subsequently, the sub-valve case 5 is laminated on the lower side (compression side chamber L2 side) of the main valve body 6 on the extension side, and is upward from the annular disk portion 5a and the upper end inner peripheral portion of the disk portion 5a. An annular boss portion 5b that protrudes, an annular case portion 5c that protrudes downward from the outer peripheral portion of the lower end of the disk portion 5a, and an annular case portion that protrudes radially inward (center side of the shock absorber D) from the tip of the case portion 5c. Including the facing portion 5d of.

Further, on the outer peripheral side of the disc portion 5a from the boss portion 5b, a communication hole 5e that opens to the inner peripheral side of the case portion 5c and penetrates the disc portion 5a in the axial direction is formed. Further, the valve stopper 80 is housed in the case portion 5c, 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 sub-valve case 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 sub-valve case 5 is a fixed end 8b that does not move with respect to the sub-valve case 5. .. Further, the outer peripheral surface of the central leaf valve 8a located at the outer peripheral end (outer peripheral end) of the sub valve body 8 becomes a free end 8c that can move up and down (both sides in the axial direction) with respect to the sub valve case 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 5f formed on the inner circumference of the facing portion 5d 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 5f. 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 5f 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 5f, 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 5f. Then, in the present embodiment, the communication hole 5e and the sub-passage 5g having the inner peripheral portions of the case portion 5c and the facing portion 5d and communicating with each other above and below the sub-valve case 5 are configured, and the sub-valve body 8 is configured. Although the sub-passage 5g is not completely closed, the sub-passage 5g 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 body 8 is not limited to three, and the sub-valve body may be detached and seated on the valve seat formed in the sub-valve case 5. 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 gap K is formed between the disc portion 5a of the sub-valve case 5 facing each other and the main body portion 4a of the main valve case 4. Then, the circumference of the gap K is surrounded by the skirt portion 4b of the main valve case 4 and the partition wall member 9, and the main passages 4c and 4d on the extension side and the compression side and the sub passage 5g can communicate with the gap K, respectively. There is. In other words, the extension side main passage 4c and the sub-passage 5g, and the compression side main passage 4d and the sub-passage 5g are communicated with each other through the gap K, respectively.

In the present embodiment, the partition wall member 9 is configured to have two disc spring members 90 and 91. As shown in FIG. 3, each disc spring member 90, 91 is formed by bending an annular thin plate, and the annular disc springs 90a, 91a located at the outer peripheral end and the inner circumference of each disc spring 90a, 91a. Includes annular flat plate-shaped extension portions 90b and 91b connected to the above.

The disc springs 90a and 91a are annular flat plate-shaped contact portions 90c and 91c, respectively, and a truncated cone ring that is connected to the inner circumferences of the contact portions 90c and 91c and is gradually reduced in diameter toward the extension portions 90b and 91b. The tapered portions 90d and 91d of the above are included. The disc spring portion 9a is composed of the pair of disc springs 90a and 91a, and when the disc spring portion 9a is compressed and elastically deformed, the contact portions 90c and 91c of the tapered portions 90d and 91d and The tilt angle with respect to the extension portions 90b and 91b changes.

Further, the extension portions 90b and 91b of the disc spring members 90 and 91 are joined by spot welding, and the pair of extension portions 90b and 91b form an annular mounting portion 9b. The piston rod 3 can be inserted into the central portion of the mounting portion 9b, and the partition wall member 9 is mounted on the outer periphery of the mounting shaft 3a of the piston rod 3 via the mounting portion 9b.

More specifically, the outer diameter of the mounting shaft 3a in the piston rod 3 is smaller than the outer diameter immediately above the mounting shaft 3a, and an annular step 3b is formed at the end of the mounting shaft 3a. Then, the partition wall member 9 is fixed to the piston rod 3 together with the main valve case 4, the sub valve case 5, etc. in a state where the inner peripheral portion of the mounting portion 9b is sandwiched between the step 3b and the nut 30 (FIG. 2). ).

Further, as shown in FIG. 3, through holes 90e and 91e penetrating in the axial direction are formed in the extension portions 90b and 91b of the disc spring members 90 and 91. Therefore, even when the partition wall member 9 is fixed to the piston rod 3 as in the present embodiment, the gap K is not partitioned by the partition wall member 9. In FIG. 3B, three arcuate through holes 90e and 91e are formed in the circumferential direction, but the positions, numbers, and shapes of the through holes 90e and 91e are not shown and may be appropriately changed. can.

Then, as shown in FIG. 2, when the partition wall member 9 is attached to the outer periphery of the piston rod 3, the disc spring portion 9a is compressed between the lower end of the skirt portion 4b and the upper end outer peripheral portion of the disc portion 5a. Elastically deforms. As a result, the contact portions 90c and 91c (FIG. 3) of the disc spring members 90 and 91 are elastically pressed against the skirt portion 4b and the disc portion 5a to be in close contact with each other.

In the state where the disc spring portion 9a is in close contact with the skirt portion 4b and the disc portion 5a in this way, the space between the skirt portion 4b and the disc portion 5a is closed by the partition wall member 9, and the liquid in the gap K is the main valve case. The partition wall member 9 can prevent leakage from between the 4 and the sub-valve case 5.

Hereinafter, the operation of the shock absorber D provided with the damping valve (valve) V 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 5f. 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 into the void K from the extension side chamber L1 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 5e and the inner peripheral portion of the case portion 5c flow downward in the middle of FIG. 2 from the gap P formed between the free end 8c of the auxiliary valve body 8 facing each other and the facing surface 5f 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 5f. It flows into the 5c, flows upward in the communication hole 5e and the gap K 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 5f 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 5f 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 sub-valve body 8 is bent upward or downward, and of course, the main valve body 6 on the extension side is extended. 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 main valve case 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 main valve case 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 operation and effect of the damping valve (valve) V according to the present embodiment and the shock absorber D provided with the damping valve V will be described.

The damping valve (valve) V according to the present embodiment includes a main valve case 4 and a sub-valve case 5 facing the main valve case 4 and having a gap K formed between the main valve case 4 and the main valve case 4. Main passages 4c and 4d formed in the main valve case 4 and leading to the gap K, main valve bodies 6 and 7 for opening and closing the main passages 4c and 4d, and sub-passages formed in the sub-valve case 5 and leading to the gap K. It includes 5 g, a sub-valve body 8 that opens and closes the sub-passage 5 g, and a partition wall member 9 that is sandwiched between the main valve case 4 and the sub-valve case 5 in an elastically deformed state. The partition wall member 9 has an annular disc spring portion 9a that is pressed against both the main valve case 4 and the sub valve case 5 on the outer peripheral side of the gap K.

According to the above configuration, for example, the size of the gap K (length in the vertical direction in FIG. 2) is 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 press the disc spring portion 9a against both the main valve case 4 and the sub valve case 5 with a pressing force (load) equal to or higher than a predetermined value. Therefore, even if the size of the gap K changes, the gap K is maintained in close contact with the main valve case 4 and the sub-valve case 5 via the disc spring portion 9a on the outer peripheral side of the gap K. Can seal the outer circumference of.

Further, according to the above configuration, the main valve case 4 and the sub valve case 5 are brought into close contact with each other via the disc spring portion 9a. When the disc spring portion 9a is used as described above, it is easier to secure the stroke length in a state of being in close contact with both the main valve case 4 and the sub valve case 5 as compared with the case where the rubber sheet (ring) is used. Therefore, it is possible to secure an adjustment allowance for the size of the gap K.

Further, according to the above configuration, in maintaining the close contact state between the main valve case 4 and the sub valve case 5 on the outer peripheral side of the gap K, a disc spring portion 9a is provided between the main valve case 4 and the sub valve case 5. All you have to do is to insert it while elastically deforming it. Therefore, strict control of dimensional tolerances is not required, no lubricant application equipment and human resources are required, and the manufacturing cost of the damping valve V and the shock absorber D provided with the damping valve V can be reduced.

Further, the shock absorber D of the present embodiment includes a cylinder 1, a piston rod 3 movably inserted into the cylinder 1 in the axial direction, and a damping valve (valve) V. Then, the damping valve (valve) V imparts resistance to the flow of liquid generated when the cylinder 1 and the piston rod 3 move relative to each other in the axial direction. Therefore, when the shock absorber D expands and contracts and the cylinder 1 and the piston rod 3 move relative to each other in the axial direction, the damping force due to the resistance of the damping valve (valve) V can be exerted.

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 void K in the medium and high speed range, it does not affect the damping force in the medium and high speed range. The pressing force of the portion 9a 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, in the present embodiment, the sub-valve case 5 is laminated on the compression side chamber L2 side of the main valve case 4, but may be laminated on the extension side chamber L1 side, and the main valve case 4 and the sub-valve case 5 are laminated. The arrangement of can be changed as appropriate.

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 auxiliary 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 main valve case 4 and the sub valve case 5 are each formed in an annular shape and mounted on the outer periphery of the mounting shaft 3a of the piston rod 3. Further, the partition wall member 9 includes an annular mounting portion 9b which is connected to the inner circumference of the disc spring portion 9a and the mounting shaft 3a is inserted into the central portion thereof, and is fixed to the outer periphery of the mounting shaft 3a via the mounting portion 9b. There is. Therefore, the main valve case 4, the sub valve case 5, and the partition wall member 9 can be prevented from being displaced in the radial direction by the mounting shaft 3a, so that the assembling property of the damping valve V can be improved.

Further, in the present embodiment, the sub-valve case 5 is laminated on the main valve case 4, and the disc spring portion 9a is arranged so as to be compressed in the stacking direction of the main valve case 4 and the sub-valve case 5. .. The stacking direction is the stacking direction, and in the present embodiment, it corresponds to the axial direction of the mounting shaft 3a (vertical direction in FIG. 2). According to the above configuration, even if the main valve case 4, the sub-valve case 5, and the partition wall member 9 are displaced in the radial direction (direction orthogonal to the stacking direction) due to dimensional tolerances or the like, the entire outer circumference of the gap K is entirely covered. The disc spring portion 9a can be easily brought into close contact with both the main valve case 4 and the sub valve case 5 at the circumference, and the damping valve V can be easily manufactured.

Further, the disc spring portion 9a of the present embodiment is configured to have a pair of disc springs 90a and 91a laminated back to back. The number of stacked disc springs and the stacking method are arbitrary, but as in the present embodiment, when a plurality of stacked disc springs 90a and 91a are provided to form the disc spring portion 9a, the disc is prepared. The stroke length of the spring portion 9a can be increased. By increasing the stroke length of the disc spring portion 9a in this way, the adjustment allowance for the size of the gap K can be increased. The degree of freedom in designing the plate thickness can be improved.

The configuration of the partition wall member 9 is not limited to the above and can be changed as appropriate. For example, as in the partition wall members 9A and 9B shown in FIGS. May be configured. Further, as in the partition member 9B shown in FIG. 5, the disc spring 93 (disc spring portion) may be compressed in a direction orthogonal to the stacking direction of the main valve case 4 and the sub valve case 5.

Further, as shown in FIG. 4, when the mounting portion 9b of the partition wall member 9A is eliminated and the disc spring 92 is compressed in the stacking direction of the main valve case 4 and the sub valve case 5, the sub valve case is used. If the protrusion 5h is provided on the 5 and the partition member 9A is provided on the outer peripheral side of the protrusion 5h, it is possible to prevent the partition member 9A from being displaced in the left-right direction (diameter direction) in FIG.

Further, as shown in FIG. 5, when the mounting portion 9b of the partition wall member 9B is eliminated and the disc spring 93 is compressed in a direction orthogonal to the stacking direction of the main valve case 4 and the sub valve case 5. When a protrusion 4e is provided on the inner circumference of the main valve case 4 and a partition wall member 9B is provided between the protrusion 4e and the sub-valve case 5, the partition wall member 9B is displaced in the vertical direction (axial direction) in FIG. Can be prevented.

Further, the damping valve (valve) V according to the present embodiment is embodied in the piston portion mounted on the piston rod 3 of the shock absorber D, and is mounted on the outer periphery of the mounting shaft 3a provided on the piston rod 3. ing. However, the rod that goes in and out of the cylinder 1 does not necessarily have to be the piston rod 3 to which the piston 2 is attached, and the position where the damping valve V is provided is not limited to the piston portion.

For example, as described above, when the shock absorber has a reservoir chamber and the volume of the piston rod entering and exiting the cylinder is compensated in this reservoir chamber, the damping valve V is provided in the middle of the passage communicating the inside of the cylinder and the reservoir chamber. May be provided. In such a case, it goes without saying that the mounting shaft 3a of the damping valve (valve) V is arranged separately from the piston rod 3.

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, K ... void, V ... damping valve (valve), 1 ... cylinder, 3 ... piston rod (rod), 3a ... mounting shaft, 4 ... Main valve case, 4c ... extension side main passage (main passage), 4d ... compression side main passage (main passage), 5 ... sub valve case, 5g ... sub passage, 6 ... Extension side main valve body (main valve body), 7 ... compression side main valve body (main valve body), 8 ... sub-valve body, 9 ... partition member, 9a ... disc spring part, 9b ... Mounting part, 90a, 91a ... Belleville spring

Claims (6)

With the main valve case
A sub-valve case facing the main valve case and forming a gap between the main valve case and the sub-valve case.
A main valve body formed in the main valve case to open and close the main passage leading to the void,
A sub-valve body formed in the sub-valve case to open and close the sub-passage leading to the void,
It is sandwiched between the main valve case and the sub-valve case in an elastically deformed state, and is pressed against both the main valve case and the sub-valve case on the outer peripheral side of the gap between the main valve case and the sub-valve case. A valve characterized by comprising a partition member having an annular disc spring portion that seals between a sub-valve case. The sub-valve case is laminated on the main valve case.
The valve according to claim 1, wherein the disc spring portion is arranged so as to be compressed in the stacking direction of the main valve case and the sub valve case. The main valve case and the sub valve case are each formed in an annular shape and mounted on the outer periphery of the mounting shaft.
The partition wall member includes an annular mounting portion that is connected to the inner circumference of the disc spring portion and the mounting shaft is inserted into the central portion, and is fixed to the outer periphery of the mounting shaft via the mounting portion. The valve according to claim 1 or 2. The valve according to any one of claims 1 to 3, wherein the disc spring portion is configured to have a plurality of laminated disc springs. Cylinder and
A rod that is movably inserted into the cylinder in the axial direction,
The valve according to any one of claims 1 to 4 is provided.
The valve is a shock absorber characterized by providing resistance to the flow of liquid generated when the cylinder and the rod move relative to each other in the axial direction. Cylinder and
A rod that is movably inserted into the cylinder in the axial direction,
Equipped with a valve,
The valve has a main valve case, a sub-valve case facing the main valve case and a gap formed between the main valve case, and a main passage formed in the main valve case and leading to the gap. It is sandwiched between the main valve body that opens and closes, the sub-valve body that is formed in the sub-valve case and opens and closes the sub-passage leading to the gap, and the main valve case and the sub-valve case in an elastically deformed state. When the cylinder and the rod move relative to each other in the axial direction by having a partition member having an annular flat spring portion pressed against both the main valve case and the sub valve case on the outer peripheral side of the gap. Gives resistance to the flow of liquid that occurs in the
The main valve case and the sub valve case are connected to the rod to form a piston.
The auxiliary valve body is set to open at a piston speed lower than the piston speed at which the main valve body opens.
The partition wall member is a shock absorber that seals between the main valve case and the sub valve case while the sub valve body is closed.

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