JP5390866B2 - valve - Google Patents

Description

  The present invention relates to an improved valve.

  Conventionally, this type of valve is embodied, for example, as a damping valve on the extension side of a piston portion of a hydraulic shock absorber for a vehicle. Specifically, two pressure chambers are separated in the hydraulic shock absorber. And a first annular leaf valve seated on a first annular valve seat installed on the outer periphery of an annular window through which a plurality of ports provided on the same circumference communicate with the piston, and the first A second leaf valve having an outer diameter larger than that of the first leaf valve seated on a second annular valve seat provided on the outer periphery of the annular valve seat is known.

  This valve is set so that the pressure in the pressure chamber upstream of the valve does not reach the valve opening pressure of the second leaf valve when the piston speed when the hydraulic shock absorber is extended is low. The second leaf valve is left seated on the second annular valve seat, and only the outer periphery of the first leaf valve is bent, and the hydraulic oil is supplied from the upstream pressure chamber to the first It moves between the leaf valve and the first annular valve seat, passes through the orifice stamped in the second annular valve seat, and moves to the downstream pressure chamber (see, for example, Patent Document 1). .

  Next, when the piston speed increases, not only the first leaf valve but also the second leaf valve bends to create a gap between the second annular valve seat and the hydraulic oil flows upstream. From the pressure chamber to the downstream pressure chamber through the space between the first leaf valve and the first annular valve seat and between the second leaf valve and the second annular valve seat.

  Since the valve configured as described above includes the first leaf valve that opens when the piston speed is low and the second leaf valve that opens when the piston speed becomes high, a hydraulic shock absorber is generated. The damping force can be raised linearly with respect to the piston speed, and good damping characteristics can be obtained.

JP-A-2-93136

  However, in the conventional valve configured as described above, it is essential to provide a double annular valve seat on the piston, and a specially-shaped piston must be used. A general-purpose valve disc set to a so-called independent port type having a plurality of valve seats individually surrounding the periphery of the valve cannot be adopted.

  Accordingly, the present invention has been developed to improve the above-described problems, and the object of the present invention is to provide a valve capable of obtaining good damping characteristics while employing a highly versatile valve disk. Is to provide.

In order to solve the above-described object, the problem-solving means of the present invention is a petal-type valve having a plurality of ports arranged on the same circumference and a plurality of surrounding portions individually surrounding the periphery of the open end of each port. A valve disc provided with a seat, an annular leaf valve stacked on the valve disc and seated on and away from the inner periphery of each valve seat, and an annular outer periphery of each valve seat disposed on the outer periphery of the leaf valve A leaf valve and a ring valve are seated directly on the valve seat, with a ring valve that is separated and seated on the side and an annular leaf spring that holds the ring valve and biases the ring valve toward the valve seat Then, the port is closed, and the leaf valve is allowed to bend by a predetermined amount independently of the leaf spring and starts to bend at a pressure smaller than that of the leaf spring when pressure is applied through the port .

According to the valve of the present invention, a general-purpose valve disc that is set to an independent port type in which each port is not communicated is used without using a specially shaped valve disc, and a buffer is used when the piston speed is in a low speed region. A damping force that rises linearly with respect to the piston speed can be generated in the container, and a good damping characteristic can be obtained.
That is, in the stroke in which the shock absorber is compressed, when the piston speed is in the low speed region, only the leaf valve is bent without bending the leaf spring.
Then, the fluid passes through a gap formed between the leaf valve and the side wall in the surrounding portion, and the valve generates a damping force that rises linearly with respect to the piston speed in the shock absorber.

  The damping characteristics can be adjusted by setting the pressure-receiving area of the leaf valve and ring valve, or the bending rigidity of the leaf valve, ring valve and leaf spring. Since it is not necessary to prepare for each damping characteristic to obtain a specially shaped valve disk, the manufacturing cost can be reduced.

It is a longitudinal cross-sectional view of the piston part of the shock absorber in which the valve in one embodiment was embodied. It is a top view of the piston which is a valve disc with which the valve in one embodiment was embodied. It is a partially expanded longitudinal cross-sectional view of the piston part which shows the state which only the leaf valve in the valve | bulb of one Embodiment bent. It is a partially expanded longitudinal cross-sectional view of the piston part which shows the state in which both the leaf valve and leaf | plate spring in one Embodiment bent.

  The valve structure of the present invention will be described below with reference to the drawings. As shown in FIGS. 1 and 2, the valve V in one embodiment is embodied as a damping valve on the pressure side of the piston portion of the shock absorber, and the pressure side chamber 42 and the extension side chamber arranged on the same circumference. 41, a plurality of ports 2 communicating with each other, and a valve seat 4 that individually surrounds the periphery of the open end of each port 2, and is slidably inserted into the cylinder 40 so that the inside of the cylinder 40 is extended with the extension side chamber 41. Piston 1 which is a valve disk partitioned into a pressure side chamber 42, an annular leaf valve 5 which is stacked on the piston 1 and is attached to and detached from the inner peripheral side of each valve seat 4, and an annular shape on the outer periphery of the leaf valve 5 A ring valve 6 disposed and seated on the outer peripheral side of each valve seat 4, and an annular leaf spring 7 that holds the ring valve 6 and biases the ring valve 6 toward the valve seat 4. Has been.

  On the other hand, a shock absorber in which the valve of the present invention is embodied is well known and will not be described in detail, but specifically, for example, a cylinder 40 and a head member for sealing the upper end of the cylinder 40 (FIG. A piston rod 8 that slidably passes through a head member (not shown), a piston 1 that is a valve disk that is inserted into the tip 9 of the piston rod 8 and is fixed to the tip 9, and a cylinder 40. An extension chamber 41 on the upper side, a pressure side chamber 42 on the lower side in FIG. 1 and a sealing member (not shown) that seals the lower end of the cylinder 40, and the cylinder 40 protrude from the cylinder 40. The cylinder 40 is configured to include a reservoir or an air chamber (not shown) that compensates for a change in the cylinder volume corresponding to the volume of the piston rod 8, and the cylinder 40 is filled with a fluid, specifically, for example, hydraulic oil.

  Further, in the above valve, when the piston 1 moves downward in FIG. 1 with respect to the cylinder 40 and the fluid passes through the port 2 and moves from the pressure side chamber 42 to the extension side chamber 41, the fluid A resistance is applied to the flow by a valve V to cause a predetermined pressure loss, thereby generating a predetermined compression side damping force in the shock absorber.

  In addition to the above-described port 2, the piston 1 is provided with a plurality of ports 3 that communicate the extension side chamber 41 and the pressure side chamber 42, and the inner periphery of the port 3 is fixed to the tip 9 of the piston rod 8. 2 is opened and closed by an annular leaf valve 10 stacked on the end surface of the piston 1 on the pressure side chamber 42 side, and the piston 1 moves upward in FIG. 3, when moving from the expansion side chamber 41 to the compression side chamber 42, a resistance is applied to the flow of the fluid by the leaf valve 10 to cause a predetermined pressure loss, and a predetermined expansion side damping force is applied to the buffer. It is supposed to be generated.

  Hereinafter, the valve will be described in detail. As shown in FIG. 1, the piston 1 serving as a valve disk is formed in an annular shape, and is opposite to the port 2 that allows fluid to pass from the compression side chamber 42 to the extension side chamber 41. And a port 3 that allows fluid to pass from the extension side chamber 41 to the compression side chamber 42.

  Further, a plurality of ports 2 and 3 are provided on the piston 1, and specifically six are shown in the figure, the ports 2 are arranged on the same circumference at equal intervals, and the ports 3 are also the same. Arranged at equal intervals on the circumference, the ports 2 and 3 are alternately arranged in the circumferential direction. The number of ports 2 and 3 can be set arbitrarily.

  Further, the piston 1 has an inner window portion 4a provided around the inner circumference through which the piston rod 8 is inserted, and an independent window which is an open end of the port 2 connected to the inner circumference seat portion 4a. 11 is provided with a petal-type valve seat 4 that has six surrounding portions 4b that individually surround the periphery of 11 and protrudes toward the extension side chamber 41 side. The surrounding portion 4b includes an arc-shaped inner wall 4c continuous with the inner peripheral sheet portion 4a, an arc-shaped outer wall 4d, and a pair of side walls 4e and 4f that connect the inner wall 4c and the outer wall 4d. The shapes of the inner wall 4c, the outer wall 4d, and the side walls 4e and 4f are not limited to those shown in FIG. 2, and may be any shape. Further, the piston 1 is provided with a petal-type valve seat 12 that individually surrounds the opening end of the port 3 on the pressure side chamber 42 side. That is, the ports 2 and 3 in the piston 1 are individually surrounded by the valve seats 4 and 12 and are not communicated with each other, and are set to a so-called independent port type.

  The piston 1 as a valve disc configured as described above includes a leaf valve 5, a ring valve 6, a spacer 13, a leaf spring 7, a spacer 14 and a valve stopper 15 stacked on the upper side in FIG. Together with the leaf valve 10 stacked below, it is assembled to the tip 9 of the piston rod 8 and fixed to the piston rod 8 by a piston nut 16.

  The leaf valve 5 is annular and is fixed to the tip 9 of the piston rod 8 inserted into the inner peripheral side as described above, and is seated on the inner peripheral side of the valve seat 4. Specifically, the outer diameter of the leaf valve 5 is set such that the outer peripheral edge faces at least the independent window 11 and can be seated on the side walls 4 e and 4 f of the surrounding portion 4 b of the valve seat 4. As a result, the leaf valve 5 semi-closes the port 2.

  As shown in FIG. 1, the ring valve 6 is thicker than the leaf valve 5 and has an inner diameter set to be equal to or larger than the outer diameter of the leaf valve 5. 4 is seated on the remaining outer peripheral side that is not closed by the leaf valve 5, and in detail, seats on the outer peripheral portion of the side walls 4e and 4f that are not seated by the leaf valve 5 of the surrounding portion 4b and the outer wall 4d. The outer diameter is set to a diameter at least capable of being seated on the outer wall 4d of the surrounding portion 4b, and the port 2 can be closed by seating on the valve seat 4 in cooperation with the leaf valve 5.

  Note that the leaf valve 5 and the ring valve 6 do not interfere with the attachment / detachment operation of the valve seat 4 with each other. Alternatively, an annular gap may be provided between the outer periphery of the leaf valve 5 and the inner periphery of the ring valve 6 so as not to hinder the function as a valve.

  Further, since the valve seat 4 protrudes toward the extension side chamber 41, even if the leaf valve 5 and the ring valve 6 are seated, only the port 2 is closed, and the open end of the extension side chamber 41 of the port 3 is closed. Instead, communication with the extension side chamber 41 of the port 3 is ensured.

  A spacer 13 that is smaller in diameter than the leaf valve 5 and determines the fulcrum position of the leaf valve 5 at the outer edge is laminated above the leaf valve 5 in FIG. 1, and an annular plate is disposed above the spacer 13. The spring 7 is laminated.

  The leaf spring 7 is composed of two annular plates as shown in the figure, and is fixed to the tip 9 of the piston rod 8 inserted into the inner peripheral side as described above, and the ring valve 6 on the outer piston 1 side. The ring valve 6 is positioned with respect to the valve seat 4 and the ring valve 6 is urged toward the valve seat 4. When holding the ring valve 6, the ring valve 6 may be integrated with the leaf spring 7 by welding or bonding, or a stepped portion is provided in the middle of the leaf spring and the outer periphery is seated on the valve seat 4 as a ring valve. In this manner, the leaf spring and the ring valve may be formed as one component.

  Thus, the leaf spring 7 holds the ring valve 6 thicker than the leaf valve 5 and the spacer 13 is interposed between the leaf valve 5 and the leaf spring 7. A gap is formed between the leaf valve 5 and the leaf valve 5 without being in contact with the leaf spring 7 until it is bent by a predetermined amount corresponding to the gap. Yes.

  In the case where the leaf spring and the ring valve are constituted by one component, the above-described step may be made higher than the thickness of the leaf valve 5 to allow the leaf valve 5 to bend. .

  In the case of this embodiment, when receiving the pressure of the pressure side chamber 42 via the port 2, the leaf valve 5 starts to bend with a smaller pressure than the leaf spring 7 that holds the ring valve 6, and the valve precedes the ring valve 6. It is set so as to be separated from the seat 4.

  In addition, the leaf | plate spring 7 may be comprised with one annular plate, and can set the material and number of sheets of an annular plate arbitrarily according to the bending rigidity requested | required.

  The leaf valve 10 stacked below the piston 1 in FIG. 1 has an outer diameter set larger than the outer diameter of the valve seat 12 and is seated on the petal-type valve seat 12. Since the valve seat 12 protrudes toward the pressure side chamber 42, even if the leaf valve 10 is seated, only the port 3 is closed, and the open end of the pressure side chamber 42 of the port 2 is not closed. Communication with the pressure side chamber 42 is ensured.

  Next, the operation of the valve configured as described above will be described. When the piston 1 moves downward in FIG. 1 with respect to the cylinder 40, the pressure in the pressure side chamber 42 increases, and the fluid in the pressure side chamber 42 tries to move into the extension side chamber 41 through the port 2.

  In the stroke in which the shock absorber is compressed in this way, the force that pushes up the leaf valve 5 and the ring valve 6 upward in FIG. 1 acts, but when the piston speed is in the low speed region, The pressure is small, and as shown in FIG. 3, only the leaf valve 5 is bent without bending the leaf spring 7 holding the ring valve 6.

  Then, the ring valve 6 is seated on the outer peripheral side of the surrounding portion 4b of the valve seat 4 and the independent window 11 remains closed. However, since the leaf valve 5 is bent, the leaf valve 5 and the surrounding portion 4b in the valve seat 4 A gap is created between them, and the independent window 11 is slightly opened. When the independent window 11 is opened by the bending of the leaf valve 5, the valve seat 4 is provided so as to protrude from the piston 1 toward the expansion side chamber 41, so that even if the ring valve 6 is seated on the outer peripheral side of the valve seat 4. The compression side chamber 42 and the extension side chamber 41 are brought into communication with each other through a gap formed between the side walls 4e, 4f and the leaf valve 5 in the surrounding portion 4b.

  Therefore, when this piston speed is in the low speed region, the fluid that is going to move from the pressure side chamber 42 to the expansion side chamber 41 passes through a gap between the port 2, the leaf valve 5 and the surrounding portion 4b in the valve seat 4, The valve V generates a damping force that rises linearly with respect to the piston speed.

  When an annular clearance is provided between the outer periphery of the leaf valve 5 and the inner periphery of the ring valve 6, the leaf valve 5 is not bent when the piston speed is extremely low, and the fluid passes through the annular clearance. Thus, a resistance may be given to the flow of the fluid to generate a damping force in the shock absorber.

  When the piston speed increases, the amount of deflection of the leaf valve 5 increases, but the ring valve 6 remains seated on the valve seat 4 until the leaf spring 7 begins to bend. If the leaf valve 5 is set so as to be bent and contact the leaf spring 7 before the leaf spring 7 is bent, it is buffered at the piston speed at which the leaf valve 5 is bent. The characteristic (damping characteristic) of the damping force generated with respect to the piston speed of the container can be changed.

  Subsequently, when the piston speed is further increased to reach a high speed region, the pressure in the pressure side chamber 42 is increased and the force for pushing the ring valve 6 upward is increased. As shown in FIG. The leaf spring 7 is also bent and the ring valve 6 is separated from the valve seat 4.

  Thus, in a state where the piston speed reaches the high speed region, the valve V generates a damping force in the shock absorber with a damping characteristic similar to that of opening a port with a single leaf valve.

  As described above, this valve V does not use a specially shaped valve disk, and adopts a general-purpose valve disk that is set to an independent port type in which each port does not communicate with each other, while the piston speed is low. Therefore, a damping force that rises linearly with respect to the piston speed can be generated in the shock absorber, and a good damping characteristic can be obtained.

  Further, the damping characteristic can be adjusted by setting the pressure receiving area of the leaf valve 5 and the ring valve 6 or the bending rigidity of the leaf valve 5, the ring valve 6 and the leaf spring 7. Therefore, it is not necessary to prepare a valve disk having a special shape that is often manufactured by each damping characteristic to be realized, so that the manufacturing cost can be reduced.

  In the above description, the case where the piston speed at which the leaf valve 5 begins to bend is lower than the piston speed at which the leaf spring 7 begins to bend is described. It is also possible to set the ring valve 6 to open the port 2 prior to the leaf valve 5 by lowering the piston speed at which the valve begins to bend.

  Furthermore, although the valve V of the present invention has been described using an example embodied in the damping valve on the pressure side of the piston portion of the shock absorber, it may be embodied only in the damping valve on the expansion side or on both sides of the expansion. Further, it can be embodied in the base valve portion, and can be applied to a shock absorber valve that functions as a damping force generating element that generates a damping force.

 This is the end of the description of the embodiment of the valve structure of the shock absorber, but the scope of the present invention is not limited to the details shown or described.

The valve of the present invention can be applied to a buffer valve.

DESCRIPTION OF SYMBOLS 1 Piston 2, 3 Port 4, 12 which is valve disc Valve seat 4a Inner peripheral seat part 4b in valve seat Enclosure part 4c in valve seat Inner wall 4d Outer wall 4e, 4f Side wall 5 Leaf valve 6 Ring valve 7 Leaf spring 8 Piston rod 9 Tip 10 Leaf valve 11 Independent window 13 Spacer 14 Spacer 15 Valve stopper 16 Piston nut 40 Cylinder 41 Extension side chamber 42 Pressure side chamber V Valve

Claims (2)

A valve disk having a plurality of ports arranged on the same circumference and a petal-type valve seat having a plurality of surrounding portions individually surrounding the periphery of the open end of each port; An annular leaf valve that is attached to and detached from the inner peripheral side of the valve seat, a ring valve that is annular and arranged on the outer periphery of the leaf valve, and that is attached to and detached from the outer peripheral side of each valve seat, and the ring valve that holds the ring valve in valve with an annular leaf spring to biasing toward the valve seat the valve, closes the port and the leaf valve and ring valve is seated directly on the valve seat, the leaf valve is independently a leaf spring predetermined amount A valve which is allowed to bend and starts to bend with a pressure smaller than that of a leaf spring when pressure is applied through a port . The valve according to claim 1, wherein the leaf valve is set so as to be in contact with the leaf spring and bend together with the leaf spring when the leaf valve is bent by a predetermined amount.

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