JP5926528B2 - Adjustment valve - Google Patents

Description

  The present invention relates to a regulating valve, and more particularly, to an improvement of a regulating valve that enables a change in resistance to the flow of hydraulic oil in a passage.

  Various adjustment valves that can change the resistance to the flow of hydraulic oil in the passage have been proposed in the past. For example, in the proposal disclosed in Patent Document 1, as shown in FIG. The valve includes a valve body V provided in the passage L and a cylinder P facing the valve body V.

  In this adjusting valve, the valve body V has a pointed portion V1 formed in a needle shape, and the cylinder P has an annular valve seat portion P1 for separating and seating the pointed portion V1, and the pointed portion V1. The front end side of the can be freely moved into and out of the cylinder P.

  Therefore, in this conventional adjustment valve, the valve body V opens and closes the passage L by opening and closing the outer periphery of the needle-like pointed portion V1 on the annular valve seat portion P1, and the passage L When opened, an annular gap appears between the outer periphery of the tip V1 and the valve seat portion P1 to provide resistance to the flow of hydraulic oil in the passage L, and the above-described resistance is increased or decreased by increasing or decreasing the annular gap. .

JP 2008-240661 A

  In the conventional adjustment valve described above, there is basically no problem in that the resistance to the flow of hydraulic oil in the passage can be adjusted in magnitude, but there are minor problems when considering the actual use. May be pointed out.

  The adjustment valve changes the area of the annular gap in accordance with the amount of movement of the tip portion V1 in the valve body V. However, since the tip portion V1 is formed in a needle shape, the amount of movement of the tip portion V1 is reduced. The area change of the annular gap tends to be large.

  Therefore, in the conventional adjustment valve, since the area change of the annular gap is likely to be large with respect to the movement amount of the tip portion V1 in the valve body V, the fine adjustment of the resistance given to the flow of hydraulic oil, that is, the damping force It becomes difficult to make fine adjustments.

  In particular, when it is desired to reduce the damping force, there is a concern that the area of the annular gap becomes too large, and a so-called damping force drop is caused in which the damping force is rapidly reduced.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to provide an adjustment valve that can prevent a sudden change in damping force when the damping force is adjusted in level.

In order to achieve the above-described object, the problem-solving means of the present invention includes an annular valve seat provided in the passage, in an adjustment valve that is provided in the passage and is capable of changing a resistance given to a flow of hydraulic oil that passes through the passage. and a relative valve body the valve seat, and an inclined portion in which the valve body is separated seated on one end of the upper Kiba Rubushito in the same said valve seat axially, said continuously to the inclined portion and a straight portion which is inserted into the valve seat, the inclined portion is seated then close the through passage at one end of the valve seat, opening the unseated then the passage from one end of the valve seat forming an orifice aperture with said straight portion, and forming a choke between the valve seat.

  Therefore, in the present invention, the inclined portion in the valve body constituting the adjustment valve opens and closes the passage by being seated on one end of the annular valve seat in the passage, and when the passage is opened, the inclined portion Causes an annular gap to appear between one end portion of the valve seat and allows the flow of hydraulic oil in the passage.

  The straight portion of the valve body forms a choke throttle with the valve seat, and the length of the choke throttle is changed by the movement of the valve body.

  Therefore, the degree of change in resistance in the passage relative to the amount of movement of the valve body can be made smaller than in the case where the resistance is adjusted by the orifice restrictor.

  As a result, in the present invention, when the resistance is given to the flow of the hydraulic oil in the passage by the adjusting valve provided in the passage, it is possible to prevent a rapid change in the resistance.

  Therefore, it is possible to finely adjust the resistance given to the flow of hydraulic oil in the passage, that is, to finely adjust the damping force. In particular, when reducing the damping force, the resistance given to the flow of hydraulic oil passing through the regulating valve. Can be prevented from falling off without abruptly decreasing.

It is a fragmentary longitudinal cross-sectional view which shows the hydraulic shock absorber which concerns on one Embodiment of this invention partially fractured | ruptured. It is a partial half vertical longitudinal cross-sectional view which expands and shows other embodiment of an adjustment valve. It is a partial semi-longitudinal longitudinal cross-sectional view which expands and shows the conventional adjustment valve.

  Hereinafter, the present invention will be described based on the illustrated embodiment. In the illustrated embodiment, the adjustment valve of the present invention is provided in a passage L in the hydraulic shock absorber, and the flow of hydraulic oil passing through the passage L is illustrated. The resistance given to can be changed.

  The hydraulic shock absorber has a first chamber R1 and a second chamber R2 that are held by a rod 2 that is inserted into a cylinder 1 that contains hydraulic oil, and that is separated by a piston 3 that is slidably inserted into the cylinder 1. .

  The passage L in which the adjustment valve is provided includes a vertical hole 2a and a horizontal hole 2b formed in the rod 2, bypasses the damping valves 3a and 3b provided in the piston 3, and the one chamber R1 in the cylinder 1 and the other chamber Allow communication with R2.

  On the other hand, the adjustment valve has an annular valve seat provided in the passage L and a valve body 5 opposed to the valve seat. The annular valve seat is shown in FIG. Thus, one end of the cylinder 6 that is the upper end in the drawing is a valve seat portion 6a.

  The valve body 5 includes an inclined portion 51 that is axially the same as the cylinder 6 and is attached to and detached from the annular valve seat portion 6a, and a straight portion 52 that is inserted into the cylinder 6 continuously to the inclined portion 51. Have.

  In this adjustment valve, the inclined portion 51 in the valve body 5 is seated on the valve seat portion 6a to close the passage L, and is separated from the valve seat portion 6a to open the passage L. A choke stop is formed between the straight portion 52 and the cylinder 6.

  More specifically, first, the cylinder 6 forming the valve seat in the adjusting valve is formed on the shaft core portion of the lower end portion of the rod 2, and one end that becomes the lower end in FIG. 1 is in the other chamber R 2 in the cylinder 1. The open vertical hole 2a is press-fitted and fixed from the lower chamber R2 side, and the inner periphery of the opening which is the upper end portion in FIG. 1 is an annular valve seat portion 6a.

  Incidentally, regarding the provision of the annular valve seat portion 6a in the longitudinal hole 2a of the rod 2, the longitudinal hole 2a may be directly processed to provide the annular valve seat portion 6a. However, as shown in FIG. The formation of the cylinder 6 is facilitated by press fitting.

  Further, the cylinder 6 shown in the figure is because a straight portion 52 described later is inserted, and because a so-called long choke stop is formed between the straight portion 52 in the cylinder 6, for example, Compared to the cylinder P in the conventional example shown in FIG. 3, it is formed longer, and the fixing property in the vertical hole 2a of the rod 2 is improved accordingly, and the function of the cylinder 6 as a so-called valve stopper, for example, is guaranteed.

  The inclined portion 51 of the valve body 5 is formed so as to converge toward the inside of the cylinder 6 press-fitted and fixed in the vertical hole 2c, and the outer periphery between the front end entering the cylinder 6 and the rear end not entering the cylinder 6 The surface is inclined (not marked).

  The inclined portion 51 closes the passage L when the outer periphery is seated on the annular valve seat portion 6a, and opens the passage L when seated away from the annular valve seat portion 6a. That is, an annular gap serving as an orifice restriction appears between the valve seat portion 6a and the passage of hydraulic oil is allowed.

  In addition, the annular gap provides resistance to the flow of hydraulic oil passing therethrough, and thus provides resistance to the flow of hydraulic oil passing through the passage L, and has a damping action.

  The straight portion 52 is formed in the shape of a rod whose outer diameter is set smaller than the inner diameter of the cylinder 6 and forms an annular gap with the cylinder 6. In the illustrated case, first, in FIG. The diameter of the rear end that is the upper end is the same as the diameter of the tip of the inclined portion 51.

  Then, the outer diameter from the rear end having the same diameter as the front end of the inclined portion 51 to the front end serving as the lower end in FIG. An annular flow path 52a composed of a restriction is formed.

  Incidentally, the choke diaphragm has a length dimension that is larger than the cross-sectional dimension. On the other hand, the choke diaphragm has an orifice diaphragm that has a smaller length dimension than the cross-sectional dimension.

  Further, the flow path 52a formed of the choke throttle has a constant flow path area and a constant length. However, in the illustrated case, even if the straight portion 52 retreats to the maximum extent, The choke throttle is set so as not to disappear, that is, the flow path 52a has a length that does not disappear.

  If the flow rate is constant, the choke throttle changes the pressure loss in proportion to the amount of movement of the valve body 5, whereas the orifice throttle changes the pressure loss in proportion to the square of the flow path area change. Let

  In other words, in the conventional adjustment valve shown in FIG. 3 described above, the change in the flow path area changes with a value that is the square of the amount of movement of the valve body V having the tip V1 formed in a needle shape.

  Therefore, the choke throttle formed in the cylinder 6 by the straight portion 52 makes the change degree of the resistance in the passage L with respect to the movement amount of the valve body 5 smaller than that in the case where the resistance is adjusted by the orifice throttle. .

  For this reason, the straight portion 52 in the valve body 5 does not rapidly increase or decrease the resistance given to the flow of hydraulic oil in the flow path 52a formed between the cylinder 6 and the cylinder 6 when moving in the vertical direction in FIG.

  Therefore, in the adjustment valve, the straight portion 52 prevents a sudden change in resistance given to the flow of hydraulic oil passing through the passage L.

  Since the choke stop is formed between the cylinder 6 and the straight portion 52 moves within the cylinder 6 and the length of the flow path 52a formed between the cylinder 6 is shortened, The resistance given to the flow of the hydraulic oil passing through the flow path 52a composed of the choke throttle is changed in size.

  As a result, the resistance given to the flow of hydraulic oil passing through the regulating valve can be finely changed without abruptly changing, and therefore, the loss of the damping force in the regulating valve can be prevented.

  In view of the above, in the adjusting valve, the valve body 5 has the inclined portion 51 so that the passage L can be opened and closed, and the straight portion 52 forms a choke throttle in the passage L. This choke restriction prevents a sudden change in resistance applied to the flow of hydraulic oil in the passage L, and enables a fine change.

  And since the resistance given to the flow of the hydraulic fluid which passes the channel | path L in an adjustment valve can be adjusted finely, when reducing the damping force in an adjustment valve, for example, it can avoid that a damping force falls rapidly, and damping force It becomes possible to prevent omission.

  The adjustment valve shown in the figure is provided in a hydraulic shock absorber and is provided in a passage L that is formed on the rod 2 and bypasses the damping valves 3a and 3b and allows communication between the one chamber R1 and the other chamber R2. By preventing the damping force from being lost in the valve, it is possible to prevent the damping force generated by the damping valves 3a and 3b, that is, the damping force from being lost in the hydraulic shock absorber.

  In the illustrated embodiment, the lateral hole 2b formed in the rod 2 in order to form the passage L may be a simple passage having a large diameter so as not to cause resistance to the flow of hydraulic oil. It becomes possible, and formation of this horizontal hole 2b is made easy.

  As described above, the valve body 5 in the adjustment valve of the present invention has a straight portion 52 and can form a choke throttle in the cylinder 6 as compared with the conventional valve body V shown in FIG. The resistance to the flow of the hydraulic oil passing through the passage L is not abruptly increased or decreased, and this characteristic can also be achieved by the following configuration.

  The point shown in FIG. 2 is that the adjusting valve has the valve body 5 and the cylinder 6, and that the valve body 5 has the inclined portion 51 and the straight portion 52 continuous to the inclined portion 51. It is common with embodiment shown to.

  Therefore, even in the place shown in FIG. 2, it is possible to obtain basically the same operational effects as those shown in FIG.

  On the other hand, in the embodiment shown in FIG. 2, the inclined portion 51 has the same axial length as the inclined portion 51 in FIG. 1, whereas the straight portion 52 in FIG. The length dimension is shorter than that of the straight part 52.

  In the embodiment shown in FIG. 2, the change portion 53 is provided between the inclined portion 51 and the straight portion 52, and the inclination angle of the outer periphery of the change portion 53, that is, in the illustrated case, The inclination angle with respect to the axis of the cylinder 6 forming the passage L is set smaller than the inclination angle with respect to the axis of the outer cylinder 6 in the inclined portion 51.

  Therefore, in the valve body 5 constituting the adjustment valve shown in FIG. 2, the choke throttle formed in the passage L between the annular gap formed by the inclined portion 51 and the straight portion 52 formed between the cylinder 6. The transition to the flow path 52a becomes smoother than the case where the changing portion 53 is not provided, and for example, the damping force in the hydraulic shock absorber can be smoothly changed.

  By the way, in the place shown in the figure, the adjustment valve operates in a so-called forward and backward direction in the passage L by the input of external force.

  In order to enable the adjustment valve to operate, the illustrated hydraulic shock absorber has an adjuster 4, and this adjuster 4 crosses the axis of the rod 2 with the eye 21 connected to the upper end of the rod 2. It is screwed in from the horizontal direction.

  Incidentally, the adjuster 4 may be screwed into the eye core 21 from the upper end of the eye 21 so as to move up and down, although not shown, instead of being screwed into the eye 21 from the lateral direction.

  The adjuster 4 shown in FIG. 1 positions the front end side, which is the right end side in FIG. 1, in the eye 21 with the rear end, which is the left end in FIG. The tip that is the right end of the rod 2 is brought into contact with the upper end of the control rod 41 that is inserted through the axial center portion of the rod 2 so as to be movable up and down.

  In other words, the tip of the adjuster 4 is a pointed tip having a cross-section that has a transverse cross section, and the upper end of the corresponding control rod 41 is a pointed tip having a cross-section that faces upward, and the inclined surfaces that form the points of each other are in contact with each other. .

  Therefore, in the adjuster 4, the control rod 41 is allowed to rise in the rod 2 when moving backward so as to come out of the eye 21, and the control rod 41 is moved to the rod 2 when moving forward so as to enter the eye 21. Lower in.

  For the rotation of the adjuster 4, an arbitrary configuration can be adopted. For example, it may be practiced manually by using a screwdriver as a tool. Although not shown, an appropriate driving source is driven by an external signal input. May be practiced.

  Further, in terms of the operation of the control rod 41, for example, the adjuster 4 may be omitted, and the control rod 41 may be moved up and down when an actuator such as a solenoid provided in the eye 21 is driven.

  Incidentally, the control rod 41 is inserted through the shaft core portion of the rod 2 so as to be movable up and down, and integrally has a valve body 5 constituting an adjustment valve at the tip which is the lower end in the drawing.

  Further, when the other chamber R2 in the cylinder 1 is on the high pressure side, the valve body 5 moves backward in the passage L so as to rise in FIG. 1 by the hydraulic action from the other chamber R2, and the one chamber in the cylinder 1 Even when R1 is on the high pressure side, the adjustment valve is caused to function in both directions in which the hydraulic shock absorber retracts in the passage L due to its hydraulic action and the hydraulic shock absorber expands and contracts.

  From this, the valve body 5 may not be integrally provided at the tip of the control rod 41 but may be a separate body and may be serially connected to the control rod 41 with the same axial direction.

  Incidentally, when the valve body 5 is integrally provided at the tip of the control rod 41, the assembly of the adjustment valve is facilitated. When the valve body 5 is separated from the tip of the control rod 41, the valve body 5 Facilitates the replacement of

  On the other hand, as shown in the figure, the passage L is provided in the cylinder 1 of the hydraulic shock absorber. However, the passage L is provided outside the cylinder 1 so that the one chamber R1 and the other chamber R2 in the cylinder 1 You may communicate.

  In addition, the hydraulic shock absorber is a single cylinder type and is set to an upright type in the figure, but instead of this, although not shown, it may be set to an inverted type. It may be set to a type.

  The suspension spring S, which is provided between the cylinder 1 and the rod 2 and urges the hydraulic shock absorber in the extending direction, has a lower end outside the cylinder 1 and is carried on the cylinder 1 side, although not shown. At this time, the lower end position of the suspension spring S may be movable up and down with respect to the cylinder 1.

  When the lower end position of the suspension spring S is moved up and down, the upper end position of the suspension spring S is raised and lowered, and therefore the upper end position of the rod 2 is raised and lowered.

  In the illustrated hydraulic shock absorber, the damping valve 3a performs a predetermined damping action when the piston 3 moves up in the cylinder 1, and is attenuated when the piston 3 moves down in the cylinder 1. The valve 3b performs a predetermined pressure side damping action.

  Further, in the above description, the damping valves 3a and 3b around which the passage L is bypassed are provided in the cylinder 1, that is, the piston 3 in the cylinder 1. 3a and 3b may be provided on a valve disk which is a partition body constituting a base valve provided in the lower end portion of the cylinder 1.

  As described above, the flow path 52a formed of the choke throttle formed in the cylinder 6 by the straight portion 52 in the valve body 5 has a constant flow path area and a constant length. The fixed length may be subdivided into a plurality of which make the flow channel area constant.

  In the above description, the flow path 52a formed of the choke throttle formed in the cylinder 6 is formed in an annular shape. However, as long as the flow path 52a is formed of the choke throttle, the flow path 52a is formed linearly. It may also be formed in a spiral shape.

  In the above description, the adjustment valve of the present invention is provided in the hydraulic shock absorber. However, the hydraulic shock absorber may be used for an industrial machine in addition to the vehicle. Adjustment valves may be installed in seismic isolation dampers and vibration dampers.

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Rod 2a Vertical hole 2b Horizontal hole 3 Piston 3a, 3b Damping valve 4 Adjuster 5 Valve body 6 Cylinder 6a Valve seat part 21 Eye 41 Control rod 51 Inclined part 52 Straight part 52a Flow path 53 Change part L path R1 One side Chamber R2 Other chamber S Suspension spring

Claims (3)

In the adjustment valve that is provided in the passage and can change the resistance given to the flow of the hydraulic oil passing therethrough,
An annular valve seat provided in the passage, and an opposite valve body the valve seat,
Yes an inclined portion in which the valve body is separated seated on one end of the upper Kiba Rubushito in the same said valve seat and the axis direction and a straight portion which is inserted into the bulb seat in succession the inclined portion And
The inclined portion is seated Then close the passage at one end of the valve seat to form an orifice aperture to open the unseated Then the passage from one end of the valve seat,
The straight portions are adjusted valve and forming a choke between the valve seat. The valve seat is made of tubular, Ru is pressed into the passage
The regulating valve according to claim 1, wherein: The valve body is closed the change portion to reduce the inclination angle with respect to the valve seat from the inclined portion between the inclined portion and the straight portions
The regulating valve according to claim 1 or 2, characterized in that

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