JP4043109B2 - Flow control valve - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a flow control valve used for controlling a damping action of a hydraulic damper.
[0002]
[Prior art]
FIG. 11 is a cross-sectional view of a main part of a hydraulic damper that is normally used.
In FIG. 11, 34 is a cylindrical cylinder, 31 is a piston fitted in the cylinder 34 so as to be reciprocally slidable, and rods 32 and 33 serving as input / output shafts are connected to both sides of the piston 31. ing.
Two oil chambers 36 and 35 are defined in the cylinder 34 by the piston 31. Reference numerals 39 and 40 denote covers that cover the oil chambers 36 and 35.
[0003]
Ports 36a and 35a are opened in the oil chambers 36 and 35, respectively, and both ports 36a and 35a are connected through oil pipes 37 and 38, respectively.
The oil pipes 37 and 38 are provided with a flow control valve 100, and the amount of oil reciprocating between the oil chambers 36 and 35 is adjusted by changing the opening degree of the flow control valve 100. ing.
[0004]
FIG. 12 is a cross-sectional view of an essential part showing an example of the prior art of the flow control valve 100. In FIG. 12, 010 is a valve case, and 011 is a valve body. The upper part of the valve body 011 is screwed into a screw part (not shown) provided on the upper part of the valve case 010.
The tip of the valve body 011 is a cone-shaped seat portion 011a, and the seat portion 011a can be seated on a valve seat 012 formed in the valve case 010. 014 is a port connected to the oil pipe 37 of the damper (may be connected in reverse to the above).
[0005]
During operation of the hydraulic damper provided with the flow control valve 100,
When displacement in the direction of the arrow Z in FIG. 11 is input to the rod 32 (or rod 33) due to vibration or the like, the oil in the oil chamber 35 is pressurized and passes through the port 35a and the oil pipe 37, and the port 014 of the flow control valve 100. To reach.
The oil reaching the port 014 of the flow control valve 100 is a flow rate determined by the gap E between the seat portion 011a of the valve body 011 and the valve seat 012, the seat portion length L of the valve seat 012, the seat portion average radius D, etc. It passes through the flow control valve 100 with the flow rate according to the following formulas (1) and (2), and reaches the oil chamber 36 through the port 013, the oil pipe 38 and the port 36a.
[0006]
That is, the flow rate Q ₁ when the valve opening gap E of the valve body 011 is smaller than a certain value is:
Q ₁ = (E ³ × π × D × ΔP) / (12 × μ × L) (1)
The flow rate Q2 when the valve opening gap E of the valve body 011 is larger than a certain value is:
Q ₂ = C × E × π × D × (2 × ΔP / ρ) ^1/2 (2)
Where ΔP = pressure difference at the inlet / outlet of the valve
μ = absolute viscosity of oil
C = Flow coefficient near gap E
ρ = specific gravity of oil
[Problems to be solved by the invention]
In the hydraulic damper using the flow control valve 100 according to the prior art, the flow rate of oil flowing through the flow control valve 100, that is, the flow rate Q (Q ₁ , Q ₂ ) that determines the damping performance of the damper is:
When the valve opening gap E is smaller than a certain value, as shown in the equation (1), the valve opening gap E is proportional to the cube of the gap E and proportional to the pressure difference ΔP, while the valve opening gap E is smaller than a certain value. As it grows,
As shown in the equation (2), the flow rate of the orifice is proportional to the gap E and proportional to the 1/2 power of the pressure difference ΔP.
[0008]
However, when designing a hydraulic damper with a flow rate adjusting valve as shown in FIG. 11, the flow rate Q flowing through the flow rate control valve 100 and the pressure difference ΔP are required to be in a linear proportional relationship.
However, when the flow control valve 100 according to the prior art is used, when the valve opening gap E of the valve body 011 is smaller than a certain value, the flow rate Q ₁ is proportional to the pressure difference ΔP as shown in the equation (1). Although there is a relationship, when the valve opening gap E becomes larger than a certain value, the flow rate Q ₂ is proportional to the 1/2 power of the pressure difference as shown in the equation (2), and is not in a linear proportional relationship. .
[0009]
For this reason, in such a prior art, the minute gap for passing oil is only one portion of the gap E between the valve body 011 and the valve seat 012. Therefore, the flow rate cannot be taken in a wide range from a small flow rate to a large flow rate. . Further, in such a conventional technique, when the flow rate is small, as shown in the above equation (1), since the flow rate Q ₁ changes with the cube of the gap E, the gap E cannot be easily adjusted. Since the relationship between the valve opening and the flow rate is different as in the equations (1) and (2), it is difficult to accurately adjust the flow rate of the hydraulic damper.
[0010]
Further, in such a hydraulic damper, since the valve opening degree of the flow rate control valve changes continuously, when trying to set the damper characteristic of the hydraulic damper to a predetermined value, the flow rate control valve according to the related art In the case of 100, as described above, it is not easy to delicately and accurately adjust the stroke of the valve body 011. Therefore, it takes time to operate the flow control valve 100, and the reproduction is performed when repeated flow rate adjustment is performed. Lack of sex.
[0011]
In view of the problems of the prior art, the present invention can change the flow rate in direct proportion to the pressure difference in the entire flow range from a small flow rate to a large flow rate, and can perform flow control with high accuracy and reproducibility. An object is to provide a flow control valve.
[0012]
[Means for Solving the Problems]
In order to solve this problem, the present invention provides the first invention as follows:
A valve case provided with a fluid flow path is fitted in a valve case provided with a fluid introduction port and a delivery port so as to be able to reciprocate, and the valve rod is displaced in the axial direction so that the area of the flow path is In the flow control valve that controls the flow rate by changing
The valve case is provided with an introduction port and a delivery port so as to face each other in a direction perpendicular to the axial direction of the valve stem , and an oil passage groove is formed across one direction of the chord direction of the disc-shaped valve plate, The oil passage groove is directed in the same direction and attached in a plurality of stages along the axial direction of the valve stem , and the oil passage is such that the fluid flowing through the oil passage groove flows from the inlet to the outlet. A groove is disposed, and the oil passage groove at each stage is formed to have a groove depth such that a pressure difference between the inlet and the outlet and a flow rate through the groove are linearly proportional to each other. By displacing the rod in the axial direction, the number of stages of the oil passage groove that communicates the introduction port and the outlet port is changed, and the area of the oil passage groove is changed in direct proportion to the displacement of the valve rod. A flow control valve characterized by being configured is proposed.
[0013]
According to a second aspect of the present invention, in the first aspect of the present invention, an adjustment screw for changing the valve stem is provided, and the pitch of the adjustment screw is made equal to the pitch of the oil passage groove.
[0014]
Further, the third invention is one of the mounting modes of the valve plate to the valve stem. In the first invention or the second invention, the plurality of stages of valve plates are arranged via pins for positioning them in the circumferential direction. And attached to the valve stem.
[0015]
According to this invention, the pitch of the adjusting screw and the pitch of the oil passage groove of each step are made the same, and the adjusting screw is rotated so that a plurality of valve plates attached along the axial direction of the valve stem are obtained. The flow rate of the flow control valve can be controlled by moving the valve stem in the axial direction and changing the number of stages applied to the inlet or outlet by the oil passage groove provided in the valve plate.
[0016]
Therefore, according to this invention, the flow rate of the flow control valve can be adjusted to the predetermined value reliably and quickly only by adjusting the rotational speed of the valve stem with the adjusting screw, and the operation is simple and reliable. Reproducibility can be achieved.
Further, since the flow rate can be directly proportional to the pressure difference, highly accurate flow rate control is possible.
[0017]
A fourth invention relates to another mounting mode of the valve plate to the valve stem. In the first invention or the second invention, each valve plate is a groove in a direction perpendicular to the axis provided on the upper surface and the lower surface thereof. And the positioning of the circumferential direction is made | formed by the convex part fitted to this groove | channel, and it is attached to the said valve stem.
[0018]
According to this invention, the positioning of each valve plate to the valve stem can be performed without causing the rotational phase of the adjusting screw and the valve plate to shift by fitting the groove in the direction perpendicular to the axis of the adjacent valve plate and the convex portion. Made.
This eliminates the need for the positioning pin as in the third aspect of the invention, eliminates the need for processing the fitting hole of the pin, reduces the number of parts, reduces the number of processing steps, and reduces the cost.
[0019]
(Delete)
[0020]
(Delete)
[0021]
(Delete)
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely illustrative examples. Only.
[0023]
FIG. 11 is a cross-sectional view of a main part of a hydraulic damper to which the flow control valve according to the present invention is applied.
In FIG. 11, 34 is a cylindrical cylinder, 31 is a piston fitted in the cylinder 34 so as to be freely slidable, and rods 32 and 33 serving as input / output shafts are connected to both sides of the piston 31. Has been.
Two oil chambers 36 and 35 are defined in the cylinder 34 by the piston 31. Reference numerals 39 and 40 denote covers that cover the oil chambers 36 and 35.
[0024]
Ports 36a and 35a are opened in the oil chambers 36 and 35, respectively, and both ports 36a and 35a are connected through oil pipes 37 and 38, respectively.
The oil pipes 37 and 38 are provided with a flow rate control valve 100 according to the present invention to control the flow rate of oil flowing between the oil chambers 35 and 36.
[0025]
1 to 6 show a flow control valve according to a first embodiment of the present invention, FIG. 1 is a longitudinal sectional view thereof, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIG. FIG. 4 is a cross-sectional view taken along line B, FIG. 4 is a first example taken along line CC in FIG. 1, FIG. 5 is a second example, and FIG.
[0026]
In FIGS. 1-6, 100 is a flow control valve, and is comprised as follows.
1 is a valve case, 2 is a fitting hole drilled in the center of the valve case 1, and 3 is a valve rod fitted in the fitting hole 2 so as to be reciprocally slidable while maintaining oil tightness. is there.
[0027]
4 is a first oil supply / discharge port, and 5 is a second oil supply / discharge port. One end of the valve stem 3 is provided with a valve shaft 6 and a valve plate mounting screw 7, and a plurality of disc-shaped valve plates 9 with oil passage grooves 8 cut and inserted are inserted into the valve shaft 6. The outer diameter D of the large-diameter portion 3a of the valve stem 6 is formed to be a certain amount larger than the width B of the first and second oil supply / discharge ports 4 and 5, as shown in FIGS. When the large-diameter portion 3a hits the first and second oil supply / discharge ports 4, 5, the valve is closed. Reference numeral 15 denotes a positioning pin for the valve plate 9. Further, a valve disintegration adjusting screw 10 is provided at the other end of the valve stem 3, and the pitch of the screw 10 is configured to be the same as the thickness of the valve plate 9. Reference numeral 11 denotes a cover, and the screw 10 is engaged with a central portion of the cover 11 and is fixed to the valve case 1 by a bolt 11a. As shown in FIGS. 4 and 5, the head of the screw 10 has a hexagonal shape so that a tool for rotating the screw 10 can be engaged. Further, as shown in FIG. 4, an arrow 12 is engraved on the top surface of the screw 10, and a point 13 is engraved on the cover 11. When the rotational phases of the arrow 12 and the point 13 are matched, the oil passage groove 8 is formed. Is opened, and the first supply / discharge oil port 4 and the second supply / discharge oil port 5 communicate with each other.
Reference numeral 16 denotes a lock nut for fixing the adjusting screw 10, and reference numeral 17 denotes an O-ring.
[0028]
In addition, instead of the arrow shown in FIG. 4, a point 14 may be marked on the top surface of the valve opening adjusting screw 10 in accordance with the point 13 on the cover 11 as shown in FIG. 5.
[0029]
In the hydraulic damper using the flow control valve 100 having such a configuration, as shown in FIG. 11, when a displacement in the Z arrow direction is input to the rod 32 (or the rod 33) due to vibration or the like, The oil is pressurized and reaches the first supply / discharge oil port 4 (or the second supply / discharge oil port 5) of the flow control valve 100 through the port 35a and the oil pipe 37. Then, the oil is guided to the second oil supply / discharge port 5 through the oil passage grooves 8 and 8 of the valve plate 9 and flows into the oil chamber 36 through the oil pipe 38 and the port 36a.
Accordingly, the hydraulic damper attenuates the vibration by a damping performance determined by a passage area in the oil passage groove 8 of the valve plate 9 of the flow control valve 100.
[0030]
The flow rate in the flow rate control valve 100 is adjusted as follows.
As shown in FIG. 6, the adjustment screw 10 for opening the valve is screwed to the lowermost position, and the uppermost valve plate 9a is connected to the lower edges 4a and 5a of the first and second oil supply / discharge ports 4 and 5. If it is also positioned below, the first oil supply / discharge oil port 4 and the second oil supply / discharge oil port 5 are closed by the large-diameter portion 3a of the valve stem 3, and the oil flow is blocked.
[0031]
When the adjusting screw 10 is rotated in the valve opening direction by one rotation from the valve open state, the valve stem 3 is raised by the screw pitch amount of the adjusting screw 10. The valve plate 9 attached to the valve stem 3 is also raised by the screw pitch amount, that is, one valve plate. As a result, the oil supply groove 4 of the valve plate 9 communicates with the oil supply / discharge oil outlet 4 in one stage. Similarly, when the screw 10 is rotated twice, the oil supply groove 8 communicates with the oil supply / discharge oil port 4 and the oil supply / discharge oil port 5 in two stages, and the amount of oil supply is doubled. Further, similarly, when the screw 10 is rotated three times, the oil passing amount is tripled.
[0032]
In such embodiments, the amount clogging communication amount of oil in the oil flowing through the oil passage grooves 8, since each of the depth of the plurality of the oil passage groove 8 is shallow processable, the oil flow quantity Q ₁ As the relationship with the pressure difference ΔP, the equation (1) is applied, and the oil flow rate Q ₁ and the pressure difference ΔP are linearly proportional.
[0033]
As described above, according to such an embodiment, the valve opening adjustment screw 10 is rotated to move the plurality of valve plates 9 attached to the valve stem 3 in the axial direction of the valve stem 3. The oil flow amount of the flow control valve 100 can be changed by changing the number of the oil flow grooves 8 provided in 9 on the first and second oil supply / discharge ports.
[0034]
That is, according to this embodiment, the oil flow rate can be reliably and quickly adjusted to the predetermined value only by adjusting the rotation speed of the valve stem 3, and reliable reproducibility can be achieved.
Further, as described above, the oil flow rate Q ₁ is linearly proportional to the pressure difference ΔP, so that highly accurate flow rate control is possible.
[0035]
7 to 8 show a second embodiment of the present invention, FIG. 7 is a view corresponding to FIG. 2, and FIG. 8 is a sectional view taken along line FF of FIG.
In this embodiment, the positioning pin 15 in the first embodiment is removed, and the valve plates 18 and the valve plate 18 and the valve stem 3 are positioned by the convex portion 20 and the groove 19. ing.
[0036]
That is, in FIGS. 7 to 8, reference numeral 18 denotes a plurality of valve plates fitted to the valve shaft 6 of the valve stem 3, and each valve plate 18 has an oil passage groove 8 similar to that in the first embodiment. Is provided.
A straight groove 19 is formed on the upper surface side, and a straight convex portion 20 is formed on the lower surface side, and the convex portion 20 of the upper valve plate 18 is a lower valve. It fits into the groove 19 of the plate 18. Then, the groove 19 of the uppermost valve plate 18 is adapted to be fitted into a convex portion 3 b formed on the valve stem 3.
[0037]
Accordingly, the positioning of the valve plate 18 and the valve stem 3 can be performed without providing the positioning pin 15 as in the first embodiment and without processing the pin insertion hole in each valve plate 18. The rotational phases of the adjusting screw 10 and the valve plate 18 do not shift.
[0038]
9 to 10 show a flow control valve according to a comparative example of the present invention, FIG. 9 is a longitudinal sectional view of a main part, and FIG. 10 is a sectional view taken along the line GG of FIG.
In this comparative example , the valve stem 24 is provided with a plurality of stages of passage holes 22 communicating with the first oil supply / discharge port 41 along the axial direction thereof, and the valve stem 24 is moved in the axial direction, thereby The amount of oil flow is changed by changing the number of steps of the passage hole 22 communicated with the two supply / discharge oil ports 51.
[0039]
That is, in FIG. 9 to FIG. 10, the valve rod 24 fitted in the fitting hole 2 of the valve case 1 so as to be freely slidable is provided with a plurality of oil passage holes 22 in the axial direction (longitudinal direction). Are formed at the same pitch P as that of the adjusting screw 10 shown in FIG. As shown in FIG. 10, a plurality of oil passage holes 22 are formed radially at equal intervals (even at irregular intervals) in the circumferential direction.
Reference numeral 21 denotes an internal hole formed in the valve rod 24 from the lower end surface thereof to a length that opens the entire inner peripheral end of the passage hole 22.
[0040]
Reference numeral 23 denotes a space formed in the valve case 1 so that the outer peripheral opening ends of the oil passage holes 22 of the respective stages can communicate with each other. As shown in FIG. 9, when the valve rod 24 is in the uppermost position. Each of the plurality of oil passage holes 22 is set to have an axial length that allows communication, and the outer periphery opens to a second oil supply / discharge port 51 formed in the valve case 1.
[0041]
Reference numeral 41 denotes a first supply / exhaust port formed in the valve case 1, which opens to the lower surface of the fitting hole 2.
When the valve stem 24 is in the lowermost position, the fitting hole 2 is such that all of the oil passage holes 22 come below the lower edge 23a of the cavity 23 and can be closed. Set to a certain depth.
[0042]
In such a comparative example , when the valve stem 24 is moved downward from the uppermost position shown in FIG. 9, the lowermost oil passage hole 22 is closed by the lower edge 23 a of the void 23 by the movement of 1 pitch P. Each time the pitch advances, the oil passage holes 22 in the second and subsequent stages are closed in the same manner as described above, and the oil passage holes 22 in the respective stages are closed in the same manner.
Then, the oil passes from the first oil supply / discharge port 41 through the internal hole 21, passes through the open oil passage hole 22, and is sent to the second oil supply / discharge oil port 51. The oil passing amount is controlled by the passage area of the hole 22.
[0043]
(Delete)
[0044]
【The invention's effect】
As described above, according to the present invention, the number of rotations of the valve stem is adjusted by the adjusting screw, and the number of stages of the oil passage groove of the valve plate opened to the fluid inlet or the outlet is changed. The flow rate can be controlled with high accuracy and reproducible control in direct proportion to the pressure difference from a small flow rate to a large flow rate.
[0045]
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a flow control valve according to a first embodiment of the present invention.
FIG. 2 is a cross-sectional view taken along line AA in FIG.
3 is a cross-sectional view taken along line BB in FIG.
4 is a first example taken along the line CC of FIG. 4;
FIG. 5 is a second example of the CC arrow view.
FIG. 6 is a response diagram of FIG. 1 for explaining the operation of the first embodiment.
FIG. 7 is a cross-sectional view corresponding to FIG. 2 showing a second embodiment of the present invention.
8 is a cross-sectional view taken along line FF in FIG.
FIG. 9 is a longitudinal sectional view of a main part of a flow control valve showing a comparative example .
10 is a cross-sectional view taken along line GG in FIG.
FIG. 11 is a longitudinal sectional view of an essential part of a hydraulic damper in which a flow control valve according to the present invention is used.
FIG. 12 is a cross-sectional view showing a main part of a flow control valve according to a conventional technique.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Valve case 2 Fitting hole 3, 24 Valve rod 3a Large diameter part 3b Convex part 4, 41 1st oil supply / exhaust port 5, 51 2nd oil supply / exhaust port 6 Valve shaft 8 Oil passage groove 9, 18 Valve plate 10 Adjustment screw 11 Cover 15 Pin 16 Lock nut 18 Valve plate 19 Groove 20 Protrusion 21 Internal hole 22 Oil passage hole 23 Space 100 Flow control valve

Claims (4)

A valve case provided with a fluid flow path is fitted in a valve case provided with a fluid introduction port and a delivery port so as to be able to reciprocate, and the valve rod is displaced in the axial direction so that the area of the flow path is In the flow control valve that controls the flow rate by changing
The valve case is provided with an introduction port and a delivery port so as to face each other in a direction perpendicular to the axial direction of the valve stem , and an oil passage groove is formed across one direction of the chord direction of the disc-shaped valve plate, The oil passage groove is directed in the same direction and attached in a plurality of stages along the axial direction of the valve stem , and the oil passage is such that the fluid flowing through the oil passage groove flows from the inlet to the outlet. A groove is disposed, and the oil passage groove at each stage is formed to have a groove depth such that a pressure difference between the inlet and the outlet and a flow rate through the groove are linearly proportional to each other. By displacing the rod in the axial direction, the number of stages of the oil passage groove that communicates the introduction port and the outlet port is changed, and the area of the oil passage groove is changed in direct proportion to the displacement of the valve rod. A flow control valve characterized by comprising. The flow control valve according to claim 1 , wherein an adjustment screw for displacing the valve stem is provided, and the pitch of the adjustment screw is the same as the pitch of the oil passage groove . The flow control valve according to claim 1 or 2, wherein the plurality of stages of valve plates are attached to the valve stem via pins that position the valve plates in the circumferential direction . 3. Each of the valve plates is positioned in the circumferential direction by means of a groove perpendicular to the axis provided on the upper and lower surfaces of the valve plate and a convex portion fitted in the groove, and is attached to the valve stem. The flow control valve described .

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