JP2008025713A - Damper device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a predetermined damper effect according to change in temperature environment. <P>SOLUTION: The damper device has a cylinder 30 for forming a fluid chamber 31 by enclosing operating fluid Q, a piston 10 movably provided for separating the fluid chamber 31 into a pressure chamber 50 side and a non-pressure chamber 60 side. The piston 10 is equipped with a distribution passage 11 for allowing distribution of the operating fluid Q between the pressure chamber 50 side and the non-pressure chamber 60 side and a valve element 20 capable of opening and closing the distribution passage 11 by deflecting. In the damper device, the valve element 20 is provided at the pressure chamber 50 side and formed of a material of which elastic factor changes according to temperature change. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a damper device capable of obtaining a predetermined damper effect corresponding to a change in temperature environment.

  In the conventional damper device, as shown in Patent Document 1, a valve body is slidably inserted into a guide bar projecting from a piston, and the pressure chamber side and the non-pressure chamber are moved by the movement of the valve body. The flow path of the working liquid communicating with the side is opened and closed.

  However, this damper device operates normally within the allowable range of the set temperature because the viscosity of the working fluid fluctuates due to changes in the temperature environment used, but the temperature environment does not exceed the allowable range of the set temperature. If it is too high or low, there is a problem that a predetermined damper effect may not be obtained.

JP 2000-265738 A

  The problem to be solved is that a predetermined damper effect cannot be obtained automatically in response to changes in the temperature environment used.

  In order to automatically cope with a change in temperature environment, the present invention automatically disposes a cylinder that encloses a working liquid to form a liquid chamber, and divides the liquid chamber into a pressure chamber side and a non-pressure chamber side so as to be movable. And a damper device having a valve body capable of opening and closing the flow passage by being bent and having a flow passage allowing the working liquid to flow between the pressure chamber side and the non-pressure chamber side. The damper device is characterized in that the valve body is provided on the pressure chamber side and the valve body is formed of a material whose elastic coefficient changes according to a temperature change.

  The damper device according to the present invention includes a cylinder that encloses a working liquid to form a liquid chamber, a piston that is movably arranged to partition the liquid chamber into a pressure chamber side and a non-pressure chamber side, and the piston includes the piston In a damper device having a flow passage that allows flow of the working liquid between the pressure chamber side and the non-pressure chamber side and is capable of opening and closing the flow passage by being bent, the valve body includes the pressure chamber. Since the valve body is formed of a material having an elastic coefficient that changes in response to a temperature change, a predetermined damper effect can be reliably obtained by automatically responding to a change in the temperature environment to be used. Therefore, there is little temperature dependency from low temperature to high temperature, and the damper performance can be made constant.

  This was realized by providing the valve body on the pressure chamber side and forming the valve body from a material whose elastic coefficient changes according to the temperature change.

  FIG. 1 is a front sectional view illustrating a damper device according to a first embodiment of the present invention, and FIG. 2 is a front sectional enlarged explanatory view showing the main part of the same.

  As shown in FIG. 1, the damper device E <b> 1 according to the first embodiment includes a piston 10, a valve body 20, and a cylinder 30.

  The cylinder 30 is filled with a working fluid Q having a viscosity such as silicon oil to form a liquid chamber 31, and a piston is formed so as to partition the liquid chamber 31 into a pressure chamber 50 side and a non-pressure chamber 60 side. 10 is inserted through a piston rod 17 so as to be movable.

  The piston 10 is provided with two right and left flow passages 11 that allow the working liquid Q to flow between the pressure chamber 50 side and the non-pressure chamber 60 side, penetrating the piston 10 in the axial direction. The pressure seat 50 side end surface 12 is formed with a valve seat 13 having a conical inclined surface from the central portion of the piston 10 toward the outer peripheral edge.

  The valve body 20 is formed of an elastic body such as rubber or plastic, and is provided on a guide bar 10a protruding from the piston 10 on the pressure chamber 50 side so as to be movable in the axial direction. In particular, in this embodiment, the valve body 20 is made of a material whose elastic coefficient changes according to a temperature change. That is, if the elastic modulus at normal temperature of the valve body 20 is set so that a predetermined damper effect can be obtained, when the temperature increases, the elastic coefficient decreases corresponding to the increased temperature, and the valve body 20 It becomes easier to bend as compared to the normal temperature, and when the temperature is lowered, the elastic modulus increases corresponding to the lowered temperature, and the valve body 20 is less likely to bend than the normal temperature.

  On the other hand, the viscosity of the working liquid Q becomes lower as the temperature rises and the fluidity improves as the temperature rises, and the viscosity becomes higher and the fluidity lowers as the temperature falls.

Therefore, when the piston 10 is moved to the pressure chamber 50 side at normal temperature, the valve body 20 is bent to the non-pressure chamber 60 side by the pressure of the working liquid Q, and each flow passage 11 is closed to obtain a predetermined damper effect. As described above, if the valve seat 13 made of the inclined surface of the piston 10 is set and the elastic coefficient of the valve body 20 is set,
When the temperature rises, the viscosity of the working liquid Q decreases as compared with the viscosity at normal temperature and the fluidity improves and the viscosity resistance decreases corresponding to the temperature rise. It becomes easy to bend compared with the time of normal temperature, and the damper effect equivalent to the time of normal temperature can be acquired. That is, when the temperature rises, the working liquid Q is improved in fluidity and the viscous resistance is lowered, and the damper effect is lowered as compared with that at normal temperature. However, the valve body 20 is more easily bent than at normal temperature. Since the flow path 11 of the working liquid Q formed in the valve seat 13 formed of the inclined surface of the piston 10 is closed more quickly than the time, the working liquid Q can be obtained so that a damper effect equivalent to that at normal temperature can be obtained. Can be finely adjusted.

  When the temperature decreases, the viscosity of the working liquid Q increases in comparison with the viscosity at normal temperature and the fluidity decreases and the viscosity resistance increases corresponding to the temperature decrease. It becomes difficult to bend compared with the case of normal temperature, and the damper effect equivalent to the normal temperature can be obtained. That is, when the temperature is lowered, the working liquid Q is decreased in fluidity and viscosity resistance is increased, and the damper effect is improved as compared with that at normal temperature. Since the flow path 11 of the working liquid Q formed on the inclined surface 13 of the piston 10 is closed more slowly than the time, the flow rate of the working liquid Q can be obtained so that a damper effect equivalent to that at normal temperature can be obtained. Can be fine-tuned.

  As described above, in this embodiment, a predetermined damper effect can be reliably obtained in response to a change in temperature of the working liquid Q and automatically in response to a change in temperature environment. Therefore, there is little temperature dependency from low temperature to high temperature, and the damper performance can be made constant.

  In addition, the inclination θ of the inclined surface 13 of the piston 10 can obtain a substantially constant damper effect in combination with the above-described function of the valve body 20 even when the temperature of the working liquid Q changes. When the pressure of the working liquid Q does not act, the valve body 20 is always restored to a flat plate shape, that is, a flat shape without being affected by a change in temperature, so that the flat shape can be maintained. It is.

  In this embodiment, the valve body 20 is formed of a material having the above-described flat characteristics from −25 ° C. to 70 ° C.

  When the piston 10 is moved to the non-pressure chamber 60 side, the working liquid Q in the non-pressure chamber 60 passes through the flow passage 11 and moves to the pressure chamber 50 side, and the valve body 20 is moved to the pressure chamber 50 by this moving pressure. The working liquid Q in the non-pressure chamber 60 moves to the pressure chamber 50 side through the flow passage 11 and can easily return the piston 10 to the original state.

  In the non-pressure chamber 60 of the cylinder 30, an elastic film 40 that is elastically deformed corresponding to the pressure fluctuation in the non-pressure chamber 60 is disposed. The elastic film 40 is made of a rubber film called a membrane, and is attached to a guide 32 inserted into the cylinder 30 as shown in the figure. Due to its elastic deformation, the non-pressure chamber 60, the pressure chamber 50, Has improved the flow of the working liquid Q between the two and contributes to the improvement of the performance of the damper device E1.

  In addition, a vent 33 is provided in the portion of the cylinder 30 that houses the elastic film 40 as shown in the figure. Therefore, the pressure around the elastic film 40 can be increased to atmospheric pressure, and the effect of the elastic film 40 can be further promoted.

  In the figure, reference numeral 34 denotes a cap, which is provided with an insertion hole 34a for the piston rod 17 in the center, and is attached to the open end 30a of the cylinder 30 so as to close the open end 30a.

  The guide 32 is formed in a substantially inverted H shape in front sectional view, and is fitted in an accommodation step portion 30 b formed on the open end 30 a side of the cylinder 30. The piston rod 17 is slidably inserted into an insertion hole 32a provided in the axial direction at the center of the guide 32, and is further inserted into a circumferential groove 32b provided on the cap 34 side. A packing 35 is accommodated so that the working liquid Q in the cylinder 30 can be prevented from leaking from the periphery of the piston rod 17 to the outside of the machine.

  The elastic film 40 is accommodated in a circumferential recess 32c formed in the axial direction at the center of the guide 32. The left and right circumferential ends 41 and 42 of the elastic film 40 are connected to the guide 32. The left and right flange portions 32d and 32e are fixed in recessed grooves 32f and 32g, and the space 32h formed on the inner periphery of the elastic membrane 40 is a communication hole formed in the right flange portion 32e. A space 32k formed between the outer circumference of the elastic membrane 40 and the inner circumference of the cylinder 30 communicates with the outside air through the vent hole 33.

  When there is an input from the control object to the piston rod 17, the force is transmitted from the piston rod 17 to the piston 10, and the piston 10 moves to the pressure chamber 50 side.

  Then, the valve body 20 is deflected to the non-pressure chamber 60 side by the pressure of the working liquid Q, each flow passage 11 is closed, a drag is applied to the piston 10 by the dynamic pressure resistance, and the movement is limited and input. Impact is alleviated.

  When there is no input from the controlled object to the piston rod 17 and the piston 10 is moved to the non-pressure chamber 60 side, the working liquid Q in the non-pressure chamber 60 passes through the flow passage 11 and moves to the pressure chamber 50 side. Then, with this moving pressure, the valve body 20 is pushed open to the pressure chamber 50 side, the working liquid Q in the non-pressure chamber 60 passes through the flow passage 11 and moves to the pressure chamber 50 side, and the piston 10 is easily moved to the original state. Return to.

  FIG. 3 is a front sectional enlarged explanatory view showing a main part of the damper device E2 according to the second embodiment of the present invention.

Since the main structure and effect of the damper device E2 according to the second embodiment are substantially the same as those of the damper device E1 of the first embodiment described above, only the structure that is characteristic of the second embodiment and the effects thereof will be described.
In the first embodiment, the pressure seat 50 side end surface 12 of the piston 10 is formed with a valve seat 13 having a conical inclined surface from the central portion of the piston 10 toward the outer peripheral edge. A valve seat 14 having a stepped inclined surface is formed. The valve seat 14 composed of this stepped inclined surface has a first inclined surface 14a having an inclination angle θa on the central portion side of the piston 10 and an inclination angle θb formed continuously on the outer peripheral side of the first inclined surface 14a. It is comprised from the 2nd inclined surface 14b.

  In the second embodiment, the inclination angle θa <the inclination angle θb is set, and the boundary edge between the first inclined surface 14a and the second inclined surface 14b is positioned in the vicinity of the center of the opening of each flow passage 11. . Accordingly, when the piston 10 is moved to the pressure chamber 50 side, the valve body 20 is deflected to the non-pressure chamber 60 side by the pressure of the working liquid Q, and first, a part of the valve body 20 is formed on the first inclined surface 14a having a small inclination angle θa. Is brought into contact with each other to close the central side of the piston 10 of each flow passage 11, and a damper effect corresponding to the closed area can be obtained. Further, the movement of the piston 10 toward the pressure chamber 50 is accelerated, and the working liquid Q When the pressure rises, the valve body 20 further bends, comes into contact with the second inclined surface 14b having a large inclination angle θb, and closes each of the flow passages 11 to obtain a large damper effect. The flow rate can be finely adjusted.

  Thus, when the valve seat 14 which consists of a stepped inclined surface is formed in the pressure chamber 50 side end surface 12 of the piston 10, when the pressure rise value in the pressure chamber 50 resulting from the movement to the pressure chamber 50 side of the piston 10 is small However, an appropriate damper effect can be obtained by reacting sensitively, and an appropriate damper effect can be obtained even when the pressure increase value is large.

  FIG. 4 is a front cross-sectional enlarged explanatory view showing a main part of a damper device E3 according to Embodiment 3 of the present invention.

Since the main configuration and effect of the damper device E3 according to the third embodiment are substantially the same as those of the damper device E1 of the first embodiment described above, only the configuration characteristic of the third embodiment and the effects achieved by the third embodiment will be described.
In the third embodiment, a valve seat 15 having an inclined surface composed of a curved surface from the central portion of the piston 10 toward the outer peripheral edge is formed on the end surface 12 of the piston 10 on the pressure chamber 50 side.

  In the third embodiment, since the valve seat 15 having an inclined surface made of a curved surface is formed, the inclination angle near the central portion of the piston 10 is eventually reduced, and the inclination angle can be increased toward the outer peripheral side.

  Therefore, when the piston 10 is moved to the pressure chamber 50 side, the valve body 20 is deflected to the non-pressure chamber 60 side by the pressure of the working liquid Q, and first, a part of the valve body 20 comes into contact with the central portion having a small inclination angle. The center side of the piston 10 in each flow passage 11 is closed, and a damper effect corresponding to the closed area can be obtained. Further, the movement of the piston 10 toward the pressure chamber 50 is accelerated, and the pressure of the working liquid Q increases. Then, the flow rate of the working liquid Q can be finely adjusted so that the valve body 20 is further bent, abuts against the outer peripheral side having a large inclination angle, and each flow passage 11 is closed to obtain a large damper effect. it can.

  When the valve seat 15 having the inclined surface formed of the curved surface is formed on the pressure chamber 50 side end surface 12 of the piston 10 in this way, the pressure increase value in the pressure chamber 50 due to the movement of the piston 10 toward the pressure chamber 50 is increased. Even when the pressure is small, it can react sensitively to obtain an appropriate damper effect, and even when the pressure increase value is large, an appropriate damper effect can be obtained.

  FIG. 5 is a front cross-sectional enlarged explanatory view showing a main part of a damper device E4 according to Embodiment 4 of the present invention.

Since the main configuration and effect of the damper device E4 according to the fourth embodiment are substantially the same as those of the damper device E1 according to the first embodiment described above, only the characteristic configuration of the fourth embodiment and the effects achieved by the fourth embodiment will be described. .
In Example 4, a plurality of valve bodies 20 are superposed and used.
(1) Valve body with the same size and performance (2) Valve body with different thickness (3) Valve body with a combination of valve bodies (4) 1-3 with different diameters, etc. It is composed by polymerization.

  Therefore, by preparing a large number of valve bodies as described above and combining them appropriately, a damper device having the required performance can be easily obtained.

  For example, as shown in FIG. 5, an existing valve element 21 having a diameter of Amm and a thickness of Tmm is disposed on the piston 10 side, and on the outside thereof, the diameter is smaller than the valve element 21 and the diameter is Aamm and the thickness is Ttmm. When the valve body 20 is formed by superposing the existing valve body 22, a valve body having a function substantially equivalent to that of a newly manufactured valve body in which the thickness of the valve body 21 is Tmm + Ttmm can be obtained. Compared with the case where a body is newly manufactured, a significant cost reduction can be achieved.

  FIG. 6 is a front sectional enlarged explanatory view showing a main part of a damper device E5 according to Embodiment 5 of the present invention.

Since the main configuration and effect of the damper device E5 according to the fifth embodiment are substantially the same as those of the damper device E1 according to the first embodiment described above, only the characteristic configuration of the fifth embodiment and the effects achieved by the fifth embodiment will be described. .
In the fifth embodiment, the end face 12 on the pressure chamber 50 side of the piston 10 is not formed with a valve seat having an inclined surface as in the other embodiments, but is configured by a valve seat 16 having a flat surface. The valve body 20 is provided on a guide bar 10 a protruding from the flat piston 10 on the pressure chamber 50 side so as to be movable in the axial direction via a spacer 70. That is, the valve body 20 is mounted apart from the valve seat 16 formed of the flat surface of the piston 10 by the thickness of the spacer 70, and the pressure chamber 50 of the piston 10 is the same as in the other embodiments described above. A gap K is formed with the side surface.

  Therefore, when the piston 10 is moved to the pressure chamber 50 side, the valve body 20 is deflected to the non-pressure chamber 60 side by the pressure of the working liquid Q, a part of the valve body 20 comes into contact, and a part of each flow passage 11 is closed. A damper effect corresponding to the closed area can be obtained, and when the movement of the piston 10 toward the pressure chamber 50 is accelerated and the pressure of the working liquid Q rises, the valve body 20 is further bent and each flow passage 11 is bent. The flow rate of the working liquid Q can be finely adjusted so that the whole can be closed and a large damper effect can be obtained.

  By appropriately selecting the thickness of the spacer 70, a damper device having the required performance can be easily obtained.

It is front view cross-section explanatory drawing which shows the damper apparatus E1 which concerns on Example 1 of this invention. It is front view cross-section enlarged explanatory drawing which shows a principal part same as the above. It is front view cross-section enlarged explanatory drawing which shows the principal part of the damper apparatus E2 which concerns on Example 2 of this invention. It is front view cross-section expansion explanatory drawing which shows the principal part of the damper apparatus E3 which concerns on Example 3 of this invention. It is front view cross-section expansion explanatory drawing which shows the principal part of the damper apparatus E4 which concerns on Example 4 of this invention. It is front view cross-section expansion explanatory drawing which shows the principal part of the damper apparatus E5 which concerns on Example 5 of this invention.

Explanation of symbols

10 piston
11 Flow passage 12 End face of piston
DESCRIPTION OF SYMBOLS 13 Valve seat which consists of inclined surfaces 14 Valve seat which consists of stepped inclined surfaces 15 Valve seat which consists of curved surfaces 16 Valve seat which consists of flat surfaces θ Inclination angle 20 Valve body
t Valve body thickness D Valve body diameter 30 Cylinder 31 Liquid chamber 50 Pressure chamber 60 Non-pressure chamber side
Q Working liquid

Claims (5)

A cylinder for enclosing the working liquid to form a liquid chamber;
A piston that divides the liquid chamber into a pressure chamber side and a non-pressure chamber side and is movably disposed;
In the damper device provided with a valve body capable of opening and closing the flow passage by bending while having a flow passage allowing the working liquid to flow between the pressure chamber side and the non-pressure chamber side,
The damper device is characterized in that the valve body is provided on the pressure chamber side and the valve body is formed of a material whose elastic coefficient changes according to a temperature change. The damper device according to claim 1,
A damper device comprising a valve seat having an inclined surface extending from a central portion of the piston toward an outer peripheral edge on a pressure chamber side end surface of the piston. The damper device according to claim 2, wherein
The damper device according to claim 1, wherein the valve seat of the piston is formed in a conical surface or a stepped conical surface or a so-called curved surface. The damper device according to any one of claims 1 to 3,
A damper device in which a plurality of the valve bodies are superposed. The damper device according to claim 1,
The damper device is characterized in that the valve body is provided via a spacer with respect to a flat piston valve seat.

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