JP2006207700A - Fluid pressure damper and elevating storage device equipped therewith - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a novel fluid pressure damper having simple construction for generating desired braking force in a desired operation region, and to provide an elevating storage device equipped therewith. <P>SOLUTION: The fluid pressure damper comprises a casing filled with fluid and a piston member for sliding along the inner wall of the casing. Particularly, a gap between the inner wall of the casing and the piston member is changed corresponding to the sliding stroke of the piston member. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fluid pressure damper for applying a braking force to the operation of a movable body that is configured to move or operate mainly within a certain range, and a lift storage device including the fluid pressure damper.

  It is configured to move or operate within a certain range, such as a lifting and lowering storage device that is installed at a kitchen height and configured so that the storage case attached to one end of the arm can be raised and lowered within a certain range. When operating the movable body, an inertial force is generated on the movable body and the article loaded on the movable body at the end of the operation range, so that a large impact sound is generated or damage or deformation is caused. To do.

  This is a problem mainly caused by the sudden stop of such a movable body at the end of the operating range. In order to prevent such a sudden stop of the movable body, a fluid pressure damper such as an air damper or an oil damper is used. (Shock absorber) is generally attached to attenuate the kinetic energy during movement or operation of the movable body.

  Examples of such a fluid pressure damper that controls the operation of the movable body include a linear motion type as shown in the sectional view of FIG. 1 and a rotary motion type as shown in the sectional view of FIG. be able to.

  A linear motion type fluid pressure damper 1 shown in FIG. 1 is a fluid pressure damper 1 composed of a substantially cylindrical casing (cylinder) 2, a fluid injected into the casing 2, a piston 3 and a piston rod 4. The piston 3 is provided with a fluid flow passage 5 so that a certain amount of fluid can pass from the pressure chamber toward the non-pressure chamber as the piston 3 moves.

  In the fluid pressure damper 1 shown in FIG. 1, when a force is applied to the piston 3 in the direction of A in the figure, the working fluid in the casing 2 passes through the fluid flow passage 5 provided in the piston 3. Then, it flows from the chamber 6 on the pressure chamber side into the chamber 7 on the non-pressure chamber side, and the piston 3 moves in the direction A.

  At this time, the resisting force generated when the working fluid passes through the fluid flow passage 5 causes the piston 3 to receive a resisting force in the direction opposite to the direction A, and the kinetic energy is attenuated so that the moving speed of the piston 3 is It becomes slow, and this is a mechanism to obtain a damper effect (braking force).

  Further, when a force is applied to the piston 3 in the direction opposite to A in the figure, the piston 3 receives a resistance force in the direction A, that is, the fluid pressure damper shown in FIG. That is, the same damper effect appears even if force is applied to the piston 3 from any direction.

  On the other hand, the rotary motion type hydraulic pressure damper 1 shown in FIG. 2 is combined so as to be rotatable with respect to the cylindrical casing 2 having a partition wall 8 projecting on the inner wall, the fluid injected into the casing 2, and the casing 2. This is a fluid pressure damper 1 composed of a rotor provided with a piston (rotary blade) 3.

  The fluid pressure damper 1 shown in FIG. 2 passes through a very small gap (clearance) formed by the piston 3 and the inner wall of the casing 2 when a force is applied to rotate the rotor clockwise in the figure. The working fluid in 2 flows from the chamber 6 on the pressure chamber side into the chamber 7 on the non-pressure chamber side, and the piston 3 moves in the rotation direction.

  At this time, the piston 3 receives a resistance force in the direction opposite to the rotation direction due to the resistance force generated when the working fluid passes through a very small gap formed by the piston 3 and the inner wall of the casing 2, and the kinetic energy is attenuated. As a result, the moving speed of the piston 3 becomes slow, whereby a damper effect (braking force) is obtained.

  In addition, when a force for rotating the rotor in the counterclockwise direction is applied, the piston 3 receives a resistance force in a direction opposite to the rotation direction. That is, the fluid pressure damper shown in FIG. The same damper effect appears regardless of the rotational force applied to the rotor in any direction.

  However, in general, the situation where attenuation of kinetic energy at the time of movement or operation of the movable body is required is almost the case where the movable body is prevented from suddenly dropping due to acceleration due to attractive force or the like. In general, the required damper effect is only when the movable body operates in one direction, and when the movable body operates in the other direction, it is hardly necessary and additional resistance is always required. It is not a thing.

  In view of this point, fluid pressure dampers that exhibit a damper effect only in one direction of operation have been developed (for example, Patent Documents 1 to 4).

JP 2000-145869 A JP 2001-82522 A JP-A-4-283636 Japanese Patent Laid-Open No. 3-267027

  However, when such a fluid pressure damper that exhibits a damper effect only in one-way operation is applied, for example, to a portion that brakes the lifting / lowering operation in the lifting / lowering storage device, in the operation of pulling down the storage case, the fluid pressure damper Since the damping force can be applied by the damper, the storage case can be prevented from suddenly dropping.On the other hand, when the storage case is returned to the original position, the storage case and the storage case are attached to the end of the operation range. Since the inertial force generated on the loaded article cannot be attenuated, a large impact sound is generated due to a sudden stop of the storage case, or the storage case or the stored item is damaged or deformed.

  That is, it is not always required that the braking force is generated during the operation of the movable body, but there is also a complicated requirement that the braking force is required only at the end point of the operation.

  Therefore, as a result of repeated studies by the inventor to solve such problems, a fluid pressure damper comprising a casing into which a fluid is injected and a piston member that slides along the inner wall of the casing, In response to the sliding stroke of the piston member, a fluid pressure damper characterized in that a change occurs in the gap formed by the inner wall of the casing and the piston member has been completed.

  That is, the present inventor makes a change in the clearance (clearance) formed between the inner wall of the casing and the piston member in accordance with the sliding stroke (stroke) of the piston member in this type of fluid pressure damper. Depending on the position of the piston member in the casing, the gap (clearance) formed by the inner wall of the casing and the piston member is made narrower or wider, so that the difference in the sliding stroke of the piston member It has been found that the amount of fluid movement from the pressure chamber to the non-pressure chamber can be changed, and the braking force generated thereby can be controlled.

  The present invention has been completed on the basis of the above knowledge, and has a novel fluid pressure damper capable of generating a desired braking force in a desired operating range with a simple structure, and a lifting and lowering storage device including the same. The purpose is to provide.

The fluid pressure damper of the present invention, which is a means for solving the above problems, is a fluid pressure damper comprising a casing into which a fluid is injected and a piston member that slides along the inner wall of the casing. In accordance with the movement stroke, the gap formed by the inner wall of the casing and the piston member is changed.
Hereinafter, the fluid pressure damper of the present invention will be described in detail.

  The fluid pressure damper of the present invention is not particularly limited as long as it is composed of a casing into which fluid is injected and a piston member that slides along the inner wall of the casing and partitions the inside of the casing into a pressure chamber and a non-pressure chamber. Specifically, for example, a substantially cylindrical (cylindrical) casing, a linear motion fluid pressure damper including a piston and a piston rod, a cylindrical casing having one or more partition walls projecting from the inner wall, and the casing And a rotary motion type hydraulic pressure damper composed of a rotor having one or a plurality of pistons (rotary blades) rotatably combined with each other.

  Further, as the “fluid” injected into the casing, when the fluid pressure damper of the present invention is configured as an oil damper, at least one selected from various liquids such as water and oil can be appropriately selected and used. When the fluid pressure damper of the present invention is configured as an air damper, at least one selected from various gases such as air, nitrogen, oxygen, and oxygen dioxide can be appropriately selected and used.

  In the case where the fluid pressure damper of the present invention is configured as an air damper, it is not always necessary to inject the fluid positively, and air in the atmosphere may be used. "Injecting" means that fluid is present in the casing.

  Further, in the fluid pressure damper of the present invention, a seal member may be provided between the piston member and the inner wall of the casing, and the seal member is not particularly limited. It is provided by providing a groove and inserting a packing such as an O-ring in the concave groove.

  In the fluid pressure damper of the present invention, the greatest feature is that the gap (clearance) formed by the inner wall of the casing and the piston member is changed corresponding to the sliding stroke of the piston member. Have

  That is, in general, the situation where attenuation of kinetic energy during movement or operation of the movable body is required is almost the case in which the movable body is prevented from suddenly dropping due to acceleration caused by attractive force or the like. In general, the required damper effect is only when the movable body operates in one direction, and when the movable body operates in the other direction, it is hardly necessary and additional resistance is always required. It is not a thing.

  Further, although it is not always required that the braking force is generated during the operation of the movable body, there is a complicated requirement that the braking force is required only at the end point of the operation.

  With respect to this point, in the fluid pressure damper of the present invention, the gap (clearance) formed by the inner wall of the casing and the piston member is changed corresponding to the sliding stroke (stroke) of the piston member, that is, the casing. Depending on the sliding stroke of the piston member, the gap (clearance) formed by the inner wall of the casing and the piston member is narrowed or widened depending on the position of the piston member inside the pressure chamber. The amount of movement of the fluid from the pressure chamber to the non-pressure chamber can be changed, and the braking force generated thereby can be controlled.

  That is, if the gap formed by the inner wall of the casing and the piston member becomes wide during the sliding stroke of the piston member, the amount of fluid movement from the pressure chamber to the non-pressure chamber increases by the gap, and the generated braking force On the other hand, if the gap formed between the inner wall of the casing and the piston member becomes narrow during the sliding stroke of the piston member, naturally, the amount of fluid moving from the pressure chamber to the non-pressure chamber is reduced, and this occurs. The braking force is weakened.

  Therefore, during the sliding stroke of the piston member, a desired braking force can be obtained in a desired operating range by causing a change in the gap formed between the casing inner wall and the piston member.

  In order to cause a change in the clearance (clearance) formed by the inner wall of the casing and the piston member corresponding to the sliding stroke (stroke) of the piston member, for example, a substantially cylindrical casing, a piston and a piston rod are used. In the linear motion type hydraulic pressure damper, this can be achieved by stepwise or continuously changing the inner diameter of the substantially cylindrical inner wall of the casing, and one or more partition walls are provided on the inner wall. In a rotary motion type hydraulic pressure damper composed of a cylindrical casing and a rotor provided with a piston (rotary vane) rotatably combined with the casing, R (radius = radius) of the inner wall of the casing is stepwise or This can be achieved by changing continuously.

  Here, in the fluid pressure damper according to the present invention, a “fluid circulation” allows a certain amount of fluid to move from the pressure chamber in the casing partitioned by the piston to the non-pressure chamber with respect to the piston, if necessary. A “road” may be provided.

  In particular, in the fluid pressure damper of the present invention, it is preferable to provide a “check valve mechanism” that opens and closes a clearance (clearance) formed by the fluid passage and / or the inner wall of the casing and the piston member in response to the fluid pressure. With this configuration, the piston moves smoothly in the direction in which the check valve mechanism is opened, while the piston moves in the direction in which the check valve mechanism closes. Because the movement of the piston is controlled, the damper effect can be exerted strongly, and in combination with the change in the clearance (clearance) formed by the inner wall of the casing and the piston member, more complex control of the braking force can be realized. Can do it.

  The check valve mechanism is not particularly limited as long as the check valve mechanism can be opened and closed in accordance with the sliding direction of the piston. A check valve hole is formed by providing a space in the check valve hole, and the check valve member inserted into the check valve hole changes its position in the hole according to the movement direction of the fluid. Can open and close the fluid flow path.

  In particular, in the fluid pressure damper of the present invention, the inner diameter of the substantially cylindrical inner wall of the casing is changed continuously or stepwise, or the R (R) of the casing is changed continuously or stepwise. Since the gap (clearance) formed by the casing and the piston member is changed, a cup-shaped check valve made of a flexible material such as silicon rubber can be appropriately adapted to the change in the gap. The member is preferably provided on the piston member, and this is preferably a check valve mechanism.

  In other words, the cup-shaped check valve member provided on the piston allows fluid to move from the side surface (periphery) of the cup-shaped check valve member when fluid pressure is received from the rear (the bottom side of the cup). The damper effect is hardly manifested, but conversely, when the fluid pressure is received from the front (the opening side of the cup), the cup is spread and the gap formed between the fluid flow passage and the inner wall of the casing and the piston member Since the (clearance) is closed, the amount of fluid movement is controlled, and the damper effect can be strongly developed.

  The lifting / lowering storage device of the present invention is provided with the fluid damper of the present invention, i.e., the fluid damper of the present invention is applied to a portion that applies a braking force to the lifting / lowering operation of the lifting / lowering device. Is adopted.

  Thus, in the lifting and lowering storage device of the present invention, not only can the damper effect be designed to occur in any operating range of the lifting and lowering operation, but more complex control can be realized by using the check valve mechanism, for example, When pulling down the storage case in the lifting and lowering storage device, braking force is generated and it can be slowly and safely pulled down. When returning the storage case to its original position, the storage case only at the end of its operating range In addition, it is possible to generate a braking force that attenuates the inertial force generated on the article loaded thereon.

  The present invention is a novel fluid pressure damper having the above-described configuration and capable of generating a desired braking force in a desired operating range with a simple structure, and a lifting / lowering storage device including the same.

  That is, the fluid pressure damper according to the present invention changes the clearance (clearance) formed between the inner wall of the casing and the piston member in accordance with the sliding stroke (stroke) of the piston member. Depending on the position of the piston member, the gap (clearance) formed between the inner wall of the casing and the piston member becomes narrower or wider, so that the pressure chamber can The amount of fluid movement to the non-pressure chamber can be changed, and the braking force generated thereby can be controlled.

  Further, the lifting and lowering storage device of the present invention is characterized in that the fluid damper of the present invention is provided, and not only can the damper effect be generated at the end point of the lifting operation, but also a check valve mechanism. In combination with the realization of more complicated control, for example, when pulling down the storage case in the lifting and lowering storage device, braking force is generated in the entire operating range, and it can be slowly and safely pulled down. In the case of returning to the original position, it is possible to generate a braking force that attenuates the inertial force generated on the storage case and the article loaded on the storage case only at the end point of the operation range. .

  Examples of the present invention will be described below, but the present invention is not limited to these examples.

  FIG. 3 is a sectional view showing a fluid pressure damper 1 according to the first embodiment of the present invention. The fluid pressure damper 1 is a linear motion type consisting of a casing 2 into which a fluid is injected, a piston member 3 and a piston rod 4. The fluid pressure damper 1 is formed by forming the inner wall of the casing 2 and the piston member 3 corresponding to the sliding stroke (stroke) of the piston member 3 by changing the inner diameter of one end of the casing 2 on the piston rod 4 side to be small. The gap (clearance) is changed.

  Further, the piston member 3 is provided with a fluid flow passage 5 in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3. A concave groove is provided on the side surface, and an O-ring 9 is fitted in the concave groove.

  Then, the fluid pressure damper 1 according to the present embodiment has the inside of the chamber 6 that becomes a pressure chamber when a force is applied to the piston member 3 in the direction A in the figure from the state of FIG. This fluid can move to the chamber 7 which is a non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5. Since no resistance force is generated, the movement of the piston member 3 is smooth and the state shown in FIG. 3B is obtained with almost no braking force.

  On the other hand, when a force is applied to the piston member 3 in the direction opposite to A in the figure from the state of FIG. 3B, the fluid in the chamber 7 serving as the pressure chamber is separated from the inner wall of the casing 2 and the piston member. 3, it is possible to move to the chamber 6 which is a non-pressure chamber through both the clearance (clearance) formed by the fluid passage 3 and the fluid flow passage 5, and almost no resistance force is generated at that time. The movement of No. 3 is smooth and the state shown in FIG. 3C is obtained with almost no braking force.

  However, when a force is applied to the piston member 3 in the direction opposite to A in the figure beyond the state of FIG. 3C, the gap formed between the inner wall of the casing 2 and the piston member 3 ( (Clearance) becomes narrower (FIG. 3 (d)), coupled with the improvement in airtightness by the O-ring 9, the fluid movement from the room 7 to the room 6 passes only through the fluid flow path 5, The piston member 3 receives the resistance force in the direction A in the figure due to the resistance force generated at the time, and the kinetic energy is attenuated to obtain the damper effect.

  3D, when a force is applied to the piston member 3 in the direction of A in the figure, a damper effect is obtained until the state of FIG. 3C is reached. The damper effect disappears when the state of (c) is exceeded.

  That is, the fluid pressure damper according to the first embodiment operates in the final operation region when a force is applied in the opposite direction of A in the drawing and from the state shown in FIG. 3D to the state shown in FIG. The damper effect is controlled to occur in the region.

  FIG. 4 is a cross-sectional view showing a fluid pressure damper 1 according to the second embodiment of the present invention. The fluid pressure damper 1 is a linear motion type consisting of a casing 2, a piston member 3, and a piston rod 4 into which fluid is injected. The fluid pressure damper 1 is a gap (clearance) formed between the inner wall of the casing 2 and the piston member 3 corresponding to the sliding stroke (stroke) of the piston member 3 by changing the inner diameter at both ends of the casing 2 to be small. This is a change.

  The piston member 3 is provided with a fluid flow passage 5 in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3. Two concave grooves are provided in each of which O-rings 9 (9a, 9b) are fitted.

  Then, the fluid pressure damper 1 according to the present embodiment has the inside of the chamber 6 that becomes a pressure chamber when a force is applied to the piston member 3 in the direction A in the figure from the state of FIG. Can move to the room 7 which is a non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5. Since almost no resistance force is generated, the movement of the piston 3 is smooth, and the state shown in FIG. 4B is obtained with almost no braking force.

  However, when a force is further applied to the piston member 3 in the direction A in the figure beyond the state of FIG. 4B, a clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3. (Fig. 4 (c)), coupled with the improvement of the airtightness by the O-ring 9, the fluid movement from the room 6 to the room 7 passes only through the fluid flow path 5, and in that case The piston member 3 receives the resistance force in the direction opposite to the direction A, and the kinetic energy is attenuated by the resistance force generated in the direction A, thereby obtaining a damper effect.

  4C, when a force is applied to the piston member 3 in the direction opposite to A in FIG. 4, a damper effect is obtained until the state shown in FIG. 4B is reached. The damper effect disappears when the state of 4 (b) is exceeded.

  On the other hand, when a force is applied to the piston member 3 in the direction opposite to A in the figure from the state of FIG. 4A, the fluid in the chamber 7 serving as the pressure chamber is separated from the inner wall of the casing 2 and the piston member. 3 and the fluid flow passage 5 through both the clearance (clearance) and the fluid flow passage 5, it is possible to move to the room 6 that is a non-pressure chamber. The movement of the piston member 3 is smooth, and the state shown in FIG. 4D is obtained with almost no braking force.

  However, when a force is applied to the piston member 3 in the direction opposite to the direction A in the figure beyond the state of FIG. 4D, the clearance (clearance) formed between the inner wall of the casing 2 and the piston member 3. ) Becomes narrow (FIG. 4 (e)), coupled with the improvement of the airtightness by the O-ring 9, the fluid movement from the room 7 to the room 6 passes only through the fluid flow path 5, Due to the resistance force generated at that time, the piston 3 receives the resistance force in the direction of A, and the kinetic energy is attenuated to obtain a damper effect.

  4 (e), when a force is applied to the piston member 3 in the direction of A in the figure, a damper effect is obtained until the state of FIG. 4 (d) is reached. The damper effect disappears when the state of (d) is exceeded.

  That is, the fluid pressure damper according to the second embodiment reaches any state of the final operation region when the force is applied in the direction opposite to A or A in the drawing, from the state shown in FIG. 4C to the state shown in FIG. In the operation region up to and in the operation region from the state of FIG. 4E to the state of FIG. 4D, the damper effect is controlled.

  FIG. 5 is a cross-sectional view showing a fluid pressure damper 1 according to the third embodiment of the present invention. The fluid pressure damper 1 is a linear motion type composed of a casing 2, a piston member 3, and a piston rod 4 into which fluid is injected. The fluid pressure damper 1 is formed by forming the inner wall of the casing 2 and the piston member 3 corresponding to the sliding stroke (stroke) of the piston member 3 by changing the inner diameter small at one end of the casing 2 on the piston rod 4 side. The gap (clearance) is changed.

  Further, the piston member 3 is provided with a fluid flow passage 5 in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3. A concave groove is provided on the side surface, and the O-ring 9 is fitted in the concave groove 31.

  In particular, in this embodiment, as a check valve mechanism, a cup-shaped check valve member 10 is disposed on the end surface of the piston member 3 (on the opposite side surface on the piston rod 4 side) toward the opposite side on the piston rod 4 side. It is prepared in an open state.

  When the fluid pressure damper 1 according to this embodiment is applied with force to the piston member 3 in the direction A in the figure from the state of FIG. 10 is expanded and the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 is closed (that is, the check valve mechanism is closed), so that the pressure chamber 6 is changed from the pressure chamber 6 to the non-pressure chamber. The movement of the fluid to a certain chamber 7 passes only through the fluid flow passage 5 (via the orifice passage 11 penetrating the check valve member 10), and the resistance force generated at that time causes the piston 3 to The kinetic energy is attenuated by receiving a resistance force in the direction opposite to the direction A, and a damper effect is obtained until the state shown in FIG.

  Next, when force is applied to the piston member 3 in the direction opposite to A in the figure from the state of FIG. 5B, the fluid can pass through the side surface (surrounding) of the check valve ( That is, since the check valve mechanism is in an open state), the fluid in the chamber 7 serving as the pressure chamber passes through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow path 5. Since it is possible to move to the non-pressure chamber 6 and almost no resistance force is generated at that time, the movement of the piston member 3 is smooth and almost no braking force is generated. It will be in the state of (c).

  However, when a force is applied to the piston member 3 in the direction opposite to A in the figure beyond the state of FIG. 5C, a clearance (clearance) formed between the inner wall of the casing 2 and the piston member 3 is formed. ) Becomes narrow (FIG. 5 (d)), coupled with the improvement of the airtightness by the O-ring 9, the fluid movement from the room 7 to the room 6 passes only through the fluid flow path 5, Due to the resistance force generated at that time, the piston 3 receives the resistance force in the direction of A, and the kinetic energy is attenuated to obtain a damper effect.

  That is, when a force is applied to the fluid pressure damper in the third embodiment in the direction A in the figure, a damper effect is generated in the entire operation area, while on the other hand, a force is applied in the opposite direction to A in the figure. Are controlled so that the damper effect is generated only in the final operation region.

  FIG. 6 is a cross-sectional view showing a fluid pressure damper 1 of the present invention according to a fourth embodiment. The fluid pressure damper 1 is a linear motion type consisting of a casing 2 into which a fluid is injected, a piston member 3 and a piston rod 4. It is a fluid pressure damper 1, and the inner wall of the casing 2 and the piston member corresponding to the sliding stroke (stroke) of the piston member 3 by changing the inner diameter small at one end of the casing 2 opposite to the piston rod 4 side. 3 is caused to change in the gap (clearance) formed by 3.

  Further, the piston member 3 is provided with a fluid flow passage 5 in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3. A concave groove is provided on the side surface, and the O-ring 9 is fitted in the concave groove 31.

  In particular, in this embodiment, as a check valve mechanism, a cup-shaped check valve member 10 is opened on the end surface of the piston member 3 (the surface on the piston rod 4 side) toward the opposite side of the piston rod 4 side. Prepared in the state.

  When the fluid pressure damper 1 according to this embodiment is applied with force to the piston member 3 in the direction A in the figure from the state shown in FIG. 10 is expanded and the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 is closed (that is, the check valve mechanism is closed), so that the pressure chamber 6 is changed from the pressure chamber 6 to the non-pressure chamber. The movement of the fluid to a certain chamber 7 passes only through the fluid flow passage 5 (via the orifice passage 11 penetrating the check valve member 10), and the resistance force generated at that time causes the piston 3 to The kinetic energy is attenuated by receiving a resistance force in the direction opposite to the direction A, and a damper effect is obtained until the state shown in FIG.

  6B, when a force is applied to the piston member 3 in the direction opposite to A in the figure, the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 is narrowed. Therefore, the fluid movement from the chamber 7 to the chamber 6 passes only through the fluid flow path 5 in combination with the improvement of the airtightness by the O-ring 9, and the piston 3 is caused by the resistance force generated at that time. In response to the resistance force in the direction A, the kinetic energy is attenuated, and the damper effect is obtained until the state shown in FIG.

  However, when the force is applied to the piston member 3 in the direction opposite to the direction A in the figure beyond the state of FIG. 6C, the clearance (clearance) formed between the inner wall of the casing 2 and the piston member 3. ) And the fluid can pass through the side surface (surrounding) of the check valve (that is, the check valve mechanism is in an open state), the fluid in the chamber 7 serving as the pressure chamber is transferred to the casing 2. It is possible to move to the non-pressure chamber 6 through both the clearance (clearance) formed by the inner wall and the piston member 3 and the fluid flow passage 5, and almost no resistance force is generated at that time. Therefore, the movement of the piston member 3 is smooth, and the state shown in FIG. 5D is obtained with almost no braking force.

  That is, when a force is applied in the direction of A in the figure, the fluid pressure damper in the fourth embodiment has a damper effect in the entire operation area, while a force is applied in the opposite direction of A in the figure. Are controlled so that the damper effect is generated in the operating range from the state of FIG. 6B to the state of FIG. 6C.

  FIG. 7 is a perspective view showing the lifting and lowering storage device 12 according to the fifth embodiment of the present invention, which is partially shown in a transparent state so that a rotation mechanism provided therein can be seen.

  The lifting and lowering storage device 12 shown in this figure has a structure in which a storage case 14 is accommodated in the outer casing 13, and the user pulls the handle 15 provided at the lower front portion of the storage case 14 forward, The storage case 14 protrudes forward from the outer casing 13 and descends to the user's working position.

  The lifting and lowering operation in the lifting and lowering storage device 12 is performed by two pivots 18 (18a and 18b) respectively provided by two arms 17 (main arm 17a and auxiliary arm 17b) pivotally attached to a base 16 fixed to the outer casing 13. ) Around the arm 17 (17a, 17b) is employed so that the arm 17 (17a, 17b) moves or operates within a certain range. The storage case 14 pivotally attached to the end 19 (19a, 19b) of each arm 17 (17a, 17b) is moved up and down by rotating.

  The rotating mechanism is provided with the fluid pressure damper 1 of the present invention in the auxiliary arm 17b in order to give a braking force to the raising / lowering operation of the storage case 14, and the urging force is applied to the rotating operation of the rotating mechanism. Is provided on the main arm 17a.

  Here, in the case where the fluid pressure damper 1 described in the third embodiment is provided as the fluid pressure damper 1, when the storage case 14 is pulled down, a braking force is generated in the entire operation area. On the other hand, when the storage case 14 is stored in the outer casing 13, braking force is generated only at the end point of the operation area. It is possible to attenuate the inertial force generated with respect to the case, and it is possible to prevent a large impact sound from being generated and the article in the storage case from being damaged or deformed.

  On the other hand, when the fluid pressure damper 1 includes the fluid pressure damper 1 described in the fourth embodiment, when the storage case 14 is pulled down, a braking force is generated in the entire operation area. Since the damper effect works against the urging force of the spring mechanism 4 when it is pulled down to the lowest point, when the storage case 14 is pulled down to the lowest point, the spring mechanism 20 The urging force can prevent the storage case 14 from bouncing up and making the storage operation difficult.

  The damper effect against the urging force of the spring mechanism 4 occurs only in the first very small operating range in the operation of storing the storage case 14 in the outer casing 13, and in the entire operating range in which the storage case 14 is stored. It does not give resistance.

  FIG. 8 is a cross-sectional view showing a fluid pressure damper 1 according to the sixth embodiment of the present invention. The fluid pressure damper 1 is injected into a cylindrical casing 2 having a partition wall 8 projecting from an inner wall thereof and the casing 2. 1 is a rotary motion type fluid pressure damper 1 composed of a rotor having a piston member 3 rotatably combined with the casing 2, and is about 6 toward the clockwise direction of rotation of the rotor in the figure. The clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 corresponding to the sliding stroke (stroke) of the piston member 3 by continuously reducing the R (R = radius) of the casing from the position of the hour. ).

  The piston member 3 is provided with a fluid flow passage 5 in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3. 3 is provided with a cup-shaped check valve member 10 as a check valve mechanism in an open state toward the chamber 6.

  When the fluid pressure damper 1 according to the present embodiment is applied with force from the state of FIG. 9A to the arm 17 provided on the rotor shaft in the rotational direction A in the figure. The fluid in the chamber 7 serving as the pressure chamber can move to the chamber 6 serving as the non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5. In this case, since almost no resistance force is generated, the movement of the piston member 3 is smooth and the state shown in FIG. 9B is obtained with almost no braking force.

  On the other hand, when force is applied to the piston member 3 in the direction of rotation opposite to A in the figure from the state of FIG. The fluid can move to the room 7 which is a non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 6, and in that case, most of the fluid can move. Since no resistance force is generated, the movement of the piston 3 is smooth and the state shown in FIG. 9C is obtained with almost no braking force.

  However, the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 gradually narrows from the point where the state shown in FIG. 9C is exceeded to the state shown in FIG. 9D. When the stop valve member 10 is expanded, the movement of the fluid from the chamber 22 to the chamber 21 passes only through the fluid flow passage 5 (via the orifice passage 11 passing through the check valve member 10). The piston 3 receives the resistance force in the rotation direction A due to the resistance force generated at that time, so that the kinetic energy is attenuated and the damper effect is obtained.

  That is, the fluid pressure damper in the sixth embodiment is controlled so that a damper effect is generated in the final operation region when a force is applied in the direction of rotation opposite to A in the drawing.

  FIG. 10 is a cross-sectional view showing a fluid pressure damper 1 of the present invention according to a seventh embodiment. The fluid pressure damper 1 is injected into a cylindrical casing 2 having a partition wall 8 protruding from an inner wall, and the casing 2. 1 is a rotary motion type fluid pressure damper composed of a rotor having a piston member 3 rotatably combined with the casing 2, and is located at about 6 o'clock in the clockwise direction of the rotor. And from the position of about 2 o'clock in the counterclockwise rotation direction of the rotor, the R (radius = radius) of the casing 2 is continuously reduced to correspond to the sliding stroke (stroke) of the piston member 3. Thus, a change is made in the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3.

  The piston member 3 is provided with fluid flow passages 5 (5a, 5b) in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3, On both end faces of the piston member 3, cup-shaped check valve members 10 (10a, 10b) as check valve mechanisms are provided in a state of opening in the direction of the room 6 and the room 7, respectively.

  When the fluid pressure damper 1 according to the present embodiment is applied with force from the state of FIG. 11A to the arm 17 provided on the rotor shaft in the rotational direction A in the figure. The fluid in the chamber 7 serving as the pressure chamber can move to the chamber 6 serving as the non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5. In this case, since almost no resistance force is generated, the movement of the piston member 3 is smooth and the state shown in FIG.

  However, the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 gradually narrows from the point where the state shown in FIG. 11 (b) is exceeded to the state shown in FIG. 11 (c). When the stop valve member 10b is expanded, the fluid movement from the chamber 7 to the chamber 6 passes only through the fluid flow passage 5 (via the orifice passage 11b passing through the check valve member 10b). Since the piston 3 receives the resistance force in the direction opposite to the direction A due to the resistance force generated at that time, the kinetic energy is attenuated and a damper effect is obtained.

  On the other hand, when a force is applied to the arm 17 provided on the shaft of the rotor from the state shown in FIG. The fluid can move to the room 7 which is a non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5, and in that case, most of the fluid flows. Since no resistance force is generated, the movement of the piston member 3 is smooth and the state shown in FIG.

  However, the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 gradually narrows from the point where the state shown in FIG. 11 (d) is exceeded to the state shown in FIG. 11 (e). When the stop valve member 10a is expanded, the fluid movement from the chamber 6 to the chamber 7 passes only through the fluid flow passage 5 (via the orifice passage 11a penetrating the check valve member 10a). Since the piston 3 receives the resistance force in the direction A by the resistance force generated at that time, the kinetic energy is attenuated and the damper effect is obtained.

  That is, the fluid pressure damper in the seventh embodiment is controlled so that the damper effect is generated in any final operation region when a force is applied in the direction A or in the opposite direction to A in the drawing.

  FIG. 12 is a cross-sectional view showing a fluid pressure damper 1 of the present invention according to an eighth embodiment. The fluid pressure damper 1 is injected into a cylindrical casing 2 having a partition wall 8 projecting from an inner wall thereof and the casing 2. 1 is a rotary motion type fluid pressure damper 1 composed of a rotor provided with a piston member 3 rotatably combined with the casing 2, and is about 6 in the clockwise direction of the rotor in the drawing. The inner wall of the casing 2 and the piston member 3 are formed corresponding to the sliding stroke (stroke) of the piston member 3 by continuously reducing the R (radius = radius) of the casing from the time position. This is a change in the clearance (clearance).

  The piston member 3 is provided with fluid flow passages 5 (5a, 5b) in which fluid can move between the chamber 6 and the chamber 7 in the casing 2 partitioned by the piston member 3, As a check valve mechanism on both end faces of the piston member 3, a cup-like check valve member 10 (a small check valve 10a corresponding to the minimum R on the inner wall of the casing 2 and a maximum R on the inner wall of the casing 2) is used. Corresponding large check valves 10b) are provided open in the direction of the rooms 6 and 7, respectively.

  When the fluid pressure damper 1 according to the present embodiment is applied with force in the rotational direction A in the figure from the state of FIG. 13A to the arm 17 provided on the shaft of the rotor. Since the check valve member 10b is pushed and expanded by the fluid pressure, the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 is closed, and fluid flows from the pressure chamber 7 to the non-pressure chamber 21. Is moved only through the fluid flow passage 5 (via the orifice passage 11b penetrating the check valve member 10b), and the piston member 3 has a rotational direction of A due to the resistance force generated at that time. The kinetic energy is attenuated by receiving the resistance force in the reverse direction, and the damper effect is obtained in the entire region up to the state of FIG.

  On the other hand, when a force is applied to the arm 17 provided on the shaft of the rotor from the state shown in FIG. The fluid can move to the room 7 which is a non-pressure chamber through both the clearance (clearance) formed by the inner wall of the casing 2 and the piston member 3 and the fluid flow passage 5, and in that case, most of the fluid flows. Since no resistance force is generated, the movement of the piston member 3 is smooth and the state shown in FIG. 13C is obtained with almost no braking force.

  However, the gap (clearance) formed by the inner wall of the casing 2 and the piston member 3 gradually narrows from the point where the state shown in FIG. 13C is exceeded to the state shown in FIG. 13D. When the stop valve member 10a is expanded, the fluid movement from the chamber 6 to the chamber 7 passes only through the fluid flow passage 5 (via the orifice passage 11a penetrating the check valve member 10a). Since the piston 3 receives the resistance force in the direction A by the resistance force generated at that time, the kinetic energy is attenuated and the damper effect is obtained.

  That is, in the fluid pressure damper in Example 8, when a force is applied in the direction A in the figure, a damper effect is generated in the entire stroke range, while a force is applied in the opposite direction to A in the figure. Are controlled so that the damper effect is generated only in the final operation region.

  FIG. 14 is a perspective view showing the lifting and lowering storage device 12 according to the ninth embodiment of the present invention, which is illustrated in a partially transparent state so that a rotation mechanism provided therein can be seen.

  The lifting and lowering storage device 12 shown in this figure has a structure in which a storage case 14 is accommodated in the outer casing 13, and the user pulls the handle 15 provided at the lower front portion of the storage case 14 forward, The storage case 14 protrudes forward from the outer casing 13 and descends to the user's working position.

  The lifting / lowering operation in the lifting / lowering storage device 1 is performed by two pivots 18 (18a, 18b) of two arms 17 (main arm 17a and auxiliary arm 17b) pivotally attached to a base 16 fixed to the outer casing 13. ) Around the arm 17 (17a, 17b) is employed so that the arm 17 (17a, 17b) moves or operates within a certain range. , The storage case 14 pivotally attached to the end 19 (19a, 19b) of the arm 17 (17a, 17b) is moved up and down.

  The rotating mechanism is provided with the fluid pressure damper 1 of the present invention in the auxiliary arm 17b in order to give a braking force to the raising / lowering operation of the storage case 14, and the urging force is applied to the rotating operation of the rotating mechanism. Is provided on the main arm 17a.

  Here, in the case where the fluid pressure damper 1 described in the eighth embodiment is provided as the fluid pressure damper 1, when the storage case 14 is pulled down, a braking force is generated in the entire operation region. On the other hand, when the storage case 14 is returned to the original position, the braking force is generated only at the end point of the operation area, and therefore the storage case 14 and the storage case 14 are loaded. The inertial force generated with respect to the article can be attenuated, and it is possible to prevent a large impact sound from being generated and the article in the storage case 14 from being damaged or deformed.

FIG. 1 is a cross-sectional view showing a conventionally known linear motion type hydraulic pressure damper. FIG. 2 is a cross-sectional view showing a conventionally known rotary motion type hydraulic pressure damper. FIG. 3 is a cross-sectional view showing the fluid pressure damper of the present invention and its sliding stroke according to the first embodiment. FIG. 4 is a cross-sectional view showing a fluid pressure damper according to the second embodiment of the present invention and its sliding stroke. FIG. 5 is a cross-sectional view illustrating the fluid pressure damper according to the third embodiment of the present invention and its sliding stroke. FIG. 6 is a cross-sectional view showing a fluid pressure damper according to the present invention and a sliding stroke thereof according to a fourth embodiment. FIG. 7 is a perspective view showing the lifting and lowering storage device according to the fifth embodiment in a partially transparent state. FIG. 8 is a cross-sectional view illustrating the fluid pressure damper of the present invention according to the sixth embodiment. FIG. 9 is a cross-sectional view illustrating a sliding stroke in the fluid pressure damper of the present invention according to the sixth embodiment. FIG. 10 is a cross-sectional view illustrating the fluid pressure damper according to the present invention according to the seventh embodiment. FIG. 11 is a cross-sectional view illustrating a sliding stroke in the fluid pressure damper of the present invention according to the seventh embodiment. FIG. 12 is a cross-sectional view illustrating the fluid pressure damper according to the eighth embodiment of the present invention. FIG. 13 is a cross-sectional view illustrating a sliding stroke in the fluid pressure damper according to the eighth embodiment of the present invention. FIG. 13: is a perspective view which shows the raising / lowering storage apparatus of this invention based on Example 9 in a partially transmissive state.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Fluid pressure damper 2 Casing 3 Piston member 4 Piston rod 5 Fluid flow passage 8 Partition 9 O-ring 10 Check valve member 11 Orifice passage 12 Lifting storage device 13 Outer casing 14 Storage case 17 Arm 20 Spring mechanism

Claims (6)

  A fluid pressure damper comprising a casing into which fluid is injected and a piston member that slides along the inner wall of the casing, in particular, the casing inner wall and the piston member are formed corresponding to the sliding stroke of the piston member A fluid pressure damper characterized in that a change occurs in the gap.   The fluid pressure damper according to claim 1, wherein the fluid pressure damper is a linear motion type fluid pressure damper.   The fluid pressure damper according to claim 1, wherein the fluid pressure damper is a rotary motion type fluid pressure damper.   The fluid pressure damper according to any one of claims 1 to 3, further comprising a check valve mechanism.   The fluid pressure damper according to claim 4, wherein the check valve mechanism is a piston member provided with a cup-shaped check valve member. A lifting and lowering storage device comprising the fluid pressure damper according to any one of claims 1 to 5.