JP2013181592A - Rotary damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary damper that can exhibit an aimed damping force, even when a pressure in an operation room has become high.SOLUTION: A rotary damper D includes: a shaft 1; a pair of side panels 2, 3 axially supporting the shaft 1 while allowing the rotation in a circumferential direction; a case 4 provided between the side panel 2 and 3 and forming an operation room R inside; and a vane 5 provided in the shaft 1 having a tip end in sliding contact with an inner circumference of the case 4 and partitioning the operation room R to one side room R1 and the other side room R2. In the rotary damper D, there are provided plates 6, 7 interposing in spaces between the case 4 and to each side panels 2, 3 and with which the vane comes in sliding contact; and a biasing unit for biasing the plates 6, 7 to the side of the vane 5. Since then, even when the pressure inside the operation room R becomes high, the plates 6, 7 are kept in contact state to the vane 5. Even if the pressure inside the operation room R becomes high, a damping force which has been aimed can be exactly executed.

Description

  The present invention relates to an improvement of a rotary damper.

  Conventionally, in a rotary damper, a shaft, a pair of side panels that pivotally support the shaft while allowing rotation in the circumferential direction, and a case that is sandwiched between these side panels to form a working chamber inside. The vane is provided on the shaft and divides the working chamber into one chamber and the other chamber.

  Then, for example, when a rotational force is applied to the shaft from the outside, the rotary damper operates to reduce the one chamber while the vane moves in the working chamber as the shaft rotates, and to reduce the other chamber. A damping force that suppresses the rotation of the shaft is exhibited by applying resistance to the flow of oil moving from the one chamber to the other chamber with a damping valve (see Patent Document 1).

JP-A-8-177828

  Considering the case where such a rotary damper is incorporated into a vehicle suspension, for example, the rotary damper case is fixed to the vehicle body, and the rotary damper shaft is swingably attached to the vehicle body to hold the wheel. By connecting to the arm, the rotary damper is incorporated into the suspension. More specifically, the shaft and the suspension arm are connected with the rotation direction of the shaft coincident with the swinging direction of the suspension arm.

  Here, in particular, when a rotary damper is used for a suspension of a four-wheel vehicle, it is necessary to generate a large damping force in order to attenuate the vibration of the heavy vehicle body, and the pressure in the working chamber becomes very high. When the working chamber becomes extremely high in pressure, the side panel holding the case is bent by the internal pressure in the working chamber, a gap is created between the vane and the side panel, and the one chamber communicates with the other chamber through the gap. End up.

  Then, the oil in the working chamber can bypass the damping valve and go back and forth between the one chamber and the other chamber through the gap, and the damping force as intended may not be exhibited.

  Accordingly, the present invention has been developed to improve the above-described problems, and the object of the present invention is to provide a rotary damper that can exhibit a desired damping force even when the working chamber has a high pressure. Is to provide.

  In order to solve the above-described problems, the problem-solving means of the present invention is provided between a shaft, a pair of side panels that pivotally support the shaft while allowing the shaft to rotate in the circumferential direction, and the side panels. In a rotary damper comprising: a case that forms a working chamber therein; and a vane that is provided on the shaft and has a tip that slides into the inner periphery of the case and divides the working chamber into one chamber and the other chamber. It is characterized by comprising a plate interposed between the case and each of the side panels and in contact with the vane, and an urging means for urging the plate and the vane side.

  Since the plate is urged to the vane side by this urging means, even if the pressure in the working chamber becomes high, the plate is kept in contact with the vane, and the one chamber and the other chamber are placed around the vane. There is no communication.

  According to the rotary damper of the present invention, a desired damping force can be exhibited even when the working chamber is at a high pressure.

It is a longitudinal cross-sectional view of the rotary damper in one embodiment. It is a cross-sectional view of the rotary damper in one embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIGS. 1 and 2, the rotary damper D in one embodiment includes a shaft 1, a pair of side panels 2 and 3 that support the shaft 1 while allowing the shaft 1 to rotate in the circumferential direction, and these A case 4 provided between the side panels 2 and 3 and forming a working chamber R therein, and a tip 1 provided on the shaft 1 and slidingly contacting the inner periphery of the case 4 to connect the working chamber R to the one chamber R1. And the other chamber R2, and the plates 6 and 7 interposed between the vane 5 and the side panels 2 and 3, and the plates 6 and 7 are urged toward the vane 5 side. And an urging means. The rotary damper D exhibits a damping force that suppresses the rotation of the shaft 1 when the shaft 1 is rotated in the circumferential direction with respect to the case 4.

  Hereinafter, each part of the rotary damper D will be described in detail. First, the shaft 1 includes a serration 1a that is provided at the tip and can be connected to a joint or the like (not shown), an enlarged diameter portion 1b that is larger in diameter than other portions provided in the middle, and an outer periphery of the enlarged diameter portion 1b. And a pair of vanes 5 and 5 provided with a phase of 180 degrees in the circumferential direction, and an opening from a side portion between the vanes 5 and 5 of the enlarged diameter portion 1b leading to the opposite vanes 5 and 5 and each other. Two communication holes 8 and 9 that do not cross in the axial direction are provided. In addition, in the place mentioned above, although the serration 1a is provided for the coupling | bonding to the coupling etc. outside a figure, the connection method is not limited to this.

  In this embodiment, the vane 5 has an arcuate surface at the tip, and has a U-shaped seal extending from the upper end in FIG. 1 on the side panel 2 side to the tip and the lower end in FIG. 1 on the side panel 3 side. The seal 10 is in sliding contact with the case 4 and the plates 6 and 7 to seal the vane 5 and the space between the case 4 and the plates 6 and 7.

  In the case of this embodiment, the side panel 2 has a cylindrical shaft holding portion 2a through which the upper end of the shaft 1 is inserted in FIG. 1, and a flange-like cap portion provided on the outer periphery of the lower end of the shaft holding portion 2a in FIG. 2b and a plurality of bolt insertion holes 2c provided in the cap portion 2b at intervals on the same circumference. Further, a cylindrical bearing 11 that is in sliding contact with the upper side of the shaft 1 in FIG. 1 is attached to the inner periphery of the shaft holding portion 2a. An annular U-packing 13 and an annular dust seal 14 that are in sliding contact with the outer periphery of the shaft 1 are respectively mounted on the side opposite to the case 4 that is the upper middle.

  The U packing 13 is in close contact with the outer periphery of the shaft 1 and seals between the shaft 1 and the side panel 2. The dust seal 14 provided at the outermost position in FIG. Prevents dust and dirt from entering between. Furthermore, an O-ring 15 is mounted on the case 4 side of the cap portion 2b, and this O-ring 15 seals between the side panel 2 and the plate 6.

  On the other hand, in the case of this embodiment, the side panel 3 has a bottomed cylindrical shape, and is provided on a shaft holding portion 3a into which the lower end of the shaft 1 in FIG. 1 is inserted, and on the outer periphery of the upper end of the shaft holding portion 3a in FIG. A flange-shaped cap portion 3b and a plurality of bolt insertion holes 3c provided in the cap portion 3b at intervals on the same circumference. Further, a cylindrical bearing 16 that is in sliding contact with the outer periphery of the lower end in FIG. 1 of the shaft 1 is attached to the inner periphery of the shaft holding portion 3a. An annular U-packing 18 that is in sliding contact with the outer periphery of the shaft 1 is mounted on the side opposite to the case 4 that is the middle and lower side. In addition, since the bottom part in the shaft holding part 3a is obstruct | occluded in the side panel 3, since the dust seal is not provided, the lower end of the shaft 1 is protruded outward without closing the bottom part of the shaft holding part 3a. If present, a dust seal can be provided. Further, an O-ring 19 is attached to the case 4 side of the cap portion 3b, and the O-ring 19 seals between the side panel 3 and the plate 7. These side panels 2 and 3 are made of a light material such as aluminum, for example, and reduce the overall weight of the rotary damper D.

  The plates 6 and 7 have a disk shape thinner than the side panels 2 and 3, and shaft insertion holes 6 a and 7 a that allow the shaft 1 to be inserted in the center, and bolt insertion holes of the side panels 2 and 3. A plurality of bolt insertion holes 6b and 7b provided at positions corresponding to 2c and 3c, and annular recesses 6c and 7c provided on the side panels 2 and 3 side are configured. When the plate 6 is laminated on the side panel 2, an annular space formed by the annular recess 6c is formed between the side panel 2 and the plate 6, and the pressure chamber P1 is formed in the space. Similarly, when the plate 7 is laminated on the side panel 3, an annular space formed by the annular recess 7c is formed between the side panel 3 and the plate 7, and the pressure chamber P2 is formed in the space. Since the pressure chambers P1 and P2 are annular in this way, the plates 6 and 7 can be urged toward the vane 5 without being interrupted by the internal pressure in the circumferential direction. 7 can be energized.

  In addition, since the vane 5 slides on the side surfaces of the vanes 5 of the plates 6 and 7, the side surfaces of the vanes 5 of the plates 6 and 7 may be made of a material having excellent wear resistance. For example, the entire plates 6 and 7 may be formed of a material having high hardness, or the surface (sliding surface) that contacts the vanes 5 of the plates 6 and 7 may be plated or a diamond-like carbon film may be formed. The surface may be subjected to gas soft nitriding treatment, heat treatment or silicon attachment treatment to increase the wear resistance of the surface. In this case, the annular recesses 6c and 7c are provided in the plates 6 and 7, but the annular recesses are provided on the surface of the side panels 2 and 3 facing the plates 6 and 7 so as to provide the pressure chambers P1 and P2. It may be.

  The case 4 includes a main body 20 having a hollow portion 21 that forms a working chamber R, a valve block 22 provided on a side portion of the main body 20, and each bolt insertion hole of the side panel 2 on the upper end side in FIG. A plurality of screw holes 23 provided at positions corresponding to 2c and a plurality of screw holes 24 provided at positions corresponding to the respective bolt insertion holes 3c of the side panel 3 on the lower end side in FIG. Has been.

  The plate 6 and the side panel 2 are laminated in order on the upper side of the case 4 in FIG. 1, and these are integrated by screwing the bolts 25 passed through the bolt insertion holes 2c and 6b into the screw holes 23. The In addition, the plate 7 and the side panel 3 are sequentially laminated below the case 4 in FIG. 1, and the bolts 26 passed through the bolt insertion holes 3 c and 7 b are screwed into the screw holes 24. It becomes. The number of bolts 25 and 26 may be as many as required in terms of strength. If bolt insertion holes 2c, 3c, 6b and 7b and screw holes 23 and 24 corresponding to the number of bolts 25 and 26 are provided, screw bolts 23 and 24 are provided. Good.

  When the plates 6 and 7 and the side panels 2 and 3 are attached to the case 4 while the shaft 1 is inserted into the hollow portion 21, the hollow portion 21 is sealed and the two fan-shaped working chambers R are formed. Form. These two working chambers R are each divided into a space L1 and a space L2 by vanes 5 provided on the shaft 1, and for example, fluid such as hydraulic oil is enclosed therein. In addition, O-rings 27 and 28 surrounding the outer periphery of the hollow portion 21 are attached to the upper and lower ends of the main body 20 of the case 4 in FIG. 1, and the space between the case 4 and the plates 6 and 7 is sealed, and the working chamber R is sealed.

  In FIG. 2, the space L1 is defined on the right side of the vane 5 when viewed from the axis of the shaft 1, and the space L2 is defined on the left side of the vane 5 when viewed from the axis of the shaft 1. When the shaft 1 rotates clockwise, each space L2 is enlarged and each space L1 is reduced by the vane 5. On the other hand, when the shaft 1 rotates counterclockwise in FIG. Is reduced and each space L1 is enlarged.

  Then, the spaces L1 in which the volumes are both expanded or reduced with the rotation of the shaft 1 are communicated with each other by the communication hole 8 of the shaft 1 to form one chamber R1. The space L2 to be enlarged or reduced is communicated by the communication hole 9 of the shaft 1 and is defined as the other chamber R2. The one chamber R1 and the other chamber R2 are partitioned by the vane 5 as can be understood from the above description. The Further, the opening position of the communication hole 8 is provided at the root of the vane 5 so that the one chamber R1 is maintained in a communication state by the communication hole 8 even when the shaft 1 rotates. The other chamber R2 is provided at the base of the vane 5 so that the other chambers R2 are maintained in communication with each other even if the shaft 1 rotates.

  Returning, a damping passage 30 is provided from the main body 20 of the case 4 to the valve block 22 to communicate the one chamber R1 and the other chamber R2, and the valve block 22 is disposed in the middle of the damping passage 30. A damping valve 32 that provides resistance to the flow while allowing only a fluid flow from the one chamber R1 to the other chamber R2, and a fluid that is disposed in the damping passage 30 in parallel with the damping valve 32 and that travels from the other chamber R2 to the one chamber R1. The check valve 33 that allows only the flow of the fluid, and the flow that is arranged in series with the damping valve 32 in the middle of the damping passage 30 while permitting only the fluid flow from the other chamber R2 to the one chamber R1. A damping valve 34 that resists the pressure, a check valve 35 that is disposed in parallel with the damping valve 34 in the damping passage 30 and that allows only the flow of fluid from one chamber R1 to the other chamber R2, and the damping passage 30 An accumulator 36 connected between the damping valve 32 and the damping valve 34 is provided even during.

  Therefore, when the shaft 1 rotates clockwise and the vane 5 compresses the one chamber R1, the fluid pushed out from the one chamber R1 passes through the damping valve 32 and the check valve 35 and expands through the damping passage 30. The damping valve 32 gives resistance to the flow of the fluid and causes a differential pressure between the one chamber R1 and the other chamber R2, thereby suppressing the rotation of the shaft 1. To demonstrate.

  On the other hand, when the shaft 1 rotates counterclockwise and the vane 5 compresses the other chamber R2, the fluid pushed out of the other chamber R2 passes through the damping valve 34 and the check valve 33 and expands through the damping passage 30. When the damping valve 34 gives resistance to the flow of the fluid, the differential pressure is generated between the other chamber R2 and the one chamber R1, thereby suppressing the rotation of the shaft 1. Demonstrate power.

  In this rotary damper D, the volume of the expansion or contraction of the one chamber R1 due to the rotation of the shaft 1 is equal to the volume of the contraction or expansion of the other chamber R2, so that it is a straight line composed of a cylinder, a piston and a piston rod. Unlike the moving rod type damper, it is not necessary to compensate for the volume change in the cylinder, but it is necessary to compensate for the volume change of the fluid due to the temperature change, in this case, the volume change of the fluid. The volume change due to the temperature change of the fluid is compensated. In addition, the accumulator 36 applies a predetermined pressure to the sealed fluid, and increases the apparent rigidity of the fluid to improve the damping force generation response.

  In addition, a U-shaped seal 29 is attached to the inner periphery of the main body 20 of the case 4 and the portion that is in sliding contact with the outer periphery of the enlarged diameter portion 1 b of the shaft 1 and the upper and lower ends of the main body 20. Further, a side seal 12 is provided on the inner periphery of the plate 6 so as to be in sliding contact with both the side wall of the shaft insertion hole 6a and the enlarged diameter portion 1b of the shaft 1 to seal between the plate 6 and the shaft 1. Furthermore, a side seal 17 is provided on the inner periphery of the plate 7 so as to be in sliding contact with both the side wall of the shaft insertion hole 7a and the enlarged diameter portion 1b of the shaft 1 and seal between the plate 7 and the shaft 1. Yes. The damping passage 30 between the one chamber R1 and the other chamber R2 is composed of the seal 29, the seal 10 provided on the vane 5, the side seals 12 and 17 attached to the inner periphery of the plates 6 and 7, and the O-rings 27 and 28. It is designed not to communicate with other than.

  The side seal 12 includes an annular seal ring 40 that is in sliding contact with the inner wall of the shaft insertion hole 6 a of the plate 6 and the enlarged diameter portion 1 b of the shaft 1, and an annular taper ring 41 that is provided closer to the case body than the seal ring 40. And a disc spring 42 as a spring member that presses the taper ring 41 toward the seal ring 40 side. The seal ring 40 has a tapered surface 40a whose inner circumference gradually increases toward the taper ring 41 at the taper ring side end, and the taper ring 41 has an outer circumference facing the seal ring 40 at the seal ring side end. The taper surface 41a which becomes gradually small is provided, and these are contact | abutted slidably so that taper surface 40a and 41a may face each other.

  Further, a disc spring 42 is interposed between the end of the taper ring 41 on the side opposite to the seal ring and the side panel 2, and the disc spring 42 presses the taper ring 41 toward the seal ring 40.

  The biasing force of the disc spring 42 is such that the taper surface 40a of the seal ring 40 and the taper surface 41a of the taper ring 41 are in contact with each other, so that the seal ring 40 is pressed against the side wall of the shaft insertion hole 6a of the plate 6; It acts in the direction of pressing against the upper end surface of the enlarged diameter portion 1b. Further, since the shaft insertion hole 6a of the plate 6 in which the side seal 12 is accommodated communicates with the pressure chamber P1, the pressure in the pressure chamber P1 acts on the seal ring 40, and the seal ring 40 It is pressed toward the shaft insertion hole 6a and the enlarged diameter portion 1b of the shaft 1 also by the pressure in the chamber P1. As a result, the periphery of the shaft 1 is tightly sealed, and communication between the one chamber R1 and the other chamber R2 through the periphery of the shaft 1 is prevented.

  Then, when the pressure in the one chamber R1 or the other chamber R2 becomes larger than the pressure chamber P1 and the seal ring 40 is retracted upward in FIG. 1 against the urging force of the disc spring 42, the seal ring 40 and the enlarged diameter portion 1b The pressure chamber P1 communicates with the one chamber R1 or the other chamber R2, and the pressure on the high pressure side of the one chamber R1 and the other chamber R2 is guided into the pressure chamber P1. .

  Thus, when the pressure on the high pressure side of the one chamber R1 and the other chamber R2 is introduced into the pressure chamber P1, the plate 6 is biased toward the vane 5 by this back pressure (pressure in the pressure chamber P1). .

  As with the side seal 12, the side seal 17 includes an annular seal ring 43 that is in sliding contact with the inner wall of the shaft insertion hole 7 a of the plate 7 and the enlarged diameter portion 1 b of the shaft 1. The annular taper ring 44 is provided, and a disc spring 45 as a spring member that presses the taper ring 44 toward the seal ring 43 side. The seal ring 43 has a taper surface 43a whose inner circumference gradually increases toward the taper ring 44 at the taper ring side end, and the taper ring 44 has an outer circumference facing the seal ring 43 at the seal ring side end. The taper surface 44a which becomes gradually smaller is provided, and the taper surfaces 43a and 44a face each other so as to be slidably contacted.

  Further, a disc spring 45 is interposed between the side end of the taper ring 44 opposite to the seal ring and the disc spring 45 presses the taper ring 44 toward the seal ring 43.

  The biasing force of the disc spring 45 is such that the taper surface 43a of the seal ring 43 and the taper surface 44a of the taper ring 44 are in contact with each other, so that the seal ring 43 is pressed against the side wall of the shaft insertion hole 7a of the plate 7; It acts in the direction of pressing against the lower end surface of the enlarged diameter portion 1b. Further, since the shaft insertion hole 7a of the plate 7 in which the side seal 17 is accommodated communicates with the pressure chamber P2, the pressure in the pressure chamber P2 acts on the seal ring 43, and the seal ring 43 It is pressed toward the shaft insertion hole 7a and the enlarged diameter portion 1b of the shaft 1 also by the pressure in the chamber P2. As a result, the periphery of the shaft 1 is tightly sealed, and communication between the one chamber R1 and the other chamber R2 through the periphery of the shaft 1 is prevented. When the pressure in the one chamber R1 or the other chamber R2 becomes larger than the pressure chamber P2 and the seal ring 43 is retracted downward in FIG. 1 against the urging force of the disc spring 45, the seal ring 43 and the enlarged diameter portion 1b The pressure chamber P2 is communicated with the one chamber R1 or the other chamber R2, and the pressure on the high pressure side of the one chamber R1 and the other chamber R2 is guided into the pressure chamber P2. .

  Thus, when the pressure on the high pressure side of the one chamber R1 and the other chamber R2 is introduced into the pressure chamber P2, the plate 7 is biased toward the vane 5 by this back pressure (pressure in the pressure chamber P2). .

  The taper rings 41 and 44 and the disc springs 42 and 45 are provided in advance for positioning and preloading the seal rings 40 and 43, so that even if the rotational speed of the rotary damper D is low, the rotary damper D is operated from the initial operation. Sealing around the shaft 1 can surely prevent the communication between the one chamber R1 and the other chamber R2, but pressure can be applied to the seal rings 40, 43 by the pressure of the pressure chambers P1, P2. In this case, the taper surfaces 40a and 43a may not be provided on the seal rings 40 and 43, respectively. Further, instead of the disc springs 42 and 45, wave washers or other springs or elastic bodies can be used.

  Therefore, in this case, the urging means is provided between the plates 6 and 7 and the side panels 2 and 3, and pressure chambers P1 and B1 for urging the plates 6 and 7 toward the vane 5 by the internal pressure. The valve element for guiding the pressure on the high pressure side of the one chamber R1 and the other chamber R2 to the pressure chambers P1 and P2 is composed of seal rings 40 and 43.

  In the rotary damper D configured as described above, the plates 6 and 7 are interposed between the vane 5 and the side panels 2 and 3, and the plates 6 and 7 are attached to the vane 5 side. Energizing means are provided.

  Since the plates 6 and 7 are biased toward the vane 5 by the biasing means, the plates 6 and 7 are kept in contact with the vane 5 even when the pressure in the working chamber R becomes high. Since the chamber R1 and the other chamber R2 communicate with each other through the vane 5 and bypass the damping valves 32 and 34, the one and the other chambers R1 and R2 do not go back and forth. The damping force can be exhibited. In this way, the rotary damper D can exhibit the desired damping force even when the pressure in the working chamber R becomes high, so that it can be used for suspension applications that suppress vibration of the vehicle body of a four-wheeled vehicle. Suitable.

  The urging means is not limited to the above-described specific configuration as long as the plates 6 and 7 can be urged toward the vane 5 side. The urging means can be configured by interposing between the side panels 2 and 3.

  Further, as in the rotary damper D of the present embodiment, the urging means is provided between the plates 6 and 7 and the side panels 2 and 3, and the plates 6 and 7 are moved toward the vane 5 by the internal pressure. In the case of the pressure chambers P1 and P2 that are biased toward the plate, in particular, a member that exerts a biasing force that biases the plates 6 and 7 is not provided between the plates 6 and 7 and the side panels 2 and 3. The plates 6 and 7 can be energized, the number of parts can be reduced, and a space for providing a member for exerting the energizing force is not required, so that the rotary damper D can be reduced in size.

  Further, when the urging means includes a valve element for guiding the pressure on the high pressure side of the one chamber R1 and the other chamber R2 to the pressure chambers P1 and P2, the rotary damper D operates, that is, the shaft 1 of the rotary damper D. When the one chamber R1 or the other chamber R2 is compressed with respect to the case 4 and the pressure in the compression chamber becomes higher than the pressure in the pressure chambers P1 and P2, this pressure is automatically set. Since it is guided to the pressure chambers P1 and P2, the urging force for urging the plates 6 and 7 increases according to the pressure state in the working chamber R, and the urging force is not insufficient or too large. Fluid leakage between the plates 6 and 7 can be reliably prevented, and the slidability of the vane 5 is not significantly inhibited.

  Further, like the rotary damper D of the present embodiment, the valve elements are seal rings 40 and 43 that seal between the inner periphery of the shaft insertion holes 6 a and 7 a of the plates 6 and 7 and the outer periphery of the shaft 5. In this case, by using the seal rings 40 and 43 that originally seal between the shaft 5 and the plates 6 and 7 as valve elements, it is not necessary to separately add a member that functions as a valve element to the rotary damper D. Therefore, the number of parts and the cost of the rotary damper D can be reduced. Further, by applying the pressures in the pressure chambers P1, P2 corresponding to the back surfaces of the seal rings 40, 43, the seal rings 40, 43 are pressed against the shaft 5 and the plates 6, 7, respectively. , 7 can be tightly sealed.

  The valve element only needs to be able to guide the high pressure of the one chamber R1 and the other chamber R2 to the pressure chambers P1 and P2, so that the pressure chamber P1 is connected to the one chamber R1, and the pressure chamber P1 is connected to the other chamber R2. A passage that communicates, a passage that communicates the pressure chamber P2 to the one chamber R1, and a passage that communicates the pressure chamber P2 to the other chamber R2, are provided from each of the pressure chambers P1 and P2 toward the one chamber R1 (the other chamber R2). Check valves that block the flow of fluid may be provided, and these check valves may be used as valve elements. These check valves and passages may be provided in the plates 6 and 7 or in the case 4. Also good.

  Further, a relief valve for releasing the pressure to the working chamber R when the pressure in the pressure chambers P1 and P2 becomes an abnormally high pressure may be provided. By providing the relief valve in this manner, the pressure crushing in the pressure chambers P1 and P2 can be avoided, and deterioration of the slidability of the vane 5 can be prevented. The relief valve may be provided with a passage that connects the pressure chambers P1 and P2 to the one chamber R1 or the other chamber R2, respectively, so that the pressure in the pressure chambers P1 and P2 is a predetermined pressure. If it becomes above, what is necessary is just to set so that it may open | release to the one chamber R1 or the other chamber R2. In this case, the pressure chambers P1 and P2 may be provided with passages communicating with the one chamber R1 and the other chamber R2, respectively, and a relief valve may be provided in these passages, or one of the pressure chamber P1 and the pressure chamber P2 may be provided as one side. A passage communicating with the chamber R1 and a passage communicating the other of the pressure chamber P1 and the pressure chamber P2 with the other chamber R2 may be provided, and a relief valve may be provided in these passages. The relief valve and the passage may be provided in the plates 6 and 7 or may be provided in the case 4.

  In the above description, the valve block 22 is provided in the case 4 and the damping valves 32 and 34 are provided in the valve block 22. However, the damping passage, the check valve, and the damping valve are provided in the vane 5, and the accumulator is connected to the shaft 1. It is also possible to eliminate the valve block by providing it in the interior, and when there is no need to change the damping characteristic (the characteristic of the damping force with respect to the rotational speed of the shaft 1) in the rotational direction of the shaft 1, A damping force may be exerted by the damping valve.

  Further, although two vanes 5 are provided as described above, the number of installations may be one or three or more, and it is only necessary to install an appropriate number according to the specifications of the rotary damper D. In the present embodiment, the case 4 is formed of a single component, but may be configured of a plurality of components.

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

  The present invention can be used for a rotary damper for various applications, for example, a rotary damper used for a suspension of a vehicle.

1 Shaft 2, 3 Side panel 4 Case 5 Vane 6, 7 Plate 6a, 7a Shaft insertion hole 40, 43 Seal ring D Rotary damper P1, P2 Pressure chamber R Working chamber R1 One chamber R2 Other chamber

Claims (5)

A shaft, a pair of side panels that pivotally support the shaft while allowing rotation in the circumferential direction, a case that is provided between the side panels to form a working chamber therein, and a tip that is provided on the shaft In a rotary damper having a vane that slidably contacts the inner periphery of the case and divides the working chamber into one chamber and the other chamber, and is interposed between each of the case and the side panels. A rotary damper comprising: a plate in sliding contact with a vane; and an urging means for urging the plate toward the vane side. The said urging | biasing means is provided between the said plate and the said side panel, The pressure chamber which urges | biases the said plate toward the said vane side with an internal pressure is characterized by the above-mentioned. Rotary damper. The rotary damper according to claim 2, wherein the biasing means includes a valve element that guides a pressure on a high pressure side of the one chamber and the other chamber to the pressure chamber. The plate includes a shaft insertion hole that allows insertion of the shaft, and the valve element is a seal ring that seals between an inner periphery of the shaft insertion hole of the plate and an outer periphery of the shaft. The rotary damper according to claim 3. The rotary damper according to any one of claims 2 to 4, further comprising a relief valve for releasing the pressure in the pressure chamber to the one chamber or the other chamber.

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