JP2006144863A - Rotary damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To temperature-compensate oil volumes in a first oil chamber and a second oil chamber without increasing the size of a rotary damper and without having the effect of pressure variations in the first and second oil chambers due to the rotation of a rotor on the rotary damper. <P>SOLUTION: In this rotary damper 100, the oil chamber 82 for temperature compensation is formed in the shaft part 21 of the rotor 20, the shaft part 21 of the rotor 20 is pivotally supported through bushes 90 and 91 installed on the axial both sides of the boss part 10A of a casing 10, and a roughly semi-annular very small clearance 13C is formed between the inner periphery of the boss part 10A positioned between the bushes 90 and 91 on both sides and the outer periphery of the shaft part 21 facing the inner periphery of the boss part 10A. An orifice hole 81 allowing the oil chamber 82 in the shaft part 21 of the rotor 20 to communicate with the very small clearance 13C is formed in the shaft part 21 of the rotor 20, and the first oil chamber 13A and the second oil chamber 13B formed on both sides of a vane 22 are allowed to communicate with the oil chamber 82 in the shaft part 21 of the rotor 20 through the very small clearance 13C and the orifice hole 81. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotary damper suitable for use in a steering damper provided in a steering handle of a motorcycle or the like, or a suspension damper provided in a rear wheel suspension device such as a motorcycle.

  As described in Patent Document 1, as a rotary damper, a fan-shaped casing, a boss formed at the center of the casing, a shaft supported on the boss of the casing, and a vane formed on the outer periphery of the shaft And a first oil chamber and a second oil chamber are defined on both sides of the vane of the rotor in the casing.

In Patent Document 1, when the oil in the first oil chamber and the second oil chamber expands due to the temperature rise of the damper itself, an accumulator 40 is provided in the casing 13 for absorbing this oil expansion. The accumulator 40 includes a free piston 41 and a spring 42 that urges the free piston 41 from behind.
JP2004-231036

  In the rotary damper of Patent Document 1, since the temperature compensating accumulator 40 is provided in the housing 13, the rotary damper is increased in size.

  Further, in the rotary damper of Patent Document 1, the accumulator 40 is in direct communication with the first oil chamber and the second oil chamber without passing through an orifice. Therefore, when the oil in the first oil chamber or the second oil chamber is pressurized by the rotation of the rotor, the free piston constituting the accumulator may be displaced, and the damping force may become unstable.

  The problem of the present invention is that the rotary damper is not increased in size, and is not affected by pressure fluctuations in the first oil chamber and the second oil chamber accompanying the rotation of the rotor. It is to compensate the temperature of the oil volume of the chamber and the second oil chamber.

  The invention of claim 1 is a rotor comprising a fan-shaped casing, a boss formed at the center of the casing, a shaft supported on the boss of the casing, and a vane formed on the outer periphery of the shaft. A rotary damper in which a first oil chamber and a second oil chamber are partitioned on both sides of the rotor vane in the casing, and a temperature compensating oil chamber is formed in the shaft portion of the rotor, The shaft portion of the rotor is pivotally supported via bushes provided on both axial sides of the boss portion of the casing, and the inner periphery of the boss portion located between the bushes on both sides, and the inner periphery of the boss portion, A semi-circular minute gap is formed between the opposing outer circumferences of the shaft portions, an orifice hole communicating with the oil chamber of the shaft portion of the rotor and the minute gap is provided in the shaft portion of the rotor, The first oil chamber and the second oil chamber partitioned on both sides are divided into the minute gap and the Those communicating with the oil chamber of the shaft portion of the rotor through the orifice hole.

  According to a second aspect of the present invention, in the first aspect of the present invention, two oil passages communicating with the first oil chamber and the second oil chamber are opened on one side in the axial direction of the shaft portion of the rotor. A blow valve that closes the opening of the two oil passages is formed in the hole, and the oil chamber for temperature compensation is formed on the other axial side of the shaft portion of the rotor. is there.

(Claim 1)
(a) A substantially semi-annular minute gap is formed between the inner periphery of the boss portion of the casing and the outer periphery of the shaft portion of the rotor, and the first oil chamber and the second oil chamber partitioned on both sides of the vane, The semi-annular minute gap and the orifice hole communicated with a temperature compensation oil chamber provided in the shaft portion of the rotor. Therefore, the hydraulic oil in the first oil chamber and the second oil chamber is squeezed by both the minute gap and the orifice hole and communicates with the temperature compensation oil chamber, and the first oil chamber or the second oil chamber is rotated by the rotation of the rotor. Even if the oil in the second oil chamber is pressurized, the pressurized oil in the first oil chamber or the second oil chamber does not easily reach the temperature compensation oil chamber and is unstable such as a delay in damping force. Does not occur.

  (b) A restriction is not formed only by the orifice hole between the first oil chamber or the second oil chamber and the temperature compensation oil chamber, and the orifice hole forms a restriction with a semi-annular minute gap. . Therefore, when forming a certain drawing resistance, the hole diameter of the orifice hole can be increased, and as a result, it is not necessary to use a small diameter drill, and the workability can be improved.

(Claim 2)
(c) A hole in which two oil passages communicating with each of the first oil chamber and the second oil chamber are formed in an end face on one end side of the shaft portion of the rotor, and the two oil passages are formed in the holes. A blow valve that closes the opening of the passage is provided, and an oil chamber for inserting a temperature-compensating free piston is formed on the end face on the other end side of the shaft portion of the rotor. The mounted hole can be accommodated compactly in the shaft portion of the rotor. Therefore, the rotary damper can be reduced in size.

  1 is a perspective view showing a rotary damper, FIG. 2 is a plan view showing the rotary damper, FIG. 3 is a sectional view taken along line III-III in FIG. 2, and FIG. 4 is a sectional view taken along line IV-IV in FIG. 5 is a sectional view taken along line VV in FIG. 3, FIG. 6 is a sectional view taken along line VI-VI in FIG. 3, FIG. 7 is a sectional view taken along line VII-VII in FIG. (A) is a cross-sectional view taken along the line AA in FIG. 5, (B) is a cross-sectional view taken along the line BB in FIG. 5, FIG. 9 is a cross-sectional view showing the rotor, and FIG. 10 is a plan view showing the rotor. FIG. 11 shows a rotary damper, (A) is a schematic diagram showing a first operation, and (B) is a schematic diagram showing a second operation.

  The rotary damper 100 shown in FIGS. 1 to 10 is used for a steering damper provided in a steering handle of a motorcycle or the like, or a suspension damper provided in a rear wheel suspension device such as a motorcycle.

  As shown in FIGS. 1 to 4, the rotary damper 100 includes a fan-shaped casing 10 and a bottom plate 11 connected by bolts 12. The casing 10 includes a peripheral wall portion 10 a, a top wall portion 10 b on the top side, and a bottom plate 11. The rotary damper 100 is housed in the casing 10, the shaft portion 21 rotatably supported on the boss portion 10 </ b> A of the casing 10 and the boss portion 11 </ b> A of the bottom plate 11 via bushes 90 and 91, and the outer periphery of the shaft portion 21. The rotor 20 is composed of a single oscillating vane 22 protruding in the radial direction. As shown in FIG. 5, the boss 10 </ b> A of the casing 10 is formed at the center of the fan-shaped casing 10. As shown in FIGS. 3 and 5, between the inner periphery of the boss portion of the casing 10 located between the bushes 90 and 91 and the outer periphery of the shaft portion 21 of the rotor 20 facing the inner periphery of the boss portion 10. Is provided with a substantially semi-annular minute gap 13C (approximately 0.2 mm). The rotary damper 100 connects the steering shaft of the steering handle to the shaft portion 21 of the rotor 20 or the rotation shaft of the suspension arm of the rear wheel suspension device. The rotary damper 100 defines a first oil chamber 13A and a second oil chamber 13B filled with oil on both sides of the vane 22 of the rotor 20 in the casing 10. The casing 10 includes a packing 14 on a mating surface with the bottom plate 11, and an O-ring 15 on a loading portion of the shaft portion 21.

  The rotary damper 100 has an outer lid 30 attached to the outer surface of the top wall portion 10 b of the casing 10 opposite to the bottom plate 11 with bolts 16. The casing 10 includes a packing 17 on the mating surface with the outer lid 30.

  As shown in FIGS. 3, 6, and 7, the rotary damper 100 communicates the first oil chamber 13 </ b> A and the second oil chamber 13 </ b> B between the outer surface of the casing 10 and the inner surface of the outer lid 30. A first oil passage 31 and a second oil passage 32 are provided in parallel. The first oil passage 31 and the second oil passage 32 are arranged so as to be symmetrical with respect to a rotation operation shaft 60 of the orifice plate 50 described later.

  The first oil passage 31 includes an outer lid side oil passage portion 31 </ b> A formed between the groove a formed on the inner surface of the outer lid 30 and the outer surface of the casing 10, and a groove formed on the outer surface of the casing 10. b and a casing side oil passage portion 31B formed between the inner surface of the outer lid 30 and a connection portion 31C that communicates the outer lid side oil passage portion 31A and the casing side oil passage portion 31B. The first oil passage 31 includes a first check valve 41 that allows only an oil flow from the first oil chamber 13A to the second oil chamber 13B, and an inlet 31i of the outer lid side oil passage portion 31A is provided. While opening to the first oil chamber 13A, the outlet 31o of the casing side oil passage portion 31B is opened to the second oil chamber 13B via the first check valve 41. The inlet 31i and the outlet 31o of the first oil passage 31 are arranged outside the swing range of the vane 22 in the casing 10 so as not to be closed by the operation of the vane 22, and are always in the oil chambers 13A and 13B. Open.

  The second oil passage 32 includes an outer lid side oil passage portion 32 </ b> A formed between the groove a formed on the inner surface of the outer lid 30 and the outer surface of the casing 10, and a groove formed on the outer surface of the casing 10. b and a casing side oil passage portion 32B formed between the inner surface of the outer lid 30 and a connection portion 32C for communicating the outer lid side oil passage portion 32A and the casing side oil passage portion 32B. The second oil passage 32 includes a second check valve 42 that allows only an oil flow from the second oil chamber 13B to the first oil chamber 13A, and an inlet 32i of the second check valve 32A is provided in the second oil valve 32A. The second oil chamber 13B is opened, and the outlet 32o of the casing-side oil passage portion 32B is opened to the first oil chamber 13A via the second check valve 42. The inlet 32i and the outlet 32o of the second oil passage 32 are arranged outside the swing range of the vane 22 in the casing 10 so as not to be closed by the operation of the vane 22, and are always in the oil chambers 13B and 13A. Open.

  As shown in FIGS. 4, 5, 6, 7, and 8, each of the peripheral wall portions 10 a that partition the first oil chamber 13 </ b> A and the second oil chamber 13 </ b> B on both sides of the vane 22 of the casing 10. The outlets 31o of the first oil passage 31 and the outlets 32o of the second oil passage 32 are opened, and the recesses 18 and 19 are formed in which the first check valve 41 and the second check valve 42 are accommodated, respectively. Is done. The recess 18 faces the second oil chamber 13B through a step wall 18A lower than the peripheral wall portion of the casing 10, screws the housing 41A of the first check valve 41, and press-fits the valve seat 41B into the housing 41A. A check ball 41C and a spring 41D are incorporated, and an opening 41E is provided (FIG. 8B). The concave portion 19 faces the first oil chamber 13A through a step wall 19A lower than the peripheral wall portion of the casing 10, and a housing 42A of the second check valve 42 is screwed. The housing 42A is provided with a valve seat 42B press-fitted. A check ball 42C and a spring 42D are incorporated, and an opening 42E is provided (FIG. 8A).

  As shown in FIGS. 3, 4, 6, and 7, the rotary damper 100 includes an orifice plate 50 that faces the connection portion 31 </ b> C of the first oil passage 31 and the connection portion 32 </ b> C of the second oil passage 32. 10 is provided so as to be movable between the outer side surface of 10 and the inner side surface of the outer lid 30. The orifice plate 50 is connected to the oil passage 31 such that the outer lid side oil passage portion 31A and the casing side oil passage portion 31B of the first oil passage 31 are electrically connected to each other at a plurality of movement stop positions (rotation stop positions). The first orifice hole group 50A composed of a plurality of corresponding orifice holes 51A, 52A,..., And the outer lid side oil passage portion 32A and the casing side oil passage portion 32B of the second oil passage 32 are electrically connected. And a second orifice hole group 50B composed of a plurality of orifice holes 51B, 52B... Corresponding to the oil passage 32.

  As shown in FIGS. 3 and 4, the orifice plate 50 is sandwiched between the connection portion 31 </ b> C of the first oil passage 31 and the connection portion 32 </ b> C of the second oil passage 32, and the rotation operation shaft is attached to the outer lid 30. It consists of a rotating disk that is pivotally supported and has a peripheral edge that faces each of the connecting parts 31C and 32C, and that is rotatably fitted in a circular recess on the outer surface of the casing 10, and includes a first orifice hole group 50A and a second The orifice hole group 50B is arranged so as to be axially symmetrical with each other at the peripheral edge thereof. The rotary operation shaft 60 is inserted fluid-tightly into the boss portion 30A of the outer lid 30 via an O-ring 60A, and the flange 61 is applied to the inner step surface of the outer lid 30 to be backed up by a retaining ring 62 and set screw 63A. The dial 63 fixed in the above is applied to the outer surface of the outer lid 30 so that the orifice plate 50 can be rotated and stopped. As shown in FIG. 4, the dial 63 includes a clip stop mechanism 64 between the outer end face of the boss 30 </ b> A of the outer lid 30, and the orifice plate 50 can be set at any one of the rotation stop positions. The orifice holes 51A, 52A ... of the orifice hole group 50A and the orifice holes 51B, 52B ... of the second orifice hole group 50B are connected to the first oil passage 31 and the second oil passage 32. Position in order 31C, 32C.

  The orifice plate 50 includes the orifice holes 51A, 52A,... Of the first orifice hole group 50A and the orifice holes 51B, 52B,... Of the second orifice hole group 50B. At the stop position, the orifice holes 51A and 51B, the orifice holes 52A and 52B,... Corresponding to the connection portion 31C of the first oil passage 31 and the connection portion 32C of the second oil passage 32 have the same diameter. . The diameter of the orifice holes 51A and 51B> the diameter of the orifice holes 52A and 52B>.

  As shown in FIGS. 3, 5, 9, and 10, the rotary damper 100 includes two oil passages that communicate with the shaft portion 21 of the rotor 20 in each of the first oil chamber 13 </ b> A and the second oil chamber 13 </ b> B. 71A and 71B are provided, and a blow valve 70 is interposed in the oil passages 71A and 71B. A blow valve for opening two oil passages 71A and 71B is provided in an end face on one end side in the axial direction of the shaft portion 21 of the rotor 20, and the blow valve for closing the openings of the two oil passages 71A and 71B is provided in the hole 72. 70 is provided. The two oil passages 71A and 71B are symmetrical to each other with respect to the center line along the longitudinal direction of the vane 22, and the two oil passages 71A1 and 71B1 obliquely intersecting the vane 22 and the shaft portion 21 It consists of two axial oil passages 71A2 and 71B2 along the axial direction, and the two axial oil passages 71A2 and 71B2 open to the bottom surface 73 of the hole 72, respectively. The bottom surface 73 constitutes the seat surface of the blow valve 70.

  The blow valve 70 is composed of a disk biased in the closing direction by a retaining ring 74 and a spring 76 backed up by a collar 75, and is given a certain valve opening pressure.

  As shown in FIGS. 3 and 5, the rotary damper 100 includes an inner periphery of the boss portion 10A of the casing 10 positioned between the bushes 90 and 91, and a shaft of the rotor 20 facing the inner periphery of the boss portion 10A. A generally semi-circular minute gap 13 </ b> C (approximately 0.2 mm) is provided between the outer periphery of the portion. An orifice hole 81 communicating with the first oil chamber 13A and the second oil chamber 13B through the semicircular minute gap 13C is provided in the shaft portion 21 of the rotor 20, and the temperature at which the orifice hole 81 opens. A compensation oil chamber 82 is formed in the end face of the shaft portion 21 on the other end side in the axial direction, and a temperature compensation free piston 80 (movable partition member) that slides in the oil chamber 82 via an O-ring 80A is provided. Interpolate. The free piston 80 is pressurized by a spring 85 backed up by a retaining ring 83 and a stopper 84. The rotary damper communicates the first oil chamber 13A and the second oil chamber 13B with the oil chamber 82 of the shaft portion 21 of the rotor 20 through the semicircular minute gap 13C and the orifice hole 81. A rubber bladder may be used in place of the free piston 80.

Hereinafter, the damping operation of the rotary damper 100 will be described (FIG. 11).
(1) When the rotor 20 rotates to the right as shown in FIG. 11A, the oil in the first oil chamber 13A is pressurized, and this oil enters the inlet 31i of the first oil passage 31, the outer lid side oil passage. It is transferred from the outlet 31o and the first check valve 41 to the second oil chamber 13B through the portion 31A, the connection portion 31C (first orifice hole group 50A of the orifice plate 50) and the casing side oil passage portion 31B. .

  The orifice plate 50 corresponds to the oil in this transfer process to one of the orifice holes 51A, 52A,..., For example, the hole diameter of the orifice hole 51A, which is positioned in the connection portion 31C in the first orifice hole group 50A. To apply a certain damping force to the rotor 20.

  At this time, the oil in the first oil chamber 13 </ b> A is prevented from flowing into the second oil passage 32 by the check action of the second check valve 42.

  (2) When the rotor 20 rotates counterclockwise as shown in FIG. 11B after the above (1), the oil in the second oil chamber 13B is pressurized, and this oil enters the inlet of the second oil passage 32. 32i, the outer lid side oil passage portion 32A, the connection portion 32C (second orifice hole group 50B of the orifice plate 50), the casing side oil passage portion 32B, and the first check valve 42 from the outlet 32o. It is transferred to the oil chamber 13A. Since the second oil passage 32 has no oil flow in the above (1) and is not affected by its inertial force, the second oil passage 13B passing through the second oil passage 32 moves from the second oil passage 13B to the first oil chamber 13A. The oil transfer is smooth.

  The orifice plate 50 corresponds to any one of the orifice holes 51B, 52B,..., For example, the hole diameter of the orifice hole 51B, which is positioned in the connection portion 32C in the second orifice hole group 50B. To apply a certain damping force to the rotor 20. The diameter of the orifice hole 51B is the same as the diameter of the orifice hole 50A described in (1) above, and the orifice plate 50 exerts the same damping force on both the left and right rotations of the rotor 20.

  At this time, the oil in the second oil chamber 13 </ b> B is prevented from flowing into the first oil passage 31 by the check action of the first check valve 41.

The blow valve 70 operates as follows.
When the vane 22 compresses the oil chamber 13A and an excessive pressure is generated in the oil chamber 13A due to overturn of the motorcycle or the like, as shown in FIGS. 3, 5, 9, and 10, the oil chamber 13A The hydraulic oil passes through the oblique oil passage 71 </ b> A <b> 1 and the axial oil passage 71 </ b> A <b> 2 formed in the shaft portion 21, and biases the blow valve 70 that closes the opening of the oil passage 71 </ b> A <b> 2 that opens to the bottom surface 73 of the hole 72. And opens to the oil chamber in the hole 72, and further passes through the oil passage 71B2 in the axial direction and the oil passage 71B1 in the oblique radial direction that open to the bottom surface 73 of the hole 72, and the oil chamber on the opposite side of the vane 22. It flows to 13B.

  As a result, excessive pressure is prevented from being generated in the oil chamber 13A, and the damper 100 is prevented from being damaged.

  When the oil chamber 13B on the opposite side of the vane 22 is compressed and excessive pressure is generated in the oil chamber 13B, the flow is opposite to that described above.

According to the present embodiment, the following operational effects can be obtained.
(a) A first semi-annular chamber 11 </ b> A formed on both sides of the vane 22 by forming a substantially semi-annular minute gap 13 </ b> C between the inner periphery of the boss portion 10 </ b> A of the casing 10 and the outer periphery of the shaft portion 21 of the rotor 20. The second oil chamber 13B communicated with the temperature compensation oil chamber 82 provided in the shaft portion 21 of the rotor 20 through the semi-annular minute gap 13C and the orifice hole 81. Accordingly, the hydraulic oil in the first oil chamber 11A and the second oil chamber 13B is squeezed by both the minute gap 13C and the orifice hole 81 and communicates with the temperature compensation oil chamber 82. Even if the oil in one oil chamber 11A or the second oil chamber 13B is pressurized, the pressurized oil in the first oil chamber 11A or the second oil chamber 13B easily reaches the temperature compensation oil chamber 82. Without being transferred to the orifice plate 50 (orifice hole group 50A or 50B), an appropriate damping force is generated, and instability such as a delay in the damping force does not occur.

  (b) A restriction is not formed only by the orifice hole 81 between the first oil chamber 11A or the second oil chamber 13B and the temperature compensation oil chamber 82, and the orifice hole 81 is a semi-annular minute gap. A diaphragm is formed together with 13C. Therefore, when forming a constant drawing resistance, the hole diameter of the orifice hole 81 can be increased, and as a result, it is not necessary to use a small diameter drill, and workability can be improved.

  (c) A hole 72 is formed in the end surface of the shaft portion 21 of the rotor 20 at which one of the two oil passages communicating with the first oil chamber 11A and the second oil chamber 13B is opened. In addition, a blow valve 70 for closing the openings of the two oil passages 71A and 71B is provided, and an oil chamber 82 for inserting a temperature compensating free piston 80 is formed on the end surface of the shaft 21 of the rotor 20 on the other end side. Therefore, the temperature compensation oil chamber 82 and the hole 72 with the blow valve 70 interposed can be accommodated in the shaft portion 21 of the rotor 20 in a compact manner. Therefore, the rotary damper 100 can be reduced in size.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention.

FIG. 1 is a perspective view showing a rotary damper. FIG. 2 is a plan view showing the rotary damper. FIG. 3 is a sectional view taken along line III-III in FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. FIG. 5 is a cross-sectional view taken along line VV in FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 7 is a sectional view taken along line VII-VII in FIG. 8A and 8B show the check valve. FIG. 8A is a cross-sectional view taken along line AA in FIG. 5, and FIG. 8B is a cross-sectional view taken along line BB in FIG. FIG. 9 is a sectional view showing the rotor. FIG. 10 is a plan view showing the rotor. FIG. 11 shows a rotary damper, (A) is a schematic diagram showing a first operation, and (B) is a schematic diagram showing a second operation.

Explanation of symbols

10 casing 10A boss 13A first oil chamber 13B second oil chamber 13C minute gap 20 rotor 21 shaft 22 vane 70 blow valve 71A, 71B oil passage 72 hole 81 orifice hole 82 temperature compensation oil chamber 90, 91 bush 100 Rotary damper

Claims (2)

A fan-shaped casing, and a boss formed at the center of the casing;
A rotor comprising a shaft portion pivotally supported on the boss portion of the casing, and a vane formed on the outer periphery of the shaft portion;
In the rotary damper which divides the first oil chamber and the second oil chamber on both sides of the vane of the rotor in the casing,
An oil chamber for temperature compensation is formed in the shaft portion of the rotor,
The shaft portion of the rotor is pivotally supported via bushes provided on both axial sides of the boss portion of the casing, and the inner periphery of the boss portion located between the bushes on both sides, and the inner periphery of the boss portion, A generally semi-annular minute gap is formed between the opposing outer periphery of the shafts,
An orifice hole communicating with the oil chamber of the shaft portion of the rotor and the minute gap is provided in the shaft portion of the rotor,
A rotary damper characterized in that a first oil chamber and a second oil chamber partitioned on both sides of the vane are communicated with an oil chamber of a shaft portion of the rotor through the minute gap and the orifice hole. A hole in which two oil passages communicating with the first oil chamber and the second oil chamber respectively open is formed on one axial side of the shaft portion of the rotor, and the two oil passages are formed in the holes. Provide a blow valve to close the opening of the road,
The rotary damper according to claim 1, wherein the temperature compensating oil chamber is formed on the other axial side of the shaft portion of the rotor.

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