JPH06337031A - Cushion structure for oscillating actuator - Google Patents

Abstract

PURPOSE:To facilitate assembly and prevent falling off by arranging a cushion member along a separate block face facing a vane and inserting its both end parts to a fitting hole of a cylinder body and a fitting hole of a cylinder cover respectively. CONSTITUTION:When rotational movement is applied to a shaft 9, a vane body 16 rotates in the inside of a casing 5, so that a volume of one of oil chambers 19a, 19b is shrunk while a volume of the other is expanded vanes 18a, 18b. In this way, a hydraulic oil flows through a gap around the vane body 16 from a hydraulic chamber shrunk side to a hydraulic chamber expanded side, so that damping force is generated by its flow resistance. When an amplitude for the rotational movement is increased, the vanes 18a, 18b are brought into contact with the cushion members 20a, 20b to compress them. Therefore, the vanes 18a, 18b are prevented from colliding with separate blocks 7a, 7b. Even when compressing action for the cushion members 20a, 20b are repeated, they do not fall off, as their both ends are held by engaging holes 3c, 4c, 3d, 4d of a body 3 and a cover 4. Assembly can be carried out only by fitting the cushion member to the engaging holes.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary damper that damps external vibrations by utilizing a swinging motion, and a swinging type actuating device such as a rotary actuator that performs a swinging motion by receiving a working medium from the outside. In, the present invention relates to a cushion structure for absorbing a shock generated when the operating device reaches a swing end.

[0002]

2. Description of the Related Art As a cushion structure in this type of swing-type actuating device, for example, as disclosed in Japanese Utility Model Application Publication No. 102036 in 1990, rubber is used in a vane portion facing a separate block of a cylinder. A cushion member made of an elastic material is provided.

When the swing-type actuating device reaches the swing end, the separate block receives the motion of the vane via the cushion member, so that the shock generated by the collision between the vane and the separate block is cushioned. The material is absorbed.

[0004]

However, in the above cushion structure, since it is necessary to attach a cushion member made of an elastic material such as rubber to the surface of the metal vane, the adhesive force between the vane and the cushion member is increased. If not, the cushion member will fall out of the vane due to the impact at the time of collision with the separate block.

On the other hand, even if the provisional law makes the adhesive force between the vane and the cushion member as strong as possible, the cushion member gradually peels off due to repeated impacts for a long time, and finally the cushion member is removed. There is probably a fear of falling out of the vane.

In addition to this, not only the cushioning effect is lost, but also the cushioning member itself may interfere with the operation of the actuating device itself, resulting in a lack of reliability as a swinging actuating device. was there.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a cushion structure for a swing-type actuating device of this type, which is easy to assemble and has a high reliability without falling off.

[0008]

In order to achieve the above object, according to the present invention, a cushion member is disposed along a cylinder side separate block surface facing a vane, and both end portions of the cushion member are arranged. Is fitted and retained in the respective locking holes of the body and the cover that close the openings at both ends of the cylinder.

[0009]

As a result, the cushion member can be assembled by simply fitting both end portions into the locking holes of the body and the cover when assembling the swing-type actuating device without using a troublesome means such as sticking.

Further, after the assembling, since it is firmly held by the locking holes of the body and the cover, the situation where it does not come off due to repeated shocks for a long time does not occur, and the desired shock absorbing action is always maintained. To do.

Therefore, it is possible to provide a highly reliable cushion structure for this type of rocking type operating device.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings by exemplifying a case where the present invention is applied to a rotary damper which is an oscillating type operating device.

In FIGS. 1 and 2, a rotary damper 1 comprises a cylinder 2 composed of a cylindrical member, a body 3 fitted in openings at both ends of the cylinder 2 and a cover 4, and forms a casing 5. 2, the body 3 and the cover 4 are connected to each other by using welded portions 6a and 6b formed by seam welding means.

On the inner peripheral surface of the cylinder 2, the cylinder 2
The two separate blocks 7a and 7b are arranged in pressure contact with the body 3 and the cover 4 and are 180 degrees out of phase with each other.

These separate blocks 7a and 7b are
Fitting holes 3a, 3b formed in the body 3 at the protruding portions at both ends of knock pins 8a, 8b inserted through them and fitting holes 4a, 4b formed in the cover 4 (the fitting holes 3a,
4a only) are fixed to the casing 5 at a predetermined position.

Incidentally, as well known in the related art in this type of rocking type actuator, the separate blocks 7a and 7b may be formed integrally with the cylinder 2.

On the other hand, a shaft 9 is inserted through the body 3 along the axis of the cylinder 2 from the outside, and the shaft 9 is rotatable by bearings 10 and 11 fitted to the body 3 and the cover 4, respectively. Support.

An oil seal 14 is provided at the end of the insertion opening of the shaft 9 in the body 3 and is fixed to the bearing 10 by a washer 12 and a snap ring 13. Keeps oil tight.

In the casing 5, a vane body 16 regulated in the rotational direction via a spline 15 is fitted on the outer periphery of the shaft 9, and the outer peripheral surface of the boss portion 16a of the vane body 16 is the cylinder. It is in sliding contact with the inner peripheral surfaces of the separate blocks 7a, 7b provided on the second side.

Further, the vane body 1 is provided on the outer periphery of the shaft 9.
A snap ring 17 is fitted in contact with the boss 16a of the shaft 6, and the snap ring 17 prevents the shaft 9 from coming out.

The vane body 16 has the bosses 16a through 1a.
Two vanes 18 that extend 80 degrees out of phase
The vanes 18a and 18b are provided with a and 18b, and the oil chambers 19a and 19b are defined between the separate blocks 7a and 7b by sliding the tip end surfaces and both side surfaces of the vanes 18a and 18b to the cylinder 2 and the bearings 10 and 11, respectively.

Cushion members 20a, 20b forming the characteristic part of the present invention are arranged along the recesses 7c, 7d formed on both sides of the separate blocks 7a, 7b facing the vanes 18a, 18b.

These cushion members 20a and 20b are
It is made of an elastic material such as rubber, and as shown in FIG. 3 when the casing 5 is assembled, both end portions of the cushion members 20a and 20b are formed on the body 3 and the cover 4, respectively. Locking holes 3c, 4c, 3d, 4 of
It is held by being loosely inserted in d.

Thus, when a rotational movement is applied to the shaft 9 from the outside, the casing 5 together with the shaft 9 is rotated.
The vane body 16 rotates inside, and the vanes 18a and 18b of the vane body 16 reduce the volume of one of the oil chambers 19a and 19b and expand the other.

As a result, the hydraulic oil flows from the reduced side of the oil chambers 19a, 19b toward the expanded side through the gap around the vane body 16 which is not a seal if it is a sliding portion, and these A damping force is generated by the flow resistance of the hydraulic oil passing through the gap, and the damping force is applied to the reciprocating rotational movement of the shaft 9 to serve as a rotary damper.

Further, a part of the hydraulic oil passing through the above-mentioned gap enters the inner surfaces of the bearings 10 and 11 which are also sliding parts but are sealless, and these bearings 1
While lubricating the sliding contact surfaces of 0 and 11, it reaches the oil seal 14 and also lubricates it.

In the above case, the shaft 9 is externally applied.
If the amplitude of the rotational motion applied to is increased,
The vanes 18a and 18b are separate blocks 7a and 7b.
Before hitting the cushion member 20a or 20b, the cushion member 2a
Compress 0a and 20b.

The movement of the vanes 18a and 18b is buffered by the compression of the cushion members 20a and 20b, and the vanes 18a and 18b are separated from the separate blocks 7a and 7b.
Prevent a violent crash into the ground.

Moreover, even if the compression operation of the cushion members 20a, 20b by the vanes 18a, 18b is repeated, the cushion members 20a, 20b are still
Both ends have locking holes 3c, 4c, 3d for the body 3 and the cover 4,
Since it is held by 4d, there is no fear that it will fall off from a predetermined position.

The cushion members 20a and 20b are provided.
In the case of this embodiment, is formed in a cylindrical shape, but it may be formed in a prismatic shape or a hollow body obtained by hollowing them.

However, if, for example, the cushion members 20a, 20b are formed in a cylindrical shape as in this embodiment, the repulsive force of the cushion members 20a, 20b will be quadratic as the vanes 18a, 18b compress. Will increase.

Therefore, the cushion members 20a, 20
The shape of b may be selected according to the purpose of use at that time.

On the other hand, in the construction of the casing 5, due to a manufacturing error or an assembly error of each component member, the separate block 7a, rather than the locking holes 3c, 4c, 3d, 4d of the body 3 and the cover 4, is separated. The recesses 7c and 7d of 7b retract,
As shown by the dotted line in FIG. 3, a step f may be formed at the boundary between the two.

In the above, the cushion members 20a, 2
It is assumed that 0b is compressed between the recesses 7c and 7d of the separate blocks 7a and 7b by the vanes 18a and 18b, leaving the portions loosely inserted in the locking holes 3c, 4c, 3d and 4d.

Then, the cushion members 20a and 20b are forcibly deformed along the step f at the boundary portion, and a concentrated load is applied to the portion, so that the portions are cracked by repeated compression and finally fracture occurs. It is assumed that there is a risk of falling out.

FIG. 4 shows a case where the above-mentioned fear is taken into consideration. The locking holes 3c, 4c, 3d,
4d is formed as a large-diameter hole or an elongated hole eccentric to the separate blocks 7a and 7b side, and the concentrated load generated by the step f is eliminated by the large-diameter hole or the elongated hole.

Further, in FIG. 5, instead of the above, the cushion members 20a, 20a are passed through the tapered portion.
By making both end portions of b thin, the elasticity of the support portion is increased, or by combining it with the above-mentioned eccentric hole, the influence of the step f on the cushion members 20a, 20b is eliminated.

In the above embodiments, the rotary damper as the rocking type operating device has been described as an example, but in contrast to this, the casing 5 is provided with the oil chambers 19a, 1a.
It is obvious that a rotary actuator can be used by providing ports leading to 9b and supplying / discharging hydraulic oil through these ports.

However, unlike the rotary actuator, in the rotary damper, since the working oil is enclosed in the oil chambers 19a and 19b, the enclosed working oil changes in oil temperature and leaks to the outside. Causes excess and deficiency, and hinders normal operation of the rotary damper.

Therefore, in the illustrated embodiment, as shown in FIG. 1, a hollow portion is formed in the axial direction from the inner end of the shaft 9 in order to compensate the excess or deficiency of the hydraulic oil. A gas chamber 22 in which a free piston 21 is slidably fitted and sealed in the hollow portion and a working oil reservoir chamber 23 that opens through the inner end of the shaft 9 are configured.

The opening portion of the hydraulic oil reservoir 23 extends from the gap 24 between the cover 4 and the shaft 9 to the oil chambers 19a and 19b through the sliding contact surfaces of the sealless bearings 10 and 11 and the spline 15 portion. Therefore, excess or deficiency of the hydraulic oil generated in the oil chambers 19a and 19b is compensated in the hydraulic oil reservoir 23.

However, in this way, the oil chambers 19a, 19a
If the excess or deficiency of hydraulic oil in b is compensated, the amount of hydraulic oil flowing from the reduced side of the oil chambers 19a, 19b to the expanded side through the gap around the vane body 16 during operation of the rotary damper 1 will be reduced. Part of the oil escapes to the hydraulic oil reservoir chamber 23, and the amount of hydraulic oil on the expanded side of the oil chambers 19a and 19b becomes insufficient, causing cavitation.

Therefore, in this embodiment, in order to prevent this, the vertical through holes 25a, 25b are provided on the vane body 16 from the boss portion 16a to the vanes 18a, 18b.
And lateral through holes 26a, 26b that intersect these vertical through holes 25a, 25b are formed in the vanes 18a, 18b.

Oil chamber 19 of the lateral through holes 26a, 26b
The openings to a and 19b are the vanes 18a and 1a, respectively.
Reed valve 2 attached to 8b with pins 27a and 27b
It is covered with 8a and 28b.

As a result, as described above, the portion of the spline 15 communicating with the hydraulic oil reservoir chamber 23 passes through the reed valves 28a, 28b from the vertical through holes 25a, 25b and the horizontal through holes 26a, 26b, and the oil chamber 19a, 19b, and the working oil in the working oil reservoir 23 is supplied to the oil chamber 1 through these passages.
Replenishment to 9a and 19 prevents the occurrence of cavitation.

When the rotary damper 1 is used as a damper for damping vibration between sprung and unsprung parts of an automobile or the like, as shown in FIG. 1, for example, only one reed valve 28a is provided. A small hole 29a is provided.

Only when the oil chamber 19a is reduced, part of the hydraulic oil in the oil chamber 19a is partially opened from the small hole 29a of the reed valve 28a through the lateral through holes 26a and 26b to open the reed valve 28b. 19b, and the horizontal through holes 26a, 26b and the vertical through holes 25a, 2
By flowing the oil to the hydraulic oil chamber 23 through 5b, a difference is generated in the generated damping force depending on the rotating direction of the rotary damper 1.

Further, in the rotary damper 1 of this embodiment, as described at the beginning, the body 3 and the cover 4 are fitted to the cylinder 2, and their joints are welded by seam welding means. The casing 5 having a welded structure is configured by connecting the members 6a and 6b.

As described above, constructing the casing 5 by the seam welding means is generally very effective in that the seam welding means is extremely efficient in terms of workability and technology.

On the other hand, however, in order to make the casing 5 have a welded structure, it is necessary to perform welding after the body 3 and the cover 4 are fitted in the cylinder 2.

Therefore, it is impossible to weld a seal member between the cylinder 2 and the body 3 and the cover 4, and the sealability between the cylinder 2 and the body 3 and the cover 4 is different from that of the body 3 with respect to the cylinder 2. There is no choice but to rely on the metal contact by press fitting the cover 4.

As a result, with such a metal contact, it is impossible to prevent the occurrence of some clearance by any means, and the welded portions 6a, 6 are passed through these clearances.
The high pressure in the oil chambers 19a and 19b acts on b.

From this, in particular, in the rotary damper 1 of this kind in which the welded portions 6a and 6b have a large diameter and the high pressure acts on the oil chambers 19a and 19b, the welded portion 6 is as much as possible.
Even if the wall thicknesses of a and 6b are increased, it is difficult to apply it as it is in terms of pressure resistance.

Therefore, in this embodiment, as shown in FIGS. 1, 6 and 7, annular pressure relief grooves 30a and 30b are formed in the metal contact portion between the cylinder 2, the body 3 and the cover 4. To form these pressure relief grooves 30
By positively connecting a and 30b to the hydraulic oil reservoir chamber 23, it is possible to make the casing 5 have a welded structure.

That is, an annular pressure relief groove 30a is formed at the metal contact portion between the cylinder 2 and the body 3 on the press-fitting surface of the body 3 with respect to the cylinder 2, and the pressure relief groove 30a is provided in the body 3. Vertical grooves 32 formed on the end faces of the separate blocks 7a and 7b by the notched grooves 31a.
leading to a.

Similarly, a pressure relief groove 30b is formed in the metal contact portion between the cylinder 2 and the cover 4 by utilizing chamfering that also serves as a guide when the cover 4 is press-fitted. The notch groove 31b provided in the vertical groove 32b on the opposite end surface of the separate blocks 7a, 7b.
Leading to.

As can be seen from the above, the pressure relief grooves 30a and 30b may be formed on the metal contact surfaces of the body 3 and the cover 4, or may be formed by utilizing their respective chamfers. , Again, cylinder 2
It may be formed on the side contact surface.

The vertical grooves 32a, 32b formed on both end surfaces of the separate blocks 7a, 7b extend vertically through the central portions of both end surfaces of the separate blocks 7a, 7b, and the knock pins 8a, 8b. Through holes 33a, 33b formed in the diametrical direction and the through holes 33a, 3b.
3b are communicated with each other through axial through holes 34a, 34b crossing 3b.

It should be noted that the vertical grooves 32a, 32b are provided at the center of both ends of the separate blocks 7a, 7b, for example, as in the example of FIG. 8, the vertical grooves 32b are provided in the cover 4. It is also possible to form them on the body 3 and cover 4 sides without forming them.

Further, as described above, in this embodiment, the vertical grooves 32a, 32b are passed through the through holes 33a, 33b of the knock pins 8a, 8b and the through holes 34a, 34b from the outer peripheral surface of the separate blocks 7a, 7b. It leads to the inner surface.

However, it is not always necessary to do this, and for example, the middle part of the vertical grooves 32a, 32b is formed as an annular groove surrounding the outer peripheral surfaces of the knock pins 8a, 8b.
These annular grooves may avoid the knock pins 8a and 8b and guide the separate blocks 7a and 7b from the outer peripheral surface to the inner peripheral surface.

The vertical grooves 32a, 32b communicate with the cutout grooves 31a, 31b extending from the pressure relief grooves 30a, 30b on the outer peripheral surfaces of the separate blocks 7a, 7b, and the inner peripheral surfaces are sealless. The bearings 10 and 11 are communicated with the notch groove portion of the spline 15 through the sliding contact surfaces.

As described above, the portion of the spline 15 communicates with the working oil reservoir 23 through the gap 24 between the cover 4 and the shaft 9 through the sliding contact surfaces of the bearings 10 and 11.

In this embodiment, in order to further secure the above communication, the vertical grooves 32 on the side of the separate blocks 7a, 7b are formed on the sliding contact surfaces of the bearings 10, 11.
Oil grooves 35a and 35b communicating with a and 32b are formed.

Of course, these oil grooves 35a and 35b are formed by the body 3 and the bearing 10, and the cover 4 and the bearing 11.
It goes without saying that it may be formed through the fitting portion of.

Thus, the annular pressure relief grooves 30a, 30b formed on the metal contact surfaces of the cylinder 2, the body 3 and the cover 4 are separated blocks 7a, 7b penetrating the notch grooves 31a, 31b and the knock pins 8a, 8b.
b vertical grooves 32a, 32b and bearings 10, 11
A series of oil passages 36a, 3 consisting of oil grooves 35a, 35b
It will lead to the working oil reservoir 23 through 6b.

As a result, the pressure relief grooves 30a, 30b are formed.
By always maintaining a low pressure, it is possible to prevent the high pressure in the oil chambers 19a, 19b from directly acting on the welded portions 6a, 6b of the cylinder 2, the body 3 and the cover 4, and to make the casing 5 a welded structure. It is possible.

In the above embodiment, the cylinder 2
On the other hand, the non-disassembly type one-piece type rotary damper in which the body 3 and the cover 4 are attached by welding to form the casing 5 has been described as an example. However, for example, the cylinder and the body are integrally structured to cover the cover 4 It goes without saying that the present invention can also be implemented in a non-disassembled, one-piece type rotary damper in which only one is welded.

The present invention can also be applied to a three-piece type or two-piece type rotary damper which can be disassembled by integrally forming them by bolts without making it non-decomposable by welding. is there.

[0070]

As described above, according to the first aspect of the present invention, both end portions of the cushion member are simply attached at the time of assembling the rocking type operation device without using a troublesome means such as attaching the cushion member. It can be assembled simply by fitting it into the locking holes on the body and cover.

In addition, since it is firmly held by the engaging holes of the body and the cover after the assembling, there is no possibility that it will fall off due to repeated impacts from the vane for a long time, and it will always be in place. It is possible to maintain the shock absorbing action during the period.

As a result, it is possible to provide a highly reliable cushion structure for this type of rocking type operating device.

Further, according to the invention of claim 2, in addition to the above, at the time of assembly, the both end holding portions of the cushion member have a gap in the compression direction with respect to the locking holes of the body and the cover. Even if there is a manufacturing error or an assembling error, a concentrated load is not applied to the boundary portion between the both end holding portions of the cushion member during compression, and cracks can be prevented from occurring there.

Further, according to the third aspect of the present invention, since the both-end holding portion of the cushion member has a smaller diameter than the portion compressed by the vane, the elastic force at the boundary portion of the both-end holding portions increases, and the above-mentioned It is possible to prevent the occurrence of cracks due to concentrated loads.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing an embodiment in which the present invention is applied to a vehicle rotary damper.

FIG. 2 is a vertical sectional side view taken along line XX in FIG.

FIG. 3 is an enlarged sectional view showing a holding portion of a cushion member.

FIG. 4 is an enlarged sectional view showing another embodiment of the above.

FIG. 5 is an enlarged sectional view showing still another embodiment of the above.

FIG. 6 is an enlarged cross-sectional view showing an intermediate portion of a cylinder-body joint.

FIG. 7 is an enlarged cross-sectional view of the intermediate portion of the joint between the cylinder and the cover.

FIG. 8 is an enlarged cross-sectional view showing another embodiment of the above coupling portion.

[Explanation of symbols]

 1 Rotary Damper 2 Cylinder 3 Body 3c, 3d Locking Hole 4 Cover 4c, 4d Locking Hole 7a, 7b Separate Block 18a, 18b Vanes 20a, 20b Cushion Member

Claims (3)

[Claims] 1. A cushion member is disposed along a cylinder-side separate block surface facing a vane, and both end portions of the cushion member are provided in respective locking holes of a body and a cover that close openings at both ends of the cylinder. A cushion structure for a swing-type actuating device, which is inserted and held. 2. The engagement hole of the body and the cover is formed as a large diameter hole or a long hole eccentric to the separate block side with respect to both end portions of the cushion member.
Cushion structure for the rocking type operating device described. 3. The cushion structure for a swing-type actuating device according to claim 1, wherein both end portions of the cushion member are formed to be thin through a taper.