JP3407830B2 - Rotary damper - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic rotary damper that damps a vehicle or other external vibrations by utilizing a swinging motion.

[0002]

2. Description of the Related Art Conventionally, as this type of rotary damper, for example, one disclosed in Japanese Patent Application Publication No. 145834 of 1988 is known.

That is, in this device, side cases forming pressure resistant wall surfaces are respectively applied to openings at both ends of a cylindrical casing, and the side cases are fixed to the casing with bolts to close the openings at both ends. A shaft is rotatably inserted through the central portion of the casing using these both side cases as bearings.

On the other hand, a seal is interposed between both side cases and the shaft to seal the inside of the casing with these seals, and a separate block provided on the inner peripheral surface of the casing and a vane extending from the shaft side. The inside of the casing is divided into a plurality of oil chambers.

As a result, when a relative rotational movement is generated between the casing and the shaft, one of the oil chambers located on both sides of the vane and the separate block is compressed and the other is expanded.

The oil chambers on the compression side and the expansion side are provided with an oil passage having a damping valve interposed therebetween (instead of this oil passage, a gap between the vane and the casing and the side case, and a separate block, the shaft and the side case). Sometimes there is a gap between them) and communicate with each other.

Thus, a flow resistance is added to the hydraulic oil pushed out from the compression-side oil chamber toward the expansion-side oil chamber, and this flow resistance causes a damping force during relative rotational movement between the casing and the shaft. Will occur.

[0008]

As described above, in the above-described conventional example, not only the shafts are rotatably supported by using both side cases constituting the pressure-resistant wall surface of the oil chamber as bearings, A seal is directly provided between the both side cases and the shaft to seal the inside of the casing.

Therefore, it is necessary to form these side cases as thick members for pressure resistant wall surfaces, and
Further, it is necessary to form a bearing portion for interposing a seal on the inner peripheral surface.

As a result, there is a problem that the side case becomes remarkably heavy, the weight of the entire rotary damper increases, and the structure itself becomes complicated and the manufacturing cost increases.

In addition to the above, bolts are used to attach the side case to the casing.

[0012] As a result, a large number of mounting bolts for joining are required, and further, it is necessary to form bolt holes, spot facings, and screw processing on the casing and the side case. There are problems in terms of simplification, weight reduction, and reduction of manufacturing cost.

Therefore, an object of the present invention is to provide a rotary damper of this type which can be easily processed and reduced in weight, and thereby can reduce the manufacturing cost.

[0014]

SUMMARY OF THE INVENTION In the present invention, the above-described object is to provide a bearing made of a thick disk, a thin cap for holding a seal, and side bearings forming pressure-resistant wall surfaces on both sides of an oil chamber. And a thin cap for sealing, which are separately formed, and the bearings are arranged inward, and the side cases are connected to the openings at both ends of the casing.

Further, in addition to the above, preferably, side cases formed by dividing the above two members into the thin-walled portions formed by notching the inner peripheral surfaces of both ends of the casing are inserted from both sides, and these thin-walled portions are inserted. This can be achieved even more effectively by crimping or by joining the thin portion and the thin cap on the side case side by welding to integrally fix both side cases to the casing.

[0016]

That is, as a result, the shaft provided with the vanes is rotatably supported through the bearings in each side case, and these bearings can define the pressure-resistant wall surfaces on both sides of the oil chamber.

Therefore, each of the bearings that support the shaft may be formed as a thick disk having a simple pressure resistant shape, and the machining thereof becomes extremely easy.

Further, since the seal holding cap and the sealing cap located outside these bearings also have a low-pressure chamber inside, they can be made into a thin structure and easily processed by means of pressing or the like. You can

Thus, it is possible to reduce the manufacturing cost as well as to facilitate the processing of the both side cases.

Further, in addition to the above, the thin-walled portions formed on the inner peripheral surfaces of both ends of the casing should not be caulked, or the thin-walled cap and the thin-walled portion should be joined by welding to integrally fix both side cases to the casing. As a result, there is no need for bolts, bolt holes, counterbore, screwing, etc. for connecting them.

Moreover, since it becomes boltless and the assembling of both side cases becomes easy, it becomes possible to facilitate the processing of the side cases described above, and also to reduce the weight and further reduce the manufacturing cost. Of.

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings.

FIG. 1 is a cut-out development view taken along the line AA in FIG. 2. The rotary damper 1 includes a cylindrical casing 2 and side cases 3 fitted into openings at both ends of the casing 2. 4, a working chamber 5 (see FIG. 2) defined by the casing 2 and the side cases 3 and 4, a vane body 6 disposed over the working chamber 5, and a vane body 6 fixed to the vane body 6. It has a shaft 7 inserted therein.

The casing 2 constitutes the outer pressure-resistant wall surface of the working chamber 5, and is formed with thin portions 2a and 2b by leaving a predetermined size in the central portion by notching the inner peripheral surfaces at both ends.

Further, two (of course, one or three or more) separate blocks 8 and 9 (see FIG. 2) having a phase difference of 180 degrees are fixed to the inner peripheral surface. The separate blocks 8 and 9 are configured so that their widths are adapted to the predetermined size of the central portion.

The side cases 3 and 4 serve as pressure-resistant wall surfaces on both sides of the working chamber 5 and support the shaft 7 of the vane body 6 rotatably.

In the case of this embodiment, the side case 3 serves as a bearing member for the shaft 7, and also has a bearing 3a made of a thick disk that also serves as a thrust bush for bearing a thrust load, and for sealing. The seal 10 and the thin cap 3b fitted therein are divided into two members.

Similarly, the side case 4 also has a thick disk bearing 4a which serves both as a bearing member and as a thrust bush for bearing the thrust load.
And a thin cap 4b for sealing are separately configured.

The thin cap 4b is provided with a hydraulic oil injection hole 4c, and the injection hole 4c is sealed by a steel ball 4d after the hydraulic oil is injected into the rotary damper 1.

As described above, by constructing the side cases 3 and 4 with the bearings 3a and 4a having a simple disk-shaped bearing and the thin caps 3b and 4b for sealing,
It becomes possible to facilitate the processing and reduce the weight while ensuring the original role described above.

The outer peripheral portions of the bearings 3a, 4a on the back side are chamfered to form annular grooves 11a, 11b between the bearings 3a, 4a and the thin caps 3b, 4b.
Seals 12a, 12b are provided in these annular grooves 11a, 11b.
Is fitted.

The above-mentioned side cases 3 and 4 are inserted to the ends of the thin-walled portions 2a and 2b of the casing 2 with the bearings 3a and 4a inside.

Then, after that, these thin portions 2 at both ends are
By bending a and 2b along the thin caps 3b and 4b, they are integrally attached to the casing 2 by caulking 39a and 39b.

Thus, the casing 2 and the side cases 3 and 4 cooperate with each other to define a closed working chamber 5.

From the outer peripheral surface of the vane body 6, the casing 2
The same number of vanes 13, 14 (see FIG. 2) as the side separate blocks 7, 8 are projected with a phase of 180 degrees.

Like the separate blocks 8 and 9, these vanes 13 and 14 are also adapted to the predetermined size of the central portion of the casing 2.

As shown in FIG. 2, the heights of the separate blocks 8 and 9 and the vanes 13 and 14 are such that the respective tips are in sliding contact with the outer peripheral surface of the vane body 6 and the inner peripheral surface of the casing 2. It is made in.

As a result, the separate blocks 8 and 9 and the vanes 13 and 14 cooperate with each other to divide the inside of the working chamber 5 into four oil chambers 15, 16, 17 and 18, and to rotate the vane body 6. Accordingly, the oil chambers 15 and 17 and the oil chambers 16 and 18
Will be alternately contracted and expanded.

On the other hand, the shaft 7 fixedly inserted into the vane body 6 is made of a pipe material and has a hollow structure.
The side cases 3 and 4 are rotatably supported by bearings 3a and 4a.

One end of the shaft 7 extends through the thin cap 3b of the side case 3 to the outside, and a protruding portion thereof is oil-tightly sealed by a seal 10.

The other end of the shaft 7 extends to the vicinity of the thin cap 4b of the side case 4 and opens in the thin cap 4b.

The open end portion of the shaft 7 to the outside is
A connecting portion 20 is formed by forming a taper 19 tapering outwards, and a block 21 is fitted to the connecting portion 20.

The block 21 is provided with a seal 21a on its outer circumference to keep the hollow portion 22 inside the shaft 7 airtight to the outside, and backs up the connecting portion 20 of the shaft 7 from the inside to prevent deformation of the portion. Also fulfill the role of doing.

In addition to the above, a screw hole 23 is formed in the outer surface of the block 21, and the connecting portion 20 to the external vibrating body is formed.
When connecting the blocks, the screw holes 23 are used to
It can be pulled outwards.

As a result, the block 21 pulled outwards cooperates with the taper 19 to ensure the sealing action of the hollow portion 22, and the spline formed on the outer peripheral surface by expanding the diameter of the connecting portion 20. It plays the role of eliminating 24 rattles.

Thus, with respect to the rotary damper 1 having the above structure, the shaft 7 is passed from the external vibrating body through the connecting portion 20.
When the reciprocating rotational movement is transmitted to the working chamber 5, the vane body 6 rotates in the working chamber 5 left and right around the axis together with the vanes 13 and 14, and the oil chamber 15 between the separate blocks 8 and 9 on the casing 2 side. , 17 and 16, 18 are contracted and expanded alternately.

As a result, the working oil in the oil chamber on the contracting side is slidably contacted between the tips of the vanes 13 and 14 and the casing 2, both side surfaces of the vanes 13 and 14 and the bearings 3a and 4a.
Flows into the oil chamber on the expansion side through a sliding contact gap between the separate blocks 8 and 9, a sliding contact gap between the vane body 6 and a gap between both side surfaces of the separate blocks 8 and 9 and the bearings 3a and 4a. .

A damping force is generated by the flow resistance of the hydraulic oil flowing through these gaps, and this damping force is applied to the vane 1.
It acts on the external vibrating body from 3, 14 through the vane body 6 and the shaft 7 to damp the movement of the vibrating body.

On the other hand, in the rotary damper 1 of this type, the oil chamber 15 to
If the working oil sealed in 18 is excessive or deficient, the damping action of the rotary damper 1 is directly adversely affected.

Therefore, in addition to preventing this,
In order to give a difference to the damping force generated in the operation direction of the rotary damper 1 and effectively suppress the vibration generated in the external vibrating body, it also has the configuration described below.

That is, the hollow portion 22 of the shaft 7 is formed by the free piston 25 fitted with the seal 25a on the outer circumference thereof, and the gas chamber 26 on the block 21 side and the oil storage chamber 27 on the open end side.
The gas chamber 26 and the oil storage chamber 27 form an accumulator.

The oil storage chamber 27 of the accumulator is provided with the bearing 4 from the inside of the thin cap 4b of the side case 4.
the vane 1 through the oil passage 28b formed in the bearing surface of a and the oil passages 29a and 29b between the vane body 6 and the shaft 7.
It communicates with the internal oil passages 30a, 30b of 3,14.

The oil passage 28 is formed on the bearing surface of the bearing 4a.
Using the sliding contact gap between the shaft 7 and the bearing 4a without drilling b, the oil storage chamber 27 is moved from the sliding contact gap to the oil passage 29.
Internal oil passage 30 of vanes 13 and 14 through a and 29b
You may make it communicate with a and 30b.

A check valve 3 provided with these internal oil passages 30a and 30b press-fitted into the vanes 13 and 14 is provided.
1, 32, 33, and 34 communicate with the oil chambers 15 to 18, and also communicate with the oil chambers 15 and 17 through orifices 35a and 35b for setting the expansion / damping force ratio provided in parallel with the check valves 31 and 33. ing.

The check valves 31 to 34 have the same structure. As shown in FIG. 3, by forming the case 36 by drawing, a check ball 37 and a check spring 38 are formed in the case 36. They are housed in a cartridge structure.

As shown in FIG. 2, these check valves 31 to 34 are press-fitted into both sides of the vanes 13 and 14 via the case 36 and embedded, and the internal oil passages 30a and 30b are passed through the check valves 31 to 34, respectively. Are communicated with the oil chambers 15 to 18, respectively.

As a result, when a shortage occurs in the hydraulic oil sealed in the oil chambers 15 to 18 due to a change in the temperature of the hydraulic oil, external leakage, etc., the hydraulic oil in the oil storage chamber 27 is stored in the oil storage chamber 2.
The check valves 31 to 34 are opened and sucked into the oil chambers 15 to 18 through the path connecting the oil reservoirs 15 to 18 with each other to compensate for this shortage.

On the contrary, when the oil amount becomes excessive, the oil chamber 15 to
The hydraulic oil in 18 is used to set the orifice 35 for setting the expansion and damping force ratio.
a, 35b to oil passages 29a, 29b and oil passage 28b
(Or, it is pushed out to the oil storage chamber 27 through the sliding contact gap between the shaft 7 and the bearing 4a), and thus the excess amount is eliminated, so that the damping action of the rotary damper 1 is properly maintained.

On the other hand, when the rotary damper 1 is operated, a part of the hydraulic oil is set to the orifices 35a, 35 for setting the expansion / damping force ratio only when the oil chambers 15, 17 are contracted.
b through the above path to the oil storage chamber 27 in the shaft 7 and limit the reduction rate of the damping force generated during the operation in that direction by the pressure loss of the orifices 35a, 35b, while reducing the damping force generated during the operation in the opposite direction. To give the right difference.

If the hydraulic oil pressure is applied between the bearing 3a of the side case 3 and the seal 10, the seal 10 may be damaged.

Therefore, in this embodiment, the oil passages 29a, 2 on the vane body 6 side are also formed on the bearing surface of the bearing 3a.
The oil passage 28a leading to 9b is bored, and the hydraulic oil pressure trapped between the bearing 3a and the seal 10 is released to the oil storage chamber 27 side through the oil passage 28a, thereby improving the durability of the seal 10.

However, regarding this point, the bearing 3
If the sliding contact gap between the shaft a and the shaft 7 is managed to be sufficiently small, the clearance between the bearing 3a and the shaft 7 exerts a throttling effect even when the oil passage 28a is not provided, thereby cutting the hydraulic oil pressure.

As a result, high pressure is not trapped between the bearing 3a and the seal 10, so that the oil passage 28a is not actually bored in the bearing surface of the bearing 3a.
When the rotary damper 1 is used, there is no risk of damage such as impairing the sealing action of the seal 10.

As described above, in the embodiment of FIG. 1 described so far, both side cases 3 and 4 are fixed to the casing 2 by caulking the thin portions 2a and 2b at both ends of the casing 2.
However, as shown in the embodiment of FIG. 4, they may be connected to each other by welding 40a and 40b.

Because, in the rotary damper 1 shown in the embodiment of FIG. 1, both side cases 3 and 4 have bearings 3a and 4a which are bearing members in the shape of thick disk and a thin cap which is a sealing member. 3b and 4b are respectively divided and configured, and further, these bearings 3a and 4a
The inside is attached to the casing 2.

Moreover, when the connecting means by the weldings 40a and 40b is adopted, naturally, the seals 12a and 12b for keeping the connecting portions oil-tight are also unnecessary.

Therefore, even if the thin-walled caps 3b and 4b are welded to the casing 2 and joined, the bearings 3a and 4a are deformed by the welding heat and the bearing function is adversely affected, or the seal member is damaged. This is because there is no fear of impairing the sealing function.

[0068]

As described above, according to the first aspect of the present invention, the left and right side cases are divided into two members, that is, a bearing as a bearing member and a thin cap as a sealing member, and By coupling these side cases to the casing with the bearings facing inward, the bearings may be configured as a simple pressure-resistant thick-walled disc, which is extremely easy to process.

Further, the seal holding cap and the sealing cap located outside these bearings can also be easily processed by a means such as a press with a thin structure.

Moreover, since the side case can be made lighter in addition to facilitating the processing, the manufacturing cost can be reduced.

According to the second aspect of the present invention, in addition to the above effects, both side cases can be easily positioned with respect to the casing and can be connected to each other without using bolts.

Therefore, the bolts for connecting the casing and the side case, the bolt holes, the spot facing, the screwing, etc. are not necessary at all, and the assembling itself of both side cases becomes easy. It is possible to reduce the weight and further reduce the manufacturing cost in addition to facilitating the processing.

Further, according to the invention of claim 3, since the side case is divided into the two members of the bearing and the thin cap, the side case can be attached to the casing by welding. Can be more easily coupled and the assembling property can be remarkably improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing an embodiment of a rotary damper according to the present invention.

FIG. 2 is a vertical sectional side view of the same.

FIG. 3 is an enlarged sectional view showing only a check valve.

FIG. 4 is a vertical sectional front view showing another embodiment of the rotary damper according to the present invention.

[Explanation of symbols]

1 rotary damper 2 casing 2a, 2b Thin part 3,4 side case 3a, 4a bearings 3b Thin-walled cap for holding seals 4b Thin wall cap for sealing 6 vanes 7 shaft 8,9 separate block 10 seals 13,14 vanes 15, 16, 17, 18 Oil chamber 39a, 39b Caulking 40a, 40b welding

Claims (3)

(57) [Claims] 1. A cylinder-shaped casing having both end openings closed by side cases forming pressure-resistant wall surfaces,
A shaft is rotatably inserted into the center of the casing using these both side cases as bearings, and a seal is interposed between the both side cases and the shaft to seal the inside of the casing and to In a main body structure of a rotary damper in which the casing is divided into a plurality of oil chambers by a separate block provided on the peripheral surface and a vane extending from the shaft side, each side case that constitutes both pressure-resistant wall surfaces of each oil chamber has a thick wall. A bearing made of a disc and a thin-wall cap for holding the seal, and a bearing of a thick-wall disc and a thin-wall cap for sealing are also divided into two parts. A rotary damper characterized in that it is connected to both end openings of the rotary damper. 2. A casing is formed by cutting out inner peripheral surfaces at both ends to form thin-walled portions, and a side case formed by dividing into a thin-walled bearing and a thin-walled cap is inserted into the thin-walled portions. The rotary damper according to claim 1, wherein both side cases are integrally fixed to the casing by caulking the thin portion. 3. A casing is formed by notching both inner peripheral surfaces of both ends to form a thin-walled portion, and each side case formed by dividing into a thin-walled disc bearing and a thin-walled cap is inserted into the thin-walled portion. The rotary damper according to claim 1, wherein the thin wall portion and the thin wall cap are joined by welding to integrally fix both side cases to the casing.