JPH0214656Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a power transmission joint in a vehicle such as an automobile. More specifically, the invention relates to a power transmission joint that can absorb vibrations in both the axial and rotational directions.

[Conventional technology]

BACKGROUND OF THE INVENTION Vibrations in the axial and rotational directions occur in power transmission shafts such as propeller shafts in vehicles such as automobiles due to torque fluctuations and the like. Therefore, as a power transmission joint used for a power transmission shaft such as a propeller shaft, it is desirable to use a joint that can absorb vibrations in both the axial direction and the rotational direction.

However, conventional power transmission joints of this type have not been configured to absorb vibrations in either the axial direction or the rotational direction. for example,
There are Japanese Utility Model Application Publication No. 50-97150 "Power Transmission Device in Vehicles" and Japanese Patent Application Publication No. 58-63504 "Joint Shaft", both of which have vibration absorption mechanisms in the form of shock absorbers using hydraulic pressure. , designed to absorb vibrations in the axial direction. However, it is not designed to absorb vibrations in the direction of rotation. Therefore, in order to absorb vibrations in the rotational direction, a separate joint must be provided, which is disadvantageous in that a plurality of joints are required and the size becomes large.

There are also joints that absorb vibrations in the rotational direction, but these types of joints generally have a flexible structure, which can cause joint angles between the drive shaft and driven shaft, misalignment, eccentricity, etc. , it may affect the bending rigidity of the joint rubber, causing a problem of increased unbalance.

[Problem that the invention attempts to solve]

Therefore, the problems that this invention attempts to solve are:
By incorporating a rotational vibration absorption mechanism into the axial vibration absorption mechanism, so-called one joint structure can absorb vibrations in both directions, the power transmission joint can be made compact, and the drive shaft and driven The purpose is to prevent the occurrence of imbalance by preventing misalignment by using a fitting connection that allows the shaft to slide in the axial direction.

[Means for solving problems]

In order to solve the above-mentioned problems, the power transmission joint of the present invention takes the following measures.

A drive shaft and a driven shaft, which are arranged on the same axis, are fitted and connected so that they can slide in the axial direction on the rotation axis, and at this joint position, the cylinder that forms the hydraulic chamber is connected to the drive shaft. It is attached to one side of the driven shaft.

The cylinder is equipped with a piston part that divides the hydraulic pressure chamber into two in the axial direction, and the piston part is formed of a radially inner part and a radially outer part, and a rotational damper is provided between the two parts. A mechanism is provided.

The radially outer portion of the piston portion is attached to the cylinder integrally in the direction of rotation but movable in the axial direction, and the inner portion in the radial direction is integrally attached to the other of the drive shaft and the driven shaft. .

Further, a communication hole serving as an orifice is provided in the piston portion to communicate between the two divided hydraulic pressure chambers, and spring means are interposed in the hydraulic pressure chambers on both sides of the piston portion.

[Effect]

The present invention achieves the following effects by taking the above-mentioned measures.

First, power is transmitted from the drive shaft to the driven shaft through the following path. Note that the next case is a case where the cylinder forming the hydraulic chamber is attached to the drive shaft.

Drive shaft → cylinder → piston part (radially outer part damper mechanism → radially inner part) → driven shaft When power is transmitted from this drive shaft to the driven shaft, vibrations in the rotational direction are suppressed by the damper mechanism of the piston part. Absorbed. That is, the damper mechanism is located between a radially outer portion and a radially inner portion of the piston portion, and is capable of absorbing relative rotational displacement between the two portions, and absorbs vibrations in the rotational direction.

Next, vibrations in the axial direction between the drive shaft and the driven shaft are absorbed by a so-called shock absorber type vibration absorption mechanism constructed inside the cylinder. That is, the piston portion moves within the cylinder due to relative movement between the drive shaft and the driven shaft. At this time, the hydraulic pressure in the hydraulic pressure chambers formed on both sides of the piston portion moves through the communication hole in the piston portion. Since the communication hole is an orifice, vibrations in the axial direction are absorbed by the flow resistance when the liquid pressure flows through the orifice.

In addition, since the drive shaft and the driven shaft are fitted together so that they can slide in the axial direction on the rotational axis, there is no joint between the drive shaft and the driven shaft, as in the case of conventional general flexible structures. No corners, misalignment, or eccentricity occur.

[Effect of idea]

The power transmission joint of the present invention incorporates a damper mechanism for absorbing vibrations in the rotational direction into the piston part of a vibration absorption mechanism formed in the form of a shock absorber for absorbing vibrations in the axial direction. Since it absorbs vibrations in both the axial and rotational directions, it can be made much more compact than conventional joints that were used in combination.

In addition, in the power transmission joint of the present invention, the driving shaft and the driven shaft are fitted and coupled so as to be slidable in the axial direction.
There is no joint angle between the drive shaft and driven shaft, no misalignment, no eccentricity, etc.
The joint will not become unbalanced.

〔Example〕

Hereinafter, embodiments of the present invention will be described based on the drawings.

1 and 2 show an embodiment of a power transmission joint according to the present invention.

The drive shaft 10 and the driven shaft 12 are arranged on the axis Y-Y, as shown in FIG. Axis Y-Y
is also the axis of rotation of the drive shaft 10 and the driven shaft 12. The driven shaft 12 is designed in this embodiment as a spider flange.

A coupling shaft body 14 is integrally provided on the drive shaft 10 . A coupling cylinder 16 is fixed to the driven shaft 12 with a nut 18 and is integrally provided therewith.
The joint shaft body 14 and the joint cylinder body 16 are connected to the rotation axis Y-
The driving shaft 10 and the driven shaft 12 are fitted in a cylindrical shape on Y.
and are coupled so as to be slidable in the axial direction.

Further, a cylinder 20 is attached to the drive shaft 10. The cylinder 20 has flange parts 2 on both sides.
2 and 24 and a cylindrical portion 26, and hydraulic chambers A and B are formed inside. The right-hand flange section 22 in FIG. The radially inner end of this flange portion 24 is in sliding contact with the coupling cylinder 16 of the driven shaft 12,
An oil seal 30 is provided at the sliding contact point to prevent leakage of the hydraulic pressure in the hydraulic chamber B. An oil seal 32 is also provided at the radially outer end of the flange portion 24 to prevent leakage of hydraulic pressure.

A piston portion 40 is disposed in the cylinder 20 . This piston portion 40 causes the cylinder 2
The hydraulic pressure chamber formed in 0 is divided into two parts: a hydraulic pressure chamber A on the right side and a hydraulic pressure chamber B on the left side as seen in FIG. The hydraulic chambers A and B are filled with oil as hydraulic pressure. Note that oil is injected and refilled into the hydraulic pressure chambers A and B by removing the plug 38 provided in the cylindrical portion 26 of the cylinder 20.

The piston section 40 is comprised of a radially outer section 42, a radially inner section 44, and a damper mechanism 50. The radially outer section 42 is attached to the cylindrical section 26 of the cylinder 20 by a spline fit 90. Therefore, the radially outer portion 42 is integral with the cylindrical portion 26 in the rotational direction, but is movable in the axial direction.
The radially inner portion 44 is connected to the coupling cylinder 1 of the driven shaft 12.
It is formed integrally with 6.

A main plate 46 is provided at the radially outer portion 42.
and a sub-plate 48 are attached. The main plate 46 is integrally attached by welding,
Subplate 48 is integrally attached by rivets 60. As shown in FIG. 1, the main plate 46 and the sub-plate 48 each have a semicircular arc cross section, and the two plates 46 and 48 are combined to form an annular space. Note that the lower ends of the main plate 46 and the sub-plate 48 are located on both sides of the radially inner portion 44 to reliably separate the hydraulic chambers A and B.

A coil spring 52 is fitted into the annular space formed by the main plate 46 and the sub-plate 48 . As shown in FIG. 2, this coil spring 52 is attached to a window 54 provided in the radially inner portion 44 via a spring seat 56. Stopper pieces 58 fixed to the main plate 46 and the sub-plate 48 by welding are disposed on both sides of the spring receiving seat 56 in the circumferential direction. These coil springs 52,
Window 54, spring seat 56, and stopper piece 5
8 constitutes a damper mechanism 50.

As a result, when a relative displacement occurs in the rotational direction between the radially outer portion 42 and the radially inner portion 44 of the piston portion 40, one spring receiving seat 56 is pushed by the stopper piece 58, and the coil spring 52 to absorb relative displacement, that is, vibration in the direction of rotation.

Although not shown, the spline fitting 90 between the cylindrical portion 26 of the cylinder 20 and the radially outer portion 42 of the piston portion 40 is provided with missing teeth on both sides of the piston portion 40. It is formed as a communication hole between hydraulic chambers A and B. This communication hole is a small hole and serves as an orifice. Note that the communication holes may not be formed actively, but may be formed using gaps between the respective components that constitute the piston portion 40.

Further, coil springs 70 and 72 as spring means are interposed in each of the hydraulic pressure chambers A and B within the cylinder 20, respectively.

As a result, a shock absorber-type vibration absorption mechanism is configured in the cylinder 20, and when the piston part 40 moves from side to side when looking inside the cylinder 20 in FIG.
It flows through a communication hole provided at 0. Since the communication hole is formed in the orifice of a small hole, a flow resistance is generated when oil flows, and this flow resistance absorbs vibrations in the axial direction.

In addition, in FIG. 1, a dust cover 80 is disposed to cover the left side portion of the cylinder 20. The dust cover 80 is attached to the driven shaft 12. This dust cover 80 prevents dust from entering the sliding portion between the left flange portion 24 of the cylinder 20 and the coupling cylinder 16 of the driven shaft 12.

Further, an oil hole 82 is bored in the coupling shaft body 14 of the drive shaft 10, and an oil hole 82 is formed in the coupling shaft body 14 of the driven shaft 12.
A hole 84 formed in the hydraulic pressure chamber A is communicated with the hydraulic pressure chamber A. Note that the reference numeral 86 is a plug, and the hole 8
4 are closed.

With the above configuration, from the drive shaft 10 to the driven shaft 12
Power is transmitted from the cylinder 20 to the piston portion 40 . In this transmission, the relative displacement in the rotational direction between the drive shaft 10 and the driven shaft 12 is allowed by the damper mechanism 50 provided in the piston section 40, and the relative displacement in the axial direction is allowed between the cylindrical section 26 of the cylinder 20 and the piston section 40. A spline fit with the radially outer portion 42 is permitted.

Vibration in the rotational direction of the drive shaft 10 and driven shaft 12 is absorbed by a damper mechanism 50 that allows relative displacement in the rotational direction, and vibration in the axial direction is absorbed by the cylinder 2 as the piston portion 40 moves left and right.
The vibration is absorbed by a shock absorber type vibration absorption mechanism formed inside the 0.

In this way, according to the illustrated joint, vibrations in both the rotational direction and the axial direction can be absorbed with a so-called one joint structure. In addition, since the piston portion 40 of the axial vibration absorption mechanism is provided with a damper mechanism that absorbs vibrations in the rotational direction,
The joint structure can be made compact. It can be made much more compact than the conventional case where they are arranged separately.

Further, the drive shaft 10 and the driven shaft 12 are connected to a joint shaft body 1
4 and the coupling cylinder 16 are fitted and attached so as to be slidable in the axial direction, so that the drive shaft 10
There is no joint angle between the drive shaft 12 and the driven shaft 12, and no misalignment or eccentricity occurs. As a result, the joint will not become unbalanced.

Although the present invention has been described above with reference to specific embodiments illustrated, the present invention is not limited to these embodiments, and various other embodiments are possible within the scope of the present invention.

For example, although the cylinder 20 is attached to the drive shaft 10 in the above embodiment, it may be attached to the driven shaft 12.

[Brief explanation of the drawing]

1 and 2 show an embodiment of the power transmission joint according to the present invention, with FIG. 1 being a front view in half-cut section, and FIG. 2 being a side view with the upper half cut away. Explanation of symbols, 10... Drive shaft, 12... Driven shaft, 20... Cylinder, 40... Piston part,
42...Radially outer part, 44...Radially inner part, 50...Damper mechanism, 70, 72...Coil spring (spring means), 90...Spline fitting, A, B...Hydraulic pressure Chamber, Y-Y...rotation axis.

Claims (1)

[Scope of utility model registration request] A drive shaft and a driven shaft, which are arranged on the same axis, are fitted and connected so that they can slide in the axial direction on the rotation axis, and at this joint position, the cylinder that forms the hydraulic chamber is connected to the drive shaft. It is attached to one side of the driven shaft, and the cylinder is provided with a piston part that divides the hydraulic pressure chamber into two in the axial direction, and the piston part is formed of a radially inner part and a radially outer part. , a damper mechanism in the rotational direction is provided between the two parts, the radially outer part is attached to the cylinder in the rotational direction but movable in the axial direction, and the radially inner part is attached to the cylinder so as to be movable in the axial direction. It is integrally attached to the other of the shaft and the driven shaft, and furthermore, a communication hole serving as an orifice is provided in the piston part to communicate between the two divided hydraulic pressure chambers, and the fluid on both sides of the piston part is connected. A power transmission joint characterized in that a pressure chamber is provided with a spring means.