JPH031802Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a measuring device for measuring the backlash of a differential mechanism of an automobile.

[Conventional technology]

Conventionally, in the differential mechanism of an automobile, the backlash between the drive pinion 1 and the ring gear 2 has been measured by fixing the drive pinion 1, applying rotational force to the ring gear 2, and measuring the amount of rotation of the ring gear. . Prior art of such backlash measuring devices includes:
For example, there is a technique disclosed in Japanese Unexamined Patent Publication No. 166508/1983. This prior art is summarized in FIG. The rotational force given to the ring gear 2 is transmitted by the rotation arm 3.
It is carried out by. The tip of this rotating arm 3 meshes with the teeth of the ring gear 2, and the rotating arm 3 is rotated around the fulcrum shaft 4, whereby the tip of the rotating arm 3 is moved in the circumferential direction of the ring gear 2, and the ring gear 2 is rotated. rotational force is applied to. The rotation is performed by movement of the rotation shaft 5. That is, in a state where the rotation shaft 5 is engaged with the rear end of the rotation arm 3 at a substantially right angle,
It is moved in the axial direction of the rotating shaft. This movement is performed by sliding the cam plate 6.

That is, the convex portion 7 formed on a part of the rotating shaft 5 is held in the inclined groove 8 formed in the cam plate 6, and the cam plate 6 is slid at a right angle to the axial direction of the rotating shaft 5. made by. The slide of the cam plate 6 is the piston 9
It is carried out by.

The rotating head 11 to which the rotating arm 3, rotating shaft 5, etc. are attached is slid along the slide base 12 by another piston 13. This slide is used to adjust the position of the rotating head 11 in accordance with the size of the ring gear 2 to be measured.

Furthermore, the mechanism that measures the amount of rotation of the ring gear 2 to which rotational force is applied and measures the backlash is as follows.
It is provided in the measuring head 14. That is, a measuring arm 15 that is moved by the rotation of the ring gear 2 and a differential transformer type length measuring device 16 that measures the movement of this measuring arm 15 are provided.

[Problem that the invention attempts to solve]

In the above prior art, the coil spring 17 engages with the rotation arm 3 and the rear end of the rotation arm 3 so that the rotation arm 3 gently transmits the force that causes the ring gear 2 to rotate. It is provided between the rotary shaft 5 and the rotary shaft 5. However, the effect of the coil spring 17 in this position is not sufficient, and when the ring gear 2 is rotated, a sudden rotational movement occurs. That is, when rotating the ring gear 2, the distance between the fulcrum shaft 4 of the rotating arm 3 and the ring gear 2 remains unchanged, so the contact force between the rotating arm 3 and the ring gear 2 is It is maximum when facing the center of ring gear 2. The energy stored due to the strong contact force is suddenly released at the next moment and becomes a force that rapidly rotates the ring gear 2. This sudden rotational force could not be absorbed by the coil spring 17 of the prior art.

Now, conventionally, a differential transformer type length measuring device has been used, but it is better to use a linear scale type length measuring device, which is less affected by the adverse effects of temperature, for measuring devices such as the one proposed in this invention. can. Alternatively, it is advantageous because the mastering work required for measuring a linear area where the voltage changes, such as with a differential transformer type length measuring instrument, is not necessary. However, when this linear scale type length measuring device is employed, due to its characteristics, if the displacement to be measured occurs too rapidly, a measurement error will occur.

The present invention has been developed in view of the above problems, and is an improvement on the technology disclosed in Japanese Patent Application Laid-Open No. 166508/1983, which prevents sudden rotational movement when rotating a ring gear, and which is capable of linear scale type measurement. It is an object of the present invention to provide a backlash measuring device for an automobile differential mechanism that can employ long instruments.

[Means for solving problems]

In the present invention, a spring is provided between a piston that slides the cam plate and the cam plate, and the force of the piston is transmitted to the cam plate via the spring. The rapid rotational movement that occurs in the ring gear manifests itself as an enlarged and large movement of the cam plate due to the action of the inclined groove of the cam plate. Therefore, if the movement of the cam plate is restricted by a spring, rapid rotational movement of the ring gear can be more effectively prevented.

〔Example〕

An embodiment of the present invention will be explained with reference to FIG.
Parts labeled with the same numbers as in FIG. 2 representing the prior art have substantially the same functions as the prior art. That is, the backlash measuring device of this embodiment also includes a rotating head 11, a cam plate 6, and a measuring head 14, as in the prior art.

Of these, the rotating head 11 is capable of sliding on a slide base 12 toward the ring gear 2. This sliding is carried out by a rotating head sliding cylinder 21. A sliding cylinder 22 is fixed to the tip of the rotating head sliding piston 13 driven by the cylinder 21. As shown in FIG. A sliding shaft 23 fixed to the rotating head 11 is slidably housed inside the sliding tube 22. The coil spring 24 connects the rotary head slide piston 13 and the rotary head 11.
is installed between. This installation is
A spring receiver 25 fixed around the sliding tube 22
The coil spring 24 is wound around the sliding tube 22 between the other spring receiver 25 fixed to the rotating head 11 and the other spring receiver 25 fixed to the rotating head 11. It is being done. A rotating arm 3 is provided on the tip side of the rotating head 11 so as to be rotatable about a fulcrum shaft 4. The tip of the rotating arm 3 is a rotating terminal 26 that meshes with the teeth of the ring gear 2.
The rear end of the rotating arm 3 has a spherical shape and engages with the rotating shaft 5. This engagement is performed in a state where the rotating arm 3 and the rotating shaft 5 are approximately at right angles, and the rotating shaft 5 is guided by the shaft guide 27 and is movable in the axial direction of the rotating shaft 5. ing.

The cam plate 6 is slidable along the slide base 12 at right angles to the axial direction of the rotating shaft 5. This sliding is performed by the cam slide cylinder 28. The force of the cam slide piston 9 driven by the cylinder 28 is transmitted to the cam plate 6 via a coil spring 29. That is, a sliding tube 22 is fixed to the tip of the cam slide piston 9. A sliding shaft 23 fixed to the cam plate 6 is slidably housed inside the sliding tube 22. A coil spring 29 is attached between the sliding tube 22 and the sliding shaft 23. For installation, the coil spring 29 is attached to the sliding tube 24 between the spring receiver 25 fixed to the sliding tube 22 and the spring receiver 25 fixed to the sliding shaft 23.
This is done by wrapping it around the tip of the In addition, in the present invention, the cam plate 6,
A coil spring 25 is also provided between the device and the base 30, which is the basis of the device, so as to absorb sudden rotational movement of the ring gear. That is, the sliding shaft 23 fixed to the cam plate 6 is slidably housed in a sliding cylinder 22 fixed to the base 30, and a coil spring is inserted between the sliding cylinder 22 and the sliding shaft 23. 31 is attached. This attachment is performed in the same way as above, between the spring receiver 25 fixed to the sliding barrel 22 and the spring receiver 25 fixed to the sliding shaft 23.
This is done by winding the coil spring 31 around the . The cam plate 6 has an inclined groove 8
is provided, and a convex portion 7 formed on a part of the rotating shaft 5 is held. The rotating shaft 5 is moved in the axial direction by the inclined surface of the inclined groove 7.

The measuring head 14 is slidable along the slide base 12 towards the ring gear 2. A measuring arm 15 is provided in the front half of the measuring head 14. The measuring arm 15 has a generally L-shape as a whole, and is rotatably provided at a corner of the L-shape by a fulcrum shaft 32. The tip of the measuring arm 15 serves as a measuring terminal 33 and meshes with the teeth of the ring gear 2. The rear end of the measuring arm 15 is in contact with a length measuring terminal 35 extending from a linear scale type length measuring device 34 . Measurement is performed by pushing up this length measuring terminal 35 with the rear end 36 of the measuring arm 15. Adjustment stopper 37 for regulating the movement of this rear end 36 to a constant level
is provided. Further, the front half 14' of the measuring head 14 is attached with an adjustment screw 3 to the main body of the measuring head 14.
8 adjusts the amount of forward protrusion. Note that the measuring head 14 is pin-coupled to the rotating head 11 by an interlocking arm 39. Therefore, the rotating head 11
As the measuring head 14 moves forward and backward, the measuring head 14 also moves forward and backward.

Note that the rotating head sliding cylinder 21
The cam slide cylinder 28 is fixed to the base 30 by a cylinder fixing plate 40. Further, the slide bases 12, 12, 12 are also fixed to this base 30.

The operation of this embodiment will be explained below.

After the differential mechanism is set and the drive pinion is fixed, the rotary head slide cylinder 21 operates to move the rotary head 11 forward toward the ring gear 2. At the same time, the measuring head 14 also moves forward. As a result, the rotation terminal 26, which is the tip of the rotation arm 3, and the measurement arm 15
Both the measuring terminal 33 at the tip of the ring gear 2
mesh with the teeth of Next, cam slide cylinder 2
8 works to move the cam plate 6 forward. As a result, the rotating shaft 5 pushed by the inclined groove 8 of the cam plate 6 moves in the axial direction, moves the rear end of the rotating arm 3, and rotates the rotating arm 3 around the fulcrum shaft 4. As a result, the rotation terminal 26 rotates the ring gear 2 clockwise in the figure. At this time, even if conventionally rapid rotational movement would occur,
By the action of the coil springs 29 and 31 that elastically support the cam plate 6 with respect to the cam slide piston 9 and the base 30, sudden rotational movement can be prevented. This sudden rotational movement can be prevented by using the rotating head 11 and the rotating head sliding piston 1.
It is further completed by a coil spring 24 installed between the 3 and 3.

Now, the rotated ring gear 2 causes the L-shaped measuring arm 15 to rotate counterclockwise in the figure around the fulcrum shaft 32. As a result, the rear end 3 of the measuring arm 15
6 pushes up the length measuring terminal 35 extending from the linear scale type length measuring device 34. The displacement of the length measuring terminal 35 caused by this pushing up is caused by the fact that the rotational movement of the ring gear 2 is not sudden.
It is done slowly. Therefore, measurement errors caused by a linear scale type length measuring device do not occur.

[Effect of idea]

According to the bump crush measuring device for an automobile differential mechanism of the present invention, the cam plate, which undergoes an expanded rotational movement when a rapid rotational movement of the ring gear occurs, is elastically supported by a spring. Rapid rotational movement can be prevented.

[Brief explanation of the drawing]

FIG. 1 is a plan view showing a backlash measuring device for an automobile differential mechanism according to an embodiment of the present invention, and FIG. 2 is a plan view of a conventional device. 1...Drive pinion, 2...Ring gear,
3... Rotating arm, 4... Fulcrum shaft, 5... Rotating shaft, 6... Cam plate, 7... Convex portion, 8
... Inclined groove, 9 ... Piston, 11 ... Rotating head, 12 ... Slide base, 13 ... Piston, 14 ... Measuring head, 15 ... Measuring arm, 16 ... Differential transformer type length measurement 17... Coil spring, 21... Rotating head slide cylinder, 22... Sliding tube, 23... Sliding shaft, 2
4...Coil spring, 25...Spring receiver, 26...
Rotation terminal, 27... Shaft guide, 28...
Cam slide cylinder, 29... coil spring,
30...Base, 31...Coil spring, 32...
Fulcrum shaft, 33...Measurement terminal, 34...Linear scale type length measuring device, 35...Length measurement terminal, 37...Adjustment stopper, 38...Adjustment screw, 39...Interlocking arm, 40... Cylinder fixing plate.

Claims (1)

[Claims for Utility Model Registration] A measuring device for fixing the drive pinion of an automobile differential mechanism and applying rotational force to the ring gear to measure the amount of rotation of the ring gear to measure bumpiness, the rotational force being The tip of the arm meshes with the teeth of the ring gear and the rotating arm is rotated around the fulcrum axis, and this rotation is provided by a rotating shaft that engages the rear end of the rotating arm at a substantially right angle. is moved in the axial direction of the rotating shaft, and this movement is achieved by a protrusion formed on a part of the rotating shaft being held in an inclined groove formed on the cam plate, and the cam plate being moved in the axial direction of the rotating shaft. A spring is provided between the piston and the cam plate, so that the force of the piston is transmitted to the cam plate via the spring. 1. A buck crush measuring device for an automobile differential mechanism, characterized in that: