JPH0489545A - Meshing tester for differential apparatus - Google Patents

Abstract

PURPOSE:To enable take out of a tested differential apparatus during a test, setting of next differential apparatus and injection of oil or draining thereof from the differential apparatus at a testing place by arranging an index tape having a plurality of setting sections allowing the setting of the differential apparatuses and an oil supply/drain means. CONSTITUTION:A differential apparatus A is set at a setting section not directly facing a testing place of an index table 5 so that another output member is connected to a braking means 6 at the setting section. When the table 5 is turned, the differential apparatus A at the setting section is moved to the testing place and then, with the operation of a supply/drain means 7, oil is injected into the differential apparatus A to perform a meshing test of a gear between an input member and a differential case. During the period, the differential apparatus A tested is taken out of the setting section not directly facing the testing place of the table 5 and next differential apparatus is set at the setting section. This eliminates a standby time and allows the injection of the oil to the differential apparatus A or the draining thereof from the differential apparatus thereby achieving a higher productivity.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention includes an input member, a differential case rotated by the input member via a gear, and a pair of output members supported by the differential case. The present invention relates to a meshing test device for a differential gear.

(Prior art) Conventionally, as this type of meshing test device, the
．． According to Publication No. 053, a driving means is connectable to an input member of a differential device arranged at a predetermined test location and rotates the input member, and a drive means is connectable to one output member of the differential device and rotates the input member. a load means for applying a load; and a braking means for applying a braking force, which is connectable to the other output member of the differential so that the rotation of the one output member is transmitted to the differential case; It is known that the gear engagement between the input member and the differential case is tested based on the rotational speed of the input member and the rotational speed of the differential case. This is transferred to the test location and set, and after the meshing test is completed, the differential gear is transferred to the subsequent oil drain location and the oil is drained.

(Problem to be Solved by the Invention) In the conventional system described above, the test cannot be performed until the tested differential gear is removed from the test site and the next differential gear is set, which requires waiting time. In addition, if oil is injected or drained from the differential gear at the front-stage injection site or the rear-stage oil extraction site, the work of moving the differential gear to the injection site or oil extraction site is troublesome, and the oil supply lubricant and drain are also troublesome. It is necessary to attach and detach the plug, which takes time and reduces productivity.

The present invention has been made in view of such problems, and
The purpose of this test is to create a test device that allows for the removal of the tested differential during the test and the installation of the next differential, as well as the ability to fill and drain oil from the differential at the test location. Our goal is to provide the following.

(Means for Solving the Problems) In order to achieve the above object, the present invention includes an input member, a differential case rotated by the input member via a gear, and a pair of output members supported by the differential case. A meshing test device for a differential gear, comprising: a driving means connectable to and rotating an input member of the differential gear disposed at a predetermined test location; and one output member of the differential gear. a load means that is connectable to the other output member of the differential and applies a load to the output member; and a braking force that is connectable to the other output member of the differential so that the rotation of the one output member is transmitted to the differential case. and a braking means for applying the same, and tests the engagement of gears between the input member and the differential case based on the rotational speed of the input member and the rotational speed of the differential case, and has a plurality of setting parts in which the differential device can be set. An index table is provided, and the differential device set in each set portion can be sequentially indexed to the test location by rotation of the index table, and the braking means is provided in each center and rear portion of the index table, respectively. Furthermore, an oil supply and drain means for injecting and draining oil from the differential gear was provided at the test location.

(Function) The differential device is set in a set part that does not directly face the test location of the index table so that the other output member is connected to the braking means of the set part, and the index table is rotated.

According to this, the differential device of the set part is moved to a test location, and then a drive means is connected to the input member of the differential device and a load means is connected to one output member, respectively, and the differential device is Inject oil into the device and perform a gear engagement test between the input member and the differential case.

During the test, the tested differential gear is taken out from the set part that does not directly face the test location on the index table, and the next differential gear is set in the set part.

After the test is completed, the oil supply and drain means is operated to drain the oil from the differential gear, the drive means is disconnected from the input member, the load means is disconnected from one of the output members, and the index table is rotated.

In this case, if each set portion of the index table is provided with a drive means and a load means, the index table becomes large because the drive means and load means are larger than the brake means.

However, this problem can be solved by arranging braking means at each set portion of the index table.

Furthermore, since the oil supply/drainage means is located at the test site, oil can be injected into and drained from the differential gear at the test site, and there is no need to attach or remove the oil supply lobe plug or drain plug.

(Example) In the drawing, (1) is the differential gear A placed at the test location (2).
A driving means connectable to the input member B of the differential device A and rotating the input member B, and (3) a load means connectable to one output member C7 of the differential device A and applying a load to the output member C1. , the setting part (4) that can set the differential gear fifA is 1
An index table (5) is provided, and the differential device A set in each set portion (4) can be sequentially indexed to the test location (2) by rotation of the index table (5). Each set portion (4) of the index table (5) is connected to the other output member C2 of the differential device A so that the rotation of the one output member itself is transmitted to the output member C2 to the differential case D. A braking means (6) is provided for applying a braking force to each of the test locations (2).
An oil supply/drainage means (7) for injecting and extracting oil from the differential gear A is provided.

More specifically, as shown in FIG. a shaft (Ie), an encoder (1d) for detecting the rotational speed of the drive shaft (lc) is provided, and an output shaft (1f) of a belt type transmission (1e) interlocked with the motor (1a). ) to the end of the drive shaft (lc) so as to be slidably splined in the axial direction, and the slider (1g) to be slidably slidable on the longitudinal rail (9) in the longitudinal direction on the machine base (8). The drive shaft (Ic) is supported by the slider (1g), and a piston rod of a hydraulic cylinder (not shown) provided on the machine base (8) is connected to the slider (1g);
In this way, the movement of the cylinder toward the extension side causes the drive shaft (1c
) was advanced through the slider (1g) so that it could be connected to the input member B as shown in FIG.

The load means (3) includes an electric power absorption needle (3a);
A rotation shaft (3
c), an encoder (3d) and a torque meter (3e) for detecting the rotational speed of the rotating shaft (3c) are provided, and a belt-type speed change is linked to the power absorption needle (3a). The input shaft (3g) of the machine (3r) is spline-engaged with the rotating shaft (3c) so as to be slidable in the axial direction, and the slider is attached to the horizontally long rail (10) on the machine base (8). (3h) is slidably supported, the rotating wheel (3c) is pivotally supported on the slider (3h), and the piston rod of the hydraulic cylinder (31) installed horizontally on the machine base (8) is attached to the slider (3h). Slider(
3h), and by operating the cylinder (31) in the extension side, the rotation shaft (3c) is moved laterally forward via the slider (3h), which causes the differential to move as shown in FIG. It was designed so that it could be connected to one output member C1 of the device A.

In the drawing, (3k) shows a rail member that can be closely fitted to the shaft hole of the outer case of the differential gear A and is provided on the rotating shaft (3c).

The index table (5) is as shown in FIG.
A rack (11) is provided which is rotatably supported by the machine base (8) on the lower support shaft (5a) and connected to a piston rod of a cylinder (not shown), and a pinion gear (5b) that meshes with the rack (11) is provided. It is fixed to the support shaft (5a), and the index table (5) is fixed to the cylinder by the operation of the cylinder.
rotation in the forward and reverse directions.

The set portion (4) of the index table (5) includes a seat plate (12) on which the differential device A is placed and a plurality of clampers (
13), and each clamper (]3) is provided with a clamp cylinder (13) as shown in FIGS. 4 and 6.
The clamp arm (1) is pivotally supported on the piston rod of 3a).
3b) in the middle part of the clamp cylinder (13a)
is connected to the bracket part (13c) of the set part (4) via a link (13e), and the clamp arm ( 13b).

As clearly shown in FIG. 5, the braking means (6) includes a lock shaft (6b) having a spline portion (6a) at its tip that can be engaged with a spline hole of the other output member C2 to the differential; It has a chuck member (6c) that is engaged with the outer periphery of the lock shaft (6b), and the index table (5).
A hydraulic cylinder (6e) is coaxially supported via a bearing (6r) in a frame (6d) fixed to the cylinder, and the chuck member (6C) is attached to the tip of the cylinder (6e). Piston (6g) in cylinder (6e)
Attach the lock shaft (6b) to the tip of the piston (
6g) was engaged with the cylinder (6e) via a parallel pin (6h) so as to be non-rotatable and slidable in the axial direction.

And a pressure chamber (61) ahead of the cylinder (6e)
and a local pressure chamber (6j) are communicated with a hydraulic power source (not shown) via each oil passage (6k) and a rotary joint (61), and thus the pressure chamber (61) at the front of the cylinder (6e)
By introducing pressure oil into the chuck member (6C), the lock shaft (6b) is moved to the engagement side (left side in Fig. 5), and the chuck member (6C) is expanded and inserted into the shaft hole J of the differential case D.
the other output member C2 of the differential device A.
can be braked so that it cannot rotate relative to the differential case D.

In this case, if the force that moves the lock shaft (6b) toward the engagement side and the force that moves the lock shaft (6b) toward the release side (right side in Fig. 5) are made the same magnitude, the lock shaft (8b) will be separated from the chuck member (6c). Due to the wedge effect, it may not move toward the release side. For this reason, in the embodiment, the piston (6g) was configured to have a stepped shape with a smaller diameter on the front side.

In the drawing, (6m) indicates an air vent hole, and (6n) indicates a sealing member that can be tightly fitted to the shaft hole of the outer case of the differential.

The oil supply/drainage means (7) is connected to the drain port E of the differential gear A at the test location (2), as shown in FIGS. 3, 4, and 7.
a first joint member (7a+) connectable to the differential gear (A), and a second joint member (7a+) connectable to the oil filler port F of the differential gear (A).
7b, ), and the first joint member (7a+) has a spring (7a3) attached to a first slider (7az) that is slidably supported on a rail (14) erected on the machine base (8). An air cylinder (7a) is installed upright on the bracket (14a) on the machine base (8) to which the rail (14) is attached, and the piston wood of this is attached to the slider. (7a2) and the cylinder (78i)
By operating in the extension side, the first joint member (7a, ) was raised as shown in Figure 4, so that it could come into close contact with the drain port E of the differential gear A at the test location (2).

Further, the second joint member (7b+) is a second slider that is slidably supported on a longitudinally longitudinal rail (15) provided on the machine base (8) in the same way as the first joint member (7a+). (7b2) is biased forward by a spring <Ibs), and an air cylinder (7b4) is provided on the plate (15a) to which the rail (work 5) is attached, and the pearstone rod of this is attached to the slider. (71)z)
Thus, by operating the cylinder in the extension side, the second joint member (7b,) is moved forward with respect to the plate (15a), and this is used to lubricate the differential gear A at the test location (2). It was made so that it could fit closely to the mouth F.

Further, the plate (15a) is slidably supported on a rail (16) erected on the machine stand (8), and the plate (15a) is slidably supported on the machine stand (8).
The piston rod of an air cylinder (17) installed upright is connected to the plate (15a), and the cylinder (17)
) causes the second joint member (7b, ) to move through the plate (15a) to an upper operating position where the member (7b+) can come into close contact with the fuel filler port F and a lower retracted position. This prevents the second joint member (7b+) from interfering with the rotation of the index table (5).

In addition, the first joint member ('yak) has a first oil passage (7) on the discharge side of the first pump (7c) as shown in FIG.
d) is connected to the first hose (7e), and the second hose (7e) is connected to the
The joint member (71) +) has a second hose (7h) connected to the second oil passage (7g) on the suction side of the second pump (7r).
is connected to the first oil passage (7d), and a normally closed first oil passage (7d) is connected to the first oil passage (7d).
A solenoid valve (71) and a second solenoid valve (7j) are interposed in the second oil passage (7g), and a downstream portion of the first solenoid valve (71) in the first oil passage (7d). A third solenoid valve (7j) is interposed in the third oil passage (7k) that communicates with the downstream part of the second solenoid valve (7j) of the second oil passage (7g), and 7d
) is branched from the upstream portion of the first solenoid valve (71) and communicates with the oil tank (7I).
A fourth solenoid valve (7p) is interposed in the differential gear A, and when injecting oil into the differential A, the first and second solenoid valves (71) (7N) are opened and the first pump (7N) is opened.
7C) through the first oil path (7d) and the first hose (
7e) and the first joint member (7a+) from the drain port E, and the oil overflowing from the oil filler port F is injected into the second joint member (7b,) and the second hose (7a+).
h), the second pump (7f) sucks in the liquid through the second oil passage (7g).

Also, when draining the oil from differential gear A, the first valve (
71) is closed, the third and fourth valve <11> (7p) is opened, the second joint member (7b,) is retreated, and the oil in the differential gear A is drained from the drain port E to the first joint member. (7a+), the second pump (7f) sucks in the fluid through the first hose (7e) and the third oil passage (7k).

In this case, the oil discharged from the first pump (7c) is returned to the oil tank (a) via the return path (7n).

In addition, a heater (7r) was installed in the oil tank (7m) to heat the oil in the oil tank (7■) to a predetermined temperature to avoid errors caused by changes in the outside temperature at the test location. .

Next, the operation of the embodiment will be explained.

First, attach the differential device A to the seat plate (12) of the set part (4) that does not directly face the test location of the index table (5), and insert the lock shaft (6) of the braking means (6) into the shaft hole of the other output member C2. 6b) is engaged, and place it on the clamper (
13), and then the index table (5
) to rotate.

According to this, the differential device A of the set part (4) is moved to the test location (2), and then the drive shaft (1) of the drive means (1) is moved.
c) and the rotating shaft (3c) of the load means (3) using a differential device A.
The drive shaft (1c) is connected to the input member B of the differential device A, and the rotation shaft (3c) is connected to the output member C1 of the differential device A.
) of the braking means (6).
Pressure oil is introduced into the pressure chamber (6j) on the other side of e) to expand the chuck member (6c) and brake the other output member C2 so that it cannot rotate relative to the differential case D. )
The first and second joint members (ya+) (7b+)
are moved forward toward the differential device A, and the first joint member (7a+) is connected to the drain port E and the second joint member (7a+).
b,) are brought into close contact with the oil filler port F, and then the first and second pumps (7c) (7f) are operated to inject and circulate oil into the differential gear A while driving the drive means (1) and the motor (1a). By operating the power absorption needle of the load means (3), the differential case D is rotated via the pinion gear G integrally molded on the input member B and the ring gear H on the outer periphery of the differential case D.
Braking means (
6), the rotation of one output member C1 is transmitted to the differential case D, and therefore a load is applied to the gears between the input member B and the differential case D, that is, the pinion gear G and the ring gear H. The load of means (3) is applied.

Furthermore, since the other output member C2 is locked against relative rotation with respect to the differential case D, one input member C7 and the differential case D rotate together, and therefore the rotational speed of the input member B is controlled by the drive shaft ( The rotational speed of the differential case D is detected by the encoder (1d) provided in the rotary wheel (3) of the load means (3) that engages one output member C4.
c) is detected by the encoder (3d) provided in step 3, and compared, the meshing of both gears G and H is tested based on the degree of change in the angular velocity of ring gear H with respect to pinion gear G.

Meanwhile, while the test is being carried out, the tested differential gear A is taken out from the set part (4), which is not directly facing the test location (2) of the index table (5), and the next differential gear A is inserted into it. set.

After the test, the oil supply and drainage means (7) is operated to drain the oil, and the drive shaft (1c) of the drive means (1) and the load means (3) are connected to each other.
) and the first joint member (7a+) of the oil supply/drainage means (7) are respectively retracted, the braking by the braking means (6) is released, and the index table (
5) to complete one step.

(Effects of the Invention) As described above, according to the present invention, the differential gear can be tested at the test site while the differential gear is being removed and set. Productivity can be improved by eliminating the need for waiting time while performing work, and since oil supply and drainage means are located at the test location,
In addition to being able to inject and drain oil from the differential gear, there is no need to attach or remove oil supply lubricants or drain plugs.Furthermore, the braking means is placed in the set part of the index table, making the index table relatively compact. has.

[Brief explanation of the drawing]

FIG. 1 is a front view showing one example of the device of the present invention, FIG. 2 is a plan view thereof, FIG. 3 is a plan view of an index table, and FIG.
The figure is a view taken along the line IV-IV, and Figure 5 is v-v of Figure 2.
6 is a front view cut along the line Vl-Vl in Fig. 4, Fig. 7 is a diagram showing the oil passage configuration of the oil supply and discharge means, and Fig. 8 is a cut plane of the differential gear in the test state. It is a diagram. (1)...Drive means (2)...Test location (3)
...Loading means (4)...Set part (5)...
Index table (6)...Brake means A...Differential devices C1, C2...Output member (7)...Oil supply/drainage means B...Input member D...Third person outside differential case Figure 6 Figure 7

Claims (1)

[Claims] A meshing test device for a differential gear comprising an input member, a differential case rotated by the input member via a gear, and a pair of output members supported by the differential case, the differential gear meshing test device being arranged at a predetermined test location. a driving means connectable to an input member of the differential to rotate the input member; a load means connectable to one output member of the differential to apply a load to the output member; and a braking means that is connectable to the other output member of the output member and applies a braking force to the output member so that the rotation of the one output member is transmitted to the differential case, the rotational speed of the input member and the rotational speed of the differential case are In a device for testing the engagement of gears between an input member and a differential case, an index table having a plurality of setting sections in which differential devices can be set is provided, and the differential device set in each setting section is set in the index table. The test location can be sequentially indexed by rotation of the table, the braking means is provided at each set portion of the index table, and the test location is provided with a supply/drain system for injecting and draining oil from the differential gear. A meshing test device for a differential gear, characterized in that it is provided with an oil means.