JPH0322590Y2 - - Google Patents

Description

[Detailed description of the invention] (Industrial application field) The present invention is a differential rotation tester suitable for a differential rotation tester used for simulation testing of mechanical parts that generate torsional vibration during rotation, such as clutch disks for automobiles. This invention relates to an improvement of a rotational oscillation output mechanism.

(Prior Art and its Problems) Conventionally, hydraulic or electric rotary actuators or mechanical testers using a planetary gear mechanism have been used as differential rotation testers.
Mechanical types are economical as they have lower manufacturing costs, operating costs, and maintenance and inspection costs than hydraulic and electric types.

The applicant of the present application has also previously filed an improved version of the above-mentioned mechanical rotary differential tester as in Japanese Patent Application No. 133934/1983. However, conventional testers only apply one system of torsional vibration to one output shaft, and there are still problems with simulation performance. In other words, it is quite difficult to generate complex torsional vibrations similar to those of an actual vehicle.

For example, when an actual vehicle accelerates, the average value of the rocking torque becomes a positive value, and when it decelerates, the average value of the rocking torque becomes a negative value, but with conventional testers, the average value of the rocking torque cannot be adjusted. Nakatsuta.

(Purpose of the invention) The present invention adjusts the average value of the oscillating torque by independently generating static torque and oscillating torque using different mechanisms, and applies dynamic torsional torque to the rotating test object. The object of the present invention is to provide a differential rotational oscillation output mechanism that can generate the following with a simple and low-cost mechanism.

(Structure of the device) (1) Technical means The present invention coaxially includes a first output shaft to which one end of the object under test is attached and a second output shaft to which the other end of the object to be tested is attached. The first output shaft is connected to the rotary drive unit via a first planetary gear mechanism, and the second output shaft is connected to the rotation drive unit via a second planetary gear mechanism to connect the first and second output shafts. are rotatable at the same speed, and a rotation mechanism is connected to the first planetary carrier of the first planetary gear mechanism to rotate the first planetary carrier by an arbitrary angle about the first output shaft; The differential rotational swing output mechanism is characterized in that a swinging mechanism for swinging the second planetary carrier around the second output shaft is connected to the second planetary carrier of the second planetary gear mechanism. .

(2) Effect The above technical means uses a rotating mechanism to apply static torque of a predetermined value, which is generated by rotating the first planetary carrier of the first planetary gear mechanism by an arbitrary angle, to the second planetary gear using a swinging mechanism. By adding weight to the swinging torque generated by swinging the second planetary carrier of the mechanism, dynamic torsional torque is applied to the test object attached between both output shafts.

(Example) Fig. 1 shows an example of a tester for generating torsional vibration of a clutch disk for an automobile. , is fixed to the inner periphery of the input boss 3 with a bolt 4. The boss 3 is integrally provided with cylindrical portions 3a on both sides, and the cylindrical portions 3a are rotatably supported on the inner peripheral side of the frame 6 via bearings 5. An input pulley 7 is fixed to the end of the boss cylinder 3a opposite to the arrow F side, and the pulley 7 is interlocked and connected to the drive motor 10 via the belt 8 and inertia body 9 shown in FIG. ing.

First and second planetary gear mechanisms 11 and 12 are arranged on the inner peripheral sides of link gears 1 and 2, respectively.
The first planetary gear mechanism 11 includes a first planetary gear 13, a first
It is equipped with a planetary carrier 14 and a first sun gear 15, and the first planetary gear 13 meshes with the first link gear 1 and the first sun gear 15, and is rotatably supported by the carrier 14 via a pin 17 in FIG. has been done. For example, two or more first planetary gears 13 are provided on the same circumference. The first sun gear 15 is integrally formed with the first output shaft 21 , and the first output shaft 21 is connected to the first planetary carrier 14 via a bearing 19 .
It is rotatably fitted to the inner circumferential surface of. The first planetary carrier 14 fits into the inner peripheral surface of the cylindrical portion 3a via the bearing metal 16, and the worm wheel 60
The worm wheel 60 is operatively connected to the rotation mechanism 18.

The second planetary gear mechanism 12 includes a second planetary gear 23, a second planetary carrier 24, and a second sun gear 25. The second planetary gear 23 meshes with the second link gear 2 and the second sun gear 25, and also has a pin. It is rotatably supported by the second planetary carrier 24 via 27. Two or more second planetary gears 23 are provided on the same circumference. The second planetary carrier 24 is formed integrally with the main swing input shaft 28. The swing input shaft 28 is fitted into the inner circumferential surface of the cylindrical portion 3a via a bearing 29 so as to be rotatable (reciprocating). A swing mechanism 30 is connected to an end of the swing input shaft 28 . The second sun gear 25 is formed integrally with the second output shaft 22, and the second output shaft 22 is rotatably fitted to the inner peripheral surface of the first output shaft 21 and the like via a bearing 31.

A thick disk-shaped test article holder 33 is fixed to the end of the first output shaft 21 on the arrow F side through a joint tube 32 . A torsion angle sensor 34 is provided on the joint tube 32.

A friction fastening type Shupan ring 35 is fixed to the end of the second output shaft 22 on the arrow F side.
A spline shaft 36 is held by a shuppan ring 35. Further, a detection ring 37 facing the angle sensor 34 is fixed to the auxiliary ring 35a.

An automobile clutch disk 39 having a damper 38 is attached to the holder 33 and the spline shaft 36 as a test product. That is, disk 3
The hub 40 of No. 9 is spline connected to the spline shaft 36, the facing 41 is held between a pair of mounting plates 42, and the plates 42 are fixed to the holder 33 with bolts 43.

FIG. 2 shows a schematic diagram of the structure of FIG. 1, making the input paths of the link gears 1, 2 clear. That is, as described above, the link gears 1 and 2 are connected to the inertial body 9 via the pulley 7 and the belt 8, and the inertial body 9 is operatively connected to the drive motor 10 via the belt transmission device 44.

FIG. 3 shows an example of the swing mechanism 30. That is, a long arm 45 is fixed to the swing input shaft 28, and the arm 45 is pivotally connected to an arm 48 of a crankshaft 47 via a connecting rod 46.
The crankshaft 47 is connected to the motor 5 via a transmission mechanism 49.
It is linked to 1. The swing angle is adjusted by changing the length of the arm 48, and the swing period is adjusted by changing the rotation speed of the motor 51.

FIG. 4 shows an example of the rotation mechanism 18. That is, the rotation mechanism 18 includes a worm wheel 60, a worm 61, a handle 62, and the like. The worm wheel 60 is fixed to the end of the first planetary carrier 14 and is rotatable together with the first planetary carrier 14 . A worm 61 is engaged with the outer periphery of the worm wheel 60, and the worm 61 has a structure that is rotationally driven by a handle 62 or a motor (not shown). Further, the bracket 63 is fixed to the housing 64.

The link gears 1 and 2 in FIG. 1 have the same diameter and the same number of teeth, and the first and second planetary gears 1 and 2 have the same diameter and the same number of teeth.
Sun gears 3 and 23 have the same diameter and the same number of teeth, and first and second sun gears 15 and 25 have the same diameter and the same number of teeth.

Next, the effect will be explained. First, rotating mechanism rotating mechanism 1
8. Both the swing mechanisms 30 are stopped, thereby locking the first and second planetary carriers 14, 24 in FIG. 1 in a fixed state. Next, the drive motor 10
The link gears 1 and 2 are rotated at the same rotation speed via the boss portion 3 and the like. The first link gear 1 is input to the first sun gear 15 via the first planetary gear 13, but since the first planetary carrier 14 is locked in a fixed state, the speed is increased and the first sun gear 1
5 is input. As the first sun gear 15 rotates, the facing 41 of the clutch disk 39 rotates at a constant speed via the first output shaft 21, the joint pipe 32, and the holder 33.

On the other hand, from the second link gear 2, the second planetary gear 23
is input to the second sun gear 25 via the second sun gear 25.
Since the planetary carrier 24 is locked in a fixed state, the speed is increased at the same speed ratio as that of the first planetary carrier 14, and the speed is input to the second sun gear 25. Second
The rotation of the sun gear 25 causes the hub 40 to rotate at the same speed as the facing 41 via the second output shaft 22 and the shuppan ring 35.

In a state where the hub 40 and facing 41 are rotating at the same speed as described above, by first driving the swinging mechanism 30, a relatively simple swinging torque as shown in FIG. 5 is output as a second output. It can be generated on the shaft 22. That is, by turning on the motor 51 in FIG. 3 and rotating the crankshaft 47, the swing input shaft 28 swings, and at the same time, the second planetary carrier 24 and second planetary gear 23 in FIG. Swings around the output shaft. When the swinging direction is the same as the rotational direction of the second sun gear 25, the rotational speed of the second sun gear 25 is accelerated, and on the other hand, when the swinging direction is opposite to the rotational direction of the second sun gear 25, the rotational speed of the second sun gear 25 is The rotational speed of is reduced. Therefore, the second sun gear 25 is connected to the first sun gear 1.
Swing torque is generated during the same rotation as 5.
As a result, a swinging torque is generated in the hub 40 with respect to the rotating facing 41.

By further driving the rotation mechanism 18 in the rotational direction of the boss part 3 while the swing mechanism 30 is being driven, the first planetary carrier 14 is twisted at an angle relative to the boss part 3. As shown in FIG.
is weighted to generate characteristic 70.

On the other hand, by driving the rotating mechanism 18 in the opposite direction of rotation of the boss portion 3, the static torque Tm2 is added to the swinging torque generated by the swinging mechanism 30 to generate the characteristic 71. Therefore, in the hub 40 with respect to the facing 41, characteristics 70 and 71 are generated in which the static torque Tm1 or the set torque Tm2 is added to the rocking torque by the rocking mechanism 30.

In this way, in this embodiment, the static torque caused by the rotating mechanism 18 provided in the first planetary gear mechanism 11 and the swinging torque caused by the swinging mechanism 30 provided in the second planetary gear mechanism 12 are made independent. Characteristics 70 and 71 are obtained by generating the signals. Therefore, the rotating mechanism 18 and the swinging mechanism 30 can be constructed by a simple and low-cost mechanism consisting of an arm, a connecting rod, a worm, and the like.

By switching the drive direction of the rotation mechanism 18 or increasing or decreasing the drive amount, the set torques Tm1 and Tm2 can be adjusted.
Adjust as desired.

Incidentally, the characteristic 70 causes the clutch disk 39 to apply a power similar to the driving state during acceleration of the automobile, and the characteristic 71 causes the clutch disk 39 to apply a power similar to the engine braking state.

In the above test condition, the power from the drive motor 10 acts on the clutch disc 39 through both output shafts 21 and 22 and then flows back to the boss 3, so the power required during the test is the power consumed by the clutch disc 39. Only a small amount of loss is sufficient.

(Effects of the Invention) As explained above, the differential rotational oscillation output mechanism according to the present invention includes the first and second output shafts 21 and 22 coaxially, and the first output shaft 21 is connected to the first planetary gear mechanism. 11, the second output shaft 22 is connected to the rotational drive unit via the second planetary gear mechanism 12, so that both shafts can rotate at the same speed, and the planetary carrier 14 of the first planetary gear mechanism 11 is connected to the rotational drive section through the second planetary gear mechanism 12. Since the mechanism 18 is connected and the swing mechanism 30 is connected to the planetary carrier 24 of the second planetary gear mechanism 12, static torque and swing torque are generated independently by different mechanisms, and the average swing torque is The value can be adjusted. Therefore, dynamic torsional torque can be applied to the rotating test object using a simple and low-cost mechanism.

(Another Embodiment) The above rotation mechanism is not limited to one that rotates the worm wheel 60; for example, the first planetary carrier 14
Other structures may also be used, such as rotating an arm fixed to.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of a differential rotation tester to which the present invention is applied, Fig. 2 is a schematic diagram of Fig. 1, Fig. 3 is a structural diagram of the swinging structure, and Fig. 4 is a structural diagram of the rotating mechanism.
FIG. 5 is a graph of the swinging torque when only the swinging mechanism is driven, and FIG. 6 is a graph of the dynamic torsion torque when the swinging mechanism and the rotating mechanism are driven. 11, 12...first and second planetary gear mechanisms, 1
4, 24...first and second planetary carriers, 21, 2
2...First and second output shafts, 18...Rotation mechanism, 3
0... Rocking mechanism.

Claims (1)

[Claims for Utility Model Registration] A first output shaft to which one end of the test object is attached and a second output shaft to which the other end of the test object is attached are coaxial, and the first output shaft is connected to a first planet. The second output shaft is connected to the rotary drive unit via a gear mechanism, and the second
The first planetary gear mechanism is connected to the rotary drive unit via a planetary gear mechanism to enable the first and second output shafts to rotate at the same speed, and the first planetary carrier is connected to the first planetary gear mechanism. A rotation mechanism that rotates by an arbitrary angle about the first output shaft is coupled to the second planetary carrier of the second planetary gear mechanism, and the second planetary carrier is rotated about the second output shaft. An operating rotational oscillation output mechanism characterized in that a oscillation mechanism for moving is connected to the oscillation mechanism.