JP3085166B2 - Power train performance test equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power train performance test apparatus, and more particularly, to a technique for evaluating the durability of a differential device with high accuracy.

[0002]

2. Description of the Related Art Generally, a performance test apparatus including a dynamometer is used for a bench test of a power train for an automobile. For example, when testing the power train of a front-wheel drive vehicle, a transaxle in which a transmission and a differential device are integrated by an engine or a motor is driven, and a dynamometer or a dynamometer is mounted on a pair of differential output shafts of the differential device. A load device consisting of a flywheel is connected to apply a load. And
The transaxle is driven in a predetermined drive mode that combines starting acceleration and steady running to measure power loss due to the power train and torque fluctuations during shifting, and wear of transmission gears and differential gears after the test is completed. Check etc.

However, when a load device is connected to each of the two differential output shafts of the differential device as described above, the configuration of the device becomes complicated and its size and equipment cost become large. Some of the performance test devices are adopted. This device employs a configuration in which both differential output shafts of a differential device are directly connected via a connecting shaft, and a load device is connected to the connecting shaft to apply a load equally to both differential output shafts. I have. Also, a speed increasing mechanism is provided between the two differential output shafts and the connection shaft (or between the connection shaft and the load device),
By increasing the rotation speed of the load device, a sufficient load is applied by a load device having a relatively small capacity.

[0004]

However, this type of performance test apparatus having a single load device has the following disadvantages. The differential device has a pair of side gears and a pinion gear housed in a differential carrier.When a differential rotation occurs between the differential output shafts, the side gear and the pinion gear mesh with each other to absorb the differential rotation. Relative rotation in the state. However, in the above-described performance test apparatus, since the two differential output shafts directly connected via the connecting shaft rotate at the same rotation speed, the differential rotation which causes the relative rotation between the side gear and the pinion gear does not occur. Therefore, the side gear and the pinion gear always transmit the torque in the same meshing state, and the load continuously acts on only a few teeth involved in the meshing out of the many teeth formed in both gears. . As a result, a relatively short performance test causes wear and damage to some of the teeth, making it impossible to evaluate the durability of the side gear and the pinion gear, and making it difficult to continue the performance test.

In order to prevent such a problem, the differential output shaft and the coupling shaft are separated at regular time intervals, one of them is rotated, the meshing state between the side gear and the pinion gear is changed, and then the pair is connected again. Replacement work was also being performed. However, the man-hour and time required for the rearrangement work put a heavy burden on the test operator, and the performance test is naturally interrupted during the work, so that the operation rate of the performance test apparatus is reduced. In addition, even when the rearrangement work is performed, it is practically impossible to equally apply a load to all the teeth, and it is still difficult to evaluate the durability of the side gear and the pinion gear.

[0006] The present invention has been made in view of the above situation,
It is an object of the present invention to provide a power train performance test device capable of preventing abrasion and damage of a part of teeth of a side gear and a pinion gear and enabling the durability of a differential device to be evaluated with high accuracy.

[0007]

In order to achieve this object, a first aspect of the present invention is a power train performance testing apparatus for testing the performance of a power train including a differential device. First transmission means coupled to a first differential output shaft of the differential device for shifting the rotation of the first differential output shaft at a predetermined first transmission ratio; and a second differential output shaft of the differential device And a second transmission means for shifting the rotation of the second differential output shaft at a predetermined second transmission ratio, and a connection for connecting the output shaft of the first transmission means and the output shaft of the second transmission means. And a load application means connected to the connection means for applying a rotational load, wherein the first speed ratio and the second speed ratio are set to different values.

According to a second aspect of the present invention, there is provided a power train performance testing apparatus according to the first aspect, wherein a value obtained by dividing the first speed ratio by the second speed ratio is close to one. According to a third aspect of the present invention, in the power train performance test apparatus according to the first or second aspect,
It is proposed that the speed ratio and the second speed ratio are both greater than 1, that is, the speed is increased by both speed change means.

[0009]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a schematic diagram showing the configuration of a performance test apparatus according to the present invention.
1 shows an automobile gasoline engine (hereinafter simply referred to as an engine) installed above. A transaxle 5 in which a transmission 3 and an operating device 4 are integrated as a power train is connected to the engine 1, and the rotation of the engine 1 is reduced on left and right operating output shafts 6 and 7 of the operating device 4. Transmitted. The actuating device 4 is, as shown in FIG.
, A pair of pinion gears 12, 13 rotatably held by a pinion shaft 11, and these pinion gears 12, 1.
3 and a pair of side gears 14, 15 connected to the left and right operation output shafts 6, 7 as main components. The pinion shaft 11 rotates integrally with the differential carrier 10 and drives side gears 14 and 15 via pinion gears 12 and 13 while allowing differential rotation between the left and right operation output shafts 6 and 7.

On the upper surface of the base 2, left and right gearboxes 2 are provided at left and right ends.
0 and a right-side gearbox 21 are arranged, and left and right operation output shafts 6 and 7 of the operating device 4 are connected to input shafts 22 and 23 projecting upward and inward of these gearboxes 20 and 21, respectively. ing. On the other hand, the output shafts 24 and 25 projecting downward and inward of the gearboxes 20 and 21 are connected by the connection shaft 26 and therefore always rotate at the same rotation speed. Right gearbox 21
A measurement output shaft 27 that rotates integrally with the output shaft 25 protrudes from the lower outside, and the measurement output shaft 27 is connected to a dynamometer 28 and a flywheel device 29.
In the figure, reference numeral 30 denotes a torque meter for detecting a driving torque of the measurement output shaft 27.

As shown in FIG. 1, the left gearbox 20 and the right gearbox 21 have the same structure. That is, in the left gearbox 20, the large gear 3 integrated with the input shaft 22 is used.
1 is engaged with a small gear 32 integral with the output shaft 24 to increase the speed. Also in the right gearbox 21, a large gear 33 integral with the input shaft 23 is engaged with a small gear 34 integral with the output shaft 25. The speed increase is performed. However, in the present embodiment, the speed increase ratio is slightly different between the two speed increasers 20 and 21, and the output shafts 24 and 25 are connected by the connection shaft 26 for convenience.
A differential rotation occurs between the input shafts 22 and 23. For example, in the left gearbox 20, the number of teeth of the large gear 31 is NLL,
Assuming that the number of teeth is NLS, the speed increase ratio NLL / NLS is 140/40.
(= 3.5), and in the right gearbox 21, if the number of teeth of the large gear 33 is NRL and the number of teeth of the small gear 34 is NRS, the speed increase ratio NRL / NRS is 136/39 (≒ 3.489). This allows
The input shaft 23 of the right gearbox 21 always rotates at a high speed of 0.37% with respect to the input shaft 22 of the left gearbox 20.

Hereinafter, the operation of the present embodiment will be described. In the performance test of the transaxle 5, after the engine 1 is started, the operation of the engine 1 and the shift of the transmission 3 are performed based on a predetermined operation mode and a shift schedule, while the dynamometer 28 and the flywheel device 29 perform predetermined operations. Of load. Thus, the evaluation of the matching between the engine 1 and the transmission 3 and the measurement of the power loss and the like by the transaxle 5 are performed, and the shift shock and the like by the transmission 3 are also measured by the torque meter 30. On this occasion,
In the present embodiment, since the rotation of the left and right operation output shafts 6 and 7 is increased by the speed increasers 20 and 21, it is possible to employ small dynamometers 28 and flywheel devices 29, and It was possible to reduce the size and equipment costs.

On the other hand, after completion of the performance test, the test operator
Disassemble the transaxle 5 and check each part for wear or damage. At this time, as described above, the right gearbox 21
Input shaft 23 rotates at a slightly higher speed with respect to the input shaft 22 of the left gearbox 20, and during the performance test, the left and right operation output shafts 6 and 7 connected to these also rotate with a slight difference in rotation. I do. Therefore, in the operating device 4, the side gears 14, 15 connected to the left and right operation output shafts 6, 7 and the pinion gears 12, 13 meshing with the side gears 14, 15 gradually rotate relative to each other. A load is equally applied to all the teeth of the gears 12 to 15. As a result, abrasion or damage occurring only to some of the teeth, which was a defect of the conventional device, was prevented, and the durability could be evaluated with high accuracy. In the present embodiment, since the difference in the speed increase ratio between the two gearboxes 20 and 21 is extremely reduced, the rotation speed of the pinion gears 12 and 13 in the operating device 4 can be reduced, and Seizure with the pinion shaft 11 could be prevented.

Although the description of the specific embodiment has been completed above, aspects of the present invention are not limited to this embodiment.
For example, in the above embodiment, the engine is used as the drive source of the power train, but an electric motor or the like may be used. Further, in the above embodiment, the present invention is applied to the transaxle performance test device. However, the present invention may be applied to a power train performance test device in which the transmission and the operating device are separated. Good. Further, other specific configurations of the apparatus, the speed increasing ratio of the speed increasing device, and the like can be appropriately changed without departing from the gist of the present invention.

[0015]

According to a first aspect of the present invention, there is provided a power train performance test apparatus for testing the performance of a power train including a differential device, wherein the performance test device is connected to a first differential output shaft of the differential device. A first transmission means for shifting the rotation of the first differential output shaft at a predetermined first transmission ratio; and a second differential output shaft of the differential device, the first differential means being connected to the second differential output shaft. A second speed change means for shifting the rotation at a predetermined second speed ratio, a connection means for connecting an output shaft of the first speed change means and an output shaft of the second speed change means, and a rotation load connected to the connection means; Load application means for applying the first gear ratio and the second gear ratio are set to different values, during the performance test, the side gear and the pinion gear in the actuator relatively rotate, The load is not applied only to some teeth, and the accuracy of durability evaluation is improved. To.

According to a second aspect of the present invention, in the power train performance testing apparatus according to the first aspect, the first
Since the value obtained by dividing the speed ratio by the second speed ratio is close to 1, the rotation speed of the pinion gear in the operating device can be reduced, and seizure between the pinion gear and the pinion shaft can be prevented. According to a third aspect of the present invention, in the power train performance testing apparatus according to the first or second aspect, both the first speed ratio and the second speed ratio are 1
Since the size is larger, the dynamometer and the flywheel device can be reduced in size.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram showing an embodiment of a performance test apparatus according to the present invention.

FIG. 2 is a sectional view showing the structure of the differential device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Engine 3 Transmission 4 Differential device 5 Transaxle 6,7 Differential output shaft 10 Differential carrier 11 Pinion shaft 12,13 Pinion gear 14,15 Side gear 20,21 Gearbox 22,23 Input shaft 24,25 Output shaft 26 Connecting shaft 27 Measurement output shaft 28 Dynamometer 29 Flywheel device 30 Torque meter 31, 33 Large gear 32, 34 Small gear

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Shinichi Kojima 4-21-1, Shimomaruko, Ota-ku, Tokyo Inside Mitsubishi Motors Engineering Co., Ltd. (56) References Japanese Utility Model 1987-17331 (JP, U) JP 54-40035 (JP, Y2) Jiko 5-24039 (JP, Y2) (58) Field surveyed (Int. Cl. ⁷ , DB name) G01M 13/02

Claims (3)

(57) [Claims] 1. A power train performance testing device for testing the performance of a power train including a differential device, wherein the performance test device is connected to a first differential output shaft of the differential device, and is connected to the first differential output shaft. First speed change means for shifting the rotation at a predetermined first speed ratio; and connecting to a second differential output shaft of the differential device to shift the rotation of the second differential output shaft at a predetermined second speed ratio. A second speed change means, a connection means for connecting an output shaft of the first speed change means and an output shaft of the second speed change means, and a load application means connected to the connection means for applying a rotational load, A performance test apparatus for a power train, wherein the first speed ratio and the second speed ratio are set to different values. 2. A power train performance testing apparatus according to claim 1, wherein a value obtained by dividing said first speed ratio by said second speed ratio is close to one. 3. The power train performance testing apparatus according to claim 1, wherein both the first speed ratio and the second speed ratio are greater than 1.