JPH0212587Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to an improvement of a testing device used for testing an automobile power transmission system.

Currently, as one of the performance tests for automobiles, transmission torque loss in power transmission systems such as transmissions and differential gears is generally measured. The measurement of this torque loss has conventionally been carried out using a testing device as shown in FIG. In this test apparatus, a specimen, for example a transmission 1, is mounted on a specimen mount 3 provided on a bed 2. Specifically, as shown in FIG. 2, the input shaft 4 of the transmission 1 is connected to one end of the rotating shaft 5 of the specimen mounting base 3 via a joint 6, and the case 7 of the transmission 1 is connected to the rotating shaft 5 of the specimen mounting base 3. It is attached to a mounting plate 9 at the end of the frame 8 of the stand 3. The other end of the rotating shaft 5 of the specimen mounting base 3 is connected to an output shaft 11 of a drive source (for example, a DC motor) 10 installed on the bed 2. Drive source 1
A torque meter 12 for measuring the input torque to the transmission 1 is provided between the output shaft 11 of the 0 and the rotating shaft 5 of the specimen mount 3. The bed 2 rides on a guide rail 13 laid on the floor or the like, and can be moved on the guide rail 13 by a cylinder 14 connected to the bed 2. On the other hand, the output shaft 15 of the transmission 1 is connected via a universal joint shaft 18 to a rotating shaft 17 of a dynamometer (for example, a DC electric dynamometer) 16 installed on the floor or the like. This dynamometer 16 has a load cell 19 as a torque measuring device for measuring the generated torque, that is, the output torque of the transmission 1.
is equipped. In this test device, the transmission 1 is driven by the driving source 10, and the input torque T ₁ is measured by the torque meter 12.
is measured and the load cell 19 of the dynamometer 16
The force torque T ₂ is measured by and their difference (T ₁
-T ₂ ), the transmission loss test torque T _l of the transmission 1 is calculated. This method of calculation requires the effort of having to measure the input torque T ₁ and the output torque T _{2 one} by one, and then calculate the loss test torque T _l based on the measurements. Furthermore, in addition to such calculation problems, in the conventional test equipment described above, the rotation shaft 5 of the specimen mounting base 3 that connects the torque meter 12 and the input shaft 4 of the transmission 1 is
is mechanically supported by the bearing 20, so there is a loss torque due to the bearing 20 between the input torque _T1 measured by the torque meter 12 and the torque actually input to the transmission 1. There is a serious drawback in that a difference occurs, which makes the calculated torque T _l inaccurate and contains errors. Therefore, in order to correct this error, it has been conventionally attempted to take into account the loss torque of the bearing 20, but the loss torque of the bearing 20 depends on the rotation speed of the rotating shaft 5, the reduction ratio of the transmission 1, etc. It is difficult to specify because it changes depending on the situation, and it is difficult to take this into consideration when calculating the transmission loss torque.

The present invention was devised in view of the above-mentioned conventional circumstances, and is intended to easily determine the accurate torque loss of a specimen in a power transmission system testing device by taking into account the torque loss at the attachment part of the specimen. The purpose is to make it possible.

The gist of the present invention to achieve the above object is to provide a specimen mount to which a power transmission system is attached, a drive source that provides driving force to the input side of the power transmission system, and an input torque to the specimen mount. A test device comprising an input torque measuring device for measuring the input torque and a dynamometer connected to the output side of the power transmission system, in which the input shaft of the power transmission system is connected to one end and the drive source is connected to the other end. A rotating shaft of the power transmission system is supported by a first swinging member via a bearing, and a bearing loss torque measuring device for measuring loss torque of the bearing is engaged with the first swinging member. The first swinging member is hydraulically buoyed and supported by a second swinging member to which the second swinging member is attached, and this second swinging member is hydraulically supported by a fixed bearing stand, and the power transmission is further carried out to this second swinging member. The present invention is characterized in that the specimen mounting base is configured by engaging a torque measuring device for measuring rocking reaction force that measures the rocking reaction force of the system.

In this power transmission system testing device, the torque applied to the input side of the power transmission system by the drive source and the torque actually applied to the input side of the power transmission system are measured by a bearing torque loss measuring device connected to the first swinging member. The error with the torque applied to the second swing member is measured, and the torque actually input to the power transmission system is determined from this error torque and the input torque measured by the input torque measuring device. Since the torque measuring device for measuring rocking reaction force measures the loss torque (rocking reaction force) between the input side and the output side of the power transmission system, it is possible to measure the loss in the bearing section and the power transmission system itself. The corrected and accurate loss torque of the power transmission system can be determined.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The testing apparatus according to the present invention will be described in detail below based on an embodiment shown in the drawings.

FIG. 3 shows the front of the specimen mounting base in one embodiment, and FIG. 4 shows its left side. Further, FIG. 5 shows a half cross section of the specimen mount, and FIG. 6 shows a fractured cross section viewed from the front. The configuration of the test apparatus of the present invention other than the specimen mounting base is the same as that of the conventional apparatus, so the corresponding members will be referred to in FIG. 1 and their explanation will be omitted here. A base 22 forming the base of this specimen mounting stand 21 is fixed onto the bed 2. A bearing stand 23 is provided on the base 22, and the input shaft 4 of the transmission 1 is attached to one end via a joint 6, and a drive source 10 such as a DC motor is connected to the other end via a torque meter 12. A rotating shaft 5 is rotatably supported by a cylindrical first swinging member 24 via a bearing 20, and this first swinging member 24 has a mounting plate 25 to which the case 7 of the transmission 1 is attached. The second swinging member 26 is fitted into the second swinging member 26 and hydraulically buoyed with respect to the second swinging member 26, and the second swinging member 26 is fitted with the bearing pedestal 23 and is hydraulically buoyed with respect to the bearing pedestal 23. Supported. The bearing stand 23 has a plurality of protruding surfaces 27a, 27b on opposite sides, and a cylindrical inner peripheral surface 28.
Two bearing stand members 23a, 23 having a, 28b
It is formed by combining b together. Each protruding surface 27a, 27
A hydraulic pool 2 is provided on b and each inner circumferential surface 28a, 28b.
9 and 30 are formed. A mounting plate 31 attached to one bearing pedestal member 23a of the bearing pedestal 23 is provided with an oil supply port 32 to which an external hydraulic power source is connected.
An annular main oil supply passage 33 is formed in the bearing pedestal member 23a connected to this oil supply port 32, and a large number of branch oil passages 34 are formed from here spanning both bearing pedestal members 23a and 23b. Furthermore, branch passages 35 and 36 are connected from these branch oil passages 34 to the hydraulic pools 29 and 30. The second swinging member 2 is attached to the inner peripheral surfaces 28a and 28b of this bearing stand 23.
6 are fitted in a swingable manner. Further, a flange-shaped thrust receiving part 37 is formed on the outer periphery of the central part of the second swinging member 26, and when the second swinging member 26 is assembled to the bearing stand 23, this thrust receiving part 37 is It is adapted to be clamped by the protruding surfaces 27a and 27b. In other words, the second swinging member 26 is radially moved by the hydraulic pressure supplied to the hydraulic pool 30 on the inner circumferential surfaces 28a, 28b of the bearing stand 23, and also to the hydraulic pool 29 on the protruding surfaces 27a, 27b. It is hydraulically supported in the thrust direction by hydraulic pressure. Second swing member 26
A plurality of hydraulic pools 39 are formed on the inner peripheral surface 38 of the shaft, and a plurality of hydraulic pools 41 are also formed on the side end surface 40 perpendicular to the axis. On the other hand, an annular auxiliary plate 42 is integrally attached to the bearing stand 23 so as to face the side end surface 40, and a hydraulic pool 43 is also formed on the surface of the annular auxiliary plate 42. Auxiliary plate 4
2 and the second swinging member 26 and the bearing stand 23 are connected to the hydraulic pools 39 and 41, 4 from the branch oil passage 34.
3 are formed. The first swinging member 24 is swingably fitted into the inner circumferential surface 38 of the second swinging member 26, and a flange-shaped thrust receiving portion 46 formed around the end portion of the first swinging member 24 is attached to the side end face 40. and the auxiliary plate 42. That is, the first swinging member 24 is hydraulically buoyed and supported by the hydraulic pool 39 of the second swinging member 26 in the radial direction and by the hydraulic pools 41 and 43 in the thrust direction. Note that the hydraulic pool 2 is connected to the bearing stand 23 and the second swinging member 26.
9, 30, 39, 41, and 43 are provided with a discharge path for hydraulic pressure supplied thereto.

As described above, since the first swinging member 24 that encloses the bearing 20 is supported in hydraulic levitation, a loss torque T _B of the transmission torque of the rotating shaft 5 due to the bearing 20 is generated here. In order to measure this, a torque arm 48 is integrally coupled to the end of the first swinging member 24 via an auxiliary member 47.
A load cell 49 is coupled to 8 as a torque measuring device. Moreover, the first swinging member 24 and the bearing stand 23
and its mounting plate 2.
The transmission 1 is attached to the second swing member 26 to which the case 7 of the transmission 1 is attached.
A loss torque (hereinafter referred to as the rocking reaction force T _X ) is generated on the input side and output side. This rocking reaction force _T
The torque arm 5 is attached to the mounting plate 25 in order to measure the
0, and connect the coupling mechanism 5 to this torque arm 50.
A load cell 51 of a torque measuring device is connected via 2.

By the way, if the input torque to the rotating shaft 5 of the specimen mounting base 21, that is, the input torque measured by the torque meter 12, is T ₁ and the input torque actually input to the transmission 1 is T ₁ ', then the input torque is T ₁ and actually input shaft 4 of transmission 1
There is a bearing 2 between the torque T ₁ ′ input to
There is an error equal to the loss torque T _B at the 0 section. Therefore, the accurate input torque (corrected input torque) T ₁ ' to the input shaft 4 of the transmission 1 is T ₁ '=T ₁
−T _B. Between the output torque T ₂ measured by the load cell 19 of the dynamometer 16, the loss torque T _L in the transmission 1, the reduction ratio i of the transmission 1, and the rocking reaction force T _X measured by the load cell 51. It is known that there is a relationship of T _X =T ₁ ′−T ₂ (1), and further, a relationship of TL=T ₁ ′−T2/i (2). Then, from equation (2), the following relationship is derived: T ₂ = i (T ₁ ′−T _L ) (3), and by substituting equation (3) into equation (1), the loss of transmission 1 can be calculated as follows. The following relational expression for determining torque T _L can be derived: T _L =T ₁ ′+1/i (T _X −T ₁ ′) (4). From this equation (4), the actual input torque T ₁ ′,
It can be seen that if the reduction ratio i and the rocking reaction force T _X are known, the loss torque T _L of the transmission 1 can be obtained. In other words, the reduction ratio i is known in advance, and the rocking reaction force
_{T ​ ​}
By obtaining the corrected input torque T ₁ ' from -T _B , it is possible to calculate an accurate loss torque T _L of the transmission 1 that compensates for the loss due to the bearing and the reduction ratio. Also, if T ₁ ' is eliminated from equations (1 ₎ and ( ₂ ), _{T L} = _T T _L can be determined accurately. Furthermore, as can be seen from equation (4), the reduction ratio i
=1, T _L =T _X , and the loss torque T _L of the transmission 1 is directly measured by the load cell 51. Also, from equation (5), when T ₂ =0, that is, no load, T _L =T _X.

In the above embodiment, the load cells 49 and 51 are used as torque measuring devices that engage the first swinging member 24 and the second swinging member 26, but a pendulum type automatic scale or other device may be used. Further, the dynamometer is not limited to the DC electric dynamometer, but other dynamometers may be used.

As described above in detail with reference to one embodiment, according to the power transmission system torque loss testing device according to the present invention, the loss of bearing portion in the specimen mounting base on which the specimen power transmission system is mounted is Since not only the torque can be measured, but also the loss torque of the power transmission system can be directly measured, the transmission loss torque in the power transmission system can be corrected by the loss of the bearing section and accurately determined.

[Brief explanation of the drawing]

Fig. 1 is a front view of the entire conventional power transmission system testing device, Fig. 2 is a partial sectional view of the specimen mounting base in Fig. 1, and Fig. 3 is a specimen in an embodiment of the testing device according to the present invention. FIG. 4 is a partially fragmented front view of the mounting base, FIG. 4 is a side view thereof, FIG. 5 is a half sectional view thereof, and FIG. 6 is a fragmented sectional view thereof as seen from the front. In the drawing, 1 is the transmission, 4 is the input shaft of the transmission, 5 is the rotating shaft of the specimen mounting base, 7 is the transmission case, 10 is the drive source, 12 is the torque meter, and 15 is the transmission. 16 is a dynamometer, 19 is a load cell, 20 is a bearing, 21 is a specimen mounting stand, 23 is a bearing stand, 24 is a first swinging member, 25 is a mounting plate, 26
is the second swinging member, 29, 30, 39, 41, 43
is a hydraulic pool, and 49 and 50 are load cells.

Claims (1)

[Scope of utility model registration request] a specimen mount to which a power transmission system is attached; a drive source that provides driving force to the input side of the power transmission system; an input torque measuring device that measures input torque to the specimen mount; and the power transmission system. A test device consisting of a dynamometer connected to the output side of a rotary shaft, one end of which is connected to the input shaft of the power transmission system, and the other end of which is connected to the drive source, is connected to a first swinging member via a bearing. A bearing portion torque loss measuring device for measuring loss torque of the bearing portion is engaged with the first swinging member, and the second swinging member to which the case of the power transmission system is attached is connected to the first swinging member. The movable member is supported in hydraulic levitation, and the second swinging member is supported in hydraulic levitation on a fixed bearing stand.
A test device for a power transmission system, characterized in that the specimen mounting base is configured by engaging a swinging member with a torque measuring device for measuring a swinging reaction force that measures a swinging reaction force of the power transmission system. .