JPH07209140A - Load-characteristic tester for rotary shaft - Google Patents

Abstract

PURPOSE:To obtain the highly accurate test results in correspondence with an actual machine by simulating the applying state on the actual machine including the occurrence behavior of torsional vibration almost perfectly, and preventing the occurrence of the inability of the continuation of the test caused by the meaningless torsional vibration. CONSTITUTION:An inertial disk 12 is attached to the tip of a rotary shaft 1 on the side of a transmission system to be tested. A spider wheel 22 is attached to an input shaft 2 for a rotating load. The inertial disk 12 and the spider wheel 22 are linked on the specified circumference with the shaft center as the center with a linking member 3, which is provided between the appeased surfaces of both the disk 12 and the wheel 22. The linking member 3 includes a spring element, which imparts the specified resistance to the force in the stretching direction by the rotary torque transmitted from the inertial disk 12 to the spider wheel 22, and an attenuating element, which attenuates the stretching action by the action of the rotary torque. The damping function of the inertial element, which is attached to the rotary shaft 1 in the actual machine, is repalced with the spring and the attenuating action, and the occurrence behavior of the torsional vibration in the actual machine is simulated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a test apparatus used for obtaining load characteristics of a rotary shaft cantilevered on a test machine.

[0002]

2. Description of the Related Art Inertia elements (body weight equivalent inertia in the case of axles and transmission shafts for helicopters in the case of axles, such as axles of various vehicles, transmission shafts for propeller rotor blades, etc. Is equivalent to the rotor blade inertia, and the rotary shaft is resisted against the loads (road surface resistance, uphill load and traction load in the case of axles, air blow stirring resistance in the case of helicopter transmission shafts) applied to this inertia element. In a transmission system that is rotationally driven from the base end side (support side), a load characteristic test is performed to confirm the load characteristic of a rotating shaft under various load conditions.

In this load characteristic test, conventionally, an entire transmission system including a drive source such as an engine, a clutch device, a transmission, etc. is fixed on a bench test bench, and an inertial body simulating inertia under actual use is used. Then, using a test device in which an appropriate rotary load such as a wet multi-plate brake is connected to the rotary shaft, various load torques are applied to the rotary shaft by sequentially controlling and adjusting the load amount of the rotary load, and the rotary shaft is rotated. It is carried out by a procedure for obtaining the load characteristics of the transmission system including the shaft.

[0004]

However, when the conventional load characteristic test as described above is performed, a torsional vibration is generated on the cantilever-supported rotating shaft under a load condition that does not cause a design problem. However, despite the fact that there is no obstacle to application to the actual machine, it is required to increase the strength of the rotating shaft in order to avoid torsional vibration during the test,
There is a problem in that the entire transmission system is upsized due to the unnecessarily large diameter of the rotating shaft.

On the other hand, in order to suppress the torsional vibration during the test,
It is possible to increase the natural frequency by using a test rotary shaft having a diameter larger than that of the actual rotary shaft, and to make the inertia of the inertial body connected to the rotary shaft smaller than that in the actual machine. . However, in such a case, under most load conditions, the test results on the bench base different from the load characteristics under the use condition are obtained, and the original test purpose cannot be achieved.

In a state of use in an actual machine, a member which is attached to the tip of the rotary shaft and serves as an inertial element often has a predetermined inertia and also has a vibration damping action against torsional vibration. For example, when the rotating shaft to be tested is an axle for various vehicles, the wheel, which is an inertia element, is grounded to the road surface via a rubber tire in which air is enclosed, and the rubber and the enclosed air are springs. Acting as an element and a damping element, torsional vibration is suppressed.

The present invention has been made in view of the above circumstances, and by substantially completely simulating the application state to the actual machine including the behavior of the torsional vibration, satisfactory test results corresponding to the actual machine can be obtained. An object of the present invention is to provide a load characteristic test device for a rotating shaft that is obtained.

[0008]

According to the present invention, there is provided a load characteristic test device for a rotating shaft, wherein a tip end of a rotating shaft supported in a cantilever manner is connected to a rotating load through an inertial body simulating inertia under actual use. Then, in the load characteristic test device for the rotating shaft, which is designed to check the load characteristic of the rotating shaft according to the transmission from the base end side,
A connecting member including a spring element and a damping element, which is used for connecting the inertial body and the rotational load, is provided.

In addition, the connecting member has a cylinder cylinder in which a viscous fluid is sealed and a part of which is connected to the inertial body or the rotation load, and the cylinder cylinder slidably fitted into the cylinder cylinder to rotate the cylinder. A piston, a part of which is connected to the load or the inertial body, a spring body that is housed in the cylinder cylinder and urges the piston to both sides in the sliding direction, and a piston that is formed on the piston and that slides with the piston. And a throttle cylinder through which the viscous fluid flows, a cylinder cylinder part of which is connected to the inertial body or the rotary load, and the rotary load slidably fitted in the cylinder cylinder. Alternatively, each is characterized by including a piston, a part of which is connected to the inertial body, and a rubber shock absorber housed inside the cylinder cylinder and elastically contacting both sides of the piston.

[0010]

In the present invention, the inertial body simulating the inertia under actual use is connected to the rotary load through the connecting member including the spring element and the damping element. The spring element of the connecting member simulates the spring action of the inertia element attached to the rotary shaft in the actual machine, and the damping element of the connecting member also simulates the damping action, so that the action of the connecting member causes the torsional vibration to be generated. It is possible to obtain the test result that corresponds to the usage condition in the actual machine by making it correspond to that in the actual machine.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing the embodiments. FIG. 1 is a schematic diagram showing the overall configuration of a load characteristic test device for a rotating shaft according to the present invention (hereinafter referred to as the device of the present invention). As shown in the figure, the load characteristic test by the device of the present invention is
A test transmission system A including an engine, a clutch and a transmission is fixed on a bench test bench B, and a tip of a rotary shaft 1 which is cantilevered by the test transmission system A and projects to one side is connected to a rotary load C. Will be implemented.

The rotary load C may be any load that can apply an appropriately changeable braking torque to its own input shaft 2 used for connection with the rotary shaft 1, and is a wet or dry multi-plate. Various brakes such as brakes and powder brakes or dynamometers can be used.

The feature of the device of the present invention resides in the connection mode between the input shaft 2 of the rotary load C and the rotary shaft 1. 2 is an enlarged cross-sectional view showing a connecting portion between the rotary shaft 1 and the input shaft 2, FIG.
FIG. 3 is a view taken along the line III-III in FIG.

As shown in the figure, at the tip of the rotary shaft 1 on the side of the test transmission system A, there is provided a fixed flange 10 for fixing predetermined inertia elements such as wheels and rotary blades in the actual machine. 10 is a connecting boss screwed to the end face
An inertial disk 12, which is an inertial body, is coaxially attached via 11. This inertial disk 12 simulates an inertial element in an actual machine, and its outer diameter and thickness are set so as to have inertia equal to that of the inertial element.

Although the connecting boss 11 and the inertial disk 12 can be integrally formed, when the connecting boss 11 and the inertial disk 12 are divided as shown in the drawing, the inertial disk 12 is replaced with the common connecting boss 11 so as to be variously used in an actual machine. It is possible to cope with different inertia elements, for example, a load characteristic test of an axle transmission system of a tractor in which various different working machines are mounted on a common vehicle body and the traction load may change greatly. Further, the inertial body is not limited to the inertial disk 12, but other shapes can be adopted, but the adoption of the disk shape allows the inertia to be set accurately, and the inertial element simulation accuracy of the actual machine can be set. Has the effect of improving.

On the other hand, on the input shaft 2 on the side of the rotational load C, a fixed adapter 20 fitted to the outer periphery of the tip portion, and the fixed adapter
A spider wheel 22 is coaxially fixed via a connecting boss 21 screwed and fixed to 20. The tip of the connecting boss 21 is internally rotatably fitted into the axial center of the connecting boss 11 on the side of the rotating shaft 1 and serves only to maintain the coaxiality between the rotating shaft 1 and the input shaft 2. The shafts 1 and 2 are connected to each other via a connecting member 3 which is interposed between the inertial disk 12 and the spider wheel 22 on an appropriate circumference centered on the shaft center.

The fixed adapter 20 is necessary in order to be able to attach the common connecting boss 21 to various rotational loads C, the test object range is narrow, and a single rotational load C can be used. If possible, the fixed adapter 20 and the connection boss 21 may be integrated. Further, the connecting boss 21 is necessary to correspond to the replacement of the spider wheel 22 corresponding to the inertial disk 12 to be replaced on the rotary shaft 1 side.

The spider wheel 22 includes a plurality of (four in the embodiment) connecting arms 23, 23 projecting outwardly.
Each of ... Has an outer diameter substantially equal to that of the inertial disk 12 so that it can be connected to the inertial disk 12 on an appropriate circumference, and the inertia is sufficiently smaller than that of the inertial disk 12. And the rigidity that can withstand the rotational torque transmitted from the rotary shaft 1 to the input shaft 2 are designed. The adoption of such a spider wheel 22 simulates the inertia under actual use. The inertial disk 12 and the input shaft 2 for the rotational load C are connected substantially directly via the connecting member 3.

The connecting arms 23, 23 of the spider wheel 22 ...
Are a plurality of protrusions (two in the embodiment) provided on the respective surfaces centering on the shaft center and facing the inertial disk 12.
., And the inertial disk 12 has a plurality of connecting projections 24, 24 ... on the circumference corresponding to the circumferences of the connecting projections 24, 24. The same number of connecting protrusions 14, 14
... is projected on the surface facing the spider wheel 22.

As will be described later, the connecting member 3 is a member including a spring element and a damping element, and as shown in FIG. 3, between the corresponding connecting protrusions 14 and 24 arranged on the circumference. The inertial disk 12 and the spider wheel 22 are connected to each other and are connected to each other. The selection of the circumference around which the connecting member 3 is erected, and the number of erected pieces on each circumference are selected according to the strength of the connection between the inertial disk 12 and the spider wheel 22, that is, the strength of the shaft torque. Is done. To increase (or weaken) the connection strength, the outer (or inner) erection circumference may be selected, and the number of erections on each circumference may be increased (or decreased).

In FIG. 3, the erected state of the connecting members 3, 3 on the inner erection circumference is shown in the upper half, and the erected state of the connecting members 3, 3 on the outer erection circumference is lower. They are shown in each half. Further, it is possible to simultaneously realize the erection of the respective connecting members 3, 3 ... At different positions in the circumferential direction, further, one side of each of the connecting members 3, 3, ... By connecting each of them on the circumference of the erection, it is possible to obtain an intermediate connection strength when erected outside and inside.
Further, the most strengthened connection state can be obtained by simultaneously constructing the connection members 3, 3, ... On both installation circumferences. In this way, by appropriately installing the connecting members 3, 3 on both the inner and outer sides,
It is possible to appropriately realize a plurality of different connection strengths between the inertial disk 12 and the spider wheel 22.

FIG. 4 is a vertical sectional view showing an embodiment of the connecting member 3. As shown in the figure, the connecting member 3 is mounted on a cylinder cylinder 30 having a cylindrical shape so as to be slidable in the axial direction in a piston plate 31.
Is internally fitted to form a pair of oil chambers S ₁ and S _{2 in} which oil as a viscous fluid is enclosed between the piston plate 31 and the lid plates 30a and 30b which close the opening portions at both ends of the cylinder tube 30. It becomes.

Piston plate 31 and lid plates facing both sides of the piston plate 31
A plurality of leaf springs 32, 32 ... Are interposed between the leaf springs 30a, 30b, and the piston leaf 31 is located at a position (neutral position) where the spring loads of the leaf springs 32, 32. It is designed to form a spring center and stop. Further, the piston plate 31 is formed with a communication hole 34 in which the oil chambers S ₁ and S ₂ on both sides are communicated with each other and a throttle member 33 is fitted in the middle thereof.
The piston plate 31 slides inside the cylinder cylinder 30 through the communication hole.
After passing through 34, the sealed oil flows from one oil chamber S ₁ (or oil chamber S ₂ ) to the other oil chamber S ₂ (or oil chamber S ₁ ) in both directions.

The piston plate 31 is equipped with a piston rod 35 which is coaxially fixed to the shaft center and extends on both sides.
One side of the piston rod 35 penetrates the axial center portion of the lid plate 30a on the same side and projects outward. Also piston rod
The other end of 35 is supported by the axial center portion of the lid plate 30b on the same side, and a connecting rod 36 having a predetermined length is coaxially projected on the outside of the lid plate 30b.

The connecting member 3 constructed as described above is installed by connecting the connecting protrusion 14 and the spider wheel 22 on the inertial disk 12 side.
The protruding end of the piston rod 35 to one of the side connection protrusions 24.
On the other hand, connect the tip of the connecting rod 36 to the connecting pin 37,
Each of them is pivotally supported by 38 so as to be swingable. In this state, when the rotating shaft 1 is rotated by the transmission from the test transmission system A, this rotation is transmitted to the input shaft 2 via the inertial disk 12, the connecting member 3 and the spider wheel 22, and the rotating load C The braking torque generated by is brought into a state of being loaded on the rotary shaft 1, and the steady or transient load characteristic test of the test transmission system A is performed by appropriately controlling and adjusting the braking torque.

During this time, the inertial disk 12 is attached to the connecting member 3.
The rotational torque transmitted from the to the spider wheel 22 acts in a direction to extend or shorten the piston rod 35 and the connecting rod 36 in the axial direction. This acting force is transmitted to the piston plate 31 fixed to the piston rod 35, and the piston plate 31 resists the spring load of the leaf springs 32, 32 ... An attempt is made to slide inside the cylinder cylinder 30 with oil passing through the communication hole 34 formed therethrough.

That is, the inertial disk 12 on the rotary shaft 1 side and the input shaft 2
Connecting member 3 installed between the side spider wheel 22
Has a function as a spring element that resists the rotational torque by the spring force of the leaf springs 32, 32, and further, a piston plate generated in the extension or contraction direction by the action of the rotational torque in both forward and reverse directions. It acts as a damping element that damps the sliding of 31 by the oil passage resistance in the communication hole 34 formed in the piston plate 31, particularly the oil passage resistance in the throttle member 33 fitted in the communication hole 34. . In this way, the connecting member 3 simultaneously functions as a spring element and a damping element with a simple structure.

In general, the inertia element attached to the tip of the rotary shaft 1 in a state of being used in an actual machine also acts as a spring element and a damping element. For example, when the test transmission system A is a transmission system for various vehicles, the wheels attached to the rotating shaft 1 are grounded on the road surface via rubber tires, and the rubber and the enclosed air are spring elements. And acts as a damping element.

Therefore, when the connecting member 3 is selected so as to obtain the spring and the damping action equivalent to those of the inertial element attached to the rotary shaft 1 in the actual machine, the connecting member 3 causes the spring and the damping action of the inertial element. The inertia of the inertia element is simulated by the inertia disk 12 and
In the above-mentioned test, the application state to the actual machine including the generation behavior of the torsional vibration in the rotary shaft 1 can be almost completely simulated, and the execution of the test is not hindered by the generation of meaningless harmful torsional vibration. The load characteristics can be obtained with high accuracy.

As described above, the action of the connecting member 3 as the spring element and the damping element can be changed depending on the circumference of the connecting member 3 and the number of the connecting members 3 on each circumference.
It is not necessary to prepare a plurality of types of connecting members 3 having different characteristics. Further, the selection of the connecting member 3 is carried out by examining the natural frequency outside the supporting portion of the rotary shaft 1 under various connected states, and matching the result with the actual operating condition of the actual machine as much as possible. do it. The connecting member 3 has a simple structure as described above, and since it is easy to reduce the weight, changes in the erection mode and the number of erected connecting members 3, 3 ... Have a very small effect on the test results.

FIG. 5 is a vertical sectional view showing another embodiment of the connecting member 3. As shown in the figure, the connecting member 3 is mounted on a cylinder cylinder 40 having a cylindrical shape so that the piston plate is slidable in the axial direction.
The rubber shock absorber 4 is fitted between the piston plate 41 and the lid plates 40a, 40b that close the openings at both ends of the cylinder tube 40.
The configuration is such that a predetermined compression is applied to 2 and 42 to hold the sandwiching pressure.

The piston plate 41 is provided with a piston rod 45 which is fixed coaxially to the shaft center portion and extends on both sides. One side of the piston rod 45 is the shaft center portion of the lid plate 40a on the same side. It penetrates and projects to the outside. The other end of the piston rod 45 is supported by the shaft center portion of the lid plate 40b on the same side, and a connecting rod 46 is coaxially projected on the outer side of the lid plate 40b.

This connecting member 3 is the connecting member 3 shown in FIG.
Similarly, the projecting end of the piston rod 45 and the tip of the connecting rod 46 are pivotally supported by one of the connecting protrusions 14 and 24 and the other end of the connecting rod 46 by separate connecting pins 47 and 48, respectively. Used. In this use state, the rotational torque transmitted from the inertial disk 12 to the spider wheel 22 acts in a direction to extend or shorten the piston rod 45 and the connecting rod 46 in the axial direction, and this acting force acts on the piston rod 45. Transmitted to the fixed piston plate 41, the piston plate 41,
An attempt is made to slide inside the cylinder cylinder 40 with the compression of one of the shock absorbers 42, 42 on both sides.

As described above, the cushioning members 42, 42 made of rubber are used.
Has both a function as a spring element that resists acting force in the direction of compressing it by its elasticity and a function as a damping element for displacement in the compression direction. Therefore, by using the connecting member 3 shown in FIG.
It is now possible to perform the above-mentioned test in a state that almost completely simulates the actual machine including the behavior of the torsional vibration in, and it is possible to obtain a highly accurate load characteristic without being obstructed by the generation of meaningless harmful torsional vibration. .

The connecting member 3 shown in FIG. 5 has an advantage that the structure can be further simplified as compared with that shown in FIG. The buffers 42, 42 are not limited to the above-mentioned rubber,
It may be made of another material that has the functions of both a spring element and a damping element.

[0036]

As described above in detail, in the device of the present invention, in connecting the rotary shaft and the rotary load through the inertial body simulating the inertia under actual use, the connecting member includes the spring element and the damping element. With the configuration using, the test will be performed in a state that simulates the actual machine including the behavior of the torsional vibration, and there is no fear that the meaningless torsional vibration will hinder the continuation of the test. It is possible to obtain test results with high accuracy corresponding to the usage conditions in.

Further, according to the second or third aspect of the present invention, it is possible to provide a connecting member having a simple structure including a spring element and a damping element, and using such a connecting member, the inertial body and the rotary load are connected. In this case, the present invention has excellent effects such that the influence on the test result can be kept small.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing an overall configuration of a device of the present invention.

FIG. 2 is an enlarged sectional view showing a characteristic part of the device of the present invention.

FIG. 3 is a view taken along the line III-III in FIG.

FIG. 4 is a vertical sectional view showing an example of a connecting member.

FIG. 5 is a vertical sectional view showing another embodiment of the connecting member.

[Explanation of symbols]

 1 rotating shaft 2 input shaft 3 connecting member 12 inertia disk 22 spider wheel 30 cylinder cylinder 31 piston plate 32 leaf spring 33 communication hole 34 throttle member 35 piston rod 36 connecting rod 40 cylinder cylinder 41 piston plate 42 shock absorber 45 piston rod 46 Connecting rod A Test transmission system B Bench test bench C Rotating load

Claims (3)

[Claims] 1. A load of the rotating shaft according to a transmission from a base end side, wherein a tip end of the rotating shaft supported in a cantilever manner is connected to a rotating load via an inertial body simulating inertia under actual use. In the load characteristic test device of the rotating shaft, which is designed to check the characteristics,
A load characteristic test device for a rotating shaft, comprising a connecting member including a spring element and a damping element and used for connecting the inertial body and the rotating load. 2. The cylinder member, wherein the connecting member is filled with a viscous fluid, and a part of which is connected to the inertial body or the rotary load, and the rotary load slidably fitted in the cylinder cylinder. Alternatively, a piston, a part of which is connected to the inertial body, a spring body that is housed in the cylinder cylinder and urges the piston to both sides in the sliding direction, and a piston that is formed on the piston and that slides with the piston. The load characteristic test device for a rotating shaft according to claim 1, further comprising: a throttle means through which the viscous fluid flows. 3. The cylinder member, a part of which is connected to the inertial body or the rotary load, and the connecting member slidably fitted into the cylinder cylinder. The load characteristic testing device for a rotating shaft according to claim 1, further comprising: a piston having parts connected to each other; and a rubber shock absorber housed inside the cylinder cylinder and elastically contacting both sides of the piston.