JPH0623679B2 - Synchronous endless flexible member running tester - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an improvement of a running tester for running a synchronous endless flexible member such as a timing belt or a chain to test various performances thereof. .

(Prior Art) Conventionally, as a tester for performing a load durability running test or a tooth jump torque measurement test of a timing belt, the timing belt to be tested is hung between the pulleys of the drive shaft and the driven shaft, and the drive shaft is A power absorption system is often used in which the driven shaft is driven and rotated while the driven shaft is braked by electricity or fluid to apply a constant load to the belt.

However, in such a power absorption type running test machine, there is a problem that the power consumption is extremely large and the use cost is high.
A running tester of a so-called power circulation system has been proposed in which timing pulleys are attached to both ends of a pair of rotary shafts, and the pulleys are connected by a transmission belt to circulate a load between them.

An example of this power circulation type tester is shown in FIG. 8. A drive shaft 1 drivingly connected to an electric motor 8 as a drive device via a transmission belt 9 and pulleys 10 and 11 and a drive shaft 1 parallel to the drive shaft 1. A driven shaft 2 disposed on the drive shaft 1, a first test timing pulley 3 rotatably attached to one end of the drive shaft 1, and a first drive rotatably attached to the other end of the drive shaft 1. A second test timing pulley 5 in which the test timing belt B is wound between the pulley 4'and one end of the driven shaft 2 so as to rotate integrally therewith, and the first test timing pulley 3; , A second driving pulley 6'rotatably attached to the other end of the driven shaft 2
And a drive belt 7'comprising a friction transmission belt wound between the first and second drive pulleys 4'and 6 '.
And the first timing pulley 3 for testing.
Pitch diameter of D _P1 , second test timing pulley 5
Is D _P2 , the pitch diameter of the first drive pulley 4'is D _P3 , and the pitch diameter of the second drive pulley 6'is D _P2 .
As _P4, by a _{D P1 / D P2 ≠ D P3} / D P4, ' the pulleys 4' driving belt 7, 6 'is forcibly slip on, to provide a load to the test timing belt B (For example, Japanese Patent Publication No. 59-
28852).

As another example, as shown in FIG. 9, in the same device configuration as described above, the pitch diameters D _{P1 to} D _P4 of the pulleys 3, 5, 4 ′ and 6 ′ are set to D _P1 / D _P2 ≠ D. _P3 / D
_{In addition to P4} , one of the drive shaft 1 and the driven shaft 2 (the driven shaft 2 in the figure) is divided in the axial direction, and the fluid coupling or the electromagnetic coupling device 12 is provided in the divided portion, and between the divided portions of the shaft 2. There is one in which a load is applied to the test belt B by giving a relative rotational speed difference and causing a slip in the fluid coupling or the electromagnetic coupling device 12 due to the speed difference (for example, Japanese Patent Publication No. 62). -17688).

However, these conventional systems are systems in which a load is applied to the belt B by forcibly generating a slip in a part of the transmission system, so that only a part of the power is circulated in the transmission system. It is a method. Therefore, the driving force of the motor 8 is spent on the slip loss load and the power consumption is large, which is not economically advantageous.

In particular, when a high load condition is required, the former one shown in FIG. 8 forcibly slips the driving belt 7 ', so that a considerably large transmission belt is used for the driving belt 7'. Even if it does, there is a risk of early damage.
On the other hand, the latter (shown in FIG. 9) has a problem that the testing machine is large and expensive because it requires a large capacity fluid coupling or electromagnetic coupling device 12.

On the other hand, a belt running tester of a complete power circulation system, in which power is completely circulated in the transmission system, has been proposed and implemented. The example will be described with reference to FIGS. 10 and 11. First, in the running tester shown in FIG. 10, the first and second drive pulleys 4 and 6 are timed in the same device configuration as above. A drive belt 7 which is composed of a pulley and which is wound between the drive timing pulleys 4 and 6 is a timing belt. Then, the pitch diameters D _{P1 to} D _P4 of the pulleys 3, 5, _{4 and 6} are set to D _P1 / D
_P2 = D _P3 / D _P4, and the test side shaft portion 1a ′ in which the drive shaft 1 ′ is rotationally integrated with the first test timing pulley 3 and the drive side shaft in which the drive shaft 1 ′ is rotationally integrated with the first drive timing pulley 4. The shaft 1a 'is divided into two parts, and the torque flange 13 is attached to the opposing parts of the shaft parts 1a' and 1b 'while the driven shaft 2
The torsion bar 14 is attached to the.

On the other hand, the test machine shown in FIG. 11 has a pitch diameter D of each pulley 3, 5, 4, 6 as in the test machine shown in FIG.
Let _{P1 to} D _P4 be D _P1 / D _P2 = D _P3 / D _P4 ,
A torque flange 13 is attached to an opposing portion of both shaft portions 1a ', 1b' in the drive shaft 1 ', and an idler pulley 16 biased by a spring 15 is pressed against one span of the drive timing belt 7. is there.

All of these running testers are designed to apply a load to the transmission system by tightening and fixing the torque flange 13 with bolts while the torque flange 13 is twisted by input. In this system, since both the test belt B and the driving belt 7 are timing belts, there is no slippage in the transmission system, and the load circulates completely in the transmission system. Since the motor 8 needs to drive only mechanical loss such as bearing friction loss and belt bending loss, power consumption is significantly reduced, which is economically advantageous.

(Problems to be Solved by the Invention) However, such a complete power circulation type testing machine has the drawbacks described below. That is, in this type of testing machine, when the test timing belt B stretches over time, the twist of the drive shaft 1'is released and the load is reduced. Is essential. The former one (shown in FIG. 10) is the torsion bar 14, and the latter one (shown in FIG. 11) is the spring 15 for biasing the idler pulley 16. However, in these devices, the torque or force gradually generated as the test belt B stretches decreases, and therefore, when the test belt B is run for a long time, a large load reduction is still avoided. I can't. For this reason, in the case of actually performing a long-time running test, the operation of releasing the torque flange 13 and resetting the torque flange 13 for the former one each time the load decreases In that case, it is necessary to change the mounting position of the spring 15 and reset it.

Further, the lower the spring constant of the torsion bar 14 and the spring 15 is, the smaller the load reduction is, which is preferable, but in reality, there is a trade-off between the spring constant and the elastic limit. Therefore, a plurality of types of torsions having different spring constants are used. Bar 14 or spring 1
It is necessary to prepare No. 5 and replace it according to the size of the load to be set.

Further, when a load is applied, the bolts are tightened while the torque flange 13 is twisted by the input, so that it takes a lot of time to set. Therefore, as described above, there is a drawback that the operability of the testing machine is extremely poor.

Further, as described above, since the load can be applied only when the tester is stopped, it is practically impossible to perform a test for continuously changing the load while the belt is running, such as a tooth jump torque measurement test. is there.

The present invention has been made in view of the above points, and an object thereof is to secure an advantage of a complete power circulation type belt running test machine that consumes less power and can easily apply a high load condition to a belt. At the same time, it is intended to eliminate the drawback and to reduce the load even during a long-running test, improve operability, and enable tests such as a tooth jump torque measurement test.

(Means for Solving the Problem) In order to achieve the above object, a solution means of the invention according to claim (1) is a drive shaft drivingly connected to a drive device, and the drive shaft is arranged in parallel with the drive shaft. A driven shaft, a first test toothed transmission wheel such as a timing pulley and a sprocket that are rotatably attached to one end of the drive shaft, and a timing pulley and a sprocket that are rotatably attached to the drive shaft at the other end. Etc. and a first drive toothed transmission wheel, which is attached to one end of the driven shaft so as to rotate integrally, and a test belt such as a timing belt or a chain can be synchronously endless between the first test toothed transmission wheel and the like. A second test toothed transmission wheel, such as a timing pulley or sprocket, around which a flexible member is wound, and a second drive toothed transmission wheel, such as a timing pulley or sprocket, which is integrally and rotationally attached to the other end of the driven shaft. And the first And a drive synchronous endless flexible member such as a timing belt or a chain wound between the second drive toothed drive wheels and a span between the drive synchronous endless drive wheels of the drive synchronous endless flexible member. A pair of movable idlers arranged respectively and a constant pressure linear motion device for linearly sliding the movable idlers so as to press the span of the synchronous endless flexible member for driving are provided.

Then, the pitch diameter of the first test toothed transmission wheel is D
_P1 , the pitch diameter of the second test toothed transmission wheel is D _P2 , the pitch diameter of the first driving toothed transmission wheel is D _P3 , the pitch diameter of the second driving toothed transmission wheel is D _P4 , the distance between the drive and driven shaft C, and the pitch length of the driving synchronous endless flexible member L _P
As D _P1 / D _P2 = D _P3 / D _P4 , and L _P > 2C + π (D _P3 + D _P4 ) / 2 + (D _P3 −D _P4 ) ² / 4C, that is, of the drive synchronous endless flexible member. The length is set to be longer than the pitch circumference constituted by the inter-axle distance C and the pitch diameters D _P3 and D _{P4 of the} toothed drive wheels for both drives.

Further, in the solution means of the invention according to claim (2), one of the pair of movable idlers is connected to the constant pressure linear motion device, and the other movable idler presses the drive synchronous endless flexible member. Connected to the biasing spring member.

Further, the solution means of the invention according to claim (3) is a torque detecting means for detecting the load torque of the driven shaft, and an output signal of the torque detecting means so that the load torque of the driven shaft becomes constant. And a control means for controlling the operation of the constant pressure direct acting device.

Further, the solution means of the invention according to claim (4) is that a fixed idler for winding the belt around at least one span of the drive synchronous endless flexible member is a drive synchronous endless flexible member wound around a movable idler. The spans on both sides of the member are arranged parallel to each other, and the constant pressure linear motion device is arranged such that the slide shaft is parallel to the spans on both sides of the movable idler.

Further, in the solution means of the invention according to claim (5), the constant pressure direct acting device is constituted by an air cylinder or a hydraulic cylinder.

(Operation) With the above configuration, in the invention of claim (1),
By operating one constant pressure linear drive device and pressing one span of the drive toothed transmission wheel with one movable idler, the slack of the drive synchronous endless flexible member is eliminated,
Then, the test synchronous endless flexible member is wound between the first and second test toothed transmission wheels, and a predetermined initial tension is applied to the test synchronous endless flexible member, and then the drive synchronous endless flexible member is applied. In order to give a small tension on the loose side so that the flexible member does not jump during running, one of the above-mentioned constant pressure linear motion devices is actuated, and one movable idler causes the span of one end of the synchronous endless flexible member for driving. Is pressed with a predetermined force. Finally, when the other constant pressure linear motion device is operated and the other movable idler presses the other span of the drive synchronous endless flexible member with a force larger than the force on the one span, the drive shaft and the driven shaft are driven. Try to rotate in opposite directions to each other, but both shafts are in a state in which the rotation is restricted by the test synchronous endless flexible member, so a load is generated in the transmission system according to the above force, and this load causes a test Tension is generated on each side span of the synchronous endless flexible member. At this time, the one movable idler is pushed back according to the displacement of the other movable idler, but the holding force does not change. Then, by driving the drive device to rotate the drive shaft, the test synchronous endless flexible member is run to perform the test.

In this case, even if the test synchronous endless flexible member is stretched during the running test, the other movable idler moves to one side by the amount of the stretch, and at the same time, one movable idler is pushed back. The pressing force applied to the synchronous endless flexible member does not change at all. Therefore, even if the running test is performed for a long time, it is possible to suppress the decrease in load as much as possible.

For this reason, it is not necessary to reset the torque flange, torsion bar, etc. during the running test, or to set the torque flange, torsion bar, etc. according to the magnitude of the spring constant load on the torque flange, torsion bar, etc. Is also easy to operate,
Therefore, the operability of the testing machine can be improved.

Further, since the load can be applied to the test synchronous endless flexible member even while the test machine is operating, it is possible to perform a test such as a tooth jump torque measurement test in which the load is continuously changed during running.

In the invention according to claim (2), one of the pair of movable idlers is connected to the constant pressure device, and the other movable idler is a spring for urging the driving synchronous endless flexible member so as to press the member. By connecting to the member, even if the test synchronous endless flexible member stretches during running, the fluctuation of the load can be absorbed by the spring member, and one of the constant pressure direct acting devices can be replaced with the spring member, Therefore, it is possible to simplify the device configuration of the tester and reduce the cost.

Further, in the invention according to claim (3), the torque detecting means detects the load torque of the driven shaft, and the control means controls the operation of the constant pressure direct acting device so that the load torque becomes constant. Therefore, the load can be accurately stabilized.

Further, in the invention according to claim (4), a fixed idler for winding the endless flexible member around at least one span of the synchronous endless flexible member for driving, a synchronous endless flexible member for driving which is wound around a movable idler. When the load is set by installing the constant pressure direct acting device so that its slide shaft is parallel to the span on both sides of the movable idler, When the pressure linear motion device is operated to pull one movable idler with a predetermined force and the other movable idler with a force larger than the one movable idler, the driving synchronous endless flexible member is pulled. Since the acting direction and the direction of the endless flexible member spans on both sides of the movable idler are parallel to each other, a half of the above force is generated on each side span of the drive synchronous endless flexible member. From this, the load generated on the drive shaft can be obtained, and thus the load generated by the constant pressure linear motion device can be easily obtained. Even if the test synchronous endless flexible member stretches, both movable idlers move only in parallel with the span of the endless flexible member, and the tensile force on the endless flexible member does not change, so the load is reduced. Does not occur. Therefore, it is possible to set a load and to stabilize the load with high accuracy without requiring a torque meter or other device.

(Example) Hereinafter, the Example of this invention is described based on drawing.

FIG. 1 shows a schematic structure of a timing belt running tester A according to a first embodiment of the present invention, and the basic structure of this tester A is that shown in FIG. 8 (FIGS. 10 and 11). Therefore, the same parts as those in FIG.

That is, the drive shaft 1 and the driven shaft 2 are rotatably supported by being arranged in parallel with each other at an inter-axis distance C in a horizontal plane, and a V pulley 11 is rotatably attached to the base end of the drive shaft 1. A V-belt 9 is wound around the pulley 11 and a V-pulley 10 attached to an output shaft 8a of an electric motor 8 as a driving device, and the drive shaft 1 includes both V-pulleys 10 and 11 and a V-belt. It is drivingly connected to the electric motor 8 via 9. The drive shaft 1 and the driven shaft 2 are switched between the drive side and the driven side depending on the direction of the load and the rotation direction of the shaft. For convenience, the side linked to the motor 8 is the drive shaft 1 and the other side is the driven shaft 2. And Further, the motor 8 may be directly connected to the drive shaft 1.

A first test timing pulley 3 having a pitch diameter D _P1 is attached to the tip end of the drive shaft 1, and a first drive timing pulley 4 having a pitch diameter D _P3 is attached to the base end portion so as to rotate integrally. Has been.

On the other hand, a second test timing pulley 5 having a pitch diameter D _P2 is provided at the tip of the driven shaft 2, and a second drive timing pulley 6 having a pitch diameter D _P4 is provided at the base end portion.
Are mounted integrally with each other. A driving timing belt 7 having a pitch length L _P is wound between the first and second driving timing pulleys 4 and 6, and is provided between the first and second testing timing pulleys 3 and 5. A test timing belt B to be tested can be wound around.

Further, air cylinders 17 and 18 as constant pressure direct acting devices are immovably fixed to the upper and lower sides of the drive timing belt 7 wound between the first and second drive timing pulleys 4 and 6, respectively. The upper cylinder 17 has a pressure chamber 17b defined by a piston 17a and a piston rod 17c that is integrally connected to the piston 17a and that can extend vertically downward, and the tip (lower end) of the piston rod 17c. ) Is rotatably supported by an upper movable idler pulley 19 composed of a flat pulley that abuts the back surface of the upper span 7a of the driving timing belt 7, and the movable idler pulley 19 is moved downward by the extension operation of the upper cylinder 17. It is configured to slide and press the back surface of the upper span 7a of the driving timing belt 7.

On the other hand, the lower cylinder 18 is integrally connected to a pressure chamber 18b defined by a piston 18a and the piston 18a, and a piston rod 18 that can extend vertically upward.
and a lower movable idler pulley 20 which is a flat pulley that abuts against the rear surface of the lower span 7b of the drive timing belt 7 at the tip (upper end) of the piston rod 18c.
Is rotatably supported, and the movable idler pulley 20 is slid upward by the extension operation of the upper cylinder 18 to press the back surface of the lower span 7b of the drive timing belt 7.

The pitch diameters D _{P1 to} D _P4 of the timing pulleys _3, 5, _{4, 6} are set to D _P1 / D _P2 = D _P3 / D _P4 . Also, each timing pulley 3, 5,
4, 6 pitch diameters D _{P1 to} D _P4 , drive shaft 1 and driven shaft 2
Relationship center distance C and pitch length _{L P} of the driving timing belt 7 and is set to _{L P> 2C + π (D} P3 + D P4) / 2 + (D P3 -D P4) 2 / 4C .

Next, a case where the traveling test of the timing belt B is performed using the above-mentioned testing machine A will be described with reference to FIG.

First, as shown in FIG. 2 (a), before the test timing belt B is hung, the distance between the drive shaft 1 and the driven shaft 2 is shortened, and the lower air cylinder 18 (constant pressure linear motion) is set. Device) to supply pressurized air to the pressure chamber 18b of the cylinder 18
Is extended to push up the lower span 7b of the drive timing belt 7 by the lower movable idler pulley 20, and in that state, the air supply to the pressure chamber 18b of the cylinder 18 is stopped and the cylinder 18 is extended. Hold.
As a result, the slack of the driving timing belt 7 is offset and eliminated.

Next, as shown in FIG. 2B, the timing belt B to be tested is wound around the first and second test timing pulleys 3 and 5, and the axial distance between the drive shaft 1 and the driven shaft 2 is set. Set the value to C. As a result, a predetermined initial tension T ₀ is applied to the test timing belt B.

Further, as shown in FIG. 3C, the lower air cylinder 1
8 is extended so that the lower movable idler pulley 20 causes the lower span 7b of the driving timing belt 7 to move.
Is pushed up with a predetermined force ΔF. This force ΔF gives a small tension on the loosening side so that the driving timing belt 7 does not cause tooth jumping during traveling, and a small force is sufficient.

Finally, as shown in FIG. 3D, the upper air cylinder 17
The compressed air is supplied to the pressure chamber 17b of the drive cylinder 17 to extend the cylinder 17, and the upper movable idler pulley 19 causes the upper span 7a of the drive timing belt 7 to move the force ΔF.
It is pushed down with a force F greater than. As a result, the drive shaft 1 tends to rotate in the clockwise direction when viewed from the tip side, and the driven shaft 2 tends to rotate in the counterclockwise direction.
Since No. 2 is in a state in which the rotation is restricted by the test timing belt B, a load is generated in the transmission system according to the force F, and this load causes tensions Ts and Ts on the upper and lower spans of the test timing belt B, respectively. Tt occurs. At this time, the lower movable idler pulley 20 is pushed back according to the displacement of the upper movable idler pulley 19, but the pressing force ΔF does not change.

After that, the electric motor 8 is operated in the above state to rotate the drive shaft 1 so that the test timing belt B is run and the test is performed.

Therefore, in the case of this embodiment, even if the test timing belt B is stretched during traveling, the upper movable idler pulley 19 is moved downward by the amount of the stretching, and at the same time, the lower movable idler pulley 20 is pushed back. And
The pressing force ΔF with respect to the belt 7 does not change at all, so that even if a running test is performed for a long time, the reduction in load can be suppressed as much as possible.

In addition, since the decrease in load is suppressed in this way, it is not necessary to reset the torque flange, torsion bar, etc., and to set the spring constant of the torque flange, torsion bar, etc. according to the magnitude of the load. The operation before the start is also easy, so that the operability of the testing machine A can be improved.

Further, since the load is applied to the belt B even when the tester A is operating, it is possible to perform a test such as a tooth jump torque measurement test in which the load is continuously changed while the belt is running.

In the above embodiment, the spans 7a and 7b of the drive timing belt 7 wound around the drive timing pulleys 4 and 6 are pressed by the movable idler pulleys 19 and 20 driven by the air cylinders 17 and 18, respectively. However, one of the movable idler pulleys 19 and 20 is connected to an air cylinder as a constant pressure direct acting device, and the other movable idler pulley 20 (or 19). May be connected to a spring member that urges the driving timing belt 7 to press it. For example, the lower movable idler pulley 20
Is coupled to the spring member, the force ΔF that pushes up the lower span 7a of the drive timing belt 7 via the lower movable idler pulley 20 may be small, as described above, so the spring constant of the spring member is low. can do.
Then, the lower movable idler pulley 20 is pushed back due to the elongation of the test belt B during traveling, but since the spring constant of the spring member is low, the load of the test belt B hardly changes.

FIG. 3 shows a second embodiment of the present invention (the same parts as those in FIG. 1 are designated by the same reference numerals and detailed description thereof will be omitted), and the load applied to the test timing belt B is automatically determined. The adjustment is made to.

That is, in this embodiment, the driven shaft 2 is provided with the torque meter 21 as a detecting means for detecting the load torque thereof. The output signal of the torque meter 21 is compared in the comparator 22 with the load torque set by the torque setting device 23 including a volume, and the signal of the difference is amplified by the amplifier 24 to generate the pressure chamber 18b of the lower air cylinder 18. Is output to the air pressure converter 25 for adjusting the air pressure supplied to the. Therefore, by the comparator 22, the torque setting device 23, the amplifier 24 and the pneumatic converter 25,
The pneumatic converter 25 receives the output signal of the torque meter 21 so that the load torque of the driven shaft 2 detected by the torque meter 21 becomes the set load torque by the torque setter 23 (so that the difference between the two becomes zero). The control device 26 is configured to control the pressure in the pressure chamber 18b of the lower air cylinder 18 and adjust the pressing force of the lower movable idler pulley 20 against the lower span 7b of the drive timing belt 7. There is.

Therefore, in this embodiment, the torque meter 21 detects a change in the load, and the air pressure to the pressure chamber 18b of the lower air cylinder 18 is controlled so that the difference between the load and the load set by the torque setter 23 is eliminated. Since the load is corrected to be constant, the load on the test belt B can be accurately stabilized.

Further, FIG. 4 shows a third embodiment of the present invention, and
The load can be set and the load can be stabilized with high accuracy without using the torque meter 21 and the control device 26 in the embodiment.

In this embodiment, one fixed idler pulley 27, 28, which is a flat pulley, is rotatably supported by spans 7a, 7b on the upper and lower sides of the driving timing belt 7, respectively.
The upper and lower spans 7a and 7b of the belt 7 are wound around the idler pulleys 27 and 28, respectively.

The position of the upper fixed idler pulley 27 is arranged such that the driving timing belt 7 is wound around the upper movable idler pulley 19 'which is a timing pulley axially supported by the tip of the piston rod 17c' of the upper air cylinder 17 '.
Both side spans 7c and 7d, that is, the span 7c located between the upper movable idler pulley 19 'and the first drive timing pulley 4 on the drive shaft 1 in the drive timing belt 7, and the upper movable idler pulley 19'. And the span 7d located between the upper fixed idler pulley 27
And are set to be parallel to each other.

On the other hand, the arrangement position of the lower fixed idler pulley 28 is such that the driving timing belt 7 wound around the lower movable idler pulley 20 ', which is a timing pulley pivotally supported at the tip of the piston rod 18c' of the lower air cylinder 18 '. Both side spans 7e and 7f, that is, the lower movable idler pulley 20 'and the driven shaft 2 in the driving timing belt 7
The span 7e located between the upper second driving timing pulley 6 and the span 7f located between the lower movable pulley 20 'and the lower fixed idler pulley 28 are set to be parallel to each other. ing.

Further, the upper and lower air cylinders 17 ', 18' constituting the constant pressure direct acting device are supplied with the pressurized air to the pressure chambers 17b ', 18b', so that the piston rods 17c ', 18'.
In the upper air cylinder 17 ', a slide shaft, which is a contraction type in which c'is depressed, and which is the expansion and contraction direction of the piston rod 17c', has the upper movable idler pulley 1 described above.
9'so as to be parallel to the spans 7c, 7d of the belt 7 on both sides, and in the lower air cylinder 18 ', similarly, the slide shaft, which is the expansion / contraction direction of the piston rod 18c', has both sides of the lower movable idler pulley 20 '. Belt 7 span 7
It is arranged so as to be parallel to e and 7f.

Therefore, in this embodiment, when the load is set, the pressure chambers 17b 'and 18b' of the air cylinders 17 'and 18' are set.
By supplying pressurized air to the air cylinders 17 ', 1
When 8'is contracted and the driving timing belt 7 is pulled by the upper movable idler pulley 19 'with a force of ΔF and the lower movable idler pulley 20' with a force of F, the forces ΔF and F act. Direction and movable idler pulleys 19 ', 20' Belt spans 7c, 7d, 7 on both sides
Since it is parallel to the directions of e and 7f, a tension of ΔF / 2 is generated on the upper span 7a of the drive timing belt 7 and a tension of F / 2 is generated on the lower span 7b. From this, the drive shaft 1 has D _P3 · (F−ΔF) / 4
(However, D _P3 is a pitch diameter of the first drive timing pulley 4), and a load generated by the air pressure acting on the air cylinders 17 ′ and 18 ′ can be easily obtained.

Even if the test timing belt B is stretched, the movable idler pulleys 19 'and 20' only move in parallel with the belt spans 7c to 7f, and the tensile forces ΔF and F on the belt 7 do not change. Therefore, there is an advantage that the load can be set and the load can be accurately stabilized without the need for a torque meter and other devices.

In the configuration of the third embodiment, the fixed idler pulleys 27 and 28 may be provided on either one of the upper and lower spans 7a and 7b of the drive timing belt 7 instead of being provided on either of them. . Further, the fixed idler pulley is one of the upper and lower spans 7a (or 7) of the drive timing belt 7.
There may be two or more in b).

That is, FIGS. 5 to 7 specifically show the third embodiment, and 31 is a fixed frame, on the upper surface of which a drive shaft mounting base 32 and a driven shaft mounting base 33 are spaced from each other by a predetermined distance. The drive shaft mounting base 3 which is arranged to face each other
2, the drive shaft 1 is provided with bearings 32a and 32a, and the driven shaft mounting base 33 is provided with the driven shaft 2 and bearings 33a and 33a.
Each is rotatably supported via. And
The driven shaft mounting base 33 is slidably supported on the frame 31 so as to come into contact with and separate from the drive shaft mounting substrate 32. Then, on the frame 31, both boards 32, 3
Two feed screws 3 extending parallel to each other in the direction passing through 3.
4, 35 are rotatably and non-slidingly supported, and the driven shaft mounting bases 33 are screwed together. The two feed screws 34 and 35 are drivingly connected to each other by a chain 36 so as to rotate integrally with each other.
Handles 37 and 38 are attached to one end of 35, and by operating either one of the handles 37 and 38 to slide the driven shaft mounting base 33 with the feed screws 34 and 35, The driven shaft 2 is brought into contact with and separated from the drive shaft 1 in parallel to adjust the distance between the shafts 1 and 2.

A first drive timing pulley 4 is provided at the base end (lower end in FIG. 5) of the drive shaft 1, and a first drive timing pulley 4 is provided at the front end (the same upper end).
The test timing pulley 3 is attached to the test timing pulley 3, and the V pulley 11 is attached to an intermediate portion near the first test timing pulley 3. A second drive timing pulley 6 is provided at the base end (lower end in FIG. 5) of the driven shaft 2.
However, the second test timing pulley 5 is attached to the tip (the same upper end). An intermediate board 39 is mounted inside the frame 31, and an electric motor 8 is installed on the intermediate board 39.
A V-belt 9 is stretched between the V-pulley 10 on the output shaft 8a and the V-pulley 11 on the drive shaft 1.

A cylinder mounting base 40 whose upper end extends upwardly from the upper surface of the frame 31 is integrally attached to the rear side (lower side in FIG. 5) of the frame 31, and a vertical vertical slide is provided on the lower end of the base 40. A lower air cylinder 18 'having a shaft is directly fixed, and a lower movable idler pulley 20' is rotatably supported at the tip (upper end) of a piston rod 18c 'of the cylinder 18'. On the other hand, a feed screw 41 extending vertically is provided on the upper portion of the cylinder mounting base 40.
Is rotatably supported by turning the handle 42,
An upper air cylinder 17 'is supported on the lower end of the feed screw 41, and an upper movable idler pulley 19' is rotatably supported on the tip (lower end) of a piston rod 17c 'of the cylinder 17'.

Further, a pair of upper fixed idler pulleys 27, 29 and a pair of lower fixed idler pulleys 28, 30 are rotatably attached to the cylinder mounting base 40, respectively. And these four fixed idler pulleys 27, 2
As described above, the mounting positions and directions of the air cylinders 17 'and 18' are set to the piston rods 17c '(or 18c') of the air cylinder 17 '(or 18').
Both spans 7c of the drive timing belt 7 wound around the movable idler pulley 19 '(or 20') at the tip,
It is set so that 7d (or 7e, 7f) are parallel to each other, and the slide axis of the air cylinder 17 '(or 18') is parallel to both spans 7c, 7d (or 7e, 7f). .

Reference numeral 43 denotes a limit switch mounted on the lower side of the lower movable idler pulley 20 'on the cylinder mounting base 40, which comes into contact with the lower idler switch 20' when the lower idler switch 20 'is moved downward so as to be turned ON, and the motor 8 Is to stop. In the figure, 44 is a pneumatic pipe.

Therefore, in the case of this modification, the four fixed idler pulleys 27, 29, 28, 30 and the air cylinders 17 ', 1
Each 8'mounting position and direction indicates the movable idler pulley 1
Both spans 7c, 7d (or 7e, 7f) of the drive timing belt 7 wound around 9 '(or 20') are parallel to each other, and both spans 7c, 7d (or 7
e, 7f) and the slide shaft of the air cylinder 17 '(or 18') are set to be parallel,
The load can be set easily, and a stable load can be applied even when the test timing belt B is run for a long time.

Further, since the upper air cylinder 17 ′ is supported by the lower end of the feed screw 41, the upper air cylinder 17 ′ is moved up and down by screwing the feed screw 41 only by operating the handle 42. Therefore, 1
With the book drive timing belt 7, the running test of the belt B can be performed by changing the distance between the axes to a wide range, and the immersiveness can be improved.

Furthermore, when the test timing belt B is cut or causes tooth jumps during the load endurance test, the pressure balance between the upper and lower air cylinders 17 'and 18' is disturbed, so that the lower air cylinder is broken. 18 '
The lower movable idler pulley 20 'of the tip of the piston rod 18c' is lowered. The limit switch 43 is turned on by this downward movement, the motor 8 is stopped, and the traveling of the belt B is stopped. That is, by simply attaching the limit switch 43, the traveling of the belt B can be immediately stopped in the event of an abnormality.

In the above embodiment, the constant pressure linear drive device for driving the drive idler pulleys 19, 20 is the air cylinders 17, 18, but hydraulic cylinders may be used.

As the constant pressure direct acting device, a movable idler pulley 1 is used.
Since it is sufficient that the force for directly moving 9 and 20 is constant irrespective of the movement amount, it is possible to apply a load by gravity acting on the weight instead of the cylinder as described above. That is, for example, in the configuration of the third embodiment, the movable idler pulleys 19 'and 20' are attached to the cylinder 1
Instead of connecting to 7'and 18 ', the idler pulleys 19' and 20 'can be slid vertically, one end of a wire or rope can be connected to it, and a weight can be attached to the other end of the wire or the like. . In that case, by changing the weight of the weight connected to one of the movable idler pulleys 19 '(or 20'), the timing belt for test B
It is possible to change the load applied to the. Further, the other movable idler pulley 20 '(or 19') may be connected to a lightweight weight because it suffices to press the belt 7 with a force small enough to prevent tooth jumping of the driving timing belt 7. As a result of using the weight as the constant pressure linear motion device in this way, there is an advantage that the manufacturing cost of the testing machine can be further reduced while satisfying the function equivalent to that of the cylinder.

Further, the drive side pulleys 4, 6, in each of the above embodiments
19, 20, and 27 to 30 may be replaced with sprockets, and the timing belt 7 may be replaced with a chain, and the same effect can be obtained.

Further, although each of the above-described embodiments is an example of a testing machine for carrying out a running test of the timing belt B, the present invention is also applied to a running testing machine of not only the timing belt B but also all synchronous transmission members such as chains and gears. be able to. For example, when a sprocket is attached instead of the first and second test timing pulleys, a chain can be hung between the two sprockets to perform the running test. In addition, when conducting a running test of a gear device such as an automobile transmission or differential gear, use the test timing pulley and belt as the drive timing pulley and belt, and attach the gear device to the drive shaft or driven shaft or both shafts. Good.

Lastly, when a running tester (see FIGS. 5 to 7) having a device configuration of the modified example of the third embodiment is manufactured and a running test of the timing belt is performed, the same load condition is given. Compared to the power absorption type running test machine, the production cost is about 1
The power consumption per hour was reduced to about 1/20, and the power consumption per hour was reduced to about 1/20.

Also, by adjusting the pressure of the pressurized air supplied to the pressure chambers of the air cylinders on both the upper and lower sides with the pressure reducing valve, a load can be easily applied to the test timing belt, and further, the load can be continuously applied. I was able to change.

When a load durability running test was performed by applying a load torque of 20 kg · m to the test timing belt, the load fluctuation after 100 hours was about ± 2% (for evaluation of the tester, The test was carried out by attaching a torque meter to the driven shaft).

Further, even when the same test was conducted by replacing the driving timing pulley, the movable and fixed idler pulleys with sprockets, and the driving timing belt with chains, the same performance as above could be evaluated. Therefore, it was found that the running tester of the present invention example can surely obtain the above effects.

(Effect of the invention) As described above, according to the invention of claim (1),
A pitch diameter D is provided at one end of a drive shaft drivingly connected to the drive device.
The first test toothed drive wheel of _P1 has a pitch diameter D at the other end.
_While the first drive toothed transmission wheel of _P3 is mounted integrally with each other while rotating, the second test toothed drive wheel of pitch diameter D _P2 is provided at one end of the driven shaft parallel to the drive shaft, and the pitch diameter is provided at the other end. D
A second drive toothed transmission wheel of _P4 is attached to each of them so as to rotate together, and a test synchronous endless flexible member is provided between both test toothed transmission wheels, and a drive synchronous endless flexible member is provided between both drive toothed transmission wheels. And a pair of movable idlers which are slidable linearly in the span between the driving synchronous endless drive wheels of the driving synchronous endless flexible member. A constant pressure linear motion device for slidingly moving the flexible member is provided, and the relationship between the pitch diameters D _{P1 to} D _P4 of the toothed transmission wheel is D _P1 / D _P2 =
D _P3 / D _P4 and the pitch of the driving synchronous endless flexible member is defined by the axial distance between the drive shaft and the driven shaft and the pitch diameters D _P3 and D _{P4 of} both drive toothed transmissions. By setting the length longer than the circumference, it is possible to obtain a complete power circulation type traveling tester that applies loads of different magnitudes simultaneously to both spans of the synchronous endless flexible member for driving to generate a load,
Large-scale motors and load devices can significantly reduce the manufacturing cost of the running tester compared to the power absorption type and incomplete power circulation type, and can also reduce the power consumption during the test, which is particularly large. It is possible to exert a remarkable effect on a running tester that requires load conditions. In addition, the setting of the load can be facilitated and the operability can be greatly improved, the stability of the load can be improved, and the setting is not necessary even if the synchronous endless flexible member is run for a long time. In addition, since the load can be continuously changed, it can be used for a tooth jump torque measurement test and the like, and has a practically excellent effect of improving versatility.

According to the invention of claim (2), the one movable idler is connected to the constant pressure linear motion device, and the other movable idler is a spring member for urging the driving synchronous endless flexible member so as to press the same. Even if the test synchronous endless flexible member is stretched during running, the load fluctuation can be absorbed by the spring member, so that the spring member of the constant pressure direct acting device can be replaced by the spring member of the testing machine. It is possible to achieve simplification and cost reduction.

Furthermore, according to the invention of claim (3), the load torque of the driven shaft is detected so that the load torque becomes constant,
By controlling the pressure of the constant pressure direct acting device, the load can be stabilized with high accuracy.

Further, according to the invention of claim (4), a fixed idler for winding the endless flexible member around at least one span of the drive synchronous endless flexible member is provided with a drive synchronous endless flexible member wound around a movable idler. The torque meter and other devices are installed by arranging the spans on both sides of the member to be parallel to each other and by arranging the constant pressure linear motion device so that the slide shaft is parallel to the spans on both sides of the movable idler. It is possible to set the load and maintain the load with high accuracy and stability without the need.

[Brief description of drawings]

1 and 2 show a first embodiment of the present invention, FIG. 1 is a perspective view schematically showing a schematic configuration of a running tester, and FIG. 2 is an explanatory diagram showing a procedure for using the tester. Is. FIG. 3 corresponds to FIG. 1 showing the second embodiment. 4 to 7 show a third embodiment, FIG. 4 is a view corresponding to FIG. 1, FIG. 5 is a plan view showing a concrete structure of a running tester in a modification thereof, and FIG. The rear view and FIG. 7 are left side views.
8 to 11 are views corresponding to FIG. 1 showing a conventional example. A: Running tester, 1 ... Drive shaft, 2 ... Driven shaft, 3 ...
... first test timing pulley, 4 ... first drive timing pulley, 5 ... second test timing pulley, 6 ... second drive timing pulley, 7 ... drive timing belt, 7a to 7f ... Span, 8 ... Electric motor (driving device), 17, 17 '... Upper air cylinder (constant pressure direct acting device), 18, 18' ... Lower air cylinder (constant pressure direct acting device) ), 19, 19 '... upper movable idler pulley, 20, 20' ... lower movable idler pulley, 21 ... torque meter (torque detecting means), 26
...... Control device, 27,29 ...... Upper fixed idler pulley, 28,30 ...... Lower fixed idler pulley, C …… Axial distance, D _{P1 to} D _P4 …… Pitch diameter, L _P …… Pitch length , B …… Timing belt for testing.

Claims (5)

[Claims] 1. A drive shaft drivingly connected to a drive device, a driven shaft arranged in parallel with the drive shaft, and a first test toothed transmission rotatably attached to one end of the drive shaft. A wheel, a first drive toothed transmission wheel that is attached to the drive shaft at the other end of the drive shaft, and a first drive toothed transmission wheel that is attached to the drive shaft at one end of the drive shaft so as to rotate together.
The second test toothed transmission wheel in which the test synchronous endless flexible member meshes with and is wound around the test toothed transmission wheel of No. 2, and the second test toothed transmission wheel that is attached to the other end of the driven shaft so as to rotate integrally therewith. Drive toothed drive wheel, the drive synchronous endless flexible member that is meshed and wound between the first and second drive toothed drive wheels, and both of the drive synchronous endless flexible members. A pair of movable idlers respectively arranged in the span between the drive toothed transmission wheels, and a constant pressure straight line for linearly sliding the movable idlers so as to press the span of the drive synchronous endless flexible member. The first test toothed transmission wheel has a pitch diameter of D _P1 and a second test gear.
Of the test toothed transmission wheel of D _P2 , the pitch diameter of the first driving toothed transmission wheel of D _P3 , the pitch diameter of the second driving toothed transmission wheel of D _P4 , the drive and driven shafts The distance between them is C,
D _P1 / D _P2 = D _P3 / D _P4 , and L _P > 2C + π (D _P3 + D _P4 ) / 2 + (D _P3 −D _P4 ) where _{P P} is the pitch length of the driving synchronous endless flexible member. ^The running tester for a synchronous endless flexible member, which is set to ² / 4C. 2. One of the movable idlers is connected to a constant pressure linear motion device, and the other movable idler is connected to a spring member for urging the driving synchronous endless flexible member to press it. The running tester for a synchronous endless flexible member according to claim (1). 3. A torque detecting means for detecting the load torque of the driven shaft, and a control means for receiving the output signal of the torque detecting means and controlling the operation of the constant pressure direct acting device so that the load torque of the driven shaft becomes constant. Claim (1) characterized in that and are provided
Alternatively, the running tester for the synchronous endless flexible member according to (2). 4. A fixed idler for winding the endless flexible member around at least one span of the drive synchronous endless flexible member, wherein both side spans of the drive synchronous endless flexible member wound around the movable idler are parallel to each other. Is arranged so that
The constant pressure direct acting device is characterized in that the slide shaft is arranged so as to be parallel to the spans on both sides of the movable idler, according to claim (1), (2) or (3). Running tester for components. 5. The traveling for synchronous endless flexible member according to claim 1, wherein the constant pressure linear motion device is an air cylinder or a hydraulic cylinder. testing machine.