JP2016045013A - Friction test device for two circular cylinders - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a friction test device for two circular cylinders capable of highly accurately estimating a contact fatigue strength of a tooth flank of the gear of a pair of gears.SOLUTION: A friction test device 1 for two circular cylinders includes: a first sample circular cylinder 2 having a true circle; a first drive motor 24 for rotationally driving the first sample circular cylinder 2; a second sample circular cylinder 3 having the true circle and arranged to face each other so as to be in parallel with a shaft center of the first sample circular cylinder 2; a second drive motor 34 for rotationally driving the second sample circular cylinder 3; and motor controllers (26, 36) for causing the second drive motor 34 to rotate with a constant velocity (V) in a state that the outer peripheral surfaces of the first and second sample circular cylinders are brought into contact with each other and causing the rotational velocity of the first drive motor 24 to be changed so as to become a sine wave shape pattern (V) )while the first sample circular cylinder 2 and the second sample circular cylinder 3 rotate once.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a test apparatus that evaluates the contact fatigue strength of gear tooth surfaces of a gear pair, and more particularly, to a two-cylinder friction test apparatus that simulates sliding of tooth surfaces by contacting and rotating two cylinders.

  The evaluation on the contact fatigue strength of the gear tooth surface is roughly divided into a case where it is performed with an actual gear using a gear testing device and a case where a gear cylinder is simulated using a two-cylinder friction test device. Here, the two-cylinder friction test apparatus is an element test apparatus that has a structure in which two cylinders are brought into rolling and sliding contact and simulates sliding of a tooth surface. There are many advantages over the gear test in terms of simplicity of experimentation and evaluation, and the production cost of the test apparatus main body and specimen.

  For example, Patent Document 1 is known as a two-cylinder friction test apparatus. In Patent Document 1, a first roll (eccentric roll) in which the first test material is pasted on a part of the outer peripheral surface, the first roll and the axial center are arranged so as to face each other, and the first roll is formed on a part of the outer peripheral surface. 2 A second roll (circular roll) on which the test material is pasted, a first motor that rotationally drives the first roll, and a second motor that rotationally drives the second roll are provided, and the first roll and the second roll are respectively constant. A configuration is disclosed in which the friction coefficient between the first test material and the second test material is measured by rotating the first roll at a peripheral speed and making contact with the first roll at a peripheral speed slower than that of the second roll. The

JP 2006-126081 A

  However, in Patent Document 1, since the first roll and the second roll are each configured to rotate once at a constant different peripheral speed, the peripheral speed at the contact position between the gears changes during one rotation like a gear pair. It is difficult to simulate the gear pair to be performed with high accuracy. Moreover, in patent document 1, since the roll by which one test material is stuck is an eccentric roll, the area | region which contacts during one rotation of a 1st and 2nd roll is also restrict | limited.

  It is an object of the present invention to provide a two-cylinder friction test apparatus that can accurately evaluate the contact fatigue strength of the gear tooth surfaces of a gear pair.

  In order to solve the above problems, a two-cylinder friction test apparatus of the present invention includes a first test cylinder that is a perfect circular roll, a first drive motor that rotationally drives the first test cylinder, and the first test cylinder. A second round test cylinder of a round roll facing to be parallel to the axis of the cylinder, a second drive motor for rotationally driving the two test cylinders, and outer peripheries of the first and second test cylinders A motor controller that rotates the second drive motor at a constant speed while keeping the surfaces in contact with each other and controls the rotation speed of the first drive motor to change while the second test cylinder rotates once. .

  The two-cylinder friction test apparatus of the present invention includes a first test cylinder, a first drive motor connected to a central axis of the first test cylinder, and driving the first test cylinder to rotate, and the first A second test cylinder that is parallel to the central axis of the first test cylinder and that is arranged in contact with the outer peripheral surface of the first test cylinder, and is connected to the central axis of the second test cylinder; A second drive motor that rotationally drives the second test cylinder, one of the first drive motor and the second drive motor is driven at a predetermined speed, and the other is driven by the first and second test cylinders. A motor controller that controls the rotational speed to change during one rotation and a load application mechanism for applying a predetermined contact pressure between the outer peripheral surfaces of the first test cylinder and the second test cylinder are provided.

  According to the present invention, since the contact state of the gear tooth surfaces of the gear pair can be simulated with high accuracy, a two-cylinder friction test apparatus capable of evaluating contact fatigue strength with high accuracy can be realized.

  For example, the slip ratio between two cylinders simulating a gear pair can be continuously changed, and the gear pair can be simulated with high accuracy.

  Further, according to the present invention, it is possible to evaluate the tooth surface strength in a state where there is no gear error with respect to all meshing tooth surface conditions.

  Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram of the two-cylinder friction test apparatus of Example 1 which concerns on one Example of this invention. It is a figure which shows the relationship between the contact position of the gear pair which mutually meshes, and a peripheral speed, a peripheral speed difference, and a slip ratio, FIG. 2 (A) shows the change of the contact position of a gear pair, FIG. 2 (B) is a gear. FIG. 2 (C) shows the relationship between the peripheral speeds at the contact positions of each pair of gears, FIG. 2 (C) shows the relationship between the contact positions and the peripheral speed difference between the gear pairs, and FIG. 2 (D) shows the slip between the contact positions and the gear pairs. The relationship with the rate is shown. It is a figure which shows the rotational speed pattern of each motor in the two-cylinder friction test apparatus which concerns on one Embodiment of this invention, a sliding rate, and the load pattern added to a test cylinder, FIG. 3 (A) shows two test cylinders. 3B shows two motor rotation speed patterns, FIG. 3C shows the slip ratio at the contact position of the two test cylinders, and FIG. 3D adds the test cylinders to the test cylinder. The load pattern is shown. It is a whole block diagram of the two-cylinder friction test apparatus of Example 2 which concerns on the other Example of this invention.

  The relationship between the meshing state of the gear pair simulated by the two-cylinder friction test device according to one embodiment of the present invention and the slip ratio will be described. FIG. 2 shows the relationship between the contact position of the gear pair meshing with each other, the peripheral speed, the peripheral speed difference, and the slip ratio.

  As shown in FIG. 2A, the meshing state of the gear pair composed of the gear A and the gear B is such that the tooth surface tip portion of the gear A and the groove of the gear B are in contact at the contact position P1. For example, the state is the state at time t1. From time t1, the tooth surface of the gear A and the tooth surface of the gear B slide and come into contact at the contact position P2 (the central portion (hereinafter referred to as intermediate portion) between the tooth surface tip and the groove). For example, the contact state is a state at time t2. From time t2, the contact state of the meshing end plate in which the tooth surface of the gear A and the tooth surface of the gear B slide further and the groove of the gear A and the tooth surface tip of the gear B contact at the contact position P3 is, for example, The state at t3.

As shown in FIG. 2B, the peripheral speed V _A of the gear A at the contact position P1 at time t1 is larger than the peripheral speed V _B at the contact position P1 of the gear B. This is because the peripheral speed at the contact position of the tooth surface is proportional to the height position of the tooth surface. The state of V _A > V _B continues until reaching time t2, and from time t1 to time t2, V _A gradually decreases, while V _B gradually increases. At time t2, V _A and V _B at the contact position P2 are V _A = V _B. Between time t2 and time 3, a state of V _A <V _B is established.

FIG. 2 (C), the circumferential speed _{V A} of the gear A as a reference, shows a variation of the peripheral speed difference _(V A -V _B) from time t1 to time t3, FIG. 2 (D) gear A change in the slip ratio S (Sliding Ratio) from time t1 to time t3 with reference to the peripheral speed V _A of _A is shown. The slip ratio S based on the peripheral speed V _A is S = (V _A −V _B ) / _VA , and changes in a sine wave shape as shown in FIG.

  As a result of intensive efforts, the inventors can simulate the behavior of the slip rate S due to the gear pair shown in FIG. 2 by setting the rotational speed patterns of the two test cylinders as shown below. And gained knowledge. Hereinafter, the operation principle of the two-cylinder friction test apparatus according to an embodiment of the present invention will be described. FIG. 3 shows the rotational speed pattern of each motor, the slip ratio, and the load pattern added to the test cylinder. As shown in FIG. 3A, the two test cylinders according to the present embodiment, the first test cylinder 2 and the second test cylinder 3 are round rolls having the same radius. In the present specification, the perfect circle roll refers to a cylindrical roll whose cross section is a perfect circle and whose center of gravity and rigid center coincide with each other, that is, whose eccentricity is zero. Further, in FIG. 3A, the first test cylinder 2 and the second test cylinder 3 are always in contact at the same position on each perfect circle roll during one rotation. That is, as shown in FIG. 3 (A), the positions on the outer peripheral surface that are spaced apart by 90 ° in the rotation direction of the first test cylinder 2 are A to D, and similarly, the outer peripheral surface of the second test cylinder 3 When the upper position is changed from A ′ to D ′, the outer peripheral surfaces of the first test cylinder 2 and the second test cylinder 3 are AA ′, BB ′, CC ′ and DD. Always touch with '. As a result, a two-cylinder friction test device that simulates the tooth surface in a state where there is no gear error can be obtained for the conditions of all meshing tooth surfaces.

FIG. 3B shows a rotational speed pattern of the motor that rotationally drives the first sample cylinder 2 and the motor that rotationally drives the second sample cylinder 3 during one rotation. The second test cylinder 3 rotates at a constant rotation speed pattern V ₂ , and the first test cylinder 2 rotates at a sinusoidal rotation speed pattern V ₁ . At this time, the slip ratio S (S = (V ₂ −V) between the first test cylinder 2 and the second test cylinder 3 based on the rotation speed pattern V ₂ of the second test cylinder 3 rotating at a constant speed. ₁ ) / V ₂ ) changes in a sine wave shape as shown in FIG. As shown in FIG. 3 (B) and FIG. 3 (C), during the period in which the contact position shifts from AA ′ to BB ′, the first test cylinder 3 slips in the preceding direction, The slip rate S gradually decreases. The slip rate S is zero at the contact position BB ′. Thereafter, during the period in which the contact position shifts from BB ′ to CC ′, the slip direction changes to the direction in which the second test cylinder 3 precedes, and the slip ratio S gradually increases. In the period in which the contact position shifts from CC ′ to DD ′, the slip direction is the direction preceding the second test cylinder 3, but the slip ratio S gradually decreases, and the contact position D− The slip rate S is zero at D ′. In the period in which the contact position shifts from DD ′ to AA ′, the first test cylinder 2 changes again in the preceding direction, and the slip ratio S gradually increases to the contact position AA ′. The first test cylinder 2 and the second test cylinder 3 make one rotation. Thus, the change over time of the slip ratio S corresponding to the reverse period of the rotation period in which the contact position shown in FIG. 3C shifts from AA ′ to CC ′ is the gear shown in FIG. It can be seen that this corresponds to the time change of the slip ratio S in the period from the time t1 to the time t3 of the gear pair composed of A and the gear B. Note that by relative to the rotational speed pattern V ₂ shown in FIG. 3 (C) In the second test試円tube 3, shown in FIG. 2 (D), has a reverse pattern of the pattern of the time variation of the slip ratio S However, it can be seen that the slip rate S is the same as the pattern shown in FIG. 2D by using the rotational speed pattern V1 of the _first sample cylinder 2 as a reference in FIG. That is, the gear tooth surfaces of the gear pair can be simulated with high accuracy.

  Further, by applying (vibrating) a sinusoidal load pattern to the first test cylinder 2 and the second test cylinder 3 shown in FIG. It is possible to simulate the gear pair including the pressure with higher accuracy. That is, it is possible to evaluate the tooth surface strength in a state where there is no gear error under the condition of all meshing gears.

  In this embodiment, as shown in FIG. 3 (B), by setting the rotational speed pattern of the first test cylinder 2 and the second test cylinder 3, the gears as shown in FIG. 3 (C). By simulating the slip ratio in the pair, the gear pair can be simulated with high accuracy. Accordingly, it is not always necessary to apply the sinusoidal load pattern shown in FIG. 3D, but by applying the load pattern to the first test cylinder 2 and the second test cylinder 3, as described above, in the gear pair. Since the contact surface pressure can also be reproduced, it is desirable to have a configuration for applying a load pattern, and further, the accuracy of simulating the gear pair can be improved.

Further, in FIG. 3 (B), the rotational speed pattern V ₁ of the motor for rotating the first test試円tube 2 has been sinusoidal, not limited to this, trapezoidal, even triangular or square-wave pattern good. However, a sine wave shape is desirable. Similarly, the applied load pattern shown in FIG. 3D may be a trapezoidal, triangular, or rectangular pattern, but is preferably a sine wave.

  Moreover, although the 1st test cylinder 2 and the 2nd test cylinder 3 were made into the perfect circle roll of the same radius, it is good not only as this but a perfect circle roll from which a radius differs.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is an overall configuration diagram of a two-cylinder friction test apparatus according to a first embodiment of the present invention. As shown in FIG. 1, the two-cylinder friction test apparatus 1 of the present embodiment includes, for example, a first test cylinder 2 and a first drive motor that rotationally drive a first test cylinder 2 that are perfect circular rolls having the same radius. 24, controls the second test cylinder 3, which is arranged so as to be parallel to the axis of the first test cylinder 2, the second drive motor 34 which rotates the second test cylinder 3, and the first drive motor 24. A second motor controller 36 for controlling the first motor controller 26 and the second drive motor 34, a load applying mechanism 4 for applying a load to the first test cylinder 2 and the second test cylinder 3, and the first motor controller 26. The overall controller 5 that controls the second motor controller 36 and the load application mechanism 4 is provided.

  The first sample cylinder 2 is coaxial with the first sample cylinder shaft 21, and the first drive motor 24 side is rotatably supported by the first sample cylinder shaft bearings 22c, 22d and 22e. Further, the opposite side of the first drive motor 24 across the first test cylinder 2 is rotatably supported by first test cylinder shaft bearings 22a and 22b. The first sample cylindrical shaft bearings 22a and 22b are accommodated in the first sample cylindrical bearing housing 23a, and the first sample cylindrical shaft bearings 22c, 22d and 22e are accommodated in the first sample cylindrical bearing housing 23b. Has been. The first drive motor 24 is coaxial with the first sample cylinder 2 and is connected to the first sample cylinder shaft 21 via the first coupling 25. The first drive motor 24 is electrically connected to the first motor controller 26.

  On the other hand, the second test cylinder 3 is coaxial with the second test cylinder shaft 31, and the second drive motor 34 side is rotatably supported by second test cylinder shaft bearings 32a, 32b and 32e. . The opposite side of the second drive motor 34 across the second test cylinder 3 is rotatably supported by second test cylinder shaft bearings 32c and 32d. The second test cylindrical shaft bearings 32a, 32b and 32e are accommodated in the second test cylindrical shaft housing 33a, and the second test cylindrical shaft bearings 32c and 32d are accommodated in the second test cylinder bearing housing 33b. Has been. The second drive motor 34 is coaxial with the second sample cylinder 3 and is connected to the second sample cylinder shaft 31 via the second coupling 35. The second drive motor 34 is electrically connected to the second motor controller 36. Here, the second test cylinder bearing housings 33a and 33b and the second drive motor 34 are on a linear motion guide (not shown) that allows translation in the direction perpendicular to the second test cylinder 3 (vertical direction in FIG. 1). is set up.

  The load addition mechanism 4 is installed between a load addition cylinder 41 installed in a direction perpendicular to the axis of the second test cylinder 3, a tank 46 for storing working fluid, a first valve 42 and a second valve 44. The pump 43 for supplying the working fluid in the load application cylinder 41, the third valve 45 for collecting the working fluid supplied to the load application cylinder 41 and finished work to the tank 46, and the first valve 42. The load controller 47 adjusts the opening degree or opening / closing of the second valve 44 and the third valve 45.

Next, operation | movement of the two-cylinder friction test apparatus 1 of a present Example is demonstrated. The overall controller 5 transmits an activation command in synchronization with the first motor controller 26, the second motor controller 36, and the load controller 47. First motor controller 26 reads the motor rotation speed pattern V ₁ of the advance of the above stored in the memory not shown FIG. 3 (B) and the first drive motor 24 shown in FIG. 1, the motor speed pattern V _{1 (sinusoidal} The first drive motor 24 is controlled in accordance with the wavy rotational speed pattern. The second motor controller 36 reads the same manner previously memorized described above stored in not shown FIG. 3 (B) and the motor speed pattern V ₂ of the second drive motor 34 shown in FIG. 1, the motor speed pattern the second drive motor 34 in response to V ₂ controls to a constant speed. The first motor controller 26 and the second motor controller 36, for example, input the rotor position from encoders installed in the first drive motor 24 and the second drive motor 34, and the motor rotation speed patterns V ₁ and V _2. When the deviation amount is detected from the relationship between the time and the position corresponding to, the position information is output as a command value to the first drive motor 24 or the second drive motor 34 in which the deviation amount is detected.

  The first drive motor 24 rotates so that the rotational speed changes with time in a sinusoidal shape within the rotation period, and this rotational driving force is transmitted through the first coupling 25 and the first sample cylindrical shaft 21 to the first sample. The first test cylinder 2 is transmitted to the cylinder 2 and rotates. On the other hand, the second drive motor 34 rotates at a constant speed at a predetermined number of rotations within the rotation period, and this rotational driving force is supplied to the second test cylinder via the second coupling 35 and the second test cylinder shaft 31. 3, the second test cylinder 3 rotates while being in contact with the first test cylinder 2.

  Further, when the load controller 47 receives an activation command from the overall controller 5, the load controller 47 reads a load pattern (constant load) stored in advance in a memory (not shown), and corresponds to the read load, The first valve is opened and the pump 43 is started. The working fluid pumped from the tank 46 by the pump 43 is supplied to the load applying cylinder 41 via the second valve 44. As a result, a constant load is applied to the second test cylinder bearing housings 33a and 33b during the rotation period. Due to the constant load applied in synchronization with the activation of the first drive motor 24 and the second drive motor 34, the second cylindrical bearing housings 33a, 33b and the second drive motor 34 are moved on the linear motion guide. The first test cylinder 2 and the second test cylinder 3 are pressed toward the first test cylinder 2 and rotate while contacting with a contact surface pressure corresponding to a certain load. Thereby, the time change of the sine wave-like slip rate S shown in FIG. 3C is reproduced.

In this embodiment, the position control by the encoder has been described as an example. However, instead of the position control, speed control, that is, a speed command corresponding to the motor rotation speed patterns V ₁ and V ₂ may be output. .

Further, in the present embodiment describes the motor rotation speed pattern V ₁ of the first driving motor 24 for rotating the first test試円cylinder 2 a sinusoidal pattern as an example, not limited to this, trapezoidal, triangular A wavy or rectangular wave pattern may be used. Alternatively, the first sample cylinder 2 may be rotated at a constant speed, and the second sample cylinder 3 may be rotated in a sinusoidal rotation speed pattern.

In the present embodiment, the first motor controller 26, the second motor controller 36, and the load controller 47 store the motor rotation speed patterns V ₁ and V ₂ and a load pattern indicating a constant load in a memory (not shown) in advance. Although described as an example, it is not limited to this. For example, the overall controller 5 stores motor rotational speed patterns V ₁ and V ₂ and a load pattern in a memory (not shown) in advance, and the first motor controller is controlled by the overall controller 5 when the two-cylinder friction test apparatus 1 is started. 26, the motor rotation speed patterns V ₁ and V ₂ and the load pattern may be transmitted together with the start command in synchronization with the second motor controller 36 and the load controller 47.

  According to this embodiment, the slip ratio between the first test cylinder 2 and the second test cylinder 3 simulating the gear pair can be continuously changed, and the gear pair can be simulated with high accuracy. It becomes. As a result, the contact fatigue strength of the gear tooth surfaces of the gear pair can be evaluated with high accuracy. Further, according to the present embodiment, it is possible to evaluate the tooth surface strength in a state where there is no gear error with respect to all meshing tooth surface conditions.

  FIG. 4 shows an overall configuration diagram of a two-cylinder friction test apparatus of Example 2 according to another example of the present invention. The same components as those shown in FIG. 1 are denoted by the same reference numerals. In the first embodiment, the load pattern applied to the second test cylindrical bearing housings 33a and 33b is a constant load, whereas in the present embodiment, the load pattern that changes with time is added. .

  As shown in FIG. 4, the two-cylinder friction test apparatus 1 ′ of the present embodiment is, for example, a first drive that rotates the first test cylinder 2 and the first test cylinder 2 that are perfect circular rolls having the same radius. The motor 24, the second test cylinder 3 that is arranged so as to be parallel to the axis of the first test cylinder 2, the second drive motor 34 that rotates the second test cylinder 3, and the first drive motor 24 A first motor controller 26 for controlling, a second motor controller 36 for controlling the second drive motor 34, a load applying mechanism 4 for applying a load to the first test cylinder 2 and the second test cylinder 3, and a first motor controller 26, an overall controller 5 for controlling the second motor controller 36 and the load application mechanism 4 is provided.

  The first sample cylinder 2 is coaxial with the first sample cylinder shaft 21, and the first drive motor 24 side is rotatably supported by the first sample cylinder shaft bearings 22c, 22d and 22e. Further, the opposite side of the first drive motor 24 across the first test cylinder 2 is rotatably supported by first test cylinder shaft bearings 22a and 22b. The first sample cylindrical shaft bearings 22a and 22b are accommodated in the first sample cylindrical bearing housing 23a, and the first sample cylindrical shaft bearings 22c, 22d and 22e are accommodated in the first sample cylindrical bearing housing 23b. Has been. The first drive motor 24 is coaxial with the first sample cylinder 2 and is connected to the first sample cylinder shaft 21 via the first coupling 25. The first drive motor 24 is electrically connected to the first motor controller 26.

  On the other hand, the second test cylinder 3 is coaxial with the second test cylinder shaft 31, and the second drive motor 34 side is rotatably supported by second test cylinder shaft bearings 32a, 32b and 32e. . The opposite side of the second drive motor 34 across the second test cylinder 3 is rotatably supported by second test cylinder shaft bearings 32c and 32d. The second test cylindrical shaft bearings 32a, 32b and 32e are accommodated in the second test cylindrical shaft housing 33a, and the second test cylindrical shaft bearings 32c and 32d are accommodated in the second test cylinder bearing housing 33b. Has been. The second drive motor 34 is coaxial with the second sample cylinder 3 and is connected to the second sample cylinder shaft 31 via the second coupling 35. The second drive motor 34 is electrically connected to the second motor controller 36. Here, the second test cylinder bearing housings 33a and 33b and the second drive motor 34 are placed on a linear guide (not shown) that allows translation in the direction perpendicular to the second test cylinder 3 (vertical direction in FIG. 4). is set up.

  The load addition mechanism 4 is installed between a load addition cylinder 41 installed in a direction perpendicular to the axis of the second test cylinder 3, a tank 46 for storing working fluid, a first valve 42 and a second valve 44. The pump 43 for supplying the working fluid to the load adding cylinder 41, the working fluid supplied to the load adding cylinder 41 and finished work, or the first for recovering the working fluid to the tank 46 to reduce the load. 3 valve 45, and load controller 47 'which adjusts the opening degree or opening / closing of 1st valve 42, 2nd valve 44, and 3rd valve 45 is comprised.

Next, the operation of the two-cylinder friction test apparatus 1 ′ of this embodiment will be described. The overall controller 5 transmits an activation command in synchronization with the first motor controller 26, the second motor controller 36, and the load controller. First motor controller 26 reads the motor rotation speed pattern V ₁ of the advance of the above stored in the memory not shown FIG. 3 (B) and the first drive motor 24 shown in FIG. 4, the motor speed pattern V _{1 (sinusoidal} The first drive motor 24 is controlled in accordance with the wavy rotational speed pattern. The second motor controller 36 reads the same manner previously memorized described above stored in not shown FIG. 3 (B) and the motor speed pattern V ₂ of the second drive motor 34 shown in FIG. 1, the motor speed pattern the second drive motor 34 in response to V ₂ controls to a constant speed. The first motor controller 26 and the second motor controller, for example, input the position of the rotor from encoders installed in the first drive motor 24 and the second drive motor 34, and the motor rotation speed patterns V ₁ and V ₂ are input. When the deviation amount is detected from the relationship between the corresponding time and position, the position information is output as a command value to the first drive motor 24 or the second drive motor 34 from which the deviation amount is detected.

  The first drive motor 24 rotates so that the rotational speed changes with time in a sinusoidal shape within the rotation period, and this rotational driving force is transmitted through the first coupling 25 and the first sample cylindrical shaft 21 to the first sample. The first test cylinder 2 is transmitted to the cylinder 2 and rotates. On the other hand, the second drive motor 34 rotates at a constant speed at a predetermined number of rotations within the rotation period, and this rotational driving force is supplied to the second test cylinder via the second coupling 35 and the second test cylinder shaft 31. 3, the second test cylinder 3 rotates while being in contact with the first test cylinder 2.

  Further, as shown in FIG. 4, the two-cylinder friction test apparatus 1 ′ of the present embodiment stores, for example, in advance in a memory (not shown) in the load controller 47 ′ constituting the load applying mechanism 4 in FIG. When the load controller 47 ′ stores a sine wave load pattern and receives a start command from the overall controller 5, the load controller 47 ′ is sine in synchronization with the start of the first drive motor 24 and the second drive motor 34. Read the wavy load pattern. The load of the first valve 42 and the second valve 44 is changed every time so that a load changing with time corresponding to the read sinusoidal load pattern is added to the second cylindrical bearing housings 33a and 33b. The opening is adjusted, and the working fluid pumped up from the tank 46 by the pump 43 is supplied to the load adding cylinder 41, and the excess working fluid is controlled to be collected in the tank 46 by adjusting the opening of the third valve 45. To do.

As shown in FIG. 3 (A), a load that changes with time in a sine wave shape at a half cycle of the rotation cycle (one rotation) of the sine wave motor rotation speed pattern V ₁ , that is, twice the frequency, is applied. The cylinder 41 is added to the second cylindrical bearing housings 33a and 33b.

  Here, as shown in FIGS. 3 (A), 3 (B) and 3 (D), the load pattern in this example is the rotational speed of the first test cylinder 2 and the second test cylinder 3. The additional load becomes maximum at the contact positions AA ′, CC ′ and AA ′ (within the rotation cycle: within one rotation) where the difference is maximum. Further, the additional load is minimized at the contact positions B-B 'and D-D' where the difference in rotational speed between the first test cylinder 2 and the second test cylinder 3 is zero. This is because, in the gear pair simulated by the first test cylinder 2 and the second test cylinder 3, when the tip of the tooth surface of one gear and the groove of the other gear are in contact, the contact pressure of the tooth surface becomes maximum. This corresponds to the fact that the contact pressure of the tooth surface is minimized when both gears come into contact with each other at the intermediate portion of the tooth surface. Therefore, by adding the load pattern shown in FIG. 3D, it is possible to reproduce the time change of the contact surface pressure generated on the gear tooth surface.

  In the present embodiment, the load pattern has been described by taking a sinusoidal pattern as an example. However, the present invention is not limited to this, and a trapezoidal, triangular, or rectangular wave pattern may be used.

In the present embodiment, the first motor controller 26, the second motor controller 36, and the load controller 47 ′ have been described with reference to an example in which the motor rotation speed patterns V ₁ and V ₂ and the load pattern are stored in a memory (not shown) in advance. However, it is not limited to this. For example, the overall controller 5 stores the motor rotation speed patterns V ₁ and V ₂ and the load pattern in a memory (not shown) in advance, and the first motor from the overall controller 5 when the two-cylinder friction test apparatus 1 ′ is started. The motor rotation speed patterns V ₁ and V ₂ and the load pattern may be transmitted together with the start command in synchronization with the controller 26, the second motor controller 36, and the load controller 47 ′.

  According to the present embodiment, in addition to the effects of the first embodiment, the time variation of the contact surface pressure generated on the tooth surfaces of the gear pair can be reproduced. The temporal change of the contact surface pressure can also be reproduced, and the contact fatigue strength of the gear tooth surfaces of the gear pair can be evaluated with higher accuracy than in the first embodiment.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, it is possible to add, delete, and replace the configurations of other embodiments with respect to a part of the configurations of the embodiments.

DESCRIPTION OF SYMBOLS 1,1 '... Two-cylinder friction test apparatus 2 ... 1st test cylinder 3 ... 2nd test cylinder 4 ... Load addition mechanism 5 ... Overall controller 21 ... 1st test cylinder shaft 22a, 22b, 22c, 22d, 22e ... first test cylindrical shaft bearings 23a, 23b ... first test cylindrical bearing housing 24 ... first drive motor 25 ... first coupling 26 ... first motor controller 31 ... second test cylindrical shaft 32a, 32b, 32c, 32d, 32e ... second test cylinder shaft bearings 33a, 33b ... second test cylinder bearing housing 34 ... second drive motor 35 ... second coupling 36 ... second motor controller 41 ... load application Cylinder 42 ... first valve 43 ... pump 44 ... second valve 45 ... third valve 46 ... tanks 47, 47 '... load controller

Claims (14)

A first test cylinder which is a perfect circle roll;
A first drive motor for rotationally driving the first sample cylinder;
A second round test cylinder of a perfect circle roll arranged to face the axis of the first test cylinder;
A second drive motor for rotationally driving the second test cylinder;
While the outer peripheral surfaces of the first and second test cylinders are in contact with each other, the second drive motor is rotated at a constant speed, and the first drive motor is rotated while the second test cylinder rotates once. A two-cylinder friction test apparatus having a motor controller for controlling the rotation speed to change. The two-cylinder friction test apparatus according to claim 1,
The rotational speed of the first drive motor changes as a sinusoidal pattern for one cycle within a rotation cycle in which the second test cylinder rotates once. The two-cylinder friction test apparatus according to claim 1,
The rotation speed of the first drive motor is any one of a trapezoidal wave pattern, a triangular wave pattern, and a rectangular wave pattern for one period within a rotation period in which the second test cylinder rotates once. A two-cylinder friction test apparatus characterized by changing as described above. The two-cylinder friction test apparatus according to claim 2,
A two-cylinder friction test apparatus comprising a load applying mechanism for applying a predetermined contact pressure between outer peripheral surfaces of the first test cylinder and the second test cylinder. The two-cylinder friction test apparatus according to claim 4,
The load applying mechanism includes a cylinder for applying a load to the first test cylinder or the second test cylinder, a pump for supplying a working fluid to the cylinder, and a load controller for controlling the cylinder and the pump. Prepared,
The two-cylinder friction test apparatus, wherein the load controller controls the cylinder and the pump so as to apply a predetermined constant load. The two-cylinder friction test apparatus according to claim 4,
The load applying mechanism includes a cylinder for applying a load to the first test cylinder or the second cylinder, a pump for supplying a working fluid to the cylinder, and a load controller for controlling the cylinder and the pump,
The two-cylinder friction test apparatus, wherein the load controller controls the cylinder and the pump to add a sinusoidal pattern as a load pattern. The two-cylinder friction test apparatus according to claim 6,
The two-cylinder friction is characterized in that the load controller controls the cylinder and the pump so that the sine wave pattern for two cycles is added as a load pattern within a rotation cycle in which the second test cylinder rotates once. Test equipment. In the two-cylinder friction test apparatus according to claim 2 or 3,
The first test cylinder has a first test cylinder shaft that is a rotation axis of the first test cylinder, and is connected to the first drive motor via the first test cylinder shaft and a first coupling. Concatenated,
The second test cylinder has a second test cylinder shaft which is a rotation axis of the second test cylinder, and is connected to the second drive motor via the second test cylinder shaft and a second coupling. A two-cylindrical friction test apparatus characterized by being connected. A first test cylinder;
A first drive motor connected to a central axis of the first sample cylinder and configured to rotationally drive the first sample cylinder;
A second test cylinder disposed parallel to the central axis of the first test cylinder and in contact with the outer peripheral surface of the first test cylinder;
A second drive motor connected to the central axis of the second test cylinder and rotating the second test cylinder;
A motor controller that drives one of the first drive motor and the second drive motor at a predetermined speed and controls the other so that the rotation speed changes while the first and second test cylinders rotate once. When,
A two-cylinder friction test apparatus comprising a load applying mechanism for applying a predetermined contact pressure between the outer peripheral surfaces of the first test cylinder and the second test cylinder. The two-cylinder friction test apparatus according to claim 9,
The motor controller controls the other motor so that the rotation speed changes in a sinusoidal pattern for one cycle within a rotation cycle in which the first and second test cylinders rotate once. Two-cylinder friction test device. The two-cylinder friction test apparatus according to claim 9,
The motor controller rotates the rotation speed in any one of a trapezoidal wave pattern, a triangular wave pattern, and a rectangular wave pattern for one period within a rotation period in which the first and second test cylinders rotate once. The two-cylinder friction test apparatus is characterized in that the other motor is controlled so as to change. The two-cylinder friction test apparatus according to claim 10 or 11,
The load applying mechanism includes a cylinder for applying a load to the first test cylinder or the second test cylinder, a pump for supplying a working fluid to the cylinder, and a load controller for controlling the cylinder and the pump. ,
The two-cylinder friction test apparatus, wherein the load controller controls the cylinder and the pump so as to apply a predetermined constant load. The two-cylinder friction test apparatus according to claim 10 or 11,
The load adding mechanism includes a cylinder for applying a load of the first test cylinder or the second test cylinder, a pump for supplying a working fluid to the cylinder, and a load controller for controlling the cylinder and the pump. Prepared,
The two-cylinder friction test apparatus, wherein the load controller controls the cylinder and the pump to add a sinusoidal pattern as a load pattern. The two-cylinder friction test apparatus according to claim 13,
The load controller controls the cylinder and the pump so that a sinusoidal pattern for two cycles is added as a load pattern within a rotation cycle in which the first and second test cylinders rotate once. Cylindrical friction test device.

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