JP6424769B2 - Power circulating gear test device - Google Patents

Description

  The present invention relates to a power circulation type gear testing device, and more particularly to a technique for measuring a torque loss due to factors other than meshing rotation of a gear such as rolling resistance of a support bearing.

  (a) The first gear and the second gear engaged with each other are attached to the first shaft and the second shaft parallel to each other, and the third gear and the fourth gear engaged with each other are the first shaft and the gear (B) any one of the first gear to the fourth gear is rotationally driven, whereby the first gear to the fourth gear are meshed and rotated; A torsional torque applying device for applying a torsional torque to either one of the first shaft portion and the second shaft portion, and (d) the torsional torque applying device. A power circulation type gear testing device is known which meshes and rotates the first gear to the fourth gear in a state where a predetermined meshing load is applied by the device. One example of the device described in Patent Document 1 is that a twisting torque is applied by an axial pulling machine. Further, in Patent Document 2, the twisting torque is applied by the slipping clutch.

JP, 2006-292700, A Unexamined-Japanese-Patent No. 8-145853 gazette

  By the way, in such a conventional power circulation type gear testing device, when measuring the meshing loss torque by meshing rotation from the load torque at the time of rotational driving, the first shaft portion and the second shaft portion are rotatably supported. And the torque loss due to the rolling resistance etc. of the supporting bearing included, and it was not always possible to measure with high accuracy.

  The present invention has been made against the background described above, and it is possible to measure loss torque (hereinafter referred to as external loss torque) due to factors other than meshing rotation of gears, such as rolling resistance of support bearings. It is to be done.

The present invention is characterized in that (a) the first gear and the second gear engaged with each other are attached to the first shaft and the second shaft parallel to each other, and the third gear and the fourth gear engaged with each other The first gear to the fourth gear are attached to the one shaft portion and the second shaft portion, and (b) any one of the first gear to the fourth gear is rotationally driven. (C) A torsional torque applying device for applying a torsional torque to either one of the first shaft portion and the second shaft portion is provided, while a power circulation path to be meshed and rotated is formed, (d) (E) a first shaft portion and a fourth shaft portion of a power circulating gear test device for meshingly rotating the first gear to the fourth gear in a state where a predetermined meshing load is applied by the torsion torque applying device; The two-shaft portion includes each of the first to fourth gears. The first gear portion is rotatably supported by a plurality of support bearings disposed on the side, and (f) the first gear to the fourth gear can be detachably attached via the connection joint. (G) each has a rotatable bearing and is connected to the first shaft and the second shaft instead of the first gear to the fourth gear. And (h) a plurality of pseudo loading devices capable of respectively applying to the bearings pseudo loads equivalent to the loads generated on the first gear to the fourth gear by the meshing load And (i) each of the first shaft portion and the second shaft portion is individually driven to rotate in a state where the pseudo load is applied to the bearing by the pseudo load applying device; 1st shaft and 2nd shaft Characterized in that it is possible to measure the load torque during individually its rotational drive.
The first shaft portion and the second shaft portion are configured to include a plurality of partial shafts disposed on a common axis so that the first gear to the fourth gear can be replaced with the bearing unit. .

  In such a power circulation type gear testing device, the bearing unit is connected to the first shaft portion and the second shaft portion instead of the first gear to the fourth gear, and the first gear to the fourth gear are generated by the meshing load. The pseudo load equivalent to the load generated on each is applied to each bearing by the pseudo load application device, and the first shaft and the second shaft are individually driven to rotate separately in that state, so that the first shafts It is possible to separately measure the load torque at the time of rotational driving of the part and the second shaft part. The load torque at this time is an external loss torque due to factors other than meshing rotation of the gears, such as rolling resistance of the support bearing, so the whole measured by the usual gear meshing rotation test connecting the first gear to the fourth gear By subtracting the external loss torque from the loss torque of the above, it is possible to obtain the meshing loss torque due to the meshing rotation of the gear with high accuracy.

  Further, since the external loss torque due to the rolling resistance and the like of the support bearing can be measured in this way, a large bearing, a tapered roller bearing, a double row bearing and the like excellent in durability even if the rolling resistance is large can be adopted as the support bearing. It is possible to improve the working efficiency by reducing the frequency of replacement of the support bearing. It is possible to determine the replacement time of the support bearing based on the value of the external loss torque due to the rolling resistance or the like of the support bearing, and maintenance can be performed easily and appropriately.

FIG. 2 is a conceptual view of a power circulation type gear testing device according to an embodiment of the present invention, in which a normal gear meshing rotation test is performed. FIG. 7 is a cross-sectional view for explaining a specific example of a connection joint which detachably connects a plurality of gears in the power circulating gear testing device of FIG. 1; FIG. 10 is a conceptual diagram when a bearing unit is attached instead of a plurality of gears in the power circulating gear testing device of FIG. 1 and external loss torque due to factors other than meshing rotation of the gears is measured.

  Although it is desirable that the coupling joint that detachably connects the first gear to the fourth gear can be replaced with a bearing unit by detaching only the first gear to the fourth gear, for example, supporting bearings on both sides of each gear The connection joint may be provided on the outside of the gear and the gear and the support bearing may be removed together. In that case, the bearing unit is previously provided with another supporting bearing, and the supporting bearing is to be replaced. Also, by driving the first shaft and the second shaft individually while the pseudo load is applied to the bearing by the pseudo load applying device, the first shaft and the second shaft are individually driven. In order to measure the load torque at the time of its rotational drive, for example, a rotary drive and a torque detector are provided on the first shaft and the second shaft respectively, but it is not necessary to measure simultaneously. By performing measurements before and after, it is also possible to use one set of rotary drive and torque detector in common for both the first and second shaft measurements. The same applies to the bearing unit and the pseudo loading device.

  The power circulation type gear testing device of the present invention is configured to include at least a first shaft portion and a second shaft portion. For example, a third shaft portion is provided on the opposite side of the second shaft portion with respect to the first shaft portion. Various modes are possible such as providing a fifth gear and a sixth gear which are disposed and meshed with and rotated by the first gear and the third gear. The support bearings are disposed on both sides of each of at least the first gear to the fourth gear, but may be additionally provided, for example, in the vicinity of the torsional torque applying device.

  The gear ratio (tooth number ratio) between the first gear and the second gear engaged with each other and the gear ratio between the third gear and the fourth gear may be the same, but using gears with different gear ratios Is also possible. When the gear ratios of the two sets of gears (the first and second gears and the third and fourth gears) are the same, the torsion torque applying device moves one shaft axially as described in Patent Document 1. In addition to the movement, for example, any one of the first shaft and the second shaft can be divided at an intermediate position, and twisting can be applied to integrally connect them to apply a twisting torque. When the gear ratios of the two sets of gears are different, either one of the first shaft portion and the second shaft portion causes differential rotation at an intermediate position, so, for example, as described in Patent Document 2, a slip clutch etc. The torsional torque can be applied by limiting the differential rotation. Each of the two sets of gears may be a test gear, but one may be a test gear and the other may be a circulation gear for forming a power circulation path.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified for the sake of explanation, and the dimensional ratios and shapes of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a conceptual diagram for explaining the basic configuration of a power circulating type gear testing device 10 according to an embodiment of the present invention, which comprises a first shaft portion 12 and a second shaft portion 14 disposed in parallel with each other. There is. While the first gear 16 and the third gear 20 are attached to the first shaft portion 12, the second gear 18 and the fourth gear 22 are attached to the second shaft portion 14. The second gear 18 is in mesh with each other, and the third gear 20 and the fourth gear 22 are in mesh with each other. Each of the first gear 16 to the fourth gear 22 is a helical gear, and the gear ratios of the two sets of gears 16 and 18, 20 and 22 meshed with each other are equal to each other. Thereby, when the first shaft portion 12 is rotationally driven in one direction at a predetermined speed, the second shaft portion 14 is rotated in the opposite direction to the first shaft portion 12 at a rotation speed according to the gear ratio, etc. The power circulation path is formed including the first gear 16 to the fourth gear 22 of As the first gear 16 to the fourth gear 22, other cylindrical gears such as a flared gear or a spur gear can also be used.

  The first shaft portion 12 is divided into four partial shafts 12a to 12d, and is rotatably supported by support bearings 24a to 24d, respectively. As the support bearings 24a to 24d, various bearings such as ball bearings and roller bearings can be adopted, and a plurality of bearings can be used in combination as needed. The first gear 16 is concentrically and removably connected between the partial shafts 12a and 12b via a pair of connection joints 26a and 26b, and the third gear 20 is connected to the pair of connection joints 28a and 28b. It is detachably connected concentrically between the partial shafts 12c and 12d. FIG. 2 is a cross-sectional view showing one specific example of the coupling joint 26a, in which an adapter 32 having a tapered hole 30 fixed to an end of the partial shaft 12a and a gear to which the first gear 16 is attached non-rotatably. An end of the holding member 36 is provided with an annular tapered projection 34 integrally or separately provided, and the tapered projection 34 is fitted into the tapered hole 30 concentrically. The plurality of clamp pieces 38 disposed inside the tapered hole 30 are displaced to the outer peripheral side by the clamp screw 40 and engaged with the tapered protrusion 34, whereby the tapered protrusion 34 is formed into the tapered hole 30. It is drawn in and is firmly connected integrally. A meshing tooth is provided at the tip of the tapered projection 34 so that relative rotation with respect to the adapter 32 is reliably prevented. Further, when the clamp screw 40 is loosened to release the engagement between the clamp piece 38 and the tapered protrusion 34, the tapered protrusion 34 can be pulled out of the tapered hole 30 to separate the gear holding member 36 from the adapter 32. The other connection joints 26b, 28a, 28b are also configured substantially the same as the connection joint 26a. That is, at the other end of the gear holding member 36, a tapered protrusion is provided symmetrically to the tapered protrusion 34, and is connected to the partial shaft 12b via the connection joint 26b. Note that, instead of the tapered hole 30 or the tapered protrusion 34, another connection joint such as one having a cylindrical fitting portion with a constant diameter can be adopted.

  Returning to FIG. 1, the first shaft portion 12 also has a torsion torque applying device 42 at an intermediate position between the first gear 16 and the third gear 20, specifically between the partial shafts 12b and 12c. Is provided. The torsional torque applying device 42 applies a predetermined torsional torque to the partial shafts 12b and 12c on both sides and integrally connects them in a state where the two sets of gears 16 and 18, 20 and 22 are engaged. As a result, the two sets of gears 16 and 18, 20 and 22 are engaged with an engagement load corresponding to the torsional torque. Further, a first rotary drive 46 is connected to the partial shaft 12 d via a first torque detector 44. The first rotary drive device 46 is an electric motor or the like, and can rotationally drive the first shaft portion 12 via the partial shaft 12d, and measures the load torque T1 at the time of the rotational drive by the first torque detector 44. be able to. With the two sets of gears 16 and 18, 20 and 22 engaged as shown in FIG. 1, the first rotary drive 46 rotationally drives the first shaft 12 to mesh and rotate them. If the load torque T1 at the time of rotational driving is measured by the first torque detector 44, the load torque T1 corresponds to the entire loss torque Tt including the loss torque due to meshing rotation.

  Similarly to the first shaft portion 12, the second shaft portion 14 is also divided into four partial shafts 14a to 14d, and these partial shafts 14a to 14d can be rotated by the support bearings 50a to 50d, respectively. It is supported by The second gear 18 is concentrically and detachably connected between the partial shafts 14a and 14b via a pair of connection joints 52a and 52b, and the fourth gear 22 is connected to the pair of connection joints 54a and 54b. It is detachably connected concentrically between the partial shafts 14c and 14d. These connection joints 52a, 52b, 54a, 54b are configured, for example, in the same manner as the connection joint 26a of FIG. The second shaft portion 14 is also provided with a circulation torque detector 56 at an intermediate position between the second gear 18 and the fourth gear 22, specifically between the partial shafts 14b and 14c. . The circulation torque detector 56 is for detecting a twisting torque between the partial shafts 14b and 14c on both sides, and applies a twisting torque by a twisting torque applying device 42 disposed on the first shaft portion 12. In this case, by adjusting the twisting state while confirming the actual twisting torque by the circulation torque detector 56, a predetermined twisting torque can be applied. It is also possible to dispose the circulation torque detector 56 coaxially with the torsion torque applying device 42, that is, on the first shaft 12 side. In addition, a second torque detector 60 and a second rotational drive device 62 are connected to a partial shaft 14 d provided outside the fourth gear 22 via a connecting and disconnecting device 58. The connection / disconnection device 58 is for connecting and disconnecting the power transmission between the partial shaft 14d and the second torque detector 60, and is constituted by a meshing clutch or the like, and as shown in FIG. When performing the gear meshing rotation test, the power transmission is interrupted by disconnecting the partial shaft 14d and the second torque detector 60. The second rotary drive device 62 is an electric motor or the like, and can rotationally drive the second shaft portion 14 via the partial shaft 14d when the connection / disconnection device 58 is in the connected state, and the load torque T2 at the time of the rotational drive Can be measured by the second torque detector 60.

  On the other hand, as shown in FIG. 3, the power circulation type gear testing device 10 of the present embodiment can connect bearing units 70 to 76 instead of the first gear 16 to the fourth gear 22. That is, since the first gear 16 is attached to the first shaft 12 by the connecting joints 26a and 26b, the first gear 16 can be easily removed from the first shaft 12 by the connecting joints 26a and 26b. it can. The same applies to the second gear 18 to the fourth gear 22. Like the gear holding member 36, the bearing unit 70 has a shaft member 78 provided with tapered projections 34 at both ends, and a bearing 80 such as a ball bearing or a roller bearing attached to an intermediate position of the shaft member 78. And can be easily mounted between the partial shafts 12a and 12b via the coupling joints 26a, 26b. The other bearing units 72 to 76 have the same configuration and can be easily attached to the first shaft portion 12 or the second shaft portion 14 instead of the second gear 18 to the fourth gear 22.

  Each of the bearing units 70 to 76 is also provided with a pseudo load applying device 82, and when the first gear 16 to the fourth gear 22 are meshed and rotated as shown in FIG. The pseudo load equivalent to the load generated in each of the first gear 16 to the fourth gear 22 can be individually applied to each bearing 80 of the bearing units 70 to 76. In the present embodiment, the first gear 16 to the fourth gear 22 are helical gears, and thrust loads and radial loads are generated by meshing loads, so that each simulated load applying device 82 is driven by an electric motor. A predetermined thrust load and radial load can be applied by a feed screw mechanism, an electromagnetic solenoid, fluid pressure such as oil pressure, magnetic force or the like. The thrust load and radial load generated in each of the first gear 16 to the fourth gear 22 can be calculated from, for example, specifications such as the twist angle and pressure angle of each gear, meshing load, rotational speed and the like.

  Then, as shown in FIG. 3, bearing units 70 to 76 are attached instead of the first gear 16 to the fourth gear 22, and a predetermined pseudo load is applied to each bearing 80 by the pseudo load applying device 82. The first shaft unit 12 is rotationally driven by the first driving device 46, and the load torque T 1 at the time of the rotational driving is measured by the first torque detector 44. The load torque T1 at this time is the external loss torque T1n related to the first shaft portion 12 due to factors other than meshing rotation of the first gear 16 to the fourth gear 22 such as rolling resistance of the support bearings 24a to 24d. Further, the connection / disconnection device 58 is connected, and the second shaft portion 14 is rotationally driven by the second drive device 62, and the load torque T 2 at the time of the rotational drive is measured by the second torque detector 60. The load torque T2 at this time is an external loss torque T2n related to the second shaft portion 14 due to factors other than meshing rotation of the first gear 16 to the fourth gear 22 such as rolling resistance of the support bearings 50a to 50d. Therefore, as shown in FIG. 1, the external torque is measured from the load torque T1, which is measured by meshing rotation of the two gears 16 and 18, 20 and 22 by the first rotary drive 46, that is, the overall loss torque Tt. By subtracting the torques T1n and T2n, it is possible to determine with high accuracy the meshing loss torque due to the meshing rotation of the two gears 16 and 18, 20 and 22. Since the external loss torques T1n and T2n include the loss torque due to the rolling resistance of the bearing 80, the loss torque due to the rolling resistance of the bearing 80 is measured or corrected by simulation or the like as necessary. You may subtract.

  As described above, in the power circulation type gear testing device 10 of the present embodiment, the bearing units 70 to 76 are connected to the first shaft portion 12 and the second shaft portion 14 instead of the first gear 16 to the fourth gear 22. In addition, a pseudo load equivalent to the load generated on each of the first gear 16 to the fourth gear 22 by the meshing load is applied to each of the bearings 80 of the bearing units 70 to 76 by the pseudo load applying device 82. By separately driving the shaft portion 12 and the second shaft portion 14 separately, the load torques T1 and T2 at the time of rotational driving of the first shaft portion 12 and the second shaft portion 14 are separately measured. Can. The load torques T1 and T2 at this time are external loss torques T1n and T2n due to factors other than meshing rotation of the two gears 16 and 18, 20 and 22, such as rolling resistance of the support bearings 24a to 24d and 50a to 50d. Therefore, by subtracting the external loss torques T1 n and T2 n from the total loss torque Tt measured in the normal gear meshing rotation test shown in FIG. The meshing torque loss due to the meshing rotation of 22 can be determined with high accuracy.

  In addition, since the external loss torques T1n and T2n due to the rolling resistance and the like of the support bearings 24a to 24d and 50a to 50d can be measured as described above, the support bearings 24a to 24d and 50a to 50d are durable even if the rolling resistance is large. It becomes possible to adopt excellent large bearings, tapered roller bearings, double row bearings, etc., and it is possible to improve the working efficiency by reducing the frequency of replacement of the support bearings 24a to 24d and 50a to 50d. It is possible to determine the replacement timing of the support bearings 24a to 24d and 50a to 50d based on the values of the external loss torques T1n and T2n, and maintenance can be performed easily and appropriately.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, this is merely an embodiment, and the present invention may be implemented in variously modified and / or improved modes based on the knowledge of those skilled in the art. Can.

  10: power circulation type gear testing device 12: first shaft portion 14: second shaft portion 16: first gear 18: second gear 20: third gear 22: fourth gear 24a to 24d, 50a to 50d: support bearing 26a, 26b, 28a, 28b, 52a, 52b, 54a, 54b: Coupling joint 42: Torsional torque application device 70, 72, 74, 76: Bearing unit 80: Bearing 82: Pseudo load application device

Claims (1)

The first gear and the second gear engaged with each other are attached to the first shaft and the second shaft parallel to each other, and the third gear and the fourth gear engaged with each other are the first shaft and the second gear. Attached to the shaft,
While any one of the first gear to the fourth gear is rotationally driven, a power circulation path is formed in which the first gear to the fourth gear are meshed and rotated,
And a torsion torque applying device for applying a torsion torque to any one of the first shaft portion and the second shaft portion,
In a power circulating gear test apparatus for meshingly rotating the first gear to the fourth gear in a state in which a predetermined meshing load is applied by the torsion torque applying device,
The first shaft portion and the second shaft portion are rotatably supported by a plurality of support bearings disposed on both sides of each of the first gear to the fourth gear.
Each of the first gear to the fourth gear is detachably connected to the first shaft or the second shaft via a connection joint.
A plurality of bearing units, each having a rotatable bearing, and coupled to the first shaft and the second shaft instead of the first gear to the fourth gear;
A plurality of simulated load applying devices capable of applying simulated loads equivalent to the loads generated on each of the first gear to the fourth gear by the meshing load to the bearings respectively;
The first shaft portion and the second shaft portion by individually driving the first shaft portion and the second shaft portion in a state where the pseudo load is applied to the bearing by the pseudo load applying device. A power circulating type gear test device characterized in that load torque at the time of rotational driving can be individually measured for a shaft portion.

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