JP6699227B2 - Power transmission device - Google Patents

Description

  The present invention relates to a power transmission device that transmits power input from a rotary shaft to a gear member.

  BACKGROUND ART Conventionally, a synchro device has been used in a power transmission device (transmission) for a vehicle in order to synchronize a rotating shaft and a gear. For example, in a conventional synchronizer, a synchronizer hub fixed to a rotating shaft, a gear rotatably supported by the rotating shaft, a synchronizer ring arranged between the synchronizer hub and the gear, and a rotating shaft attached to the synchronizer hub. And a sleeve that is slidably supported in the axial direction and is engageable with the synchronizer ring and the gear. The synchronizer ring is formed with a friction surface that transmits the rotation of the synchronizer hub to the cone surface of the gear.

JP, 2013-194907, A

  However, in the conventional power transmission device, even when the synchronizer ring is not used (that is, when the synchronizer ring is not engaged), friction is generated on the friction surface of the synchronizer ring, which causes drag loss due to the so-called synchronizer ring. there were.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a power transmission device capable of eliminating drag loss due to a synchronizer ring.

  A power transmission device of the present invention includes a rotating shaft having a spline, a gear member arranged coaxially with the rotating shaft, having a first tooth portion, and integrally rotating with the rotating shaft and in an axial direction of the rotating shaft. A rotation absorbing mechanism that is disposed on the spline so as to be movable in the direction of the axis and meshes with the first tooth portion of the gear member by the movement in the axial direction so that the gear member rotates integrally with the rotation shaft. The rotation absorbing mechanism includes a sleeve member that rotates integrally with the rotation shaft, a moving member that moves the sleeve member in the axial direction, and the moving member that frictionally engages with the sleeve member. And a friction member which is disposed between the sleeve member and absorbs a rotation difference between the rotation shaft and the gear member by friction when rotating relative to the sleeve member.

  According to this configuration, when synchronizing the gear member and the rotating shaft, the sleeve member is slid in the axial direction of the rotating shaft by the moving member of the rotation absorbing mechanism. Then, the rotation absorbing mechanism meshes with the first tooth portion (low tooth portion) of the gear member, and the gear member rotates integrally with the rotation shaft. In this case, since the rotation absorbing mechanism rotates integrally with the rotation shaft, a rotation difference occurs between the rotation shaft and the gear member. In this rotation absorbing mechanism, a friction member is arranged between the moving member and the sleeve member, and the friction member and the sleeve member are frictionally engaged with each other. Therefore, when the friction member and the sleeve member rotate relative to each other, the rotation difference between the rotation shaft and the gear member is absorbed by the friction of the friction member. In this case, since it is not necessary to provide the synchronizer ring as in the conventional case, it is possible to eliminate drag loss due to the synchronizer ring at the time of non-engagement.

  In the power transmission device of the present invention, the sleeve member has a second tooth portion that meshes with the first tooth portion of the gear member, and the rotation absorbing mechanism moves the second tooth portion by moving in the axial direction. When the tooth portion meshes with the first tooth portion, the gear member rotates integrally with the rotating shaft, and the friction member is connected to the sleeve member when the second tooth portion meshes with the first tooth portion. In the case of relative rotation, the difference in rotation between the rotating shaft and the gear member may be absorbed by friction.

  According to this configuration, when the sleeve member is slid in the axial direction of the rotation shaft by the moving member of the rotation absorbing mechanism, the second tooth portion (spline) of the sleeve member causes the first tooth portion (low tooth portion) of the gear member. And the gear member rotates integrally with the rotary shaft. In this case, when the second tooth portion meshes with the first tooth portion, when the friction member and the sleeve member rotate relative to each other, the difference in rotation between the rotation shaft and the gear member can be absorbed by the friction of the friction member. .

  In the power transmission device of the present invention, the rotation absorbing mechanism has a third tooth portion that meshes with the gear member before the second tooth portion meshes with the first tooth portion, and the third tooth portion. When the gear meshes with the gear member, relative rotation may occur between the friction member and the sleeve member.

  According to this structure, the third tooth portion of the rotation absorbing mechanism meshes with the gear member before the second tooth portion meshes with the first tooth portion. When relative rotation occurs between the friction member and the sleeve member when the third tooth portion meshes with the gear member, the difference in rotation between the rotation shaft and the gear member can be absorbed by the friction of the friction member.

  Further, in the power transmission device of the present invention, the rotation absorbing mechanism may include a pressing member that presses the friction member against the sleeve member by using an urging force obtained by an urging member.

  According to this structure, the friction member is pressed against the sleeve member by the biasing force (pressurization) obtained by the biasing member. As a result, a friction torque can be generated on the friction surface, and the difference in rotation between the rotating shaft and the gear member can be absorbed by friction. The biasing member can be configured by, for example, a disc spring or a coil spring.

  In the power transmission device of the present invention, a plurality of the friction members may be arranged side by side in the axial direction.

  According to this configuration, the friction torque can be increased by increasing the number of friction members. This increases the degree of freedom in designing the friction torque.

  According to the present invention, drag loss due to the synchronizer ring can be eliminated.

It is explanatory drawing of the power transmission device (synchro mechanism) in embodiment of this invention. It is a top view of the gear member in the embodiment of the present invention. It is a top view of a friction member in an embodiment of the invention. It is a top view of a sleeve member in an embodiment of the invention. It is explanatory drawing which shows the pre-engagement state of the power transmission device (synchro mechanism) in embodiment of this invention. It is explanatory drawing which shows the main engagement state of the power transmission device (synchro mechanism) in embodiment of this invention. It is explanatory drawing of the power transmission device (synchro mechanism) in other embodiment.

  Hereinafter, a power transmission device according to an embodiment of the present invention will be described with reference to the drawings. In the present embodiment, the case of a power transmission device used for a vehicle transmission or the like is illustrated.

  A configuration of a power transmission device according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is an explanatory diagram of a synchronizing mechanism that is a power transmission device. As shown in FIG. 1, the synchronizing mechanism 1 includes a rotating shaft 2, a gear member 3, and a rotation absorbing mechanism 4. The gear member 3 is provided coaxially with the rotating shaft 2 and is rotatable independently of the rotating shaft 2. For example, the rotating shaft 2 is a main shaft to which power from a drive source (not shown) such as an engine is transmitted, and the gear member 3 is a gear for shifting to a low speed side or a high speed side. A spline 5 is provided on the outer peripheral surface of the rotating shaft 2. Further, on the outer peripheral surface of the gear member 3, a low tooth portion 6 which is a first tooth portion and a high tooth portion 7 are provided (see FIG. 2). The low tooth portions 6 are formed over the entire outer circumference of the gear member 3, and the high tooth portions 7 are formed on a part of the outer circumference of the gear member 3 (for example, at three positions at 120 degree intervals, or at 90 degree intervals). Are formed at four intervals). A rotation absorbing mechanism 4 is provided on the spline 5 of the rotary shaft 2 so as to rotate integrally with the rotary shaft 2 and to be movable in the axial direction of the rotary shaft 2.

  The rotation absorbing mechanism 4 includes a sleeve member 8, a moving member 9, and a sleeve holder (friction member) 10. The inner peripheral surface of the sleeve member 8 is provided with a spline 11, which is a second tooth portion (see FIG. 4). The spline 11 is formed over the entire circumference of the sleeve member 8. The spline 11 of the sleeve member 8 is configured to mesh with the spline 5 of the rotary shaft 2, and the sleeve member 8 rotates integrally with the rotary shaft 2 and is movable in the axial direction of the rotary shaft 2. The spline 11 of the sleeve member 8 is configured to mesh with the low tooth portion 6 of the gear member 3 when the sleeve member 8 moves in the axial direction toward the gear member 3.

  The sleeve member 8 can be moved in the axial direction by the moving member 9. For example, the moving member 9 is a fork. The friction member 10 is provided between the moving member 9 and the sleeve member 8, and the moving member 9 and the sleeve member 8 are frictionally engaged with each other via the friction member 10. In the present embodiment, the friction member 10 includes a main body member 12, a friction plate 13, and a pressing member 14.

  A groove portion 15 into which the moving member 9 (fork) is fitted is provided on the outer peripheral surface of the main body member 12. A plate portion 16 is provided on one gear member 3 side of the main body member 12 (on the left side in FIG. 1 ). A dog tooth portion 17, which is a third tooth portion, is provided on the inner peripheral surface at the tip of the plate portion 16 (see FIG. 3 ). The dog tooth portion 17 engages with the high tooth portion 7 of the gear member 3. The dog tooth portions 17 are provided on a part of the inner circumference of the plate portion 16 (for example, at three positions at 120° intervals or at four positions at 90° intervals) so as to correspond to the high tooth portions 7 of the gear member 3. ) Is formed. A friction surface is formed on the surface of the plate portion 16 on the sleeve member 8 side (right side in FIG. 1), and a friction surface is also formed on the surface of the sleeve member 8 on the plate portion 16 side (left side in FIG. 1). Has been done.

  A spline 18 is provided on the inner peripheral surface of the main body member 12. The friction plate 13 is configured to mesh with the spline 18 of the main body member 12, is integrally rotatable with the main body member 12, and is movable in the axial direction of the rotary shaft 2. The pressing member 14 is fixed to the main body member 12 by a snap 19 so as not to move in the axial direction of the rotating shaft 2. A biasing member 20 is housed inside the pressing member 14. The biasing member 20 is composed of, for example, a disc spring or a coil spring. The friction plate 13 is pressed toward the sleeve member 8 by the urging force obtained from the urging member 20. It can be said that the sleeve member 8 is sandwiched from both sides by the friction member 10 (the main body member 12 and the friction plate 13) and is grasped from both sides by the urging force of the urging member 20. A friction surface is formed on the surface of the friction plate 13 on the sleeve member 8 side (left side in FIG. 1), and a friction surface is also formed on the surface of the sleep member on the friction plate 13 side (right side in FIG. 1). ing.

  A plate portion 21 similar to the plate portion 16 of the main body member 12 is provided on the other gear member 3 side (right side in FIG. 1) of the pressing member 14, and the inner peripheral surface of the tip of the plate portion 21 is provided. Is also provided with a dog tooth portion 22 that engages with the high tooth portion 7 of the gear member 3. The dog tooth portions 22 are also formed on a part of the inner circumference of the plate portion 21 (e.g., at three positions at 120 degree intervals or four at 90 degree intervals) so as to correspond to the high tooth portions 7 of the gear member 3. Formed).

  The operation of the synchronizing mechanism 1 configured as described above will be described with reference to the drawings. Here, the operation when synchronizing the rotating shaft 2 that is rotating and the gear member 3 that is not rotating using the synchro mechanism 1 will be described.

  When synchronizing the rotating shaft 2 and the gear member 3 using the synchronizing mechanism 1 of the present embodiment, first, as shown in FIG. 5, the moving member 9 is moved to move the sleeve member 8 in the axial direction. The gear member 3 (the gear member 3 on the left side in FIG. 5), which is the object of meshing, is slid along. Then, the dog tooth portion 17 of the friction member 10 engages with the high tooth portion 7 of the gear member 3. When the friction member 10 starts to rotate integrally with the gear member 3, the friction member 10 serves as rotation resistance of the gear member 3, and a difference in rotation occurs between the friction member 10 and the sleeve member 8. That is, the friction member 10 and the sleeve member 8 rotate relative to each other. In this case, the sleeve member 8 is sandwiched from both sides by the friction member 10 and is grasped from both sides by the urging force of the urging member 20. Therefore, the rotation difference between the friction member 10 and the sleeve member 8 is absorbed by the friction of the friction surface.

  In this way, when there is no difference in rotation between the friction member 10 and the sleeve member 8 and the gear member 3 and the rotary shaft 2 are synchronized, the moving member 9 is further moved as shown in FIG. The spline 11 of the member 8 can mesh with the low tooth portion 6 of the gear member 3.

  According to the synchro mechanism 1 of this embodiment, when the gear member 3 and the rotary shaft 2 are synchronized, the sleeve member 8 slides in the axial direction of the rotary shaft 2 by the moving member 9 of the rotation absorbing mechanism 4. Then, the rotation absorbing mechanism 4 meshes with the low tooth portion 6 of the gear member 3, and the gear member 3 rotates integrally with the rotating shaft 2. In this case, since the rotation absorbing mechanism 4 rotates integrally with the rotary shaft 2, a rotation difference occurs between the rotary shaft 2 and the gear member 3. In the rotation absorbing mechanism 4, a friction member 10 is arranged between the moving member 9 and the sleeve member 8, and the friction member 10 and the sleeve member 8 are frictionally engaged with each other. Therefore, when the friction member 10 and the sleeve member 8 rotate relative to each other, the rotation difference between the rotating shaft 2 and the gear member 3 is absorbed by the friction of the friction member 10. In this case, since it is not necessary to provide the synchronizer ring as in the conventional case, it is possible to eliminate drag loss due to the synchronizer ring at the time of non-engagement.

  Specifically, when the sleeve member 8 is slid in the axial direction of the rotary shaft 2 by the moving member 9 of the rotation absorbing mechanism 4, the spline 11 of the sleeve member 8 meshes with the low tooth portion 6 of the gear member 3, and the gear The member 3 comes to rotate integrally with the rotary shaft 2. In this case, when the spline 11 meshes with the low tooth portion 6, when the friction member 10 and the sleeve member 8 relatively rotate, the difference in rotation between the rotary shaft 2 and the gear member 3 is absorbed by the friction of the friction member 10. be able to.

  More specifically, the dog teeth 17 and 22 of the rotation absorbing mechanism 4 mesh with the high teeth 7 of the gear member 3 before the splines 11 mesh with the low teeth 6. When relative rotation occurs between the friction member 10 and the sleeve member 8 when the dog tooth portions 17 and 22 are meshed with the high tooth portion 7, a difference in rotation between the rotary shaft 2 and the gear member 3 is generated. Can be absorbed by friction.

  Further, in the present embodiment, the friction member 10 is pressed against the sleeve member 8 by the biasing force (pressurization) obtained by the biasing member 20. As a result, a friction torque can be generated on the friction surface, and the difference in rotation between the rotary shaft 2 and the gear member 3 can be absorbed by friction.

  Although the embodiments of the present invention have been described above by way of example, the scope of the present invention is not limited to these and can be modified or modified according to the purpose within the scope of the claims. is there.

  For example, as shown in FIG. 7, a plurality of friction plates 13 of the friction member 10 can be arranged side by side in the axial direction. FIG. 7 shows an example in which three friction plates 13 are provided side by side, but the number of friction plates 13 is not limited to this. In this case, the friction torque can be increased by increasing the number of friction members 10. This increases the degree of freedom in designing the friction torque.

  INDUSTRIAL APPLICABILITY As described above, the power transmission device according to the present invention has the effect of eliminating drag loss due to the synchronizer ring, and is useful as a vehicle transmission or the like.

1 Synchro mechanism (power transmission device)
2 rotating shaft 3 gear member 4 rotation absorbing mechanism 5 spline 6 low tooth portion (first tooth portion)
7 High-tooth part 8 Sleeve member 9 Moving member 10 Sleeve holder (friction member)
11 splines (second tooth)
12 main body member 13 friction plate 14 pressing member 15 groove portion 16 plate portion 17 dog tooth portion (third tooth portion)
18 Spline 19 Snap 20 Biasing Member 21 Plate Part 22 Dog Tooth Part (Third Tooth Part)

Claims (5)

A rotary shaft having a spline,
A gear member arranged coaxially with the rotation shaft and having a first tooth portion,
It is arranged on the spline so as to rotate integrally with the rotary shaft and to be movable in the axial direction of the rotary shaft, and when the spline meshes with the first tooth portion of the gear member by the movement in the axial direction, A rotation absorbing mechanism in which a gear member rotates integrally with the rotation shaft,
Equipped with
The rotation absorbing mechanism,
A sleeve member that rotates integrally with the rotating shaft,
A moving member for moving the sleeve member in the axial direction,
It is arranged between the moving member and the sleeve member so as to frictionally engage with the sleeve member, and absorbs a rotation difference between the rotary shaft and the gear member by friction when rotating relative to the sleeve member. A friction member to
Power transmission device. The sleeve member has a second tooth portion that meshes with the first tooth portion of the gear member,
In the rotation absorbing mechanism, when the second tooth portion meshes with the first tooth portion due to the movement in the axial direction, the gear member integrally rotates with the rotating shaft,
The friction member absorbs a rotation difference between the rotating shaft and the gear member by friction when the second tooth portion rotates relative to the sleeve member when the second tooth portion meshes with the first tooth portion. 1. The power transmission device according to 1. The rotation absorbing mechanism has a third tooth portion that meshes with the gear member before the second tooth portion meshes with the first tooth portion,
The power transmission device according to claim 2, wherein relative rotation occurs between the friction member and the sleeve member when the third tooth portion meshes with the gear member.   4. The rotation absorbing mechanism according to claim 1, further comprising a pressing member that presses the friction member against the sleeve member by using an urging force obtained by an urging member. Power transmission device.   The power transmission device according to any one of claims 1 to 4, wherein a plurality of the friction members are arranged in parallel in the axial direction.

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