JP6987913B2 - Lock type bidirectional clutch - Google Patents

Description

The present invention is a clutch device that changes the power transmission state between the input member and the output member, in particular, the forward / reverse rotation power from the input member (drive side) is transmitted, and the power is transmitted from the output member (driven side). The power transmission is related to a lock type bidirectional clutch that shuts off the output member as non-rotatable.

In a power transmission system that drives work equipment from a drive source such as a motor, for example, an elevating device that moves an article up and down by a motor, when the article is in a predetermined position, the article is automatically stopped when the motor is stopped. An operation that holds the position may be required. Therefore, using a lock-type bidirectional clutch equipped with an input shaft (input member) and an output shaft (output member), the input shaft is connected to a motor that can rotate forward and reverse, and the article is rotated by the rotation of the output shaft. Devices for raising and lowering are known. In the bidirectional clutch of this device, when the input shaft is rotated forward / reverse by the motor, the output shaft is linked to rotate forward / reverse to raise and lower the article, while when the output shaft is rotated forward / reverse, the output is output. The shaft is locked to prevent the article from falling.

An outline of the lifting device using the lock type bidirectional clutch and an example of the structure of the bidirectional clutch will be described with reference to FIGS. 10 and 11. FIG. 10 shows an AA cross-sectional structure of an elevating device that raises and lowers an article by a belt and a pulley, and a bidirectional clutch provided in the driving device. In FIG. 11A, the output shaft is an input shaft. (B) shows the AA cross section in the state where the article is moved up and down in conjunction with each other, and (b) shows the AA cross section in the state where the output shaft is locked to prevent the article from falling.
The elevating device of FIG. 10 is a device in which a belt B is hung between the pulleys P1 and P2 arranged vertically and an article W to be transferred to the belt B is fixed, and this is rotationally driven by the upper pulley P1. A motor M capable of rotating forward and reverse is connected via a bidirectional clutch DC. The bidirectional clutch DC has an input shaft IS connected to the motor M, an output shaft OS connected to the pulley P1, and a fixed housing HG.

As shown in the cross-sectional view taken along the line AA, the input shaft IS is divided into a plurality of fan-shaped portions in the housing HG of the bidirectional clutch DC, and the output shaft OS is fitted inside the fan-shaped portions. The output shaft OS is provided with a protrusion that enters between the fan-shaped portions adjacent to the input shaft IS, and a roller R is provided between the V-shaped recess formed at the tip of the protrusion and the housing HG. It is intervening.

As shown in FIG. 11A, when the input shaft IS is rotated by the motor M, the side surface of the fan-shaped portion of the input shaft IS and the side surface of the protrusion of the output shaft OS come into contact with each other, and the output shaft OS is input. It rotates in the same direction and at the same speed while being pushed by the axis IS. The same applies when the input shaft IS rotates in the reverse direction. In the elevating device of FIG. 10, when the motor M is rotated forward and backward, the article W fixed to the belt B can be raised or lowered.
On the other hand, when the output shaft OS rotates, as shown in (b), the roller R is pushed up by the slope of the V-shaped recess and moves outward, and the protrusions of the housing HG and the output shaft OS It is sandwiched between the parts. As a result, the output shaft OS is locked and stopped at that position, and the rotation is not transmitted to the input shaft IS. That is, in the elevating device of FIG. 10, even if the drive by the motor M is stopped, the article W can be automatically prevented from falling due to its own weight. Such a lock type bidirectional clutch is disclosed in Japanese Patent No. 4805653 according to the inventor of the present applicant.

The lock-type bidirectional clutch can be applied to, for example, in a finishinger of a copier, an elevating device for transferring a paper table on which paper is placed, or an elevating device for raising and lowering a window blind of a building. By using this, it becomes possible to automatically control the power transmission by a simple device, and it becomes unnecessary to use electric power or the like as in the case of controlling by an electromagnetic clutch, and from the output shaft side. It is also possible to protect the motor of the drive source in the event of an unexpected reverse input.

By the way, in a power transmission system for rotationally driving mechanical parts or work equipment, a speed reducer or a speed increaser for changing a rotational speed or torque is also commonly used so as to match the characteristics of the driving equipment. Recently, automatic operation using power has progressed in various fields, and in OA equipment such as copiers, various equipment is often driven by using a very small motor as a drive source. Since a small motor rotates at high speed and has low torque, in such a case, a small speed reducer that adjusts the rotation speed or the like is often interposed in the power transmission system.

As the reducer, there is a friction transmission type such as a belt transmission device that uses pulleys of different diameters, but a gear type reducer is generally used, and among them, an internal gear that utilizes planetary motion is used. There is a type reducer. In this reducer, an external gear (planetary gear body) that meshes with the fixed internal gear is eccentrically arranged inside the fixed internal gear to form an inscribed gear mechanism. When the external gear is moved along the internal gear and revolved, the external gear itself rotates due to the meshing of both gears, and deceleration is performed by utilizing the difference between the revolution speed and the rotation speed of the rotation. A reducer generally called a cyclo reducer (“Cyclo” is a registered trademark) is a kind of such an inscribed gear type reducer.

The following Patent Document 2 shows an example of an inscribed gear mechanism type speed reducer for which the applicant of the present application has filed a patent application prior to the present application. The speed reducer shown in Patent Document 2 has an input member and an output member that can rotate around a common rotation axis, a fixed internal gear, and a fixed internal gear that is eccentrically arranged inside the fixed internal gear. It is equipped with a planetary gear body that revolves and rotates while meshing with. The input member is provided with a circular eccentric plate, and the output member is provided with an output external gear. The planetary gear body includes a planetary external gear that fits on the outside of the eccentric plate of the input member and meshes with the fixed internal gear, and a planetary internal gear that meshes with the output external gear. The gears are axially adjacent and integral and have a common central axis.

When the input member rotates in one direction, the eccentric plate of the input member eccentrically rotates around a common rotation axis and rotates in one direction. As a result, the planetary external gear into which the eccentric plate is fitted is revolved in one direction around a common rotation axis and is rotated in the other direction by meshing with the fixed internal gear. Since the planetary external gear is integrated with the planet internal gear and has a common central axis, the planet internal gear operates in the same manner as the planet internal gear. At this time, the output external tooth gear that meshes with the planetary external tooth gear takes out only the rotation component of the planetary external tooth gear, decelerates with respect to the rotation of the input member, and rotates on its axis.

Japanese Patent No. 4805653 Japanese Unexamined Patent Publication No. 2013-245801

In the lock type bidirectional clutch shown in Patent Document 1, in order to achieve the function, it is necessary to provide a gap between the fan-shaped portion of the input shaft IS and the protrusion of the output shaft OS, and it is necessary to provide a gap during operation. Impact noise is generated. Further, when the bidirectional clutch is applied to the elevating device of FIG. 10, there is no problem when the motor M is rotated forward to raise the article W, but when the motor M is reversed and the article W is lowered, the article W Due to gravity, the speed of the output shaft OS may repeatedly fluctuate finely, causing vibration and abnormal noise. This is due to the following reasons.
When the motor M is rotated in the reverse direction to lower the article W, the output shaft OS may rotate (overrun) faster than the input shaft IS due to the gravity acting on the article W, and when an overrun occurs, In the state shown in FIG. 11B, the roller R and the housing HG mesh with each other, and the output shaft OS is locked. This locked state is released when the roller R is pushed by the rotation of the input shaft IS, but the repeated biting and releasing causes fine fluctuations in the speed of the output shaft OS. In order to release the locked state, it is necessary to apply a torque (moment) that overcomes the frictional force acting on the roller, but this point is the same when raising the article W in the stopped state, and the motor M Is required to have a torque for releasing the bite in addition to the load torque for raising the article W.

Further, in the lock type bidirectional clutch of FIG. 10, the rotation speed of the output shaft OS is always equal to the rotation speed of the input shaft IS, and the rotation direction of the output shaft OS is also equal to the rotation direction of the input shaft IS. With the bidirectional clutch itself, it is not possible to shift gears to change the rotation direction or speed, so it is not possible to increase or decrease the torque between the input / output shafts, and when the load torque acting on the output shaft OS is large. , It is necessary to prepare a large motor that generates torque commensurate with it as a drive source.

The present invention has been made in view of the above facts, and its main technical problem is to prevent the generation of abnormal noise and the like due to operation, and to reliably maintain the locked state when the output shaft is stopped. It is to provide a new and improved lock type bidirectional clutch that can be used.

In view of the above problems, as a result of diligent studies, the present inventor has eccentricized the auxiliary internal gear to the fixed external gear that is a part of the internal planetary gear mechanism type reducer without using a biting roller. meshes with matched seen, the auxiliary internal gear and axially biased by biasing means into contact with the axial end surface of the planetary gear body, further, annular shape auxiliary internal gear formed on an inner peripheral surface It has been found that the above-mentioned main technical problem can be solved by fitting the auxiliary plate of the above to the accommodating space having a circular cross section of the fixed housing .

That is, according to the present invention, an input member and an output member that can rotate around a common rotation axis are provided, and forward / reverse rotation from the input member is transmitted to the output member and the output member. The transmission of rotation from the input member to the input member is a lock type bidirectional clutch in which the output member becomes non-rotatable and is cut off.
The input member is provided with a cylindrical eccentric ring, the output member is provided with an output internal gear, and the output member is further provided with an output internal gear.
A fixed housing having a storage space having a circular cross section and a planetary gear body housed in the storage space are provided.
The central axis of the accommodation space portion is concentric with the common rotation shaft, and a fixed external gear having a central axis concentric with the common rotation shaft is arranged in the accommodation space portion.
The planetary gear body includes a planetary internal gear that fits inside the eccentric ring of the input member and meshes with the fixed external gear, and a planetary external gear that meshes with the output internal gear. The tooth gear and the planetary external gear are adjacent to each other in the axial direction and are integrated and have a common central axis, and the planetary gear body is eccentric with respect to the common rotation axis and can revolve and rotate.
An annular-shaped auxiliary plate is further fitted in a gap in the accommodation space, and an auxiliary internal gear that meshes with the fixed external gear is a common rotation shaft on the inner peripheral surface of the auxiliary plate. Both of the lock types are formed eccentrically with respect to the relative direction, and the auxiliary internal gear is urged axially by an urging means to be brought into contact with the axial end face of the planetary internal gear. An anti-clutch is provided.

Preferably, before Symbol number of teeth and the planetary internal gear in the auxiliary gear is preferably 1 greater than and the number of teeth of the fixed outer gear the same. Preferably, the number of teeth of the output internal gear is one more than the number of teeth of the planetary external gear. Preferably, the planetary internal gear comprises a connecting member with a cylindrical fitting that fits inside the eccentric ring of the input member. It is convenient that the teeth of the fixed external gear, the planetary internal gear, the planetary external gear, and the output internal gear all have a trochoidal tooth profile. In this case, the tooth of the auxiliary internal gear preferably has a trochoidal tooth profile.

The lock type bidirectional clutch of the present invention is arranged eccentrically with respect to an input member and an output member that can rotate around a common rotation axis, a fixed external gear, and a common rotation axis, and meshes with the fixed external gear. It is equipped with a planetary gear body that revolves and rotates. The input member is provided with a cylindrical eccentric ring, and the output member is provided with an output internal gear. The planetary gear body includes a planetary internal gear that fits inside the eccentric ring of the input member and meshes with the fixed external gear, and a planetary external gear that meshes with the output internal gear. The gears are axially adjacent and integral and have a common central axis. Furthermore the fixed external gear, an auxiliary internal gear eccentrically have meshed seen if the auxiliary internal gear is being brought into contact is biased axially in the axial end face of the planetary internal gear by the biasing means The annular-shaped auxiliary plate on which the auxiliary internal gear is formed on the inner peripheral surface is gap-fitted in the accommodating space having a circular cross section of the fixed housing.

Since the lock type bidirectional clutch of the present invention has the above-mentioned configuration, the rotation from the input member to the output member is decelerated and transmitted. When the rotation is transmitted from the input member to the output member, the planetary internal gear (planetary gear body) slides with respect to the auxiliary internal gear. On the other hand, the transmission of rotation from the output member to the input member is caused by the so-called backlash in the circumferential direction due to the meshing of the planetary internal gear and the fixed external gear and the circumferential backlash due to the meshing of the auxiliary internal gear and the fixed external gear. The phase shift between them and the friction between the planetary gears and the auxiliary internal gears caused by the urging means regulate the rotation of the planetary gears, which locks and shuts off the output member.

In the lock type bidirectional clutch of the present invention, the internal gear mechanism type speed reducer is used to transmit the rotational power from the input member to the output member and cut off the transmission in the opposite direction. Since the rotation transmission from the output member is cut off without using the frictional force by locking the internal gear mechanism, the holding of the output member stopped is not limited by the frictional force. Further, since the locked state of the inscribed gear mechanism occurs immediately when trying to drive from the output member side, unlike the bidirectional clutch of FIG. 10, no impact noise is generated during operation. Further, there is no occurrence of speed fluctuation of the output member due to repeated biting and disengaging of the roller, and there is no need to apply extra torque for disengaging the biting of the roller.

The figure which shows the whole structure of the preferable embodiment of the lock type bidirectional clutch configured according to this invention. The figure which shows the input member of the lock type bidirectional clutch shown in FIG. 1 by itself. The figure which shows the output member of the lock type bidirectional clutch shown in FIG. 1 by itself. The figure which shows the housing of the lock type bidirectional clutch shown in FIG. 1 alone. The figure which shows the planetary gear body of the lock type bidirectional clutch shown in FIG. 1 by itself. The figure which shows the auxiliary plate of the lock type bidirectional clutch shown in FIG. 1 by itself. It is a figure for demonstrating the operation when the lock type bidirectional clutch shown in FIG. 1 is rotated from the input member side. It is a figure for demonstrating operation when the lock type bidirectional clutch shown in FIG. 1 is tried to rotate from an output member side. The figure which shows the whole structure of the modification of the lock type bidirectional clutch configured according to this invention. The figure which shows an example of the conventional lock type bidirectional clutch. The figure explaining the operation of the lock type bidirectional clutch of FIG.

Hereinafter, preferred embodiments of the lock type bidirectional clutch configured according to the present invention will be described in more detail with reference to the accompanying drawings.

Explaining with reference to FIG. 1, the lock type bidirectional clutch, which is configured according to the present invention and is indicated by a number 2, has an input member 4, an output member 6, a fixed external gear 8, and a planetary gear body 10. And are equipped. In FIG. 1, for easy understanding, the housing 30, the shield plate 46, and the bearings 42, 52, and 60, which will be described later, are not hatched.

Explaining with reference to FIG. 2 together with FIG. 1, the input member 4 is made of metal and includes an input shaft portion 12. The input shaft portion 12 has a cylindrical shape as a whole, and faces the outer peripheral surface of one end portion in the axial direction (the right end portion in the central vertical cross section of FIG. 1 and the AA cross section of FIG. 2) in the radial direction. A pair of notches 14 are formed. The input shaft portion 12 is connected to a drive source (not shown) such as a motor via a pair of notches 14. A circular input flange 16 is connected to the other end of the input shaft portion 12 in the axial direction (the left end thereof). The center of the input flange 16 is eccentric by e with respect to the rotation axis of the input shaft portion 12 (common rotation axis o described later). A cylindrical eccentric ring 18 extending toward the other side in the axial direction is provided on the outer peripheral edge of the input flange 16. An annular groove 20 extending continuously in the circumferential direction is formed at the other end of the inner peripheral surface of the eccentric ring 18 in the axial direction.

Explaining with reference to FIG. 1, the output member 6 is arranged adjacent to the input member 4 in the axial direction, and the output member 6 and the input member 4 are rotatable about a common rotation axis o. The output member 6 is made of metal and includes an output shaft portion 22 located coaxially with the common rotation shaft o together with the input shaft portion 12. The output shaft portion 22 has a cylindrical shape as a whole, and faces the outer peripheral surface of the other end portion in the axial direction (the left end portion in the central vertical cross section of FIG. 1 and the AA cross section of FIG. 3) in the radial direction. A pair of notches 24 are formed. The output shaft portion 22 is connected to a driven member (not shown) such as an elevating device via a pair of notches 24. A circular output flange 26 is connected to one end of the output shaft portion 22 in the axial direction (the right end thereof). The center of the output flange 26 is concentric with the common rotation axis o. An output internal gear 28 is provided on the outer peripheral edge of the output flange 26. Therefore, the output internal gear 28 is concentric with the common rotation shaft o. In the illustrated embodiment, the teeth of the output internal gear 28 have a trochoidal tooth profile, and the number of teeth is nine.

As shown in FIG. 1, the fixed external gear 8 is arranged concentrically with the common rotation shaft o. Solid Teisotoha gear 8 is provided on the stationary housing, generally designated by the numeral 30. When the housing 30 is described with reference to FIG. 1 and FIG. 4A, the housing 30 is made of metal and has a substantially square end plate 32 and a tubular outer circumference extending axially from the outer peripheral edge of the end plate. A wall 34 is provided, and a cross section accommodating an eccentric ring 18 of the input member 4, an output internal gear 28 of the output member 6, a planetary gear body 10, an auxiliary gear body described later, and the like is provided inside the outer peripheral wall 34. A circular accommodation space 36 is provided. A circular central through hole 38 through which the output shaft portion 22 of the output member 6 is inserted and rotatably supports the output shaft portion 22 is formed in the center of the end plate 32. The fixed external gear 8 is provided at the center of the end plate 32 and inside the outer peripheral wall 34 (that is, inside the accommodation space 36). The teeth of the fixed external gear 8 have a trochoidal tooth profile, and the number of teeth is nine. At the center of the fixed external gear 8, a concave portion 40 having a circular cross section is formed so as to communicate with the central through hole 38 and open in the accommodation space 36. The recess 40 is concentric with the central through hole 38, and the recess 40 is provided with a well-known bearing 42 that rotatably supports the output shaft portion 22. An outer through hole 44 that penetrates in the axial direction is also formed at each corner of the outer peripheral wall 34. A bolt used for fixing a shield plate, which will be described later, is inserted into the outer through hole 44.

The open end of the outer wall 34 is closed by the shield plate 46 shown in FIG. 4 (b). The shield plate 46 is made of metal and is a substantially square shape corresponding to the end plate 32 of the housing 30. A circular central through hole 48 through which the input shaft portion 12 of the input member 4 is inserted and rotatably supports the input shaft portion 12 of the input member 4 is formed in the center of the shield plate 46. In the center of the shield plate 46, a recess 50 having a circular cross section is also formed, which communicates with the central through hole 48 and is open on the side opposite to the central through hole 48 in the axial direction. The recess 50 is concentric with the central through hole 48, and the recess 50 is provided with a well-known bearing 52 that rotatably supports the input shaft portion 12. An outer through hole 54 that penetrates in the axial direction is formed at each corner of the shield plate 46. The housing 30 and the shield plate 46 are fastened by inserting bolts (not shown) into the outer through holes 44 and 54 and fastening them with nuts.

As shown in FIG. 1, the planetary gear 10 in the inside of the housing 30, it is arranged eccentrically with respect to the common central axis o. Explaining with reference to FIG. 1, the planetary gear body 10 is made of metal, and has a planetary internal gear 56 that fits inside the eccentric ring 18 of the input member 4 and meshes with the fixed external gear 8. It is provided with a planetary external gear 58 that meshes with the output internal gear 28. In the illustrated embodiment, the planetary internal gear 56 is fitted inside the eccentric ring 18 via a well-known bearing 60. The planetary gear body 10 includes a partition wall 61 for partitioning the planetary internal gear 56 and the planetary external gear 58, and the planetary internal gear 56 is the other side surface of the partition wall 61 (center vertical cross section of FIG. 1 and FIG. 5). The planetary external tooth gear 58 is provided on one side surface (the right side surface of the same) on the left side surface in the AA cross section. As a result, the planetary internal gear 56 and the planetary external gear 58 are adjacent to each other in the axial direction and are integrated and have a common central axis o'. The planetary gear body 10 is also formed with a through hole having a circular cross section that penetrates concentrically with the central axis o'in the axial direction, through which the output shaft portion 22 is inserted. As shown in FIG. 1, the common central axis o'of the planetary internal gear 56 and the planetary external gear 58 is located eccentrically with respect to the common rotation axis o. In the illustrated embodiment, the teeth of the planetary internal gear 56 and the planetary external gear 58 are both trochoid teeth, the number of teeth of the planetary internal gear 56 is 10, and the number of teeth of the planetary external gear 58 is 8. be. That is, the number of teeth of the planetary external gear 58 is one less than the number of teeth of the output internal gear 28.

As shown in FIG. 1, the metal auxiliary internal gear 62 also each other viewed engage the fixed external gear 8. Explaining with reference to FIG. 6 together with FIG. 1 , an annular-shaped auxiliary plate 64 is gap-fitted in the accommodating space 36 having a circular cross section, and the auxiliary internal gear 62 is the inner circumference of the auxiliary plate 64. It is formed on the surface, and the center of the auxiliary internal gear 62 is eccentric with respect to the common rotation axis o. Therefore, the auxiliary internal gear 62 is eccentrically meshed with the fixed external gear 8. The number of teeth of the auxiliary internal gear 62 is the same as the number of teeth of the planetary internal gear 56, and is one more than the number of teeth of the fixed external gear 8. The auxiliary internal gear 62 is brought into contact with the axial end face of the planetary internal gear 56 by the urging means 66. The urging means 66 is a metal wave spring, which is arranged between the input flange 16 of the input member 4 and the shield plate 46, as will be understood by reference to the central longitudinal section of FIG. The planetary gear body 10 is elastically pressed against the auxiliary plate 64 via the input member 4 and the output member 6.

ｎａ：出力内歯歯車の自転角速度
ｎｂ：遊星外歯歯車の自転角速度
ｎｃ：遊星外歯歯車の公転角速度
ａ：出力内歯歯車の歯数
ｂ：遊星外歯歯車の歯数
の関係があることから、出力内歯歯車２８（出力部材６）の自転角速度は以下のように算出される。図示の実施形態にあっては、上述したとおり、遊星外歯歯車５８の自転角速度ｎｂは１／１０、同歯車の公転角速度ｎｃは１、そして、出力内歯歯車２８の歯数ａは９、遊星外歯歯車５８の歯数ｂは８であることから、上記（式）によれば、出力内歯歯車２８の自転角速度ｎａは１／５となる。従って、出力部材６は、入力部材４の１回転に対して１／５に減速して時計方向に回転せしめられる。 Subsequently, the operation of the lock type bidirectional clutch 2 will be described with reference to FIGS. 7 and 8. As shown by each arrow in FIG. 7, when the input member 4 is rotated clockwise (when viewed from the right side of the central vertical sectional view) by the motor of the drive source, the eccentric ring 18 of the input member 4 has a common rotation axis. It rotates eccentrically around o. That is, the eccentric ring 18 rotates clockwise as a whole while moving (revolving) clockwise along a circle having a radius e around a common rotation axis o. Then, the planetary internal gear 56 fitted inside the eccentric ring 18 revolves integrally with the eccentric ring 18 as shown by each arrow in the BB cross section, and has the number of teeth with the fixed external gear 8 that meshes with the eccentric ring 18. It is rotated by the difference. In the illustrated embodiment, the fixed external gear 8 has 9 teeth and the planetary internal gear 56 has 10 teeth. Therefore, when the eccentric ring 18 makes one rotation, the planetary internal gear fitted therein is fitted. The 56 revolves by 1 and rotates by 1/10 due to the difference in the number of teeth between the planetary internal gear 56 and the fixed external gear 8. At this time, the planetary internal gear 56 is in contact with the auxiliary plate 64 in a state of being urged in the axial direction by the urging means 66, but the planetary internal gear 56 resists the friction with the auxiliary plate 64 and described above. It works as you did. Since the planetary internal gear 56 and the planetary external gear 58 are integrated, when the planetary external gear 58 rotates as described above, the output internal gear 28 is clockwise as shown by the arrow in the AA cross section. It is rotated to. At this time, in the case of the internal gear mechanism as shown in the AA cross section,

na: Rotation angular velocity of the output internal gear
nb: Rotation angular velocity of planetary external gear
nc: Revolution angular velocity of planetary external gear
a: Number of teeth of the output internal gear
b: Since there is a relationship with the number of teeth of the planetary external gear, the rotation angular velocity of the output internal gear 28 (output member 6) is calculated as follows. In the illustrated embodiment, as described above, the rotation angular velocity nb of the planetary external gear 58 is 1/10, the revolution angular velocity nc of the gear is 1, and the number of teeth a of the output internal gear 28 is 9. Since the number of teeth b of the planetary external gear 58 is 8, the rotation angular velocity na of the output internal gear 28 is 1/5 according to the above (formula). Therefore, the output member 6 is decelerated to 1/5 with respect to one rotation of the input member 4 and rotated clockwise.

On the other hand, as shown by each broken line arrow in FIG. 8, even if the output member 6 is to be rotated, the output member 6 is locked in the transmission of the rotation from the output member 6 to the input member 4. That is, the transmission of rotation from the output member 6 to the input member 4 is blocked because the output member 6 cannot rotate. This is a phase shift that occurs between the so-called backlash in the circumferential direction due to the meshing of the planetary internal gear 56 and the fixed external gear 8 and the circumferential backlash due to the meshing of the auxiliary internal gear 62 and the fixed external gear 8. This is because the rotation of the planetary gear body 10 is restricted by the friction between the planetary gear body 10 and the auxiliary internal gear 62 generated by the urging means 66.

In the lock type bidirectional clutch of the present invention, the internal gear mechanism type speed reducer is used to transmit the rotational power from the input member to the output member and cut off the transmission in the opposite direction. Since the rotation transmission from the output member is cut off without using the frictional force by locking the internal gear mechanism, the holding of the output member stopped is not limited by the frictional force. Further, since the locked state of the inscribed gear mechanism occurs immediately when trying to drive from the output member side, unlike the bidirectional clutch of FIG. 10, no impact noise is generated during operation. Further, there is no occurrence of speed fluctuation of the output member due to repeated biting and disengaging of the roller, and there is no need to apply extra torque for disengaging the biting of the roller.

FIG. 9 shows a modified example of the lock type bidirectional clutch configured according to the present invention. The modified example of the lock type bidirectional clutch represented by the number 2'as a whole and the lock type bidirectional clutch 2 described above are different in the configuration of the connection portion between the input member and the planetary gear body, and in other configurations, they are different. It is the same. In the following, for the same configuration as the lock type bidirectional clutch 2 described above, "'" is added after the number, detailed description thereof is omitted, and only different configurations will be described.

The input flange 16'and the eccentric ring 18' provided with the input member 4'have a relatively small diameter. Inside the eccentric ring 18', a cylindrical input support wall 68'concentric with the common rotation shaft o is provided, and the input support wall 68'is connected to the input flange 16'. The planetary internal gear 56'includes a connecting member 72' with a cylindrical fitting portion 70' that fits inside the eccentric ring 18'of the input member 4'. For easy understanding, in FIG. 9, the connecting member 72'is shown in light ink. As shown in the central longitudinal section of FIG. 9, in the illustrated embodiment, the fitting portion 70'is fitted inside the eccentric ring 18'via a well-known bearing 60', and is inside the fitting portion 70'. The input support wall 68'is fitted in the room so as to be relatively rotatable. In the present embodiment, the diameter of the bearing 60'can be made smaller than the diameter of the bearing 60 of the lock type bidirectional clutch 2 of FIG. 1, the manufacturing cost can be reduced, and the radial direction can be made compact. can do. A disk-shaped connection flange 74'is connected to the other end in the axial direction of the fitting portion 70'(the left end in the central vertical cross section of FIG. 9). A circular through hole 76'is formed in the center of the connection flange 74', and inside the circular through hole 76', the end face of the input support wall 68' is in contact with the output flange 26' of the output member 6'and is bearing by this. .. A cylindrical connection wall 78'that extends in the direction opposite to the fitting portion 70' is formed on the outer peripheral edge of the connection flange 74'. On the inner peripheral surface of the connecting wall 78', a plurality of locking grooves 80' that extend linearly in the axial direction are formed at equal intervals in the circumferential direction. On the outer peripheral surface of the planetary internal gear 56', a locking piece 82'that engages with the locking groove 80'in the circumferential direction is formed corresponding to the locking groove 80', and the locking groove 80'is formed. And the locking piece 82', the planetary internal gear 56'is integrated with the connecting member 72'. Since the operation of the lock type bidirectional clutch 2'is the same as the operation of the lock type bidirectional clutch 2, the description of the operation will be omitted.

Although the lock type bidirectional clutch configured according to the present invention has been described in detail with reference to the attached drawings, the present invention is not limited to the above-described embodiment and is appropriately used as long as it does not deviate from the present invention. Can be modified or changed. For example, in the illustrated embodiment, the number of teeth of the planetary external gear is set to be one less than the number of teeth of the output internal gear, but the number of teeth and the difference in the number of teeth of both gears can be arbitrarily set. .. Further, in the illustrated embodiment, both the output internal gear and the working external gear have a trochoidal tooth profile, but if the above-mentioned operation is possible, the tooth profile of both gears is not limited to the trochoid tooth profile and can be any tooth profile. It's okay to have it. Furthermore, in the illustrated embodiment, each component constituting the lock type bidirectional clutch is made of metal, but these may be formed of a synthetic resin or other appropriate material.

2: Lock type bidirectional clutch 4: Input member 6: Output member 8: Fixed external gear 10: Planetary gear 18: Eccentric wheel 28: Output internal gear 56: Planet internal gear 58: Planetary external gear 62: Auxiliary internal gear 66: Energizing means

Claims (6)

An input member and an output member that can rotate around a common rotation axis are provided, and forward / reverse rotation from the input member is transmitted to the output member, and rotation from the output member to the input member is performed. The transmission is a lock type bidirectional clutch in which the output member becomes non-rotatable and is cut off.
The input member is provided with a cylindrical eccentric ring, the output member is provided with an output internal gear, and the output member is further provided with an output internal gear.
A fixed housing having a storage space having a circular cross section and a planetary gear body housed in the storage space are provided.
The central axis of the accommodation space portion is concentric with the common rotation shaft, and a fixed external gear having a central axis concentric with the common rotation shaft is arranged in the accommodation space portion.
The planetary gear body includes a planetary internal gear that fits inside the eccentric ring of the input member and meshes with the fixed external gear, and a planetary external gear that meshes with the output internal gear. The tooth gear and the planetary external gear are adjacent to each other in the axial direction and are integrated and have a common central axis, and the planetary gear body is eccentric to the common rotation axis and can revolve and rotate.
An annular-shaped auxiliary plate is further fitted in a gap in the accommodation space, and an auxiliary internal gear that meshes with the fixed external gear is a common rotation shaft on the inner peripheral surface of the auxiliary plate. Both of the lock types are formed eccentrically with respect to the relative direction, and the auxiliary internal gear is urged axially by an urging means to be brought into contact with the axial end face of the planetary internal gear. Directional clutch. The lock type bidirectional clutch according to claim 1 , wherein the number of teeth of the auxiliary internal gear and the number of teeth of the planetary internal gear are the same and one more than the number of teeth of the fixed external gear. The lock type bidirectional clutch according to claim 1 or 2 , wherein the number of teeth of the output internal gear is one more than the number of teeth of the planetary external gear. The lock type bidirectional according to any one of claims 1 to 3 , wherein the planetary internal gear includes a connecting member having a cylindrical fitting portion that fits inside the eccentric ring of the input member. clutch. The lock type bidirectional clutch according to any one of claims 1 to 4 , wherein the teeth of the fixed external gear, the planetary internal gear, the planetary external gear, and the output internal gear all have a trochoidal tooth profile. .. The lock type bidirectional clutch according to claim 5 , wherein the tooth of the auxiliary internal gear has a trochoidal tooth profile.

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