JP2010090907A - Rotary reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a backlashless reduction gear with a simple structure achieving a low reduction ratio. <P>SOLUTION: An eccentric shaft part 16 is integrally formed on the front end of a rotation input shaft 13 of the rotary reduction gear 4, and an eccentric plate 18 revolves with a radius in correspondence with an eccentric amount in a state of rotation impossible by the eccentric rotation. A cylindrical cam follower 20 is attached to the eccentric plate 18 at an equal angular interval on the identical circle. The cam follower 20 is provided with a tapered circular outer peripheral surface 20a, and a tapered tooth surface 22a of an external tooth of a trochoid gear 22 integrally formed on a rear end of a rotation output shaft 14 is meshed with it in a backlashless state by thrust force by a pressurizing nut 23. Play of an Oldham's mechanism 19 supporting the eccentric plate 18 is eliminated by an Oldham's pressurizing mechanism composed of a set collar 24 and a shim plate 25. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a backlashless rotary speed reducer capable of realizing a reduction speed ratio, for example, a reduction speed ratio of 1/10 or less.

  Reduction gears used in industrial equipment include gear-type reduction gears, rolling ball reduction gears, cyclo reduction gears (registered trademark of Sumitomo Heavy Industries, Ltd.), and harmonic drive reduction gears (Harmonic Drive Systems registered trademark) is known. For example, a cyclo reducer is disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2003-278849).

In general, since a gear type reduction gear uses an involute tooth profile for a gear, slip occurs at a contact point of the gear. Therefore, if the backlash is removed, problems such as early wear of the tooth surface and a decrease in rotation transmission efficiency occur. The rolling ball type reducer is a mechanism that takes out the decelerated rotation by rolling the ball in the guide groove in the shape where the epicycloid curve and the hypocycloid curve face each other. There is a problem that the amount of rolling is large and wear tends to occur. The cyclo reducer fixes the pin, rotates the trochoid gear as a planetary gear eccentrically, takes out only the rotation of the trochoid gear at the inner pin hole and the inner pin arranged at equal angles in the trochoid gear, and rotates at reduced speed. It is a mechanism to obtain. It is necessary to provide a gap twice the amount of eccentricity between the inner pin hole and the inner pin due to the mechanism, and it is difficult to remove backlash. Although the harmonic drive speed reducer has a small number of components and high angle transmission accuracy, it is difficult to realize a reduction speed ratio of less than 1/50 due to the structure.
JP 2003-278849 A

  Here, there is a demand for a backlashless speed reducer with a reduced speed ratio. If a gear type reduction gear is intended to realize backlash-free, problems such as early wear of the tooth surface and a decrease in rotation transmission efficiency occur. The rolling ball type speed reducer requires complicated processing, and high processing accuracy is required to make it backlash-free. The cyclo reducer is difficult to realize backlash-less. Furthermore, it is difficult for a harmonic drive speed reducer to achieve a reduction speed ratio, for example, 1/10 or less.

  In view of these points, an object of the present invention is to propose a rotary speed reducer with a reduced speed ratio and a simple structure without backlash.

In order to solve the above problems, the rotary speed reducer of the present invention is
A rotary input shaft;
With the rotation of the rotation input shaft, an eccentric rotation shaft that rotates eccentrically about the rotation center axis of the rotation input shaft,
An eccentric plate that is supported in a state in which rotation is impossible, and that performs a revolving motion about the rotation center axis along with the eccentric rotation of the eccentric rotation shaft;
A cylindrical rotatable cam follower that is attached to one end face of the eccentric plate in the direction of the rotation center axis and is equiangularly spaced on the same circle and extends in the direction of the rotation center axis.
A tooth profile is defined by an epitrochoid curve that can be meshed with each cam follower at the same time, and there are external teeth having a smaller number of teeth than the number of cam followers, and a trochoid gear that can rotate around the rotation center axis,
A rotary output shaft attached coaxially to the trochoid gear;
A pressurizing mechanism that applies a thrust force in a direction in which the cam follower and the trochoid gear are relatively pressed;
The circular outer peripheral surface of each cam follower is a tapered circular outer peripheral surface whose outer diameter gradually decreases toward the trochoid gear,
The tooth surface of the trochoid gear is a tapered tooth surface capable of making line contact with the tapered circular outer peripheral surface of the cam follower.

  In the rotary speed reducer of the present invention, the contact point between the cam follower and the trochoid gear is a rolling contact, so that backlash can be removed, the contact portion is less worn, and the rotation transmission efficiency is high. Further, since the complicated processed parts requiring accuracy are only the tooth surfaces of the trochoid gear, they can be manufactured easily and inexpensively. Further, since the cam follower is caused to revolve and obtain a reduced rotation directly from the trochoid gear, it is easy to remove the backlash. Further, theoretically, a reduction speed ratio of ½ can be realized, and a high reduction ratio of, for example, 1/1000 or more can be realized by increasing the number of stages.

  In particular, in the present invention, the circular outer peripheral surface of the cam follower and the tooth surface of the trochoid gear are tapered surfaces, and the thrust force is applied by the pressurizing mechanism so as to ensure that they are in a line contact state. Therefore, meshing (contact) between them is ensured, and a reduction gear with high rotation transmission efficiency without backlash can be realized.

  Here, the eccentric plate may be supported on the circular outer peripheral surface of the eccentric rotation shaft in a rotatable state, and the eccentric plate may be supported in an unrotatable state by an Oldham mechanism. The Oldham mechanism includes a rotation restricting plate that supports the eccentric plate in a state of being movable in a first direction orthogonal to the rotation center axis via the first rolling element, and the rotation restricting plate. It can be set as the structure provided with the stationary plate supported in the state which can move to the 2nd direction orthogonal to the said rotation center axis line and the said 1st direction via 2 rolling elements.

  In this case, an Oldham pressurization mechanism that applies a pressing force in a direction in which the eccentric plate, the rotation restricting plate, and the fixed plate are pressed against each other is disposed, and rotation transmission caused by rattling of these members is provided. It is desirable to prevent a decrease in efficiency.

The rotary speed reducer of the present invention is
A cylindrical reducer housing,
At the rear end of the speed reducer housing, the cylindrical fixing plate is coaxially connected and fixed,
The rotation output shaft includes a rear shaft portion located in the reducer housing, and a distal shaft portion protruding forward from the front end of the reducer housing,
The rear shaft portion is supported in a rotatable state by the speed reducer housing via an output side bearing,
The trochoid gear is coaxially attached to the rear end portion of the rear shaft portion,
The rotary input shaft extends from the rear side through the fixed plate into the speed reducer housing,
The rotary input shaft is supported in a freely rotatable state by the fixed plate via an input-side rear bearing, and a tip portion of the rotary input shaft is connected to the rotary output shaft via an input-side front bearing. It is supported in a freely rotatable state by the rear end,
The eccentric rotation shaft may be integrally formed on the outer peripheral surface of the rotation input shaft.

  In this case, as the pressurizing mechanism, a pressurizing nut that is screwed into the front end opening of the speed reducer housing and that applies a thrust force to the outer ring of the output side bearing can be used. An appropriate thrust force can be applied by adjusting the screwing amount of the pressurizing nut.

  Further, as the Oldham pressurizing mechanism, a collar fixed to a rear side portion of the inner ring of the rear bearing on the rotation input shaft and a shim plate inserted between the inner ring and the collar can be used. By adjusting the thickness of the shim plate, the Oldham mechanism can be maintained in an appropriate state without backlash.

  In the rotary speed reducer according to the present invention, a cylindrical cam follower arranged at equal angular intervals on the same circle revolves around the rotation center axis, and is directly decelerated and rotated from a trochoid gear that is engaged (contacted). To take out. Further, the outer peripheral surface of the cam follower and the tooth surface of the trochoid gear are tapered surfaces, and a thrust force is applied by a pressurizing mechanism so that these surfaces are surely brought into a line contact state. Therefore, according to the present invention, a reduction gear with a reduced speed ratio, no backlash and a simple structure can be realized.

  Embodiments of a rotary speed reducer to which the present invention is applied will be described below with reference to the drawings.

(overall structure)
Fig.1 (a) is an end elevation which shows the front end surface of the rotary actuator provided with the rotary speed reducer which concerns on this Embodiment, FIG.1 (b) is the side view, and the part of a rotary speed reducer is A-. It is shown in a cross section cut along line A. FIG. 2 is a perspective view with a part cut away to show the internal configuration of the rotary speed reducer in the rotary actuator, and FIG. 3 is an explanatory view showing the positional relationship between the cam follower and the trochoid gear.

  The rotary actuator 1 has a motor 2 and a rotary speed reducer 4 connected and fixed coaxially to a mounting flange 3 at the front end of the motor 2.

  The rotary speed reducer 4 includes a cylindrical speed reducer housing 11, and a cylindrical fixing plate 12 is connected and fixed coaxially to the rear end of the speed reducer housing 11. Inside the reduction gear housing 11 and the fixed plate 12, a rotational input shaft 13 is coaxially disposed on the rear side thereof, and a rotational output shaft 14 is coaxially disposed on the front side thereof. The rotational output shaft 14 is decelerated. Projecting forward from the front end of the machine housing 11. A motor output shaft 15 is connected and fixed to the rotary input shaft 13 in a coaxial state.

  In the speed reducer housing 11, an eccentric shaft portion 16 that is eccentric by a predetermined amount with respect to the rotation center axis 1 a is integrally formed at the distal end portion of the rotation input shaft 13. An eccentric plate 18 having a constant thickness is supported on a circular outer peripheral surface of the eccentric shaft portion 16 via a bearing 17 in a rotatable state. The eccentric plate 18 is supported by the fixed plate 12 through the Oldham mechanism 19 in a state in which it cannot rotate, and corresponds to the amount of eccentricity about the rotation center axis 1a as the eccentric shaft portion 16 rotates. Revolve around the radius.

  A plurality of, for example, ten cylindrical cam followers 20 (20 (0) to 20 (9)) are arranged at equal angular intervals on the same circle on the front end face of the eccentric plate 18 (see FIG. 3). ). Each cam follower 20 is supported so as to be rotatable about a shaft 21 protruding from the end face of the eccentric plate 18 in the direction of the rotation center axis 1a. A trochoid gear 22 is disposed inside these cam followers 20. The trochoid gear 22 is integrally formed at the rear end of the rotary output shaft 14, and its external tooth profile is defined by a trochoid curve that can simultaneously engage (contact with) each cam follower 20. The number of teeth of the trochoid gear 22 of this example is “9” which is “1” less than that of the cam follower 20 (in FIG. 3, each tooth is indicated by A to I).

  Here, the contact state between the cam follower 20 and the trochoid gear 22 is ensured by the thrust force applied by the pressurizing mechanism including the pressurizing nut 23. Further, rattling in the direction of the rotation center axis 1 a in the Oldham mechanism 19 is prevented by an Oldham pressurizing mechanism including a set collar 24 and a shim plate 25 attached to the rear end portion of the rotation input shaft 13.

(Configuration of each part)
Next, the structure of each part of the rotary speed reducer 4 will be described. First, the speed reducer housing 11 includes a cylindrical front half portion 11a and a rear half portion 11b whose outer peripheral surface is rectangular, and a fixing plate 12 having the same outer peripheral shape is fixed to the rear end of the rear half portion 11b. ing. A cylindrical rotary input shaft 13 is rotatably supported on the inner peripheral surface of a circular hole formed in the center of the fixed plate 12 via an input side rear bearing 26. The front end portion of the rotary input shaft 13 is supported in a rotatable state by an input-side front bearing 27 attached to the inner peripheral surface of a recess formed on the rear end surface of the rotary output shaft 14.

  The Oldham mechanism 19 disposed between the fixed plate 12 and the eccentric plate 18 includes a ring-shaped rotation restricting plate 30 disposed therebetween. On the rear end face of the rotation restricting plate 30 and the front end face of the fixing plate 12 facing the rotation restricting plate 30, one or a plurality of strips having a fixed length extending in a direction perpendicular to the rotation center axis 1a are provided at portions facing each other. Strip guide grooves 30a and 12a are formed. In these guide grooves 30a and 12a, rolling elements 31 such as steel balls and cylindrical rollers are accommodated in a freely rollable state.

  Similarly, the front end face of the rotation restricting plate 30 and the rear end face of the eccentric plate 18 facing the rotation restricting plate 30 are orthogonal to the rotation center axis 1a and the guide grooves 30a, 12a at the facing portions. One or a plurality of guide grooves 30b, 18a having a certain length extending in the direction are formed. In these guide grooves 30b and 18a, rolling elements 32 such as steel balls and cylindrical rollers are accommodated in a freely rollable state. Here, the direction of the rear guide grooves 30a, 12a and the direction of the front guide grooves 30b, 18a of the rotation restricting plate 30 are set to be orthogonal to each other.

  As described above, the Oldham mechanism 19 is configured to support the eccentric plate 18 so as to be movable by a certain amount in the radial direction. When the eccentric shaft portion 16 at the tip of the rotary input shaft 13 rotates eccentrically with the rotation of the rotary input shaft 13, the eccentric plate 18 supported by the Oldham mechanism 19 is prevented from rotating, and the eccentric amount about the rotation center axis 1a is increased. Revolve around the corresponding radius.

  Here, the set collar 24 of the Oldham pressurizing mechanism is fixed to the outer peripheral surface of the rear end portion that protrudes rearward from the input-side rear bearing 26 attached to the fixed plate 12 in the rotary input shaft 13. A ring-shaped shim plate 25 having a constant thickness is inserted between the set collar 24 and the inner ring 26a of the input side rear bearing 26. By increasing the thickness of the shim plate 25 to be inserted, the eccentric plate 18 is relatively pulled backward, and the eccentric plate 18, the rotation restricting plate 30 and the fixed plate 12 are pressed against each other. Thereby, the rotation transmission error and backlash resulting from the clearance gap between the rolling element arrange | positioned among these and a guide groove can be suppressed. Instead of the set collar 24 and the shim plate 25, the inner ring 26a of the input side rear bearing 26 may be urged in the sliding direction by a pressurizing nut screwed into the outer peripheral surface of the rotary input shaft 13.

  Next, each cam follower 20 attached to the front end face of the eccentric plate 18 in a rotatable state includes a tapered cylindrical surface 20a whose outer diameter gradually decreases toward the front (output side), that is, toward the trochoid gear 22. ing. Similarly, the tooth surface 22a of the external teeth of the trochoid gear 22 is a taper surface whose outer diameter gradually decreases toward the rear (input side), that is, toward the cam follower 20, and is linear with the tapered circular outer peripheral surface 20a of the cam follower 20. Contact is possible.

  The rotary output shaft 14 in which the trochoid gear 22 is integrally formed at the rear end includes a rear shaft portion 14a having an outer diameter slightly smaller than that of the trochoid gear 22, and a slightly smaller diameter intermediate shaft portion formed on the front side. 14b and a front end side shaft portion 14c formed on the front side. The rear end portions of the rear side shaft portion 14 a and the front end side shaft portion 14 c are supported in a rotatable state by an output side rear bearing 33 and an output side front bearing 34 attached to the inner peripheral surface of the speed reducer housing 11.

  Here, a pressurizing nut 23 is screwed and fixed to the front end opening of the speed reducer housing 11 from the front. The pressurizing nut 23 has a male screw cut on the outer peripheral surface, and a female screw that can be screwed to the male screw is cut on the inner peripheral surface of the front end opening of the speed reducer housing 11. When the pressurizing nut 23 is screwed in, the pressurizing nut 23 presses against the outer ring 33a of the output-side front bearing 33, and a thrust force directed rearward is applied to the rotary output shaft 14 through the bearing 33. As a result, the tapered tooth surface 22a of the trochoid gear 22 formed integrally with the rear end of the rotation output shaft 14 is pressed against the tapered outer peripheral surface 22a of each cam follower 20, and the contact state between them is ensured. The meshing state without backlash can be formed.

  Note that a thrust force may be applied using a shim plate instead of the pressurizing nut. For example, when the rotary output shaft 14 is a disk-shaped flange type, a thrust plate having a predetermined thickness can be sandwiched between the output flange and the bearing to adjust the thrust force.

(Decelerated rotational motion)
When the motor 2 of the rotary actuator 1 is driven, the rotary input shaft 13 connected to the output shaft 15 rotates, and the eccentric plate 18 rotates around the rotation center axis 1a by the eccentric shaft portion 16 at the front end portion thereof. Do. In this example, when the eccentric plate 18 performs a revolving motion (eccentric rotation) once, the cam follower 20 swings by the difference between the number of teeth and the number of teeth of the trochoid gear 22, that is, by one tooth. The trochoid gear 22 meshing with (in contact with) the cam follower 20 rotates by one tooth around the rotation center axis 1a in the direction opposite to the rotation direction of the rotation input shaft 13. Therefore, the rotation output shaft 14 with which the trochoid gear 22 is integrally formed rotates in a direction opposite to the input rotation shaft 13 at a reduction ratio of 1/9 of the input rotation speed. Further, since the backlash of the rolling contact portion can be removed by the pressurizing mechanism including the pressurizing nut 23 and the Oldham pressurizing mechanism 19 including the set collar 24 and the shim plate 25, the rotation transmission error can be reduced.

(A) is an end view which shows the front end surface of the rotary actuator provided with the rotary speed reducer to which this invention is applied, (b) is the side view, The part of the rotary speed reducer was cut | disconnected by the AA line | wire It is shown in cross section. FIG. 2 is a perspective view with a part cut away to show an internal configuration of a rotary speed reducer in the rotary actuator of FIG. 1. It is explanatory drawing which shows the relationship between the cam follower of a rotary reduction gear, and a trochoid gear.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotary actuator 1a Rotation center axis 2 Motor 3 Mounting flange 4 Rotary reduction gear 11 Reduction gear housing 12 Fixed plate 13 Rotation input shaft 14 Rotation output shaft 15 Motor output shaft 16 Eccentric shaft part 17 Bearing 18 Eccentric plate 19 Oldham mechanism 20 Cam follower 20a Tapered circular outer peripheral surface 22 Trochoid gear 22a Tapered tooth surface 23 Pressurizing nut 24 Set collar 25 Shim plate 26 Input side rear bearing 26a Inner ring 27 Input side front bearing 30 Rotation restricting plates 31, 32 Rolling elements 33, 34 Output side bearing 34a outer ring

Claims (6)

A rotary input shaft (13);
With the rotation of the rotation input shaft (13), an eccentric rotation shaft (16) that rotates eccentrically about the rotation center axis (1a) of the rotation input shaft (13);
An eccentric plate (18) that is supported in a state in which rotation is not possible, and that performs a revolving motion about the rotation center axis (1a) along with the eccentric rotation of the eccentric rotation shaft (16);
A cylindrical rotation attached to one end face of the eccentric plate (18) in the direction of the rotation center axis (1a) on the same circle at equal angular intervals and extending in the direction of the rotation center axis (1a). A free cam follower (20),
A tooth profile is defined by an epitrochoid curve that can simultaneously mesh with each cam follower (20), and there are fewer external teeth than the number of cam followers (20), and the rotation center axis (1a) is the center. A rotatable trochoid gear (22);
A rotary output shaft (14) attached coaxially to the trochoid gear (22);
A pressurizing mechanism (23) that applies a thrust force in a direction in which the cam follower (20) and the trochoid gear (22) are relatively pressed;
The circular outer peripheral surface of each cam follower (20) is a tapered circular outer peripheral surface (20a) whose outer diameter gradually decreases toward the trochoid gear (22),
The toothed surface of the trochoid gear (22) is a tapered toothed surface (22a) capable of linear contact with the tapered circular outer peripheral surface (20a) of the cam follower (20). ). The rotary speed reducer (4) according to claim 1,
The eccentric plate (18) is supported on the circular outer peripheral surface of the eccentric rotation shaft (16) in a rotatable state.
An Oldham mechanism (19) supporting the eccentric plate (18) in a state in which it cannot rotate,
This Oldham mechanism (19)
A rotation restricting plate (30) supporting the eccentric plate (18) in a movable state in a first direction perpendicular to the rotation center axis (1a) via the first rolling element (32); ,
The rotation restricting plate (30) is supported via a second rolling element (31) so as to be movable in a second direction that is diametered from the rotation center axis (1a) and the first direction. A rotary speed reducer (4) comprising a fixed plate (12). In the rotary speed reducer (4) according to claim 2,
An Oldham pressurizing mechanism (24, 25) for applying a pressing force in a direction in which the eccentric plate (18), the rotation restricting plate (30) and the fixed plate (12) are pressed against each other. Characteristic rotary reducer (4). The rotary speed reducer (4) according to claim 3,
A cylindrical reducer housing (11),
The cylindrical fixing plate (12) is connected and fixed coaxially to the rear end of the reduction gear housing (11),
The rotation output shaft (14) includes a rear shaft portion (14a, 14b) positioned in the speed reducer housing (11) and a front end side projecting forward from the front end of the speed reducer housing (11). A shaft portion (14c),
The rear shaft portions (14a, 14b) are supported by the reduction gear housing (11) in a rotatable state via output side bearings (33, 34),
The trochoid gear (22) is attached coaxially to the rear end of the rear shaft portion (14a),
The rotary input shaft (13) extends from the rear side through the fixed plate (12) into the speed reducer housing (11),
The rotary input shaft (13) is supported by the fixed plate (12) through an input-side rear bearing (26) so as to be rotatable, and the tip of the rotary input shaft (13) is It is supported in a rotatable state by a rear end portion of the rotation output shaft (14) via an input side front bearing (27),
The rotary speed reducer (4), wherein the eccentric rotation shaft (16) is integrally formed on an outer peripheral surface of the rotation input shaft (13). The rotary speed reducer (4) according to claim 4,
The pressurizing mechanism includes a pressurizing nut (23) that is screwed into a front end opening of the speed reducer housing (11) and applies a thrust force to the outer ring (34a) of the output side bearing (34). A rotary speed reducer (4) characterized by The rotary speed reducer (4) according to claim 5,
The Oldham pressurizing mechanism is
A collar (24) fixed to a rear side portion of the inner ring (26a) of the input-side rear bearing (26) in the rotary input shaft (13), and inserted between the inner ring (26a) and the collar (24). A rotary speed reducer (4) characterized by comprising a shim plate (25).

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