WO2016056633A1 - ウォーム減速機およびウォーム減速機の組立方法 - Google Patents
ウォーム減速機およびウォーム減速機の組立方法 Download PDFInfo
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- WO2016056633A1 WO2016056633A1 PCT/JP2015/078681 JP2015078681W WO2016056633A1 WO 2016056633 A1 WO2016056633 A1 WO 2016056633A1 JP 2015078681 W JP2015078681 W JP 2015078681W WO 2016056633 A1 WO2016056633 A1 WO 2016056633A1
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- Prior art keywords
- worm
- wheel
- housing portion
- pair
- bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
- B62D5/0409—Electric motor acting on the steering column
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H2057/0213—Support of worm gear shafts
Definitions
- the present invention relates to a worm speed reducer that is used by being incorporated in, for example, an electric power steering apparatus and an assembling method thereof.
- the steering apparatus for an automobile transmits the rotation of the steering wheel 1 to the input shaft 3 of the steering gear unit 2, and pushes the pair of left and right tie rods 4, 4 as the input shaft 3 rotates. Pull to give the steering angle to the front wheels.
- the steering wheel 1 is supported and fixed to the rear end portion of the steering shaft 5, and the steering shaft 5 is rotatably supported by the steering column 6 with the cylindrical steering column 6 inserted in the axial direction.
- the front end portion of the steering shaft 5 is connected to the rear end portion of the intermediate shaft 8 via a universal joint 7, and the front end portion of the intermediate shaft 8 is connected to the input shaft 3 via another universal joint 9. .
- FIG. 15 shows a structure described in Patent Document 1 as an example of a conventional structure of a worm speed reducer incorporated in an electric power steering apparatus.
- the worm speed reducer 21 is provided inside the speed reducer housing 11 fixed to the electric motor 10 a, the worm 14 having the worm teeth 13 formed in the axially intermediate portion of the worm shaft 12, And a worm wheel 15 that meshes.
- the worm 14 is rotatably supported at both ends in the axial direction inside the worm accommodating portion 17 of the housing 11 by a pair of rolling bearings 16a and 16b such as deep groove type ball bearings. By connecting one end of the worm 14 (the left end in FIG. 15) to the output shaft 18 of the electric motor 10a, the worm 14 can be driven to rotate.
- the worm wheel 15 is rotatably provided inside the wheel housing portion 19 of the housing 11, and its own rotation center axis is arranged at a twisted position with respect to the worm 14.
- the worm wheel 15 is made by connecting and fixing a synthetic resin tooth portion 20 around a metal wheel portion 29 for the purpose of reducing the manufacturing cost and reducing the weight. Then, by engaging the tooth portion 20 with the worm tooth 13 without a gap (with zero backlash), the rotational force is generated between the worm wheel 15 and the worm 14 and a time lag based on the backlash is generated. It can be transmitted without any problems.
- the worm wheel 15 is fitted and fixed to a portion near the front end of the steering shaft 5a. As a result, the rotational driving force generated by the electric motor 10a can be transmitted to the steering shaft 5a via the worm reduction gear 21 including the worm 14 and the worm wheel 15.
- the above-described worm reduction gear 21 is assembled as follows, for example. First, in the housing 11, a bearing holding portion 22a provided at the back end portion (the right end portion in FIG. 15) of the worm accommodating portion 17 that accommodates the worm 14 is connected to the tip side rolling bearing 16a (on the right side in FIG. 15). The outer ring is fixed internally (with an interference fit). Next, the worm wheel 15 is rotatably supported in the wheel accommodating portion 19 of the housing 11. Then, the worm 14 is offset radially outward (upward in FIG. 15) of the worm wheel 15 with respect to the central axis of the worm housing portion 17 so that the worm teeth 13 do not interfere with the tooth portion 20 of the worm wheel 15.
- the worm housing portion 17 is inserted into the worm housing portion 17 through the opening of the worm housing portion 17 in a distorted state.
- the worm 14 is displaced inwardly in the radial direction of the worm wheel 15 (downward in FIG. 15), and the worm tooth 13 and the tooth part 20 of the worm wheel 15 are mutually connected.
- Engage While rotating the worm wheel 15 in a state where the worm teeth 13 and the tooth portions 20 are engaged with each other, the worm 14 is further inserted into the worm accommodating portion 17 and the tip of the worm 14 is connected to the rolling bearing 16a on the tip side. Press fit into the inner ring.
- the base end side rolling bearing 16b (FIG. 15 (to the left) (the outer ring of the rolling bearing 16b on the base end side is fitted into the bearing holding portion 22b by a clearance fit or an interference fit, and the inner ring is fitted onto the outer peripheral surface of the intermediate portion of the worm 14 by an interference fit.
- the base end side rolling bearing 16b (FIG. 15 (to the left) (the outer ring of the rolling bearing 16b on the base end side is fitted into the bearing holding portion 22b by a clearance fit or an interference fit, and the inner ring is fitted onto the outer peripheral surface of the intermediate portion of the worm 14 by an interference fit.
- the axial displacement of the rolling bearing 16 b on the proximal end side and the worm 14 is prevented.
- the output shaft 18 of the electric motor 10a is connected to the base end part (left end part of FIG. 15) of the worm
- the worm 14 and a pair of rolling bearings 16a and 16b for rotatably supporting the worm 14 are separately assembled in the worm accommodating portion 17 of the housing 11. For this reason, an assembly cost increases and the manufacturing cost of the worm reduction gear 21 increases.
- a worm shaft with each ball bearing is inserted into a worm shaft housing portion of a housing to which a preload application member is attached, and after insertion, each elastic restoring force of an arm portion of the preload application member Preload is applied to the ball bearing.
- the worm shaft since the worm shaft is inserted while the outer ring of the ball bearing on the base end side is in contact with the arm portion of the preload applying member, the worm shaft needs to be moved along the axial direction. For this reason, it is necessary to assemble the worm wheel after assembling the worm shaft so as not to interfere with the ball bearing on the tip side when the worm shaft is assembled.
- the present invention provides a worm speed reducer and an assembling method thereof that can reduce the assembling cost in view of the above circumstances.
- the worm speed reducer includes a housing, a worm wheel, and a worm.
- the housing includes a wheel housing portion and a worm housing portion that is in a twisted position with respect to the wheel housing portion and is partially continuous with the wheel housing portion.
- the worm wheel is rotatably supported in the wheel housing portion.
- the worm is provided with a worm tooth at an axially intermediate portion of the worm shaft, and in a state where the worm tooth is engaged with the worm wheel, two axial positions sandwiching the worm tooth are provided by a pair of bearings. It is rotatably supported in the worm housing part.
- the worm wheel is rotatably supported in the wheel housing portion, and the pair of worm gears are positioned at the two positions in the axial direction across the worm teeth of the worm.
- An outer side of the worm housing portion is inserted into the worm housing portion in a state where the worm is offset radially outward of the worm wheel so that the worm teeth and the worm wheel do not interfere with each other by externally fitting a bearing. Insert from.
- the bearing externally fitted to the front side in the worm insertion direction of the pair of bearings passes through the outer diameter side of the portion of the outer peripheral edge (tooth tip circle) of the worm wheel that protrudes most in the worm housing portion.
- the worm is displaced inward in the radial direction of the worm wheel, the worm teeth and the worm wheel are meshed, and the worm teeth and the worm wheel are meshed with each other, and a predetermined position in the worm housing portion is obtained.
- the worm is rotatably supported with respect to the worm housing portion by the pair of bearings.
- the outer diameter of the bearing existing on the front side in the insertion direction of the worm is set to the outer peripheral edge (tooth tip circle) of the worm wheel with respect to the radial direction of the worm.
- the distance is made smaller than the distance between the most protruding portion in the worm housing portion and the inner surface of the worm housing portion.
- the outer diameter of the bearing fitted on the front side in the insertion direction of the worm may be smaller than the diameter of the tip circle of the worm tooth.
- the outer diameter of the bearing fitted on the front side in the insertion direction of the worm may be larger than the diameter of the root circle of the worm tooth.
- each of the pair of bearings is a rolling bearing in which a plurality of rolling elements are provided between an outer ring and an inner ring, and 2 in the inner peripheral surface of the worm housing portion with respect to the axial direction of the worm.
- a pair of bearing holding portions for holding the outer rings of the pair of rolling bearings may be provided at positions. Then, after the outer ring of one rolling bearing of the pair of rolling bearings begins to be fitted into one bearing holding portion of the pair of bearing holding portions, the pair of rolling bearings The outer ring of the other rolling bearing may begin to be fitted into the other bearing holding portion of the pair of bearing holding portions.
- a preload application mechanism for elastically pressing the worm teeth toward the worm wheel may not be provided.
- the one bearing holding portion provided at the inner end of the worm housing portion has an inner peripheral surface having a smaller diameter than the inner peripheral surface of the worm housing portion, and the worm housing portion has an inner peripheral surface thereof.
- a guide portion that decreases in diameter from the bearing holding portion toward the bearing holding portion, and the bearing that is fitted on the front side in the insertion direction of the worm is brought into contact with the guide portion while the worm is placed in the radial direction of the worm wheel.
- the worm teeth and the worm wheel may be engaged with each other.
- each of the pair of bearings is a rolling bearing in which a plurality of rolling elements are provided between an outer ring and an inner ring, and the worm is the pair of rolling elements.
- the bearings are rotatably supported by a pair of bearing holding portions provided at two positions on the inner peripheral surface of the worm housing portion.
- one of the pair of bearing holding portions provided at the inner end of the worm accommodating portion has a bottomed cylindrical shape, and the inner ring is provided at the tip of the worm of the pair of rolling bearings.
- the outer ring of one of the rolling bearings with the outer fitting fixed is directly fitted (press-fitted) into the one bearing holding portion without any other member interposed.
- the outer diameter of the outer ring of the one rolling bearing is set to a portion of the outer peripheral edge (tooth circle) of the worm wheel that protrudes most in the worm housing portion with respect to the radial direction of the worm, and the worm housing portion. It is smaller than the distance between the inner surface.
- the outer diameter of the one rolling bearing may be smaller than the diameter of the tip circle.
- the outer diameter of the one rolling bearing may be larger than the root diameter of the worm tooth.
- a relief recess that is recessed radially outward may be formed in an upper portion of the inner peripheral surface of the worm housing portion, and the relief recess has an arc shape having a first radius, and the first radius is The second radius, which is the outer radius of the worm, may be greater than or equal to the second radius.
- the one bearing holding portion provided at the inner end of the worm housing portion has an inner peripheral surface having a smaller diameter than the inner peripheral surface of the worm housing portion, and the worm housing portion has an inner peripheral surface thereof.
- a guide portion that decreases in diameter toward the bearing holding portion may be provided.
- the inner diameter of the other bearing holding portion on the opening side of the worm housing portion is d 22d
- the outer diameter of the outer ring of the rolling bearing on the front side in the worm insertion direction is D 16c
- the outer diameter of the worm wheel is D 15 and the distance between the central axis of the worm wheel and the central axis of the worm housing portion is L
- a configuration satisfying the relationship of the following expression (1) may be used.
- the worm and a pair of bearings for rotatably supporting the worm can be integrally assembled in the worm housing portion of the housing. Therefore, the manufacturing cost of the worm speed reducer can be reduced.
- the worm is inserted into the worm housing portion with the worm wheel being offset radially outward so that the worm teeth and the worm wheel do not interfere with each other.
- the bearing on the front side passes through the outer diameter side of the portion of the worm wheel that protrudes most in the worm housing portion, and then the worm teeth and the worm wheel are engaged with each other.
- the axial displacement of the worm in the state where the worm teeth and the worm wheel are meshed with each other is not offset, and the assembly work is started at the beginning. Therefore, the amount of the worm teeth can be reduced as compared with the case where the worm teeth and the worm wheel are engaged with each other (when there is no space for offsetting the worm). As a result, for example, even when no backlash is provided between the worm teeth and the worm wheel, it is possible to hardly cause damage such as scratches on the worm teeth and the worm wheel.
- the worm can be assembled into the worm housing portion in a state where positioning in the radial direction is achieved in the final stage of the assembling work into the worm housing portion. Moreover, since the above-mentioned worm speed reducer is assembled by the assembling method as described above, the manufacturing cost can be reduced.
- Sectional drawing which shows 1st Embodiment of this invention in the state before assembling a housing and a worm
- the first embodiment of the present invention is inserted in the worm housing portion of the housing and the one rolling bearing, which is fitted and fixed to the tip portion of the worm, is positioned on the outer diameter side of the uppermost portion of the worm wheel.
- FIG. XX sectional drawing of FIG. Sectional drawing which shows 1st Embodiment of this invention in the state which displaced the worm to the radial inside of the worm wheel, and mesh
- the worm is further inserted into the worm housing portion from the state of FIG. 7, and the side surface of the rolling bearing on the rear side in the insertion direction of the worm and the end surface of the worm housing portion are in contact with each other, similar to FIG. Figure.
- FIG. 9 is a view similar to FIG. 7, showing the worm displaced from the state of FIG.
- FIG. 10 is a view similar to FIG. 7, showing the worm further inserted into the worm housing portion from the state of FIG. 9.
- FIG. 3 is a cross-sectional view showing a state in which a worm in which worm teeth are not formed to the end is displaced inward in the radial direction of the worm wheel and the worm teeth and the worm wheel are engaged with each other.
- Sectional drawing which shows the modification of this invention which provided the guide part in the housing.
- the partially cut side view which shows an example of the steering apparatus for motor vehicles known conventionally. Sectional drawing of the part which incorporated the worm reduction gear among power steering devices.
- First Embodiment 1 to 6 show a first embodiment of the present invention.
- the worm and a pair of bearings for rotatably supporting the worm are integrally assembled in the worm housing portion of the housing to reduce the assembly cost.
- the worm reducer 21a in the method of assembling the worm reducer of the present embodiment is basically the same as the worm reducer 21 shown in FIG. 15 described above except for the dimensional relationship of a part of each member constituting the worm reducer 21a. Has the same configuration.
- the worm speed reducer 21a of the present embodiment is provided inside the speed reducer housing 11a fixed to the electric motor 10a, and the worm 14a in which the worm teeth 13 are formed in the intermediate portion in the axial direction of the worm shaft 12. And a worm wheel 15 that meshes with the worm teeth 13.
- the housing 11a includes a wheel accommodating portion 19 that accommodates the worm wheel 15, and a worm accommodating portion 17a that is provided in a state where a part of the wheel accommodating portion 19 is continuous (opened).
- the central axis of the wheel accommodating portion 19 and the central axis of the worm accommodating portion 17a are in a twisted positional relationship with each other.
- the worm 14a has a distal end portion (right end portion in FIGS.
- the rolling bearings 16c and 16d are rotatably supported inside the worm accommodating portion 17a of the housing 11a. That is, the tip side of the pair of rolling bearings 16c and 16d (the front side in the insertion direction of the worm 14a with respect to the worm housing portion 17a when the worm reduction gear 21a is assembled, the right side in FIGS. 1, 2, 4 to 6).
- the inner ring constituting the rolling bearing 16c is externally fitted and fixed to the distal end portion of the worm 14a (externally fitted with an interference fit), and the outer ring constituting the rolling bearing 16c on the distal end side is connected to the rear end portion (see FIG.
- the inner side of the bearing holding portion 22a provided on the back side is provided with a gap fit.
- the outer ring constituting the rolling bearing 16c on the distal end side may be fitted into the bearing holding portion 22a on the inner side by an interference fit.
- the base end side of the pair of rolling bearings 16c and 16d (the rear side in the insertion direction of the worm 14a with respect to the worm housing portion 17a when the worm reduction gear 21a is assembled, the left side of FIGS.
- the inner ring constituting the rolling bearing 16d is fitted and fixed to the proximal end portion of the worm 14a, and the outer ring constituting the rolling bearing 16d on the proximal end side is provided in the opening of the worm housing portion 17a. It is fitted in the bearing holding portion 22d on the side with a clearance fit. Then, a rolling bearing on the base end side is provided by a retaining ring (snap ring) or the like that is locked to a portion adjacent to the axially adjacent portion of the bearing holding portion 22d on the opening side in the base end side. The outer ring constituting 16d is prevented from coming out of the bearing holding portion 22d on the opening side.
- the outer ring constituting the base end side rolling bearing 16d may be fitted into the bearing holding portion 22d on the opening side by interference fit.
- the upper part of the inner peripheral surface of the worm accommodating part 17a (the part located on the opposite side of the worm wheel 15 with respect to the radial direction of the worm accommodating part 17a) is radially outward (above FIGS. 1 to 6). ) Is provided in the relief recess 28.
- the base end portion of the worm 14a is connected to the output shaft 18 (see FIG. 15) of the electric motor 10a so that the worm 14a can be driven to rotate.
- the worm wheel 15 is rotatably provided inside the wheel housing portion 19 of the housing 11a, and its own rotation center axis is arranged at a twisted position with respect to the worm 14a.
- the worm wheel 15 is manufactured by coupling and fixing a synthetic resin tooth portion 20 around a metal wheel portion 29.
- the tooth portion 20 is meshed with the worm tooth 13 without any gap (with zero backlash). Therefore, in the case of this embodiment, the preload provision mechanism for elastically pressing the worm tooth 13 toward the tooth part 20 is not provided.
- the worm wheel 15 is fitted and fixed to a portion near the front end of the steering shaft 5a.
- the rotational driving force generated by the electric motor 10a can be transmitted to the steering shaft 5a via the worm speed reducer 21a including the worm 14a and the worm wheel 15.
- the above-mentioned worm reduction gear 21a is assembled as follows. First, as shown in FIG. 1, the worm wheel 15 is rotatably supported at a predetermined position in the wheel accommodating portion 19 of the housing 11a. Further, the inner rings constituting the rolling bearings 16c and 16d are externally fixed to the front end portion and the proximal end portion of the worm 14a (externally fitted by interference fit). Next, as shown in FIGS. 2 to 4, the worm 14 a is arranged in the radial direction of the worm wheel 15 with respect to the central axis of the worm housing portion 17 a so that the worm teeth 13 do not interfere with the teeth 20 of the worm wheel 15.
- the outer diameter side (upward) of the most protruding portion (uppermost portion), that is, the outer diameter side (upper) of the center of the worm wheel 15 in the axial direction of the worm 14 a is passed so as not to interfere with the worm wheel 15.
- each member which comprises the worm reduction gear 21 is controlled as follows. That is, the inner diameter of the bearing holding portion 22d on the opening side is d 22d , the outer diameter of the rolling bearing 16c on the tip side (the outer ring constituting it) is D 16c, and the outer diameter of the worm wheel 15 (the tooth tip of the tooth portion 20).
- the rolling bearing 16c on the distal end side is inserted. And the inner peripheral surface of the bearing holding portion 22d on the opening side are prevented from interfering with each other.
- a relief recess 28 that is recessed radially outward is formed in the upper part of the inner peripheral surface of the worm housing portion 17a, and the worm 14a is moved toward the center axis of the worm housing portion 17a. Even if it is inserted into the worm housing portion 17a in a state offset to the outside in the radial direction of the wheel 15, the worm teeth 13 do not interfere with the inner peripheral surface of the worm housing portion 17a.
- the outer diameter D 16c of the tip side rolling bearing 16c (the outer ring constituting it) is set to the uppermost part of the outer peripheral edge of the worm wheel 15 and the inner peripheral surface (relief recess) of the worm housing part 17a. 28) and the distance G in the radial direction of the worm 14a (D 16c ⁇ G). Accordingly, when the worm 14a is inserted into the worm housing portion 17a from the opening of the worm housing portion 17a with the worm 14a being offset with respect to the central axis of the worm housing portion 17a, the rolling bearing 16c on the distal end side is inserted.
- relief recess 28 has an arc shape of radius R 1 in the axial direction of the cross section.
- the radius R 1 has a relationship of R 1 ⁇ R 2 with the outer radius R 2 of the worm 14 a (worm tooth 13).
- the outer diameter D 16c of the rolling bearing 16c on the distal end side is made larger than the root circle diameter D f of the worm tooth 13 (D 16c > D f ).
- D 16c > D f the root circle diameter of the worm tooth 13
- the strength and rigidity of the tip portion of the worm 14a are secured, and the radial load capacity of the rolling bearing 16c on the tip side is secured. If the strength and rigidity of the tip of the worm and the radial load capacity of the tip-side rolling bearing supported and fixed to the tip of the worm can be sufficiently secured, the outer diameter of the tip-side rolling bearing can be reduced to the worm teeth. It can also be made smaller than the bottom circle diameter.
- the outer diameter D 16d of the rolling bearing 16d on the proximal end that is supported and fixed near the proximal end of the worm 14a is made larger than the tip diameter Dk of the worm tooth 13. (D 16d > D k ).
- one bearing holding part 22c provided in the back end part of the worm storage part has an inner peripheral surface having a smaller diameter than the inner peripheral surface of the worm storage part 17a, and is more than the inner peripheral surface of the worm storage part 17a. It is formed in the wheel accommodating part 19 side.
- one bearing holding portion 22d provided on the opening side of the worm housing portion has an inner circumferential surface having a diameter larger than that of the inner circumferential surface of the worm housing portion 17a, and is formed concentrically with the one bearing holding portion 22c.
- the tip-side rolling bearing 16c is passed through the uppermost part of the outer peripheral edge of the worm wheel 15, and the worm 14a is inserted into the worm accommodating portion 17a.
- the tip-side surface of the tip-side rolling bearing 16c (FIGS. 1 and 2). 4 to 6) are abutted against a bearing holding portion 22c provided at the inner end of the worm housing portion 17a and a stepped portion 26 continuous with the inner peripheral surface of the intermediate portion of the worm housing portion 17a.
- the worm 14a is displaced radially inward (downward in FIGS. 1 to 6) so that the central axis of the worm 14a and the central axis of the worm accommodating portion 17a are concentric. As shown in FIG.
- the worm teeth 13 and the tooth portions 20 of the worm wheel 15 are engaged with each other. Specifically, when the front end surface of the rolling bearing 16c on the front end comes into contact with a stepped portion 26 continuous with the inner peripheral surface of the intermediate portion of the worm accommodating portion 17a (the worm 14a is displaced inward in the radial direction of the worm wheel 15). On the other hand, the worm teeth 13 are engaged with the teeth 20 at the center of the worm wheel 15. In this state, the outer ring of the rolling bearing 16c on the distal end side and the bearing holding portion 22c are arranged concentrically. In the case of this embodiment, the bearing holding portion 22c has a bottomed cylindrical shape with the back end side (the right side in FIGS.
- the bearing holding portion 22c is not limited to the bottomed cylindrical shape that is always closed, but may be a bottomed cylindrical shape by configuring the bottom portion 22c1 with another member such as a lid, and the bottom portion 22c1 is opened during maintenance. You may let them.
- the worm 14a is further inserted into the worm housing portion 17a, whereby the outer ring of the rolling bearing 16c on the distal end side is connected to the bearing holding portion 22c as shown in FIGS.
- the outer ring of the rolling bearing 16d on the base end side is directly press-fitted (tightened) into the bearing holding portion 22d provided in the opening of the worm accommodating portion 17a. Fit with a fit or fit with a gap fit.
- the inner peripheral surfaces of the bearing holding portions 22c and 22d are directed from the opening side (left side in FIGS. 1, 2, 4 to 6) to the back end side (right side in FIGS. 1, 2, 4 to 6).
- the worm 14a is slightly inclined in a direction in which the inner diameter decreases until just before the position where the outer ring is fitted. Accordingly, the worm 14a is positioned in the radial direction as the outer rings of the pair of rolling bearings 16c and 16d are press-fitted into the pair of bearing holding portions 22c and 22d, respectively.
- the meshing state becomes appropriate (the backlash does not exist in the meshing portion).
- the outer ring of the rolling bearing 16c on the distal end side supported and fixed to the distal end portion of the worm 14a is moved to the back of the worm housing portion 17a. It begins to be press-fitted (internally fitted) into the bearing holding portion 22c provided at the end. Then, when the outer ring of the rolling bearing 16c on the distal end side is press-fitted to some extent (about half) into the bearing holding portion 22c, the outer ring of the rolling bearing 16d on the proximal end side supported and fixed to the proximal end portion of the worm 14a is accommodated in the worm.
- each part is regulated so that it can be press-fitted into the bearing holding part 22d provided in the opening part of the part 17a. That is, in the present embodiment, the rolling bearing 16c on the distal end side corresponds to one rolling bearing described in the claims, and the rolling bearing 16d on the proximal end side also corresponds to the other rolling bearing. .
- the worm 14a abuts the distal end surface of the rolling bearing 16d on the base end side against the stepped portion 27 where the bearing holding portion 22d and the intermediate portion of the worm accommodating portion 17a are continuous to achieve positioning in the axial direction.
- a portion (bearing holding portion 22d) in which the rolling bearing 16d on the base end side is fitted is adjacent to the axial direction.
- the axial displacement of the rolling bearing 16d on the proximal end side, and thus the worm 14a is prevented by locking the retaining ring.
- a screw (nut) or a member such as a plate member (leaf spring) fixed by the screw is used for the rolling bearing 16d on the proximal end side.
- the outer ring can be biased toward the tip side of the worm 14a. Then, the spline shaft portion 30 provided at the base end portion of the worm 14a is spline-engaged with the output shaft 18 of the electric motor 10a, and the opening of the worm housing portion 17a is closed by the motor case 25 housing the electric motor 10a.
- the worm 14a and the pair of rolling bearings 16c and 16d for rotatably supporting the worm 14a are provided in the worm housing portion 17a of the housing 11a. Since it can be assembled integrally, the assembly cost can be suppressed, and the manufacturing cost of the worm reducer 21a can be reduced.
- the worm 14a is inserted into the worm housing portion 17a while being offset from the central axis of the worm housing portion 17a in the radial direction of the worm wheel 15, and the tip of the worm 14a is inserted.
- the worm teeth 13 and the worm wheel 15 are passed through the rolling bearing 16c fitted on the outer end of the worm wheel 15 so as not to interfere with the outer diameter side of the worm wheel 15 that protrudes most in the worm housing portion 17a.
- the tooth portion 20 is meshed. For this reason, when the worm 14a is assembled into the worm accommodating portion 17a, the axial displacement of the worm 14a in a state where the worm teeth 13 and the tooth portions 20 are engaged with each other is started without the worm being offset. Compared to the case where the worm teeth and the tooth portions of the worm wheel are meshed from the beginning (the case where there is no space for offsetting the worm), the amount can be reduced.
- the worm teeth 13 and the tooth portions 20 are assembled when the worm reducer 21a is assembled. It is difficult to cause damage such as scratches.
- the worm speed reducer 21a has a tooth preventing portion 20 of the worm wheel 15 made of a synthetic resin, so that the effect of preventing damage during assembly can be significantly obtained.
- the outer ring of the rolling bearing 16c on the distal end side supported and fixed to the distal end portion of the worm 14a at the final stage of the assembly work of the worm 14a into the worm housing portion 17a After press-fitting into the bearing holding portion 22c provided at the end and press-fitting to some extent, the outer ring of the other rolling bearing 16d supported and fixed to the portion near the base end of the worm 14a is provided in the bearing holding provided at the opening of the worm accommodating portion 17a. It is configured to start press-fitting into the portion 22d.
- [Second Embodiment] 7 to 10 show a second embodiment of the present invention.
- the length between the pair of rolling bearings 16c and 16d fixed to the worm 14a is longer than the length from the stepped portion 26 of the worm accommodating portion 17b to the opening end of the other bearing holding portion 22d.
- the length between the pair of rolling bearings 16c and 16d fixed to the worm 14b is shorter than the length from the stepped portion 26 of the worm housing portion 17b to the opening end of the other bearing holding portion 22d. Is shown.
- the worm 14b is offset radially outward of the worm wheel 15 with respect to the central axis of the worm housing portion 17b, as in the case of the first embodiment described above.
- the worm housing portion 17b is inserted into the worm housing portion 17b through the opening.
- a rolling bearing 16c on the distal end side fitted on the distal end portion (the right end portion in FIGS. 7 to 10) of the worm 14b is passed through the uppermost portion of the outer peripheral edge of the worm wheel 15, and the worm 14b is further passed through the worm 14b.
- the distal end side surface of the rolling bearing 16d on the proximal end side that is externally fitted to the proximal end portion of the worm 14b (the front side surface in the insertion direction of the worm 14b) is inserted into the housing portion 17b.
- the right side surface in FIGS. 7 to 10 is abutted against the opening side end surface (the left end surface in FIGS. 7 to 10) of the worm housing portion 17b.
- the worm 14b is displaced radially inward of the worm wheel 15 so that the central axis of the worm 14b and the central axis of the worm accommodating portion 17b are concentric, as shown in FIG.
- the worm tooth 13 provided at the axially intermediate portion of the worm 14b and the tooth portion 20 of the worm wheel 15 are engaged with each other.
- the worm 14b is further inserted into the worm accommodating portion 17b.
- the outer ring of the rolling bearing 16d on the base end side starts to be fitted into the bearing holding portion 22d provided at the opening of the worm housing portion 17b.
- the outer ring of the rolling bearing 16d on the base end side is fitted to the bearing holding portion 22d to some extent (about half), the outer ring of one rolling bearing 16c supported and fixed to the distal end portion of the worm 14a. Is fitted into a bearing holding portion 22c provided at the back end of the worm housing portion 17a. That is, in the case of this embodiment, the rolling bearing 16d on the base end side corresponds to one rolling bearing described in the claims, and the rolling bearing 16c on the distal end side is described in the claims. This corresponds to the other rolling bearing. The structure and operation of the other parts are the same as in the first embodiment.
- this invention is not limited to embodiment mentioned above, A deformation
- the preload mechanism shown in FIG. 11 is added to press the worm against the worm wheel in a state where the worm is assembled to the worm housing portion by the worm speed reducer assembling method according to the embodiment of the present invention. You can also.
- a leaf spring accommodating portion 42 is formed in the housing 11a at the upper portion of the outer peripheral portion of the rolling bearing 16c.
- flat portions 43 In a portion of the housing 11a corresponding to the lower half of the outer peripheral portion of the rolling bearing 16c, there are provided flat portions 43 that are parallel to each other and that slidably guide the outer diameter portion in the horizontal direction of the rolling bearing 16c.
- a corrugated leaf spring 41 is accommodated in the leaf spring accommodating portion, and an urging force for moving the rolling bearing 16 c downward in FIG. 11 is generated by the leaf spring 41.
- the worm 14a inserted into the inner ring of the rolling bearing 16c at one end of the shaft end is urged against the worm wheel 15 by this urging force.
- the worm teeth 13 are formed up to the end portion. However, as shown in FIG. 12, even if the worm teeth 13a are not formed up to the end portion, the worm 14a is replaced with the worm teeth 13a. When the wheel 15 is displaced inward in the radial direction, the worm teeth 13 a are engaged with the teeth 20 at the center of the worm wheel 15.
- a guide portion 31 for guiding the rolling bearing 16c may be provided so that one of the rolling bearings 16c and the bearing holding portion 22c are arranged concentrically.
- the worm 14a is displaced inward in the radial direction, and the one rolling bearing 16c and the bearing holding portion 22c are arranged concentrically. That is, by providing the guide portion 31, the worm 14a is displaced radially inward based on the force that displaces the worm 14a in the axial direction, and the one rolling bearing 16c and the bearing holding portion 22c are arranged concentrically. Can do.
- the guide portion 31 has a conical surface toward the bearing holding portion 22c.
- the guide portion 31 may be a guide as long as the diameter decreases from the inner peripheral surface of the worm accommodating portion 17a toward the bearing holding portion 22c.
- the shape of the part is not limited to this.
- the outer diameter D 16c of the rolling bearing 16c on the tip side is made smaller than the tip circle diameter D k of the worm tooth 13 (D 16c ⁇ D k ), but the worm tooth It may be larger than the tooth tip circle diameter D k of 13 (D 16c > D k ).
- the radius R 1 of the relief recess 28 may be R1 ⁇ D 16c / 2.
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Abstract
Description
前記ハウジングは、ホイール収容部と、前記ホイール収容部に対し捩れの位置に存在して前記ホイール収容部にその一部を連続させたウォーム収容部とを有する。
前記ウォームホイールは、前記ホイール収容部内に回転可能に支持されている。
前記ウォームは、ウォーム軸の軸方向中間部にウォーム歯を設けられ、前記ウォーム歯を前記ウォームホイールと噛合させた状態で、前記ウォーム歯を挟んだ軸方向の2位置を1対の軸受により前記ウォーム収容部内に回転可能に支持されている。
そして、前記1対の軸受のうち前記ウォームの挿入方向前側に外嵌された軸受を、前記ウォームホイールの外周縁(歯先円)の前記ウォーム収容部内に最も突出した部分の外径側を通過させる。その後、前記ウォームを、前記ウォームホイールの径方向内方に変位させ、前記ウォーム歯と前記ウォームホイールとを噛合させ、前記ウォーム歯と前記ウォームホイールとを噛合させながら、前記ウォーム収容部内の所定位置までこのウォームを更に挿入する事により、前記ウォームを前記1対の軸受により前記ウォーム収容部に対し回転可能に支持する。
上述の組み立て方法において、前記ウォーム歯と前記ウォームホイールとの間にバックラッシュを設けなくてもよい。この場合、より具体的には、前記ウォーム歯をこのウォームホイールに向け弾性的に押圧する為の予圧付与機構を設けなくてもよい。
また、前記ウォーム収容部の奥端部に設けた前記一方の軸受保持部は、前記ウォーム収容部の内周面よりも小径の内周面を有し、前記ウォーム収容部は、その内周面から前記軸受保持部に向かって縮径するガイド部を有し、前記ウォームの挿入方向前側に外嵌された軸受を、前記ガイド部に当接させながら前記ウォームを、前記ウォームホイールの径方向内方に変位させ、前記ウォーム歯と前記ウォームホイールとを噛合させるようにしてもよい。
この場合、前記一方の転がり軸受の外径は、前記歯先円直径よりも小さくしてもよい。
また、前記一方の転がり軸受の外径は、前記ウォーム歯の歯底円直径よりも大きくしてもよい。
また、前記ウォーム収容部の内周面上部に径方向外方に凹んだ逃げ凹部を形成してもよく、前記逃げ凹部は第1の半径を有する円弧形状を有し、前記第1の半径は、前記ウォームの外半径である第2の半径以上であってもよい。
さらに、前記ウォーム収容部の開口側の前記他方の軸受保持部の内径をd22dとし、前記ウォームの挿入方向前側の転がり軸受の外輪の外径をD16cとし、前記ウォームホイールの外径をD15とし、前記ウォームホイールの中心軸と前記ウォーム収容部の中心軸との間の距離をLとした場合、次の(1)式の関係を満たす構成であってもよい。
又、前記ウォームを、ウォーム歯とウォームホイールとが干渉しない様に、このウォームホイールの径方向外方にオフセットさせた状態で前記ウォーム収容部内に挿入し、前記両軸受のうち前記ウォームの挿入方向前側に存在する軸受を、前記ウォームホイールのうち前記ウォーム収容部内に最も突出した部分の外径側を通過させた後、前記ウォーム歯と前記ウォームホイールとを噛合させる。この為、前記ウォームの前記ウォーム収容部内への組み付け時に、これらウォーム歯とウォームホイールとを噛合させた状態での前記ウォームの軸方向変位量を、このウォームをオフセットせず、組み付け作業の開始当初から前記ウォーム歯とウォームホイールとを噛合させた場合(ウォームをオフセットさせるスペースが存在しない様な場合)と比較して、少なく抑えられる。この結果、例えば前記ウォーム歯と前記ウォームホイールとの間にバックラッシュを設けない場合にも、これらウォーム歯やウォームホイールに傷等の損傷を生じ難くできる。
又、上述のウォーム減速機は、上述の様な組立方法により組み立てられる為、製造コストを低減する事ができる。
図1~6は、本発明の第1実施形態を示している。本実施形態は、ハウジングのウォーム収容部内に、ウォームと、ウォームを回転可能に支持する為の1対の軸受とを一体に組み付けて、組立コストの低減を図る。本実施形態のウォーム減速機の組立方法における、ウォーム減速機21aは、ウォーム減速機21aを構成する各部材の一部の寸法関係を除き、前述の図15に示したウォーム減速機21と基本的には同様の構成を有する。
即ち、本実施形態のウォーム減速機21aは、電動モータ10aに固定した、減速機用のハウジング11aの内側に設けられており、ウォーム軸12の軸方向中間部にウォーム歯13を形成したウォーム14aと、ウォーム歯13と噛合するウォームホイール15とを備える。ハウジング11aは、ウォームホイール15を収容するホイール収容部19と、ホイール収容部19に一部が連続(開口)した状態で設けられたウォーム収容部17aとを備える。ホイール収容部19の中心軸とウォーム収容部17aの中心軸とは、互いに捩れの位置関係にある。ウォーム14aは、先端部(図1,2,4~6の右端部)と基端寄り部分(図1,2,4~6の左端寄り部分)とを、深溝型玉軸受等の1対の転がり軸受16c、16dにより、ハウジング11aのウォーム収容部17aの内側に回転可能に支持している。即ち、1対の転がり軸受16c、16dのうちの先端側(前記ウォーム減速機21aを組み立てる際のウォーム収容部17aに対するウォーム14aの挿入方向前側で、図1、2、4~6の右側)の転がり軸受16cを構成する内輪を、ウォーム14aの先端部に外嵌固定(締り嵌めで外嵌)すると共に、先端側の転がり軸受16cを構成する外輪を、ウォーム収容部17aの奥端部(図1、2、4~6の右端部)に設けた奥側の軸受保持部22aに隙間嵌めで内嵌している。但し、先端側の転がり軸受16cを構成する外輪を、この奥側の軸受保持部22aに締り嵌めで内嵌しても良い。又、1対の転がり軸受16c、16dのうちの基端側(前記ウォーム減速機21aを組み立てる際のウォーム収容部17aに対するウォーム14aの挿入方向後側で、図1、2、4~6の左側)の転がり軸受16dを構成する内輪を、ウォーム14aの基端寄り部分に外嵌固定すると共に、この基端側の転がり軸受16dを構成する外輪を、ウォーム収容部17aの開口部に設けた開口側の軸受保持部22dに隙間嵌めで内嵌している。そして、この開口側の軸受保持部22dのうちで基端側の転がり軸受を内嵌した部分と軸方向に隣接する部分に係止した止め輪(スナップリング)等により、基端側の転がり軸受16dを構成する外輪が開口側の軸受保持部22dから抜け出るのを防止している。但し、この基端側の転がり軸受16dを構成する外輪を、開口側の軸受保持部22dに締り嵌めで内嵌しても良い。ウォーム収容部17aの内周面のうちの上部(このウォーム収容部17aの径方向に関して、前記ウォームホイール15側と反対側に位置する部分)には、径方向外方(図1~6の上方)に凹んだ逃げ凹部28が設けられている。又、ウォーム14aの基端部を電動モータ10aの出力軸18(図15参照)に接続して、ウォーム14aを回転駆動可能にしている。
このような関係を有することで、ウォーム14aをウォーム収容部17aと干渉しないように適切に逃げ凹部28に逃がしつつ、ウォーム14aを軸方向に変位させることができる。
このため、ウォーム収容部の奥端部に設けた一方の軸受保持部22cは、ウォーム収容部17aの内周面よりも小径の内周面を有し、ウォーム収容部17aの内周面よりもホイール収容部19側に形成されている。また、ウォーム収容部の開口側に設けた一方の軸受保持部22dは、ウォーム収容部17aの内周面よりも大径の内周面を有し、一方の軸受保持部22cと同心に形成される。
なお、軸受保持部22cは、常時塞がった有底円筒状に限らず、底部22c1を蓋など別部材で構成することで、有底円筒状としてもよく、メンテナンスの際などに、底部22c1を開口させてもよい。
又、本実施形態の場合、ウォーム14aを、ウォーム収容部17aの中心軸に対して、ウォームホイール15の径方向外方にオフセットさせた状態でウォーム収容部17a内に挿入し、ウォーム14aの先端部に外嵌した先端側の転がり軸受16cと、ウォームホイール15のうちウォーム収容部17a内に最も突出した部分の外径側とを干渉しない様に通過させた後、ウォーム歯13とウォームホイール15の歯部20とを噛合させる様にしている。この為、ウォーム14aのウォーム収容部17a内への組み付け時に、ウォーム歯13と歯部20とを噛合させた状態でのウォーム14aの軸方向変位量を、ウォームをオフセットせず、組み付け作業の開始当初からウォーム歯とウォームホイールの歯部とを噛合させた場合(ウォームをオフセットするスペースが存在しない様な場合)と比較して、少なく抑えられる。従って、本実施形態のウォーム減速機21aの様に、ウォーム歯13と歯部20との間にバックラッシュを設けていない場合にも、ウォーム減速機21aの組立時に、ウォーム歯13や歯部20に傷等の損傷を生じ難くできる。特にウォーム減速機21aは、ウォームホイール15の歯部20を合成樹脂により構成している為、組立時の損傷防止効果を顕著に得る事ができる。
図7~10は、本発明の第2実施形態を示している。第1実施形態では、ウォーム14aに固定された1対の転がり軸受16c、16d間の長さが、ウォーム収容部17bの段差部26から他方の軸受保持部22dの開口端までの長さより長いが、本実施形態では、ウォーム14bに固定された1対の転がり軸受16c、16d間の長さが、ウォーム収容部17bの段差部26から他方の軸受保持部22dの開口端までの長さより短い場合を示している。
その他の部分の構成及び作用は、第1実施形態と同様である。
例えば、本発明の実施の形態に係るウォーム減速機の組立方法により、ウォームをウォーム収容部に組み付けた状態で、ウォームをウォームホイールに対して押圧する為に、図11に示す予圧機構を追加することもできる。図11において、転がり軸受16cの外周部の上部には、板ばね収容部42がハウジング11aに形成されている。転がり軸受16cの外周部の下半部に相当するハウジング11aの部分には、転がり軸受16cの水平方向の外径部を摺動可能に案内する、互いに平行な平面部43を設けている。板ばね収容部に波形形状の板ばね41を収容し、この板ばね41によって転がり軸受16cを図11において、下方へ移動させる付勢力を発生させている。この付勢力によって軸端の一端を転がり軸受16cの内輪に挿入されたウォーム14aがウォームホイール15に対して付勢される。
2 ステアリングギヤユニット
3 入力軸
4 タイロッド
5、5a ステアリングシャフト
6 ステアリングコラム
7 自在継手
8 中間シャフト
9 自在継手
10、10a 電動モータ
11、11a ハウジング
12 ウォーム軸
13、13a ウォーム歯
14、14a、14b ウォーム
15 ウォームホイール
16a~16c 転がり軸受
17、17a、17b ウォーム収容部
18 出力軸
19 ホイール収容部
20 歯部
21、21a ウォーム減速機
22a~22d 軸受保持部
23 係止溝
24 止め輪
25 モータケース
26 段差部
27 段差部
28 逃げ凹部
29 ホイール部
30 スプライン軸部
31 ガイド部
41 板ばね
42 板ばね収容部
43 平面部
Claims (10)
- ホイール収容部と、前記ホイール収容部に対し捩れの位置に存在して前記ホイール収容部にその一部を連続させたウォーム収容部とを有するハウジングと、
前記ホイール収容部内に回転可能に支持されたウォームホイールと、
ウォーム軸の軸方向中間部にウォーム歯を設けられ、前記ウォーム歯を前記ウォームホイールと噛合させた状態で、前記ウォーム歯を挟んだ軸方向の2位置をそれぞれ1対の軸受により前記ウォーム収容部内に回転可能に支持されたウォームと
を備えるウォーム減速機の組立方法であって、
前記ウォームホイールを前記ホイール収容部内に回転可能に支持させ、
前記ウォームの前記ウォーム歯を挟んだ軸方向の前記2位置に前記1対の軸受を外嵌し、
前記ウォーム歯と前記ウォームホイールとが干渉しない様に、前記ウォームを前記ウォームホイールの径方向外方にオフセットさせた状態で、前記ウォーム収容部内に前記ウォーム収容部の開口側から挿入し、
前記1対の軸受のうち前記ウォームの挿入方向前側に外嵌された軸受を、前記ウォームホイールの外周縁の前記ウォーム収容部内に最も突出した部分の外径側を通過させ、
前記ウォームを、前記ウォームホイールの径方向内方に変位させ、前記ウォーム歯と前記ウォームホイールとを噛合させ、
前記ウォーム歯と前記ウォームホイールとを噛合させながら、前記ウォーム収容部内の所定位置まで前記ウォームを更に挿入する事により、前記ウォームを前記1対の軸受により前記ウォーム収容部に対し回転可能に支持する、ウォーム減速機の組立方法。 - 前記1対の軸受がいずれも外輪と内輪との間に複数の転動体を設けて成る転がり軸受であり、前記ウォームの軸方向に関して、前記ウォーム収容部の内周面の2位置に前記1対の転がり軸受の外輪をそれぞれ保持する為の1対の軸受保持部を設けており、
前記1対の転がり軸受のうちの一方の転がり軸受の外輪を、前記1対の軸受保持部のうちの一方の軸受保持部に内嵌し始めた後で、前記1対の転がり軸受のうちの他方の転がり軸受の外輪を、前記1対の軸受保持部のうちの他方の軸受保持部に内嵌し始める、請求項1に記載のウォーム減速機の組立方法。 - 前記ウォーム歯と前記ウォームホイールとの間にバックラッシュを設けない、請求項1または2に記載のウォーム減速機の組立方法。
- 前記ウォーム収容部の奥端部に設けた前記一方の軸受保持部は、前記ウォーム収容部の内周面よりも小径の内周面を有し、
前記ウォーム収容部は、その内周面から前記軸受保持部に向かって縮径するガイド部を有し、
前記ウォームの挿入方向前側に外嵌された軸受を、前記ガイド部に当接させながら前記ウォームを、前記ウォームホイールの径方向内方に変位させ、前記ウォーム歯と前記ウォームホイールとを噛合させる、請求項2又は3に記載のウォーム減速機の組立方法。 - ホイール収容部と、前記ホイール収容部に対し捩れの位置に存在してこのホイール収容部にその一部を連続させたウォーム収容部とを有するハウジングと、
前記ホイール収容部内に回転可能に支持されたウォームホイールと、
ウォーム軸の軸方向中間部にウォーム歯を設けられ、前記ウォーム歯を前記ウォームホイールと噛合させた状態で、前記ウォーム歯を挟んだ軸方向の2位置を1対の軸受により前記ウォーム収容部の内周面の2位置に回転可能に支持されたウォームと
を備えるウォーム減速機に於いて、
前記1対の軸受がいずれも外輪と内輪との間に複数の転動体を設けて成る転がり軸受であり、
前記ウォームを、前記1対の転がり軸受により、前記ウォーム収容部の内周面の前記2位置に設けた1対の軸受保持部に回転可能に支持しており、
前記1対の軸受保持部のうち前記ウォーム収容部の奥端部に設けた一方の軸受保持部が有底円筒状であり、
前記1対の転がり軸受のうち前記ウォームの先端部にその内輪を外嵌固定した一方の転がり軸受の外輪を、前記一方の軸受保持部に直接内嵌固定しており、
前記一方の転がり軸受の外輪の外径が、前記ウォームの径方向に関する、前記ウォームホイールの外周縁のうち前記ウォーム収容部内に最も突出した部分と、前記ウォーム収容部の内面との間の距離よりも小さい、ウォーム減速機。 - 前記ウォームの挿入方向前側に外嵌された軸受の外径は、前記ウォーム歯の歯先円直径よりも小さい、請求項5に記載のウォーム減速機。
- 前記ウォームの挿入方向前側に外嵌された軸受の外径は、前記ウォーム歯の歯底円直径よりも大きい、請求項5または6に記載のウォーム減速機。
- 前記ウォーム収容部の内周面上部に径方向外方に凹んだ逃げ凹部を形成しており、
前記逃げ凹部は第1の半径を有する円弧形状を有し、前記第1の半径は、前記ウォームの外半径以上である、請求項5~7のうち何れか1項に記載のウォーム減速機。 - 前記ウォーム収容部の奥端部に設けた前記一方の軸受保持部は、前記ウォーム収容部の内周面よりも小径の内周面を有し、
前記ウォーム収容部は、その内周面から前記軸受保持部に向かって縮径するガイド部を有する、請求項5~8のうち何れか1項に記載のウォーム減速機。
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JP2016553157A JP6350671B2 (ja) | 2014-10-09 | 2015-10-08 | ウォーム減速機およびウォーム減速機の組立方法 |
CN201580051471.8A CN106687712B (zh) | 2014-10-09 | 2015-10-08 | 蜗轮蜗杆减速机和蜗轮蜗杆减速机的组装方法 |
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CN106687712A (zh) | 2017-05-17 |
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