CN106438931B - Output shaft, speed reducer and motor with speed reducer - Google Patents
Output shaft, speed reducer and motor with speed reducer Download PDFInfo
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- CN106438931B CN106438931B CN201510608501.2A CN201510608501A CN106438931B CN 106438931 B CN106438931 B CN 106438931B CN 201510608501 A CN201510608501 A CN 201510608501A CN 106438931 B CN106438931 B CN 106438931B
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- Prior art keywords
- output
- shaft
- output shaft
- tooth
- end surface
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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
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60J—WINDOWS, WINDSCREENS, NON-FIXED ROOFS, DOORS, OR SIMILAR DEVICES FOR VEHICLES; REMOVABLE EXTERNAL PROTECTIVE COVERINGS SPECIALLY ADAPTED FOR VEHICLES
- B60J1/00—Windows; Windscreens; Accessories therefor
- B60J1/08—Windows; Windscreens; Accessories therefor arranged at vehicle sides
- B60J1/12—Windows; Windscreens; Accessories therefor arranged at vehicle sides adjustable
- B60J1/16—Windows; Windscreens; Accessories therefor arranged at vehicle sides adjustable slidable
- B60J1/17—Windows; Windscreens; Accessories therefor arranged at vehicle sides adjustable slidable vertically
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gears, Cams (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Gear Transmission (AREA)
Abstract
The invention provides a novel output shaft which achieves desired strength. The output shaft (13) has a shaft member (40) and an output member fixed to the shaft member. The shaft member (40) has a serration part (41) comprising tooth crests (41a) and tooth roots alternately arranged in the circumferential direction and extending in the axial direction, and a plurality of 1 st protrusions (40d) annularly formed at intervals on an annular 1 st end surface intersecting the axial direction. The output member has a plurality of grooves (42d) extending in the axial direction so as to engage with the serrations (41), and a plurality of 2 nd recessed portions formed annularly at intervals on a 2 nd end surface opposite to the 1 st end surface and formed so as to engage with the plurality of 1 st raised portions (40 d).
Description
Technical Field
The present invention relates to an output shaft used for a speed reducer.
Background
Conventionally, a motor with a speed reducer used for a power window device of a vehicle such as an automobile is known. As such a motor with a speed reducer, for example, a structure is known which includes a motor main body that rotationally drives a rotating shaft, and a speed reduction unit as a rotation transmission device having a worm gear mechanism that reduces the rotation of the rotating shaft. Further, as such a speed reducing unit, there is a structure in which a worm wheel is coupled to an output shaft via a damper mechanism (see patent document 1).
Further, as the output shaft, there has been devised a configuration in which a gear portion is formed at one end of a shaft portion thereof. The gear portion of the output shaft is engaged with a gear portion of a lifter (regulator) and is coupled to a window of the vehicle via the lifter (see patent document 2).
[ Prior art documents ]
[ patent document ]
[ patent document 1] Japanese patent No. 5662131 publication
[ patent document 2] Japanese patent No. 5134985 publication
Disclosure of Invention
[ problem to be solved by the invention ]
As the output shaft, there are conceivable a case where the shaft portion and the gear portion are integrally formed, and a case where the shaft portion and the gear portion are assembled as separate members.
However, if the shape of the output shaft is complicated, it is difficult to integrally form the shaft portion and the gear portion, and the process becomes complicated, which leads to an increase in manufacturing cost. On the other hand, if the shaft portion and the gear portion are made as separate members and the output shaft is assembled, there is room for improvement in that the fitting portion between the gear portion and the shaft portion may be deformed or the like when the gear portion receives an excessive force.
The present invention has been made in view of such circumstances, and an object thereof is to provide a novel output shaft that achieves a desired strength.
[ means for solving the problems ]
In order to solve the above problem, an output shaft according to an aspect of the present invention is an output shaft used for a speed reducer, and includes a shaft member and an output member fixed to the shaft member. The shaft member has a serration portion composed of tooth crests and tooth roots alternately arranged in a circumferential direction and extending in an axial direction, and a plurality of 1 st protrusions or a plurality of 1 st recesses formed annularly at intervals on an annular 1 st end surface intersecting the axial direction. The output section includes: a plurality of grooves extending in the axial direction so as to engage with the serration; and a plurality of 2 nd concave parts or a plurality of 2 nd convex parts which are formed annularly on the 2 nd end surface opposite to the 1 st end surface with intervals and are engaged with the plurality of 1 st convex parts or the plurality of 1 st concave parts.
According to this aspect, not only the serrations of the shaft member engage with the grooves of the output member, but also the 1 st projections or the 1 st recesses formed annularly on the 1 st end surface of the shaft member engage with the 2 nd recesses or the 2 nd projections formed annularly on the 2 nd end surface of the output member, so that the torsional strength of the output shaft after the output member and the shaft member are integrated is improved.
The shaft member may have a 1 st portion and a 2 nd portion continuous with the 1 st portion. Can be as follows: the output member is fixed to the 1 st portion; the saw teeth are formed on the periphery of the 1 st part; the 1 st end face is a step difference between the 1 st part and the 2 nd part; the output section includes: a hole formed at the center of the output member for the 1 st portion to enter, a plurality of teeth formed at the outer circumferential portion, and a plurality of grooves formed at the inner circumference of the hole.
Alternatively, the shaft member may have a 1 st portion and a 2 nd portion continuous with the 1 st portion. Can be as follows: the output member is fixed to the 1 st portion; the serration is formed on the inner peripheral portion of the 1 st part; the 1 st end face is a face of the 1 st part which is in contact with the output member; the output member includes an entrance portion formed at a center of the output member into the 1 st portion, and a plurality of grooves formed at an outer periphery of the entrance portion.
The output member may form a slot between the center of the aperture and the tooth. This reduces variation in the radial thickness of the output member due to the groove.
The shaft member may have a plurality of 1 st protrusions. The output member may have a plurality of 2 nd recesses. The output member may form a 2 nd recess between the center of the bore and the tooth. This enables the 2 nd recess to be formed in a thicker region of the gear member, thereby reducing a decrease in strength due to the formation of the recess.
The shaft member may form a crest of the serration between the shaft center of the 1 st part and the 1 st projection.
The output member may form a 2 nd lobe between the center of the hole and the root between the teeth. Thus, the 2 nd projecting portion can be formed in a thin region of the output member, and the strength in the vicinity of the tooth root can be improved.
The 1 st portion may have a locking portion in which a tip end portion protruding from the hole of the output member is deformed. This prevents the shaft member from falling off the output member.
The shaft member and the output member may be made of sintered metal. Thus, the output shaft with high strength can be manufactured by using the die. Further, by using sintered metal of an appropriate grade for each of the shaft member and the output member, the degree of freedom in manufacturing can be increased and the cost can be reduced.
The output component may be a carburized and quenched component. This can further improve the strength of the teeth to which a large force is applied.
The serration may be a number of teeth crests that is an integer multiple of the number of teeth. This can alleviate the stress acting on the output member constituting the output shaft.
The other scheme of the invention is also an output shaft. The output shaft is used for an output shaft of a speed reducer, and includes: a shaft member having a 1 st portion and a 2 nd portion continuous with the 1 st portion; and an output member fixed to the 1 st portion of the shaft member. The output member has a hole formed at the center thereof for the 1 st portion to enter and for the front end of the 1 st portion to protrude. With respect to the shaft member, in a state where the tip of the 1 st portion protrudes from the hole of the output member, the tip is fixed to the output member, and a region near the boundary of the 1 st portion and the 2 nd portion is fixed to the output member.
According to this aspect, even if the 1 st portion of the shaft member is not press-fitted over the entire hole of the output member, the shaft member and the output member are fixed to each other at least at the 2 nd position, so that the shaft member cannot fall off from the output member.
The shaft member may be configured such that a gap is formed with the output member between the front end of the 1 st portion and the area near the boundary in a state of being fixed with the output member. This reduces the force required for assembling the shaft member and the output member, suppresses deformation and breakage of the members, and improves productivity.
The shaft member may have a plurality of 1 st protrusions or a plurality of 1 st recesses formed annularly at intervals on an annular 1 st end surface as a step between the 1 st portion and the 2 nd portion. The output member may have a plurality of 2 nd recesses or a plurality of 2 nd protrusions formed annularly at intervals on a 2 nd end surface opposite to the 1 st end surface and formed to engage with the plurality of 1 st protrusions or the plurality of 1 st recesses. The plurality of 1 st projections or the plurality of 1 st recesses and the plurality of 2 nd recesses or the plurality of 2 nd projections may be pressed into each other.
Another aspect of the present invention is a speed reducer. This speed reducer includes: a worm for driving rotation of the motor; a worm wheel meshed with the worm; an output shaft engaged with the driven member to drive the driven member; a transmission mechanism for transmitting rotation of the worm wheel to the output shaft; and a housing accommodating the worm wheel.
According to this aspect, a speed reducer having a high output shaft strength can be provided.
Still another aspect of the present invention is a motor with a speed reducer. The motor with the speed reducer is provided with a motor and the speed reducer connected with a shaft of the motor.
Through this scheme, can provide the motor of taking speed reducer that the intensity of an output shaft is high.
In addition, an embodiment in which arbitrary combinations of the above-described constituent elements and expressions of the present invention are changed between a method, an apparatus, a system, and the like is also effective as an aspect of the present invention.
[ Effect of the invention ]
The present invention can provide a novel output shaft that can achieve a desired strength.
Drawings
Fig. 1 is a front view of an output gear side of a motor with a speed reducer according to embodiment 1.
Fig. 2 is a diagram showing a schematic configuration of the power window system according to embodiment 1.
Fig. 3 is an enlarged view of a main portion showing an engagement state between the output shaft and the driven member in embodiment 1.
Fig. 4 (a) is a perspective view of an output shaft of embodiment 1; fig. 4 (b) is a perspective view of the output shaft of embodiment 1 viewed from a direction different from that of fig. 4 (a).
Fig. 5 is a front view of a shaft member constituting an output shaft of embodiment 1.
Fig. 6 is a bottom view of the shaft member shown in fig. 5 viewed from the X1 direction.
FIG. 7 is a partial cross-sectional view A-A' of the shaft member shown in FIG. 6.
Fig. 8 is a plan view of the shaft member shown in fig. 5 viewed from the X2 direction.
FIG. 9 is an enlarged partial cross-sectional view of the shaft member shown in FIG. 8 taken along line B-B.
Fig. 10 is a front view of a gear member constituting an output shaft of embodiment 1.
FIG. 11 is a cross-sectional A-O-B view of the gear member shown in FIG. 10.
Fig. 12 is a rear view of the gear member constituting the output shaft of embodiment 1.
FIG. 13 is a close-up view of the C-C cross section of the gear member shown in FIG. 12.
Fig. 14 is a plan view of the output shaft of embodiment 1.
Fig. 15 is a sectional view a-a of the output shaft shown in fig. 14.
Fig. 16 is a schematic diagram for explaining engagement between the 1 st convex portion of the shaft member and the 2 nd concave portion of the gear member.
Fig. 17 is a schematic diagram for explaining the engagement between the 1 st convex portion and the 2 nd concave portion in the modification.
Fig. 18 is a front view of the gear component of embodiment 2.
Fig. 19 is an enlarged perspective view of the vicinity of the hole of the gear member.
Fig. 20 is an exploded perspective view of the output shaft of embodiment 3.
Fig. 21 is an exploded perspective view of the output shaft of embodiment 3 viewed from a direction different from that of fig. 20.
Fig. 22 is a front view of an output disc constituting the output shaft of embodiment 3.
Fig. 23 is a D-D sectional view of the output disk shown in fig. 22.
Fig. 24 is a rear view of an output disc constituting the output shaft of embodiment 3.
Fig. 25 is an enlarged partial view of a section E-E of the output tray shown in fig. 24.
Fig. 26 (a) is a schematic diagram of an output shaft of embodiment 4, and fig. 26 (b) is a schematic diagram of an output shaft of a modification of embodiment 4.
Fig. 27 is a schematic view of an output shaft of embodiment 5.
[ notation ]
10 motor parts, 12 speed reducers, 13 output shafts, 14 gear boxes, 40 shaft parts, 40a small diameter parts, 40b large diameter parts, 40c 1 st end surfaces, 40d 1 st convex parts, 40e grooves, 40f locking parts, 40g 1 st convex parts, 40h convex parts, 41 sawtooth parts, 41a tooth tops, 41b tooth roots, 42 gear parts, 42a holes, 42b peripheral parts, 42c teeth, 42d grooves, 42e 2 nd end surfaces, 42f 2 nd concave parts, 42h 2 nd convex parts, 42j tooth roots and 100 motors with speed reducers.
Detailed Description
The following describes in detail specific embodiments for carrying out the present invention with reference to the drawings. In the description of the drawings, the same elements are denoted by the same reference numerals, and overlapping description is appropriately omitted. The following configurations are merely examples, and do not limit the scope of the present invention in any way.
[ embodiment 1]
(Motor with speed reducer)
The motor with a speed reducer according to embodiment 1 is a motor applied to a power window system of a vehicle, for example. Fig. 1 is a front view of an output gear side of a motor with a speed reducer according to embodiment 1. The motor with speed reducer 100 includes a motor portion 10 and a speed reducer 12 coupled to a shaft of the motor portion 10.
The speed reducer 12 includes a worm (not shown) for transmitting rotation of the motor, a worm wheel (not shown) meshing with the worm, an output shaft 13 meshing with the driven member to drive the driven member, a transmission mechanism (not shown) for transmitting rotation of the worm wheel to the output shaft, and a gear box 14 serving as a housing for accommodating the worm wheel.
(Power window System)
Fig. 2 is a diagram showing a schematic configuration of the power window system according to embodiment 1. Fig. 3 is an enlarged view of a main portion showing an engagement state between the output shaft and the driven member in embodiment 1. As shown in fig. 2, a power window system 200 for a vehicle includes a motor 100 with a speed reducer and a cross-arm lifter 110.
The lifter 110 includes a metal bracket 22 fixed to the inner panel 20 of the door 18, a lift arm 26 rotatably coupled to the bracket 22 via a pivot shaft 24, a sector gear 28 integrally coupled to the lift arm 26, a balance arm 30 rotatably coupled to the lift arm 26, a balance bracket 32 guiding movement of a lower end portion of the balance arm 30, and a lift arm bracket 34 guiding movement of an upper end portion of the lift arm 26 and an upper end portion of the balance arm 30. Further, a window glass 36 as an opening/closing body is attached to the lift arm bracket 34.
As shown in fig. 1, a plurality of cylindrical mounting portions 38 are integrally formed on the gear case 14, and the gear case 14 is fixed to the mount 22 by fastening the mounting portions 38 to a plurality of screws (not shown) penetrating the mount 22. That is, the motor 100 with a reduction gear is fixed to the elevator 110 at the reduction gear 12, and the motor unit 10 is separated from the elevator 110.
Fig. 4 (a) is a perspective view of the output shaft of embodiment 1, and fig. 4 (b) is a perspective view of the output shaft of embodiment 1 viewed from a direction different from that of fig. 4 (a).
The output shaft 13 is a member used for the speed reducer 12, and is formed by combining a plurality of members. Specifically, the output shaft 13 includes a shaft member 40 and a gear member 42 as an output member fixed to an end of the shaft member 40. Then, as shown in fig. 3, the motor with reducer 100 and the lifter 110 are arranged in such a manner that the gear member 42 meshes with the sector gear 28.
Therefore, when the rotation shaft is rotated by the driving of the motor unit 10, the driving force is transmitted to the output shaft 13 via the worm shaft and the worm wheel, and the output shaft 13 (gear member 42) rotates. Then, the rotation of the gear member 42 is transmitted to the sector gear 28, the lift arm 26 rotates around the pivot shaft 24, and the lift 110 operates to move the lift arm bracket 34 up and down, so that the window glass 36 is opened and closed.
(shaft component)
Next, the structure of the shaft member of the output shaft will be described in detail. Fig. 5 is a front view of a shaft member constituting an output shaft of embodiment 1. Fig. 6 is a bottom view of the shaft member 40 shown in fig. 5, viewed from the X1 direction. Fig. 7 is a partial sectional view a-a' of the shaft member 40 shown in fig. 6. Fig. 8 is a plan view of the shaft member 40 shown in fig. 5 viewed from the X2 direction. Fig. 9 is a partial enlarged view of the shaft member 40 shown in fig. 8, taken along the B-B section.
The shaft member 40 of embodiment 1 has a cylindrical small diameter portion 40a as part 1 and a cylindrical large diameter portion 40b as part 2. The small diameter portion 40a and the large diameter portion 40b are continuous via a step. The small-diameter portion 40a and the large-diameter portion 40b may have a prism shape or other shapes. The shaft member 40 includes a serration part 41 formed on the outer peripheral part of the small diameter part 40a and including tooth tips 41a and tooth roots 41b alternately arranged in the circumferential direction and extending in the axial direction, and a plurality of 1 st protrusions 40d formed annularly at intervals on an annular 1 st end surface 40c as a step (flange part) between the small diameter part 40a and the large diameter part 40 b. Further, a groove 40e for a C-shaped positioning ring for fixing the other member and the shaft member 40 in a coupled state is formed in the vicinity of the end portion of the large diameter portion 40b opposite to the small diameter portion 40 a.
The serration 41 of embodiment 1 has 8 tooth tops 41a and 8 tooth roots 41b extending in the axial direction. The 1 st projection 40d is provided at 8 equal intervals (45 ° intervals) in the circumferential direction of the 1 st end surface 40 c. In the shaft member 40 of embodiment 1, the crest portion 41a of the serration portion 41 is formed between the shaft center O of the small-diameter portion 40a and the 1 st projection 40 d. This increases the symmetry of the shape, and increases the strength of the entire shaft member against external force.
The shaft member 40 of embodiment 1 is preferably an Fe-based sintered alloy containing copper or nickel, for example, from the viewpoint of strength. Such a sintered alloy can be obtained by molding a powder compact at high temperature and high pressure using a die. The characteristics of the material required for the shaft member 40 are preferably suitable for cutting to form the groove 40e for the C-shaped positioning ring, in addition to obtaining a desired strength of the finished member. Of course, a material suitable for forming a complicated shape by a mold is more preferable.
(Gear parts)
Next, the structure of the gear member of the output shaft will be described in detail. Fig. 10 is a front view of a gear member constituting an output shaft of embodiment 1. Fig. 11 is a cross-sectional a-O-B view of gear member 42 shown in fig. 10. Fig. 12 is a rear view of the gear member constituting the output shaft of embodiment 1. Fig. 13 is a close-up view of the cross-section C-C of gear member 42 shown in fig. 12.
The gear member 42 is fixed to the small diameter portion 40a by inserting the small diameter portion 40a of the shaft member 40 into a hole 42a in the center of the gear member 42. The gear member 42 is formed with axially extending slots 42d between the center O of the bore 42a and the teeth 42 c. The 8 grooves 42d have a shape corresponding to the shape of the tooth crest 41a of the serration 41 of the shaft member 40, and are provided at equal intervals (45 ° intervals) in the circumferential direction of the inner periphery of the hole 42 a. This reduces the variation in the radial thickness of the gear member 42 due to the formation of the groove 42 d.
The gear member 42 of embodiment 1 has 8 2 nd recesses 42 f. The gear member 42 forms a 2 nd recess 42f between the center of the hole 42a and the tooth 42 c. This enables the 2 nd recessed portion 42f to be formed in a thick region of the gear member 42, that is, at the root of the tooth 42c, and thus a decrease in strength due to the formation of the recessed portion can be reduced.
The gear member 42 may be formed with a plurality of 2 nd convex portions 42h on the 2 nd end surface 42e, instead of the 2 nd concave portion (see fig. 12). At this time, the 2 nd projection 42h is preferably formed between the center O of the hole 42a and the tooth root 42j between the tooth 42c and the tooth 42 c. This enables the 2 nd convex portion 42h to be formed in the region near the tooth root where the thickness of the gear member 42 is small, and therefore the strength near the tooth root can be improved.
In the case where a plurality of 2 nd convex portions 42h are provided on the 2 nd end surface 42e of the gear member 42, a plurality of 1 st convex portions 40d may be provided on the 1 st end surface 40c of the corresponding shaft member 40 instead of the 1 st convex portions 40 d.
The gear member 42 of embodiment 1 is preferably an Fe-based sintered alloy containing copper or nickel, for example, from the viewpoint of strength. Further, since the teeth 42c are subjected to a large force, it is preferable to further increase the strength and carburize and quench the gear member 42. Of course, quenching may or may not be required depending on the application and shape of the component. For example, either or both of the shaft member 40 and the gear member 42 may be quenched, or neither of the shaft member 40 and the gear member 42 may be quenched.
Since the shaft member 40 and the gear member 42 are formed of sintered metal in this manner, an output shaft having high strength can be manufactured by a mold. Further, since the shaft member 40 and the gear member 42 are independent members, the degree of freedom of manufacture can be increased and the cost can be reduced by using sintered metals of appropriate grades.
(output shaft)
The following describes the details of the structure of the output shaft 13 after the shaft member 40 and the gear member 42 are assembled. Fig. 14 is a plan view of the output shaft 13 of embodiment 1. Fig. 15 is a sectional view a-a of the output shaft 13 shown in fig. 14.
The output shaft 13 is fixed to the small-diameter portion 40a of the shaft member 40 in a state where the both are inserted into the hole 42a of the gear member 42. In embodiment 1, the small-diameter portion 40a may have a locking portion 40f in which a tip portion protruding from the hole 42a of the gear member 42 is deformed. This prevents the shaft member 40 from falling off the gear member 42. The deformation of the distal end portion may be performed by applying force or heat from the outside.
In the output shaft according to embodiment 1, the number of the tooth tops 41a of the serration 41, the number of the 1 st protrusions 40d, the number of the grooves 42d of the gear member 42, and the number of the 2 nd recesses 42f are all 8. The number of the crest portions 41a of the serration portion 41, the number of the 1 st convex portions 40d, the number of the grooves 42d of the gear member 42, and the number of the 2 nd concave portions 42f are preferably N times (N is an integer) or 1/N times (N is an integer) the number of the other structures. For example, the number of the top portions 41a of the serration parts 41 may be an integral multiple of the number of the teeth 42c of the gear member 42. Further, the tooth top portion 41a of the serration 41, the 1 st protrusion 40d, the groove 42d of the gear member 42, and the 2 nd recess 42f are linearly arranged in the radial direction. Alternatively, the radial arrangement is also possible.
By thus forming the serration part 41 of the shaft member 40, the 1 st convex part 40d, the teeth 42c of the gear member 42, and the 2 nd concave part 42f into a highly symmetrical shape or arrangement, the strength of the output shaft 13 itself can be increased, and the stress acting on the gear member 42 constituting the output shaft 13 can be relaxed.
In addition, since the output shaft 13 engages not only the tooth tips 41a of the serration parts 41 of the shaft member 40 with the grooves 42d of the gear member 42 but also the plurality of 1 st protrusions 40d formed annularly on the 1 st end surface 40c of the shaft member 40 with the plurality of 2 nd recesses 42f formed annularly on the 2 nd end surface 42e of the gear member 42, the torsional strength of the output shaft 13 is improved after the gear member 42 and the shaft member 40 are integrated.
That is, by engaging the plurality of members with each other at a plurality of positions two-dimensionally or three-dimensionally, when a large input is input to the output shaft 13, it is difficult for the force acting between the members to be intensively applied to one engagement portion, and deformation of the engagement portion or the like can be suppressed, as compared with the case where the plurality of members are engaged with each other only at 1 position one-dimensionally. Therefore, by using such an output shaft, a speed reducer or a motor with a speed reducer having a high output shaft strength can be provided.
(engagement state of convex part and concave part)
Fig. 16 is a schematic diagram for explaining the engagement between the 1 st convex portion 40d of the shaft member 40 and the 2 nd concave portion 42f of the gear member 42. Fig. 16 is a view in which the 1 st convex portion 40d and the 2 nd concave portion 42f arranged in a ring shape are developed linearly. By bringing the 1 st end face 40c and the 2 nd end face 42e into proximity or contact with each other in the state shown in fig. 16, the 1 st convex portion 40d and the 2 nd concave portion 42f are engaged with each other.
Fig. 17 is a schematic diagram for explaining the engagement between the 1 st convex portion and the 2 nd concave portion in the modification. The 1 st projection 40g of the modification further has a projection 40h at the center of the tooth top. When the 2 nd end surface 42e and the 1 st end surface 40c are brought close to each other in assembling the shaft member 40 and the gear member 42, the 1 st projecting portion 40g is expanded in the width direction (the circumferential direction of the 1 st end surface 40 c) by the projection 40h being reliably crushed and deformed at the bottom of the 2 nd recessed portion 42 f. This can reduce the gap between the 1 st convex portion 40g and the 2 nd concave portion 42f at the time of engagement, and can maintain a more reliable press-fitting state. Therefore, even if the output shaft 13 repeats normal rotation and reverse rotation, noise and vibration due to backlash can be suppressed.
[ 2 nd embodiment ]
Fig. 18 is a front view of the gear member 44 of embodiment 2. Fig. 19 is an enlarged perspective view of the vicinity of the hole of the gear member 44. In the gear member 42 of embodiment 1, an annular continuous recess 42m is formed in the 3 rd end surface 42k on the opposite side of the 2 nd end surface 42e (see fig. 10 and 11). In contrast, in the gear member 44 of embodiment 2, a plurality of radial recesses 42n are further formed in the bottom of the annular continuous recess 42 m. The recess 42n is formed from the inner periphery of the hole 42a toward the radial outer periphery side. Further, the recess 42n is formed to a certain distance from the center O of the hole 42 a. Further, since a plurality of grooves 42d are formed in the inner periphery of the hole 42a and the radius of the hole 42a is not constant, the length of the recess 42n is also varied.
In this manner, a plurality of recesses 42n are formed annularly at intervals on the 3 rd end surface 42 k. Thus, when the tip end portion of the small diameter portion 40a of the shaft member 40 is protruded from the hole 42a of the gear member 44 and deformed by applying an external force to the tip end portion in this state, a part of the tip end portion enters the plurality of concave portions 42 n. As a result, the shaft member 40 and the gear member 44 are more firmly fixed, and the occurrence of looseness in the rotational direction and looseness in the extraction direction (axial direction) of the shaft member 40 with respect to the gear member 44 can be further suppressed.
[ embodiment 3 ]
The power window system for a vehicle according to embodiment 1 is a cross-arm type lifter, but the present invention is also applicable to a rope-sheave type lifter. The following describes an output shaft applied to a sheave type elevator.
Fig. 20 is an exploded perspective view of the output shaft of embodiment 3. Fig. 21 is an exploded perspective view of the output shaft of embodiment 3 viewed from a direction different from that of fig. 20.
The output shaft 46 is used for the speed reducer 12, and has a structure in which a plurality of components are combined. Specifically, the output shaft 46 includes the shaft member 40 and an output disc 48 as an output member fixed to an end of the shaft member 40. The shaft member 40 has substantially the same configuration as that of embodiment 1 except that the number of grooves of the serration part and the number of the 2 nd recess parts are different, and therefore, the description thereof is omitted as appropriate.
Fig. 22 is a front view of an output disc 48 constituting the output shaft of embodiment 3. Fig. 23 is a D-D sectional view of output disk 48 shown in fig. 22. Fig. 24 is a rear view of the output disc 48 constituting the output shaft of embodiment 3. Fig. 25 is a close-up view of a section E-E of the output tray 48 shown in fig. 24.
The output tray 48 of embodiment 3 includes: a hole 48a formed in the center of the disc-shaped member, into which the small diameter portion 40a of the shaft member 40 enters; 3 engaging portions 48c formed on one end surface 48b of the disc shape; a plurality of grooves 48d formed in the inner periphery of the hole 48a and extending in the axial direction so as to engage with the serration 41 of the shaft member 40; and a plurality of 2 nd recessed portions 48f formed annularly at intervals at the other end surface 48e facing the 1 st end surface 40c of the shaft member 40 and engaged with the plurality of 1 st projecting portions 40 d.
The small diameter portion 40a of the shaft member 40 is inserted into a hole 48a in the center of the output disc 48, whereby the output disc 48 is fixed to the small diameter portion 40 a. The 9 grooves 48d have a shape corresponding to the shape of the tooth crest 41a of the serration 41 of the shaft member 40, and are provided at equal intervals (40 ° intervals) in the circumferential direction of the inner periphery of the hole 48 a.
The output disk 48 of embodiment 3 has 9 2 nd recesses 48 f. The output disk 48 may have a plurality of 2 nd convex portions formed on the other end surface 48e instead of the 2 nd concave portion. When a plurality of 2 nd convex portions are provided on the other end surface 48e of the output tray 48, a plurality of 1 st concave portions may be provided on the 1 st end surface 40c of the corresponding shaft member 40 instead of the plurality of 1 st convex portions 40 d.
[ 4 th embodiment ]
Fig. 26 (a) is a schematic diagram of an output shaft of embodiment 4, and fig. 26 (b) is a schematic diagram of an output shaft of a modification of embodiment 4.
The output shaft 50 shown in fig. 26 (a) includes a cylindrical shaft member 52 and a disc-shaped output member 54 fixed to the shaft member 52. The shaft member 52 has a concave hole 52a formed in the center thereof. The inner circumferential surface of the hole 52a includes a serration portion 52b including tooth crests and tooth roots alternately arranged in the circumferential direction and extending in the axial direction, and a plurality of 1 st protruding portions 52d (or a plurality of 1 st recessed portions) annularly formed at intervals on an annular 1 st end surface 52c intersecting the axial direction Ax.
The output member 54 is the aforementioned gear member or output disc or the like. The output member 54 has a plurality of grooves 54a extending in the axial direction so as to engage with the serration 52b, and a plurality of 2 nd recesses 54c (or a plurality of 2 nd protrusions) formed annularly at intervals on a 2 nd end surface 54b opposite to the 1 st end surface 52c and formed so as to engage with the plurality of 1 st protrusions 52d (or the plurality of 1 st recesses).
Thus, not only the serration 52b of the shaft member 52 engages with the groove 54a of the output member 54, but also the plurality of 1 st protrusions 52d (or the plurality of 1 st recesses) formed annularly on the 1 st end surface 52c of the shaft member 52 engages with the plurality of 2 nd recesses 54c (or the plurality of 2 nd protrusions) formed annularly on the 2 nd end surface 54b of the output member 54, so that the torsional strength of the output shaft 50 when the output member and the shaft member are integrated is improved.
In other words, the output shaft 50 can be expressed as follows. The shaft member 52 has a 1 st portion 52e and a 2 nd portion 52f continuous with the 1 st portion 52 e. The output member 54 is fixed to the 1 st portion 52e, the serration 52b is formed on the inner peripheral portion of the hole 52a of the 1 st portion 52e, and the 1 st end surface 52c is a surface of the 1 st portion 52e which is in contact with the output member 54. The output member 54 has a cylindrical entrance portion 54d formed in the center of the output member and entering the 1 st portion 52e, and a plurality of grooves 54a formed in the outer periphery of the entrance portion 54 d.
The output shaft 56 shown in fig. 26 (b) includes a cylindrical shaft member 58 and a disc-shaped output member 60 fixed to the shaft member 58. A through hole 58a is formed in the center of the shaft member 58. The through hole 58a has, on its inner peripheral surface, a serration part 58b composed of tooth tips and tooth roots alternately arranged in the circumferential direction and extending in the axial direction, and a plurality of 1 st protruding parts 58d (or a plurality of 1 st recessed parts) annularly formed at intervals on an annular 1 st end surface 58c intersecting with the axial direction Ax.
The output member 60 is the aforementioned gear member or output disc or the like. The output member 60 includes a plurality of grooves 60a extending in the axial direction so as to engage with the serrations 58b, and a plurality of 2 nd recesses 60c (or a plurality of 2 nd protrusions) formed annularly at intervals at a 2 nd end surface 60b opposite to the 1 st end surface 58c so as to engage with the plurality of 1 st protrusions 58d (or the plurality of 1 st recesses).
As a result, the torsional strength of the output shaft 56, in which the output member and the shaft member are integrated, is improved, as in the case of the output shaft 50.
In other words, the output shaft 56 described above can also be expressed as follows. The 1 st and 2 nd portions 58e, 58f of the shaft member 58 are continuous without distinction. The output member 60 is fixed to the 1 st portion 58e, the serrations 58b are formed on the inner peripheral portion of the through hole 58a of the 1 st portion 58e, and the 1 st end surface 58c is a surface that contacts the output member 60 of the 1 st portion 58 e. The output member 60 has a cylindrical entrance portion 60d formed in the center of the output member and entering the 1 st portion 58e, and a plurality of grooves 60a formed in the outer periphery of the entrance portion 60 d. The tip of the entering portion 60d is deformed by an external force and functions as a locking portion. This makes it more difficult to pull out the output member 60 from the shaft member 58.
[ 5 th embodiment ]
Fig. 27 is a schematic view of an output shaft of embodiment 5. The output shaft 62 shown in fig. 27 has a similar configuration to the output shaft 13 of embodiment 1, but differs in that the shaft member 64 is fastened (press-fitted) to the output member 66 via serrations.
The output shaft 62 includes: a shaft member 64 having a cylindrical 1 st portion 64a as a small diameter portion and a cylindrical 2 nd portion 64b as a large diameter portion continuous with the 1 st portion 64 a; and an output member 66 fixed to the 1 st portion 64a of the shaft member 64. The output member 66 has a through hole 66a formed at the center thereof into which the 1 st part 64a enters and from which the front end of the 1 st part protrudes. In a state where the tip of the 1 st part 64a protrudes from the through hole 66a of the output member 66, the tip is deformed, so that the shaft member 64 is fixed to the output member 66 (region R1), and a region R2 near the boundary between the 1 st part 64a and the 2 nd part 64b is fixed to the output member 66.
Thus, even if the 1 st portion 64a of the shaft member 64 is not press-fitted over the entire through hole 66a of the output member 66, the shaft member 64 and the output member 66 are fixed to each other at least 2 places (the region R1 and the region R2), and the shaft member 64 cannot be detached from the output member 66.
The shaft member 64 is configured so as to form a gap with the output member 66 between the front end of the 1 st part 64a (region R1) and the region R2 (region R3) near the boundary in a state of being fixed to the output member 66. This reduces the force required for assembling the shaft member 64 and the output member 66, and can suppress deformation and breakage of the members, thereby improving productivity.
The shaft member 64 has a plurality of 1 st protrusions 64d (or a plurality of 1 st recesses) formed annularly at intervals on an annular 1 st end surface 64c that is a step between the 1 st portion 64a and the 2 nd portion 64 b. The output member 66 has a plurality of 2 nd recesses 66c (or a plurality of 2 nd protrusions) formed annularly at intervals on a 2 nd end surface 66b facing the 1 st end surface 64c and formed to engage with the plurality of 1 st protrusions 64d (or the plurality of 1 st recesses). The 1 st projections 64d (or 1 st recesses) and the 2 nd recesses 66c (or 2 nd projections) are press-fitted into each other.
The present invention has been described above with reference to the above embodiments, but the present invention is not limited to the above embodiments, and configurations obtained by appropriately combining or replacing the embodiments are also included in the scope of the present invention. Further, the order of combination or processing in the embodiments may be appropriately rearranged based on the knowledge of those skilled in the art, or various modifications such as design changes may be applied to the embodiments, and the embodiments to which such modifications are applied may be included in the scope of the present invention.
Claims (10)
1. An output shaft for use in a speed reducer, comprising:
shaft member, and
an output member fixed to the shaft member;
the shaft member includes:
a serration part composed of tooth crest parts and tooth root parts alternately arranged in the circumferential direction and extending in the axial direction, an
A plurality of 1 st protrusions or a plurality of 1 st recesses formed annularly at intervals on a 1 st annular end surface intersecting with the axial direction;
the output section includes:
a plurality of grooves extending in the axial direction in such a manner as to engage with the saw-tooth portions, an
A plurality of 2 nd concave portions or a plurality of 2 nd convex portions formed annularly at a 2 nd end surface opposed to the 1 st end surface with a space therebetween and formed in a direction of engaging with the plurality of 1 st convex portions or the plurality of 1 st concave portions,
the shaft member having a 1 st portion and a 2 nd portion continuous with the 1 st portion;
the output member is fixed to the 1 st portion;
the serration part is formed at an outer circumferential part of the 1 st part;
the 1 st end face is a step difference between the 1 st part and the 2 nd part;
the output section includes:
a hole formed at the center of the output member for the 1 st portion to enter,
a plurality of teeth formed on the outer peripheral portion, an
The plurality of grooves formed at an inner periphery of the hole,
the shaft member has the plurality of 1 st protrusions;
the output member has the plurality of 2 nd recesses;
the output member forms the 2 nd recess between the center of the bore and the tooth.
2. The output shaft of claim 1,
the output member forms the slot between the center of the bore and the tooth.
3. Output shaft according to claim 1 or 2,
the shaft member forms the crest portion of the serration between the shaft center of the 1 st part and the 1 st projection.
4. The output shaft of claim 1,
the output member forms the 2 nd lobe between the center of the hole and the root between the heel and the tooth.
5. The output shaft of claim 1,
the 1 st portion has a locking portion in which a tip end portion protruding from the hole of the output member is deformed.
6. Output shaft according to claim 1 or 2,
the shaft member and the output member are made of sintered metal.
7. The output shaft of claim 6,
the output member is a carburized and quenched member.
8. Output shaft according to claim 1 or 2,
the number of the tooth tops of the serration part is an integer multiple of the number of the teeth.
9. A speed reducer, comprising:
a worm for driving the rotation of the motor,
a worm wheel meshed with the worm screw,
an output shaft according to any one of claims 1 to 8 engaged with a driven member to drive the driven member,
a transmission mechanism that transmits rotation of the worm wheel to the output shaft, an
A housing accommodating the worm wheel.
10. A motor with a speed reducer is characterized by comprising:
an electric machine, and
the reducer of claim 9 coupled to a shaft of the motor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015158272A JP6585419B2 (en) | 2015-08-10 | 2015-08-10 | Output shaft, reducer and motor with reducer |
| JP2015-158272 | 2015-08-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106438931A CN106438931A (en) | 2017-02-22 |
| CN106438931B true CN106438931B (en) | 2020-08-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510608501.2A Active CN106438931B (en) | 2015-08-10 | 2015-09-22 | Output shaft, speed reducer and motor with speed reducer |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6585419B2 (en) |
| CN (1) | CN106438931B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11052937B2 (en) * | 2018-01-19 | 2021-07-06 | Steering Solutions Ip Holding Corporation | Splined component assembly and method |
| KR102301016B1 (en) * | 2019-09-09 | 2021-09-13 | 현대위아 주식회사 | Constant velocity joint |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001339906A (en) * | 2000-05-24 | 2001-12-07 | Koito Mfg Co Ltd | Rotating drive unit |
| US20090188168A1 (en) * | 2008-01-28 | 2009-07-30 | Asmo Co., Ltd. | Door noise suppressing structure in open/close body drive apparatus |
| CN101563834A (en) * | 2006-12-21 | 2009-10-21 | 马渊马达株式会社 | Motor with speed reducer, and its manufacturing method |
| CN102269257A (en) * | 2010-05-14 | 2011-12-07 | 马渊马达株式会社 | Frame body, decelerator and motor equipped with decelerator |
| JP2012225430A (en) * | 2011-04-20 | 2012-11-15 | Ntn Corp | Sliding type constant velocity universal joint |
| CN102803789A (en) * | 2010-03-15 | 2012-11-28 | 马渊马达株式会社 | Worm wheel, reduction gear, and motor with reduction gear |
| CN103154556A (en) * | 2010-10-20 | 2013-06-12 | Ntn株式会社 | Electric direct-acting actuator and electric disc-brake device |
| CN103228941A (en) * | 2010-12-17 | 2013-07-31 | 阿斯莫有限公司 | Rotation transmitting device and motor |
| CN203098750U (en) * | 2013-02-28 | 2013-07-31 | 马渊马达株式会社 | Reducer, motor with reducer and output gear |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5532631Y2 (en) * | 1974-07-26 | 1980-08-04 | ||
| JP2008057629A (en) * | 2006-08-30 | 2008-03-13 | Toyota Motor Corp | Rotation-linear motion converting mechanism and its manufacturing method |
| JP5250825B2 (en) * | 2008-11-20 | 2013-07-31 | 株式会社ジェイテクト | Vehicle drive shaft |
| JP2012229724A (en) * | 2011-04-25 | 2012-11-22 | Mabuchi Motor Co Ltd | Reduction gear, motor with reduction gear and output gear |
| JP5353973B2 (en) * | 2011-08-23 | 2013-11-27 | 日本精工株式会社 | Torque transmission device for steering device |
-
2015
- 2015-08-10 JP JP2015158272A patent/JP6585419B2/en active Active
- 2015-09-22 CN CN201510608501.2A patent/CN106438931B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001339906A (en) * | 2000-05-24 | 2001-12-07 | Koito Mfg Co Ltd | Rotating drive unit |
| CN101563834A (en) * | 2006-12-21 | 2009-10-21 | 马渊马达株式会社 | Motor with speed reducer, and its manufacturing method |
| US20090188168A1 (en) * | 2008-01-28 | 2009-07-30 | Asmo Co., Ltd. | Door noise suppressing structure in open/close body drive apparatus |
| CN102803789A (en) * | 2010-03-15 | 2012-11-28 | 马渊马达株式会社 | Worm wheel, reduction gear, and motor with reduction gear |
| CN102269257A (en) * | 2010-05-14 | 2011-12-07 | 马渊马达株式会社 | Frame body, decelerator and motor equipped with decelerator |
| CN103154556A (en) * | 2010-10-20 | 2013-06-12 | Ntn株式会社 | Electric direct-acting actuator and electric disc-brake device |
| CN103228941A (en) * | 2010-12-17 | 2013-07-31 | 阿斯莫有限公司 | Rotation transmitting device and motor |
| JP2012225430A (en) * | 2011-04-20 | 2012-11-15 | Ntn Corp | Sliding type constant velocity universal joint |
| CN203098750U (en) * | 2013-02-28 | 2013-07-31 | 马渊马达株式会社 | Reducer, motor with reducer and output gear |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6585419B2 (en) | 2019-10-02 |
| JP2017036797A (en) | 2017-02-16 |
| CN106438931A (en) | 2017-02-22 |
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