WO2011118448A1 - 減速機構、減速機構付きモータ及び減速機構の製造方法 - Google Patents
減速機構、減速機構付きモータ及び減速機構の製造方法 Download PDFInfo
- Publication number
- WO2011118448A1 WO2011118448A1 PCT/JP2011/056035 JP2011056035W WO2011118448A1 WO 2011118448 A1 WO2011118448 A1 WO 2011118448A1 JP 2011056035 W JP2011056035 W JP 2011056035W WO 2011118448 A1 WO2011118448 A1 WO 2011118448A1
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- WIPO (PCT)
- Prior art keywords
- worm
- reduction mechanism
- speed reduction
- worm wheel
- meshing
- Prior art date
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
-
- 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
- F16H1/163—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 with balls between the co-operating parts
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0853—Skewed-shaft arrangement of the toothed members
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/088—Profiling with corrections on tip or foot of the teeth, e.g. addendum relief for better approach contact
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0886—Profiling with corrections along the width, e.g. flank width crowning for better load distribution
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
- H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
- H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
-
- 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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19828—Worm
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19828—Worm
- Y10T74/19842—Distribution of pressure
Definitions
- the present invention relates to a speed reduction mechanism including a worm and a worm wheel, a motor with a speed reduction mechanism, and a method of manufacturing the speed reduction mechanism.
- Patent Document 1 discloses a reduction mechanism that reduces the amount of wear by setting the pressure angle of the worm larger than the pressure angle of the worm wheel.
- the speed reduction mechanism of Patent Document 1 reduces the amount of wear by making the worm pressure angle slightly larger than the worm wheel pressure angle.
- a large loss of rotational force mainly due to kinetic friction occurs at the meshing portion, and the transmission efficiency of the rotational force is deteriorated. Therefore, improvement in the transmission efficiency of the rotational force is required.
- the efficiency of the motor becomes worse as the transmission efficiency of the rotational force becomes worse, and the desired speed reduction efficiency cannot be obtained. Therefore, the improvement of the transmission efficiency of rotational force is calculated
- An object of the present invention is to provide a speed reduction mechanism with high rotational force transmission efficiency, a motor with a speed reduction mechanism, and a method for manufacturing the speed reduction mechanism.
- a speed reduction mechanism including a worm and a worm wheel meshing with the worm.
- the number of meshing teeth is always n + 1 due to rotation, or deceleration that varies between n + 1 and n (where n is a natural number).
- the pressure angle of the worm is set larger than the pressure angle of the worm wheel so that the maximum number of meshing teeth is n or less.
- the number of meshing teeth is always n + 1 due to rotation under the condition that the pressure angles of the worm and the worm wheel are the same, or change between n + 1 and n (where n is a natural number).
- n is a natural number.
- the surface pressure on each tooth decreases, thereby increasing the friction coefficient and increasing the power loss at the meshing portion.
- the worm pressure angle is set larger than the worm wheel pressure angle so that the maximum number of meshing teeth is n or less, the number of meshing teeth does not become n + 1. Therefore, power loss can be reduced, and consequently rotation transmission efficiency can be improved.
- the number of meshing teeth is always 5 by rotation under the condition that the pressure angles of the worm and the worm wheel are the same, or between 5 and 4
- the pressure angle of the worm is set larger than the pressure angle of the worm wheel so that the maximum number of meshing teeth is 4 or less.
- the number of meshing teeth is always 5 by rotation, or in the worm and worm wheel that changes between 5 and 4,
- the surface pressure on each tooth is decreased, thereby increasing the coefficient of friction and increasing the power loss at the meshing portion.
- the worm pressure angle is set larger than the worm wheel pressure angle so that the maximum number of meshing teeth is 4 or less, the number of meshing teeth is not five. Therefore, power loss can be reduced, and consequently rotation transmission efficiency can be improved.
- the pressure angle of the worm is set to a maximum angle while the relationship between the worm and the worm wheel is established.
- the meshing tooth is set by setting the worm pressure angle to the maximum angle within the range in which the relationship between the worm and the worm wheel is established, that is, the worm and the worm wheel can function as a worm gear. The average of the numbers can be minimized. Therefore, the power loss can be greatly reduced, and the rotation transmission efficiency can be greatly improved.
- the motor with a speed reduction mechanism includes the speed reduction mechanism configured as described above and a motor body that rotationally drives the worm. According to this configuration, the efficiency of the motor with a speed reduction mechanism can be improved.
- a method for manufacturing a speed reduction mechanism including a worm and a worm wheel is provided.
- the number of meshing teeth is always n + 1 due to rotation, or deceleration that varies between n + 1 and n (where n is a natural number).
- the pressure angle of the worm is set larger than the pressure angle of the worm wheel so that the maximum number of meshing teeth is n or less.
- the number of meshing teeth is always n + 1 by rotation under the condition that the pressure angles of the worm and the worm wheel are the same, or change between n + 1 and n (where n is a natural number).
- n is a natural number
- the worm pressure angle is set larger than the worm wheel pressure angle so that the maximum number of meshing teeth is n or less, so the number of meshing teeth is n + 1. There is nothing. Therefore, power loss can be reduced, and consequently rotation transmission efficiency can be improved. Therefore, a speed reduction mechanism with good speed reduction efficiency can be easily manufactured.
- the schematic diagram of the motor with a speed-reduction mechanism which concerns on one embodiment of this invention.
- the schematic diagram which shows the structure of the motor main body of FIG. The schematic diagram which expand
- (A) And (b) is the elements on larger scale of the deceleration mechanism of FIG.
- (A) And (b) is the partial expansion schematic diagram of the deceleration mechanism which concerns on a prior art.
- (A) is the partial expansion schematic diagram which looked at the worm wheel in another example from the radial direction outer side.
- (B) is the partial expansion schematic diagram which looked at the worm wheel in another example from the axial direction.
- (C) is the partial expansion schematic diagram which looked at the worm in another example from the axial direction.
- the motor 1 with a speed reduction mechanism includes a motor body 2 and a gear portion 3.
- the motor 1 is used as a drive source for a vehicle wiper (not shown) that wipes the windshield of the vehicle.
- the motor body 2 includes a cylindrical yoke housing 4 having a bottom portion 4a, and at least one magnet having four magnetic pole portions (two N poles and two S poles) on the inner peripheral surface of the yoke housing 4. 5 is fixed. That is, the motor body 2 includes two magnetic circuits. In the magnet 5, the N pole and the S pole are alternately arranged in the circumferential direction of the yoke housing 4.
- a rotor (rotor) 6 that is an armature is rotatably disposed inside the magnet 5 in the radial direction.
- the rotor 6 includes a rotating shaft 7, a rotor core 63, and a commutator 25.
- the base end portion of the rotating shaft 7 located on the bottom portion 4a side of the yoke housing 4 is supported by a bearing 23 provided at the center of the bottom portion 4a. Further, the distal end portion of the rotating shaft 7 extends from the opening portion of the yoke housing 4 toward the gear portion 3.
- the rotor core 63 is disposed at a position facing the magnet 5 in the radial direction, and is fixed to the rotary shaft 7 so as to be integrally rotatable.
- the rotor core 63 includes 18 teeth 63a extending radially outward from the rotation shaft 7 in the radial direction.
- a slot 63b is formed in a space between teeth 63a adjacent to each other in the circumferential direction of the rotor core 63 (see FIG. 3).
- the commutator 25 is fixed to a portion of the rotary shaft 7 on the gear portion 3 side of the rotor core 63 so as to be integrally rotatable.
- the commutator 25 includes a cylindrical insulator (not shown) made of an insulating resin material and fitted on the rotary shaft 7, and 18 segments 27 fixed to the outer peripheral surface of the insulator.
- Each segment 27 has a rectangular plate shape that is long in the axial direction of the rotary shaft 7 and is curved along the outer peripheral surface of the insulator.
- the 18 segments 27 are arranged in parallel at equal angular intervals in the circumferential direction, and are arranged so as to exhibit a substantially cylindrical shape as a whole. Further, the segments 27 adjacent in the circumferential direction of the rotating shaft 7 are separated from each other in the circumferential direction of the rotating shaft 7.
- the gear portion 3 includes a gear housing 11 connected and fixed to the opening edge portion of the yoke housing 4.
- the gear housing 11 has an opening that opens toward the yoke housing 4, and a brush holder 32 disposed on the radially outer side of the commutator 25 is fixed to the opening by a screw 33.
- the brush holder 32 is made of an insulating resin material and has an annular shape.
- a cylindrical bearing holding portion 31 a extending along the axial direction of the rotating shaft 7 is provided in the opening portion of the gear housing 11.
- An annular bearing 34 that supports the substantially central portion of the rotating shaft 7 is accommodated in the bearing holding portion 31a.
- a ball bearing is used as the bearing 34. This is because when a sliding bearing such as a sintered metal bearing is used as the bearing 34, the required load capacity cannot be obtained and the bearing 34 may be damaged.
- the bearing 34 supports the rotary shaft 7 together with the bearing 23. Further, a screw-like worm 8 is formed at a portion of the rotating shaft 7 that passes through the bearing 34 and extends into the gear housing 11.
- the gear housing 11 has a worm housing recess 11a and a wheel housing recess 11b communicating with the worm housing recess 11a.
- a worm 8 is housed in the worm housing recess 11a, and a disk-like worm wheel 12 is housed in the wheel housing recess 11b in a state of being engaged with the worm 8.
- the worm 8 and the worm wheel 12 constitute a speed reduction mechanism 53 that decelerates the rotation of the rotary shaft 7.
- the worm 8 is made of metal.
- the worm wheel 12 is a self-lubricating resin having a linear molecular structure, and is made of, for example, POM (polyacetal) or PA (nylon).
- a connecting hole 12a is formed in the central portion of the worm wheel 12 in the radial direction, and a substantially cylindrical output shaft 54 that extends in the axial direction of the worm wheel 12 and rotates integrally with the worm wheel 12 is formed in the connecting hole 12a. Is provided.
- the distal end portion of the output shaft 54 protrudes outward from the gear housing 11, and the proximal end portion of the crank arm 55 is fixed to the distal end portion of the output shaft 54.
- a vehicle wiper (not shown) is connected to the tip of the crank arm 55 via a link mechanism (not shown).
- FIG. 3 is a schematic diagram in which the motor main body 2 and the power supply brush in the present embodiment are developed in a planar shape.
- 18 coils 65 are wound around the teeth 63 a by overlapping winding.
- Each coil 65 is wound around the rotor core 63 through the slot 63b so as to straddle the four teeth 63a continuously arranged in the circumferential direction.
- the winding start end of each coil 65 is connected to one of the segments 27, and the winding end end of each coil 65 is circumferentially connected to the segment 27 to which the winding start end is connected. It is connected to another adjacent segment 27.
- the brush holder 32 (see FIG. 2) provided in the gear unit 3 holds six power supply brushes 70 in the shape of a square tube extending in the radial direction.
- the six power supply brushes 70 two brushes are common brushes 71, the other two brushes are low-speed driving brushes 72, and the remaining two brushes are high-speed driving brushes 73.
- These brushes 71, 72, 73 are arranged in the order of the common brush 71, the high-speed driving brush 73, and the low-speed driving brush 72 from the rear side to the leading side in the rotational direction of the commutator 25.
- the high speed driving brush 73 is disposed on the common brush 71 on the leading side in the rotational direction of the commutator 25, and the low speed driving brush 72 is disposed on the leading side in the rotational direction of the commutator 25 with respect to the high speed driving brush 73. Has been placed.
- Each of the power supply brushes 70 is biased toward the commutator 25 by a spring or the like (not shown), and the tip thereof is on the outer peripheral surface of the commutator 25 (that is, the radially outer side surface of the segment 27). It is pressed so that it can slide. As shown in FIG. 3, segment numbers “1” to “18” are assigned to the 18 segments 27 in order in the circumferential direction.
- the common brush 71 functions as an anode brush, and the low speed driving brush 72 and the high speed driving brush 73 function as a cathode brush.
- a pigtail (not shown) is connected to each power supply brush 70, and current is supplied to the power supply brush 70 via these pigtails.
- the rotor 6 when current is supplied to the rotor 6 via the common brush 71 and the low-speed driving brush 72, the rotor 6 is rotated at a low speed. Further, when a current is supplied to the rotor 6 through the common brush 71 and the high-speed driving brush 73, the rotor 6 is rotated at a higher speed than at the time of low-speed driving.
- the rotation of the rotary shaft 7 is decelerated by the worm 8 and the worm wheel 12 and output from the output shaft 54, and the vehicle wiper connected to the crank arm 55 via the link mechanism is provided. It is reciprocally rotated.
- the width in the circumferential direction of the rotary shaft 7 and the circumferential direction of the rotary shaft 7 of the six power supply brushes 70 (that is, two common brushes 71, two low-speed driving brushes 72 and two high-speed driving brushes 73).
- the arrangement position will be described in detail.
- one type of three types of power supply brushes 70 that is, a common brush 71, a low-speed driving brush 72, and a high-speed driving brush 73, as the rotor 6 rotates.
- a short-circuit state in which only two power supply brushes 70 short-circuit two adjacent segments 27 in the circumferential direction (short-circuit state)
- a non-short-circuit state in which any power-supply brush 70 does not short-circuit two adjacent segments 27 in the circumferential direction (short-circuit state)
- the width in the circumferential direction and the width in the circumferential direction of each brush 71 to 73 are set so as to repeat the above.
- the number P of the magnetic pole portions of the magnet 5 is set to a value satisfying P ⁇ 4, and the number of teeth 63a and the number of segments 27 are set to the same number.
- the number of teeth 63a that is, the number of segments 27
- the value of S is set so that (2S / P) is an odd number.
- the width of the segment 27 is L1
- the interval between adjacent segments 27 is L2
- the width of the common brush 71 is B1
- the width of the low-speed driving brush 72 is B2
- the high-speed driving brush 73 Is B3.
- the three brushes 71 to 73 arranged with the high-speed driving brush 73 as the center are considered as one set, and the width of the arrangement area of the one set of brushes 71 to 73 is A, high-speed driving.
- the distance between the common brush 71 and the low-speed driving brush 72 across the brush 73 is D1
- the distance between the common brush 71 and the high-speed driving brush 73 is D2
- the high-speed driving brush 73 and the low-speed driving brush 73 The distance between the two is 72.
- each value is set so as to satisfy the following conditions.
- B1> L2, B2> L2, B3> L2 A ⁇ (n ⁇ L1 + (n + 1) ⁇ n2), D1> ((n ⁇ 1) ⁇ L1 + (n ⁇ 2) ⁇ L2), D2> (n1 ⁇ L1 + (n1-1) ⁇ L2) D3> (n2 ⁇ L1 + (n2-1) ⁇ L2) n n1 + n2 + 1 “N” is a number corresponding to the number of segments 27 arranged in the angular range of (360 ° / P).
- the common brush 71, the low-speed driving brush 72, and the high-speed driving brush 73 are set with the width in the circumferential direction and the arrangement position in the circumferential direction so as to satisfy the above conditions.
- the circumferential widths B 1, B 2, and B 3 have the same value and are narrower than the circumferential width of the segment 27.
- the common brush 71 and the low speed driving brush 72 arranged with the high speed driving brush 73 interposed therebetween are arranged at the same 90 ° intervals as the angular intervals between the adjacent magnetic pole portions of the magnet 5.
- the worm 8 and the worm wheel 12 of the present embodiment are set so that the pressure angle of the worm 8 is larger than the pressure angle of the worm wheel 12.
- the number of meshing teeth is always n + 1 due to rotation, or the worm and worm change between n + 1 and n (where n is a natural number).
- the pressure angle of the worm 8 is set larger than the pressure angle of the worm wheel 12 so that the maximum number of meshing teeth is n or less.
- the pressure angle of the worm 8 is set larger than the pressure angle of the worm wheel 12 so that the maximum number of meshing teeth is n or less.
- the pressure angles thereof are both ⁇ °, and the number of meshing teeth is five by rotation (FIG. 5 (a). )) And 4 (see FIG. 5B) (the average number of meshing teeth is 4.1).
- the pressure angle of such a worm 51 and the worm wheel 52 is the worm 8 and the worm wheel 12 shown to Fig.4 (a) and FIG.4 (b). That is, the pressure angle of the worm 8 is set larger than the pressure angle of the worm wheel 12 so that the maximum number of meshing teeth is 4 or less.
- the pressure angle of the worm wheel 12 is set to ⁇ ° and the pressure angle of the worm 8 is set to 1.76 ⁇ ⁇ °, so that the maximum number of meshing teeth is four. Therefore, the average number of meshing teeth is 3.7.
- the period (angle) in which the number of meshing teeth is four (the contact between) the teeth 8a of the worm 8 and the teeth 12b of the worm wheel 12 is in contact (contact).
- the period (angle) in which the number of meshing teeth is three occupies 30%.
- the pressure angle of the worm 8 is set large (in this embodiment, 1.76 ⁇ ⁇ °) so that the maximum number of meshing teeth is 4 or less, the normal pitch of the pressure angle is ⁇ Same as for °. Further, the pressure angle (1.76 ⁇ ⁇ °) of the worm 8 of the present embodiment is set to the maximum angle while the relationship between the worm 8 and the worm wheel 12 (so-called worm gear relationship) is established. Yes. At this maximum angle, the tooth tip of the worm 8 changes from a trapezoidal shape to a triangular shape, but the diameter of the worm 8 does not decrease. In addition, the pressure angle of the worm 8 in which the number of meshing teeth is always four is 1.2 ⁇ ⁇ °. Further, in FIGS. 4 and 5, in order to make it easy to visually understand that they are engaged (contacted), black circles are illustrated at the positions where they are engaged (contacted).
- the worm 8 is made of metal, and the worm wheel 12 is made of resin.
- FIG. 6 shows the relationship between the axial position and the meshing position in the worm 8 of the speed reduction mechanism 53 of FIG. That is, FIG. 6 shows meshing characteristics in the speed reduction mechanism 53 in which the worm 8 is made of metal, the worm wheel 12 is made of resin, and the pressure angle of the worm 8 is larger than the pressure angle of the worm wheel 12.
- FIG. 7 shows the relationship between the axial position and the meshing position in the worm 51 of the conventional reduction mechanism of FIG. That is, FIG.
- FIG. 7 shows meshing characteristics in a speed reduction mechanism in which the worm 51 is made of metal, the worm wheel 52 is made of resin, and the pressure angles of the worm 51 and the worm wheel 52 are the same.
- “Axial position” indicates the axial position of the worm
- “engagement position” indicates the engagement position of the worm and the worm wheel as the position in the radial direction of the worm.
- the “output shaft center” indicates a position in the worm axial direction of a straight line that is orthogonal to the worm axis and passes through the worm wheel axis. Note that the value of the “engagement position” increases as the engagement position approaches the tooth bottom of the worm.
- the meshing position has the maximum value at the center of the output shaft, and the meshing position at the meshing start and meshing end has substantially the same value.
- the axial position E2 at the start of meshing between the worm 51 and the worm wheel 52 is relatively far from the output shaft center 0, and the shaft at the meshing end is correspondingly increased.
- the direction position D2 is relatively close to the output shaft center 0.
- the maximum value H2 of the meshing position is relatively small, and the interval W2 between the position of the maximum value H2 and the output shaft center 0 is relatively large.
- the center C2 of the range from the axial position E2 at the start of meshing to the axial position D2 at the meshing end is located on the side of the axial position E2 at which meshing starts with respect to the output shaft center 0.
- the axial position E1 at the start of meshing between the worm 8 and the worm wheel 12 is relative to the output shaft center 0 as compared with the conventional speed reduction mechanism.
- the axial position D1 at the end of engagement is farther from the output shaft center 0.
- the maximum value H1 of the meshing position is larger than that of the conventional reduction device, and the interval W1 between the position of the maximum value H2 and the output shaft center 0 is smaller than that of the conventional reduction device.
- the center C1 in the range from the axial position E1 at the start of engagement to the axial position D1 at the end of engagement is located on the side of the axial position D1 at the end of engagement with respect to the output shaft center 0.
- the pressure angle of the worm 8 is 1.76 which is the maximum angle in the range where the relationship between the worm 8 and the worm wheel 12 is established, that is, the worm 8 and the worm wheel 12 can function as a worm gear. Since x ⁇ °, the average number of meshing teeth can be set to the minimum of 3.7. Therefore, the power loss can be greatly reduced, and the rotation transmission efficiency can be greatly improved.
- the worm wheel 12 is made of a self-lubricating resin having a linear molecular structure, when pressure is applied from the worm 8, molecules on the surface of the worm wheel 12 follow the direction of pressure from the worm 8. It is arranged in a straight line and the friction is further reduced in the pressure direction. Therefore, power loss due to dynamic friction can be greatly reduced, and rotation transmission efficiency can be further improved.
- the above embodiment may be modified as follows.
- the speed reduction mechanism in which the number of meshing teeth changes between 5 and 4 by rotation under the condition that the pressure angles of the worm 8 and the worm wheel 12 are both ⁇ ° has been described.
- the maximum meshing is achieved for the speed reduction mechanism in which the number of meshing teeth is always n + 1 by rotation or changes between n + 1 and n (where n is a natural number).
- the pressure angle of the worm 8 may be set so that the number of teeth is n or less.
- the maximum number of meshing teeth is 5 or less.
- the pressure angle of the worm 8 may be set.
- the maximum number of meshing teeth is 3 or less.
- the pressure angle of the worm 8 is set to 1.76 ⁇ ⁇ °, but is not limited to this. Under the condition that the pressure angles are the same, the maximum meshing is achieved for a speed reduction mechanism in which the number of meshing teeth is always n + 1 due to rotation or changes between n + 1 and n (where n is a natural number). As long as the pressure angle of the worm 8 is set so that the number of teeth is n or less, the pressure angle of the worm 8 may be appropriately changed.
- the pressure angle of the worm 8 is 1.76 ⁇ ⁇ which is the maximum angle in the relationship between the worm 8 and the worm wheel 12 (within the range in which the worm 8 and the worm wheel 12 can function as a worm gear). It may be set at or below (for example, 1.5 ⁇ ⁇ °, 1.2 ⁇ ⁇ °, etc.). If the pressure angle of the worm wheel is changed to other than ⁇ °, for example, the pressure angle of the worm that satisfies the condition changes. Even in this case, if the worm pressure angle is set to the maximum while the relationship between the worm and the worm wheel is established, the average number of meshing teeth can be minimized and power loss can be greatly reduced. As a result, the rotation transmission efficiency can be greatly improved.
- the shape of the teeth 12b of the worm wheel 12 may be a shape in which notches 12c are formed at both ends in the axial direction when viewed from the outside in the radial direction, as shown in FIG. 8 (a). .
- both ends of the teeth 12b of the worm wheel 12 in the axial direction are different from a simple linear shape as shown by a broken line in FIG. It may be a shape (a shape in which the notch portion 12c is formed) scraped off so as to be narrow.
- the tip shape of the teeth 12b of the worm wheel 12 may be a shape in which a notch 12d is formed so as to be tapered when viewed from the axial direction. .
- the tip of the tooth 12b of the worm wheel 12 is tapered so that the width is abruptly narrowed, as seen from the axial direction, unlike a simple smooth curved shape as shown by a broken line in FIG. 8B.
- the shape may be cut off (the shape in which the notch 12d is formed).
- the tip shape of the tooth 8a of the worm 8 may be a shape in which the notch portion 8b is formed so as to be tapered when viewed from the direction perpendicular to the axis, as shown in FIG. 8C. .
- the tip of the tooth 8a of the worm 8 is shaved so as to taper off abruptly, unlike a simple linear shape as shown by a broken line in FIG.
- the shape shape (shape in which the notch part 8b was formed) may be sufficient.
- the present invention is embodied in the motor 1 with a speed reduction mechanism including the speed reduction mechanism (worm 8 and worm wheel 12) and the motor main body 2 that rotationally drives the worm 8.
- the motor main body 2 is provided. It may be embodied as a speed reduction mechanism used in other devices that are not.
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Abstract
Description
同構成によれば、ウォームの圧力角を、ウォームとウォームホイールとの関係が成り立つ中で、すなわち、ウォームとウォームホイールとがウォームギヤとして機能し得る範囲で、最大の角度とすることで噛合い歯数の平均を最小とすることができる。そのため、動力損失を大幅に低減することができ、ひいては回転伝達効率を大幅に向上させることができる。
同構成によれば、減速機構付きモータの効率を向上させることができる。
図1及び2に示すように、減速機構付きモータ1は、モータ本体2とギヤ部3とを備えている。このモータ1は、車両のフロントガラス等を払拭する車両用ワイパ(図示略)の駆動源として用いられる。
図3に示すように、前記ティース63aには、18個のコイル65が重ね巻にて巻装されている。各コイル65は、連続して周方向に並ぶ4つのティース63aをそれぞれ跨ぐように、スロット63bを通ってロータコア63に巻装されている。また、各コイル65の巻き始めの端部は前記セグメント27のうちの一つに接続され、各コイル65の巻き終わりの端部は前記巻き始めの端部が接続されたセグメント27と周方向に隣り合う他のセグメント27に接続されている。
B1>L2、B2>L2、B3>L2
A<(n×L1+(n+1)×n2)、
D1>((n-1)×L1+(n-2)×L2)、
D2>(n1×L1+(n1-1)×L2)
D3>(n2×L1+(n2-1)×L2)
n=n1+n2+1
尚、「n」は、(360°/P)の角度範囲に配置されたセグメント27の数に相当する数である。言い換えると、「n」は、モータ本体2に備えられるセグメント27の数(即ちティース63aの数Sに同じ)を磁極部の数Pで割って得られた商である。商が整数でない場合には、切り上げた数が「n」とされる。また、「n1」及び「n2」は、前記「n=n1+n2+1」を満たす正の整数である。本実施形態のように、マグネット5の磁極部の数Pが「4」、セグメント27の数が「18」であるときは、例えば、n=5、n1=2、n2=2に設定される。
(1)ウォーム及びウォームホイールの圧力角が互いに同じ(共にα°)という条件下では回転により噛合い歯数が5つと4つとの間で変化するウォーム及びウォームホイールでは、噛合い歯数が5つに増加すると各歯に対する面圧が低下し、それにより摩擦係数が増大し、噛合い部分での動力損失が増大してしまう。しかし、本実施の形態では、最大の噛合い歯数が4以下となるようにウォーム8の圧力角がウォームホイール12の圧力角より大きく設定されるため、噛合い歯数が5つとなることがない。そのため、動力損失を低減することができ、ひいては回転伝達効率を向上させることができる。即ち、本実施の形態のように噛合い歯数が減少すると各歯に対する面圧が増大し、それにより摩擦係数が低下し、噛合い部分での動力損失を低減できることになり、ひいては回転伝達効率を向上させることができる。よって、減速機構付きモータ1の効率を向上させることができる。又、ウォーム8の圧力角を上記のように設定する製造方法では、回転伝達効率の良い減速機構(減速機構付きモータ1)を容易に製造することができる。
上記実施の形態では、ウォーム8及びウォームホイール12の圧力角が共にα°という条件下では回転により噛合い歯数が5つと4つとの間で変化する減速機構について記載した。圧力角が共に同じという条件下では回転により噛合い歯数が常時n+1になるか、若しくは、n+1とn(但し、nは自然数)との間で変化するような減速機構について、最大の噛合い歯数がn以下となるようにウォーム8の圧力角が設定されればよい。例えば、ウォーム及びウォームホイールの圧力角が互いに同じという条件下では回転により噛合い歯数が6つと5つとの間で変化するような減速機構について、最大の噛合い歯数が5以下となるようにウォーム8の圧力角が設定されればよい。又、例えば、ウォーム及びウォームホイールの圧力角が互いに同じという条件下ででは回転により噛合い歯数が4つと3つとに変化するような減速機構について、最大の噛合い歯数が3以下となるようにウォーム8の圧力角が設定されればよい。このようにしても、動力損失を低減することができ、ひいては回転伝達効率を向上させることができる。
Claims (5)
- ウォームと、
前記ウォームに噛合するウォームホイールと、
を備えた減速機構であって、
前記ウォーム及び前記ウォームホイールの圧力角が互いに同じという条件下では回転により噛合い歯数が常時n+1になるか、若しくは、n+1とn(但し、nは自然数)との間で変化するような減速機構について、最大の噛合い歯数がn以下となるように前記ウォームの圧力角が前記ウォームホイールの圧力角より大きく設定される減速機構。 - 前記ウォーム及び前記ウォームホイールの圧力角が互いに同じという条件下では回転により噛合い歯数が常時5つになるか、若しくは、5つと4つとの間で変化するような減速機構について、最大の噛合い歯数が4つ以下となるように前記ウォームの圧力角が前記ウォームホイールの圧力角より大きく設定される請求項1に記載の減速機構。
- 前記ウォームの圧力角は、前記ウォームと前記ウォームホイールとの関係が成り立つ中で、最大の角度に設定される請求項1又は2に記載の減速機構。
- 請求項1~3のいずれか一項に記載の減速機構と、
前記ウォームを回転駆動するモータ本体と
を備える減速機構付きモータ。 - ウォーム及びウォームホイールを備える減速機構の製造方法であって、
前記ウォーム及び前記ウォームホイールの圧力角が互いに同じという条件下では回転により噛合い歯数が常時n+1になるか、若しくは、n+1とn(但し、nは自然数)との間で変化するような減速機構について、最大の噛合い歯数がn以下となるように前記ウォームの圧力角を前記ウォームホイールの圧力角より大きく設定する製造方法。
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US13/635,319 US9154015B2 (en) | 2010-03-24 | 2011-03-15 | Speed reduction mechanism, motor with speed reduction mechanism, and method for producing speed reduction mechanism |
CN201180015716.3A CN102822564B (zh) | 2010-03-24 | 2011-03-15 | 减速机构、带减速机构的电动机、及减速机构的制造方法 |
KR1020127025056A KR101742045B1 (ko) | 2010-03-24 | 2011-03-15 | 감속 기구, 감속 기구 부착 모터 및 감속 기구의 제조 방법 |
DE112011100994.1T DE112011100994B4 (de) | 2010-03-24 | 2011-03-15 | Untersetzungsmechanismus und Motor mit Untersetzungsmechanismus |
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BR112012023644A BR112012023644B1 (pt) | 2010-03-24 | 2011-03-15 | mecanismo de redução de velocidade, motor com mecanismo de redução de velocidade, e método para a produção de um mecanismo de redução de velocidade |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108087496A (zh) * | 2016-11-21 | 2018-05-29 | 马渊马达株式会社 | 齿轮单元、减速器及带减速器的马达 |
WO2019044139A1 (ja) * | 2017-08-30 | 2019-03-07 | 株式会社ミツバ | 減速機構付モータ |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BR112012023644B1 (pt) * | 2010-03-24 | 2020-04-07 | Asmo Co Ltd | mecanismo de redução de velocidade, motor com mecanismo de redução de velocidade, e método para a produção de um mecanismo de redução de velocidade |
CN103883707B (zh) * | 2014-04-21 | 2016-05-11 | 株洲齿轮有限责任公司 | 齿轮及齿轮组 |
DE102014210253B4 (de) * | 2014-05-28 | 2016-02-11 | Aktiebolaget Skf | Getriebe für eine in einer Höhe verstellbare Ablage sowie Verfahren zum Verändern einer Höhe einer Ablage |
USD774576S1 (en) * | 2015-04-20 | 2016-12-20 | SZ DJI Technology Co., Ltd. | Motor |
JP6566245B2 (ja) * | 2015-05-21 | 2019-08-28 | 株式会社ジェイテクト | ウォーム減速機およびステアリング装置 |
CN105106479A (zh) * | 2015-10-13 | 2015-12-02 | 王俊英 | 一种用于防治化疗药物外渗性损伤的中药及多功能搅拌装置 |
JP2017194127A (ja) * | 2016-04-21 | 2017-10-26 | 株式会社ジェイテクト | ウォーム減速機および電動パワーステアリング装置 |
CN108245357B (zh) * | 2016-12-28 | 2020-07-14 | 美好罗伯特有限公司 | 机械手术台以及混合手术室系统 |
EP3406939B1 (de) * | 2017-05-24 | 2020-04-01 | IMS Gear SE & Co. KGaA | Zahnradpaarung für ein schraubradgetriebe oder ein stirnradgetriebe, schraubradgetriebe oder stirnradgetriebe mit einer derartigen zahnradpaarung sowie verwendung einer derartigen zahnradpaarung in schraubradgetrieben und stirnradgetrieben |
US20200255053A1 (en) | 2019-02-12 | 2020-08-13 | Steering Solutions Ip Holding Corporation | Worm shaft for steering assembly |
DE102019217019A1 (de) * | 2019-11-05 | 2021-05-06 | Robert Bosch Gmbh | Getriebeverzahnung |
CN112564353A (zh) * | 2020-12-24 | 2021-03-26 | 贵阳万江航空机电有限公司 | 一种电机转子端部的限位结构及限位方法 |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004066947A (ja) * | 2002-08-06 | 2004-03-04 | Honda Motor Co Ltd | 電動パワーステアリング装置 |
Family Cites Families (34)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1525642A (en) * | 1922-09-28 | 1925-02-10 | Anthony B Cox | Gear teeth and method of designing the same |
US1790607A (en) * | 1929-03-11 | 1931-01-27 | Nikola Trbojevich | Steering gear |
PL146060B2 (en) * | 1986-12-17 | 1988-12-31 | Gear transmission with variable pressure angle and method of machining tooth profiles of such gear | |
DE4041567C2 (de) * | 1990-12-22 | 2001-07-26 | Zahnradfertigung Ott Gmbh U Co | Schneckengetriebe |
JPH05338067A (ja) * | 1992-06-05 | 1993-12-21 | Mitsubishi Heavy Ind Ltd | シングルフェーサ |
JPH10220561A (ja) * | 1997-02-05 | 1998-08-21 | Polyplastics Co | 樹脂歯車対 |
KR19990005289U (ko) * | 1997-07-15 | 1999-02-05 | 이영서 | 마이컴 회로를 이용한 가스 차단 안정장치 |
JP2000097293A (ja) | 1998-09-24 | 2000-04-04 | Yuuji Hanaguchi | 無端帯式のウオーム減速機 |
US6247376B1 (en) * | 1999-07-13 | 2001-06-19 | Valeo Electrical Systems, Inc. | Rollable enveloped worm with two curve profile |
JP2002139127A (ja) * | 2000-11-07 | 2002-05-17 | Nsk Ltd | 電動式パワーステアリング装置のギヤ |
US6571655B2 (en) * | 2001-07-26 | 2003-06-03 | Juken Kogyo Co., Ltd. | Involute gear pair structure |
US6976556B2 (en) * | 2002-08-06 | 2005-12-20 | Honda Giken Kogyo Kabushiki Kaisha | Electric power steering apparatus |
US7798033B2 (en) * | 2002-11-14 | 2010-09-21 | Ims Gear Gmbh | Power-assisted steering having a gear mechanism |
JP4069023B2 (ja) * | 2003-06-12 | 2008-03-26 | 本田技研工業株式会社 | ウォームホイールの加工方法 |
JP2005012673A (ja) * | 2003-06-20 | 2005-01-13 | Shinko Electric Ind Co Ltd | データ通信システム、icタグおよびリーダライタ |
US7174865B2 (en) * | 2004-07-19 | 2007-02-13 | Masami Sakita | Engine with a variable compression ratio |
US20070078038A1 (en) * | 2004-07-20 | 2007-04-05 | Teruhisa Ando | Gear mechanism and reduction planetary gear |
JP2006177426A (ja) | 2004-12-22 | 2006-07-06 | Mabuchi Motor Co Ltd | 減速機付小型モータ |
US8100028B2 (en) * | 2005-04-08 | 2012-01-24 | Tsutomu Miyaoku | Cornu's spiral tooth gear |
RU2291337C1 (ru) * | 2005-06-01 | 2007-01-10 | Открытое акционерное общество "Электростальский завод тяжелого машиностроения" | Беззазорная червячная передача и способ нарезания зубьев червячного колеса беззазорной червячной передачи |
US7721616B2 (en) * | 2005-12-05 | 2010-05-25 | Gm Global Technology Operations, Inc. | Sprung gear set and method |
JP4801482B2 (ja) * | 2006-03-30 | 2011-10-26 | 本田技研工業株式会社 | 電動ステアリング装置 |
JP2008002526A (ja) | 2006-06-21 | 2008-01-10 | Asmo Co Ltd | ウォーム及びモータ装置 |
US8250940B2 (en) * | 2006-07-20 | 2012-08-28 | Steering Solutions Ip Holding Corporation | System and method for controlling contact between members in operable communication |
CN101162037B (zh) * | 2006-10-11 | 2011-08-03 | 德昌电机股份有限公司 | 蜗轮传动机构 |
US7484438B2 (en) * | 2006-12-12 | 2009-02-03 | Robert Murphy | Right angle driving tool |
JP2009047267A (ja) | 2007-08-21 | 2009-03-05 | Asmo Co Ltd | ウォーム及びモータ装置 |
CN201083251Y (zh) * | 2007-09-20 | 2008-07-09 | 国营江北机械厂 | 小模数大功率蜗轮蜗杆副 |
US8408353B2 (en) * | 2008-02-12 | 2013-04-02 | Jtekt Corporation | Vehicle steering apparatus |
JP5100781B2 (ja) | 2009-04-21 | 2012-12-19 | 本田技研工業株式会社 | ウォームギヤ機構及びウォームギヤ機構を搭載した電動パワーステアリング装置 |
US7926381B2 (en) * | 2009-06-30 | 2011-04-19 | Hamilton Sundstrand Corporation | Idler gear for a generator |
BR112012023644B1 (pt) * | 2010-03-24 | 2020-04-07 | Asmo Co Ltd | mecanismo de redução de velocidade, motor com mecanismo de redução de velocidade, e método para a produção de um mecanismo de redução de velocidade |
JP5776924B2 (ja) * | 2010-08-31 | 2015-09-09 | アイシン精機株式会社 | 歯車加工装置、カッター、及び波動歯車装置 |
KR101686206B1 (ko) * | 2013-04-02 | 2016-12-13 | 주식회사 만도 | 자동차의 전동식 동력 보조 조향장치 및 이의 조립 방법 |
-
2011
- 2011-03-15 BR BR112012023644A patent/BR112012023644B1/pt active IP Right Grant
- 2011-03-15 JP JP2012506951A patent/JP5378593B2/ja active Active
- 2011-03-15 KR KR1020127025056A patent/KR101742045B1/ko active IP Right Grant
- 2011-03-15 US US13/635,319 patent/US9154015B2/en active Active
- 2011-03-15 WO PCT/JP2011/056035 patent/WO2011118448A1/ja active Application Filing
- 2011-03-15 CN CN201180015716.3A patent/CN102822564B/zh active Active
- 2011-03-15 DE DE112011100994.1T patent/DE112011100994B4/de active Active
- 2011-03-15 CN CN201610023710.5A patent/CN105610276B/zh active Active
- 2011-03-15 KR KR1020167001552A patent/KR101676330B1/ko active IP Right Grant
-
2013
- 2013-09-24 JP JP2013197155A patent/JP5711331B2/ja active Active
-
2015
- 2015-03-03 JP JP2015041288A patent/JP5977387B2/ja active Active
- 2015-09-01 US US14/841,925 patent/US10024414B2/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004066947A (ja) * | 2002-08-06 | 2004-03-04 | Honda Motor Co Ltd | 電動パワーステアリング装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108087496A (zh) * | 2016-11-21 | 2018-05-29 | 马渊马达株式会社 | 齿轮单元、减速器及带减速器的马达 |
WO2019044139A1 (ja) * | 2017-08-30 | 2019-03-07 | 株式会社ミツバ | 減速機構付モータ |
US11870324B2 (en) | 2017-08-30 | 2024-01-09 | Mitsuba Corporation | Motor having deceleration mechanism |
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Publication number | Publication date |
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JP5711331B2 (ja) | 2015-04-30 |
JP2015111008A (ja) | 2015-06-18 |
JP2013253705A (ja) | 2013-12-19 |
KR20130016238A (ko) | 2013-02-14 |
CN102822564B (zh) | 2016-02-10 |
BR112012023644B1 (pt) | 2020-04-07 |
US20130008276A1 (en) | 2013-01-10 |
CN102822564A (zh) | 2012-12-12 |
DE112011100994T5 (de) | 2013-02-07 |
KR101676330B1 (ko) | 2016-11-15 |
US20150369353A1 (en) | 2015-12-24 |
KR101742045B1 (ko) | 2017-05-31 |
CN105610276B (zh) | 2018-09-14 |
JP5378593B2 (ja) | 2013-12-25 |
DE112011100994B4 (de) | 2023-03-16 |
JP5977387B2 (ja) | 2016-08-24 |
JPWO2011118448A1 (ja) | 2013-07-04 |
BR112012023644A2 (pt) | 2016-08-02 |
CN105610276A (zh) | 2016-05-25 |
US9154015B2 (en) | 2015-10-06 |
KR20160017097A (ko) | 2016-02-15 |
US10024414B2 (en) | 2018-07-17 |
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