WO2011024964A1 - 多軸駆動装置 - Google Patents
多軸駆動装置 Download PDFInfo
- Publication number
- WO2011024964A1 WO2011024964A1 PCT/JP2010/064628 JP2010064628W WO2011024964A1 WO 2011024964 A1 WO2011024964 A1 WO 2011024964A1 JP 2010064628 W JP2010064628 W JP 2010064628W WO 2011024964 A1 WO2011024964 A1 WO 2011024964A1
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- WO
- WIPO (PCT)
- Prior art keywords
- output
- input
- gear
- drive device
- axis drive
- Prior art date
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- 230000007246 mechanism Effects 0.000 claims description 71
- 230000002093 peripheral effect Effects 0.000 claims description 44
- 230000009471 action Effects 0.000 claims description 17
- 238000000926 separation method Methods 0.000 abstract 1
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- 238000007906 compression Methods 0.000 description 12
- 230000005540 biological transmission Effects 0.000 description 10
- 230000008901 benefit Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000007704 transition Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000035807 sensation Effects 0.000 description 1
Images
Classifications
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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
- F16H1/14—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising conical gears only
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/0296—Central command actuator to selectively switch on or engage one of several special purpose circuits or mechanisms
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/0224—Non-manual adjustments, e.g. with electrical operation
- B60N2/02246—Electric motors therefor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/04—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable
- B60N2/06—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable slidable
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/04—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable
- B60N2/16—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable height-adjustable
-
- 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
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/16—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and oscillating motion
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/065—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with a plurality of driving or driven shafts
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
- F16H2063/3056—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using cam or crank gearing
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
-
- 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
- Y10T74/19023—Plural power paths to and/or from gearing
- Y10T74/19051—Single driven plural drives
-
- 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
- Y10T74/19219—Interchangeably locked
- Y10T74/19251—Control mechanism
-
- 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
- Y10T74/19219—Interchangeably locked
- Y10T74/19251—Control mechanism
- Y10T74/19279—Cam operated
Definitions
- the present invention relates to a multi-axis drive device that drives a plurality of output shafts with a single motor suitable for application to, for example, an electric seat for vehicles.
- the vehicle seat can be adjusted to the position and position of the occupant by adjusting the position of multiple locations, such as sliding in the entire longitudinal direction, vertical movement of the seating surface, or reclining of the seat back (backrest). Many of these formats are used.
- the adjustment of these movable parts was performed manually, but as a more convenient one, an electric seat that is adjusted by motor drive is provided.
- the drive device using the electromagnetic clutch described in Patent Documents 1 and 2 is disadvantageous in terms of economy due to the cost of the electromagnetic clutch.
- the drive devices described in Patent Documents 3 and 4 contribute to the cost reduction because the clutch is mechanical, but are not designed to reduce the weight and space of the output shaft selection mechanism. There wasn't.
- the present invention provides a multi-axis drive device that can reduce weight and space by adopting a mechanical clutch with a simplified configuration when driving a plurality of output shafts with one motor. It is an object.
- the multi-axis drive device of the present invention has an input member connected to the rotating shaft of the motor and an output shaft, is provided so as to be freely disengaged from the input member, and the input member rotates when engaged.
- a plurality of output members to be transmitted and a plurality of output members are disposed between the plurality of output members and have an action portion.
- a selector member that selectively engages the output member with the input member by moving the output member toward the input member, and a rotary operation that is connected to the selector member and is operated by rotating the selector member. And a member.
- the selector member is rotated by the operation member so that the action portion is opposed to any output member, the output member is moved to the input member side, and the output member is engaged with the input member. Thereby, rotation of an input member can be transmitted to an output member.
- the mechanism for branching the power of the motor to a plurality of output members and the selection of the output member to be operated are achieved with a compact configuration in which the output members are arranged around the selector member. Can be achieved.
- the action part of the selector member of the present invention includes a form that is a concave or convex part formed on the surface of the selector member facing the output member.
- the action portion of the selector member of the present invention includes a form in which the action portion is provided in a plurality of stages in a direction orthogonal to the operation direction of the selector member. According to this embodiment, a large number of output shafts can be arranged according to the number of stages of the cam surface, and a larger number of output shafts can be incorporated.
- the present invention includes a mode in which the opposing angle of the output shaft to the action portion is arbitrarily set.
- the output member can be arranged according to a preferable direction in which the output shaft extends.
- the action part is a concave part
- the output member includes a form having a convex part that protrudes from the front end surface and fits into the concave part.
- an action part is a convex part
- an output member includes a form pressed by this convex part.
- the output member includes a bevel gear
- the input member includes a bevel gear that meshes with the bevel gear by crossing the axes.
- the input member is a spur gear to which the rotation of the motor is transmitted
- the output member includes a spur gear that meshes with the spur gear
- the selector member includes an urging unit that urges the output member toward the input member, and the selector member has a cylindrical curved surface and contacts the output member to separate the output member from the input member. And a recess for moving the output member toward the input member by fitting the output member.
- the output member is moved by the urging force of the urging means and engaged with the input member.
- the output member is engaged with the input member by one operation of rotating the selector member, and a click feeling is obtained when the output member is fitted in the recess, so that the operability and the operational feeling are excellent.
- a convex part can be provided instead of the concave part. That is, a biasing means for biasing the output member in a direction away from the input member is provided, and the selector member has an outer peripheral portion that forms a cylindrical curved surface and contacts the output member to separate the output member from the input member. A convex portion that is provided on the outer peripheral portion and moves the output member toward the input member by pressing the output member can be provided. Even in such an aspect, the output member can be engaged with the input member by one operation of rotating the selector member.
- the input member When the operation mode of the selector member is rotation, the input member can be constituted by one gear, but the first input gear connected to the rotation shaft of the motor and the outer peripheral side of the first input gear
- the second input gear includes a first gear portion that meshes with the outer peripheral portion of the first input gear, and a second gear portion that meshes freely with the output member. It can be made into the form. In such a form, since the output member can be engaged with the second gear portion from an arbitrary direction, the degree of freedom in design increases as described below.
- the output member is preferably provided so that the position can be arbitrarily set along a circle centered on the axis of the second input gear, and the second input gear is centered on the axis of the first input gear. It is desirable that the position can be arbitrarily set along the circle. In such an aspect, the position and angle of the output member can be appropriately changed according to the position of the member to which the output member is connected.
- the present invention includes the following modes.
- the selector member is provided on the cam surface, and a cam surface that separates the output member from the input member by contacting the output member. And a recess that moves the output member toward the input member when the output member is fitted.
- a click feeling can be obtained when the output member is fitted in the recess, so that the operability and the operation feeling are excellent.
- the biasing means biases the output member in a direction away from the input member, and the selector member comes into contact with the output member to separate the output member from the input member, and the cam. It can also be set as the structure provided with the convex part which is provided in the surface and moves this output member to the input member side by pressing an output member.
- stopper means for restricting the movement range of the selector member. According to this aspect, it is possible to prevent the output shaft from being detached from the cam surface.
- a movable part provided in a predetermined movable mechanism is connected to the output member, and a switch for operating the motor is slidably provided on the operation member. It is possible to adopt a configuration in which the motor is rotated forward by sliding in the direction, and the motor is reversed by sliding in the reverse direction, and the sliding direction of the switch coincides with the movable direction of the movable part.
- a vehicle seat can be applied as the movable mechanism, and in this case, the output member is connected to the adjustment mechanism of the movable part of the vehicle seat.
- Such an aspect has an advantage that it is easy to use because the operation sensation matches the actual operation.
- the mechanism for branching the power of the motor to the plurality of output members and the selection of the output member to be operated are achieved with a compact configuration, it is possible to reduce the weight and save space. Play.
- FIG. 4 is a partially fragmented front view taken along line II in FIG. 3 of the multi-axis drive device according to the first embodiment of the present invention. It is the II-II arrow directional view of FIG.
- FIG. 3 is a view taken in the direction of arrow III in FIG. 1. It is a side view which shows the usage example of the multi-axis drive device of 1st Embodiment. It is a partially broken front view of the multi-axis drive device concerning a 2nd embodiment of the present invention.
- FIG. 6 is a view on arrow VI in FIG. 5. It is a partial crushing front view of the multi-axis drive device concerning a 3rd embodiment of the present invention.
- FIG. 4 is a partially fragmented front view taken along line II in FIG. 3 of the multi-axis drive device according to the first embodiment of the present invention. It is the II-II arrow directional view of FIG.
- FIG. 3 is a view taken in the direction of arrow III in FIG. 1. It is a
- FIG. 8 is a cross-sectional view taken along arrow XIII-XIII in FIG. 7. It is a partially broken front view of the multi-axis drive device concerning a 4th embodiment of the present invention. It is a partially fractured front view of the multi-axis drive device concerning a 5th embodiment of the present invention. It is an axial sectional view of a cam in a 5th embodiment. It is a top view which shows typically the multi-axis drive device which concerns on 6th Embodiment of this invention. It is a front view which shows the multi-axis drive device typically. It is a top view which shows the modification of 6th Embodiment. It is a side view which shows the other modification of 6th Embodiment. It is a top view of the modification.
- FIGS. 1 to 11 show a multi-axis drive device according to the first embodiment.
- This multi-axis drive device has, for example, three movable mechanisms: a mechanism for adjusting the height of the seat seat surface, a reclining mechanism for adjusting the angle of the seat back portion, and a mechanism for adjusting the front-rear position of the seat.
- it is suitable for operating these movable mechanisms by selectively diverging the power of one motor 10 that rotates forward and backward.
- the motor 10 is fixed to a main frame 1 having a disk shape at one end on the side from which a motor shaft (motor rotation shaft) 11 protrudes.
- a first input gear 12 is fixed to the tip of the motor shaft 11.
- Three bearings 13 are concentrically arranged around the motor 10 around the motor 10, and a shaft 15 of a second input gear (input member) 14 is rotatably supported on the bearing 13.
- the second input gear 14 includes a spur gear portion (first gear portion) 14a that meshes with the first input gear 12, and a bevel gear portion (second gear portion) 14b that is disposed at a distance from the spur gear portion 14a. It is made up of.
- the three second input gears 14 are arranged such that their rotational centers are located at the vertices of an isosceles triangle.
- the main frame 1 has a rectangular plate-like sub frame 2 attached thereto.
- the end portion of the subframe 2 is cut out in a semicircular shape, and that portion is fitted to the side surface of the bearing 13.
- a bearing block 3 is attached to one surface of the subframe 2, and an output shaft 22 of an output gear (output member) 21 is rotatably supported on the bearing block 3.
- the output gear 21 is a bevel gear that can mesh with the bevel gear portion 14 b of the second input gear 14, and is biased toward the distal end side (bevel gear portion 14 b side) by a coil spring 23.
- a pin 24 that protrudes toward the distal end side is integrally formed at the center of the distal end surface of the output gear 21.
- the tip of the pin 24 is formed in a hemispherical shape.
- reference numeral 30 denotes a disk-shaped dial (operation member).
- the dial 30 has a rotation shaft 31 extending coaxially with the motor shaft 11 at the center, and the rotation shaft 31 is rotatably supported by the frame 4.
- a cam (selector member) 41 is fixed to the end of the rotating shaft 31.
- the cam 41 has a disc shape, and a substantially trapezoidal concave portion 42 is formed on the outer peripheral portion thereof.
- the pin 24 of any one of the output gears 21 is protruded toward the distal end side by the coil spring 23 and fits into the recess 42, and the output gear 21 meshes with the bevel gear portion 14 b of the second input gear 14. Yes. Thereby, the rotation of the motor 10 is transmitted from the first and second input gears 12 and 14 to the output shaft 22 via the output gear 21.
- the pins 24 of the other two output gears 21 are in contact with the outer peripheral surface of the cam 41, and the output gear 21 is separated from the bevel gear portion 14b of the second input gear 14. 1 to 3, the pin 24 of the output gear 21 at a position forming the apex angle of an isosceles triangle is fitted in the recess 42.
- a predetermined angle ⁇ (this implementation)
- the center of the other two concave portions 42 is located at an inclined position (45 ° in the form).
- the cam 41 is rotated by rotating the dial 30, and when the pin 24 fits into the recess 42, a feeling of clicking during operation can be obtained, and the dial 30 is reliably positioned at the connection position of the output gear 21. Can be done.
- a rectangular parallelepiped switch 50 for selecting ON / OFF of the motor 10 and the rotation direction of the motor 10 is attached to the surface of the dial 30.
- the switch 50 is regulated so as to slide to both sides in the longitudinal direction (CD direction in FIG. 3) and to stop at an intermediate point of the sliding range by a biasing member (not shown).
- the switch 50 extends through the center point of the dial 30, and one end thereof is in a state of protruding outward from the dial 30.
- the protruding end is configured as an instruction unit 51.
- the switch 50 has the indicator 51 with respect to the center line of the pin 24. It is attached to the dial 30 so as to be inclined 45 ° counterclockwise.
- the motor 10 is turned off at the neutral point in the stopped state where it does not move in the longitudinal direction. Then, for example, the motor 10 is operated such that when the motor 10 is slid in the C direction, the motor 10 is rotated forward, and when the motor 10 is slid in the D direction, the motor 10 is reversed.
- the multi-axis drive device is arranged on the side surface of the seat cushion where the occupant seated on the seat cushion can operate the dial 30, the motor shaft 11 extends in the left-right direction of the vehicle body, and
- the second input gear 14 at the position forming the apex angle of the isosceles triangle of the two input gears 14 is positioned in the traveling direction of the vehicle, and the other second input gears 14 are mounted so as to be lined up and down at the rear.
- the front one is the front second input gear 14A
- the lower one is the lower second input gear 14B
- the upper one is the upper second input gear 14C.
- the output gear 21 the front one is the front output gear 21A
- the lower one is the lower output gear 21B
- the upper one is the upper output gear 21C.
- a torque cable (not shown) is connected to the output shaft 22 of each output gear 21A to 21C.
- the torque cable transmits the rotation of each output shaft 22 to a reclining mechanism that adjusts the angle of the seat back portion, a seat front-rear position adjustment mechanism, and a seat seat surface height adjustment mechanism to operate these mechanisms. is there.
- the output shaft 22 of the front output gear 21A is used as a reclining mechanism
- the output shaft 22 of the lower output gear 21B is used as a seat seat surface height adjusting mechanism
- the output shaft 22 of the upper output gear 21C is connected via a torque cable.
- Each is connected to a seat front-rear position adjustment mechanism.
- the motor 10 rotates so that when the switch 50 is slid forward (C direction), the back of the seat tilts forward, and when the switch 50 is slid rearward (D direction), the back is tilted backward. To do.
- the backrest can be adjusted to a desired angle.
- the mechanism for branching the power of the motor 10 to the plurality of output shafts 22 is configured so that the second input gear 14 has an output integrated with each output shaft 22.
- the gear 21 is engaged.
- the output shaft 22 is selected by rotating the dial 30 and moving the output gear 21 to be connected to the second input gear 14 side.
- the mechanism for branching the power of the motor 10 to the plurality of output gears 21 and the selection of the output gear 21 to be operated are achieved with a compact configuration in which the output gear 21 is arranged around the cam 41, the weight can be reduced. Space can be saved.
- the output gear 21 meshes with the second input gear 14 by one operation of rotating the cam 41, and a click feeling is obtained when the pin 24 of the output gear 21 is fitted in the recess 42. Therefore, it is excellent in operability and operation feeling.
- the position of the output gear 21 can be arbitrarily set along the periphery of the second input gear 14, and the position of the second input gear 14 and the output gear 21 can be arbitrarily set along the periphery of the first input gear 12. Can be set. Thereby, the position and angle of the output shaft 22 can be appropriately changed according to the position of the member to which the output shaft 22 is connected.
- the position and operation direction of the switch 50 in the state of being attached to the seat are adjustable mechanisms (reclining mechanism, seat front / rear position adjusting mechanism, seat seat surface height adjusting mechanism). Since it matches the direction of movement, the operational feeling matches the actual movement, making it easy to use.
- FIGS. 5 and 6 show a second embodiment of the present invention.
- the rotating shaft of the motor 10 is installed in a state orthogonal to the rotating shaft of the first input gear 12 in the configuration of the first embodiment.
- a third input gear 11a constituting a bevel gear is fixed to the tip of the motor shaft 11 of the motor 10 as shown in FIG.
- an input shaft 16 is fixed to the center of the first input gear 12, and a fourth input gear 16a constituting a bevel gear meshing with the third input gear 11a is fixed to the tip of the input shaft 16.
- FIGS. 7 and 8 show a third embodiment of the present invention.
- the rotation operation of the dial 30 (referred to as the first dial 30 in this embodiment) is performed by another dial (second dial) 35 to output gears. 21 is configured to switch connections.
- the first dial 30 is rotatably supported on one side (the right side in FIG. 7) of the frame 70 via a rotating shaft 30a. Then, as shown in FIG. 8, the second dial 35 is rotatable on the other surface side (left side in FIG. 6) of the frame 70 via the rotation shaft 35a at a position that is not coaxial with the periphery of the first dial 30. It is supported.
- the second dial 35 is provided with a switch 50A similar to the switch 50 described above.
- the frame 70 is a frame such as a seat frame when the present apparatus is applied to a movable vehicle seat as in the first embodiment.
- the rotation shaft 35 a of the second dial 35 penetrates the frame 70 and protrudes to one side, and the rotation shaft 35 a of the second dial 35 and the rotation shaft 30 a of the first dial 30. Further, a transmission belt (transmission member) 80 is wound around. When the second dial 35 is rotated, the rotation is transmitted to the first dial 30 via the transmission belt 80, whereby the first dial 30 is rotated and the connection of the output gear 21 is switched.
- the second dial 35 is disposed at an arbitrary position away from the first dial 30 and the dials 30 and 35 are connected by the transmission belt 80 to be driven by the cam 41.
- the selection of the output shaft 25 can be performed at a position not restricted by the positions where the cam 41 and the dial 30 are disposed. Therefore, the degree of freedom in design increases.
- a gear train in which one gear or a plurality of gears are engaged may be employed.
- FIG. 9 is a diagram showing a fourth embodiment of the present invention.
- three bearing blocks 60 are supported on the main frame 5 supporting the motor 10 so as to be slidable in a direction approaching and separating from the first input gear 12.
- a spring seat 5 a is provided on the outer peripheral portion of the main frame 5, and a coil spring 23 is interposed between the spring seat 5 a and the bearing block 60.
- the bearing block 60 is biased toward the rotation center of the first input gear 12 by the coil spring 23.
- the output shaft 62 of the output gear (output member) 61 is rotatably supported by the bearing block 60.
- the output gear 61 is a spur gear that can mesh with the first input gear 12.
- a pin 64 is integrally formed at the center of one end surface of the output gear 61 so as to protrude toward one end side.
- a cam 41, a dial 30, a switch 50, and the like equivalent to those in the first embodiment are provided.
- the cam 41 is formed with three recesses 42 at substantially the same position as in the first embodiment.
- the bearing block 60 is arranged so as to form an isosceles triangle.
- each time the dial 30 is rotated 45 ° the pin 64 of the output gear 61 is fitted in the recess 42, and the output The gear 61 meshes with the first input gear 12. That is, when the dial 30 is rotated from the state shown in FIG. 9, the pin 64 fitted in the recess 42 rides on the outer peripheral surface of the cam 41, and the output gear 61 is separated from the first input gear 12.
- the same operation and effect as in the above embodiment can be obtained.
- the output gear 61 is directly meshed with the first input gear 12, the number of gears is greatly reduced and the configuration is simplified.
- FIGS. 10 and 11 are views showing a fifth embodiment of the present invention.
- reference numeral 71 denotes an output gear.
- the output gear 71 includes an output shaft 72 and a pin 74 equivalent to the output gear 21 shown in FIG. 1, but the direction of the bevel gear of the output gear 71 is opposite to that shown in FIG. 1, and It is arranged inside the second output gear 14.
- reference numeral 81 denotes a cam.
- three convex portions 82 having a cylindrical curved surface are formed at locations separated by 120 ° in the circumferential direction.
- the same operation and effect as in the above embodiment can be obtained.
- the output gear 71 since the output gear 71 is moved to the second input gear 14 side by the convex portion 82 of the cam 81, the output gear 71 is connected to the second input even if the coil spring 23 sags.
- the bevel gear portion 14b of the gear 14 can be reliably meshed.
- the present invention is not limited to the above-described embodiments.
- the friction surfaces are not connected. It is possible to adopt a configuration by joining.
- the operation member is not limited to the dials 30 and 35, and may be of a type in which one end portion such as a lever is rotated.
- the position and angle of the output gear 21 that is actuated by the rotation of the dial 30 can be arbitrarily set.
- the number of output shafts is also arbitrary.
- the seat seat surface height adjustment is divided into two parts at the front and rear of the seat cushion, and this is also applied to a structure having a total of four output shafts. Is possible.
- the output gear 21 is meshed with the second input gear 14.
- the first input gear 12 may be configured as a bevel gear and meshed with the first input gear 12. it can.
- the selector member (the cam 41) according to the present invention is rotated by the operation member (the dial 30), but the selector member may be linearly moved by the operation member.
- the present invention includes.
- a sixth embodiment as the embodiment will be described.
- FIGS. 12 to 16 show a multi-axis drive device according to a sixth embodiment.
- reference numeral 110 denotes a cam member (selector member).
- This cam member 110 is a rectangular plate-like member that is long in the horizontal Y direction, and is supported by a guide support member (not shown) so as to be movable in the longitudinal direction (Y direction, the front and back direction in the drawing in FIG. 13).
- Both side surfaces along the longitudinal direction of the cam member 110 are cam surfaces 111, and a plurality of recesses 112 that are open in the thickness direction are formed at predetermined positions of the cam surfaces 111.
- Both sides of the concave portion 112 of the cam surface 111 are convex portions 113 along the Y direction. A transition part from the concave part 112 to the convex part 113 is formed on a slope.
- a rectangular hole 114 extending in the Y direction is formed in the central portion of the cam member 110, and a rack portion 115 in which teeth are arranged in the Y direction is formed on one inner surface of the hole 114 extending in the Y direction.
- the rack portion 115 is engaged with a pinion gear 122 formed on the operation shaft 121 (rack and pinion mechanism).
- the operation shaft 121 extends upward, and a disc-shaped dial (operation member) 120 is coaxially fixed to the tip thereof.
- the dial 120 When the dial 120 is rotated, the pinion gear 122 rotates integrally, and is driven by the pinion gear 122 to move the rack portion 115 in the Y direction, whereby the cam member 110 moves linearly in the Y direction.
- a plurality of output shafts (output members) 130 extending in the X direction are arranged along the Y direction with their tips opposed to the cam surface 111.
- These output shafts 130 are supported by a guide support member (not shown) so as to be able to advance and retreat with respect to the cam surface 111 along the axial direction (X direction).
- a bevel gear 132 having a tooth surface facing the cam member 110 is formed integrally and coaxially in the middle of the shaft portion 131, and the output shaft 130 of the shaft portion 131 facing the cam surface 111 is formed.
- the tip (convex portion) is formed in a curved surface shape.
- the output shaft 130 is urged so as to advance toward the cam surface 111 by a compression spring 133 that is externally mounted on the shaft portion 131 and engages with the bevel gear 132.
- a compression spring 133 that is externally mounted on the shaft portion 131 and engages with the bevel gear 132.
- a motor 140 is disposed in a state where a motor shaft (motor rotation shaft) 141 extends upward.
- a clutch shaft 143 extending in the vertical direction is connected to the motor shaft 141 via a power transmission member 142.
- the power transmission member 142 is not limited as long as it transmits the rotation of the motor shaft 141 to the clutch shaft 143, and examples thereof include a gear train and a belt.
- the clutch shaft 143 is disposed for each output shaft 130, and a bevel gear 144 is integrally formed at the upper end thereof.
- the power of the motor 140 is transmitted to each clutch shaft 143 via the power transmission member 142, and each clutch shaft 143 is rotated when the motor 140 is operated.
- the clutch shaft 143 constitutes an input member according to the present invention, and the clutch shaft 143 having the bevel gear 144 and the bevel gear 132 of the output shaft 130 constitute the clutch mechanism 150 of the present embodiment.
- the operation of the motor 140 is turned on and off by a switch 123 provided on the dial 120.
- this clutch mechanism 150 when the output shaft 130 enters the recess 112 of the cam member 110, the bevel gear 132 is engaged with the bevel gear 44 on the clutch shaft 143 side (the left side in FIG. 13), and the motor The power of 140 is transmitted to the output shaft 130 through the power transmission member 42, the clutch shaft 143, and the clutch mechanism 150, and the output shaft 130 rotates.
- the output shaft 130 rides on the convex portion 113 of the cam member 110, the bevel gear 132 on the output shaft 130 side is detached from the bevel gear 42 on the clutch shaft 143 side, and the clutch shaft 143 is idled.
- the output shaft 130 is in a disconnected state where it does not rotate (the state on the right side of FIG. 13).
- the output shaft 130 enters the recess 112 of the cam surface 111 by rotating the dial 120 and sending the cam member 110 in the Y direction.
- the clutch mechanism 150 is connected, and the output shaft 130 rotates. Therefore, the output shaft 130 is selectively driven according to the feed direction and the feed length of the cam member 110 in the Y direction by the rotation operation of the dial 120.
- the output shaft 130 to be driven can be arbitrarily set according to the formation position of the recess 112 and the position of the output shaft 130. In addition, by arbitrarily setting the formation position of the recess 112 and the position of the output shaft 130, the number of output shafts 130 to be driven can be set to one or a plurality.
- the tip of the output shaft 130 is always in contact with the cam surface 111 by being biased by the compression spring 133, and the recess 112 and the protrusion 113 can be slid alternately. Since the transition portion from the concave portion 112 to the convex portion 113 is formed on the inclined surface, the output shaft 130 smoothly slides on the cam surface 111.
- the rack portion 115 can be provided at an arbitrary position as long as the cam member 110 can be moved in the Y direction.
- the rack portion 115 is formed on the inner surface of the hole 114 formed in the center of the cam member 110, but this is an example of the position where the rack portion 115 is formed.
- a protruding portion 116 is integrally provided at one end portion in the longitudinal direction of the cam member 110, a hole 114 is formed in the protruding portion 116, and a similar rack portion 115 is formed on the inner surface thereof.
- the pinion gear 122 of the operation shaft 121 of the dial 120 is engaged with the rack portion 115. According to this, the position of the dial 120 can be relatively separated from the output shaft 130.
- the output shaft 130 can also be arranged at an arbitrary position with respect to the cam surface 111 of the cam member 110. For these reasons, the degree of freedom of arrangement of the dial 120 including the operation shaft 121 and the output shaft 130 is greatly improved.
- the rack portion 115 does not need to be directly formed on the cam member 110, and can be indirectly provided via a transmission member such as a rod. When the rack portion 115 is indirectly provided, the tooth row of the rack portion 115 does not have to be parallel to the moving direction of the cam member 110, and may be in any direction if possible.
- a large number of output shafts 130 can be arranged along the cam surface 111 within a range where they do not interfere with each other, and more output shafts 130 can be arranged if the cam surface 111 is lengthened if necessary.
- the cam member 110 is provided with a plurality of steps in the vertical direction by increasing the thickness of the cam member 110 or by overlapping a plurality of cam members 110, and the output shaft 130 is arranged in correspondence with the cam surface 111.
- a typical arrangement pattern is also possible.
- 15 and 16 are specific examples of such a multi-stage structure, and show a modification of the embodiment shown in FIG.
- two-stage cam surfaces 111 are formed on both side surfaces of the cam member 110 in the thickness direction. That is, the cam surface 111 is formed in two stages in a direction orthogonal to the Y direction in which the cam surface 111 extends.
- the concave portions 112 are formed at predetermined positions on the upper and lower cam surfaces 111, and output shafts 130 associated with the clutch mechanism 150 are arranged corresponding to the concave portions 112. According to such a form, there exists an advantage that many output shafts 130 can be integrated, without the whole becoming long.
- the output shaft 130 is arranged with the axial direction parallel to the X direction in FIG. 12, but as shown by the broken line in FIG. It is also possible to arrange it so as to be inclined. This is advantageous in that when the direction in which the preferred output shaft 130 extends is not parallel to the X direction, the arrangement angle of the output shaft 130 can be adjusted according to the preferred direction.
- stopper means for restricting the movement range of the cam member 110 because the output shaft 130 can be prevented from coming off from the cam surface 111.
- the stopper means may be of any form, for example, a member that contacts the end of the cam member 110 in the moving direction, or a member that restricts the rotation of the dial 120.
- the clutch mechanism 150 is connected when the output shaft 130 enters the recess 112, and the clutch mechanism 150 is disconnected when the output shaft 130 rides on the protrusion 113. That is, the clutch mechanism 150 is disconnected when the output shaft 130 enters the recess 112, and the clutch mechanism 150 is connected when the output shaft 130 rides on the projection 113.
- the multi-axis drive device of the above-described embodiment is suitable as a device for operating the vehicle electric seat with the motor 140. That is, for each movable shaft such as a mechanism for adjusting the height of the seat seat surface, a reclining mechanism for adjusting the angle of the seat back portion, and a mechanism for adjusting the front-rear position of the seat of the electric seat for a vehicle. Can be connected via a torque cable or the like, and the power of the motor 140 can be selectively branched to each movable mechanism to operate these movable mechanisms.
- the multi-axis drive device of the present invention can be applied not only to an electric seat but also to a mechanical device in which a plurality of movable mechanisms are selectively driven.
- rotation of an input gear (input member) 202 which is a spur gear fixed to a motor shaft (rotary shaft) 201 that rotates when the motor 200 operates, causes a plurality of output shafts (output members) 210 to rotate.
- a configuration in which the output shaft 210 that is transmitted through the clutch mechanism 220 provided for each output shaft 210 and is rotated by the cam members (selector members) 230, 240, 250, 260, 270, 280 is selected in common, And it has a basic structure.
- the output shaft 210 has the same configuration as that of the output shaft 130 of the sixth embodiment, and a bevel gear 212 having a tooth surface facing the distal end side is integrally formed in the middle of the shaft portion 211 having a curved distal end. And it is formed coaxially.
- the output shaft 210 has its tip directed to the cam members 230, 240, 250, 260, 270, 280, and the direction of the cam members 230, 240, 250, 260, 270, 280 is driven by a compression spring 213 that engages the bevel gear 212 It is urged to advance to abut.
- the clutch mechanism 220 is arranged around the input gear 202, and bevel gears 221 that rotate integrally with a spur gear 203 that is provided so as to mesh with the input gear 202 and rotate, and an output that can mesh with the bevel gear 221. It is constituted by the bevel gear 212 of the shaft 210.
- the cam members 230, 240, 250, 260, 270, and 280 have their respective characteristics, and will be described below for each embodiment.
- FIGS. 17 to 19 The cam member 230 of the seventh embodiment is formed in a rectangular parallelepiped shape, and is supported by a guide member (not shown) so as to be movable up and down while maintaining the posture in which the longitudinal direction is horizontal in FIG.
- a dial shaft 231 having a screw formed on the outer peripheral surface is threaded into one end of the cam member 230 from above.
- a disc-shaped dial (not shown) is concentrically fixed to the upper end of the dial shaft 231. By rotating the dial, the cam member 230 moves upward or downward according to the rotation direction. Yes. That is, the dial shaft 231 and the cam member 230 constitute a ball screw mechanism.
- a recess 233 is formed on both side surfaces 232a and 232b of the cam member 230 via slopes.
- the number and location of the recesses 233 are arbitrary.
- one side 232a is formed at the upper end and the lower end at two positions spaced apart in the longitudinal direction, and the other side 232b is intermediate in the vertical direction. Thus, it is formed at a position where it hits between the two recesses 233 on the side surface 232a side.
- the output shaft 210 is disposed on both sides of the cam member 230, and the cam member 230 is positioned at a position where the tip of the cam member 230 abuts the side surfaces 232 a and 232 b of the cam member 230 at right angles and can be fitted into the recesses 233. On the other hand, it is supported to move forward and backward.
- the tip of the output shaft 210 is in contact with the side surfaces 232a and 232b, the output shaft 210 is retracted against the force of the compression spring 213.
- the bevel gear 212 is separated from the bevel gear 221 and the clutch mechanism 220 is disconnected.
- the clutch mechanism 220 is disconnected, the power of the motor 200 is transmitted only to the bevel gear 221.
- FIGS. 20 to 23 The cam member 240 of the eighth embodiment is formed in a cylindrical shape, and is rotatably supported by a bearing member (not shown) with the axial direction horizontal in FIGS. 20 and 21.
- a dial shaft 241 extending upward is connected to one end of the cam member 240 via bevel gears 242a and 242b meshing with each other.
- a disc-shaped dial (not shown) is concentrically fixed to the upper end of the dial shaft 241. When this dial is rotated, the cam member 240 is rotated in either the forward or reverse direction according to the rotation direction of the dial via the bevel gears 242a and 242b.
- a plurality of recesses 243 are formed on the peripheral surface 240a of the cam member 240 so as to be dispersed in the axial direction.
- the number of the concave portions 243 and the formation position in the circumferential direction are arbitrary, and in this case, as shown in FIG. 23, the concave portions 243 are formed at positions that equally divide the circumferential direction.
- the recessed part 243 is formed through the slope so that the front-end
- the output shaft 210 is arranged on both sides of the cam member 240 in a state along the radial direction of the cam member 240, the tip of the shaft portion 211 abuts on the circumferential surface 240 a of the cam member 240 orthogonally, and the tip is a concave portion.
- the cam member 240 is supported so as to be able to advance and retract at a position where it can be fitted to the H.243.
- the output shaft 210 is in a retracted state against the force of the compression spring 213 when the tip of the shaft portion 211 is in contact with the peripheral surface 240a of the cam member 240. At this time, the clutch mechanism 220 is in a disconnected state.
- the tip of the shaft portion 211 of the output shaft 210 is fitted into the recess 243, and the output shaft 210 advances toward the cam member 240.
- the output shaft 210 in which the tip of the shaft portion 211 is fitted in the recess 243 rotates when the power of the motor 200 is transmitted to the clutch mechanism 220 in a connected state.
- FIGS. 24 to 26 In the ninth embodiment, the spur gear 203 is directly meshed with the motor shaft 201, and the spur gear 203 constitutes the input member. This configuration is the same in the following tenth to twelfth embodiments.
- the cam member 250 of the ninth embodiment has a configuration in which two discs 252 having the same outer diameter are integrally and concentrically stacked, and is attached to a dial shaft 251 provided at the center of the upper disc 252. A dial (not shown) is fixed concentrically.
- a recess 253 is formed at an arbitrary position on the outer peripheral surface 252 a of each disk 252.
- the number of the concave portions 253 and the formation position in the circumferential direction are arbitrary. In this case, one concave portion 253 is formed in the upper disc 252 and two concave portions 253 are formed in the lower disc 252. Yes.
- the output shaft 210 is disposed to face each disk 252 of the cam member 250.
- one (indicated by 210A) is provided for the upper disk 252 and two (indicated by 210B) for the lower disk 252.
- Each output shaft 210 is supported so as to be movable forward and backward with respect to the cam member 250 at a position where the tip of the shaft portion 211 abuts against the outer peripheral surface 252a of each disk 252.
- the output shaft 210 is in a state of retreating against the force of the compression spring 213 when the tip of the shaft portion 211 is in contact with the outer peripheral surface 252a of each disk 252.
- the clutch mechanism 220 is in a disconnected state.
- the tip of the shaft portion 211 of the output shaft 210 is fitted into the concave portion 253 of each disk 252, and the output shaft 210 advances to the cam member 250 side.
- the output shaft 210 in which the tip of the shaft portion 211 is fitted in the recess 253 rotates when the clutch mechanism 220 is in a connected state and the power of the motor 200 is transmitted. If the surface on which the recesses 253 are formed is provided in a plurality of stages as in this embodiment, a large number of output shafts 210 can be arranged according to the number of stages, and more output shafts 210 can be incorporated. There is an advantage of becoming.
- FIGS. 27 to 28 The cam member 260 of the tenth embodiment is formed in a fan shape.
- the cam member 260 is integrally fixed to a dial shaft 261 of a dial (not shown) via a fan-shaped connecting plate 262, and is rotated about the dial shaft 261 as a fulcrum by rotating the dial.
- the cam member 260 has an outer peripheral surface 260a and an inner peripheral surface 260b, and a concave portion 263 is formed in the outer peripheral surface 260a and the inner peripheral surface 260b.
- the number of the recesses 263 and the formation position in the circumferential direction are arbitrary, and in this case, one is formed at approximately the middle position in the circumferential direction.
- the output shaft 210 is disposed to face the outer peripheral surface 260a and the inner peripheral surface 260b of the cam member 260. Here, two are disposed on the outer peripheral surface 260a side, and one is disposed on the inner peripheral surface 260b side.
- Each output shaft 210 is supported so as to be movable forward and backward with respect to the cam member 206 at a position where the tip of the shaft portion 211 abuts against the outer peripheral surface 260a and the inner peripheral surface 260b.
- the output shaft 210 retreats against the force of the compression spring 213, and at this time, the clutch mechanism 220 is in a disconnected state.
- the tip of the shaft portion 211 of the output shaft 210 is fitted into the recess 263, and the output shaft 210 advances toward the cam member 263.
- the output shaft 210 in which the tip of the shaft portion 211 is fitted in the concave portion 262 rotates when the power of the motor 200 is transmitted to the clutch mechanism 220 in a connected state.
- the operation of the output shaft 210 can be switched, and there is an advantage that the degree of freedom in layout is improved.
- FIGS. 29 to 30 The cam member 270 of the eleventh embodiment is disk-shaped, and a plurality of recesses 273 are formed at arbitrary positions on the outer peripheral surface 270a.
- a dial shaft 271 to which a dial (not shown) is fixed is offset from the rotation center of the cam member 270, and the cam member 270 and the dial shaft 271 are connected by a pair of spur gears 272a and 272b that mesh with each other to rotate the dial. Then, the cam member 270 rotates through the gears 272a and 272b.
- the output shaft 210 is disposed opposite to the outer peripheral surface 270a of the cam member 270 as in the ninth embodiment, and is compressed when the tip of the shaft portion 211 is in contact with the outer peripheral surface 270a of the cam member 270.
- the clutch mechanism 220 is in a disconnected state at this time.
- the tip of the shaft portion 211 of the output shaft 210 is fitted into the recess 273 of the cam member 270, and the output shaft 210 advances toward the cam member 270.
- the output shaft 210 in which the tip of the shaft portion 211 is fitted in the concave portion 273 rotates when the clutch mechanism 220 is connected and the power of the motor 200 is transmitted.
- the operation of the output shaft 210 can be switched even when the dial cannot be arranged between the output shafts 210, and the degree of freedom in layout is improved. There are advantages. Further, by changing the gear ratio of the spur gears 272a and 272b, the operation angle of the dial for connecting / disconnecting the clutch mechanism 220 can be adjusted.
- the cam member 280 of the twelfth embodiment is a disc-shaped member having a plurality of recesses 283 formed on the outer peripheral surface 280a, and a dial (not shown) is concentrically fixed via a dial shaft 281 provided at the center. ing.
- the plurality of output shafts 210 arranged around the cam member 280 do not directly contact the outer peripheral surface 280a of the cam member 280 but are rotated by the output shaft 210 pushed by the compression spring 213.
- the distal end of 285 is in contact with the outer peripheral surface 280 a and is configured to fit into the recess 183.
- the force when the cam member 280 ejects the link 285 from the recess 283 is increased by the lever principle. Even if the force is strong, it can be operated reliably. Further, by devising the arrangement and shape of the link 285, the output shaft 210 can be moved greatly by the lever ratio of the link 285 even when the cam member 280 is small and the depth of the recess 283 cannot be ensured. For this reason, the cam member 280 can be provided with a large number of recesses 283 so that a large number of output shafts 210 can be arranged, or any arrangement can be accommodated, and the degree of freedom in layout is improved.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Aviation & Aerospace Engineering (AREA)
- Transportation (AREA)
- Gear Transmission (AREA)
- Seats For Vehicles (AREA)
- Transmission Devices (AREA)
Abstract
Description
上記出力部材を上記入力部材側へ付勢する付勢手段を備え、上記セレクタ部材は、円筒曲面をなし出力部材と接触することで該出力部材を入力部材から離間させる外周部と、この外周部に設けられ出力部材が嵌ることで該出力部材を入力部材側へ移動させる凹部とを備えることができる。このような態様では、セレクタ部材を回転させて凹部を出力部材に対向させると、付勢手段の付勢力により出力部材が移動して入力部材と係合する。このように、セレクタ部材を回転させるという1つの動作で出力部材が入力部材と係合するとともに、出力部材が凹部に嵌るときにクリック感が得られるので、操作性および操作感覚に優れている。
11,141,201…モータ軸(モータの回転軸)
12…第1入力ギヤ(平歯車)
14…第2入力ギヤ(入力部材)
14a…平歯車部(第1歯車部)
14b…傘歯車部(第2歯車部)
21…出力ギヤ(出力部材)
22,25,62,72…出力軸
23,133…コイルバネ(付勢手段)
24…ピン(凸部)
30,120…ダイヤル(操作部材)
41…カム(セレクタ部材)
42,112,233,243,253,263,273,283…凹部(作用部)
50…スイッチ
61…出力ギヤ(出力部材)
110,230,240,250,260,270,280…カム部材(セレクタ部材)
111…カム面(作用部)
130…出力軸(出力部材)
133,213…圧縮ばね(付勢部材)
143…クラッチ軸(入力部材)
202…入力ギヤ(入力部材)
210…出力軸(出力部材)
[1]第1実施形態:図1~図11
(1)第1実施形態の構成
図1~図4は、第1実施形態に係る多軸駆動装置を示している。この多軸駆動装置は、例えば車両用電動シートの、シート座面の高さを調節する機構、シート背もたれ部の角度を調節するリクライニング機構、およびシートの前後位置を調節する機構の3つの可動機構に対し、正逆回転する1つのモータ10の動力を選択的に分岐させてこれら可動機構を作動させるものとして好適である。
以上が第1実施形態の多軸駆動装置の構成であり、続いて、図4を参照して多軸駆動装置を車両用電動シートに適用した例を説明する。
前後位置調節機構を作動させてシートの前後位置を調節するには、ダイヤル30を回転させて図4(a)に示すようにスイッチ50の指示部51を前方に向ける。すると、カム41の凹部42が上側第2入力ギヤ14Cに臨む位置まで移動し、凹部42に上側出力ギヤ21Cのピン24が嵌って上側第2入力ギヤ14Cに上側出力ギヤ21Cが噛み合う。一方、前側および下側出力ギヤ21A,21Bにおいては、ピン24がカム41の外周面と接触することにより、前側および下側第2入力ギヤ14A,14Bと離間している。
リクライニング機構でシートの背もたれ角度を調節するには、ダイヤル30を回転させて図4(b)に示すようにスイッチ50の指示部51を前方、かつ斜め下方45°に向ける。すると、カム41の凹部42が前側第2入力ギヤ14Aに臨む位置まで移動し、凹部42に前側出力ギヤ21Aのピン24が嵌って前側第2入力ギヤ14Aに前側出力ギヤ21Aが噛み合う。一方、下側および上側出力ギヤ21B,21Cにおいては、ピン24がカム41の外周面と接触することにより、下側および上側第2入力ギヤ14B,14Cと離間している。
座面高さ機構を作動させてシート座面の高さを調節するには、ダイヤル30を回転させて図4(c)に示すようにスイッチ50の指示部51を下方に向ける。すると、カム41の凹部42が下側第2入力ギヤ14Bに臨む位置まで移動し、凹部42に下側出力ギヤ21Bのピン24が嵌って下側第2入力ギヤ14Bに下側出力ギヤ21Bが噛み合う。一方、前側および上側出力ギヤ21A,21Cにおいては、ピン24がカム41の外周面と接触することにより、前側および上側第2入力ギヤ14A,14Cと離間している。
上記第1実施形態の多軸駆動装置によれば、モータ10の動力を複数の出力軸22に分岐させる機構は、第2入力ギヤ14に、各出力軸22と一体の出力ギヤ21を噛み合わせる構成である。また、出力軸22の選択は、ダイヤル30を回転させて、接続させたい出力ギヤ21を第2入力ギヤ14側へ移動させることによりなされる。
図5および図6は、本発明の第2実施形態を示している。この第2実施形態は、上記第1実施形態の構成において、モータ10の回転軸が第1入力ギヤ12の回転軸に直交する状態に設置されている。
図7および図8は、本発明の第3実施形態を示している。この第3実施形態は、上記第1実施形態の構成において、ダイヤル30(この実施形態では第1のダイヤル30と称する)の回転操作を別のダイヤル(第2のダイヤル)35で行って出力ギヤ21の接続の切り替えを行う構成となっている。
図9は本発明の第4実施形態を示す図である。図9に示すように、モータ10を支持するメインフレーム5には、3個の軸受ブロック60が第1入力ギヤ12に対して接近離間する方向へ摺動自在に支持されている。メインフレーム5の外周部には、バネ座5aが設けられ、バネ座5aと軸受ブロック60との間には、コイルバネ23が介装されている。このコイルバネ23によって、軸受ブロック60は第1入力ギヤ12の回転中心に向けて付勢されている。
図10および図11は本発明の第5実施形態を示す図である。図10において符号71は出力ギヤである。出力ギヤ71は、図1に示す出力ギヤ21と同等の出力軸72およびピン74を備えたものであるが、出力ギヤ71の傘歯車の向きが図1に示すものと逆とされ、かつ、第2出力ギヤ14の内側に配置されている。
本発明は前記各実施形態には限定されず、例えば、第2入力ギヤ14と出力ギヤ21のように歯が噛み合う構成の代わりに、摩擦面どうしの接合による構成などを採用することができる。また、操作部材としてはダイヤル30、35に限られず、レバー等、一端部を回動操作する形式のものであってもよい。
(1)第6実施形態の構成
図12および図13は、第6実施形態に係る多軸駆動装置を示している。これら図で符号110はカム部材(セレクタ部材)である。このカム部材110は水平なY方向に長い長方形状のプレート状部材であって、図示せぬガイド支持部材により長手方向(Y方向、図13では図面の表裏方向)に移動自在に支持されている。カム部材110の長手方向に沿った両側面はカム面111とされ、これらカム面111の所定箇所には、厚さ方向に開放する複数の凹部112が形成されている。そしてカム面111の凹部112の両側はY方向に沿った凸部113とされている。凹部112から凸部113に至る移行部は斜面に形成されている。
上記多軸駆動装置によれば、ダイヤル120を回転操作させてカム部材110をY方向に送ることにより、出力軸130がカム面111の凹部112に進入してクラッチ機構150が接続状態となり、その出力軸130が回転する。したがってダイヤル120の回転操作によるカム部材110のY方向への送り方向、および送り長さに応じて出力軸130は選択的に駆動される。駆動させる出力軸130は、凹部112の形成位置や出力軸130の位置に応じて任意に設定することができる。また、凹部112の形成位置や出力軸130の位置を任意に設定することにより、駆動させる出力軸130の数を1つ、または複数に設定することができる。
第7実施形態のカム部材230は直方体状に形成されたもので、図示せぬガイド部材により図17において長手方向を水平とした姿勢のまま上下動可能に支持されている。カム部材230の一端部には、外周面にねじが形成されたダイヤル軸231が上方から貫通して螺合されている。ダイヤル軸231の上端には円板状の図示せぬダイヤルが同心状に固定され、該ダイヤルを回転させることにより、その回転方向に応じてカム部材230が上方または下方に移動するようになっている。すなわち、ダイヤル軸231とカム部材230によりボールねじ機構が構成されている。
第8実施形態のカム部材240は円筒状に形成されたもので、図示せぬ軸受け部材により図20および図21において軸方向を水平として回転可能に支持されている。カム部材240の一端部には、互いに噛み合う傘歯車242a,242bを介して、上方に延びるダイヤル軸241が接続されている。ダイヤル軸241の上端には、円板状の図示せぬダイヤルが同心状に固定されている。このダイヤルを回転させると、傘歯車242a,242bを介してカム部材240がダイヤルの回転方向に応じて正逆いずれかの方向に回転するようになっている。
第9実施形態では、モータ軸201に平歯車203が直接噛み合わされており、平歯車203が入力部材を構成している。なお、この構成は、以下の第10~第12実施形態も同様とされている。
第10実施形態のカム部材260は、扇状に形成されたものである。このカム部材260は、図示せぬダイヤルのダイヤル軸261に、扇状の連結板262を介して一体的に固定されており、ダイヤルを回転させることによりダイヤル軸261を支点として回転させられる。カム部材260は、外周面260aおよび内周面260bを有しており、これら外周面260aおよび内周面260bには凹部263が形成されている。凹部263の数および周方向の形成位置は任意であり、この場合は、周方向のほぼ中間位置にそれぞれ1つずつ形成されている。
第11実施形態のカム部材270は円板状で、外周面270aの任意の位置に複数の凹部273が形成されている。図示せぬダイヤルが固定されるダイヤル軸271はカム部材270の回転中心とはオフセットされており、カム部材270とダイヤル軸271とは互いに噛み合う一対の平歯車272a,272bで接続され、ダイヤルを回転させるとギヤ272a,272bを介してカム部材270が回転するようになっている。
第12実施形態のカム部材280は、外周面280aに複数の凹部283が形成された円板状のもので、中心に設けられたダイヤル軸281を介して図示せぬダイヤルが同心状に固定されている。この実施形態ではカム部材280の周囲に配された複数の出力軸210は先端がカム部材280の外周面280aに直接当接するのではなく、圧縮ばね213で押される出力軸210によって旋回させられるリンク285の先端が外周面280aに当接し、また、凹部183に嵌合するように構成されている。
Claims (21)
- モータの回転軸に接続された入力部材と、
出力軸を有し、前記入力部材に対して係脱自在に設けられ、係合したときに該入力部材の回転が伝達される複数の出力部材と、
複数の前記出力部材の間に配設され、かつ作用部を有し、作動させられることにより前記出力部材のいずれかに該作用部が対向して作用することにより該出力部材を前記入力部材側へ移動させて該出力部材を該入力部材に選択的に係合させるセレクタ部材と、
このセレクタ部材に連結され、回転させることにより該セレクタ部材が作動させられる回転式の操作部材と、
を備えたことを特徴とする多軸駆動装置。 - 前記セレクタ部材の前記作用部は、該セレクタ部材の前記出力部材への対向面に形成された凹部もしくは凸部であることを特徴とする請求項1に記載の多軸駆動装置。
- 前記セレクタ部材の前記作用部は、該セレクタ部材の作動方向に直交する方向に複数段の状態で設けられていることを特徴とする請求項1または2に記載の多軸駆動装置。
- 前記出力軸の前記作用部に対する対向角度が任意に設定されることを特徴とする請求項1~3のいずれかに記載の多軸駆動装置。
- 前記作用部は前記凹部であり、前記出力部材は、その先端面から突出し該凹部に嵌る凸部を備えていることを特徴とする請求項2~4のいずれかに記載の多軸駆動装置。
- 前記作用部は前記凸部であり、前記出力部材は該凸部で押圧されることを特徴とする請求項2~4のいずれかに記載の多軸駆動装置。
- 前記出力部材は傘歯車を備え、前記入力部材は、前記傘歯車と軸線どうしを交叉させて噛み合う傘歯車を備えていることを特徴とする請求項1~6のいずれかに記載の多軸駆動装置。
- 前記入力部材は、前記モータの回転が伝達される平歯車であり、前記出力部材は、該平歯車と噛み合う平歯車を備えていることを特徴とする請求項1~6のいずれかに記載の多軸駆動装置。
- 前記セレクタ部材の作動形態が回転であることを特徴とする請求項1~8のいずれかに記載の多軸駆動装置。
- 前記出力部材を前記入力部材側へ付勢する付勢手段を備え、
前記セレクタ部材は、円筒曲面をなし前記出力部材と接触することで該出力部材を前記入力部材から離間させる外周部と、この外周部に設けられ前記出力部材が嵌ることで該出力部材を前記入力部材側へ移動させる前記凹部とを備えていることを特徴とする請求項9に記載の多軸駆動装置。 - 前記出力部材を前記入力部材から離間する方向へ付勢する付勢手段を備え、
前記セレクタ部材は、円筒曲面をなし前記出力部材と接触することで該出力部材を前記入力部材から離間させる外周部と、この外周部に設けられ前記出力部材を押圧することで該出力部材を前記入力部材側へ移動させる前記凸部とを備えていることを特徴とする請求項9に記載の多軸駆動装置。 - 前記入力部材は、前記モータの前記回転軸に接続された第1入力ギヤと、この第1入力ギヤの外周側に設けられた複数の第2入力ギヤとを備え、前記第2入力ギヤは、前記第1入力ギヤの外周部と噛み合う第1歯車部と、前記出力部材と係脱自在に噛み合う第2歯車部とを備えたことを特徴とする請求項9~11のいずれかに記載の多軸駆動装置。
- 前記出力部材は、前記第2入力ギヤの軸線を中心とする円に沿って位置が任意に設定可能に設けられていることを特徴とする請求項12に記載の多軸駆動装置。
- 前記第2入力ギヤは、前記第1入力ギヤの軸線を中心とする円に沿って位置が任意に設定可能に設けられていることを特徴とする請求項12または13に記載の多軸駆動装置。
- 前記セレクタ部材の作動形態は、直線移動であることを特徴とする請求項1~8のいずれかに記載の多軸駆動装置。
- 前記セレクタ部材の直線移動は、該セレクタ部材と前記操作部材との間に介在させられたラック・アンド・ピニオン機構によってなされることを特徴とする請求項15に記載の多軸駆動装置。
- 前記出力部材を前記入力部材側へ付勢する付勢手段を備え、
前記セレクタ部材は、前記出力部材と接触することで該出力部材を前記入力部材から離間させるカム面と、このカム面に設けられ前記出力部材が嵌ることで該出力部材を前記入力部材側へ移動させる前記凹部とを備えていることを特徴とする請求項15または16に記載の多軸駆動装置。 - 前記出力部材を前記入力部材から離間する方向へ付勢する付勢手段を備え、
前記セレクタ部材は、前記出力部材と接触することで該出力部材を前記入力部材から離間させるカム面と、このカム面に設けられ前記出力部材を押圧することで該出力部材を前記入力部材側へ移動させる前記凸部とを備えていることを特徴とする請求項15または16に記載の多軸駆動装置。 - 前記セレクタ部材の移動範囲を規制するストッパ手段を有することを特徴とする請求項15~18のいずれかに記載の多軸駆動装置。
- 前記出力部材には、所定の可動機構が備える可動部位が接続され、
前記操作部材には、前記モータを作動させるスイッチがスライド自在に設けられ、該スイッチは、一の方向へスライドさせることで前記モータを正転させ、逆方向へスライドさせることで前記モータを逆転させ、前記スイッチのスライド方向は、前記可動部位の可動方向に一致していることを特徴とする請求項1~19のいずれかに記載の多軸駆動装置。 - 前記可動機構が車両用シートであり、該車両用シートが有する可動部位の調節機構に、前記出力部材が接続されていることを特徴とする請求項20に記載の多軸駆動装置。
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KR20127006396A KR101362635B1 (ko) | 2009-08-28 | 2010-08-27 | 다축 구동 장치 |
CN201080038249.1A CN102472365B (zh) | 2009-08-28 | 2010-08-27 | 多轴驱动装置 |
US13/391,777 US9027442B2 (en) | 2009-08-28 | 2010-08-27 | Multi-shaft drive device |
KR1020137033292A KR20130141733A (ko) | 2009-08-28 | 2010-08-27 | 다축 구동 장치 |
JP2011506512A JP4880088B2 (ja) | 2009-08-28 | 2010-08-27 | 多軸駆動装置 |
EP10812013.0A EP2472143A4 (en) | 2009-08-28 | 2010-08-27 | DRIVE DEVICE WITH SEVERAL WAVES |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2772385A1 (en) * | 2011-10-24 | 2014-09-03 | Aisin Seiki Kabushiki Kaisha | Seat drive device |
EP2772385A4 (en) * | 2011-10-24 | 2015-03-11 | Aisin Seiki | SEAT DRIVE DEVICE |
US9604550B2 (en) | 2011-10-24 | 2017-03-28 | Aisin Seiki Kabushiki Kaisha | Seat drive device |
EP2788602B1 (en) | 2011-12-07 | 2018-02-21 | United Technologies Corporation | Accessory gearbox with tower shaft removal capability |
Also Published As
Publication number | Publication date |
---|---|
JP2012102879A (ja) | 2012-05-31 |
JP2012107752A (ja) | 2012-06-07 |
JPWO2011024964A1 (ja) | 2013-01-31 |
JP5318935B2 (ja) | 2013-10-16 |
EP2472143A4 (en) | 2014-09-17 |
CN102472365A (zh) | 2012-05-23 |
EP2472143A1 (en) | 2012-07-04 |
US20120144943A1 (en) | 2012-06-14 |
JP4880088B2 (ja) | 2012-02-22 |
KR20120052391A (ko) | 2012-05-23 |
KR101362635B1 (ko) | 2014-02-12 |
US9027442B2 (en) | 2015-05-12 |
CN102472365B (zh) | 2015-02-25 |
KR20130141733A (ko) | 2013-12-26 |
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