WO2024111069A1 - Unité de palier et unité de moteur avec réducteur de vitesse - Google Patents

Unité de palier et unité de moteur avec réducteur de vitesse Download PDF

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Publication number
WO2024111069A1
WO2024111069A1 PCT/JP2022/043237 JP2022043237W WO2024111069A1 WO 2024111069 A1 WO2024111069 A1 WO 2024111069A1 JP 2022043237 W JP2022043237 W JP 2022043237W WO 2024111069 A1 WO2024111069 A1 WO 2024111069A1
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WO
WIPO (PCT)
Prior art keywords
bearing
shaft
bearing holder
case
holder
Prior art date
Application number
PCT/JP2022/043237
Other languages
English (en)
Japanese (ja)
Inventor
悟志 菊地
Original Assignee
マブチモーター株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by マブチモーター株式会社 filed Critical マブチモーター株式会社
Priority to PCT/JP2022/043237 priority Critical patent/WO2024111069A1/fr
Publication of WO2024111069A1 publication Critical patent/WO2024111069A1/fr

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings

Definitions

  • This disclosure relates to a bearing unit equipped with a bearing that rotatably supports a shaft, and a motor unit with a reducer to which this bearing unit is applied.
  • Patent Document 1 discloses an end cover in which a motor shaft is disposed, which is provided with a structure for fixing the bearing (bearing fixing part).
  • the bearing fixing part disclosed in Patent Document 1 has an elastic piece with a support surface whose inner diameter is smaller than the outer diameter of the bearing, and when the bearing is fitted, the elastic piece elastically deforms and presses against the bearing from the radial outside, thereby holding (fixing) the bearing.
  • the present invention was conceived in consideration of these problems, and one of its objectives is to provide a bearing unit capable of maintaining the force that holds the bearing, and a motor unit with a reducer to which said bearing unit is applied.
  • this objective is not the only objective, and another objective of the present invention is to achieve effects that cannot be obtained by conventional technology, which are derived from the configurations shown in the embodiments for carrying out the invention described below.
  • a bearing unit disclosed herein includes a bearing that rotatably supports a shaft, and a bearing holder that has the same axis as the bearing and holds the bearing by being incorporated into a case in which the shaft is disposed.
  • the bearing holder has a base that covers an outer circumferential surface of the bearing and restricts the bearing from moving in one axial direction, a contact portion that is located on the other axial side of the bearing holder and comes into contact with the case when the bearing holder is incorporated into the case and displaces radially inward, and a curved portion that is located between the base and the contact portion and elastically deforms in response to the displacement of the contact portion to restrict the bearing from moving in the other axial direction.
  • the curved portion has a smaller radial thickness than the contact portion.
  • the curved portion elastically deforms with the other of the two as a base point in the axial direction rather than the center position of the bearing.
  • the bearing unit includes a shaft receiving part that is disposed on the other side of the bearing and is integrated with both the bearing and the bearing holder before being assembled into the case.
  • the shaft receiving part has a fitting portion that is lightly pressed into the bearing holder so as to be separable in the axial direction before assembly into the case, and a pressing portion that presses the bearing toward the one side while the fitting portion is lightly pressed into the bearing holder, and after assembly into the case, the shaft receiving part is pressed toward the other side by the shaft, thereby eliminating the lightly pressed state between the fitting portion and the bearing holder.
  • the pressing portion extends from the fitting portion to the one side and has an outer peripheral surface with a smaller diameter than the fitting portion, and after the shaft receiving part is assembled into the case, the shaft presses the shaft toward the other side, thereby releasing the lightly pressed-in state between the fitting portion and the bearing holder and holding the pressing portion so as to be freely axially slidable relative to the bearing holder.
  • the bearing holder has a plurality of the curved portions, and the curved portions are provided at approximately equal intervals in the circumferential direction.
  • the motor unit with a reducer disclosed herein comprises a motor section having a shaft, a reduction mechanism having a worm that rotates integrally with the shaft of the motor section and a worm wheel that meshes with the worm, and a gear box to which the motor section is attached and which houses the reduction mechanism, and a bearing unit described in any one of (1) to (6) above is applied to the end of the shaft that is disposed within the gear box as a case.
  • the disclosed invention provides a bearing unit capable of maintaining the force required to hold a bearing, and a motor unit with a reducer to which the bearing unit is applied.
  • FIG. 1 is a plan view of a motor unit with a reducer according to an embodiment of the present invention, showing a main portion in cross section.
  • FIG. 2 is an enlarged view of a portion X (bearing unit) in FIG.
  • FIG. 3 is a perspective view showing a state before the bearing unit in FIG. 2 is installed in a gear box.
  • FIG. 4 is an axial cross-sectional view of the bearing unit of FIG. 3 .
  • 3 is a perspective view of the bearing holder of the bearing unit of FIG. 2 as viewed from the other axial direction.
  • 6 is a plan view of the bearing holder of FIG. 5 as viewed from the other axial direction.
  • FIG. 3 is a diagram for explaining the operation of the bearing unit in FIG. 2, showing a state before a shaft is disposed therein;
  • Fig. 1 is a plan view of a motor unit 1 with a reducer (hereinafter referred to as "motor unit 1") according to this embodiment, showing a cross section of the main parts.
  • the motor unit 1 is applied to, for example, a power window device of a vehicle.
  • the motor unit 1 includes a motor section 2 as a drive source, a reduction mechanism 3 that reduces the rotational speed of a shaft 2A of the motor section 2 and outputs the reduced speed, and a gear box 4 (case) that houses the reduction mechanism 3.
  • the motor section 2 is, for example, a brushed DC motor, and has a rotor 2B and a magnet 2C built into a housing 2D.
  • the motor section 2 is integrated with the gear box 4 by attaching the housing 2D to the gear box 4.
  • the shaft 2A is the rotating shaft of the motor section 2, and rotates integrally with the rotor 2B.
  • One end 2a of the shaft 2A is rotatably supported by the housing 2D that forms the outer shell of the motor section 2, and the other end 2b (end) extends into the gear box 4 and is rotatably supported by the gear box 4.
  • the bearing unit 10 of this embodiment supports the other end 2b of the shaft 2A, and is arranged coaxially with the shaft 2A.
  • the direction in which the axis C extends is called the "axial direction”
  • the direction perpendicular to the axis C is called the "radial direction”
  • the direction around the axis C is called the "circumferential direction”.
  • one end side of the shaft 2A (the right side in FIG. 1 where the one end 2a is located) is called the “one axial side”
  • the direction toward the one axial side (the right side in FIG. 1) is called the “one side”.
  • the other end side of the shaft 2A (the left side in FIG.
  • the other end 2b is located
  • the other axial side is called the “other axial side”
  • the direction toward the other axial side is called the “other side”.
  • the axis C side is called the “radially inner side”
  • the opposite side is called the "radially outer side”.
  • the reduction mechanism 3 has a worm 3A that is fixed to the shaft 2A and rotates integrally with the shaft 2A, and a worm wheel 3B that has teeth that mesh with the worm 3A.
  • the worm 3A is, for example, a screw gear, and the worm wheel 3B is a helical gear.
  • An output gear 3C that meshes with a gear provided in the vehicle's power window device to drive the device is connected to the worm wheel 3B.
  • the gearbox 4 is a case having inside it a worm accommodating space S1 that accommodates the worm 3A, and a wheel accommodating space S2 that accommodates the worm wheel 3B. As shown in FIG. 2, on the other side of the worm accommodating space S1, a bearing accommodating space S3 for accommodating the other end 2b of the shaft 2A is formed by protruding.
  • the gearbox 4 is provided with an accommodating portion 4A that forms the bearing accommodating space S3.
  • the accommodating portion 4A is, for example, cylindrical with a bottom that is concentric with the axis C.
  • the bearing unit 10 is accommodated in the accommodation portion 4A and rotatably supports the other end portion 2b of the shaft 2A.
  • the bearing unit 10 comprises a bearing holder 30 fixed to the accommodation portion 4A, and a bearing 20 held by the bearing holder 30 as a result of being incorporated into the accommodation portion 4A.
  • the bearing unit 10 maintains the force holding the bearing 20 for a long period of time.
  • the bearing unit 10 of this embodiment further comprises a shaft receiving part 40 and a thrust damper 50.
  • the bearing 20 is a component that rotatably supports the shaft 2A, and is annular with a through hole that can be fitted onto the shaft 2A.
  • the bearing 20 is preferably, for example, an oil-less metal that is impregnated with lubricating oil.
  • a bearing 20 having an outer circumferential surface 20g formed in a spherical shape is shown as an example.
  • the shape of the outer circumferential surface 20g of the bearing 20 is not limited to this, and may be, for example, cylindrical.
  • the bearing holder 30 is a part that is incorporated into the gear box 4 to hold the bearing 20 and restrict the movement of the bearing 20.
  • the bearing holder 30 has a base 31 that covers a part of the outer circumferential surface 20g of the bearing 20 and restricts the movement of the bearing 20 to one side when incorporated into the gear box 4, and a first arm 34 that extends from the base 31 and restricts the movement of the bearing 20 to the other side.
  • the bearing holder 30 of this embodiment further has a second arm 37 that extends from the base 31 at a position offset from the first arm 34 in the circumferential direction.
  • the bearing holder 30 has these parts 31, 34, and 37 integrally formed from resin.
  • the resin used for the bearing holder 30 has, for example, excellent flexibility.
  • the bearing holder 30 is molded from such a resin, allowing the deformation of the first arm 34 to be described later.
  • the base 31 is a portion of the bearing holder 30 that is located on one axial side.
  • the base 31 is provided with a cylindrical tube portion 32 that covers one axial side of the outer circumferential surface 20g of the bearing 20 when the bearing 20 is housed in the bearing holder 30, and a restricting surface portion 33 that is provided on one side of the tube portion 32 and restricts the movement of the bearing 20 to one side.
  • the inner peripheral surface 32f of the cylindrical portion 32 covers the range from one end surface 20a of the bearing 20 to the center position P of the bearing 20 in the axial direction (or the range slightly beyond the center position P) when the bearing 20 is accommodated in the bearing holder 30.
  • the inner peripheral surface 32f of the cylindrical portion 32 covers the range from the center position P to a position Pb (hereinafter also referred to as the "base end position Pb") on the other side (however, on the other side of the other end surface 20b of the bearing 20).
  • the inner peripheral surface 32f has a hemispherical shape whose inner diameter decreases from the base end position Pb to one side, for example, in correspondence with the shape of the outer peripheral surface 20g of the bearing 20.
  • the inner diameter D1 on the other axial side of the cylindrical portion 32, where the inner diameter of the inner peripheral surface 20f is the largest, is set to be equal to or slightly larger than the outer diameter D2 of the bearing 20.
  • the outer shape of the cylindrical portion 32 is not particularly limited, but is at least a shape that can be accommodated in the accommodation portion 4A.
  • the tubular portion 32 is formed in a generally cylindrical shape with an outer diameter D3 that is sufficiently larger than the outer diameter D2 of the bearing 20 and smaller than the inner diameter D4 of the housing portion 4A.
  • the regulating surface portion 33 protrudes radially inward from the inner peripheral surface 32f of the tubular portion 32 and forms a regulating surface 33r facing the other direction.
  • the regulating surface portion 33 is, for example, annular in shape having a thickness in the axial direction and a hole 33h through which the shaft 2A is inserted on its radially inner side.
  • the inner peripheral surface of the regulating surface portion 33 forming the hole 33h may be provided with a guide surface 33q whose inner diameter decreases from the end face on one axial side to the other.
  • the outer shape of the regulating surface portion 33 is not particularly limited, like the outer shape of the tubular portion 32, but is at least a shape that can be accommodated in the accommodating portion 4A.
  • the regulating surface portion 33 is a substantially annular shape having an outer diameter that is larger than the outer diameter D3 of the tubular portion 32 and can be press-fitted into the accommodating portion 4A.
  • the regulating surface portion 33 is press-fitted into the accommodating portion 4A, and thereby the position of the bearing holder 30 is fixed relative to the gearbox 4.
  • the regulating surface portion 33 of this embodiment also has the function of fixing the position of the bearing holder 30 relative to the gear box 4.
  • the outer peripheral surface of the regulating surface portion 33 may be provided with a plurality of ribs that protrude radially outward.
  • Each of the first arm 34 and the second arm 37 is an extension from the other axial side of the base 31, i.e., the base end position Pb.
  • a bearing holder 30 having three first arms 34 and three second arms 37 is exemplified.
  • the three first arms 34 and the three second arms 37 are alternately arranged at a distance from each other in the circumferential direction, as shown in Figures 5 and 6.
  • Each of the first arms 34 has the same shape, but is arranged differently (phase).
  • Each of the second arms 37 also has the same shape, but is arranged differently (phase). Note that it is preferable that adjacent first arms 34 and second arms 37 are arranged at equal intervals in the circumferential direction so that the force holding the bearing 20 and the force applied to the shaft 2A are not biased.
  • the first arm 34 is a portion that restricts the movement of the bearing 20 in the other direction, and restricts the movement of the bearing 20 in the other direction by deforming when assembled into the gear box 4.
  • the first arm 34 is provided with a contact portion 35 that is displaced when assembled into the gear box 4, and a curved portion 36 that elastically deforms in response to the displacement of the contact portion 35 to restrict the movement of the bearing 20 in the other direction.
  • the contact portion 35 is a portion of the bearing holder 30 located on the other axial side, and is provided at least on the other side of the base portion 31. As shown in FIG. 6, before the contact portion 35 is assembled into the gear box 4, the contact portion 35 has an edge 35e located radially outward of an imaginary circle R4 having the same diameter as the inner diameter D4 of the accommodating portion 4A. In this embodiment, the edge 35e is provided along an imaginary circle R5 having a larger diameter than the imaginary circle R4. When the contact portion 35 is assembled into the gear box 4, as shown in FIG. 2, the edge 35e comes into contact with the inner circumferential wall of the accommodating portion 4 and is pushed radially inward, displacing the contact portion 35 radially inward.
  • the curved portion 36 is a portion located between the base 31 and the contact portion 35.
  • the curved portion 36 extends from the base end position Pb in the other direction and connects the portion on the other axial side of the base 31 and the portion on one axial side of the contact portion 35.
  • the curved portion 36 is formed so as to extend along the axial direction as shown in FIG. 4 and not restrict movement of the bearing 20 in the other direction.
  • the curved portion 36 elastically deforms radially inward with the base end position Pb as a base point in association with the displacement of the contact portion 35 as shown in FIG. 2. This restricts movement of the bearing 20 in the other direction.
  • the curved portion 36 has, for example, an arc-shaped wall portion when viewed from the axial direction, and has an inner surface 36f and an outer surface 36g extending in the circumferential direction.
  • the inner surface 36f is continuous with the inner peripheral surface 32f of the tubular portion 32.
  • the inner surface 36f extends substantially parallel to the axial direction as shown in Figs. 4 and 6, and forms an inner peripheral surface having substantially the same diameter as the inner diameter D1 on the other axial side of the tubular portion 32 together with an inner surface 37f of the second arm portion 37 described later.
  • the outer surface 36g is not continuous with the outer peripheral surface of the tubular portion 32, and is extended along the axial direction, for example, radially inward from the outer peripheral surface of the tubular portion 32.
  • a notch portion 31p is provided on the outer peripheral surface of the base portion 31 to form a surface continuous with the outer surface 36g, but the notch portion 31p may be omitted. If the notch 31p is omitted, the deformation of the curved portion 36 can be more reliably achieved with the base end position Pb as the base point. Conversely, if the notch 31p is provided, the outer surface 36g does not become an undercut portion, so injection molding of the bearing holder 30 can be easily achieved.
  • the curved portion 36 is configured to have a radial thickness smaller than that of the contact portion 35 in order to promote deformation when assembled into the gearbox 4.
  • the contact portion 35 is configured to have a radial thickness greater than that of the curved portion 36.
  • the contact portion 35 is shaped to diverge radially outward so that the radial thickness increases from one axial end connected to the curved portion 36 to the other end. Forming the contact portion 35 in this manner ensures that the contact portion 35 has a higher rigidity than the curved portion 36. This prevents the contact portion 35 itself from deforming when the end edge 35e comes into contact with the wall of the accommodation portion 4A and the contact portion 35 is pushed radially inward.
  • the second arm 37 is a part that functions to integrate the bearing unit 10 together with the shaft receiving part 40. As shown in FIG. 6, the second arm 37 is arc-shaped when viewed from the axial direction, and forms an inner circumferential surface surrounding the bearing 20 together with the inner surface 36f of the curved portion 36.
  • the inner surface 37f of the second arm 37 is continuous with the inner circumferential surface 32f of the tubular portion 32 as shown in FIG. 2 and FIG. 4.
  • the outer surface 37g of the second arm 37 is continuous with the outer circumferential surface of the tubular portion 32.
  • the second arm 37 extends from the base end position Pb at least further than the other end surface 20b of the bearing 20, and preferably extends to the same extent as the first arm 34 or further than the first arm 34.
  • the shaft receiving part 40 is a part that abuts against the shaft 2A from the other side when assembled in the gearbox 4, and as shown in FIG. 4, has the function of integrating the bearing unit 10 together with the bearing holder 30 before assembly in the gearbox 4. Furthermore, the shaft receiving part 40 of this embodiment has the function of pressing the bearing 20 housed in the bearing holder 30 to one side before assembly in the gearbox 4, thereby maintaining the coaxial state between the bearing 20 and the bearing holder 30.
  • the shaft receiving part 40 has a fitting portion 41 that is lightly pressed into the second arm portion 37 of the bearing holder 30 in an axially separable manner before being assembled into the gearbox 4, and a pressing portion 42 that has a smaller outer diameter than the fitting portion 41 and extends in one direction from the fitting portion 41.
  • the shaft receiving part 40 also has a receiving surface 40a that faces in one direction on one axial side of the shaft receiving part 40. In this embodiment, the receiving surface 40a is provided radially inward of the pressing portion 42.
  • the shaft receiving part 40 of this embodiment is further provided with a flange portion 43 that extends on the other axial side of the fitting portion 41 and has an outer circumferential surface with a larger diameter than the fitting portion 41, and a press-in portion 44 that extends on the other axial side of the flange portion 43 and has an outer circumferential surface with a smaller diameter than the flange portion 43.
  • the shaft receiving part 40 has a stepped shape with these four portions 41, 42, 43, 44 with different outer diameters arranged side by side in the axial direction.
  • a resin with high strength, rigidity, and abrasion resistance is used for the shaft receiving part 40.
  • the fitting portion 41 is a portion that is lightly pressed into the second arm portion 37 of the bearing holder 30 in an axially separable manner before being assembled into the gearbox 4.
  • the fitting portion 41 is, for example, cylindrical with an outer peripheral surface that can be lightly pressed into the second arm portion 37 of the bearing holder 30.
  • the outer diameter of the fitting portion 41 is set to be equal to or slightly larger than the inner diameter of the inner peripheral surface 37f of the second arm portion 37, i.e., the inner diameter D1 on the other axial side of the tubular portion 32.
  • the pressing portion 42 is a portion that extends in one direction from the fitting portion 41, and has the function of abutting against the other end face 20b of the bearing 20 and pressing the bearing 20 in one direction when the fitting portion 41 is lightly pressed into the second arm portion 37 before installation into the gearbox 4.
  • the pressing portion 42 has the function of guiding the shaft receiving part 40 in the axial direction relative to the bearing holder 30 after the lightly pressed state between the shaft receiving part 40 and the bearing holder 30 is released, as shown in FIG. 2.
  • the pressing portion 42 is, for example, cylindrical with an outer peripheral surface smaller in diameter than the outer peripheral surface of the pressing portion 42 and a pressing surface 42a facing one side in the axial direction.
  • the outer diameter of the pressing portion 42 is set to be at least smaller than the inner diameter of the inner peripheral surface 37f of the second arm portion 37 and larger than the inner diameter of the through hole of the bearing 20.
  • the outer diameter of the pressing portion 42 is preferably set to be slightly smaller than the inner diameter of the inner peripheral surface 37f of the second arm portion 37.
  • the length by which the pressing portion 42 extends from the fitting portion 41 is set to a length that allows the pressing surface 42a to be pressed against the other end surface 20b of the bearing 20 when the shaft receiving part 40 and the bearing holder 30 are lightly pressed in, as shown in FIG. 4.
  • the receiving surface 40a is provided on the radially inner side of the pressing portion 42.
  • the receiving surface 40a is provided at a location where the radially inner portion of the pressing surface 42a is recessed in order to collect the grease to be applied to the receiving surface 40a.
  • a groove that functions as a grease reservoir is provided in the recessed portion of the pressing surface 42a so as to surround the radially outer side of the receiving surface 40a, but this groove may be omitted.
  • the press-in portion 44 is a portion that makes the shaft receiving part 40 and the thrust damper 50 in a fitted state (integral), and the flange portion 43 is a portion that regulates the fitting amount (press-in amount) of the fitting portion 41 to the second arm portion 37 and the fitting amount (press-in amount) of the press-in portion 44 to the thrust damper 50.
  • the press-in portion 44 is columnar (e.g., cylindrical) having an outer diameter that can be pressed into the inner hole 50h of the thrust damper 50 described later.
  • the axial dimension of the press-in portion 44 is shorter than the axial dimension of the thrust damper 50, and is set to a length that forms a small gap between the end wall on the other axial side of the housing portion 4A when the motor unit 1 is stationary, as shown in FIG. 2. This gap is set to be smaller than the expected displacement and sufficiently absorbs the load and impact in the thrust direction of the shaft 2A when the motor unit 1 is driven.
  • the flange portion 43 is generally disk-shaped and has a larger diameter than the fitting portion 41 and the press-fit portion 44.
  • the outer diameter of the flange portion 43 is set to be large enough so that the flange portion 43 is not embedded in the inner hole 50h when the shaft receiving part 30 is pushed from one side to the other in the axial direction by the shaft 2A, and is set to be smaller than the inner diameter D4 of the accommodation portion 4A.
  • the thrust damper 50 is a cylindrical member (e.g., rubber) made of a material that can expand and contract in the axial direction, and has the function of absorbing thrust displacement of the shaft 2A via the shaft receiving part 40.
  • the thrust damper 50 is, for example, cylindrical with an inner hole 50h on the radially inner side.
  • the inner diameter of the inner hole 50h is set to be equal to or larger than the outer diameter of the press-fit portion 44 to enable the press-fit portion 44 to be press-fitted into the thrust damper 50.
  • the inner peripheral surface of the thrust damper 50 that forms the inner hole 50h may be provided with a plurality of ribs that protrude radially inward, as shown in FIG. 3.
  • the outer diameter of the thrust damper 50 is, for example, set to be smaller than the inner diameter D4 of the accommodating portion 4A to form a gap between the thrust damper 50 and the inner peripheral wall of the accommodating portion 4A.
  • bearing unit 10 is incorporated into the gear box 4, and the bearing holder 30 is The bearing unit 10 is a unit made up of the components 20, 30, 40, and 50, which are integrated together before being assembled into the gear box 4. The integrated bearing unit 10 is then assembled into the gear box 4. Then, when the shaft 2A is inserted into the gear box 4, the integrated state is dissolved and each of the components 20, 30, 40, and 50 is disposed in a predetermined position. This allows the components 20, 30, 40, and 50 to function properly.
  • the bearing 20 is inserted from the other side into the radially inner side of the bearing holder 30 and accommodated.
  • the press-fit portion 44 of the shaft receiving part 40 is press-fit into the inner hole 50h of the thrust damper 50.
  • Grease is also applied to the receiving surface 40a of the shaft receiving part 40.
  • the mating portion 41 of the shaft receiving part 40 is lightly press-fit into the second arm portion 37 of the bearing holder 30 in which the bearing 20 is accommodated.
  • the bearing unit 10 is in a state in which the parts 20, 30, 40, and 50 shown in Figures 3 and 4 are integrated.
  • one axial side portion of the outer peripheral surface 20g of the bearing 20 abuts against the inner peripheral surface 32f of the tubular portion 32 of the bearing holder 30.
  • the movement of the bearing 20 in one direction is also restricted by the restricting surface 33r.
  • the other end surface 20b of the bearing 20 is pressed from the other side by the pressing portion 42 of the shaft receiving part 40 that is lightly press-fitted into the bearing holder 30. This restricts the bearing 20 from moving in the other direction relative to the bearing holder 30, and maintains a coaxial state with the bearing holder 30 without rotating along the hemispherical inner peripheral surface 32f of the tubular portion 32.
  • the process of assembling the bearing unit 10 into the gear box 4, i.e., the process until each of the components 20, 30, 40, 50 can perform its function, is completed by inserting the bearing unit 10 into the housing portion 4A from one side, pressing the regulating surface portion 33 of the bearing holder 30 into the inner peripheral wall of the housing portion 4A, and then inserting and arranging the shaft 2A into the gear box 4.
  • the bearing unit 10 of this embodiment by simply assembling the bearing unit 10 and the motor portion 2 into the gear box 4, the multiple components 20, 30, 40, 50 can be arranged in the predetermined positions without any special operations or additional processes, and each of the components 20, 30, 40, 50 can be made to perform its function.
  • the contact portion 35 of the bearing holder 30 is displaced radially inward as the end edge 35e comes into contact with the inner peripheral wall of the housing 4 and is pushed radially inward, as shown in FIG. 7.
  • the curved portion 36 of the bearing holder 30 elastically deforms radially inward with the base end position Pb as the base point, and the other axial side portion of the curved portion 36 is pressed against the bearing 20 from the other side. This restricts the movement of the bearing 20 to the other side, and the function of the bearing holder 30 is exerted.
  • the bearing holder 30 and the shaft receiving part 40 are maintained in a lightly pressed-fit state.
  • the bearing 20 is pressed by the pressing part 42 so that it does not rotate along the hemispherical inner circumferential surface 32f of the cylindrical part 32. This allows the shaft 2A to be inserted smoothly.
  • the shaft receiving part 40 When the shaft 2A is inserted into the gearbox 4, the shaft receiving part 40 is pushed into the other by the shaft 2A. This causes the fitting portion 41 of the shaft receiving part 40 to be pushed out from the second arm portion 37 of the bearing holder 30, and the light press-fit state between the two is released, as shown in FIG. 2. By releasing the light press-fit state between the bearing holder 30 and the shaft receiving part 40, the shaft receiving part 40 becomes movable relative to the bearing holder 30, and together with the thrust damper 50, it can exert its function of restricting movement of the shaft 2A in the thrust direction (axial direction).
  • the pressing portion 42 of the shaft receiving part 40 does not completely separate (fall off) from the second arm part 37 of the bearing holder 30, but remains positioned radially inside the second arm part 37.
  • the bearing 20 When the shaft receiving part 40 is pushed into the other side, the bearing 20 is released from the state where it was pressed to one side by the pressing part 42. As a result, the bearing 20 is held only by the bearing holder 30 and is able to perform the function of rotatably supporting the shaft 2A. Furthermore, the bearing 20 of this embodiment is able to perform an automatic centering function by allowing a predetermined angle of inclination with the axis C, which allows it to automatically center itself with the rotation of the shaft 2A.
  • a force acts on the bearing 20 via the shaft 2A to move it in the other direction, but the movement of the bearing 20 in the other direction is restricted by the elastically deformed curved portion 36.
  • a force acts on the curved portion 36 in the radially outward direction (a force in the direction in which the elastically deformed curved portion 36 tries to return to its original state), but this force is transmitted to the accommodating portion 4A via the contact portion 35.
  • the accommodating portion 4A is part of the gearbox 4 and has high rigidity, so it does not deform even when a force is transmitted, and the contact portion 35 cannot physically move. This prevents the curved portion 36 from opening in the radially outward direction, and as a result, the bearing holder 30 maintains the state in which it holds the bearing 20.
  • the bearing 20 is subjected to a force that moves it in the other direction due to the thrust force acting on the shaft 2A depending on the driving state of the motor unit 1, but the curved portion 36 and the contact portion 35 act as described above to restrict the movement of the bearing 20 in the other direction, and the bearing holder 30 maintains the state in which the bearing 20 is held.
  • the shaft 2A may be subjected to a gear reaction force (radial load) generated between the worm 3A and the worm wheel 3B. This radial load is received by the inner peripheral surface 32f of the cylindrical portion 32 and the inner surface 37f of the second arm portion 37 of the bearing holder 30, and is transmitted to the housing portion 4A via the curved portion 36 and the contact portion 35. Therefore, the movement of the shaft 2A in the radial direction (lifting of the shaft 2A) is restricted.
  • the thrust damper 50 is pushed into the other side by the shaft receiving part 40 being pushed into the other side. This causes the thrust damper 50 to shrink in the axial direction and become capable of performing its function. In other words, the thrust damper 50 becomes capable of expanding and contracting according to the thrust force acting on the shaft 2A while the motor unit 1 is being driven. When the thrust damper 50 is pushed into the other side, the thrust damper 50 deforms so as to bulge radially outward.
  • the bearing 20 is held by the bearing holder 30 having the contact portion 35 that comes into contact with the gear box 4 and displaces radially inward when the bearing unit 10 is assembled into the gear box 4 as a case, and the curved portion 36 that elastically deforms with the displacement of the contact portion 35.
  • the curved portion 36 is deflected to restrict the axial movement of the bearing 20, and the force holding the bearing 20 can be maintained even when the shaft 2A is inserted or the motor unit 1 is being driven.
  • the inner diameter of this part is made smaller than the outer diameter of the bearing, and the force generated radially inward when the bearing pushes this part apart is used.
  • the contact part 35 of the bearing holder 30 is displaced radially inward when it comes into contact with the gear box 4, and the curved part 36 elastically deforms in response to this displacement, restricting the movement of the bearing 20 to the other side, so there is no possibility that the contact part 35 and the curved part 36 will open radially outward. Therefore, the force with which the bearing holder 30 holds the bearing 20 does not decrease, and the bearing 20 can be maintained in a fixed position.
  • the contact portion 35 and the curved portion 36 are located at the same position as the inner peripheral surface 32f of the cylindrical portion 32 or radially outward from the inner peripheral surface 32f, as shown in FIG. 4.
  • no undercut portion is formed radially inside the bearing holder 30 before being assembled into the gear box 4, so that the bearing holder 30 can be easily manufactured.
  • the curved portion 36 is set to have a smaller radial thickness than the contact portion 35. This makes the rigidity of the contact portion 35 relatively high, allowing the curved portion 36 to bend significantly. This makes it possible to more reliably restrict the movement of the bearing 20 by the curved portion 36 when the bearing unit 10 is assembled into the gear box 4.
  • the curved portion 36 elastically deforms with the other base end position Pb as the base point rather than the center position P of the bearing 20. This makes it possible to more reliably restrict the movement of the bearing 20 by the curved portion 36 when the bearing 20 is assembled into the gear box 4. Furthermore, since the portion of the bearing 20 corresponding to the center position P does not deform, it is possible to prevent the bearing 20 from being pressed into the bearing holder 30.
  • the components 20, 30, 40, and 50 are integrated into a single assembled bearing before the bearing unit 10 is assembled into the gear box 4. This prevents the bearing 20 from falling out of the bearing holder 30 when assembled into the gear box 4, and allows the multiple components 20, 30, 40, and 50 attached to the other end 2b of the shaft 2A to be positioned together in appropriate positions, simplifying the assembly procedure and facilitating the assembly work.
  • the shaft receiving part 40 is released from the lightly pressed-in state with the bearing holder 30 after being assembled into the gear box 4.
  • the pressing portion 42 of the shaft receiving part 40 does not completely separate from the second arm portion 37 of the bearing holder 30, and is held so as to be freely slidable in the axial direction relative to the second arm portion 37. Therefore, the coaxial state between the shaft receiving part 40 and the bearing holder 30 can be maintained.
  • three first arms 34 are provided on the bearing holder 30, and these three first arms 34 are provided at approximately equal intervals in the circumferential direction. In this way, by providing a plurality of first arms 34 (i.e., the contact portions 35 and the curved portions 36) at approximately equal intervals in the circumferential direction, the bearings 20 can be held in a balanced manner.
  • bearing unit 10 and the motor unit 1 described in the above embodiment are merely examples, and are not limited to those described above.
  • the motor unit 1 may be applied to a device other than a power window device for a vehicle.
  • the bearing unit 10 may be applied, for example, to a shaft other than the shaft 2A disposed in the gear box 4.
  • the bearing unit 10 may also be applied to one end 2a of the shaft 2A.
  • the housing 2D becomes the "case" in the claims.
  • the thrust damper 50 may be omitted.
  • the flange portion 43 and the press-fit portion 44 of the shaft receiving part 40 may be omitted.
  • the shaft receiving part 40 is not limited to the above-mentioned shape as long as it has at least an engagement part 41 that is lightly pressed into the bearing holder 30 so as to be separable before installation in the gearbox 4, and a pressing part 42 that presses the bearing 20 to one side when the engagement part 41 is lightly pressed into the bearing holder 30.
  • the pressing surface 42a of the pressing part 42 may have a function of abutting against the other end surface 2b of the shaft 2A.
  • both the shaft receiving part 40 and the thrust damper 50 may be omitted.
  • the second arm portion 37 of the bearing holder 30 may be omitted.
  • the shaft may be inserted into the bearing unit 10 from the other end to one end in the axial direction.
  • the regulating surface portion 33 of the bearing holder 30 may be a plate-like member that closes the inner hole of the cylindrical portion 32 from one side and abuts against one end of the shaft.
  • At least one contact portion 35 and one curved portion 36 are provided on the bearing holder 30. If multiple contact portions 35 and multiple curved portions 36 are provided, i.e., if multiple first arms 34 are provided, the first arms 34 do not need to be provided at approximately equal intervals in the circumferential direction.
  • Motor unit (motor unit with reducer) 2 Motor section 2A Shaft 2b Other end section (end section) 3 Reduction mechanism 3A Worm 3B Worm wheel 4 Gear box (case) REFERENCE SIGNS LIST 10 Bearing unit 20 Bearing 20g Outer circumferential surface 30 Bearing holder 31 Base 35 Contact portion 36 Curved portion 40 Shaft receiving part 41 Fitting portion 42 Pressing portion C Axis P Center position

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

L'invention concerne une unité de palier (10) qui comprend : un palier (20) qui supporte avec faculté de rotation un arbre (2A) ; et un support de palier (30) qui a le même axe (C) que le palier (20) et maintient le palier (20) lorsqu'il est installé dans un carter (4) dans lequel l'arbre (2A) est disposé. Le support de palier (30) comprend une partie de base (31) qui recouvre une surface périphérique externe (20g) du palier (20) et limite le mouvement du palier (20) vers un côté dans le sens axial, une partie de contact (35) qui est positionnée sur l'autre côté du support de palier (30) dans le sens axial et entre en contact avec le carter (4) de façon à être déplacée vers l'intérieur dans le sens radial lorsqu'elle est installée dans le boîtier (4), et une partie incurvée (36) qui est positionnée entre la partie de base (31) et la partie de contact (35) et se déforme élastiquement en association avec le déplacement de la partie de contact (35) de façon à limiter le mouvement du palier (20) vers l'autre côté dans le sens axial.
PCT/JP2022/043237 2022-11-22 2022-11-22 Unité de palier et unité de moteur avec réducteur de vitesse WO2024111069A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/043237 WO2024111069A1 (fr) 2022-11-22 2022-11-22 Unité de palier et unité de moteur avec réducteur de vitesse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/043237 WO2024111069A1 (fr) 2022-11-22 2022-11-22 Unité de palier et unité de moteur avec réducteur de vitesse

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WO2024111069A1 true WO2024111069A1 (fr) 2024-05-30

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5026244U (fr) * 1973-07-04 1975-03-26
JP2002101601A (ja) * 2000-09-26 2002-04-05 Jidosha Denki Kogyo Co Ltd モータ及びモータの製造方法
JP2005282666A (ja) * 2004-03-29 2005-10-13 Nsk Ltd ウォーム減速機付駆動装置
CN109861436A (zh) * 2017-11-30 2019-06-07 马渊马达株式会社 电机单元的轴向减震结构以及电机单元

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5026244U (fr) * 1973-07-04 1975-03-26
JP2002101601A (ja) * 2000-09-26 2002-04-05 Jidosha Denki Kogyo Co Ltd モータ及びモータの製造方法
JP2005282666A (ja) * 2004-03-29 2005-10-13 Nsk Ltd ウォーム減速機付駆動装置
CN109861436A (zh) * 2017-11-30 2019-06-07 马渊马达株式会社 电机单元的轴向减震结构以及电机单元

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