WO2006009292A1 - Dispositif de transmission électrique - Google Patents

Dispositif de transmission électrique Download PDF

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Publication number
WO2006009292A1
WO2006009292A1 PCT/JP2005/013680 JP2005013680W WO2006009292A1 WO 2006009292 A1 WO2006009292 A1 WO 2006009292A1 JP 2005013680 W JP2005013680 W JP 2005013680W WO 2006009292 A1 WO2006009292 A1 WO 2006009292A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
power transmission
transmission device
contact surface
carrier
Prior art date
Application number
PCT/JP2005/013680
Other languages
English (en)
Japanese (ja)
Inventor
Mitsuru Sekiya
Original Assignee
Mikuni Corporation
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 Mikuni Corporation filed Critical Mikuni Corporation
Publication of WO2006009292A1 publication Critical patent/WO2006009292A1/fr

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Classifications

    • 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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/10—Means for influencing the pressure between the members
    • F16H13/14—Means for influencing the pressure between the members for automatically varying the pressure mechanically
    • 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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/02—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members without members having orbital motion
    • F16H13/04—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members without members having orbital motion with balls or with rollers acting in a similar manner

Definitions

  • the present invention relates to a power transmission device that transmits rotational force from an input shaft to an output shaft, and more particularly, to a power transmission device that transmits rotational force by a traction drive using a tractive force.
  • Conventional power transmission devices that employ this method include an input shaft, a central roller (or input disk) that rotates integrally with the input shaft, and a plurality of rollers that make rolling contact with the outer peripheral surface of the central roller.
  • Roller a circular outer drum that is inscribed in multiple rollers, an output shaft that rotates integrally with the outer drum, and the like.
  • Something is known (see, for example, Japanese Patent Application Laid-Open No. 1 1 1 1 3 8 4 8).
  • the conventional power transmission device since the conventional power transmission device has a structure in which a normal load is always applied, it is not possible to provide a clutch function for turning on / off the drive torque from the input shaft to the output shaft at a desired timing. Have difficulty.
  • the present invention has been made in view of the circumstances of the above-described conventional apparatus, and its object is to reduce the load on the output shaft side while simplifying the structure and reducing the manufacturing cost. Accordingly, the minimum normal load necessary to obtain a traction drive can be variably applied to prevent wear or damage of the contact surface and improve durability. It is an object of the present invention to provide a traction drive type power transmission device that can transmit and transmit drive torque from the input shaft to the output shaft at a desired timing. Disclosure of the invention
  • the power transmission device of the present invention that achieves the above-mentioned object is a drive rotating body that rotates integrally with an input shaft and has a contact surface on the outer periphery of the force shaft, and rotates integrally with the output shaft and contacts the outer periphery thereof.
  • a driven rotating body having a surface, a roller that rolls in contact with the contact surface of the driving rotating body and the driven rotating body, and the rotational speed of the output shaft is slower than the value set by the rotational speed of the input shaft
  • a load adjustment mechanism that automatically increases the normal load that presses the roller against the contact surface.
  • the load adjusting mechanism acts to automatically increase the normal load that presses the roller against the transmissible surface until the rotation delay is resolved.
  • the required normal load is feedback-controlled according to the load fluctuation of the output shaft, and a stable traction force is obtained, so that the power (rotational force) is reliably transmitted.
  • the excessive load force more than necessary is not required, slipping or the like on the contact surface does not occur, so that durability is improved.
  • the configuration may further include a clutch mechanism that adjusts the normal load by operating the load adjustment mechanism from the outside, and further turns on / off transmission of drive torque from the input shaft to the output shaft. it can.
  • the clutch mechanism when transmission of driving torque is necessary, the clutch mechanism is turned on (clutch on), and when transmission of driving torque is not necessary, the clutch mechanism is turned off (clutch off).
  • the load adjusting mechanism supports the roller in a rotatable manner and supports the roller so as to revolve around the input shaft, and the roller can be held in a predetermined position so as not to rotate, and the roller can be inscribed.
  • a cam member having a cam surface that exerts a cam action so as to gradually increase with a transition from a state in which no normal load is applied to a state in which a normal load is applied.
  • the mechanism includes a connecting member connected to rotate the carrier within a predetermined angular range, and a reciprocating drive of the connecting member to switch between a state in which the normal load is not applied and a state in which the normal load is applied.
  • Sources and configurations can be employed.
  • the carrier rotates in a predetermined angular range, and a normal load is applied (clutch on to which driving torque is transmitted) and the normal line.
  • the state is switched to each other when no load is applied (clutch off where drive torque is not transmitted). In this way, transmission of drive torque can be turned on and off with a simple operation.
  • a load adjustment mechanism can be provided with a simple structure by adopting a carrier that supports the roller so that it can rotate and revolve, and a force member that has a force surface that can incline the roller.
  • the clutch mechanism can be provided with a simple structure, and the entire apparatus can be simplified and downsized.
  • the connecting member includes a first connecting rod connected to the drive source, and a carrier.
  • a configuration including a second connecting rod connected to the rear, and a connecting panel that exerts an urging force interposed between the first connecting port pad and the second connecting port pad can be adopted.
  • the cam surface of the cam member does not apply a normal load to the roller (for example, the state where the force surface is detached from the roller or is in contact with the roller but does not exert a pressing force). State), and a clutch-off state in which the drive torque is not transmitted.
  • the connecting panel is elastically restored by a predetermined amount, and at the same time, the second connecting rod is also pulled back, and the carrier rotates backward to a stable position.
  • the cam surface of the cam member enters a state in which a normal load is applied to the roller (for example, a state in which the cam surface contacts the roller and exerts a pressing force), and the clutch-on to which the drive torque is transmitted. It becomes the state of.
  • the connecting member is configured by interposing the connecting spring between the first connecting rod and the second connecting rod, thereby allowing the carrier to move and ensuring the normal load pack control. be able to.
  • the first connecting rod and the second connecting rod are formed so as to contact each other while compressing and deforming the connecting panel when the carrier is rotated in a state where no normal load is applied. Can be adopted.
  • the first connecting port abuts the second connecting port and a predetermined pushing stroke is obtained, and the carrier is reliably rotated by a predetermined angle. Therefore, transmission of the drive torque can be reliably turned off without depending on the urging force of the connecting panel.
  • the carrier has a long hole that guides the support shaft of the roller in a direction away from the contact surface of the drive rotator, and in a direction to release the support shaft of the roller from the contact surface of the drive rotator. It is possible to adopt a configuration that holds a spring to be biased. According to this configuration, when the carrier rotates in a clutch-off state where driving torque is not transmitted, the roller is urged by the panel while its support shaft is guided by the long hole, and is separated from the contact surface of the driving rotating body. It becomes the state of. Thus, it is possible to reliably form a clutch-off state in which the driving torque is not transmitted with a simple structure.
  • the carrier has an arm portion that extends in a cantilever shape in the circumferential direction and rotatably supports the roller at its free end, and the arm portion is elastically deformed inward in the radial direction in advance. It is possible to adopt a configuration that is assembled in such a state.
  • the roller when the carrier rotates in a clutch-off state in which the driving torque is not transmitted, the roller is in a non-contact state in which the roller is detached from the contact surface of the driving rotating body due to the elastic return of the arm portion outward in the radial direction It becomes.
  • a clutch-off state in which drive torque is not transmitted can be reliably formed with a simple structure.
  • the drive source of the clutch mechanism guides the atmospheric pressure when the drive torque transmission is turned off, and powerfully guides the negative pressure when the drive torque transmission is turned on to reciprocate the connecting member. It is possible to adopt a configuration that is a diaphragm type actuator.
  • the clutch when atmospheric pressure is introduced to the actuator, the clutch is turned off, and when negative pressure is introduced to the actuator, the clutch is turned on. In this way, the clutch can be switched on and off by simple pressure control.
  • the drive source of the clutch mechanism is a motor that reciprocates the connecting member.
  • FIG. 1 is a cross-sectional view showing an embodiment of a power transmission device according to the present invention.
  • FIG. 2 is another cross-sectional view showing an embodiment of a power transmission device according to the present invention.
  • FIG. 3 is an enlarged cross-sectional view of a part of the power transmission device.
  • FIG. 4 is a cross-sectional view showing a part of the power transmission device.
  • FIG. 5 is a cross-sectional view showing a part of the power transmission device.
  • FIG. 6 is a plan view showing a cam ring constituting a part of the power transmission device.
  • FIG. 7 is a schematic diagram for explaining the operation of the power transmission device.
  • FIG. 8 is a cross-sectional view when the clutch mechanism forming a part of the power transmission device is in a clutch-on state.
  • FIG. 9 is a cross-sectional view when the clutch mechanism forming a part of the power transmission device is in a clutch-on state.
  • FIG. 10 is a cross-sectional view when the clutch mechanism forming a part of the power transmission device is in a clutch-off state.
  • FIG. 11 is a cross-sectional view of the clutch mechanism that forms a part of the power transmission device in a clutch-off state.
  • FIG. 12 shows another embodiment of the power transmission device according to the present invention, and is a cross-sectional view when a clutch mechanism constituting a part thereof is in a clutch-off state.
  • Fig. 13 shows the clutch mechanism that forms part of the power transmission device shown in Fig. 12.
  • FIG. 14 shows still another embodiment of the power transmission device according to the present invention, and is a cross-sectional view when a clutch mechanism forming a part thereof is in a clutch-off state.
  • the power transmission device includes a housing 1 0, an input shaft 20 0 that is rotatably supported with respect to the housing 10, and a housing 1 that is coaxial with the input shaft 2 0.
  • An output shaft 30 that is rotatably supported with respect to 0, an input disk 21 that is formed integrally with the input shaft 20 and rotates, and an output shaft 30 that is integrally formed.
  • Output disk 3 1 as a driven rotating body that rotates in rotation, carrier 40 0, carrier 4 0 (support shaft 4 3 described later) that is rotatably connected around input shaft 20 and forms part of the load adjustment mechanism ) Rotating (spinning) with respect to the three rollers 50 and 5 that are supported freely.
  • the drive torque is transmitted by rotating the annular cam ring 60 and carrier 40 within a predetermined angle range.
  • The has an on Z off to the clutch mechanism 7 0 like.
  • the housing 10 is divided into two parts by an aluminum material or the like, and is fastened by a bolt (not shown) to define an accommodation space therein, and a bearing 11 is fitted therein. It is formed so as to define an annular groove 13 and the like for fitting the fitting hole 12 and the cam ring 60 to be fitted together so as to be non-rotatable around the axis L.
  • the input shaft 20 is supported by a housing 10 via a bearing 11 so as to be rotatable about the axis L and not to move in the direction of the axis L.
  • a disk-shaped input disk 21 is formed in a body. As shown in FIG.
  • the input disk 21 has a cylindrical contact surface 2 1 a with a radius R 2 1 on its outer periphery, and rotates together with the input shaft 20.
  • the output shaft 30 is supported by a housing 10 via a bearing 11 so as to be rotatable about the axis L and not to move in the direction of the axis L.
  • a disk-shaped output disk 31 is formed in a body.
  • the output disk 3 1 has a cylindrical contact surface 3 1 a with a radius R 3 1 on its outer periphery, and rotates integrally with the output shaft 30. .
  • the radius R 3 1 of the contact surface 3 1 a is set larger than the radius R 2 1 of the contact surface 2 1 a (R 3 1> R 2 1).
  • the carrier 40 is supported by the input shaft 20 so as to be rotatable around the axis L, and extends in the radial direction at intervals of approximately 120 degrees in the circumferential direction.
  • the arm portion 41, the extending portion 4 2 extending in the radial direction between the two arm portions 41, the support shaft 43 having the axis S and the like are respectively implanted in the arm portion 41.
  • the three spindles 4 3 each support a roller 50 so as to be rotatable. That is, the three central rollers 50 are arranged at substantially equal intervals in the circumferential direction.
  • the carrier 40 supports the three rollers 50 so as to be rotatable, and supports the periphery of the input shaft 20 so as to be capable of revolving.
  • the roller 50 rotates integrally with the input side roller 5 1 and the input side roller 5 1 that roll on the contact surface 2 1 a of the input disk 21 and outputs the same.
  • Side disk 3 1 contact surface 3 1
  • Output roller 5 2 rolling on a, input side roller 51 and output side roller 52 It is formed by a pressed roller 53 that receives a pressing force in contact with the surface 61.
  • the three rollers 50 are respectively supported by the support shafts 43 of the carrier 40 and are arranged around the axis L of the input shaft 20 at an interval of approximately 120 degrees, and the carrier 40 is predetermined. By rotating in this angular range, a planetary roller that revolves within a predetermined angular range while rotating is formed.
  • the tractive force F t can be obtained substantially uniformly in the circumferential direction, so that the power (rotational force) is more reliable. Is transmitted to.
  • the input side roller 51 has a cylindrical contact surface 5 1 a that has a radius R 51 on its outer periphery and contacts the contact surface 2 1 a of the input disk 21.
  • the output-side roller 52 has a cylindrical contact surface 5 2 a that has a radius R 52 on its outer periphery and contacts the contact surface 3 1 a of the output disk 31.
  • the radius R 52 of the contact surface 5 2 a is set to be smaller than the radius R 51 of the contact surface 51 a (R 5 2 ⁇ R 5 1).
  • the pressed roller 53 is a radial bearing type roller, and has a radius R 53 (not shown) on the outer periphery thereof and is in contact with the cam surface 6 1 of the cam ring 60. It has a cylindrical contact surface 5 3 a.
  • the radius R 5 3 of the contact surface 5 3 a is smaller than the radius R 5 1 of the contact surface 5 1 a and larger than the radius R 5 2 of the contact surface 5 2 a (R 5 2 and R 5 3 R 5 1) Set.
  • the pressed roller 53 is disposed between the input side roller 51 and the output side roller 52 in the axis S direction. Therefore, the pressing load exerted by the cam ring 60 (cam surface 6 1) is divided approximately evenly between the input roller 51 and the output roller 52 located on both sides of the pressed roller 53. Since normal loads F c and F c ′ are applied, contact between the contact surface 5 1 a and the contact surface 2 1 a and between the contact surface 5 2 a and the contact surface 3 1 a is prevented. As a result, stable rolling contact is obtained and functional reliability is improved.
  • the cam ring 60 has a disc-shaped contour having a predetermined thickness in the axis L direction, and is substantially equidistant in the circumferential direction on the inner side.
  • the pressed rollers 53 are formed in such a manner as to define three cam surfaces 61 that can be inscribed in rolling contact with each other.
  • the cam ring 60 is accommodated in the annular groove 13 of the housing 10 and is held by the pin 14 so as not to rotate but to be movable in the radial direction within a predetermined range.
  • the three cam surfaces 61 are cam profinoles that continuously change so that the distance from the rotation center P passing through the axis L is 1S Ha ⁇ Hb ⁇ Hc (Ha> Hb> Hc). ⁇ .
  • the curvature 1 ⁇ 1) demarcating the part of the region is formed so as to have a center at a position deviated by a predetermined amount from the rotation center P, and the curvature radii Re and Re 'at both ends are small.
  • the revolution of the pressed roller 53 that is, the roller 50
  • the cam surface 61 presses against the pressed roller 53 (that is, a normal load with respect to the input side roller 51 and the output side roller 52).
  • the pressure roller 53 moves as it moves in the VI direction.
  • the line load increases (the load that presses the pressed roller 53 toward the center P increases), while the normal load decreases as the pressed roller 53 moves in the V2 direction (centering on the pressed roller 53). (The load to be pushed closer to P is smaller.)
  • the three rollers 50 are supported so as to be rotatable and the carrier 40 is supported so as to be able to revolve around the input shaft 20.
  • Forced cam action to increase F c ', and formed so as to restrict the revolution of roller 50 to a predetermined angle range When the rotational speed of the output shaft 30 becomes slower than the value (predetermined value) set by the rotational speed of the input shaft 20 due to the cam ring 60 with the cam surface 61, etc., the delay is eliminated.
  • a load adjustment mechanism that automatically increases the normal load F c pressed against a is configured.
  • the clutch mechanism 70 must be switched between a state in which no normal load is applied (clutch off) and a state in which the normal load is applied (clutch on).
  • a connecting member connected to the extension part 42 of the carrier 40 so as to rotate within a predetermined angle range ⁇ 0 + ⁇ ( ⁇ is an angle that changes according to the load state of the output shaft 30, ⁇ 0) 7 1, formed by a drive source 7 2 provided in a housing 10 for reciprocating the connecting member 71.
  • the connecting member 7 1 includes a first connecting rod 7 1 a slidably supported on the housing 10, and an extended portion 4 2 of the carrier 40 (connecting hole 4 2 a) a second connecting rod 7 1 b slidably connected to the first connecting rod 7 1 b, a first connecting rod 7 1 a and a second connecting rod 7 1 b, and a coiled connecting spring 7 that exerts an urging force 1 c and so on.
  • the drive source 72 is a diaphragm type actuator.
  • the movable plate 7 2 a is connected to the first connection port 7 1 a, and the inertia is deformed by being sandwiched between the movable plates 7 2 a.
  • the first connection port 7 1 a directly contacts the second connection port 7 1 b while compressing and deforming the connection spring 7 1 c, and a constant pushing stroke is obtained. It ’s like that. Accordingly, the carrier 40 can be reliably rotated by a predetermined angle, and transmission of the drive torque can be reliably turned off (blocked) without depending on the urging force of the connection panel 71 c. .
  • connection panel 7 1 c between the first connection port 7 1 a and the second connection port 7 1 b, the angle range A in which the normal load is applied.
  • the movement of the carrier 40 can be allowed, and feed load control of the normal load can be performed reliably.
  • the clutch mechanism 70 is formed by the diaphragm-type actuator as the connecting member 71 connected to the carrier 40 and the drive source 72, so that the atmospheric pressure or the negative pressure is applied to the actuator. With simple pressure control that guides the clutch, the clutch can be switched on and off, and the clutch mechanism 70 can be easily configured.
  • the entire device can be simplified and miniaturized.
  • the transmission ratio ⁇ is a radius R 21 of the contact surface 21 a of the input disk 21, a radius R 51 of the contact surface 51 a of the input side roller 51, and an output side roller.
  • this power transmission device is provided as a reduction device that transmits the rotational force by reducing the rotational speed V i ⁇ of the input shaft 20 to the rotational speed Vo u t «V in).
  • the negative pressure Pm is guided to the actuator, the connecting member 71 is pulled outward, and the carrier 40 is at a predetermined stable angle 0 act position.
  • the pressed roller 53 contacts the cam surface 61 of the cam ring 60 and receives a pressing load, and the roller 50 (the input side roller 51 and the output side roller 52) has a predetermined stable normal load. Is applied, and the drive torque of the input shaft 20 is transmitted to the output shaft 30.
  • the side roller 52 also rotates in the other direction (C2 direction) at the speed Vr.
  • the output disk 31 and the output shaft 30 integrally rotate in one direction (C1 direction) at a speed Vout (predetermined value).
  • the pressed roller 5 3 of the roller 50 is positioned at a predetermined position on the cam surface 61 (for example, a region of H b with a wide gap) without revolving (Carrier 4
  • the roller 5 0 exerts the minimum normal load F c, F c ′ on the input disk 21 and the output disk 31.
  • the pressed roller 5 3 rolls on the cam surface 61 (revolving) and revolves in the opposite direction (that is, the carrier 40 becomes C 2 in FIG. 9). Rotate in the direction) and move to the Hb region with a wider gap. Then, the force surface 61 reduces the pressing load pressing the pressed roller 53, and the pressed roller 53 reduces the normal load of the input side roller 51 and the output side roller 52.
  • the cam ring 60 and the roller 50 are supported so as to rotate and revolve so that the normal load F c and F c ′ are always applied as much as possible rather than applying a normal load more than necessary.
  • the load adjustment mechanism consisting of the carrier 40 and the like feed-pack controls the normal loads F c and F c according to the fluctuation of the load torque of the output shaft 30, more normal load than necessary is applied.
  • the rotational force is reliably transmitted from the 20 input shafts to the output shaft 30, and the contact surfaces 3 la, 5 2 a, 5 1 a, 2 1 a are not fatigued or deteriorated. It is prevented and durability is improved.
  • a clutch mechanism that adjusts the normal load by operating a load adjustment mechanism (such as carrier 40) from the outside to turn on / off the transmission of drive torque from the input shaft 20 to the output shaft 30.
  • a load adjustment mechanism such as carrier 40
  • FIGS. 12 and 13 show another embodiment of the power transmission device according to the present invention.
  • the same components as those in the previous embodiment are denoted by the same reference numerals and description thereof is omitted. To do.
  • the carrier 40 is formed with a long hole 41a extending in the linear direction passing through the rotation center P in the arm 41, as shown in FIG. Pins 4 1 b are planted on both sides of the long hole 4 1 a.
  • the support shaft 4 3 ′ that rotatably supports the rotor 50 is supported so as to be movable along the long hole 41 a so as not to tilt.
  • the long hole 4 la moves the support shaft 4 3 of the roller 5 0 away from the contact surface 2 1 a of the input disk 2 1, that is, the contact surface 5 1 a of the input side roller 5 1 enters the input disk 2 1
  • the guide is directed in a direction away from the contact surface 2 1 a.
  • a torsion type spring 80 is externally fitted to the support shaft 4 3 ′, and both ends of the spring 80 are hooked to the pins 4 1 b to attach the support shaft 4 3, outward. I'm on the brink.
  • the panel 8 0 moves the support shaft 4 3 ′ of the roller 5 0 away from the contact surface 2 1 a of the input disk 2 1, that is, the contact surface 5 1 a of the input side roller 5 1 It is energized in the direction of separating from the contact surface 2 1 a.
  • the roller 50 (the input side roller 51) can move in the direction away from the contact surface 21a of the input disk 21 and has a biasing force in the direction away from the contact surface 21a. Supported by Carrier 40 in the exposed state.
  • FIG. 14 shows still another embodiment of the power transmission device according to the present invention.
  • the above-described implementation is performed except that the carrier 40 0 ′ and the clutch mechanism 70 0 ′ are changed. It has the same configuration as the form. Therefore, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
  • the carrier 40 0 ′ has three arms 4 1 ′ that extend in a cantilever shape in the circumferential direction and can be elastically deformed, as shown in FIG.
  • the A support shaft 4 3 is implanted at the free end of the arm 4 1 ′, and a roller 50 is rotatably supported.
  • the carrier 4 0 ′ has the roller 5 0 (pressed roller 5 3) moved to the cam surface 6 1 in a state where the arm 4 1 is elastically deformed inward in the radial direction (toward the center P). It is assembled so as to be inscribed in. That is, the roller 50 (the input side roller 5 1) is supported by the carrier 40 0 ′ in a state in which an urging force is exerted in a direction away from the contact surface 21 a of the input disk 21.
  • the clutch mechanism 70 is formed by a connecting member 7 1 ′, a drive source 7 2 ′ for reciprocating the connecting member 7 1, and the like.
  • the connecting member 7 1 includes a first connecting rod 7 1 a slidably supported by the housing 10, a second connecting rod 7 1 b similar to the above, and a connecting panel 7. 1 c, etc.
  • the first connecting port 7 1 a is a lead screw having a male screw formed on one end side.
  • the drive source 72 is a step motor that is fixed to the housing 10 and includes a rotor and a stator.
  • the rotor (not shown) is formed to have a female screw that is screwed into the male screw of the first connecting port 7 1 a and rotates at a predetermined position.
  • a DC motor having a rotor with a female screw together with a sensor for detecting the rotation amount or the rotation angle position may be adopted, or directly to the first connecting rod 7 1 a ′.
  • a linear motor that is connected and reciprocated may be used.
  • the drive source 7 2 ′ is a motor
  • the on / off state of the clutch can be switched easily by reciprocating the connecting member 7 1 simply by forward / reverse rotation or forward / reverse movement.
  • the load adjustment mechanism is constituted by the cam ring 60 fixed to the housing 10 and the carrier 40 0, 4 0 1, 4 0 ′ 'supporting the roller 50 so as to rotate and revolve freely.
  • the normal load that automatically presses the roller 50 against the contact surfaces 3 1 a and 2 1 a when the rotational speed of the output shaft 30 becomes lower than the predetermined value is automatically increased.
  • the power transmission device is a speed reduction device that reduces the rotational speed of the input shaft 20 and transmits it to the output shaft 30.
  • the power transmission device is not limited to this.
  • the present invention may be employed in a speed increasing device that increases the rotational speed and transmits it to the output shaft 30.
  • the annular cam ring 60 is shown as the cam member.
  • the present invention is not limited to this, and a method of fixing a plurality of cam members each having a cam surface to the housing 10. May be adopted.
  • rollers 50 and the three cam surfaces 61 have been described.
  • the present invention is not limited to this, and as long as functional reliability is ensured, one or Two rollers 50 and a cam surface 61 may be employed, or four or more rollers 50 and a cam surface 61 may be employed.
  • the clutch mechanism 7 0, 7 0 ′ The drive source 7 2, 7 2 consisting of the material 7 1, 7 1 ′ and diaphragm type actuator or motor is adopted, but the present invention is not limited to this, and the carriers 4 0, 4 0 ′, 4 0 are specified. Any other clutch mechanism can be used as long as it can be rotated within this angular range.
  • the diaphragm type actuator and motor are shown as the drive sources 7 2 and 7 2 ′ constituting the clutch mechanisms 70 and 70, but the invention is not limited to this.
  • Other drive sources may be employed as long as they are electromagnetic actuators that reciprocate the connecting members 7 1, 7 1 by force.
  • the pressed roller 53 is detached from the cam surface 61 in the clutch-off state, or the input side roller 51 is detached from the transversal surface 21a of the input disk 21.
  • the present invention is not limited to this configuration. Even when the pressed roller 53 is in contact with the cam surface 61, the normal load is zero or the transmission of the driving torque is interrupted. If so, it is included in the category of the clutch mechanism according to the present invention.
  • the load adjustment mechanism is adopted while achieving the simplification of the structure and the reduction of the manufacturing cost. Since the minimum normal load necessary to obtain a traction drive can be variably applied, wear or damage to the contact surface can be prevented, thus improving durability and reliably transmitting power. be able to.
  • the power transmission device of this effort makes it possible to simplify the structure and reduce the manufacturing cost while variably printing the minimum normal load to make contact surfaces.
  • As a general power machinery power transmission device it is possible to prevent wear or damage, improve durability, and at the same time turn on and off the drive torque transmission at the desired timing.
  • it is required to be reduced in size and weight, and is useful as a power transmission device such as a power mechanism for which maintenance-free operation is desired.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Ce dispositif de transmission électrique comprend un arbre d'entrée (20) et un disque d'entrée (21), un arbre de sortie (30) et un disque de sortie (31), des rouleaux (50) roulant en contact avec le disque d'entrée (21) et le disque de sortie (31) et un mécanisme de contrôle de charge constitué d'un vecteur (40) soutenant les rouleaux (50) par rotation et révolution et un anneau elliptique (60) ayant une face elliptique (61) pour augmenter automatiquement une charge normale pressant les rouleaux (50) contre les deux disques (21) et (31) lorsque la vitesse rotative de l'arbre de sortie (30) est inférieure à une valeur spécifiée. Ainsi, la structure du dispositif de transmission électrique peut être simplifiée, son coût de fabrication peut être abaissé, on peut fournir une force de traction stable puisqu'une charge normale minimum est appliquée dessus à tout moment et on peut augmenter sa durée de vie puisqu'une charge indue ne lui est pas appliquée.
PCT/JP2005/013680 2004-07-20 2005-07-20 Dispositif de transmission électrique WO2006009292A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004210890 2004-07-20
JP2004-210890 2004-07-20

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WO2006009292A1 true WO2006009292A1 (fr) 2006-01-26

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010103907A1 (fr) * 2009-03-07 2010-09-16 日産自動車株式会社 Engrenage à friction
WO2014006885A1 (fr) 2012-07-05 2014-01-09 日本曹達株式会社 Composé d'organosilicium, composition formant film mince l'utilisant, et film organique mince

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JP2002106662A (ja) * 2000-10-05 2002-04-10 Nsk Ltd 摩擦ローラ式変速機
JP2003049911A (ja) * 2001-05-28 2003-02-21 Nsk Ltd 摩擦ローラ式変速機

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US3287986A (en) * 1964-01-16 1966-11-29 Trw Inc Multiroller drive assembly and disengaging apparatus
JP2002106662A (ja) * 2000-10-05 2002-04-10 Nsk Ltd 摩擦ローラ式変速機
JP2003049911A (ja) * 2001-05-28 2003-02-21 Nsk Ltd 摩擦ローラ式変速機

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010103907A1 (fr) * 2009-03-07 2010-09-16 日産自動車株式会社 Engrenage à friction
JP2010209953A (ja) * 2009-03-07 2010-09-24 Nissan Motor Co Ltd 摩擦伝動装置
EP2405158A1 (fr) * 2009-03-07 2012-01-11 Nissan Motor Co., Ltd. Engrenage à friction
CN102341619A (zh) * 2009-03-07 2012-02-01 日产自动车株式会社 摩擦传动装置
EP2405158A4 (fr) * 2009-03-07 2012-06-20 Nissan Motor Engrenage à friction
US8944955B2 (en) 2009-03-07 2015-02-03 Nissan Motor Co., Ltd. Friction gearing
WO2014006885A1 (fr) 2012-07-05 2014-01-09 日本曹達株式会社 Composé d'organosilicium, composition formant film mince l'utilisant, et film organique mince

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