WO2012049762A1 - 振動減衰装置 - Google Patents
振動減衰装置 Download PDFInfo
- Publication number
- WO2012049762A1 WO2012049762A1 PCT/JP2010/068109 JP2010068109W WO2012049762A1 WO 2012049762 A1 WO2012049762 A1 WO 2012049762A1 JP 2010068109 W JP2010068109 W JP 2010068109W WO 2012049762 A1 WO2012049762 A1 WO 2012049762A1
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- WO
- WIPO (PCT)
- Prior art keywords
- driven
- side impeller
- impeller
- direct coupling
- rolling
- Prior art date
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0252—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a damper arranged on input side of the lock-up clutch
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2128—Damping using swinging masses, e.g., pendulum type, etc.
Definitions
- the present invention relates to an apparatus for attenuating torsional vibrations, and more particularly to a vibration damping apparatus having a configuration in which a rotating body that is rotatable relative to the rotating body is housed inside a rotating body that receives torque and rotates. It is about.
- Rotating bodies such as drive shafts and gears for transmitting the torque generated by the power source to the target location or member are caused by fluctuations in the input torque itself, fluctuations in the load, friction, etc. Inevitably vibrates. The frequency of the vibration changes according to the number of rotations, and a higher-order vibration higher than the secondary vibration is also generated. Therefore, the amplitude becomes large due to resonance, which may cause noise and durability deterioration. is there. For this reason, devices or mechanisms for preventing vibration as described above are widely used in various devices that transmit power by rotation. Examples thereof are described in JP-A-7-280037 and JP-A-2000-297843.
- a vibration absorber described in Japanese Patent Application Laid-Open No. 7-280037 includes a rolling chamber formed in a portion on the outer peripheral side of a rotating body such as a flywheel, and a ball or roller (not shown) that is rotatably accommodated therein.
- a rolling chamber formed in a portion on the outer peripheral side of a rotating body such as a flywheel, and a ball or roller (not shown) that is rotatably accommodated therein.
- the rolling element resonates with the torsional vibration and rolls inside the rolling chamber, and the dynamic vibration absorption action causes the torsional vibration to occur. It is configured to absorb.
- an accommodation chamber for movably accommodating a rolling mass is formed on the outer periphery of the hub, and the rolling mass has a larger diameter elastomer.
- the rolling mass When the centrifugal force acting on the rolling mass is small, that is, when the hub rotation speed is low, the rolling mass is held away from the inner peripheral wall of the storage chamber by the elastomer. On the other hand, when the rotational speed of the hub increases and the centrifugal force increases, the elastomer is compressed and the rolling mass contacts the inner peripheral wall of the storage chamber and moves along the inner peripheral wall. Is configured to do.
- Japanese Patent Laid-Open No. 7-280037 discloses a vibration absorber in which a rolling element having an outer diameter smaller than the radius of the rolling chamber is disposed inside a circular rolling chamber, and a V-shaped guide having a large opening angle.
- a member is rotatably provided at the center of the rolling chamber, and a rolling element is held between the guide member and the inner peripheral wall of the rolling chamber. Therefore, when a large torsional vibration occurs, the rolling element rotates together with the guide member, so that the vibration is suppressed, and at a low rotational speed, the rolling element is interposed between the guide member and the inner peripheral wall of the rolling chamber. Since it is held, it is said that abnormal noise and fine vibration are prevented.
- the dynamic damper described in Japanese Patent Laid-Open No. 2000-297843 has an elastomer interposed between the rolling mass and the inner wall surface of the storage chamber, so that torque is transmitted via the elastomer, so that the vibration damping capability
- the elastic force of the elastomer is set so that maintaining the rolling mass away from the inner peripheral wall of the containment chamber at a low rotational speed is compatible with attenuating the vibration of the target frequency. It may be difficult to perform, or the elastomer may deteriorate over time, and abnormal noise may be generated or vibration damping characteristics may be changed.
- the present invention has been made by paying attention to the above technical problem, and provides a vibration damping device that is simple in configuration and excellent in vibration damping capability by effectively utilizing existing members or functions. It is the purpose.
- the present invention connects the driving side impeller and the driven side impeller operated by the fluid pressure and the driving side impeller that generates the fluid flow and the driven side impeller that is driven by the fluid flow.
- a vibration transmission device that attenuates torsional vibration of the driven-side impeller or a rotating member that rotates integrally with the driven-side impeller in a fluid transmission device including a direct coupling clutch that rotates together with the driven-side impeller A rolling chamber, a rolling element housed in the rolling chamber in the same direction as the rotation direction of the driven impeller and relatively rotatable with respect to the driven impeller, and the direct clutch is operated in a released state. It is operated by fluid pressure so as to fix the rolling element in the rolling chamber and to operate the direct coupling clutch in an engaged state. That a movable member for releasing fixation of the rolling element operating Te is characterized in.
- the direct coupling clutch is disposed inside the fluid transmission device so as to move back and forth in a direction parallel to a rotation center axis of the driving side impeller and the driven side impeller.
- a housing in which a moving chamber is formed is arranged so as to face the direct coupling clutch and rotate integrally with the driven impeller, and the movable member is opposed to the direct coupling clutch and includes a rolling chamber.
- a vibration damping device having a side surface and connected to the direct coupling clutch.
- the drive side impeller and the driven side impeller are disposed on the same axis so as to face each other, and a cover member that covers an outer peripheral side of the driven side impeller is provided on the drive side impeller.
- the direct coupling clutch is disposed between the driven impeller and the cover member so as to face the inner surface of the cover member and on the same axis as the driven impeller.
- a fluid pressure is applied between the driven side impeller and the direct coupling clutch on the same axis as the driven side impeller and the direct coupling clutch and presses the direct coupling clutch against the inner surface of the cover member.
- the movable member is configured to move to the inner surface side of the cover member together with the direct coupling clutch to release the fixing of the rolling element. It is a vibration damping device according to claim is.
- the drive side impeller and the driven side impeller are disposed on the same axis so as to face each other, and a cover member that covers an outer peripheral side of the driven side impeller is provided on the drive side impeller.
- the direct coupling clutch is disposed between the driven impeller and the cover member so as to face the inner surface of the cover member and on the same axis as the driven impeller.
- a housing formed inside is arranged to rotate integrally with the driven-side impeller inside the cover member, and the movable member forms one side surface of the rolling chamber, and the direct coupling clutch is The direction in which the movable member releases the fixing of the rolling element by the fluid pressure when the fluid pressure is applied to the inner surface of the cover member to be engaged. That it is configured to move to a vibration damping apparatus according to claim.
- this invention is the vibration damping device according to any one of the above inventions, wherein a surface of the movable member that presses the rolling element is formed by a high friction member.
- the direct coupling clutch when the input rotational speed of the fluid transmission device is relatively low, or when the input torque is large, the direct coupling clutch is controlled to be in a released state in order to reduce the vibration by utilizing the buffer action by the fluid. Is done.
- the movable member is operated by the fluid pressure that sets the direct coupling clutch in the released state, and the rolling element is fixed by the movable member.
- the free movement of the rolling elements within the rolling chamber is restricted, so that it is possible to prevent or suppress such a situation that the rolling element comes into contact with the inner surface of the rolling chamber, or abnormal noise is generated accordingly.
- the rolling element can be reliably fixed.
- the direct coupling clutch is set to the engaged state.
- the movable member is operated by the fluid pressure, and the movable member moves so as to release the fixed rolling element.
- the rolling element can move freely inside the rolling chamber. Therefore, if torsional vibration occurs in the driven impeller or a member integrally connected thereto, the rolling element is relatively moved inside the rolling chamber. The torsional vibration is absorbed and damped by such relative movement of the rolling elements. That is, when the rotational speed increases, the damper function is exhibited.
- a part of the rolling chamber is constituted by a movable member, and fixing of the rolling element by moving the movable member and release of the fixing are performed by fluid pressure that engages or releases the direct coupling clutch. It can be configured by changing the structure of the rolling chamber, and there is no need to add a new component. As a result, according to the present invention, it is possible to obtain a vibration damping device having a simple configuration and excellent vibration damping capability.
- FIG. 4 is an enlarged view of a portion IV in FIG. 3.
- the vibration damping device is a so-called pendulum type, and a rotating body corresponding to a weight capable of moving freely relative to the rotating body is provided on the rotating body that receives torque and rotates. It is made to hold.
- the vibration damping device can be configured to be provided inside the fluid transmission device, and in particular, provided in the fluid transmission device including the direct coupling clutch (lock-up clutch), the pressure for releasing the direct coupling clutch is set.
- the rolling elements are fixed by using them, and the rolling elements are unfixed by using a pressure for engaging the direct clutch.
- FIG. 1 shows an example in which a vibration damping device is provided inside a torque converter 1 which is a fluid power transmission device having a torque amplifying function.
- the torque converter 1 shown here is similar to a torque converter widely installed in conventional vehicles. It has the composition of. That is, the pump impeller 2 that is a member on the input side is configured by attaching the pump blades 3 arranged in an annular shape to the inner surface of the pump shell 4, and the turbine runner 5 is disposed facing the pump impeller 2. Yes.
- the turbine runner 5 has a shape that is substantially symmetric with the pump impeller 2 and is configured by fixing a large number of annularly arranged turbine blades on the inner surface of an annular (or semi-doughnut-shaped) shell. ing. Accordingly, the pump impeller 2 and the turbine runner 5 are arranged to face each other on the same axis.
- the front cover 6 covering the outer peripheral side of the turbine runner 5 is integrally joined to the outer peripheral end of the pump shell 4.
- the front cover 6 is a so-called bottomed cylindrical member having a front wall surface facing the inner surface of the pump shell 4, and a shaft portion 7 is formed at the center of the outer surface of the front wall.
- the shaft portion 7 is formed so as to protrude, and is inserted into a tip portion of a crankshaft 8 of an engine (not shown), and is connected to the crankshaft 8 via a bearing 9 so as to be relatively rotatable.
- a drive plate 10 is attached to the crankshaft 8, and the drive plate 10 and the front cover 6 are connected via a damper 11.
- a cylindrical shaft 12 is integrally provided at the inner peripheral end of the pump shell 4, and the cylindrical shaft 12 extends to the back side of the pump shell 4 (the side opposite to the engine side). Not connected to the oil pump.
- a fixed shaft 13 having an outer diameter smaller than the inner diameter of the cylindrical shaft 12 is inserted into the cylindrical shaft 12, and a tip portion of the torque converter 1 surrounded by the pump shell 4 and the front cover 6 is inserted. It extends to the inside.
- the fixed shaft 13 is a hollow shaft-shaped part formed integrally with a fixed wall (not shown) that holds the oil pump, and is formed between the outer peripheral surface of the fixed shaft 13 and the inner peripheral surface of the cylindrical shaft 12.
- the space is a fluid flow path (that is, an oil path) 14.
- the distal end portion of the fixed shaft 13 is located on the inner peripheral side of the turbine runner 5 described above or on the inner peripheral side of the portion between the pump impeller 2 and the turbine runner 5.
- the inner race of the clutch 15 is spline-fitted.
- a stator 16 disposed between the inner peripheral portion of the pump impeller 2 and the inner peripheral portion of the turbine runner 5 facing the outer periphery of the one-way clutch 15 is attached. That is, in a state where the speed ratio between the pump impeller 2 and the turbine runner 5 is small, the rotation of the stator 16 is prevented by the one-way clutch 15 even if the oil flowing out from the turbine runner 5 acts on the stator 16. In the state where oil is fed to the pump impeller 2 by changing the flow direction of the oil and the speed ratio is large and the oil strikes the so-called back surface of the stator 16, the stator 16 is rotated so as not to disturb the oil flow. It is configured.
- an output shaft (input shaft of a transmission not shown) 17 is rotatably inserted, and the tip portion protrudes (beyons) the tip portion of the fixed shaft 13.
- a hub shaft 18 is spline-fitted to the outer periphery of the front end of the front cover 6 that extends near the inner surface of the front cover 6 and protrudes from the fixed shaft 13.
- the hub shaft 18 is formed with a flange-shaped hub 19 projecting to the outer peripheral side, and the above-described turbine runner 5 is connected to the hub 19 so as to be integrated with the hub 19.
- a damper housing 20 is integrally provided on the hub shaft 18.
- the damper housing 20 constitutes a part of the vibration damping device according to the present invention, and includes an annular hollow portion along the rear surface (side surface on the front cover 6 side) of the turbine runner 5, and the hollow portion as a hub. And a flange-like portion connected to the shaft 18.
- the hollow portion has a rectangular cross section with a shallow depth measured in the axial direction, and is a circular portion as a whole, and a so-called main body portion 21 that opens to the front cover 6 side, It is comprised by the cover part 23 engage
- the damper housing 20 and a member that rotates integrally with the damper housing 20 correspond to the rotating body in the present invention.
- the inner surface of the hollow part is formed as a curved surface whose outer peripheral surface continuously changes in the radial direction to be uneven, and the inner peripheral surface is a simple arc surface.
- a portion partitioned by a portion where the distance between the outer peripheral surface and the inner peripheral surface is narrow is the rolling chamber 24.
- rolling elements 25 that are movable in the rotational direction of the turbine runner 5 are accommodated.
- the rolling element 25 is a disk-shaped weight as an example, and the outer diameter thereof is smaller than the maximum distance between the outer peripheral surface and the inner peripheral surface forming the rolling chamber 24 and is rolling. It is set larger than the minimum interval on both sides of the chamber 24.
- each rolling element 25 is configured to be movable in the left-right direction in FIG. 2 inside each rolling chamber 24.
- the outer peripheral surface of each rolling chamber 24 is a surface that contacts when the rolling element 25 receives centrifugal force and moves along the rolling element 25, and therefore, its central portion is the starting point.
- the left and right side surfaces are configured as, for example, toroidal surfaces.
- the lid portion 23 corresponds to a movable member in the present invention, and in a state where the lid portion 23 is moved to the opening end side of the hollow portion, the lid portion 23 is separated from the rolling element 25, and in a state where the lid portion 23 is pushed into the hollow portion, The rolling element 25 is sandwiched between the bottom surface of the hollow portion and the rolling element 25 is fixed.
- the inner surface (the left side surface in FIG. 1) 23A of the lid portion 23 is formed by a high friction member such as a rough surface or a non-slip film. Yes.
- a lock-up clutch (direct coupling clutch) 26 is provided between the damper housing 20 and the front cover 6.
- the lock-up clutch 26 is for transmitting torque between the driving side member and the driven side member without passing through a fluid, as is conventionally known, and is an example shown in FIG.
- the hub shaft 18 and the front cover 6 are connected to each other. That is, the lock-up clutch 26 is mainly composed of a disk-shaped lock-up piston 27 disposed between the vibration damping device and the inner surface of the front cover 6, and the lock-up piston 27 is composed of the hub shaft described above. 18 is spline-fitted so as to be movable in the axial direction and integrated with the hub shaft 18 in the rotational direction.
- a friction material 28 that is pressed against the front cover 6 and generates a frictional force is attached to the outer peripheral side of the side surface of the lockup piston 27 that faces the front cover 6 as much as possible.
- the outer diameter of the lock-up piston 27 is an outer diameter that is slightly smaller than the inner diameter of the front cover 6, and the outer peripheral end thereof extends in the axial direction along the inner peripheral surface of the front cover 6. A cylindrical portion 29 is formed. Accordingly, the lock-up piston 27 is pushed in the right direction in FIG. 1 and the friction material 28 comes into contact with the front cover 6 to be in an engaged state so that torque is transmitted between the front cover 6 and the hub shaft 18. Further, the friction material 28 is separated from the front cover 6 by being pushed back to the left in FIG.
- the lid portion 23 which is a movable member, is connected to the back surface of the lockup piston 27 (the surface opposite to the surface on which the friction material 28 is attached). That is, the lid portion 23 is configured to move back and forth in the axial direction together with the lockup piston 27.
- the output shaft 17 described above is formed with an oil passage 30 along its central axis.
- the oil passage 30 opens at the tip of the output shaft 17. Further, there is a slight gap between the inner surface of the front cover 6 and the lock-up piston 27, and therefore the oil passage 30 is opened and communicated with the gap.
- the oil path 14 between the cylindrical shaft 12 and the fixed shaft 13 described above communicates with a portion on the back side of the lockup piston 27, that is, a portion in which the turbine runner 5 is accommodated.
- the hydraulic pressure of the engagement oil passage 14 is reduced to that of the release oil passage 30.
- the pressure on the back side of the lock-up piston 27 becomes higher than the pressure between the lock-up piston 27 and the pressure between the front cover 6 and as a result, the lock-up piston 27 is pushed to the front cover 6 side. It is pressed against the inner surface of the cover 6. That is, the lockup clutch 26 is engaged.
- the lock-up piston 27 moves in this manner, the lid 23 in the vibration damping device moves in the right direction in FIG. 1, so that the pinching of the rolling elements 25 is released.
- the engagement / release control is a map in which the engagement region is defined by parameters indicating the vehicle running state such as the vehicle speed and the accelerator opening.
- the control is executed by controlling the oil pressure of the oil passages 14 and 30 or the supply / discharge of the oil pressure based on the map, and the control is the same as the conventional control executed in the vehicle. It's okay.
- the lock-up clutch 26 is controlled to be in a released state in order to reduce vehicle body vibration, booming noise, and the like. Specifically, the hydraulic pressure supplied from the release oil passage 30 is increased, and as a result, the hydraulic pressure on the front cover 6 side with the lock-up piston 27 interposed therebetween is changed to the pressure on the turbine runner 5 side opposite thereto. It becomes higher and the lockup piston 27 is pushed away from the inner surface of the front cover 6. Thus, the friction material 28 attached to the lock-up piston 27 is separated from the inner surface of the front cover 6, and the transmission of torque between the two is interrupted. That is, the lockup clutch 26 is released.
- the pump impeller 2 rotates together with the front cover 6 to generate a spiral flow of oil.
- the oil is supplied to the turbine runner 5 from the outer peripheral side of the pump blade 3, and the turbine runner 5 is rotated by the kinetic energy of the oil. In this way, power is transmitted from the drive-side pump impeller 2 to the driven-side turbine runner 5.
- the turbine runner 5 and the above-described damper housing 20 are integrated via the hub shaft 18, power is transmitted from the turbine runner 5 to the output shaft 17 and output, and the damper housing 20 is connected to the turbine runner 5. Rotate with.
- the rolling elements 25 housed in the rolling chamber 24 inside the damper housing 20 are fixed to the inner surface of the rolling chamber 24. It is prevented or suppressed in advance that the moving body 25 comes into contact with the inner surface of the rolling chamber 24 and abnormal noise is generated accordingly.
- the lockup clutch 26 is engaged. Specifically, the hydraulic pressure supplied from the above-described engagement oil passage 14 is increased or the hydraulic pressure of the release oil passage 30 is decreased, and as a result, the turbine runner 5 is disposed with the lock-up piston 27 interposed therebetween. The hydraulic pressure on the applied side becomes higher than the hydraulic pressure on the front cover 6 side, and the lockup piston 27 is pushed toward the front cover 6 by the hydraulic pressure difference.
- the lid 23 moves together with the lock-up piston 27 in the right direction in FIG. 1, that is, in the direction in which the width or volume of the rolling chamber 24 is increased. For this reason, the load that presses the rolling element 25 against the inner surface of the rolling chamber 24 does not act, so the fixing of the rolling element 25 is released. Therefore, when the reciprocating motion in the rotational direction occurs in the turbine runner 5 or the damper housing 20 integrated with the turbine runner 5 due to torsional vibration, the rolling element 25 moves relative to the damper housing 20 with a delay in the rolling chamber 24. Torsional vibration is attenuated by such relative movement of the rolling elements 25.
- the rolling element 25 is fixed inside the rolling chamber 24, so that the generation of abnormal noise can be prevented or suppressed, and the rotational speed.
- the fixing of the rolling element 25 is released by the lock-up hydraulic pressure, and the vibration damping action by the rolling element 25 can be caused.
- the rolling chamber 24 is sealed in an airtight state by the sealing material 22, and air at about atmospheric pressure is sealed therein. Accordingly, when the lid portion 23 moves into the rolling chamber 24, the internal pressure of the rolling chamber 24 increases, but the hydraulic pressure for releasing the lock-up clutch 26 is higher than the internal pressure of the rolling chamber 24.
- a part of the rolling chamber 24 is configured by the lid portion 23 that is a movable member, and the rolling body 25 is fixed by moving the lid portion 23 and the fixing thereof. Is released by fluid pressure that engages or releases the lock-up clutch 26, so that it is not necessary to add a new component by changing the structure of the rolling chamber 24. As a result, a vibration damping device having a simple configuration and excellent vibration damping capability can be obtained.
- FIGS. 3 and 4 The specific example described above is an example in which the engagement hydraulic pressure and the release hydraulic pressure of the lock-up clutch 26 are applied to the lid portion 23 that is a movable member via the lock-up piston 27.
- the present invention is not limited to this specific example, and the engagement hydraulic pressure and the release hydraulic pressure can be directly applied to the movable member. Examples are shown in FIGS. 3 and 4.
- FIG. 3 and FIG. 4 the same reference numerals as those in FIG. 1 and FIG.
- a space portion partitioned in an airtight state is formed on the back side of the turbine runner 5 (the surface side opposite to the surface on which the turbine blades are attached), and a rolling chamber is formed therein. 24, the rolling element 25, or a movable member is accommodated.
- the damper housing 201 integrated with the hub shaft 18 includes a fixed side wall portion 202 extending radially outward along the back surface of the lockup piston 27, and an outer peripheral end of the fixed side wall portion 202. And a cylindrical portion 203 that extends toward the turbine runner 5 and is joined to the rear surface of the turbine runner 5. A boss portion 204 that slightly protrudes toward the turbine runner 5 side is formed at an intermediate portion in the radial direction of the fixed side wall portion 202.
- a movable side wall portion 205 that is disposed to face the fixed side wall portion 202 and forms the rolling chamber 24 together with the fixed side wall portion 202 and the cylindrical portion 203 is provided.
- the movable side wall portion 205 is a plate-like member having an overall outer diameter that is about the inner diameter of the cylindrical portion 203 integral with the fixed side wall portion 202 and is slightly smaller than the outer diameter of the hub 19.
- the intermediate portion is bent so as to form a cylindrical portion 206 having an outer diameter smaller than the inner diameter of the boss portion 204.
- the outer peripheral end of the movable side wall portion 205 is slidably in contact with the inner peripheral surface of the cylindrical portion 203 integral with the fixed side wall portion 202 via the sealing material 207, and the cylindrical portion 206 of the movable side wall portion 205 is The inner wall of the boss 204 formed on the fixed side wall 202 is slidably in contact with the sealant 208. In this way, the rolling chamber 24 that is kept airtight by the sealing materials 207 and 208 is formed between the fixed side wall portion 202 and the movable side wall portion 205.
- the inner peripheral end of the movable side wall portion 205 is slidably in contact with the outer peripheral surface of the boss portion 209 formed on the hub 19 so as to protrude toward the fixed side wall portion 202 via the sealing material 210, and thus the movable side wall portion. 205 is supported by the boss portion 209 on the inner peripheral side. That is, the space between the rear surface of the turbine runner 5 and the movable side wall 205 is maintained in an airtight state by the sealing materials 207 and 210 described above, and air at about atmospheric pressure is contained in the space.
- the movable side wall portion 205 corresponds to the movable member in the present invention, and an oil passage for applying the engagement pressure of the lockup clutch 26 to the movable side wall portion 205 is formed. That is, a portion of the movable side wall portion 205 that is on the inner peripheral side of the cylindrical portion 206 and that faces the fixed side wall portion 202 in the movable side wall portion 205 is airtight by the sealing materials 207, 208, and 210 described above. It is exposed to the part other than the space part maintained in the.
- a through hole 211 is formed in a portion on the inner peripheral side of the fixed side wall portion 202 so as to guide the oil pressure to the so-called exposed portion (or pressure receiving surface).
- FIG. 4 shows an enlarged portion of the through hole 211.
- another through-hole 212 is formed in the inner peripheral side portion of the hub 19, and so-called engagement pressure is introduced from a location where the one-way clutch 15 is disposed.
- the movable side wall portion 205 and the fixed side wall portion 205 are attracted to the fixed side wall portion 202 side so that the movable side wall portion 205 assists the load that sandwiches the rolling element 25 between the fixed side wall portion 202 and the movable side wall portion 205.
- a tension spring 213 may be provided between the first spring 202 and the second spring 202.
- the mutually opposing inner surfaces of the movable side wall portion 205 and the fixed side wall portion 202 function to fix the rolling element 25, at least one of these inner surfaces may be formed by a high friction member.
- the vibration damping device configured as shown in FIGS. 3 and 4, when hydraulic pressure is supplied so as to engage the lockup clutch 26, the hydraulic pressure passes through the through holes 211 and 212 described above, and the movable side wall. It acts on the pressure receiving surface in the portion 205. As a result, the movable side wall 205 moves in a direction away from the fixed side wall 202 (leftward in FIG. 3), so that the distance between the movable side wall 205 and the fixed side wall 202 increases, and the rolling element 25 is released from being fixed. Is done. That is, the rolling element 25 functions to attenuate torsional vibrations by moving in the rolling chamber 24.
- the lockup clutch 26 when the lockup clutch 26 is released due to an increase in engine load or the like, the above-described so-called engagement pressure does not act on the movable side wall portion 205, so the movable side wall portion 205 moves toward the fixed side wall portion 202.
- the rolling element 25 moves and is fixed by being sandwiched between the movable side wall portion 205 and the fixed side wall portion 202. Therefore, even if a temporary fluctuation occurs in the rotational speed of the turbine runner 5, the rolling element 25 does not move in the rolling chamber 24, so that it is possible to avoid or suppress a situation such as abnormal noise.
- the configuration can be simplified and the necessary vibration damping function can be exhibited.
- the present invention can be applied to a fluid transmission device having a drive-side impeller, a driven-side impeller, and a direct coupling clutch.
- the fluid transmission device according to the present invention is other than the above-described torque converter having a torque amplifying effect.
- the fluid transmission device may be used.
- the movable member only needs to be configured to operate by hydraulic pressure that engages the direct coupling clutch to release the fixed rolling element. Therefore, the rolling element, the rolling chamber, or the movable member is incorporated in the fluid transmission device. It does not have to be.
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
Description
Claims (5)
- 流体流を生じさせる駆動側インペラとその流体流によって駆動される従動側インペラと流体圧によって動作させられて前記駆動側インペラおよび従動側インペラを連結する直結クラッチとを備えた流体伝動装置における前記従動側インペラもしくは前記従動側インペラと一体となって回転する回転部材の捩り振動を減衰する振動減衰装置において、
前記従動側インペラと一体となって回転する転動室と、
その転動室内に前記従動側インペラの回転方向と同方向でかつ前記従動側インペラに対して相対回転可能に収容された転動体と、
前記直結クラッチを解放状態に動作させる流体圧によって動作して前記転動体を前記転動室内に固定し、かつ前記直結クラッチを係合状態に動作させる流体圧によって動作して前記転動体の固定を解除する可動部材と
を備えていることを特徴とする振動減衰装置。 - 前記直結クラッチは、前記流体伝動装置の内部に前記駆動側インペラおよび従動側インペラの回転中心軸線と平行な方向に前後動するように配置され、
前記転動室が内部に形成されたハウジングがその直結クラッチに対向しかつ前記従動側インペラと一体となって回転するように配置され、
前記可動部材は、前記直結クラッチに対向するとともに前記転動室の側面を形成しかつ前記直結クラッチに連結されている
ことを特徴とする請求項1に記載の振動減衰装置。 - 前記駆動側インペラと従動側インペラとが互いに対向して同一軸線上に配置されるとともに、前記従動側インペラの外周側を覆うカバー部材が前記駆動側インペラと一体化して設けられ、
前記直結クラッチは、前記従動側インペラと前記カバー部材との間で前記カバー部材の内面に対向しかつ前記従動側インペラと同一軸線上に配置され、
前記ハウジングは、前記従動側インペラと前記直結クラッチとの間に前記従動側インペラおよび直結クラッチと同一軸線上に配置され、
前記直結クラッチを前記カバー部材の内面に押し付けて係合状態とする流体圧が作用している場合に、前記可動部材が前記直結クラッチと共に前記カバー部材の内面側に移動して前記転動体の固定を解除するように構成されていることを特徴とする請求項2に記載の振動減衰装置。 - 前記駆動側インペラと従動側インペラとが互いに対向して同一軸線上に配置されるとともに、前記従動側インペラの外周側を覆うカバー部材が前記駆動側インペラと一体化して設けられ、
前記直結クラッチは、前記従動側インペラと前記カバー部材との間で前記カバー部材の内面に対向しかつ前記従動側インペラと同一軸線上に配置され、
前記転動室が内部に形成されたハウジングが前記カバー部材の内部に前記従動側インペラと一体となって回転するように配置され、
前記可動部材は、その転動室の一つの側面を形成し、
前記直結クラッチを前記カバー部材の内面に押し付けて係合状態とする流体圧が作用している場合に、前記可動部材がその流体圧によって前記転動体の固定を解除する方向に移動するように構成されていることを特徴とする請求項1に記載の振動減衰装置。 - 前記可動部材の前記転動体を押圧する面は、高摩擦部材によって形成されていることを特徴とする請求項1ないし4のいずれかに記載の振動減衰装置。
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CN201080002779.0A CN102575744B (zh) | 2010-10-15 | 2010-10-15 | 振动衰减装置 |
JP2011512339A JP5177288B2 (ja) | 2010-10-15 | 2010-10-15 | 振動減衰装置 |
DE112010005938.1T DE112010005938B4 (de) | 2010-10-15 | 2010-10-15 | Schwingungsdämpfvorrichtung |
US13/119,357 US8708116B2 (en) | 2010-10-15 | 2010-10-15 | Vibration damping device |
PCT/JP2010/068109 WO2012049762A1 (ja) | 2010-10-15 | 2010-10-15 | 振動減衰装置 |
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US (1) | US8708116B2 (ja) |
JP (1) | JP5177288B2 (ja) |
CN (1) | CN102575744B (ja) |
DE (1) | DE112010005938B4 (ja) |
WO (1) | WO2012049762A1 (ja) |
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JPWO2012049762A1 (ja) | 2014-02-24 |
US20130186724A1 (en) | 2013-07-25 |
DE112010005938T5 (de) | 2013-10-02 |
CN102575744A (zh) | 2012-07-11 |
DE112010005938B4 (de) | 2015-11-19 |
US8708116B2 (en) | 2014-04-29 |
DE112010005938T8 (de) | 2014-02-06 |
CN102575744B (zh) | 2014-01-22 |
JP5177288B2 (ja) | 2013-04-03 |
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