JP5051447B2 - Fluid transmission device - Google Patents

Fluid transmission device Download PDF

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JP5051447B2
JP5051447B2 JP2007285315A JP2007285315A JP5051447B2 JP 5051447 B2 JP5051447 B2 JP 5051447B2 JP 2007285315 A JP2007285315 A JP 2007285315A JP 2007285315 A JP2007285315 A JP 2007285315A JP 5051447 B2 JP5051447 B2 JP 5051447B2
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mass
turbine runner
inertial mass
elastic
vibration
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JP2009115112A (en
Inventor
義崇 三島
義裕 吉村
智彦 土屋
坪井  彰
浩也 安部
康浩 森本
友彦 薄井
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本田技研工業株式会社
株式会社エフ・シー・シー
株式会社ユタカ技研
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0205Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations 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
    • F16H2045/0226Combinations 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
    • F16H2045/0231Combinations 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 arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273Combinations 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
    • F16H2045/0278Combinations 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 comprising only two co-acting friction surfaces

Description

  The present invention relates to a fluid transmission device that transmits rotational power between a drive shaft and a driven shaft via a fluid, and more specifically, increases the transmission efficiency of rotational power by directly connecting the drive shaft and the driven shaft. The present invention relates to a fluid transmission device provided with a lockup mechanism capable of operating.

  A fluid transmission device is a device that converts rotational power input to a drive shaft into kinetic energy of a fluid, and then converts it to rotational power again and transmits it to a driven shaft. Such a fluid transmission device typically includes a pump impeller coupled to a drive shaft via a cover, and a turbine runner coupled to a driven shaft via a turbine hub. The pump impeller and the turbine runner are disposed to face each other in the internal space of the cover, and a fluid circulation path is formed therebetween. The pump impeller rotates with the drive shaft to feed fluid to the circulation path, and the fed fluid circulates in the circulation path while rotating the turbine runner. Thereby, rotational power is transmitted to the driven shaft.

  As one type of such a fluid transmission device, a torque converter that amplifies torque at the time of power transmission from a drive shaft to a driven shaft is known and used in vehicles such as automobiles. Such a torque converter typically includes a stator that is provided between the pump impeller and the turbine runner and converts the direction of the fluid flow, and the torque is amplified by the conversion action of the stator flow. In the torque converter for a vehicle, the crankshaft of the engine corresponds to the drive shaft, and the input shaft of the transmission corresponds to the driven shaft.

  In the torque converter for a vehicle, a clutch is provided between the cover and the turbine runner, and by connecting the clutch, the crankshaft of the engine and the input shaft of the transmission are directly connected to enable high-efficiency power transmission. One having a lock-up mechanism is known. Here, when the crankshaft and the input shaft are directly connected without passing through the fluid, the torsional vibration of the crankshaft excited by the rotational fluctuation of the engine is directly transmitted to the input shaft.

  Therefore, a torque converter having a lock-up mechanism generally includes a damper mechanism that attenuates torsional vibration transmitted from the crankshaft to the input shaft. Conventional damper mechanisms typically include a plurality of coil springs arranged side by side in the circumferential direction, with one end of each coil spring engaging a clutch and the other end engaging a turbine runner or input shaft. Is configured. Furthermore, a damper mechanism has also been proposed in which a vibration system including a mass element and a coil spring and having a degree of freedom in the rotation direction is added between the clutch and the input shaft (see, for example, Patent Document 1).

In the fluid transmission device disclosed in Patent Document 1, the damper mechanism includes a plurality of coil springs arranged in two rows in the circumferential direction on the outer peripheral side and the inner peripheral side, And an intermediate transmission element interposed between the coil springs on the circumferential side. The intermediate transmission element is connected to the clutch via a coil spring on the outer peripheral side, and is connected to the input shaft via a coil spring on the inner peripheral side. That is, a vibration system that includes an intermediate transmission element and a coil spring and has a degree of freedom in the rotational direction is added between the clutch and the input shaft. A turbine runner is joined to the intermediate transmission element by fixing means such as welding, and the turbine runner is used as a mass element.
JP 2004-308904 A

  In recent years, in the field of vehicles such as automobiles, in order to improve fuel efficiency, there is a tendency to expand a lockup region having excellent transmission efficiency to a low rotation region where the engine speed is relatively low. For example, in an automobile, the speed is generally 500 to 700 rpm in an idling state, and the lockup is conventionally performed at about 1200 rpm, but there is a demand for locking up at about 1000 rpm at the start of running. However, low-frequency vibrations excited in a low rotation range are easily perceived, and abnormal noise due to the vibrations tends to be heard. In recent years, when driving comfort has been demanded, in order to expand the lock-up region to a low rotation range, it is required to improve the damping capacity of the damper mechanism against vibrations excited in the low rotation range, and in addition, models with different vibration characteristics. It is desired that the damper mechanism be optimized every time.

  However, Patent Document 1 does not specifically explain how to set the inertial mass of the mass element that affects the damping capacity of the damper mechanism. Furthermore, in the damper mechanism disclosed in Patent Document 1, a turbine runner is joined to an intermediate transmission element, and this turbine runner is used as a mass element. In such a configuration, it is necessary to change the design of the turbine runner when changing the vibration characteristics of the damper mechanism, and it is difficult to greatly change the vibration characteristics of the damper mechanism. Therefore, there is a limit to optimizing the damper mechanism for each vehicle type having different vibration characteristics. In addition, although patent document 1 also discloses adding an additional mass element to the turbine runner, this increases the number of parts and increases the cost.

  In the fluid transmission device disclosed in Patent Document 1, the turbine runner is connected to the input shaft via an intermediate transmission element and an inner peripheral coil spring. In such a configuration, even when the lockup is not performed, the inner peripheral coil spring is interposed in the transmission path of the rotational power from the turbine runner to the input shaft. When a coil spring having a small spring constant is used as the coil spring on the inner peripheral side, for example, in a vehicle, the responsiveness to the accelerator operation may be dull and drivability may be lowered in a low vehicle speed range.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a fluid transmission device in which vibration characteristics can be easily changed and which has excellent damping ability for vibration excited in a low rotation range. .

In order to achieve the above object, a fluid transmission device according to a first aspect of the present invention includes a pump impeller coupled to a drive shaft and a turbine runner coupled to a driven shaft, and the pump impeller and the A fluid transmission device in which a fluid is circulated through a circulation path formed between the turbine runner and rotational power is transmitted from the pump impeller to the turbine runner via the fluid, the turbine runner being connected to the drive shaft. And a damper mechanism interposed between the turbine runner and the lockup clutch, the damper mechanism being rotatable relative to the lockup clutch and the turbine runner. An inertial mass, a first elastic body for connecting the inertial mass to the lock-up clutch, and the inertial mass for the turbine runner Anda second elastic member connecting the inertial mass of the inertial mass body state, and are 0.7 times more inertial mass of the turbine runner, the inertial mass body, and the mass body, the added mass A body and a third elastic body, and the additional mass body is rotatable relative to the mass body main body, and is connected to the mass body main body via the third elastic body. It is characterized by that.

  According to the fluid transmission device of the first aspect of the present invention, the first elastic body, the second elastic body, and the inertia mass body as the damper mechanism are generally configured as the damper mechanism between the lock-up clutch and the turbine runner. A vibration system having a degree of freedom is interposed. When the torsional vibration of the drive shaft is transmitted to the inertial mass body via the lock-up clutch, the inertial mass body is excited with phase lag or antiphase vibration. Thereby, the vibration transmitted to the driven shaft can be attenuated or canceled. Further, by setting the inertial mass of the inertial mass body to 0.7 times or more of the inertial mass of the turbine runner, it is possible to improve the damping ability of torsional vibration particularly in a low rotation range. Furthermore, the inertial mass and the turbine runner are independent of each other. Thereby, the vibration characteristics of the damper mechanism can be easily and greatly changed without changing the design of the turbine runner by changing the inertial mass body variously. The damper mechanism is interposed between the turbine runner and the lockup clutch. When the damper mechanism is not locked up, the rotational power is directly transmitted from the turbine runner to the input shaft without passing through the damper mechanism. Thereby, for example, in a vehicle, the responsiveness to the accelerator operation can be kept good in the low vehicle speed region.

Further, according to the fluid transmission device of the first aspect of the present invention, the additional mass body is caused to vibrate in the opposite phase with respect to the mass body at the resonance frequency of the vibration system between the lockup clutch and the inertial mass body. This can cancel out the vibration of the mass body. Thereby, the torsional vibration transmitted from the drive shaft to the driven shaft can be further damped.

  DESCRIPTION OF EMBODIMENTS Hereinafter, a preferred embodiment of a fluid transmission device according to the present invention will be described in detail with reference to the drawings. FIG. 1 is a cross-sectional view of a first embodiment of a fluid transmission device according to the present invention, FIG. 2 is a schematic view showing a vibration model of the fluid transmission device of FIG. 1, and FIG. 3 is a second embodiment of the fluid transmission device according to the present invention. 4 is a sectional view of a third embodiment of the fluid transmission device according to the present invention, FIG. 5 is a sectional view of the fourth embodiment of the fluid transmission device according to the present invention, and FIG. 6 is the fluid of FIG. FIG. 7 is a schematic view showing a vibration model of the transmission, and FIG. 7 is a cross-sectional view of a fifth embodiment of the fluid transmission according to the present invention.

(First embodiment)
As shown in FIG. 1, the fluid transmission device 1 of this embodiment is a torque converter mounted on a vehicle such as an automobile, for example, and includes a crankshaft 2 of an engine (not shown) and a transmission (not shown). It is interposed between the input shaft 3 and the rotational power input to the crankshaft 2 is transmitted to the input shaft 3.

  The fluid transmission device 1 includes a pump impeller 10 connected to the crankshaft 2 and a turbine runner 11 connected to an input shaft 3 arranged coaxially with the crankshaft 2. The pump impeller 10 and the turbine runner 11 are disposed to face each other and have a substantially spindle shape in cross section. A circulation path 30 for circulating a fluid such as oil generally called fluid is formed between the two. A fluid is circulated through the circulation path 30, and rotational power is transmitted from the pump impeller 10 to the turbine runner 11 through the fluid.

  Further, the fluid transmission device 1 is provided between the pump impeller 10 and the turbine runner 11 and includes a stator 12 positioned on the circulation path 30. The stator 12 converts the flow direction of the fluid circulating in the circulation path 30 and amplifies the torque.

  The shell 13 of the pump impeller 10 is joined to a cover 14 covering the turbine runner 11 by an appropriate means such as welding. A plurality of fastening bosses 15 are arranged in the circumferential direction on the outer peripheral surface of the cover 14, and a drive plate 16 is fastened to these fastening bosses 15. The drive plate 16 is fastened to the crankshaft 2 via fastening means such as bolts. The pump impeller 10 is connected to the crankshaft 2 via the cover 14 and the drive plate 16 and rotates integrally with the crankshaft 2.

  The shell 17 of the turbine runner 11 is joined to a turbine hub 18 spline-fitted to the input shaft 3 by an appropriate means such as welding. The turbine runner 11 is connected to the input shaft 3 via the turbine hub 18 and rotates integrally with the input shaft 3. A thrust bearing 19 is provided between the turbine hub 18 and the cover 14.

  A cylindrical stator shaft 4 is disposed coaxially with the input shaft 3 on the outer periphery of the input shaft 3. The stator shaft 4 supports a hub 21 of the stator 12 via a one-way clutch 20. The stator shaft 4 is supported in a state in which, for example, an end thereof is fixed to a transmission case and does not rotate. A thrust bearing 22 a is provided between the hub 21 of the stator 12 and the shell 13 of the pump impeller 10, and a thrust bearing 22 b is provided between the hub 21 of the stator 12 and the turbine hub 18. It has been.

  A working chamber 23 communicating with the circulation path 30 is formed between the turbine runner 11 and the cover 14. The fluid transmission device 1 includes a lockup clutch 24 that can connect the turbine runner 11 and the cover 14, and the lockup clutch 24 includes a clutch piston 25 provided in the working chamber 23. The clutch piston 25 is formed in an annular shape, and the turbine hub 18 is inserted inside the clutch piston 25, and an inner peripheral portion is rotatably supported by the turbine hub 18. The clutch piston 25 is slidable on the outer peripheral surface of the turbine hub 18 in the axial direction.

  The clutch piston 25 divides the working chamber 23 into an inner working chamber 23a on the turbine runner 11 side and an outer working chamber 23b on the cover 14 side, and both the working chambers 23a and 23b are located outside the clutch piston 25. The clearances 26 formed between the peripheral edge and the inner peripheral surface of the cover 14 communicate with each other. An annular friction lining 27 is joined to one side surface of the clutch piston 25 facing the inner side surface of the cover 14.

  The fluid transmission device 1 includes a damper mechanism 40 that is provided between the turbine runner 11 and the lockup clutch 24 and connects the two. Details of the damper mechanism 40 will be described later.

  The fluid transmission device 1 configured as described above is connected to a pump (not shown) that supplies the fluid, and fluid is exchanged between the fluid transmission device 1 and the pump. The fluid supplied from the pump is a first flow path 28 between the shell 13 of the pump impeller 10 and the hub 21 of the stator shaft 4 and the stator 12 or a second flow between the turbine hub 18 and the cover 14. It flows into the circulation path 30 and the working chamber 23 communicating with the circulation path 30 through the path 29 to fill the circulation path 30 and the working chamber 23. Switching between the first flow path 28 and the second flow path 29 is performed by controlling a valve provided on the pump side.

  The working chamber 23 is divided into an inner working chamber 23 a and an outer working chamber 23 b by a clutch piston 25, and both the working chambers 23 a and 23 b communicate with each other through a clearance 26. This clearance 26 generates a differential pressure between the inner working chamber 23a and the outer working chamber 23b.

  When the fluid flows into the working chamber 23 and the circulation path 30 through the second flow path 29, the outer working chamber 23b has a higher pressure than the inner working chamber 23a. As a result, the clutch piston 25 moves backward toward the turbine runner 11 to separate the friction lining 27 from the inner surface of the cover 14. Thereby, the lockup clutch 24 is disconnected. At this time, the rotational power of the crankshaft 2 is transmitted from the crankshaft 2 to the pump impeller 10 via the drive plate 16 and the cover 14, and the turbine runner 11 via the fluid circulating in the circulation path 30 from the pump impeller 10. And is transmitted from the turbine runner 11 to the input shaft 3 via the turbine hub 18.

  On the other hand, when the fluid flows into the circulation path 30 and the working chamber 23 through the first flow path 28, the inner working chamber 23a has a higher pressure than the outer working chamber 23b. As a result, the clutch piston 25 moves forward to the cover 14 side, and the friction lining 27 is frictionally engaged with the inner surface of the cover 14. Thereby, the lock-up clutch 24 is connected, and the turbine runner 11 is directly connected to the crankshaft 2 and locked up. At this time, the rotational power of the crankshaft 2 is transmitted from the crankshaft 2 to the turbine runner 11 via the drive plate 16, the cover 14, the lockup clutch 24, and the damper mechanism 40, and from the turbine runner 11 via the turbine hub 18. It is transmitted to the input shaft 3. Thus, when the turbine runner 11 is directly connected to the crankshaft 2 by the lock-up, in other words, in a state where the turbine runner 11 is mechanically connected without any fluid, there is no transmission loss due to fluid slip.

  A damper mechanism 40 is provided between the turbine runner 11 and the lockup clutch 24, and the damper mechanism 40 connects the turbine runner 11 and the lockup clutch 24. The damper mechanism 40 includes an inertial mass body 41, a first elastic body 42 that connects the inertial mass body 41 to the lockup clutch 24, and a second elastic body 43 that connects the inertial mass body 41 to the turbine runner 11. Contains.

  A plurality of first elastic bodies 42 are arranged side by side in the circumferential direction in an annular housing recess 44 formed at the outer peripheral edge of the clutch piston 25 of the lockup clutch 24. Each first elastic body 42 can be elastically deformed in a circumferential direction or a tangential direction of the circumference. For example, a coil spring or the like is used as the first elastic body 42. A support member 45 fixed to the clutch piston 25 is interposed between the first elastic bodies 42 adjacent to each other in the circumferential direction, and the support members 45 are first elastic members disposed on both sides thereof. One end of each of the bodies 42, 42 is supported. A cover plate 46 for fixing the first elastic body 42 in the housing recess 44 is fixed to the clutch piston 25.

  The inertia mass body 41 has a mass body main body 47 which is a main component. The mass body 47 is formed in an annular shape, and the turbine hub 18 is inserted inside the mass body main body 47, and the inner peripheral portion is rotatably supported by the turbine hub 18. The mass body main body 47 thus supported is rotatable relative to the clutch piston 25 of the lockup clutch 24 supported by the turbine hub 18 and the turbine runner 11 joined to the turbine hub 18. A plurality of engaging arms 48 extending in the axial direction toward the clutch piston 25 side are provided on the outer peripheral edge of the mass body main body 47. Each engagement arm 48 is interposed between first elastic bodies 42, 42 that are adjacent in the circumferential direction in the housing recess 44 of the clutch piston 25.

  When relative rotation occurs between the clutch piston 25 of the lockup clutch 24 and the mass body main body 47 of the inertial mass body 41, the first elastic body 42 is supported at one end by the support member 45 of the clutch piston 25. At the same time, the other end is supported by the engagement arm 48 of the mass body main body 47 so that the clutch piston 25 and the mass body main body 47 are elastically compressed. As a reaction of compression of the first elastic body 42, the elastic reaction force of the first elastic body 42 acts on the clutch piston 25 and the mass body main body 47. Thereby, rotational power is transmitted from the lockup clutch 24 to the inertia mass body 41. The lockup clutch 24 and the inertia mass body 41 are connected via the first elastic body 42 when the relative rotation occurs between the lockup clutch 24 and the inertia mass body 41. It is sufficient that the elastic reaction force of the first elastic body 42 acts on the clutch 24 and the inertia mass body 41, and the present invention is not limited to the above-described form.

  The second elastic body 43 is disposed in each of a plurality of receiving holes 49 formed in the mass body main body 47 of the inertial mass body 41 side by side in the circumferential direction. The second elastic body 43 can be elastically deformed in the circumferential direction or the tangential direction of the circumference within the accommodation hole 49. As the second elastic body 43, a coil spring or the like is used similarly to the first elastic body 41.

  The turbine runner 11 joined to the turbine hub 18 includes an engaging means 50 that engages with the second elastic body 43. The engaging means 50 includes a pair of holder plates 51a and 51b formed in an annular shape. have. The pair of holder plates 51a and 51b are disposed so that the turbine hub 18 is inserted inside the holder plates 51a and 51b and the mass body main body 47 of the inertia mass body 41 is sandwiched from the front and back sides. The pair of holder plates 51 a and 51 b are integrated by a plurality of fastening members 52 that penetrate the mass body main body 47 on the outer peripheral side and the inner peripheral side of the accommodation hole 49 that accommodates the second elastic body 43. The holder plate 51a on the turbine runner 11 side has its inner peripheral edge adjacent to the inner peripheral edge of the shell 17 of the turbine runner 11, and the inner peripheral fastening member 52 has a pair of holder plates 51a and 51b. The shell 17 is also fastened. Thereby, the pair of holder plates 51 a and 51 b are joined to the shell 17.

  A through hole 53 through which the fastening member 52 is inserted is formed in the mass body main body 47 of the inertia mass body 41. In each through hole 53, a cylindrical spacer 54 is provided between the pair of holder plates 51 a and 51 b to secure a gap between the holders 51 a and 51 b and the front and back surfaces of the mass body 47. It is inserted with. Each through-hole 53 has a predetermined length in the circumferential direction, and the fastening member 52 and the spacer 54 fitted on the fastening member 52 can be displaced in the circumferential direction within the through-hole 53. Yes. Therefore, the inertial mass body 41 can rotate relative to the turbine runner 11 within a predetermined twist angle range.

  The pair of holder plates 51a and 51b accommodate accommodation holes 55a and 55b for accommodating the second elastic bodies 43 at positions corresponding to the accommodation holes 49 with the mass body main body 47 of the inertia mass body 41 interposed therebetween. Is formed. Reference numeral 56 denotes a cover plate that holds the second elastic body 43 in the receiving holes 49, 55a, and 55b. The cover plate 56 is fixed to the holder plates 51a and 51b.

  When relative rotation occurs between the mass body main body 47 of the inertia mass body 41 and the turbine runner 11, one end of the second elastic body 43 is supported by the edge of the accommodation hole 49 of the mass body main body 47. At the same time, the other end is supported by the edges of the receiving holes 55 a and 55 b of the engaging means 50 provided in the turbine runner 11, whereby the mass body 47 and the turbine runner 11 are elastically compressed. As a reaction of compression of the second elastic body 43, the elastic reaction force of the second elastic body 43 acts on the mass body 47 and the turbine runner 11, thereby rotating power from the inertia mass body 41 to the turbine runner 11. Is transmitted. The inertia mass body 41 and the turbine runner 11 are connected via the second elastic body 43 when the relative mass is generated between the inertia mass body 41 and the turbine runner 11. As long as the elastic reaction force of the second elastic body 43 acts on the turbine runner 11, the embodiment is not limited to the above-described form.

  In addition, when using a coil spring for the 1st elastic body 42 and the 2nd elastic body 43, a coil diameter becomes large, so that a spring constant is small. Here, the first elastic body 42 is arranged on the outer peripheral side of the maximum bulge portion of the turbine runner 11 having a substantially spindle shape in cross section, and the second elastic body 43 is the maximum bulge portion of the turbine runner 11. It is arranged on the inner circumference side. Thus, by arranging the both elastic bodies 42 and 43 while avoiding the maximum bulge portion of the turbine runner 11 having the largest restriction on the arrangement space, it is possible to sufficiently secure the arrangement space of the both elastic bodies 42 and 43. Thereby, the degree of freedom of selection of the spring constants of both elastic bodies 42 and 43 is improved, and the angle of twist of the inertial mass body 41 with respect to the lockup clutch 24 and the turbine runner 11 can be widened.

  In the fluid transmission device 1 configured as described above, the inertial mass of the inertial mass body 41 is attenuated in order to attenuate torsional vibration transmitted from the crankshaft 2 to the input shaft 3 while being locked up in the low rotation range. That is, in this embodiment, the inertial mass of the mass body 47 is 0.7 times or more the inertial mass of the turbine runner 11 (including the engaging means 50).

  In the locked-up state, the torsional vibration of the crankshaft 2 is transmitted to the input shaft 3 through the same path as the rotational power. Referring to FIG. 2, a first elastic body 42, a second elastic body 43, and an inertial mass body 41 having the above-described inertial mass are provided between the lockup clutch 24 and the turbine runner 11, and are freely rotatable. The inertial mass body 41 is excited by a phase delay or an antiphase vibration. Thereby, the vibration transmitted to the input shaft 3 is attenuated or canceled. Furthermore, the viscous resistance of the fluid acts on the inertial mass body 41 rotating in the inner working chamber 23a filled with the fluid, and the vibration transmitted to the input shaft 3 is also attenuated by this.

  As described above, according to the fluid transmission device of this embodiment, when the torsional vibration of the crankshaft 2 is transmitted to the inertial mass body 41 via the lockup clutch 24, the inertial mass body 41 has a phase lag or Antiphase vibrations are excited. Thereby, the vibration transmitted to the input shaft 3 is attenuated or canceled. And since the inertial mass of the inertial mass body 41 is 0.7 times or more of the inertial mass of the turbine runner 11, it is excellent in the damping capability of the torsional vibration in the low rotation range. From the above, it is possible to secure good vibration characteristics in the low rotation range and expand the lockup region to the low rotation range.

  Further, the inertia mass body 41 and the turbine runner 11 are independent from each other, and the vibration characteristics of the damper mechanism 40 can be easily changed without changing the design of the turbine runner 11 by variously changing the inertia mass body 41. And it is possible to change greatly. Thereby, the damper mechanism 40 can be easily optimized for each vehicle type having different vibration characteristics.

(Second Embodiment)
Next, a second embodiment of the fluid transmission device according to the present invention will be described with reference to FIG. In addition, about the member same as the fluid transmission apparatus 1 of 1st Embodiment mentioned above, description is abbreviate | omitted or simplified by attaching | subjecting the same code | symbol in a figure, About the member equivalent functionally, code | symbol equivalent in a figure The description is omitted or simplified by attaching.

  As shown in FIG. 3, in the fluid transmission device 101 of the present embodiment, the turbine runner 11 includes an engagement means 150 that engages with the second elastic body 43 of the damper mechanism 40, and the engagement means 150 includes It has a pair of holder pouches 151a and 151b formed in an annular shape. The pair of holder plates 151a and 151b are arranged so that the turbine hub 18 is inserted inside them and the mass body body 47 of the inertial mass body 41 is sandwiched from the front and back sides. The pair of holder plates 151 a and 151 b are integrated by a plurality of fastening members 52 that penetrate the mass body main body 47 of the inertia mass body 41 on the outer peripheral side and the inner peripheral side of the accommodation hole 49 that accommodates the second elastic body 43. It is said that.

  The outer peripheral edge portion of the holder plate 151 a on the turbine runner 11 side is located opposite to the maximum bulge portion of the shell 17 of the turbine runner 11. The holder plate 151 a and the shell 17 are connected to each other by a connecting member 157 that is joined to the outer peripheral edge of the holder plate 151 a and the maximum bulge of the shell 17.

(Third embodiment)
Next, a third embodiment of the fluid transmission device according to the present invention will be described with reference to FIG. In addition, about the member same as the fluid transmission apparatus 1 of 1st Embodiment mentioned above, description is abbreviate | omitted or simplified by attaching | subjecting the same code | symbol in a figure, About the member equivalent functionally, code | symbol equivalent in a figure The description is omitted or simplified by attaching.

  As shown in FIG. 4, the fluid transmission device 201 of this embodiment includes a lockup clutch 224 that can connect the turbine runner 11 and the cover 214. The lock-up clutch 224 is a so-called multi-plate clutch, and includes a plurality of disc-shaped clutch disks 260 and a clutch plate 261, and an annular clutch piston 264 that urges the clutch disks 260 and the clutch plate 261. And provided between the cover 214 and the damper plate 225 that holds the first elastic body 42.

  The plurality of clutch disks 260 are held in their inner peripheral portions by a cylindrical inner diameter hub 263 fixed to the damper plate 225, and are movable in the axial direction. Further, the plurality of clutch plates 261 are held at the outer peripheral portion by a cylindrical outer diameter hub 262 fixed to the cover 214, and are movable in the axial direction. The clutch disks 260 and the clutch plates 261 are arranged so as to be alternately overlapped in parallel with each other at an interval in the axial direction. The damper plate 225 can rotate with respect to the turbine hub 18 but does not move in the axial direction. The clutch piston 264 is supported by the spacer 266 at its inner periphery so that it can slide in the axial direction on the outer peripheral surface of a cylindrical spacer 266 fixed to the cover 214.

  The clutch piston 264 forms a working chamber 223 between the cover 214 and the outer diameter hub 262. The working chamber 223 is formed from the inner space 201a of the torque converter surrounded by the shell 13 and the cover 214 of the pump impeller 10. It is isolated. The spacer 266 has a second flow path 229 communicating with the working chamber 223, and the fluid is supplied from the pump to the working chamber 223 through the second flow path 229. The pressure inside is adjusted appropriately. The fluid is supplied from the pump to the internal space 201a of the torque converter including the circulation path 30 through the first flow path 28, and the internal space 201a of the torque converter is maintained at a predetermined pressure.

  When the pressure in the working chamber 223 is released and the pressure in the working chamber 223 becomes lower than the internal space 201a of the torque converter, the clutch piston 264 moves to the cover 214 side. As a result, the adjacent clutch disk 260 and the clutch plate 261 are separated from each other, and the lockup clutch 224 is disconnected. At this time, the rotational power of the crankshaft 202 is transmitted from the crankshaft 202 to the pump impeller 10 via the drive plate 216 and the cover 214, and the turbine runner 11 via the fluid circulating in the circulation path 30 from the pump impeller 10. And is transmitted from the turbine runner 11 to the input shaft 203 via the turbine hub 18.

  On the other hand, when the pressure in the working chamber 223 is increased and the pressure in the working chamber 223 becomes higher than the internal space 201a of the torque converter, the clutch piston 264 moves to the turbine runner 11 side. Accordingly, the clutch piston 264 urges the clutch disk 260 and the clutch plate 261 to move to the turbine runner 11 side, and the clutch disk 260 and the clutch plate 261 are connected to the stopper 265 fixed to the outer diameter hub 262. Hold between. As a result, the adjacent clutch disk 260 and the clutch plate 261 are frictionally engaged, the lockup clutch 224 is connected, and the turbine runner 11 is directly connected to the crankshaft 202 and locked up. At this time, the rotational power of the crankshaft 202 is transmitted from the crankshaft 202 to the turbine runner 11 via the drive plate 216, the cover 214, the lockup clutch 224, and the damper mechanism 40, and from the turbine runner 11 via the turbine hub 18. It is transmitted to the input shaft 203. Thus, in the state where the turbine runner 11 is directly connected to the crankshaft 202 by the lock-up, there is no transmission loss due to fluid slip.

(Fourth embodiment)
Next, with reference to FIG. 5 and FIG. 6, 4th Embodiment of the fluid transmission apparatus which concerns on this invention is described. In addition, about the member same as the fluid transmission apparatus 1 of 1st Embodiment mentioned above, description is abbreviate | omitted or simplified by attaching | subjecting the same code | symbol in a figure, About the member equivalent functionally, code | symbol equivalent in a figure The description is omitted or simplified by attaching.

  As shown in FIG. 5, the fluid transmission device 301 of this embodiment includes a damper mechanism 340 that is provided between the turbine runner 11 and the lockup clutch 24 and connects the two. The damper mechanism 340 includes an inertial mass body 341, a first elastic body 42 that connects the inertial mass body 341 to the lockup clutch 24, and a second elastic body 43 that connects the inertial mass body 341 to the turbine runner 11. Is included.

  The inertial mass body 341 includes a mass body main body 347, an additional mass body 370 having a relatively small inertial mass compared to the mass body main body 347, and a third elastic body 371. The mass body main body 347 is formed in an annular shape, and the turbine hub 18 is inserted inside the mass body main body 347, and the inner peripheral portion is rotatably supported by the turbine hub 18.

  The additional mass body 370 is provided in a guide groove 372 that is provided on the back surface of the mass body main body 347 and extends in the circumferential direction, and is movable along the guide groove 372, that is, is rotatable relative to the mass body main body 347. Is provided. Although the form of the additional mass body 370 is not particularly limited, in order to prevent eccentricity of the rotating inertial mass body 341, the additional mass body 370 is configured by one annular member or a plurality of small piece members. It is preferable to arrange them at substantially equal intervals in the circumferential direction.

  The third elastic body 371 is disposed in the accommodation hole 373 formed in the mass body main body 347. The third elastic body 371 can be elastically deformed in the circumferential direction or the tangential direction of the circumference within the accommodation hole 373. As the third elastic body 371, a coil spring or the like is used similarly to the first elastic body 41. The third elastic body 371 is supported at both ends by the edge of the accommodation hole 373, and is supported at both ends by a support member 374 provided in the additional mass body 370 at a portion exposed from the accommodation hole 373. Reference numeral 375 denotes a cover plate that holds the third elastic body 371 in the accommodation hole 373, and the cover plate 375 is fixed to the additional mass body 370.

  When relative rotation occurs between the mass body main body 347 and the additional mass body 370, the third elastic body 371 is supported at one end by the edge of the accommodation hole 373 of the mass body main body 370 and at the other end. Is supported by the support member 374 of the additional mass body 370, and is elastically compressed between the mass body main body 347 and the additional mass body 370. As a reaction of compression of the third elastic body 371, the elastic reaction force of the third elastic body 371 acts on the mass body main body 347 and the additional mass body 370. In addition, the connection form of the mass body main body 347 and the additional mass body 370 via the third elastic body 371 is the mass body when the relative rotation occurs between the mass body main body 347 and the additional mass body 370. Any structure may be used as long as the elastic reaction force of the third elastic body 371 acts on the main body 347 and the additional mass body 370, and the present invention is not limited to the above-described form.

  In the fluid transmission device 301 configured as described above, the inertial mass of the inertial mass body 341 is attenuated in order to attenuate the torsional vibration transmitted from the crankshaft 2 to the input shaft 3 while being locked up in the low rotation range. That is, in this embodiment, the total inertial mass of the mass body main body 347 and the additional mass body 370 is 0.7 times or more the inertial mass of the turbine runner 11 (including the engaging means 50).

  In the locked-up state, the torsional vibration of the crankshaft 2 is transmitted to the input shaft 3 through the same path as the rotational power. Referring to FIG. 6, between the lock-up clutch 24 and the turbine runner 11, a first elastic body 42, a second elastic body 43, and an inertial mass body 341 having the above-described inertial mass are configured to rotate freely. The inertial mass body 341 is excited by a phase delay or an antiphase vibration. Thereby, the vibration transmitted to the input shaft 3 is attenuated or canceled. And since the inertial mass of the inertial mass body 341 is 0.7 times or more of the inertial mass of the turbine runner 11, it is excellent in the damping capability of the torsional vibration in the low rotation range.

  In the fluid transmission device 301 according to the present embodiment, the vibration system VS1 including the additional mass body 370 and the third elastic body 371 and having a degree of freedom of rotation is independent of the rotational power transmission path in the inertial mass body 341. Is provided. According to this configuration, at the resonance frequency of the vibration system VS2 between the lockup clutch 24 and the mass body main body 347, the vibration system VS1 is vibrated in a phase opposite to that of the vibration system VS2, thereby canceling the vibration of the mass body main body 347. Can do. Thereby, the torsional vibration transmitted from the crankshaft 2 to the input shaft 3 can be further damped.

(Fifth embodiment)
Next, a fifth embodiment of the fluid transmission device according to the present invention will be described with reference to FIG. In addition, about the member same as the fluid transmission apparatus 1 of 1st Embodiment mentioned above, description is abbreviate | omitted or simplified by attaching | subjecting the same code | symbol in a figure, About the member equivalent functionally, code | symbol equivalent in a figure The description is omitted or simplified by attaching.

  As shown in FIG. 7, the fluid transmission device 401 of the present embodiment includes a damper mechanism 440 that is provided between the turbine runner 11 and the lockup clutch 24 and connects the two. The damper mechanism 440 includes an inertial mass body 441, a first elastic body 42 that connects the inertial mass body 441 to the lockup clutch 24, and a second elastic body 43 that connects the inertial mass body 441 to the turbine runner 11. Is included.

  The inertial mass body 441 includes a mass body main body 447 which is a main component. The mass body 447 is formed in an annular shape, and the turbine hub 18 is inserted inside the mass body main body 447, and the inner peripheral portion is rotatably supported by the turbine hub 18. The mass body main body 447 is provided with at least one resistor. FIG. 7 shows a wing-shaped resistor 480, and a plurality of such resistors 480 are erected in the circumferential direction on the surface of the mass body main body 447. The form of the resistor is not particularly limited as long as it is provided so as to protrude from the outer surface of the mass body main body 447.

  In the fluid transmission device 401 configured as described above, the inertial mass of the inertial mass body 441 is attenuated in order to attenuate the torsional vibration transmitted from the crankshaft 2 to the input shaft 3 while being locked up in the low rotation range. That is, in this embodiment, the total inertial mass of the mass body main body 447 and the resistor 480 is 0.7 times or more the inertial mass of the turbine runner 11 (including the engaging means 50).

  In the locked-up state, the torsional vibration of the crankshaft 2 is transmitted to the input shaft 3 through the same path as the rotational power. Between the lock-up clutch 24 and the turbine runner 11, a vibration system having a rotational degree of freedom, which is composed of the first elastic body 42, the second elastic body 43, and the inertia mass body 441 having the inertia mass, is interposed. In addition, the inertial mass body 441 is excited by phase delay or antiphase vibration. Thereby, the vibration transmitted to the input shaft 3 is attenuated or canceled. And since the inertial mass of the inertial mass body 441 is 0.7 times or more of the inertial mass of the turbine runner 11, it is excellent in the damping capability of torsional vibration in the low rotation range.

  Furthermore, according to the fluid transmission device 401 of the present embodiment, the viscous resistance of the fluid acts on the resistor 480 that rotates together with the mass body main body 447 in the working chamber 23 filled with fluid, and the resistor 480 has an inertial mass. It becomes resistance in the rotation direction of the body 441. Thereby, the torsional vibration transmitted from the crankshaft 2 to the input shaft 3 can be further damped.

  Next, an embodiment of the fluid transmission device according to the present invention will be described with reference to FIGS. FIG. 8A is a vibration model in which the fluid transmission device 1 according to the first embodiment described above is modeled. The first elastic body, the second elastic body, and the inertial mass between the lockup clutch and the turbine runner. A vibration system composed of a body and having a degree of freedom of rotation is interposed. FIG. 8B is a vibration model of a conventional fluid transmission device, and the vibration system between the lockup clutch and the turbine runner is omitted from the vibration model shown in FIG.

  Example 1 in FIG. 9 is the vibration model shown in FIG. 8A, and the inertial mass of the inertial mass body is 0.7 times the inertial mass of the turbine runner. Example 2 is a vibration model shown in FIG. 8A, in which the inertial mass of the inertial mass body is 2.0 times the inertial mass of the turbine runner. Comparative Example 1 is a vibration model shown in FIG. 8A, in which the inertial mass of the inertial mass body is 0.3 times the inertial mass of the turbine runner. Comparative Example 2 is a vibration model shown in FIG. The frequency characteristics of the vibration transmissibility of Examples 1 and 2 and Comparative Examples 1 and 2 were obtained by calculation. In calculating the frequency characteristics, the specifications of the vibration models of the example and the comparative example are set with reference to a general automobile.

  The calculation result of the frequency characteristic is shown in FIG. In FIG. 9, the horizontal axis indicates the frequency of rotational fluctuation determined by the engine speed or the number of cylinders, and the vertical axis indicates the ratio between the vibration amplitude output from the driven shaft and the vibration amplitude input to the drive shaft. The vibration transmissibility is shown. Assuming that the engine locks up when the engine speed reaches 1000 rpm, paying attention to the frequency characteristics after 1000 rpm, the inertial mass of the inertial mass body is the turbine runner in the vibration model shown in FIG. It can be seen that in Examples 1 and 2, which are 0.7 times or more the inertial mass, the vibration transmissibility is reduced as compared with Comparative Example 2 of the vibration model shown in FIG. On the other hand, even in the vibration model shown in FIG. 8A, the comparative example 1 in which the inertial mass of the inertial mass is less than 0.7 times the inertial mass of the turbine runner has a resonance frequency in the frequency band equivalent to 1000 rpm or later. The vibration transmissibility is higher than that of Comparative Example 2 of the vibration model shown in FIG.

  Next, in Example 3 in which the inertial mass of the inertial mass body is 1.0 times the inertial mass of the turbine runner in the vibration model shown in FIG. The spring constant of the elastic body connecting the inertial mass body and the turbine runner (indicated by the symbol k in FIG. 8A) is changed into two types of large and small, and in Comparative Example 2, the lockup clutch and the turbine runner are connected. The spring multiplier of the elastic body (indicated by the symbol k ′ in FIG. 8B) was changed into two kinds of large and small, and the frequency characteristic of the vibration transmissibility was obtained by calculation.

  FIG. 10 shows the frequency characteristics of Examples 1 and 3 and Comparative Examples 1 and 2 when the spring constant is small, and FIG. 11 shows the frequency characteristics of Examples 1 and 3 and Comparative Examples 1 and 2 when the spring constant is large. Show. Assuming that the engine locks up when the engine speed reaches 1000 rpm, paying attention to the frequency characteristics after 1000 rpm, FIG. 8 and FIG. 11 show that regardless of the spring constant, FIG. In Examples 1 and 3 in which the inertial mass of the inertial mass body is 0.7 times or more of the inertial mass of the turbine runner in the vibration model shown in FIG. 8, the vibration transmission is compared with Comparative Example 2 in the vibration model shown in FIG. It can be seen that the rate is reduced. On the other hand, Comparative Example 1 in which the inertial mass of the inertial mass body is less than 0.7 times the inertial mass of the turbine runner in the vibration model shown in FIG. As shown in FIG. 11, in the frequency band near 1000 rpm, there is not much difference between the vibration model and Comparative Example 2 of the vibration model shown in FIG. 8B, and when the spring constant is large, as shown in FIG. A resonance frequency exists in a frequency band equivalent to 1000 rpm or more, and the vibration transmissibility is higher at the resonance frequency than in the comparative example 2 of the vibration model shown in FIG.

  From the above, between the lock-up clutch and the turbine runner, a vibration system having a rotational degree of freedom, which is roughly composed of a first elastic body, a second elastic body, and an inertia mass body as a damper mechanism, is interposed. It can be seen that when the inertial mass of the inertial mass body is 0.7 times or more the inertial mass of the turbine runner, the torsional vibration damping capability in the low rotation range is improved.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimension, numerical value, form, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

It is sectional drawing of 1st Embodiment of the fluid transmission apparatus which concerns on this invention. It is a schematic diagram which shows the vibration model of the fluid transmission apparatus of FIG. It is sectional drawing of 2nd Embodiment of the fluid transmission apparatus which concerns on this invention. It is sectional drawing of 3rd Embodiment of the fluid transmission apparatus which concerns on this invention. It is sectional drawing of 4th Embodiment of the fluid transmission apparatus which concerns on this invention. It is a schematic diagram which shows the vibration model of the fluid transmission apparatus of FIG. It is sectional drawing of 5th Embodiment of the fluid transmission apparatus which concerns on this invention. (A) is a schematic diagram which shows the vibration model of the fluid transmission apparatus of an Example, (B) is a schematic diagram which shows the vibration model of the fluid transmission apparatus of a comparative example. It is a graph which shows the frequency characteristic of an Example and a comparative example. It is a graph which shows the frequency characteristic of the vibration transmissibility of an Example and a comparative example. It is a graph which shows the frequency characteristic of the vibration transmissibility of an Example and a comparative example.

Explanation of symbols

1 Fluid transmission device 2 Crankshaft (drive shaft)
3 Input shaft (driven shaft)
4 Stator shaft 10 Pump impeller 11 Turbine runner 12 Stator 13 Pump impeller shell 14 Cover 15 Fastening boss 16 Drive plate 17 Turbine runner shell 18 Turbine hub 20 One-way clutch 21 Stator hub 23 Working chamber 23a Inner working chamber 23b Outer working chamber 24 Lock Up clutch 25 Clutch piston 26 Clearance 27 Friction lining 28 First flow path 29 Second flow path 30 Circulation path 40 Damper mechanism 41 Inertial mass body 42 First elastic body 43 Second elastic body

Claims (1)

  1. A pump impeller coupled to the drive shaft, and a turbine runner coupled to the driven shaft,
    A fluid transmission device in which a fluid is circulated through a circulation path formed between the pump impeller and the turbine runner, and rotational power is transmitted from the pump impeller to the turbine runner via the fluid;
    A lock-up clutch that directly connects the turbine runner to the drive shaft; and a damper mechanism that is interposed between the turbine runner and the lock-up clutch.
    The damper mechanism includes an inertial mass body that is rotatable relative to the lockup clutch and the turbine runner, a first elastic body that connects the inertial mass body to the lockup clutch, and the inertial mass body. A second elastic body connected to the turbine runner,
    Inertial mass of the inertial mass body state, and are 0.7 times more inertial mass of the turbine runner,
    The inertial mass body includes a mass body main body, an additional mass body, and a third elastic body,
    The additional mass body can be relatively rotated with respect to the mass body, a hydraulic power transmission, wherein that it is connected to the mass body via the third elastic member.
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