CN111120531B - Torsional vibration reducing device - Google Patents
Torsional vibration reducing device Download PDFInfo
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- CN111120531B CN111120531B CN201911044672.1A CN201911044672A CN111120531B CN 111120531 B CN111120531 B CN 111120531B CN 201911044672 A CN201911044672 A CN 201911044672A CN 111120531 B CN111120531 B CN 111120531B
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- 230000002093 peripheral effect Effects 0.000 claims abstract description 50
- 230000007246 mechanism Effects 0.000 claims abstract description 43
- 230000009467 reduction Effects 0.000 claims abstract description 4
- 230000005540 biological transmission Effects 0.000 claims description 17
- 239000012530 fluid Substances 0.000 claims description 13
- 230000009699 differential effect Effects 0.000 claims description 4
- 230000000116 mitigating effect Effects 0.000 claims 2
- 230000000694 effects Effects 0.000 description 5
- 230000001133 acceleration Effects 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
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- 230000008859 change Effects 0.000 description 1
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- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
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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
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/1204—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system
- F16F15/1206—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system with a planetary gear system
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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
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
- F16F15/12373—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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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
- F16H2045/0268—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 the damper comprising a gearing
Abstract
The invention provides a torsional vibration reducing device, which can increase the inertia moment required for reducing the vibration of the input torque without enlarging the device in the radial direction. In a torsional vibration reduction device (1), an additional inertia body (27) is added to a third rotating element (22) so as to protrude from the third rotating element (22) in the direction of the rotation central axis at the outer peripheral portion of the third rotating element (22), a planetary rotating mechanism (20) has a center rotating element (21), a ring rotating element (22), and a carrier rotating element (24), a first rotating element is set as one of the center rotating element (21) and the carrier rotating element (24), a second rotating element is set as the other of the center rotating element (21) and the carrier rotating element (24), and the third rotating element is set as the ring rotating element (22).
Description
Technical Field
The present invention relates to a torsional vibration reducing device configured to reduce torsional vibration caused by fluctuation (vibration) of an input torque.
Background
Patent document 1 describes an example in which a planetary gear mechanism is used as a device for reducing torsional vibration. The planetary gear mechanism is arranged inside the torque converter having the lock-up clutch and outside the spring damper in the radial direction so as to be concentric with the spring damper. A lockup clutch and an input-side member of a spring damper are connected to a carrier of the planetary gear mechanism, and torque is input to the carrier via the lockup clutch. Further, an output-side member of a spring damper is connected to the sun gear. That is, the carrier and the sun gear are coupled via the spring damper. Annular side plates having an outer diameter and an inner diameter substantially equal to an outer diameter and an inner diameter of the ring gear are provided on both sides of the ring gear in the axial direction, and the side plates and the ring gear are integrated by rivets. The side plates and the rivets function as inertial mass bodies together with the ring gear. When the input torque vibrates, the springs of the spring damper expand and contract, and the carrier and the sun gear rotate relative to each other at a predetermined angle. Accordingly, the ring gear is forcibly rotated, and the inertia torque of the ring gear acts as a resistance to the vibration of the input torque, thereby reducing the vibration of the torque output from the planetary gear mechanism.
Prior art documents
Patent document
Patent document 1: international publication No. 2016/208767
Disclosure of Invention
Problems to be solved by the invention
In the device for reducing the vibration of the torque by the reciprocating motion of the inertial mass body, the resonance rotation speed can be reduced as the inertial torque is larger, and the vibration damping torque can be increased. The inertia torque is determined by the inertia moment and the angular acceleration, and the inertia moment increases as the mass of the inertial mass body increases and the inertial mass body is disposed radially outward. In the device described in patent document 1, since the ring gear and the side plate are configured to function as the inertial mass body, the moment of inertia can be increased as compared with a case where another rotating element functions as the inertial mass body. However, the outer diameter of the ring gear is restricted by a clearance set between the ring gear and the inner surface of the torque converter in order to avoid interference therebetween, the inner diameter of the torque converter, and the like. On the other hand, the pitch circle diameter of the ring gear is restricted by the pitch circle diameters of the pinion gear and the sun gear disposed inside the ring gear, the mounting position of the spring in the radial direction of the torque converter, and the like. Therefore, it is difficult to increase the inertia moment by increasing the size of the ring gear in the radial direction. Even if the ring gear should be increased in size, the size of the entire apparatus may be increased if only the ring gear is increased in size.
The present invention has been made in view of the above-described technical problem, and an object thereof is to provide a torsional vibration reducing device capable of increasing an inertia moment required for reducing vibration of an input torque without increasing the size of the device in a radial direction.
Means for solving the problems
In order to achieve the above object, the present invention provides a torsional vibration reducing device including: a planetary rotation mechanism that has a first rotation element to which torque is input, a second rotation element, and a third rotation element functioning as a rotating inertial mass body, and that performs a differential action by the first rotation element, the second rotation element, and the third rotation element; an elastic member that couples the first rotating element and the second rotating element so as to be relatively rotatable by a predetermined angle, wherein the torsional vibration reduction device is configured such that the elastic member is elastically deformed by vibration of the torque to relatively rotate the first rotating element and the second rotating element and also to generate vibration during rotation of the third rotating element, wherein an additional inertial body is added to the third rotating element so as to protrude from the third rotating element in a direction of a rotation center axis of the planetary rotation mechanism in a radial direction of the planetary rotation mechanism and at an outer peripheral portion of the third rotating element, and wherein the planetary rotation mechanism includes: a central rotation element; an inner meshing rotation element disposed on a concentric circle with respect to the center rotation element; and a carrier rotating element that holds a plurality of planetary rotating elements that are disposed between an outer peripheral portion of the center rotating element and an inner peripheral portion of the ring rotating element and that rotate and revolve by relative rotation between the center rotating element and the ring rotating element, wherein the first rotating element is one of the center rotating element and the carrier rotating element, the second rotating element is the other of the center rotating element and the carrier rotating element, and the third rotating element is the ring rotating element.
In the present invention, the additional inertial body may be formed in a cylindrical shape having a length in the rotation central axis direction longer than that of the inner-meshing rotation element, and the inner-meshing rotation element may be integrated with an inner circumferential surface of the additional inertial body in the radial direction.
In the present invention, the additional inertial body may be formed by an annular plate having the same outer diameter as the outer diameter of the internal meshing rotation element and an inner diameter larger than the inner diameter of the internal meshing rotation element, a protruding portion protruding in the rotation central axis direction may be provided on an outer peripheral portion of the plate, and the plate may be provided on at least one of both side surfaces of the internal meshing rotation element in the rotation central axis direction.
In the present invention, the elastic member may be arranged concentrically with the planetary rotation mechanism on an inner side of the planetary rotation mechanism in the radial direction.
In the present invention, a fluid power transmission device may be provided, the fluid power transmission device including: a housing coupled to an engine; a drive-side member that is coupled to the housing and generates a fluid flow; a driven side member driven by the fluid flow; and a direct clutch that engages with an inner surface of the housing to connect the driving-side member and the driven-side member, wherein the planetary rotation mechanism is provided inside the fluid transmission device.
In the present invention, the first rotational element may be the carrier rotational element, and the second rotational element may be the center rotational element.
In the present invention, the central rotation element of the planetary rotation mechanism may be configured by a sun gear, the ring rotation element may be configured by a ring gear, the planetary rotation element may be configured by a pinion gear, and the carrier rotation element may be configured by a carrier that holds the pinion gear.
Effects of the invention
According to the present invention, when the elastic member is elastically deformed by the vibration of the torque to cause the first rotating element and the second rotating element to rotate relative to each other, the third rotating element functioning as the rotational inertial mass body is forcibly rotated by the differential action of the planetary rotating mechanism. Since the rotation of the third rotating element is caused by the vibration of the torque, the vibration is generated in the rotation of the third rotating element. The third rotation element is an internal-meshing rotation element of the planetary rotation mechanism, and an additional inertial body is added to the internal-meshing rotation element at an outer peripheral portion of the internal-meshing rotation element so as to protrude from the internal-meshing rotation element in a rotation center axis direction of the planetary rotation mechanism. Therefore, the inertia moment of the entire internal meshing rotation element is increased as compared with a case where the additional inertia body is provided in the inner circumferential portion of the internal meshing rotation element in the radial direction or is provided substantially uniformly across from the inner circumferential portion to the outer circumferential portion of the internal meshing rotation element in the radial direction. Further, the inertia torque of the inter-meshing rotation element determined by the inertia moment and the angular acceleration increases. That is, the inertia moment can be increased without particularly increasing the outer diameter of the internal-meshing rotation element. Further, the entire apparatus is not particularly large-sized.
Drawings
Fig. 1 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a first embodiment of the present invention.
Fig. 2 is an enlarged cross-sectional view of a part of the planetary gear mechanism shown in fig. 1.
Fig. 3 is a side view showing a ring gear in an enlarged manner.
Fig. 4 is a diagram showing a relationship between the engine speed and the engine torque reduced by the torsional vibration reducing device.
Fig. 5 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a second embodiment of the present invention.
Fig. 6 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a third embodiment of the present invention.
Fig. 7 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a fourth embodiment of the present invention.
Fig. 8 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a fifth embodiment of the present invention.
Fig. 9 is a cross-sectional view schematically showing an example of a torsional vibration damper according to a sixth embodiment of the present invention.
Detailed Description
Next, embodiments of the present invention will be explained. Fig. 1 is a cross-sectional view showing an example of a torque converter 2 including a torsional vibration damper 1 according to a first embodiment of the present invention. The torque converter 2 is coupled to an output shaft (neither shown) of the drive power source. Since the driving force source is an internal combustion engine that outputs power by intermittently combusting a mixed gas of fuel and air, the output torque of the driving force source inevitably vibrates. In the following description, the drive force source is referred to as an engine. The torque converter 2 has a configuration similar to that of a conventionally known torque converter, and the housing 3 of the torque converter 2 is formed in a liquid-tight state by a front cover 4 coupled to an output shaft of an engine and a pump housing 5 integrated with the front cover 4.
A fluid (oil) for transmitting torque is sealed inside the housing 3. A plurality of pump vanes 6 are mounted on the inner surface of the pump housing 5, thereby constituting a pump impeller 7. A turbine 8 that receives and rotates the fluid flow generated by the pump impeller 7 is disposed opposite to the pump impeller 7. The turbine 8 is formed in a shape substantially symmetrical to the pump impeller 7, and is constituted by a turbine casing, not shown, and a plurality of turbine blades 9 attached to an inner surface of the turbine casing. The turbine 8 is coupled to an input shaft (neither shown) of the transmission via a turbine hub 10. The torque converter 2 described above corresponds to the fluid transmission device in the embodiment of the present invention, the pump impeller 7 corresponds to the driving-side member in the embodiment of the present invention, and the turbine runner 8 corresponds to the driven-side member in the embodiment of the present invention. The transmission may be a conventionally known transmission such as a stepped transmission in which the speed ratio changes stepwise, or a continuously variable transmission in which the speed ratio changes continuously.
A stator 11 is disposed between the pump impeller 7 and the turbine runner 8. The stator 11 is attached to a fixed shaft in the torque converter 2 via a one-way clutch 12. The stator 11 is configured to change the flow direction of the oil flowing out from the turbine runner 8 and supply the oil to the pump runner 7 in a state where the speeds of the pump runner 7 and the turbine runner 8 are relatively low, and to be pressed against the oil flowing out from the turbine runner 8 and rotated in a state where the speed is relatively high, so that the flow direction of the oil is not changed. Therefore, the one-way clutch 12 is configured to engage in a relatively low speed state to stop the rotation of the stator 11, and to rotate the stator 11 in a relatively high speed state.
A lockup clutch 13 is disposed to face the inner surface of the front cover 4, and this lockup clutch 13 corresponds to a direct clutch in the embodiment of the present invention. The lockup clutch 13 shown in fig. 1 is a multiple-plate clutch including, for example, a plurality of clutch disks 14 and a plurality of clutch plates 16, the clutch disks 14 being spline-fitted to a clutch hub integrated with the front cover 4, and the clutch plates 16 being spline-fitted to an inner peripheral surface of a clutch drum 15 disposed so as to cover an outer peripheral side of the clutch hub and alternately disposed with the clutch disks 14. The clutch disks 14 and the clutch plates 16 are alternately arranged between the lock piston 17 and a not-shown snap ring attached to the clutch drum 15. Therefore, the clutch disc 14 and the clutch plate 16 are brought into frictional contact by the forward movement of the lock piston 17 and the clutch disc 14 and the clutch plate 16 are sandwiched between the snap rings, and the torque is transmitted therebetween. That is, the lockup clutch 13 is in an engaged state for transmitting torque. A return spring 18 is disposed in parallel with at least a part of the lock-up clutch 13 in the radial direction of the torque converter 2 and on the inner peripheral side of the lock-up clutch 13. The return spring 18 presses the lock piston 17 in a direction to release the lock clutch 13, that is, in a direction to separate the clutch disc 14 and the clutch plate 16.
The torsional vibration damper 1 is disposed adjacent to the lock-up clutch 13 in the rotational center axis direction (hereinafter, simply referred to as the axial direction) of the torque converter 2. The torsional vibration damper 1 includes a planetary rotation mechanism and a spring damper 19 according to the embodiment of the present invention. The planetary rotation mechanism is a mechanism that mainly performs a differential action by three rotation elements such as a planetary gear mechanism and a planetary roller mechanism, and in the example shown here, it is configured by a single-pinion type planetary gear mechanism 20. The planetary gear mechanism 20 includes a sun gear 21, a ring gear 22 arranged concentrically with the sun gear 21, and a carrier 24 rotatably holding a plurality of pinion gears 23 meshing with the sun gear 21 and the ring gear 22. The sun gear 21 corresponds to a first rotating element, a second rotating element, and a central rotating element in the embodiment of the present invention, the ring gear 22 corresponds to a third rotating element and a ring rotating element that function as a rotating inertial mass body in the embodiment of the present invention, the pinion gear 23 corresponds to a planetary rotating element in the embodiment of the present invention, and the carrier 24 corresponds to a first rotating element, a second rotating element, and a carrier rotating element in the embodiment of the present invention.
The clutch drum 15 of the lock-up clutch 13 and the drive plate 25 of the spring damper 19 are connected to the carrier 24, and this structure becomes an input element. The sun gear 21 is formed on the outer peripheral portion of the driven disc 26 of the spring damper 19, and this structure becomes an output element. An additional inertial body 27 configured to protrude in the axial direction from the ring gear 22 is integrally provided on the outer peripheral portion of the ring gear 22. That is, the additional inertia body 27 is provided at a position offset in the radial direction from the outer peripheral portion of the ring gear 22. Therefore, the inertia moment generated by the ring gear 22 becomes larger than in the case where the additional inertia bodies 27 of the same mass are provided on the inner peripheral portion of the ring gear 22 or in the case where the additional inertia bodies are provided substantially uniformly in the radial direction so as to extend from the inner peripheral portion to the outer peripheral portion of the ring gear 22. The additional inertia mass 27 may be formed separately from the ring gear 22 and attached to the ring gear 22 so as to rotate integrally with the ring gear 22.
The above-described spring damper 19 is provided on the inner peripheral side of the planetary gear mechanism 20 in the radial direction of the torque converter 2 so as to be engaged with the planetary gear machineThe structures 20 are arranged concentrically. Here, "aligned" means a state in which at least a part of each of the spring damper 19 and the planetary gear mechanism 20 overlaps in the radial direction. The drive plate 25 of the spring damper 19 is disposed on the upstream side in the torque transmission direction of the spring damper 19, and is configured by an annular first drive plate 25A and an annular second drive plate 25B. Outer peripheral portion 25A of first drive disk 25AOAnd an inner peripheral portion 25AIAre configured so as to be offset from each other in the axial direction, and in the example shown in fig. 1, the outer peripheral portion 25A of the first drive disk 25AORelative to its inner peripheral part 25AIBut on the lock-up clutch 13 side.
Outer peripheral portion 25B of second drive disk 25BOAnd an inner peripheral portion 25BIConfigured to be offset from each other in the axial direction, in the example shown in fig. 1, the outer peripheral portion 25B of the second drive disk 25BORelative to its inner peripheral part 25BIBut on the turbine 8 side. Therefore, in the axial direction, the outer peripheral portion 25A of the first drive disk 25AOAnd an outer peripheral portion 25B of the second drive disk 25BOAre spaced apart more than their inner peripheral portions 25AI、25BISpaced apart from each other and where the planetary gear mechanism 20 is disposed. In addition, in the outer peripheral portion 25A of each drive disc 25A, 25BO、25BOThe pinion gear 23 of the planetary gear mechanism 20 is rotatably mounted. Therefore, each of the drive disks 25A, 25B doubles as the carrier 24.
Annular center plates 28A, 28B are provided on the downstream side of the respective drive disks 25A, 25B in the torque transmission direction and on both sides of the respective drive disks 25A, 25B in the axial direction, respectively. The respective drive disks 25A, 25B and the respective center plates 28A, 28B are coupled via a first spring 29 so as to be relatively rotatable by a predetermined angle. An annular driven disc 26 is disposed downstream of the center plates 28A, 28B in the torque transmission direction and between the driving discs 25A, 25B in the axial direction. The driven plate 26 and the center plates 28A and 28B are coupled to each other via a second spring, not shown, so as to be rotatable relative to each other by a predetermined angle. These first spring 29 and second spring are constituted by coil springs in the example shown here, and further, both are set to substantially the same torsional rigidity (spring constant). External teeth are formed on the outer peripheral surface of the driven disk 26, and this structure becomes the sun gear 21 of the planetary gear mechanism 20 as described above. The driven disk 26 is riveted at its inner peripheral portion to the turbine hub 10. In addition, the first spring 29 and the second spring correspond to elastic members in the embodiment of the present invention, and the elastic members only need to be members that are mainly elastically deformed so as to allow relative rotation of the driving disc 25 and the driven disc 26.
Fig. 2 is an enlarged cross-sectional view of the planetary gear mechanism 20 shown in fig. 1. Specifically describing the structure of the planetary gear mechanism 20, the outer peripheral portion 25A of each of the drive disks 25A and 25B is providedO、25BOThe pinion pin 30 is held, and the pinion 23 is rotatably attached to the outer peripheral side of the pinion pin 30 via a bearing 31 such as a needle bearing. Thrust washers 32 having a large diameter are provided at both sides of the pinion 23 in the axial direction. The thrust washer 32 has an outer diameter slightly larger than the pitch circle diameter of the ring gear 22. On both sides of each thrust washer 32, there are provided other washers 33 having a smaller diameter than the thrust washer 32. These washers 32 and 33 receive an axial component force generated by the engagement of the pinion gear 23 with the sun gear 21 and an axial component force generated by the engagement of the pinion gear 23 with the ring gear 22, and suppress the movement of the ring gear 22 in the axial direction due to the component forces. As described above, the additional inertial body 27 is formed so as to protrude in the axial direction from the ring gear 22, and the inner diameter of the additional inertial body 27 is set to be larger than the outer diameter of the clutch drum 15 and the outer diameter of the thrust washer 32. Therefore, interference of the additional inertial body 27 with the clutch drum 15 or the thrust washer 32 can be avoided or suppressed.
Further, the outer peripheral portion of the clutch drum 15 slightly extends toward the turbine 8 in the axial direction. Outer peripheral portion 25A of first drive disk 25AOOn the surface of the outer periphery of the cylinder, which is located inward in the radial directionAnd a fitting manner. Further, on the surface of the clutch drum 15 on the first drive plate 25A side in the axial direction, a fitting portion 34 recessed in the axial direction is formed, and the head portion 35 of the pinion pin 30 is fitted to the fitting portion 34.
Fig. 3 is an enlarged side view of a part of the ring gear 22. As shown in fig. 3, the additional inertial body 27 is integrally provided on the outer peripheral portion of the ring gear 22 so as to leave a predetermined clearance C with the inner surface 36 of the housing 3. The clearance C is determined in design in order to avoid or suppress interference of the additional inertial body 27 with the inner surface 36 of the housing 3.
Next, the operation of the first embodiment will be explained. When the lock-up clutch 13 is in the engaged state, the engine torque is input to the carrier 24. On the other hand, torque for rotating the transmission, not shown, acts on the sun gear 21 via the first spring 29 and the second spring. Therefore, a load that compresses the first spring 29 and the second spring is generated by the torque for rotating the engine torque and the transmission, and a displacement corresponding to the load occurs in the first spring 29 and the second spring. As a result, carrier 24 and sun gear 21 are caused to rotate relatively at a predetermined angle, and drive disks 25A, 25B and driven disk 26 are caused to rotate relatively at a predetermined angle.
The compression force (torsion force) acting on the first spring 29 and the second spring is changed by the vibration of the engine torque. Therefore, relative rotation between carrier 24 and sun gear 21 is repeated by the vibration of the engine torque. Thereby, the pinion gear 23 rotates within a range of a predetermined angle, so that the ring gear 22 is forcibly rotated, and vibration is generated in the rotation. At this time, the rotational speed of the ring gear 22 is increased by the gear ratio with respect to the rotational speed of the sun gear 21, and therefore the angular acceleration of the ring gear 22 is increased.
Further, since the additional inertia body 27 is provided so as to be offset toward the outer peripheral portion of the ring gear 22, the inertia moment of the ring gear 22 becomes larger than in a case where the additional inertia body 27 is provided on the inner peripheral portion of the ring gear 22 or is provided substantially uniformly across from the inner peripheral portion to the outer peripheral portion of the ring gear 22 in the radial direction. As a result, the inertia torque of the ring gear 22 determined by the inertia moment and the angular acceleration increases. Since this inertia torque acts as a vibration damping torque with respect to the vibration of the engine torque, the engine torque input to the carrier 24 is reduced and smoothed by the inertia torque of the ring gear 22, and is output from the driven plate 26. In the first embodiment, the additional inertial body 27 is formed so as to extend in the axial direction, and the ring gear 22 is not particularly increased in size in the radial direction. Therefore, the torque converter 2 and the torsional vibration damper 1 are not particularly increased in size. In the above configuration, the shape of the inner peripheral portion of the ring gear 22 is not particularly changed by providing the additional inertial body 27, and therefore, the cause of the inhibition of the rotation of the ring gear 22 can be eliminated, and the ring gear 22 can be smoothly rotated.
Fig. 4 is a diagram showing a relationship between the engine speed and the engine torque reduced by the torsional vibration reduction device 1. In the first embodiment, since the moment of inertia of the ring gear 22 can be increased as described above, the engine speed ω at which the vibration of the torque at the driven plate 26 can be minimized as shown in fig. 4 can be compared with a case where the moment of inertia of the ring gear 22 is not increased0The antiresonance point a of (a) is shifted to the low rotation speed side. This makes it possible to smoothly vibrate the torque in the low rotation speed region and to engage the lockup clutch 13 in the low rotation speed region. That is, the rotation speed range in which the lockup clutch 13 can be maintained in the engaged state is expanded to the low rotation speed side, and therefore fuel efficiency can be improved.
Further, the engine speed ω at the antiresonance point a0Can be calculated by the following expression (1). In the following formula (1), "K1"represents the torsional rigidity (spring constant) of the first spring 29 and" K2"indicates the second bulletTorsional stiffness of the spring (spring constant), "IR"represents the inertia moment of the ring gear 22 provided with the additional inertia body 27 as described above," I2"represents the inertia moment of the center plates 28A, 28B," B "is the gear ratio of the planetary gear mechanism 20 obtained by dividing the number of teeth of the sun gear 21 by the number of teeth of the ring gear 22.
Mathematical formula 1
The moment of inertia I of the ring gear 22 is expressed by equation (1)RThe greater the engine speed ω corresponding to the antiresonance point a0The smaller. Therefore, in the first embodiment, the engine speed ω is determined at the engine speed ω that is determined in design by the vibration of the torque output from the driven plate 260In the minimum manner to minimize the moment of inertia I of the internal gear 22RThe setting is performed. Further, in the first embodiment, since the additional inertia body 27 is provided so as to be offset toward the outer peripheral portion of the ring gear 22, it is possible to reduce the moment of inertia I required for obtaining the design, as compared with the case where the additional inertia body 27 is provided at the inner peripheral portion of the ring gear 22RAnd the mass of the inertial body 27 is added as needed. That is, a large moment of inertia I can be obtained with a small massR。
The present invention is not limited to the above-described embodiment, and the additional inertial body 27 may be provided so as to increase the mass of the outer peripheral portion of the ring gear 22 to be larger than the mass of the inner peripheral portion. The example shown in fig. 5 is an example in which the additional inertial body 27 is integrally provided on the side surface on the turbine 8 side, of the two side surfaces of the ring gear 22 in the axial direction. In the configuration shown in fig. 5, interference with the lockup clutch 13 can be further suppressed while obtaining the same operation and effect as those of the first embodiment shown in fig. 1.
The example shown in fig. 6 is an example in which the outer peripheral surface of the additional inertial body 27 having the structure shown in fig. 2 is formed in accordance with the shape of the inner surface 36 of the housing 3. In the configuration shown in fig. 6, the mass of the additional inertial body 27 can be increased as much as possible while interference with the inner surface 36 of the housing 3 is further suppressed, and the clearance C can be reduced as much as possible.
The example shown in fig. 7 is an example in which the additional inertial body 27 having the structure shown in fig. 2 is configured separately from the ring gear 22. The additional inertia body 27 shown in fig. 7 is formed in a cylindrical shape having a length in the axial direction longer than that of the ring gear 22, and the ring gear 22 is fixed to the inside thereof by a predetermined fixing means. The fixing means may be conventionally known, and may be press-fit, welding, caulking, bolting, or the like. In the configuration shown in fig. 7, since the additional inertia element 27 is formed as a separate body, the design and manufacture of the ring gear 22 are not particularly changed, and thus the increase in cost can be minimized. Further, since the inertia moment of the ring gear 22 can be increased or decreased by replacing the additional inertia body 27 attached to the ring gear 22 with the additional inertia body 27 having a different axial length or outer diameter, the inertia moment of the ring gear 22 can be easily tuned. Even with the configuration shown in fig. 7, the same operation and effect as those of the first embodiment shown in fig. 1 can be obtained.
The example shown in fig. 8 is an example in which additional inertial bodies 27 formed by annular plates are provided on both side surfaces of the ring gear 22 in the axial direction. The outer peripheral portion of the additional inertial body 27 is a protrusion 27A protruding in the axial direction, and as shown in fig. 8, the cross section of the additional inertial body 27 is formed in an L shape. The outer diameter of the additional inertial body 27 shown in fig. 8 is set to be substantially the same as the outer diameter of the ring gear 22, and the inner diameter thereof is set to be larger than the outer diameter of the thrust washer 32 in order to avoid interference with the thrust washer 32. The additional inertia bodies 27 are welded, riveted, or bolted to both side surfaces of the ring gear 22. In the structure shown in fig. 8, the additional inertial body 27 can be formed by, for example, press working, and therefore the manufacturing cost of the additional inertial body 27 can be kept to a minimum. Further, since the inertia moment of the ring gear 22 can be increased or decreased by replacing the additional inertia body 27 attached to the ring gear 22 with the additional inertia body 27 having the different size of the protrusion 27A, the inertia moment of the ring gear 22 can be easily tuned. Even with the configuration shown in fig. 8, the same operation and effect as those of the first embodiment shown in fig. 1 can be obtained.
The example shown in fig. 9 is an example in which the additional inertial body 27 shown in fig. 8 is integrally provided on a side surface on the turbine 8 side, of both side surfaces of the ring gear 22 in the axial direction. With such a configuration, interference with the lock-up clutch 13 can be further suppressed, and the same operation and effect as those of the first embodiment shown in fig. 1 and 8 can be obtained.
In the embodiment of the present invention, the sun gear may be used as an input element, and the carrier may be used as an output element. The point is that the ring gear may be configured to function as the rotating inertial mass body. The planetary rotation mechanism according to the embodiment of the present invention is not limited to a gear, and may be configured by a roller.
Description of the symbols
1 … torsional vibration damper; 20 … planetary gear mechanism (planetary rotation mechanism); 21 … sun gear (central rotation element); 22 … ring gear (inner meshing rotation element); pinion gear 23 … (planetary rotation element); 24 … planetary carrier (planetary carrier rotation element); 27 … adding inertia body; 29 … first spring (elastic member).
Claims (7)
1. A torsional vibration reducing device is provided with:
a planetary rotation mechanism that has a first rotation element to which torque is input, a second rotation element, and a third rotation element functioning as a rotating inertial mass body, and that performs a differential action by the first rotation element, the second rotation element, and the third rotation element;
an elastic member that connects the first rotating element and the second rotating element so as to be rotatable relative to each other by a predetermined angle,
the torsional vibration reduction device is configured such that the elastic member is elastically deformed by vibration of the torque to relatively rotate the first rotating element and the second rotating element, and vibration is generated in rotation of the third rotating element,
the torsional vibration damper is characterized in that,
an additional inertial body is added to the third rotating element so as to protrude from the third rotating element in the direction of the rotation center axis of the planetary rotating mechanism in the radial direction of the planetary rotating mechanism and in the outer peripheral portion of the third rotating element,
the planetary rotation mechanism includes:
a central rotation element;
an inner meshing rotation element disposed on a concentric circle with respect to the center rotation element;
a carrier rotating element that holds a plurality of planetary rotating elements that are disposed between an outer peripheral portion of the center rotating element and an inner peripheral portion of the ring rotating element and that rotate and revolve by relative rotation between the center rotating element and the ring rotating element,
the first rotational element is one of the center rotational element and the carrier rotational element,
the second rotating element is the other of the center rotating element and the carrier rotating element,
the third rotation element is set as the inter-engagement rotation element.
2. The torsional vibration mitigation device of claim 1,
the additional inertia element is formed in a cylindrical shape having a length in the rotation central axis direction longer than the inner meshing rotation element, and the inner meshing rotation element is integrated with an inner circumferential surface of the additional inertia element in the radial direction.
3. The torsional vibration mitigation device of claim 1,
the additional inertial body is formed by an annular plate having the same outer diameter as the outer diameter of the inner meshing rotation element and a larger inner diameter than the inner diameter of the inner meshing rotation element,
a projection projecting in the direction of the rotation center axis is provided on the outer peripheral portion of the plate,
the plate is provided on at least one of both side surfaces of the inter-meshing rotary element in the rotation center axis direction.
4. The torsional vibration damper as defined in any one of claims 1 to 3,
the elastic members are arranged concentrically with the planetary rotation mechanism on the inner side of the planetary rotation mechanism in the radial direction.
5. The torsional vibration damper as defined in any one of claims 1 to 3,
a fluid transmission device is provided, the fluid transmission device having:
a housing coupled to an engine;
a drive-side member that is coupled to the housing and generates a fluid flow;
a driven side member driven by the fluid flow;
a direct clutch that engages with an inner surface of the housing to connect the driving-side member and the driven-side member,
the planetary rotation mechanism is provided inside the fluid transmission device.
6. The torsional vibration damper as defined in any one of claims 1 to 3,
the first rotating element is set as the carrier rotating element,
the second rotation element is set as the center rotation element.
7. The torsional vibration damper as defined in any one of claims 1 to 3,
the central rotation element of the planetary rotation mechanism is configured by a sun gear, the ring rotation element is configured by a ring gear, the planetary rotation element is configured by a pinion gear, and the carrier rotation element is configured by a carrier that holds the pinion gear.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018205582A JP7021050B2 (en) | 2018-10-31 | 2018-10-31 | Torsion vibration reduction device |
| JP2018-205582 | 2018-10-31 |
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| CN111120531A CN111120531A (en) | 2020-05-08 |
| CN111120531B true CN111120531B (en) | 2022-04-19 |
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| JP2008164013A (en) | 2006-12-27 | 2008-07-17 | Aisin Aw Co Ltd | Damper device for vehicle |
| JP5169725B2 (en) | 2008-10-22 | 2013-03-27 | トヨタ自動車株式会社 | Damper device and fluid transmission device |
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| JP6384573B1 (en) * | 2017-03-08 | 2018-09-05 | トヨタ自動車株式会社 | Torsional vibration reduction device |
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| CN103221715A (en) * | 2010-11-19 | 2013-07-24 | 丰田自动车株式会社 | Vehicle damping device |
| CN106015455A (en) * | 2015-03-30 | 2016-10-12 | 丰田自动车株式会社 | Torsional vibration damper |
| CN107709827A (en) * | 2015-06-26 | 2018-02-16 | 爱信艾达工业株式会社 | Damper device |
| DE102016122463A1 (en) * | 2015-12-18 | 2017-06-22 | Toyota Jidosha Kabushiki Kaisha | torsional vibration damper |
| CN108603565A (en) * | 2016-01-29 | 2018-09-28 | 爱信艾达工业株式会社 | Damper device |
| CN107228174A (en) * | 2016-03-23 | 2017-10-03 | 丰田自动车株式会社 | Possessing twisting vibration reduces the torque-converters of device |
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| JP2020070875A (en) | 2020-05-07 |
| CN111120531A (en) | 2020-05-08 |
| JP7021050B2 (en) | 2022-02-16 |
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