CN215861525U - Torque fluctuation suppression device - Google Patents
Torque fluctuation suppression device Download PDFInfo
- Publication number
- CN215861525U CN215861525U CN202122368990.2U CN202122368990U CN215861525U CN 215861525 U CN215861525 U CN 215861525U CN 202122368990 U CN202122368990 U CN 202122368990U CN 215861525 U CN215861525 U CN 215861525U
- Authority
- CN
- China
- Prior art keywords
- torque fluctuation
- rotating body
- suppression device
- fluctuation suppression
- flywheel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Mechanical Operated Clutches (AREA)
Abstract
The present invention relates to a torque fluctuation suppression device. The torque fluctuation suppression device is prevented from having an excessively large torsion angle. The torque fluctuation suppression device (10) is configured to be used in a gas. The torque fluctuation suppression device (10) is configured to suppress torque fluctuation of a motor. A torque fluctuation suppression device (10) is provided with a first rotating body (2), a second rotating body (3), and a variable stiffness mechanism (4). The first rotating body (2) is arranged to be rotatable. The second rotating body (3) is configured to rotate together with the first rotating body (2) and is capable of rotating relative to the first rotating body (2). The variable rigidity mechanism (4) changes the torsional rigidity between the first rotating body (2) and the second rotating body (3) according to the number of rotations of the first rotating body (2) or the second rotating body (3). The torque fluctuation suppression device (10) is designed such that the natural frequency thereof is greater than the combustion frequency of the prime mover.
Description
Technical Field
The present invention relates to a torque fluctuation suppression device.
Background
The torque fluctuation suppression device is configured to suppress torque fluctuation from a motor such as an engine. For example, the torque fluctuation suppression device described in patent document 1 changes the torsional rigidity between the hub flange and the inertia ring according to the rotation speed of the engine. Specifically, the torque fluctuation suppression device has a variable torsional rigidity that increases as the engine speed increases.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2017-53467
SUMMERY OF THE UTILITY MODEL
Technical problem to be solved by the utility model
When the torque variation from the motor is large, there is a risk that the torsion angle of the torque variation suppression device becomes excessively large. For example, when the torque fluctuation suppression device is mounted on a vehicle having a manual transmission, the torque fluctuation suppression device is preferably disposed between the motor and the vibration damping device. In this case, since the torque variation before being attenuated by the vibration damping device is input to the torque variation suppression device, there is a possibility that the torsion angle becomes excessively large.
If the torsion angle in the torque fluctuation suppression device becomes too large, there is a possibility that the torque may not be fluctuated properly, or that the centrifugal member collides with the hub flange to generate a knocking sound. As described above, if the torsion angle in the torque fluctuation suppression device becomes too large, various problems may be caused.
Therefore, an object of the present invention is to suppress an excessively large torsion angle of the torque fluctuation suppression device.
Means for solving the technical problem
The torque fluctuation suppression device according to one aspect of the present invention is configured to be used in a gas. The torque fluctuation suppression device is configured to suppress torque fluctuation of the motor. The torque fluctuation suppression device includes a first rotating body, a second rotating body, and a variable stiffness mechanism. The first rotating body is configured to be rotatable. The second rotating body is configured to rotate together with the first rotating body and is relatively rotatable with respect to the first rotating body. The variable rigidity mechanism changes torsional rigidity between the first rotating body and the second rotating body according to the rotation speed of the first rotating body or the second rotating body. The torque fluctuation suppression device is designed such that its natural frequency is greater than the combustion frequency of the prime mover.
The torque fluctuation suppression device is designed such that the natural frequency thereof is higher than the combustion frequency of the prime mover. That is, the torque fluctuation suppression device is designed to have a natural frequency greater than the optimum natural frequency at a certain rotation speed. As a result, it is possible to suppress the torque fluctuation suppression function from being lowered to some extent and the torsion angle of the torque fluctuation suppression device from becoming excessively large.
Preferably, the torque fluctuation suppression device is designed such that the natural frequency thereof is 1.1 times or more the combustion frequency of the prime mover.
Preferably, the torque fluctuation suppression device is designed such that the natural frequency thereof is 1.4 times or less the combustion frequency of the prime mover.
Preferably, the first rotating body is a flywheel attached to a crankshaft.
Preferably, the flywheel has a disc portion and a mounting portion. The disk portion is attached to the crankshaft. The mounting portion is mounted on the outer periphery of the disc portion.
Preferably, the second rotation body is an inertia ring. The inertia ring is disposed between the disk portion and the mounting portion in the axial direction. The mounting portion has a projection portion penetrating the inertia ring and extending to the disc portion.
Preferably, the flywheel has a ring gear formed on an outer peripheral surface of the mounting portion.
Preferably, the variable stiffness mechanism has a centrifugal member and a cam mechanism. The centrifugal member is configured to be movable in a radial direction by a centrifugal force based on rotation of the first rotating body or the second rotating body. The cam mechanism is configured to receive a centrifugal force acting on the centrifugal member and convert the centrifugal force into a circumferential force in a direction in which a torsion angle between the first rotating body and the second rotating body is reduced.
Preferably, the cam mechanism has a cam surface and a cam follower. The cam surface is formed in the eccentric member. The cam follower abuts against the cam surface and transmits force between the centrifugal member and the second rotating body.
Preferably, the variable stiffness mechanism is configured to increase torsional stiffness between the first rotating body and the second rotating body as the rotation speed of the first rotating body or the second rotating body increases.
Effect of the utility model
According to the present invention, the torsion angle of the torque fluctuation suppression device can be suppressed from becoming excessively large.
Drawings
Fig. 1 is a schematic diagram showing a power transmission path.
Fig. 2 is a sectional view of the clutch device.
Fig. 3 is a plan view of the torque fluctuation suppression device with one of the inertia rings removed.
Fig. 4 is a graph showing a relationship between the engine speed and the torsion angle of the torque fluctuation suppression device.
Fig. 5 is a graph showing a relationship between the engine speed and the torque variation output from the torque variation suppression device.
Fig. 6 is a plan view of the torque fluctuation suppression device with one of the inertia rings removed.
Description of the reference numerals
2: a flywheel; 21: a circular plate portion; 22: an installation part; 221: a convex portion; 3: an inertia ring; 4: a variable stiffness mechanism; 41: a centrifuge; 412: a cam surface; 42: a cam mechanism; 421: a cam follower; 10: a torque fluctuation suppression device; 103: a crankshaft.
Detailed Description
Hereinafter, a torque fluctuation suppression device according to the present embodiment will be described with reference to the drawings. In the following description, the axial direction refers to a direction in which the rotation axis O of the torque fluctuation suppression device extends. The circumferential direction is a circumferential direction of a circle centered on the rotation axis O, and the radial direction is a radial direction of a circle centered on the rotation axis O.
[ integral Structure ]
As shown in fig. 1, the torque fluctuation suppression device 10 is disposed between an engine (ICE)101 (an example of a motor) and a transmission (T/M) 102. The transmission is, for example, a manual transmission. The torque fluctuation suppression device 10 is disposed between the engine 101 and the damper 124. The torque fluctuation suppression device 10 is used in a gas. That is, the torque fluctuation suppression device 10 is not disposed in oil. The torque fluctuation suppression device 10 is configured to suppress torque fluctuation of the engine.
As shown in fig. 2, the torque fluctuation suppression device 10 is incorporated in the clutch device 100. The clutch device 100 includes a torque fluctuation suppression device 10, a clutch cover assembly 11, and a clutch disc assembly 12.
[ Torque fluctuation suppression device ]
As shown in fig. 2 and 3, the torque fluctuation suppression device 10 includes a flywheel 2 (an example of a first rotating body), a pair of inertia rings 3 (an example of a second rotating body), and a variable stiffness mechanism 4.
< flywheel >
As shown in fig. 2, the flywheel 2 is configured to be able to rotate. The flywheel 2 is mounted on the crankshaft 103. The flywheel 2 rotates integrally with the crankshaft 103.
The flywheel 2 includes a disk portion 21, a mounting portion 22, and a ring gear 23. The disc portion 21 is formed in a disc shape. The inner peripheral portion of the disc portion 21 is coupled to the crankshaft 103. For example, the disc portion 21 is fixed to the crankshaft 103 by a fastening member such as a bolt. The disc portion 21 has a recess 211 formed in the outer peripheral portion thereof and opening radially outward. The concave portion 211 is formed to be open to the outside in the radial direction and has a predetermined depth.
The mounting portion 22 is formed in a ring shape. The mounting portion 22 extends in the circumferential direction. The attachment portion 22 is attached to the circular plate portion 21. The mounting portion 22 is fixed to the circular plate portion 21 by a fastening member such as a rivet. The mounting portion 22 rotates integrally with the disk portion 21. The mounting portion 22 includes a plurality of protrusions 221, an annular protrusion 222, and a friction surface 223.
The convex portion 221 protrudes toward the disc portion 21. The convex portions 221 are arranged at intervals in the circumferential direction. The projection 221 penetrates one of the inertia rings 3. The tip end surface of the projection 221 abuts against the disc portion 21.
The annular projection 222 is annular and extends in the circumferential direction. The annular projection 222 is disposed at an outer peripheral end of the mounting portion 22. The annular projection 222 projects in a direction away from the disc portion 21. That is, the annular convex portion 222 protrudes to the opposite side of the convex portion 221.
The friction surface 223 faces the transmission side. The clutch disk 121 of the clutch disk assembly 12 described later is pressed against the friction surface 223.
The ring gear 23 is provided on the outer peripheral surface of the mounting portion 22. The ring gear 23 rotates integrally with the mounting portion 22. The ring gear 23 may be formed of a member different from the mounting portion 22, or may be formed of one member.
< inertia ring 3 >
The inertia ring 3 is rotatable together with the flywheel 2 and is relatively rotatable with respect to the flywheel 2. That is, the inertia ring 3 is elastically coupled to the flywheel 2. The inertia ring 3 is an annular plate. Specifically, the inertia ring 3 is formed in a continuous annular shape. The inertia ring 3 functions as a mass body of the torque fluctuation suppression device 10.
The pair of inertia rings 3 are disposed so as to sandwich the flywheel 2. Specifically, the pair of inertia rings 3 are disposed so as to sandwich the circular plate portion 21 of the flywheel 2. The pair of inertia rings 3 are disposed on both sides of the flywheel 2 with a predetermined gap therebetween in the axial direction. The flywheel 2 and the pair of inertia rings 3 are arranged in an axial direction. One inertia ring 3 is disposed between the disk portion 21 and the mounting portion 22 in the axial direction. The inertia ring 3 has the same rotational axis as the flywheel 2.
The pair of inertia rings 3 are fixed to each other by rivets 31. Thus, the pair of inertia rings 3 cannot move in the axial direction, the radial direction, and the circumferential direction relative to each other.
< variable stiffness means 4 >
As shown in fig. 3, the variable stiffness mechanism 4 is configured to change the torsional stiffness between the flywheel 2 and the inertia ring 3 according to the rotation speed of the flywheel 2 or the inertia ring 3. In the present embodiment, the variable stiffness mechanism 4 is configured to change the torsional stiffness in accordance with the rotation speed of the flywheel 2. Specifically, the variable stiffness mechanism 4 increases the torsional stiffness between the flywheel 2 and the inertia ring 3 as the rotation speed of the flywheel 2 increases.
The variable stiffness mechanism 4 has a centrifugal member 41 and a cam mechanism 42. The centrifugal member 41 is attached to the flywheel 2. Specifically, the centrifugal piece 41 is disposed in the concave portion 211 of the flywheel 2. The centrifugal member 41 is disposed in the recess 211 so as to be movable in the radial direction. The centrifugal member 41 is movable in the radial direction by a centrifugal force based on the rotation of the flywheel 2.
In detail, the centrifugal member 41 has a plurality of guide rollers 411. Since the centrifugal member 41 moves in the radial direction, the guide roller 411 rolls on the inner wall surface of the concave portion 211. Thereby, the centrifugal piece 41 can smoothly move in the radial direction.
The centrifugal member 41 has a cam surface 412. The cam surface 412 is formed in an arc shape that is recessed inward in the radial direction in a front view (as viewed in the axial direction as shown in fig. 3). Further, the cam surface 412 is an outer peripheral surface of the centrifugal piece 41. As described later, the cam surface 412 of the centrifugal piece 41 functions as a cam of the cam mechanism 42.
The cam mechanism 42 is configured to convert a centrifugal force into a circumferential force in a direction in which a torsion angle is reduced when the centrifugal force acting on the centrifugal element 41 causes torsion (relative displacement in the circumferential direction) between the flywheel 2 and the inertia ring 3.
The cam mechanism 42 is constituted by a cam follower 421 and a cam surface 412 of the centrifugal member 41. The cam surface 412 of the centrifugal piece 41 functions as a cam of the cam mechanism 42. The cam follower 421 is attached to the body portion of the rivet 31. That is, the cam follower 421 is supported by the rivet 31. The cam follower 421 is preferably rotatably attached to the rivet 31, but may be non-rotatably attached. The cam surface 412 is a surface against which the cam follower 421 abuts, and is arcuate when viewed in the axial direction. When the flywheel 2 and the inertia ring 3 rotate relatively within a predetermined angular range, the cam follower 421 moves along the cam surface 412.
When a torsion angle (rotational phase difference) is generated between the flywheel 2 and the inertia ring 3 by the contact between the cam follower 421 and the cam surface 412, the centrifugal force generated in the centrifugal piece 41 is converted into a force in the circumferential direction such that the torsion angle is reduced.
< natural frequency >
The torque variation suppression device 10 is designed as the natural frequency f of the torque variation suppression device 10VDDSpecific to combustion frequency f of engine 101CIs large. For example, the natural frequency f of the torque fluctuation suppression device 10 is preferably setVDDSet as the combustion frequency f of the engineCMore than 1.1 times of the total amount of the active ingredients. In addition, the torque becomesNatural frequency f of dynamic suppression device 10VDDPreferably combustion frequency f of engine 101C1.4 times or less.
Natural frequency f of torque fluctuation suppression device 10VDDRepresented by the following formula.
Further, k denotes the torsional rigidity (Nm/rad) of the torque fluctuation suppression device 10, and I denotes the inertia amount (kgm) of the torque fluctuation suppression device 102). The torsional rigidity changes according to the rotation speed N (r/min) of the flywheel 2 of the torque fluctuation suppression device 10, and is represented by the following equation.
k＝f(N2)…(2)
Therefore, the natural frequency f of the torque fluctuation suppression device 10VDDRepresented by the following formula (3).
Here, the torsional rigidity k ═ f (N)2) Can be represented by the following formula.
Here, R denotes a distance from the rotation axis O to the center of the cam follower 421, m denotes a mass of the centrifugal element 41, R denotes a distance from the rotation axis O to the center of gravity of the centrifugal element 41, ω denotes a rotation speed (rad/s) of the flywheel 2, θ denotes an angle formed by the direction of P0 and the direction of the component force P2 (see fig. 6), and α denotes a torsion angle (see fig. 6).
In addition, the combustion frequency f of the engine 101CRepresented by the following formula.
In addition, n represents the number of cylinders of the engine 101, and Ne represents the rotation speed (rpm) of the engine 101.
Fig. 4 is a graph showing a relationship between the rotation speed of the engine 101 and the torsion angle of the torque fluctuation suppression device 10. The horizontal axis represents the rotation speed of the engine 101, and the vertical axis represents the torsion angle. In fig. 4, a line a represents the natural frequency f of the torque fluctuation suppression device 10VDDIs set to have a combustion frequency f with respect to the engine 101CThe same condition applies. In addition, line B represents the natural frequency f of the torque fluctuation suppression device 10VDDSet to combustion frequency f of engine 101C1.1 times of the case. In addition, line C represents the natural frequency f of the torque fluctuation suppression device 10VDDSet to combustion frequency f of engine 101C1.2 times of the case. Further, line D represents the natural frequency f of the torque fluctuation suppression device 10VDDSet to combustion frequency f of engine 101C1.4 times of the case. As shown in fig. 4, the natural frequency f of the torque fluctuation suppression device 10 is setVDDSpecific to combustion frequency f of engine 101CThe large torque makes it possible to reduce the torsion angle of the torque fluctuation suppression device 10.
Fig. 5 is a graph showing a relationship between the rotation speed of the engine 101 and the torque variation output from the torque variation suppression device 10. The horizontal axis represents the rotation speed of the engine 101, and the vertical axis represents torque variation (rotation speed variation). Line A represents the natural frequency f of the torque fluctuation suppression device 10VDDIs set to have a combustion frequency f with respect to the engine 101CThe same condition applies. In addition, line B represents the natural frequency fVDDSet to combustion frequency fCThe characteristic is 1.4 times that of the case where the line C is 1.4 times, the line D is 1.5 times, the line E is 1.6 times, and the line F is 1.7 times. In addition, line G represents the characteristics in the case where no dynamic vibration reducer is provided.
As shown in fig. 5, when the dynamic vibration reducer is not provided, the torque variation increases around 3000rpm of the engine speed. On the other hand, as shown by the line a, the natural frequency f of the torque fluctuation suppression device 10 is setVDDIs set to be equal to the combustion frequency fCIn the same case, the torque fluctuation does not increase, and in other regions, the torque fluctuation is smaller than in the case where the dynamic vibration reducer is not provided.
As shown by the lines B to F, even at the natural frequency F of the torque fluctuation suppression device 10VDDSet to combustion frequency fC1.2 to 1.7 times, the torque fluctuation is smaller as a whole than that in the case where the dynamic vibration absorber is not provided. On the other hand, as shown by the line D to the line F, the natural frequency F of the torque fluctuation suppression device 10 is knownVDDSet to combustion frequency fCWhen the torque is 1.5 times or more, the torque variation is amplified when the engine speed is around 3000 rpm. Therefore, the natural frequency f is preferably setVDDIs set as a combustion frequency fC1.4 times or less.
[ operation of Torque fluctuation suppression device ]
The operation of the torque fluctuation suppression device 10 will be described with reference to fig. 3 and 6.
Torque from the engine 101 is transmitted to the flywheel 2. In the present embodiment, torque is transmitted from the engine 101 to the flywheel 2 without passing through the damper 124.
When there is no torque variation during torque transmission, the flywheel 2 and the inertia ring 3 rotate in the state shown in fig. 3. In this state, the cam follower 421 of the cam mechanism 42 abuts on the radially innermost position (the central position in the circumferential direction) of the cam surface 412. In this state, the torsion angle between the flywheel 2 and the inertia ring 3 is substantially 0.
In fig. 3 and 6, the torsion angle between the flywheel 2 and the inertia ring 3 indicates the center position in the circumferential direction of the centrifugal member 41 and the cam surface 412, and the center position and the circumferential direction deviation of the cam follower 421.
If there is a torque variation during torque transmission, a torsion angle α is generated between the flywheel 2 and the inertia ring 3 as shown in fig. 6. Fig. 6 shows a case where the twist angle + α occurs on the + R side.
As shown in fig. 6, when a torsion angle + α is generated between the flywheel 2 and the inertia ring 3, the cam follower 421 of the cam mechanism 42 moves to the right in fig. 6 relatively along the cam surface 412. At this time, since a centrifugal force acts on the centrifugal element 41, a reaction force received from the cam follower 421 by the cam surface 412 formed on the centrifugal element 41 is in the direction and magnitude of P0 in fig. 6. By this reaction force P0, a first component force P1 in the circumferential direction and a second component force P2 in the direction of moving the centrifugal piece 41 toward the radially inner side are generated.
Then, the first component force P1 becomes a force that moves the flywheel 2 in the right direction in fig. 6 via the cam mechanism 42 and the centrifugal piece 41. That is, a force in a direction of decreasing the torsion angle α of the flywheel 2 and the inertia ring 3 acts on the flywheel 2. In addition, the centrifugal piece 41 is moved to the inner peripheral side against the centrifugal force by the second component force P2.
When a torsion angle is generated in the reverse direction, the cam follower 421 moves along the cam surface 412 to the left side in fig. 6, but the operation principle is the same.
As described above, when a torsion angle is generated between the flywheel 2 and the inertia ring 3 due to torque variation, the centrifugal force acting on the centrifugal element 41 and the action of the cam mechanism 42 cause the flywheel 2 to receive a force (the first component force P1) in a direction to reduce the torsion angle between the two. This force suppresses torque variation.
The above-described force for suppressing torque variation changes depending on the centrifugal force, that is, the rotation speed of the flywheel 2, and also changes depending on the rotational phase difference and the shape of the cam surface 412. Therefore, by appropriately setting the shape of the cam surface 412, the characteristics of the torque fluctuation suppression device 10 can be optimized in accordance with the engine specification and the like.
As described above, the force with which the torque fluctuation suppression device 10 suppresses the torque fluctuation changes depending on the rotation speed of the flywheel 2. Specifically, when the engine 101 rotates at a high speed, the flywheel 2 also rotates at a high speed, and thus the centrifugal force acting on the centrifugal member 41 is large. Therefore, the torsional rigidity of the variable stiffness mechanism 4 also increases, and the torsional angle between the flywheel 2 and the inertia ring 3 decreases. On the other hand, when the engine 101 rotates at a low speed, the flywheel 2 also rotates at a low speed, and thus the centrifugal force acting on the centrifugal element 41 is small. Therefore, the torsional rigidity of the variable stiffness mechanism 4 is also reduced, and the torsion angle between the flywheel 2 and the inertia ring 3 is increased.
In this way, the torsional rigidity of the variable rigidity mechanism 4 changes in accordance with the rotation speed of the flywheel 2. When the flywheel 2 rotates at a low speed, the torsional rigidity of the variable rigidity mechanism 4 is small, and therefore the torsion angle between the flywheel 2 and the inertia ring 3 tends to be large.
[ Clutch case Assembly ]
As shown in fig. 2, the clutch cover assembly 11 includes a clutch cover 111, a pressure plate 112, and a diaphragm spring 113.
The clutch cover 111 is annular and extends in the circumferential direction. The clutch cover 111 is fixed to the mounting portion 22 of the flywheel 2. Specifically, the outer peripheral portion of the clutch cover 111 is fixed to the annular projection 222 of the mounting portion 22 by a fastening member such as a bolt.
The platen 112 is an annular member. The pressure plate 112 is configured to press the clutch disk 121 against the flywheel 2. Specifically, the pressure plate 112 is biased toward the flywheel 2 by a leaf spring 113.
The diaphragm spring 113 is configured to urge the pressure plate 112 toward the flywheel 2. The pressure plate 112 is urged by the diaphragm spring 113 to press the clutch disc 121 toward the flywheel 2.
[ Clutch disc Assembly ]
The clutch disc assembly 12 has a clutch disc 121, an input side rotating body 122, an output side rotating body 123, and a damper 124. The clutch disk 121 is configured to frictionally engage with the flywheel 2.
The damper 124 elastically couples the input-side rotating body 122 and the output-side rotating body 123. The damper 124 has a plurality of coil springs. The coil springs are arranged at intervals in the circumferential direction.
[ modified examples ]
The present invention is not limited to the above-described embodiments, and various modifications and corrections can be made without departing from the scope of the present invention.
< modification 1 >
In the above-described embodiment, the flywheel 2 is illustrated as an example of the first rotating body, but the first rotating body is not limited thereto. That is, a rotor different from the flywheel 2 can be used as the first rotor.
< modification 2 >
In the above embodiment, the flywheel 2 has the ring gear 23, but is not limited to this structure. For example, a ring gear may be provided on the outer peripheral surface of the inertia ring 3. In this case, the engine 101 is started via the torque fluctuation suppression device 10.
< modification 3 >
In the above embodiment, the torque fluctuation suppressing device 10 is attached to the clutch device 100, but the torque fluctuation suppressing device 10 may be attached to another power transmission device such as a vibration damping device.
Claims (10)
1. A torque fluctuation suppression device, used in a gas, for suppressing a torque fluctuation of a prime mover,
the torque fluctuation suppression device includes:
a first rotating body configured to be rotatable;
a second rotating body configured to rotate together with the first rotating body and relatively rotatable with the first rotating body; and
a variable stiffness mechanism that changes torsional stiffness between the first rotating body and the second rotating body according to the number of revolutions of the first rotating body or the second rotating body,
the torque fluctuation suppression device is designed such that the natural frequency of the torque fluctuation suppression device is greater than the combustion frequency of the prime mover.
2. The torque fluctuation suppression device according to claim 1,
the torque fluctuation suppression device is designed such that the natural frequency of the torque fluctuation suppression device is 1.1 times or more the combustion frequency of the prime mover.
3. The torque fluctuation suppression device according to claim 1 or 2,
the torque fluctuation suppression device is designed such that the natural frequency of the torque fluctuation suppression device is 1.4 times or less the combustion frequency of the prime mover.
4. The torque fluctuation suppression device according to claim 1 or 2,
the first rotating body is a flywheel attached to a crankshaft.
5. The torque fluctuation suppression device according to claim 4,
the flywheel has:
a disc portion attached to the crankshaft; and
and an attachment portion attached to an outer peripheral portion of the circular plate portion.
6. The torque fluctuation suppression device according to claim 5,
the second rotating body is an inertia ring disposed between the circular plate portion and the mounting portion in the axial direction,
the mounting portion has a projection that penetrates the inertia ring and extends to the disc portion.
7. The torque fluctuation suppression device according to claim 5 or 6,
the flywheel has a ring gear formed on an outer peripheral surface of the mounting portion.
8. The torque fluctuation suppression device according to claim 1 or 2,
the variable stiffness mechanism includes:
a centrifugal member configured to be movable in a radial direction by a centrifugal force based on rotation of the first rotating body or the second rotating body; and
and a cam mechanism configured to receive a centrifugal force acting on the centrifugal member and convert the centrifugal force into a circumferential force in a direction in which a torsion angle between the first rotating body and the second rotating body is reduced.
9. The torque fluctuation suppression device according to claim 8,
the cam mechanism includes:
a cam surface formed on the centrifugal member; and
and a cam follower that abuts against the cam surface and transmits force between the centrifugal member and the second rotating body.
10. The torque fluctuation suppression device according to claim 1 or 2,
the variable stiffness mechanism is configured to increase torsional stiffness between the first rotating body and the second rotating body as the rotation speed of the first rotating body or the second rotating body increases.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020-180315 | 2020-10-28 | ||
| JP2020180315A JP2022071388A (en) | 2020-10-28 | 2020-10-28 | Torque fluctuation suppressing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215861525U true CN215861525U (en) | 2022-02-18 |
Family
ID=80261791
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122368990.2U Active CN215861525U (en) | 2020-10-28 | 2021-09-28 | Torque fluctuation suppression device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2022071388A (en) |
| CN (1) | CN215861525U (en) |
-
2020
- 2020-10-28 JP JP2020180315A patent/JP2022071388A/en active Pending
-
2021
- 2021-09-28 CN CN202122368990.2U patent/CN215861525U/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| JP2022071388A (en) | 2022-05-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107923481B (en) | Torque fluctuation suppression device, torque converter, and power transmission device | |
| US8651965B2 (en) | Vibration damping device | |
| JP5633577B2 (en) | Torsional vibration damping device | |
| JP6757680B2 (en) | Torque fluctuation suppression device, torque converter, and power transmission device | |
| JP7208826B2 (en) | rotating device | |
| JP2020133813A (en) | Rotary device | |
| JP5960559B2 (en) | Torque fluctuation reduction device | |
| JP7300284B2 (en) | Torque fluctuation suppressor and torque converter | |
| US5884740A (en) | Friction clutch | |
| WO2018199323A1 (en) | Vibration damping device | |
| WO2018016211A1 (en) | Dynamic vibration absorber | |
| US20190257398A1 (en) | Vibration damping device | |
| JP7263066B2 (en) | Torque fluctuation suppressor and torque converter | |
| CN215861525U (en) | Torque fluctuation suppression device | |
| JP6539180B2 (en) | Torque fluctuation suppressing device, torque converter, and power transmission device | |
| CN111609108A (en) | Rotating device | |
| US20200032875A1 (en) | Vibration damping device | |
| JP7218221B2 (en) | Torque fluctuation suppressor and torque converter | |
| JP2013164090A (en) | Torsional vibration damping device | |
| JP2013174294A (en) | Torsional vibration damping device | |
| JP6709764B2 (en) | Torque fluctuation suppressing device, torque converter, and power transmission device | |
| JP5754513B2 (en) | Torsional vibration damping device | |
| US11067149B2 (en) | Centrifugal pendulum | |
| KR102514969B1 (en) | Dual mass flywheel | |
| WO2020230651A1 (en) | Damper apparatus |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |