JP2017053460A - Hydraulic power transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic power transmission that comprises a dynamic vibration absorber, and that can be compactly constituted particularly in an axial direction.SOLUTION: A torque converter (1) comprises a pump (20) and a turbine (30) in a case (10) connected to an engine, and comprises a dynamic vibration absorber (80) that includes a rockable rocking body and that reduces vibration caused by the engine. The pump (20) and the turbine (30) comprise a pump core ring (22) and a turbine core ring (32) that support a plurality of blades (23) and (33) respectively. The pump core ring (22) and the turbine core ring (32) comprise inner surfaces opposed to each other and recessed outward on both sides, and a core space (C) is formed between the inner surfaces. At least a portion of the dynamic vibration absorber (80) is arranged in the core space (C).SELECTED DRAWING: Figure 1

Description

  The present invention relates to a fluid transmission device mounted on a vehicle, and more particularly to a fluid transmission device including a dynamic vibration absorber, and belongs to the technical field of a vehicle transmission device.

  A fluid transmission device that is used in a transmission such as an automatic transmission or a continuously variable transmission mounted on a vehicle and transmits engine output to a transmission mechanism is integrated with the case in a case connected to the output shaft of the engine. And a turbine that is disposed opposite to the pump and transmits power to and from the pump via a fluid.

  Here, as the fluid transmission device, one having a lock-up clutch that directly connects the pump side and the turbine side is known in order to improve the fuel efficiency of the engine.

  In such a fluid transmission device having a lock-up clutch, since the torque fluctuation of the engine is directly transmitted to the transmission mechanism side when the lock-up clutch is engaged, the lock-up clutch engagement area has recently been expanded to improve the fuel efficiency of the engine. As a result, the problem of vibrations caused by engine torque fluctuations tends to become apparent.

  For this reason, the necessity of providing a dynamic vibration absorber capable of reducing vibration in the fluid transmission device is increasing. For example, Patent Literature 1 discloses a fluid transmission device provided with a centrifugal pendulum damper as a dynamic vibration absorber. Yes.

JP 2012-077827 A

  However, since the pendulum damper is disposed on the axial engine side of the turbine in the fluid transmission device described in Patent Document 1, the axial dimension is increased, so that the axial dimension is shortened to be compact. It is desirable.

  In particular, in a fluid transmission device incorporated in a horizontal transmission whose axial center extends in the vehicle body width direction, if the axial dimension is large, the axial dimension of the entire transmission increases, and the frame member of the vehicle body Therefore, it is desirable to reduce the axial dimension and make the structure compact.

  Therefore, an object of the present invention is to enable a compact configuration in the axial direction, particularly in a fluid transmission device including a dynamic vibration absorber.

  In order to solve the above problems, the fluid transmission device according to the present invention is configured as follows.

First, the invention according to claim 1 of the present application is
In a case connected to a drive source, a pump that rotates integrally with the case, and a turbine that is disposed opposite to the pump and that transmits power to the pump via a fluid are provided. In a fluid transmission device including a dynamic vibration absorber that has a swingable swinging body and reduces vibration caused by the drive source,
The pump and the turbine each include a pump coring and a turbine coring that support a plurality of blades,
The pump coring and the turbine coring have inner surfaces that are opposed to each other and recessed on both outer sides, and form a core space between these inner surfaces,
At least a part of the dynamic vibration absorber is disposed in the core space.

The invention according to claim 2 is the fluid transmission device according to claim 1,
At least one of the pump coring or the turbine coring is an annular plane in which a part of the inner surface is orthogonal to the rotation axis.
The dynamic vibration absorber is attached to the annular plane.

The invention according to claim 3 is the fluid transmission device according to claim 1 or 2,
The pump coring and the turbine coring are provided with inner peripheral portions that face each other and extend close to each other on the inner peripheral side.

  With the above configuration, according to the invention described in claim 1 of the present application, the fluid transmission device is provided with the dynamic vibration absorber that reduces the vibration caused by the driving source, and at least a part of the dynamic vibration absorber is the pump core ring. Since a dynamic vibration absorber is provided by effectively utilizing the core space that has been hollow in the past, the dynamic vibration absorber is disposed in the core space formed by the turbine core ring. If it is not arranged, the external dimensions of the fluid transmission device, especially the axial dimension, will increase if an attempt is made to secure a space for installing the dynamic vibration absorber so as not to interfere with surrounding components. In particular, the axial dimension of the fluid transmission device is shortened. Thus, the fluid transmission device can be configured in a compact manner.

  According to the second aspect of the present invention, the pump core ring or the turbine core ring has an inner surface facing the core space formed in an annular plane, and by attaching a dynamic vibration absorber to the annular plane, the same width is obtained. Compared to the case where the core space having a height is not a flat surface, for example, a torus-shaped curved surface and its inner surface is formed, a larger core space can be effectively used as a storage space for a dynamic vibration absorber. The dynamic vibration absorber that vibrates in the core space can be more stably attached to the inner surface.

  According to the invention described in claim 3, the pump core ring and the turbine core ring have inner peripheral portions that are opposed to each other at a predetermined interval and extend toward the inner peripheral side, so that they extend to the outer peripheral side. As in the case where the outer peripheral portion is provided, the flow of fluid into the core space can be suppressed. Furthermore, since it does not protrude into the core space as in the case of the outer peripheral portion, a wider space can be secured as a storage space for the dynamic vibration absorber.

It is sectional drawing of the fluid transmission apparatus which concerns on 1st Embodiment of this invention. It is the arrow view which looked at the peripheral part of the dynamic vibration damper shown in FIG. 1 from the axial direction. It is a system diagram which shows the power transmission system of the fluid transmission apparatus of FIG. It is a graph explaining the effect of the vibration reduction by the dynamic vibration absorber (pendulum damper) of FIG. It is sectional drawing of the fluid transmission apparatus which concerns on 2nd Embodiment of this invention. It is the arrow view which looked at the peripheral part of the dynamic vibration damper shown in FIG. 5 from the axial direction. FIG. 6 is a system diagram showing a power transmission system of the fluid transmission device of FIG. 5. It is sectional drawing of the fluid transmission apparatus which concerns on 3rd Embodiment of this invention. It is a system diagram which shows the power transmission system of the fluid transmission apparatus which concerns on 4th Embodiment of this invention. It is a system diagram which shows the power transmission system of the fluid transmission apparatus which concerns on 5th Embodiment of this invention. It is a graph explaining the effect of the vibration reduction by the dynamic vibration absorber (dynamic damper) of FIG.

  Hereinafter, an embodiment in which the present invention is applied to a torque converter of an automatic transmission will be described.

(First embodiment)
First, the fluid transmission device according to the first embodiment will be described in detail with reference to FIGS.

[Overall configuration of torque converter]
As shown in FIG. 1, a torque converter 1 as a fluid transmission device according to this embodiment includes a case 10 that is incorporated in an automatic transmission and forms an outer shell thereof.

  The case 10 includes an engine crank that includes a plurality of stud bolts 16 fixed to an outer peripheral portion of a front cover 11 that constitutes an engine-side surface that is a drive source side, and a nut A that is screwed to the stud bolt 16. It is attached to the outer peripheral part of the drive plate D attached to the end part of the shaft B using the crank bolt C. As a result, the entire torque converter 1 is coupled to the crankshaft B and driven by the engine. In the following description, for the sake of convenience, the engine side (the right side in the figure) is the front, and the non-engine side (the left side in the figure) is the rear.

  The torque converter 1 includes a pump 20 that rotates integrally with the case 10 in a case 10 connected to the engine, a turbine 30 that is opposed to the engine, and an inner side of a facing portion between the pump 20 and the turbine 30. And a stator 40 disposed.

  The case 10 is filled with oil as a power transmission fluid, and is configured so that the oil can circulate through an annular path formed by the pump 20, the turbine 30, and the stator 40. Thus, the torque converter 1 can transmit the rotational force input to the pump 20 to the turbine 30 using the oil circulating in the annular path as a transmission medium. Hereinafter, each component of the torque converter 1 will be described in detail.

[pump]
The pump 20 includes a pump shell 21 constituting an outer shell, a pump core ring 22 constituting an inner shell, and a plurality of pump blades 23 supported between the pump shell 21 and the pump core ring 22. .

  The pump shell 21 is coupled to the non-engine side of the case 10 and is configured to be rotatable integrally with the case 10.

  The pump shell 21 is a ring-shaped member having a bowl-shaped cross section that bulges rearward, and an inner peripheral surface thereof is formed into a concave curved surface by press molding. A plurality of pump blades 23 are arranged radially at equal intervals in the circumferential direction on the inner peripheral surface of the pump shell 21, and the rear peripheral edge thereof is fixed by spot welding or the like. In the present embodiment, the front end 23a on the outer peripheral side of the pump blade 23 is formed in a straight line inclined forward toward the outer peripheral side.

  Further, the pump shell 21 has a pump sleeve 24 extending to the transmission mechanism side coupled to the inner peripheral end thereof by welding or the like. The front end of the pump sleeve 24 is engaged with a gear type oil pump (not shown) disposed behind the torque converter 1, so that the rotation of the crankshaft B causes the case 10, the pump shell 21 and the pump sleeve 24 to pass through. The lever oil pump is driven.

  The pump core ring 22 is a ring-shaped member having a bowl-shaped cross section that bulges rearward, and its inner surface is formed into a shape recessed backward by press molding, and a bottom surface constituting a part of the rear of the inner surface 22a is formed in the cyclic | annular plane orthogonal to a rotating shaft line. Moreover, the pump core ring 22 has an inner peripheral portion 22b that extends to the inner peripheral side.

  Further, the pump core ring 22 has a front base end portion of the pump blade 23 fixed to the outer peripheral surface thereof.

  Then, by rotating integrally with the case 10, the oil filled in the case 10 is guided by the pump blade 23 and the inner peripheral surface of the pump shell 21, while turning around the oil around the axis. A flow a from the rear to the front is generated.

[Turbine]
The turbine 30 includes a turbine shell 31 constituting an outer shell, a turbine core ring 32 constituting an inner shell, and a plurality of turbine blades 33 supported between the turbine shell 31 and the turbine core ring 32. .

  The turbine shell 31 is a ring-shaped member that is provided facing the pump shell 21 and has a hook-shaped cross section that bulges forward, and an inner peripheral surface thereof is formed into a concave curved surface by press molding. A plurality of turbine blades 33 are arranged radially at equal intervals in the circumferential direction on the inner peripheral surface of the turbine shell 31, and the front peripheral edge thereof is fixed by spot welding or the like. In the present embodiment, the rear end 33a on the outer peripheral side of the turbine blade 33 is parallel to the front end 23a of the pump blade 23 facing this, and is linearly inclined forward toward the outer peripheral side. Is formed.

  The turbine shell 31 is connected to a turbine hub 34 extending in the axial direction on the inner peripheral side thereof by a rivet or the like. The turbine hub 34 has a spline formed on the inner peripheral surface thereof, and is connected to the turbine shaft 25 extending to the transmission mechanism side of the automatic transmission on the inner peripheral side thereof by spline fitting.

  The turbine core ring 32 is a ring-shaped member having a bowl-shaped cross section that bulges forward, and its inner surface is formed into a shape recessed forward by press molding, and a bottom surface that constitutes a part of the front of the inner surface. 32a is formed in the cyclic | annular plane orthogonal to a rotating shaft line.

  As described above, the turbine core ring 32 and the pump core ring 22 have inner surfaces that are opposed to each other and that are recessed on both outer sides. Therefore, in the present embodiment, an annular shape having a substantially rectangular cross section is provided between these inner surfaces. The core space C is formed.

  Further, the turbine core ring 32 has an inner peripheral portion 32b extending to the inner peripheral side, and the inner peripheral portion 22b of the pump core ring 22 and the inner peripheral portion 32b of the turbine core ring 32 face each other and are close to each other. And it extends to the inner peripheral side.

  Furthermore, the rear base end portion of the turbine blade 33 is fixed to the outer peripheral surface of the turbine core ring 32.

  As described above, when the inner peripheral surface of the turbine shell 31 and the inner peripheral surface of the pump shell 21 are arranged to face each other, the flow a generated by the rotation of the pump 20 is introduced into the turbine shell 31, An inward flow b is formed by the peripheral surface and the turbine blade 33, and when the flow b presses the turbine blade 33, the turbine 30 receives a force in the circumferential direction and is driven in the same direction as the pump 20. . This driving force is transmitted to the speed change mechanism by the turbine shaft 25 connected to the turbine 30.

[Stator]
The stator 40 is disposed inside a facing portion between the pump 20 and the turbine 30, and a plurality of blades 43 extending in a radial direction between the inner ring portion 41 and the outer ring portion 42 are spaced apart at a predetermined interval in the circumferential direction. The entire structure is integrated. The blade 43 is disposed so as to be positioned between the inner peripheral end of the pump blade 23 in the pump 20 and the inner peripheral end of the turbine blade 33 in the turbine 30. Thereby, the flow b of the fluid that has driven the turbine 30 is introduced from the turbine 30 side, and a flow c passing between the blades 43 is formed. This flow c is formed on the curved portion 21a of the pump shell 21 on the inner peripheral side. Is introduced into the flow a to form a flow that circulates between the pump blades 23, 33, and 43 of the pump 20, the turbine 30, and the stator 40.

  Here, the outer ring portion 42 of the stator 40 has a circumferential groove 42a on its outer peripheral surface. The inner peripheral portion 22b of the pump core ring 22 and the inner peripheral portion 33b of the turbine core ring 32 are disposed so that the peripheral edge enters the peripheral groove 42a through a gap.

[One-way clutch]
The torque converter 1 also includes a one-way clutch 50 for supporting the stator 40 and realizing a torque increasing action by the stator 40. The one-way clutch 50 is disposed inside the stator 40, and includes an outer race 51, an inner race 52, and a plurality of sprags 53 interposed between the races 51, 52. The inner peripheral surface of the inner ring portion 41 of the stator 40 is press-fitted to the outer peripheral surface, and the inner race 52 is connected to the stator shaft 26 whose inner peripheral surface extends from a transmission case (not shown) of the automatic transmission. The stator shaft 26 is connected by spline fitting.

  The one-way clutch 50 is axially supported by thrust bearings 54 and 55 disposed between the turbine hub 34 positioned in front thereof and the pump sleeve 24 coupled to the pump shell 21 positioned rearward. The position of the direction is regulated, and thereby the stator 40 is positioned in the axial direction with respect to the pump 20 and the turbine 30.

  The stator 40 rotates freely by the idle rotation of the one-way clutch 50 when a pressing force acts on one surface of the blade 43 due to the flow c and receives a rotational force in one direction. When a pressing force acts on the other surface of 43 and receives a rotational force in the other direction, the one-way clutch 50 is fixed by being locked. At this time, a torque increasing action is generated, the torque input from the engine to the pump 20 is increased, and the torque is output from the turbine 30 to the turbine shaft 25.

[Lock-up clutch]
Furthermore, the torque converter 1 includes a lockup clutch 60 disposed between the turbine 30 and the case 10. The lockup clutch 60 directly connects the pump 20 side and the turbine 30 side, and includes a piston 61 provided in the case 10 so as to face the front cover 11 and a plurality of the pistons 61 fixed to the front surface of the piston 61. And a friction plate 62.

  The piston 61 is configured to be slidable in the axial direction with respect to the turbine hub 34, and a hydraulic chamber 4 is formed between the piston 61 and the turbine shell 31 to supply the fastening hydraulic pressure of the lockup clutch 60. Yes. When a predetermined fastening hydraulic pressure is supplied to the hydraulic chamber 4, the piston 61 slides backward, the friction plate 62 provided on the piston 61 is pressed against the front cover 11, and the lockup clutch 60 is fastened. The

[Damper spring mechanism]
The damper spring mechanism 70 bends in the rotational direction when the lock-up clutch 60 is engaged and reduces vibration caused by the engine, and is provided adjacent to the lock-up clutch 60.

  The damper spring mechanism 70 includes a spring receiving member 71 formed integrally with the piston 61 and extending rearward, and a plurality of springs 72 arranged at equal intervals in the circumferential direction by the spring receiving member 71. The damper spring 72 preferably has a wide torsion angle and low rigidity.

  The end of the spring holding plate 73 coupled to the outer peripheral surface of the turbine shell 31 and extending forward is engaged with one end of the spring 72. When the lockup clutch 60 is engaged, the rotation on the pump shell 21 side is performed. That is, the rotation of the crankshaft B is input to the spring receiving member 71 via the lock-up clutch 60 and is transmitted from the spring holding plate 73 to the turbine shell side, specifically to the turbine hub 34 via the damper spring 72. It is like that.

[Dynamic vibration absorber]
In this embodiment, the torque converter 1 includes a centrifugal pendulum damper 80 as a dynamic vibration absorber that has a swingable swinging body in the case 10 and reduces vibrations caused by the engine.

  A plurality of pendulum dampers 80 are arranged in the circumferential direction in a core space C surrounded by the pump core ring 22 and the turbine core ring 32. The pendulum damper 80 includes a mass member 81 that is an oscillating body, and a plurality of support pins 82 that slidably support the mass member 81 with respect to the turbine core ring 32 that is a support.

  As shown in FIG. 2, the mass member 81 is an arc-shaped member having a substantially rectangular cross section and extending in the circumferential direction. The mass member 81 has an arc-shaped guide hole 81a provided penetrating in the front-rear direction. A support pin 82 is inserted into 81 a so that it can swing with respect to the annular flat surface 33 a on the inner surface of the turbine core ring 32. In addition, the support pin 82 has a crown portion whose diameter is expanded at both ends so that the support pin 82 does not accidentally come out of the guide hole 81a of the mass member 81.

  In this way, when the pendulum damper 80 is coupled to the turbine core ring 32, when power is transmitted from the case 10 via the turbine hub 34 coupled to the turbine core ring 32, the pendulum damper 80 is Torque fluctuation due to the engine can be reduced.

[Operation of torque converter]
The operation of the torque converter 1 having the above configuration will be described below with reference to FIG.

  When the lockup clutch 60 is not engaged, the engine output is transmitted to the turbine 30 via oil from the pump 20 coupled to the case 10 that rotates integrally with the crankshaft B of the engine, and the turbine hub 34 and the turbine shaft. 25 to the transmission mechanism. In this case, the output torque of the engine is increased and output to the transmission mechanism at a gear ratio that can increase the torque of the stator 40.

  On the other hand, when the lock-up clutch 60 is engaged, the pump 20 side and the turbine 30 side are connected via the lock-up clutch 60, so that the engine output of the case 10 that rotates together with the crankshaft B of the engine is integrated. It is transmitted from the front cover 11 to the lockup clutch 60, the damper spring mechanism 70, and the turbine hub 34 coupled to the turbine 30, and is transmitted to the transmission mechanism via the turbine shaft 25. In this case, transmission to the speed change mechanism without passing through oil improves torque transmission efficiency compared to when the lock-up clutch 60 is not engaged, thereby improving the fuel efficiency of the engine.

  Since the pendulum damper 80 is attached to the turbine core ring 32 coupled to the turbine hub 34 to which power from the engine is transmitted, vibrations caused by the engine both when the lockup clutch 60 is not engaged and when the lockup clutch 60 is engaged. It is comprised so that may be reduced. In this embodiment, since the centrifugal pendulum damper 80 is used as the dynamic vibration absorber, as shown in FIG. 4, according to the pendulum damper 80, the mass member 81 swings to correspond to the target resonance frequency. Vibration can be reduced not only over the engine speed but also over a wide range of engine speeds. In this example, a comparison example in which only a lock-up damper is provided when combined with a four-cylinder engine is compared with an example in which a pendulum damper is added to the lock-up damper. The embodiment is aimed at a secondary resonance peak that is likely to cause a problem with a booming sound in the comparative example. The embodiment in which the pendulum damper is added shows that the secondary resonance peak can be almost eliminated, and the base of the resonance peak connected thereto is widely attenuated.

(Second Embodiment)
Next, the fluid transmission device according to the second embodiment will be described in detail with reference to FIGS. The fluid transmission device 101 according to the second embodiment is the same as the fluid transmission device 1 according to the first embodiment except that the dynamic vibration absorber is different, and the same components are denoted by the same reference numerals and described. Is omitted.

  As shown in FIG. 5, the torque converter 101 as the fluid transmission device according to the second embodiment also has a pump 20, a turbine 30, a stator 40, a one-way clutch 50, a lock-up clutch 60, and a damper spring mechanism 70. These are housed in the case 10 and the case 10 is filled with oil.

  Similar to the first embodiment, the torque converter 101 includes a centrifugal pendulum damper 180 as a dynamic vibration absorber that has a oscillating body that can oscillate in the case 10 and that reduces vibration caused by a drive source. This embodiment is different from the pendulum damper 80 of the first embodiment only in that the pendulum damper 180 is attached to the pump core ring 22 instead of the turbine core ring 32.

  A plurality of pendulum dampers 180 are arranged in the circumferential direction in a core space C surrounded by the pump core ring 22 and the turbine core ring 32. In the case of the present embodiment, the pendulum damper 180 includes a mass member 181 that is an oscillating body and a plurality of support pins 182 that support the mass member 181 with respect to the pump core ring 22 that is a support. Have.

  As shown in FIG. 6, the mass member 181 is an arc-shaped member having a substantially rectangular cross section and extending in the circumferential direction, and has an arc-shaped guide hole 181 a provided penetrating in the front-rear direction. The support pin 182 is inserted into the shaft 181a so as to be swingable with respect to the annular flat surface 23a of the inner surface of the pump core ring 22.

  From the above, as shown in FIG. 7, the pendulum damper 180 is attached to the pump core ring 22 of the pump 20 to which power from the engine is transmitted. Also, the engine is configured to reduce vibrations caused by the engine. Also in this embodiment, since the centrifugal pendulum damper 180 is used as the dynamic vibration absorber, as shown in FIG. 4, according to the pendulum damper 180, the mass member 181 swings to a target resonance frequency. Vibration can be reduced not only over the corresponding engine speed but also over the wide engine speed.

(Third embodiment)
Next, the fluid transmission device according to the third embodiment will be described in detail with reference to FIG. The fluid transmission device 201 according to the third embodiment is the same as the fluid transmission device 1 according to the first embodiment except that the dynamic vibration absorber is different, and the same components are denoted by the same reference numerals and described. Is omitted.

  As shown in FIG. 8, in the torque converter 201, as in the first embodiment, a centrifugal pendulum damper is provided as a dynamic vibration absorber that has a swingable swinging body in the case 10 and reduces the vibration caused by the drive source. 280 is provided. The pendulum damper 280 is attached to the turbine core ring 32 in the same manner as in the first embodiment. In the present embodiment, the pendulum damper 280 is disposed outside the core space C surrounded by the pump core ring 22 and the turbine core ring 32. It differs from the pendulum damper 80 of the first embodiment only in that a part is provided.

  The pendulum damper 280 includes a mass member 281 that is a rocking body, and a plurality of support pins 282 that support the mass member 281 with respect to the turbine core ring 32 that is a support.

  In the case of the present embodiment, the mass member 281 is an arc-shaped member extending in the circumferential direction, and a main body portion 281a having a substantially rectangular cross section disposed in the core space C, and the main body portion 281a are provided integrally with the outer peripheral direction. And a convex portion 281b protruding outside the core space C. The main body portion 281a is formed with an arcuate guide hole 281c provided so as to penetrate in the front-rear direction, and the support pin 282 is inserted into the guide hole 281a to thereby form an annular plane on the inner surface of the turbine core ring 32. It is supported so as to be able to swing with respect to 33a.

  From the above, like the first and second embodiments, the pendulum damper 280 is configured to reduce vibration caused by the engine both when the lock-up clutch 60 is not engaged and when it is engaged, and the mass member 181. The vibration can be reduced not only over the engine speed corresponding to the target resonance frequency but also over the engine speed with a wide base.

  In this embodiment, the pendulum damper 280 is attached to the turbine core ring 32, but may be attached to the pump core ring 22 as in the second embodiment.

(Fourth embodiment)
Next, a fluid transmission device according to a fourth embodiment will be described in detail with reference to FIGS. 9 and 11. The fluid transmission device 301 according to the fourth embodiment is the same as the fluid transmission device 1 according to the first embodiment except that the dynamic vibration absorber is different, and the same components are denoted by the same reference numerals and described. Is omitted.

  As shown in FIG. 9, the torque converter 301 includes a dynamic damper 380 as a dynamic vibration absorber. The dynamic damper 380 is at least partially disposed in the core space C. In this embodiment, the dynamic damper 380 has a mass body attached to the turbine core ring 32 of the turbine 30 via an elastic member. Yes.

  The pendulum damper 380 is configured to reduce vibration caused by the engine both when the lock-up clutch 60 is not engaged and when it is engaged. In the case of this embodiment, the dynamic damper 380 is used as a dynamic vibration absorber. Therefore, as shown in FIG. 11, the resonance frequency generated in the engine can be moved out of the normal range by the vibration of the mass body of the dynamic damper 380.

(Fifth embodiment)
Next, a fluid transmission device according to a fifth embodiment will be described in detail with reference to FIGS. 10 and 11. The fluid transmission device 401 according to the fifth embodiment is the same as the fluid transmission device 301 according to the fourth embodiment except that the target to which the dynamic vibration absorber is attached is different. The reference numerals are attached and the description is omitted.

  As shown in FIG. 10, the torque converter 401 includes a dynamic damper 480 as a dynamic vibration absorber, as in the fourth embodiment. The dynamic damper 480 is at least partially disposed in the core space C. In this embodiment, the dynamic damper 480 has a mass body attached to the pump core ring 22 of the pump 20 via an elastic member. Yes.

  Similar to the fourth embodiment, the pendulum damper 480 is configured to reduce vibration caused by the engine both when the lock-up clutch 60 is not engaged and when it is engaged, and as shown in FIG. By the vibration of the mass body of the damper 480, the resonance frequency generated in the engine can be moved out of the normal range.

  As described above, according to the present embodiment, the torque converter 1 is provided with the dampers 80, 180, 280, and 380 that reduce vibration caused by the engine, and the dampers 80, 180, 280, and 380 include at least the pump core ring 22 and the turbine. In the torque converter 1 provided with the dampers 80, 180, 280, 380, the dampers 80, 180, 280, 380 and the pump core ring 22 are arranged in the core space C formed by the core ring 32. Compared with the case where it is disposed outside the core space formed by the turbine core ring 32, the axial dimension of the torque converter 1 is particularly shortened, and the torque converter 1 can be configured compactly.

  Further, according to the present embodiment, the pump core ring 22 or the turbine core ring 32 has the inner surfaces facing the core space C formed on the annular planes 22a and 32a, and the dampers 80, 180, and 280 are formed on the annular planes 22a and 32a. By attaching 380, the core space C having the same width and height is not flat, but, for example, a larger core space C is formed in the damper 80, compared to the case where the inner surface is formed by a torus-like curved surface. The dampers 80, 180, 280, 380 that can be used effectively as storage spaces for 180, 280, 380 and vibrate in the core space C can be more stably attached to the inner surface.

  Further, according to the present embodiment, the pump core ring 22 and the turbine core ring 32 have the inner peripheral portions 22b and 33b that are opposed to each other at a predetermined interval and extend to the inner peripheral side, so that the outer peripheral side is provided. Similarly to the case where the outer peripheral portion to be extended is provided, the flow of fluid into the core space C can be suppressed. Furthermore, since it does not protrude into the core space C as in the case of the outer peripheral portion, a wider space can be secured as a storage space for the dampers 80, 180, 280 and 380.

  The present invention is not limited to the illustrated embodiments, and various improvements and design changes can be made without departing from the scope of the present invention.

  For example, in this embodiment, the case where the pendulum dampers 80, 180, 280, and 380 are used as the dynamic vibration absorber has been described. However, the present invention is not limited to this, and for example, a dynamic damper, a viscous damper, or the like may be used. .

  As described above, according to the present invention, a fluid transmission device including a dynamic vibration absorber can be configured to be compact in the axial direction in particular, so that the fluid transmission device or a manufacturing technology of a vehicle on which the fluid transmission device is mounted is provided. It may be suitably used in the field.

1, 101, 201, 301 Torque converter (fluid transmission)
10 Case 20 Pump 22 Pump core ring 22b Inner peripheral surface (inner surface) of pump core ring
23 Pump blade
30 Turbine 32 Turbine core ring 32b Inner peripheral surface (inner surface) of turbine core ring
33 Turbine blade (blade)
80, 180, 280 Pendulum damper (dynamic vibration absorber)
380, 480 Dynamic damper (dynamic vibration absorber)
C core space

Claims (3)

In a case connected to a drive source, a pump that rotates integrally with the case, and a turbine that is disposed opposite to the pump and that transmits power to the pump via a fluid are provided. In a fluid transmission device including a dynamic vibration absorber that has a swingable swinging body and reduces vibration caused by the drive source,
The pump and the turbine each include a pump coring and a turbine coring that support a plurality of blades,
The pump coring and the turbine coring have inner surfaces that are opposed to each other and recessed on both outer sides, and form a core space between these inner surfaces,
At least a part of the dynamic vibration absorber is disposed in the core space. At least one of the pump coring or the turbine coring is an annular plane in which a part of the inner surface is orthogonal to the rotation axis.
The fluid transmission device according to claim 1, wherein the dynamic vibration absorber is attached to the annular plane. The fluid transmission device according to claim 1, wherein the pump core ring and the turbine core ring are provided with inner peripheral portions that face each other and are close to each other and extend toward the inner peripheral side.

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