WO2020012905A1

WO2020012905A1 - Rotational variation reducing device

Info

Publication number: WO2020012905A1
Application number: PCT/JP2019/024399
Authority: WO
Inventors: 小林　篤; 村田　豊
Original assignee: ユニプレス株式会社
Priority date: 2018-07-11
Filing date: 2019-06-20
Publication date: 2020-01-16
Also published as: JPWO2020012905A1; JP6656491B1

Abstract

An elastic body damper mechanism 18 constituting a rotational variation reducing device provided with a planetary gear mechanism is disposed outside the casing 5 of a transmission 4 and is provided with a prime mover-side input member 26 and a first output member 28. An elastic body 30 having torsional rigidity in a rotational direction is disposed between the input member 26 and the output member 28. In addition to a first output shaft 34, a second output shaft 36 branches from the elastic body damper mechanism 18 at a position closer to the input member 26 than the elastic body 30. First and second output shafts 34, 36 are introduced into the casing through a wall surface section of the casing 5. The planetary gear mechanism 16 is mounted in the casing 5 of the transmission 4. One of the three rotating elements of the planetary gear mechanism 16 is rotationally driven by the first output shaft 34, and another one is rotationally driven by the second output shaft 36. The remaining rotational element which is not involved in the transmission of power functions as a damper mass.

Description

Rotation fluctuation reduction device

The present invention relates to a rotation fluctuation reduction device that reduces rotation fluctuation of a prime mover and transmits the rotation fluctuation to an output shaft of a transmission, and more particularly to a rotation fluctuation reduction device provided with a planetary gear mechanism.

As a rotation fluctuation reduction device that reduces the rotation fluctuation of the prime mover and transmits it to the output shaft of the transmission, there is a torque converter that is configured by combining an elastic damper mechanism using a coil spring as an elastic body with a planetary gear mechanism. In a combination with a lock-up clutch in a transmission equipped with a lock-up clutch, it is widely used for the purpose of reducing rotation fluctuation at the time of direct drive by engagement of the lock-up clutch. In this type of rotation fluctuation reduction device, in most cases, the elastic body is arranged in the rotation direction between the input member and the output member, and one of the rotating elements of the planetary gear mechanism including the carrier, the ring gear, and the sun gear is provided on the input member. The other one is connected to the output member, and the other one of the rotating elements is arranged so as to be free to participate in power transmission. The free rotating element increases the damper mass in the rotating inertial system and can contribute to the reduction of rotation fluctuation. The connection between the elastic damper mechanism and the rotating element and the planetary gear mechanism is the same in that a straight-type pinion is used, but various things that are slightly different in the connection between the elements have been proposed. (Patent Documents 1 to 3). Further, as a device related to the same person as the present applicant, a device using a so-called Ravigneaux gear as a pinion has been proposed (Patent Document 4). The above-described rotation fluctuation reducing device configured by combining an elastic damper mechanism with a planetary gear mechanism is generally intended for use in combination with a lock-up clutch of a torque converter. In vehicles equipped with a torque converter, from the viewpoint of improving fuel consumption efficiency, engagement of the lock-up clutch is performed from a low rotation speed region. This is an effective means as a countermeasure for suppressing specific noise such as muffled noise which becomes a problem. Further, the torque converter oil used as a torque transmission medium in the torque converter can be used for lubrication of the gear meshing portion of the planetary gear mechanism as it is, and the elastic damper mechanism is housed in the torque converter housing together with the planetary gear mechanism. Therefore, there is an advantage that a lubrication device dedicated to lubrication is not required.

JP 2011-558557 JP-A-11-159595 JP-A-10-184799 WO2016 / 47660

(4) Conventionally, a rotation fluctuation reducing device configured by combining an elastic damper mechanism with a planetary gear mechanism has been generally intended for use in a torque converter housing as described above. However, in the case of installation in a torque converter, the planetary gear mechanism is installed coaxially with the drive shaft and a coil spring is arranged on the outer peripheral side. There is a concern that smooth elastic deformation of the coil spring may be hindered due to friction with the support portion that receives the deformation of the coil spring under a force, and a problem such as a limitation on the degree of freedom of the elastic characteristic of the coil spring may occur. There was also concern. Furthermore, spatial restrictions in the torque converter make it difficult to respond to more sophisticated control of vibration damping characteristics, such as changing the manner of connection between the coil spring and the rotating element by installing a clutch or the like. Also, from the viewpoint of marketability, there has been a demand for the applicability of the excellent vibration damping characteristics of the rotation fluctuation reduction device combining the elastic damper mechanism with the planetary gear mechanism to a hybrid vehicle, which is a more recent trend. .

A rotation fluctuation reduction device according to the present invention is a rotation fluctuation reduction device that reduces the rotation fluctuation of a prime mover and transmits the reduced rotation fluctuation to an output shaft. The rotation fluctuation reduction device includes at least an input member on the prime mover side and an output member on the output shaft side. An elastic damper mechanism configured by arranging an elastic body having torsional rigidity in the rotational direction between the output shafts; a carrier configured by rotatably supporting a plurality of pinions; A planetary gear mechanism having at least three rotating gear elements, and at least two gears meshing with each other, and a resilient damper mechanism provides an elasticity in addition to the output shaft (hereinafter referred to as a first output shaft). A second output shaft for taking a rotary motion on the input member side of the body is branched, one of the rotating elements of the planetary gear mechanism is provided by the first output shaft, and the other is provided by a second output shaft. Drive each by And at least one of the remaining rotating elements not involved in power transmission functions as a damper mass, and the elastic damper mechanism houses a planetary gear mechanism and lubricating oil for lubricating the planetary gear mechanism. And a connection of the first output shaft and the second output shaft to corresponding rotating elements of the planetary gear mechanism is made through a wall portion of the housing. It has become.

The housing for accommodating the planetary gear mechanism is also a housing for accommodating a speed change mechanism for shifting the rotation of the prime mover and transmitting the speed to an output shaft, and the first output shaft forms an input shaft of the speed change mechanism. Can be.

The elastic body damper mechanism includes an input member on the prime mover side, an output member on the output shaft side, and an elastic body for connecting the input member and the output member in a rotational direction, and the second output shaft is connected to the input member. It is possible to adopt a configuration of branching more.

The elastic damper mechanism connects the input member on the prime mover side, the output member on the first output shaft side, the intermediate member between the input member and the output member, and the rotational direction connection between the input member and the intermediate member. And a second elastic body that connects the intermediate member and the output member in a rotational direction, and the second output shaft can be branched from the input member.

Further, the elastic damper mechanism includes an input member on the prime mover side, an output member on the first output shaft side, an intermediate member installed between the input member and the output member, and an intermediate member provided between the input member and the intermediate member. And a second elastic body that connects between the intermediate member and the output member in the rotational direction, wherein the second output shaft is branched from the intermediate member. can do.

Further, the elastic body damper mechanism includes an input member on the prime mover side, an output member on the first output shaft side, a first elastic body that connects the input member and the output member in a rotational direction, a damper mass, A second elastic body that couples the damper mass to the output member without participating in power transmission, wherein the second output shaft is branched from the input member. Further, it is possible to install a clutch that is engaged and disengaged between the second output shaft extending in the housing and the planetary gear mechanism.
In addition, bearings with seals on the inner peripheral side and the outer peripheral side can be provided for sealing the first output shaft and the second output shaft with the wall of the housing.

The elastic damper mechanism and the planetary gear mechanism are separated from each other, and the planetary gear mechanism is installed in a housing that can supply lubricating oil, so that the planetary gear mechanism can operate stably even in a dry environment. It is possible to add a vibration damping effect by the gear mechanism.

By separating the elastic damper mechanism and the planetary gear mechanism, the degree of freedom in designing each structure and layout is increased, and the optimal design of the rotation fluctuation reducing device using the planetary gear mechanism becomes possible. That is, in the conventional planetary gear type rotation fluctuation reduction device built in the torque converter, a large centrifugal force applied to the elastic body is imposed due to a structural constraint that the elastic body must be arranged on the outer peripheral side of the planetary gear mechanism. There is a problem that the degree of freedom in designing the elastic body for obtaining the desired vibration damping characteristics is limited due to measures against the above (for example, a low-rigidity coil spring cannot be used). The planetary gear mechanism, which needs to be installed inside the housing, and the elastic damper mechanism, which does not require lubrication, can be arranged outside, so the degree of freedom in the design of the elastic body is increased. The restriction on the setting of vibration damping characteristics (particularly, low rigidity) is reduced, and a design closer to the optimal design can be performed.

In addition, since the degree of freedom in the structural design of the elastic damper mechanism can be increased, it is easy to add a mass element (intermediate member, etc.) via the elastic body, and by combining with the planetary gear mechanism, a further vibration suppression effect can be obtained. We can expect improvement. In short, the present invention relates to an elastic body using a planetary gear mechanism, which attenuates a rotation fluctuation component included in the driving force from a prime mover and transmits the transmission to a transmission mechanism, with respect to an elastic damper mechanism not using a planetary gear mechanism. It is possible to maximize the advantage of the damper mechanism.

FIG. 1 is a diagram showing a configuration of a rotation fluctuation reducing device according to a first embodiment of the present invention. FIG. 2 is a diagram showing a configuration of a rotation fluctuation reducing device according to a second embodiment of the present invention. FIG. 3 is a cross-sectional view (along the line VII-VII in FIG. 5) of a detailed configuration of a main part of a rotation fluctuation reducing device according to a second embodiment of the present invention shown in a diagram in FIG. FIG. FIG. 4 is a perspective view showing each part of the rotation fluctuation reducing device in an exploded state. FIG. 5 is a front view of the elastic fluctuation damper mechanism in the rotation fluctuation reducing device of FIG. 3 in an assembled state. FIG. 6 is a sectional view taken along section line VI-VI in FIG. FIG. 7 is a sectional view taken along section line VII-VII in FIG. FIG. 8 is a sectional view taken along section line VIII-VIII in FIG. FIG. 9 is a perspective view illustrating a preferred assembly procedure of the intermediate member shown in FIG. FIG. 10 is a diagram showing a configuration of a rotation fluctuation reducing device according to a third embodiment of the present invention. FIG. 11 shows a detailed configuration of a main part of a rotation fluctuation reducing device according to a third embodiment of the present invention shown in a diagrammatic view in FIG. 10 as a sectional view on one side of a rotation center. FIG. 12 is a diagram showing a configuration of a rotation fluctuation reducing device according to a fourth embodiment of the present invention. FIG. 13 is a diagram showing a configuration of a rotation fluctuation reducing device according to a fifth embodiment of the present invention. FIG. 14 is a graph showing the frequency characteristics of the rotation fluctuation of the transmission input shaft in the embodiment (first and second embodiments) of the present invention in comparison with the prior art. FIG. 15 is a graph showing the frequency characteristics of the rotation fluctuation of the transmission input shaft in the embodiment of the present invention (the first embodiment and the fifth embodiment including the clutch) in comparison with the conventional technology.

FIG. 1 is a schematic diagram of a first embodiment of the present invention. In this embodiment, a generator is driven by a prime mover 2 (internal combustion engine), and a driving motor for driving driving wheels is driven by the generator. The present invention is directed to a device for reducing rotation fluctuation in a drive train of a hybrid vehicle. Describing this drive train, the prime mover 2 drives a generator (not shown) of the hybrid vehicle. Although a generator is not shown, a transmission 4 is provided for optimally controlling the speed of rotation from the prime mover 2 via the flywheel 3 and transmitting the rotation to the generator. The transmission 4 includes a casing 5 (a housing of the present invention), a transmission mechanism 6 disposed in the casing 5, an input shaft 7, and an output shaft 8. A second input shaft 10 is provided in addition to the input shaft 7 (hereinafter referred to as a first input shaft 7) for connection between an elastic damper mechanism and a planetary gear mechanism, which will be described later, and the first input shaft 7 and the second input shaft are provided. The shaft 10 is concentrically arranged and is supported by the casing 5 while sealing the lubricating oil. The speed change mechanism 6 includes an input gear 11 on a first input shaft 7 that meshes in series, an output gear 12 on an output shaft 8, and an intermediate gear 14 between the input gear 11 and the output gear 12. The casing 5 is sealed with lubricating oil for lubricating the meshing portion between the gears 11, {12, {14}, and if necessary, well-known means for circulating the lubricating oil are provided. Further, the flywheel 3 provided on the output shaft side of the prime mover 2 is for dealing with the rotational fluctuation inevitably appearing on the output shaft side of the prime mover 2, but it alone cannot sufficiently reduce the rotational fluctuation. Therefore, the rotation fluctuation reducing device 16 is provided. The rotation fluctuation reducing device 16 includes an elastic damper mechanism 18 and a planetary gear mechanism 20. According to the present invention, the planetary gear mechanism 20 is installed in the casing 5 of the transmission 4 and needs to be shared with the lubrication of the meshing part of the transmission mechanism 6 because it is necessary to lubricate the meshing portions of the gears constituting the planetary gear mechanism 20. ing. On the other hand, the elastic damper mechanism 18 is installed outside the casing 5 because lubrication with lubricating oil is not required for the intended operation.

The elastic damper mechanism 18 installed outside the casing 5 and constituting the rotation fluctuation reducing device 16 of the present invention is an elastic member that connects the input member 26, the output member 28, and the input member 26 and the output member 28 in the rotational direction. And a body 30. The input member 26 is connected to the prime mover 2 via the flywheel 3. The elastic damper mechanism 18 has a first output shaft 34 from the output member 28 and a second output shaft 36 branched from the input member 26. The planetary gear mechanism 20 according to the embodiment of the present invention installed in the casing 5 is a so-called Ravigneaux type planetary gear mechanism, and has a stepped pinion 38 (a plurality of which are arranged at intervals in the circumferential direction as is well known). ) Is rotatably supported (not shown in FIG. 1 (see FIGS. 3 and 4)), and a small-diameter sun gear 40 meshed with the large-diameter portion 38-1 of the stepped pinion 38 on the inner peripheral side. And a large-diameter sun gear 42 meshing on the inner peripheral side with the small-diameter portion 38-2 (the pitch of the teeth is the same as the large-diameter portion 38-1) of the stepped pinion 38. As is well known, a Ravigneaux type planetary gear mechanism can include up to five rotating elements. In this embodiment, a carrier 46 that supports a stepped pinion 38, a small diameter sun gear 40, and a large diameter sun gear 42 And three rotating elements.

The connection between the elastic damper mechanism 18 and the planetary gear mechanism 20 will be described. The first output shaft 34 connected to the output member 28 is directly connected to the first input shaft 7 in the casing 5 of the transmission 4. The large-diameter sun gear 42 of the planetary gear mechanism 20 is installed on the first input shaft 7, and the large-diameter sun gear 42 is configured to rotate integrally with the first input shaft 7. The second output shaft 36 branched from the input member 26 of the elastic damper mechanism 18 extends as it is to the second input shaft 10 of the transmission 4, and in the casing 5, the small diameter sun gear 40 of the planetary gear mechanism 20. Are rotated integrally with the second input shaft 10.

The operation of the rotation fluctuation reducing device 16 according to the above-described embodiment will be described. The elastic body 30 is arranged in series with the drive train extending from the prime mover 2 to the first input shaft 7 of the transmission 4 to change the output torque of the prime mover 2. The elastic body 30 functions so as to suppress the rotation fluctuation. On the other hand, the large-diameter sun gear 42 on the first input shaft 7 connected thereto by the first output shaft 34 is driven, and the small-diameter sun gear 40 on the second input shaft 10 connected thereto by the second output shaft 36. Driving force is transmitted. The large-diameter sun gear 42 meshes with the small-diameter portion 38-2 of the stepped pinion 38, and the small-diameter sun gear 40 meshes with the large-diameter portion 38-1 (integral with the small-diameter portion 38-2) of the stepped pinion 38. If the output shaft of the prime mover 2 has no rotational fluctuation, the stepped pinion 38 rotates integrally with the carrier 46 (not shown), and the stepped pinion 38 does not rotate relative to the small-diameter sun gear 40 and the large-diameter sun gear 42. On the other hand, with respect to the rotation fluctuation of the output shaft of the prime mover 2, the difference in the number of teeth between the small-diameter portion 38-2 and the large-diameter portion 38-1 causes a difference in rotation speed between the large-diameter sun gear 42 and the small-diameter sun gear 40. The stepped pinion 38 rotates in accordance with the difference in number, and the stepped pinion 38 revolves with a carrier 46 (not shown in FIG. 1) that rotatably supports the stepped pinion 38. Such an inertial force caused by the rotation and revolution of the stepped pinion 38, together with the elastic force of the elastic body 30 of the elastic body damper mechanism 18, can effectively suppress the rotation fluctuation from the prime mover 2. . The operation of the rotation fluctuation reduction device 16 of the present embodiment is performed by a rotation fluctuation reduction device including an elastic damper mechanism and a planetary gear mechanism housed in a housing of a conventionally proposed various types of torque converters (Patent Document 1). Operation equivalent to 1 to 4) is achieved. In the present embodiment, the output from the elastic damper mechanism 18 that operates the elastic body 30 having the torsional rigidity in the rotation direction is output from the first output shaft 34 from the output member 28 and the first output shaft 34 from the input member 26. Because the two output shafts 36 are divided into two systems, the planetary gear mechanism 20 that requires lubrication of the gear meshing portion is installed in the casing 5, and the elastic damper mechanism 18 that does not require lubrication is disposed outside the casing 5. It becomes possible to install it. Therefore, it is not necessary to dispose the elastic damper mechanism 18 in a space having a large restriction such as a housing of the torque converter while effectively utilizing the space of the casing 5 in which the size of the space is restricted. A great degree of freedom in design can be obtained.

FIG. 2 is a schematic view of a rotation fluctuation reducing device 116 according to a second embodiment of the present invention. The difference from the rotation fluctuation reducing device 16 of FIG. 1 is only an elastic damper mechanism 118 installed outside the casing 5. The elastic body of the elastic body damper mechanism 118 is composed of a first elastic body 30A and a second elastic body 30B, and an intermediate member is provided between the first elastic body 30A and the second elastic body 30B. The feature is that 44 is arranged, and there is no difference in other configurations from FIG. Therefore, the same reference numbers are used for other parts.

The intermediate member 44 disposed between the first elastic body 30A and the second elastic body 30B in the elastic body damper mechanism 118 serves as an additional mass for torsional vibration in the drive train of the transmission 4 from the prime mover 2, It is possible to more effectively suppress the torque fluctuation component in the drive train.

FIGS. 3 to 8 show a structural example of the rotation fluctuation reducing device 116 of the second embodiment shown as a diagram in FIG. In FIG. 3, the casing 5 is partially illustrated, and a partition wall between the casing 5 and an elastic damper mechanism 118 installed outside the casing 5 is formed by 5-1 (see also FIG. 4). A partition wall for supporting the planetary gear mechanism 20 and the first input shaft 7 of the transmission 4 arranged in S is indicated by 5-2 (see also FIG. 4). The transmission 4 in FIG. 1 is also disposed in the space S, but only the input gear 11 is shown. The input gear 11 has an inner spline 11-1 meshed with a spline 7-1 of the first input shaft 7, and the input gear 11 rotates integrally with the first input shaft 7. As the configuration of the planetary gear mechanism 20, a stepped pinion 38 also shown in FIG. 2, a small-diameter sun gear 40 meshed with the large-diameter portion 38-1 of the stepped pinion 38 on the inner peripheral side, and a small-diameter portion of the stepped pinion 38 The large-diameter sun gear 42 meshing on the inner peripheral side is shown at 38-2. The large-diameter sun gear 42 has an inner peripheral spline 42-1 meshed with the spline 7-1 of the first input shaft 7, and the large-diameter sun gear 42 rotates integrally with the first input shaft 7. FIG. 2 shows a carrier 46 (formed by welding a carrier plate 46-2 to a carrier base 46-1), and a stepped pinion 38 is rotatably mounted on the carrier 46 by a pin 47. (See also FIG. 4 for the configuration of the carrier 46).

The structure of the elastic damper mechanism 118 installed outside the casing 5 will be described. The input member 26, the output member 28, the

elastic members

30A and 30B, and the intermediate member 44 in FIGS. This is shown in the schematic diagram of FIG. The positional relationship between the input member 26 and the output member 28 on the rotation axis is opposite to that in FIG. As shown in the exploded view of FIG. 4, the

elastic bodies

30A and 30B are realized as coil springs arranged alternately in the circumferential direction on the same diameter surface. Hereinafter, instead of the

elastic bodies

30A and 30B, the

coil springs

30A and 30B will be described. 30B. The three

coil springs

30A and 30B are alternately arranged in the rotation direction. In FIG. 4, the input member 26 is formed with three spring receiving portions 26-1 protruding radially outward and spaced apart in the circumferential direction. Each spring receiving portion 26-1 includes a pair of spring receiving seats 26-1a and 26-1b separated in the rotation direction. On both sides of each spring receiving part 26-1, spring inner peripheral holding parts 26-2a, # 26-2b and spring outer peripheral holding parts 26-9a, # 26-9b project outward and bend. The outer peripheral portion of the spring receiving portion 26-1 of the input member 26 is bent to form an extended portion 26-3 extending in the axial direction toward the prime mover and a flywheel mounting portion 26-4 at the tip thereof. A flyhole mounting bolt hole 26-4 'is formed in the flywheel mounting portion 26-4'. Further, the input member 26 forms a cylindrical portion 26-6 corresponding to the second output shaft 36 in the schematic diagram of FIG. 2 and a cylindrical portion 26-7 serving as the second input shaft 10 (FIG. 3 also). reference).

The output member 28 includes three spring receiving portions 28-1 protruding outward in the radius at equal intervals in the circumferential direction. In FIG. 4, each spring receiving portion 28-1 forms a pair of spring receiving seats 28-1a and 28-1b that are separated in the rotation direction. Each spring receiving portion 28-1 includes spring inner peripheral holding portions 28-2a and # 28-2b and outer peripheral holding portions 28-4a and # 28-4b that are bent outward on both sides. When viewed from the front, the spring receiving portion 28-1 of the output member 28 has substantially the same shape as the spring receiving portion 26-1 of the input member 26, and in the assembled state (neutral state described later) of FIG. The spring receiving portion 26-1 of the input member 26 is not visible because the spring receiving portion 26-1 of the input member 26 is just hidden behind (the outer flywheel mounting portion 26-4 is visible). In the neutral state, the pair of spring receiving portions 26-1a and 26-1b of each spring receiving portion 26-1 of the input member 26 is connected to the pair of spring receiving portions 28-1 of the corresponding spring receiving portion 28-1 of the output member 28. Each of the seats 28-1a and # 28-1b also overlaps in the rotational direction, and the spring seats 26-1a and # 26-1b are shown in parentheses in FIG. Also, a plurality of rivet holes 28-3 are formed in the inner peripheral portion of the output member 28, and in the assembling process, the rivet holes 28-3 integrate the separate mounting member 50 with the output member 28 by the rivets 52. (See FIG. 3).

In FIG. 4, the intermediate member 44 is joined by rivets 45 so as to be sandwiched between the front auxiliary plate 44 'and the rear auxiliary plate 44 "at three peripheral portions in the circumferential direction (see also FIG. 8). The intermediate member 44 cooperates with the front and rear auxiliary plates 44 ', # 44 "to move the window frame-shaped opening 44-1 for accommodating the coil springs 30A, 30B in the circumferential direction. Are formed at equal intervals. Each window frame-shaped opening 44-1 is provided with a pair of spring seats 44-1a,... 44-1b (spring seats 44-1a,... The planes which are flush with the spring seats 44-1a and 44-1b of the auxiliary plates 44 'and # 44 "also play a role, but are not denoted for the sake of simplicity). , # 44-1b, the front auxiliary plate 44 'and the rear auxiliary plate 44 "form a bent portion in a direction away from each other, whereby a pair of spring outer peripheral holding portions 44'-1a," 44 "-are respectively provided. 1a and 44'-1b, forming "44" -1b. The intermediate member 44 has a cylindrical portion 44-4 (rotatably fitted to the boss portion 50-2 of the mounting member 50 for the input member 28) for maintaining a centered state with respect to the center of rotation at the center. The input member 26 and the output member 28 are connected by

coil springs

30A and 30B as described later.

FIG. 4 also shows the configuration of the planetary gear mechanism 20, and it can be seen that the planetary gear mechanism 20 is isolated from the elastic damper mechanism 118 by the partition wall portion 5-1 of the casing 5. The carrier 46 of the planetary gear mechanism 20 is configured by fixing a carrier plate 46-2 to a carrier base 46-1. Four stepped pinions 38 are attached to the carrier 46 by pins 47 therebetween. In FIG. 4, the small-diameter sun gear 40 is hidden by the carrier 46 and is not visible, but is engaged with the large-diameter portion 38-1 of the stepped pinion 38, and the large-diameter sun gear 42 is engaged with the small-diameter portion 38-2 of the stepped pinion 38. Attached to engage. FIG. 4 also shows the first input shaft 7 (including the above-described splines 7-1 and # 7-2) and the partition wall 5-2 supporting the first input shaft 7.

The assembly of the input member 26, the output member 28, the

coil springs

30A and 30B, and the intermediate member 44 will be described. With the input member 26 in front of the intermediate member 44, the extension 26-3 of the input member 26 is connected to the intermediate member. 44 so as to fit into the window frame-shaped opening 44-1. The first coil spring 30A is disposed between the spring seat 26-1a of the spring seat 26-1 of the input member 26 and the spring seat 44-1a of the intermediate member 44 which is circumferentially close to and opposed to the spring seat 26-1a. On the other hand, the second coil spring 30B is disposed and accommodated between the spring seat 44-1b of the intermediate member 44 and the spring seat 26-1b of the input member 26 which is circumferentially close to and opposed to the spring seat 44-1b. In other words, the positional relationship is such that the spring receiving portion 26-1 is split between the first coil spring 30A and the second coil spring 30B at the middle in the circumferential direction in one window frame-shaped opening 44-1. . In this state, the first coil spring 30A and the second coil spring 30B are balanced in the amount of contraction so as to generate a set load, and each spring receiving portion 26-1 has a window frame-shaped opening 44-1 for accommodating the same. Is located in the middle in the circumferential direction. In this state, the output member 28 is mounted. That is, the spring receiving portion 28-1 of the output member 28 is positioned so as to overlap the spring receiving portion 26-1 of the input member 26 from above, and between the overlapping spring receiving portion 28-1 and the spring receiving portion 26-1. The spring seat 28-1a and the spring seat 26-1b are aligned with the spring seat 26-1b in the rotation direction. Therefore, each of the spring receiving portions 28-1 of the output member 28 is axially extended from the corresponding spring receiving portion 26-1 of the input member 26 by the inner surfaces 28-1 'and 2626-3' of the extending portions 26-3. The elastic member damper mechanism 118 shown in the sectional view of FIG. 3 in which the intermediate member 44 is positioned between the output member 28 and the input member 26 can be inserted while sliding. (Neutral state of the elastic damper mechanism 118).

In the above description of FIGS. 4 to 8, the intermediate member 44 constituting the elastic damper mechanism 118 is formed by integrating the front auxiliary plate 44 ′ and the rear auxiliary plate 44 ″ by rivets 45 from the beginning of assembly. Although it is described as having a piece structure, this is because it is convenient to explain the configuration of each part of the intermediate member 44 in relation to its function, but this is not the case. The preferred assembly procedure is somewhat different and will be useful for an understanding of the construction and function of the intermediate member 44, which will now be described with reference to FIG. The member 44 is separated from the front auxiliary plate 44 ′ and the rear auxiliary plate 44 ″, and the input member 26 is disposed between the rear auxiliary plate 44 ″ and the intermediate member 44. An auxiliary plate 44 'is located. The inter-member 44, the front auxiliary plate 44 ', and the rear auxiliary plate 44 "include a plurality of pairs of aligned rivet holes 44a," 44'a., "44" a. On the plate 44 ", the outer peripheral surface of the extension 26-3 is the inner peripheral concave surface 44" -2 of the rear auxiliary plate 44 "(the inner peripheral surface of the window frame-shaped opening 44-1 when the intermediate member 44 is assembled. ). In this state, the intermediate member 44 and the front auxiliary plate 44 'are aligned, and each rivet 45 is inserted into each pair of aligned rivet holes 44a, # 44'a, # 44 "a, and the tip is caulked. As a result, the intermediate member 44 integrates the front auxiliary plate 44 'and the rear auxiliary plate 44 "with the input member 26 positioned between the rear auxiliary plate 44" and the first and second coil springs 30A. , # 30B and subsequent steps are the same as those already described with reference to FIGS.

The connection of the elastic damper mechanism 118 assembled in this way to the prime mover side and the transmission side will be described. In FIG. 3, the flyhole 3 has a ring shape, and is attached to the flywheel mounting portion 26-4 of the input member 26. It is fastened together with the connecting plate 54 by the bolt 58 and the nut 60. The connecting plate 54 is fastened to the end face of the output shaft side member 64 of the motor by a bolt 62. The input member 26 forms a cylindrical portion 26-6 just before the partition 5-1 of the casing 5, and this corresponds to the second output shaft 36 in the schematic diagram of FIG. The second output shaft 36) forms a cylindrical portion 26-7 which is introduced into the casing 5 as it is, and the cylindrical portion 26-7 forms the second input shaft 10 of the transmission in FIG. The outer peripheral spline teeth 26-7 'of the cylindrical portion 26-7 are spline-fitted with the spline teeth 40-1 of the small-diameter sun gear 40 of the planetary gear mechanism 20, and transmit rotational driving force. As for the output member 28, a mounting member 50 integrally connected to the output member 28 by a rivet 52 is formed on an inner peripheral spline 50-1 (formed on the inner circumference of the central boss 50-2 of the mounting member 50) as shown in FIG. The spline 7-2 at the tip of the first input shaft 7, which is also the first output shaft 34 in the schematic diagram, is spline-fitted. By fitting the cylindrical support portion 44-4 of the intermediate member 44 to the outer peripheral surface of the spline fitting portion (the outer peripheral surface of the center boss portion 50-2), the intermediate member 44 is aligned with the center of rotation. You can rotate while always maintaining. In FIG. 3, reference numeral 65 denotes a fastener such as a snap ring for fixing the assembly of the elastic damper mechanism 118 on the shaft. Thrust bearings 74, {75, {76} of each part inside the transmission 4 are shown.

The shaft sealing structure between the two output shafts of the elastic damper mechanism 118 and the two input shafts of the transmission including the planetary gear mechanism 20 in this embodiment will be described. The inner peripheral side bearing 66 and the outer peripheral side bearing 68 are arranged concentrically on the partition wall portion 5-1. Both the inner peripheral side bearing 66 and the outer peripheral side bearing 68 can be configured as a well-known sealed bearing (such as a ball bearing). That is, on the partition wall portion 5-1 side, the inner peripheral bearing 66 is disposed between the transmission rotating shaft 7 and the cylindrical portion 26-6 of the input member 26, and the outer peripheral bearing 68 is connected to the cylindrical portion 26-6. It is arranged between the inner peripheral parts 5-1 'of the partition wall part 5-1. Thereby, the support and shaft sealing of the two coaxial input / output shafts between the elastic damper mechanism 118 and the casing 5 by the partition wall of the casing 5 can be achieved. Further, a bearing 70 is provided for supporting the first input shaft 7 on the partition 5-2 side (see also FIG. 4).

動作 The operation of the rotation fluctuation reduction device 116 shown in FIGS. 3 to 8 will be described focusing on the elastic damper mechanism 118. FIG. 5 shows a case where there is no rotation fluctuation as described above. When the input member 26 is twisted clockwise from this state, each spring receiving portion 26-1 of the input member 26 compresses the first coil spring 30A via the spring receiving seat 26-1a, and the compressed first coil spring 30A is pressed. The coil spring 30A twists the intermediate member 44 through the spring seat 44-1a of the window frame-shaped opening 44-1. The torsion of the intermediate member 44 is adjusted by the second coil spring through the spring seat 44-1b. The compressed second coil spring 30B twists the output member 28 clockwise through the spring seat 28-1b of the spring receiving portion 28-1. Conversely, when the input member 26 is twisted counterclockwise, each spring receiving portion 26-1 of the input member 26 compresses the second coil spring 30B via the spring receiving seat 26-1b, and the compressed The second coil spring 30B twists the intermediate member 44 via the spring seat 44-1b of the window frame-shaped opening 44-1. The twist of the intermediate member 44 is caused by the first spring via the spring receiver 44-1a. The compressed first coil spring 30A twists the output member 28 counterclockwise via the spring seat 28-1a of the spring receiving portion 28-1 of the output member 28 by compressing the coil spring 30A. Rotational fluctuations can be suppressed by the torsional elasticity of the

coil springs

30A and 30B in such torsional vibration and the revolution of the carrier 46 and the rotation of the stepped pinion 38, which are free rotating elements in the planetary gear mechanism 20, and Further, the addition of the mass element of the intermediate member 44 between the

coil springs

30A and 30B can further increase the rotation fluctuation suppressing effect.

FIG. 10 shows a schematic diagram of a rotation fluctuation reducing device 216 according to a third embodiment of the present invention, which is similar to the embodiment of FIG. 2 except that the branch of the second output shaft 36 is shown in FIG. From the input member 26 to the elastic member damper mechanism 218 as the intermediate member 44. The manner in which the

output shafts

34 and 36 are connected to the rotating elements of the planetary gear mechanism 20 is the same, and the

output shafts

34 and 36 are stepped on the large-diameter and small-diameter sun gears 42 and 40 on the

input shafts

7 and 10 respectively connected to the

output shafts

34 and 36. There is no difference in the configuration in which the small and large suture portions 38-2 and 38-1 of the pinion 38 are engaged. The rotation fluctuation in the output of the prime mover 2 appears as a rotation speed difference between the intermediate member 44 and the output member 28, and the large and small sun gears 42 and # 40 have different rotations due to the rotation of the intermediate member 44 and the output member 28 at different rotation speeds. This is driven by a number, and the rotation of the carrier 46, which is a free rotating element not involved in power transmission, and the rotation of the stepped pinion 38 cooperate with the

coil springs

30A and 30B to suppress rotation fluctuation.

FIG. 11 illustrates the schematic structure of FIG. 10 as a specific cross-sectional view of an actual machine similar to that of FIG. 3 of the second embodiment. A cylindrical portion 44-5 is formed as the second output shaft 36, and is introduced into the partition 5-1 of the casing 5 to form an integral cylindrical portion 44-6 as the second input shaft 10 of the transmission 4. The cylindrical portion 44-6 is spline-fitted with the small diameter sun gear 40 of the planetary gear mechanism 20. As in FIG. 3, the inner peripheral bearing 66 and the outer peripheral bearing 68 with seals are arranged concentrically. The inner peripheral bearing 66 is disposed between the first input shaft 7 of the transmission 4 and the cylindrical portion 44-5 of the intermediate member 44, and the outer peripheral bearing 68 is disposed between the cylindrical portion 44-5 of the intermediate member 44 and the partition wall. 5-1 is disposed between the inner peripheral portions 5-1 ′. Thereby, the support and shaft sealing of the two coaxial input / output shafts between the elastic damper mechanism 218 and the casing 5 by the partition of the casing 5 can be achieved. In this embodiment, the input member 26 is free on the output shaft side, and the intermediate opening 26-5 is smoothly rotatably fitted while maintaining the same concentricity with the cylindrical portion 44-5 of the intermediate member 44. .

FIG. 12 shows a rotation fluctuation reducing device 316 according to a fourth embodiment of the present invention. The rotation fluctuation reduction device 316 of this embodiment has the same basic configuration as that of the first embodiment, but is free (independent of power transmission) of the output member 28 via the second elastic body 80 through the damper mass. 82 is different from the first embodiment. In this embodiment, the second elastic body 80 and the damper mass 82 do not contribute to the transmission of the driving force, and constitute a so-called dynamic vibration absorber. By adding a dynamic vibration absorber to the planetary gear mechanism 20, it is possible to change and expand the vibration damping characteristics of the prime mover 2 against rotation fluctuations.

FIG. 13 shows a rotation fluctuation reducing device 416 according to a fifth embodiment of the present invention. This embodiment has the same basic configuration as that of the first embodiment, except that an adjustment clutch 88 is provided in the transmission 4. The adjustment clutch 88 is provided between the small-diameter sun gear 40 which is an input portion of the planetary gear mechanism 20 and the second output shaft 36 of the elastic damper mechanism 18. The adjustment clutch 88 can be configured as a known friction clutch. The adjustment clutch 88 can have functions of fastening, breaking, and incompletely fastening (arbitrarily sliding) the input from the output shaft 36 to the planetary gear mechanism 20. When the adjusting clutch 88 is engaged, the vibration damping function of the planetary gear mechanism 20, that is, the planetary damper is enabled, and when the adjusting clutch 88 is engaged, the planetary gear mechanism 20 is shut off to disable the function of the planetary damper. Can be. In addition, depending on the situation of use, the adjustment clutch 88 may be slid into an incompletely engaged state, thereby protecting the planetary gear mechanism against excessive input and improving the vibration damping effect due to the occurrence of hysteresis required by the vibration system. Can be.

FIGS. 14 and 15 show the frequency characteristics of the rotational fluctuations of the transmission input shaft after numerical analysis (this analysis method is well known and results are shown only) by modeling the vehicle drive system from the prime mover 2 to the output shaft. , A is a conventional damper having only a coil spring, b is a planetary damper having no intermediate mass such as the first embodiment (FIG. 1), and c is a planetary mass having an intermediate mass such as the second embodiment (FIG. 2). The results of the damper are shown in FIG. 14, and the characteristic b of the planetary damper has a temporary peak frequency on the lower frequency side as compared with the conventional damper characteristic a in FIG. Therefore, it can be seen that the damper characteristic a is superior to the conventional damper characteristic a in that the rotation fluctuation at a low rotation around 20 Hz, which is a problem in noise control, can be suppressed well. As a countermeasure against noise, it is particularly advantageous to suppress the rotation fluctuation around 20 Hz, so that the planetary damper has an advantage here. However, on the side of the frequency (high rotation) exceeding about 60 Hz, the characteristic a of the conventional damper is superior to the characteristics b and c of the planetary damper, which can be said to be a weak point of the planetary damper.

15 shows a case where with a modulating clutch 88 by the embodiment of FIG. 13 d, by d', frequency of f ₁ indicates the point of blocking clutch of around 50 Hz, to f ₁ is adjusted clutch 88 substantially matches the frequency characteristic becomes d and properties of planetary damper b by engagement of, characteristics similar to the conventional damper characteristic a as d'at f ₁ after a frequency to block the modulating clutch 88 is obtained, the spring only It is possible to obtain more ideal characteristics obtained by splicing convenient portions of the conventional damper and the planetary damper.
Explanation of reference numerals

2. Motor (internal combustion engine)
3: Flywheel 4: Transmission 5: Casing (housing of the present invention)
5-1 5-2 Partition wall part of casing 6 Transmission mechanism 7 First input shaft 8 of transmission mechanism Output shaft 10 of transmission mechanism Second input shaft 11 of transmission mechanism Input gear of transmission mechanism
16, 116, 216, 316, 416… Rotation fluctuation reduction device
18, 118, 218 elastic body damper mechanism 20 planetary gear mechanism of elastic body damper mechanism 26 input member of elastic body damper mechanism 26-1 spring receiving part
26-1a, 26-1b ... Spring seat 28 ... Output member of elastic damper mechanism 28-1 ... Spring receiver
28-1a, 28-1b ... spring seat 30 ... elastic body 30A of elastic body damper mechanism ... first elastic body (coil spring)
30B: second elastic body (coil spring)
34, a first output shaft of the elastic damper mechanism 36, a second output shaft 38 of the elastic damper mechanism 38, a stepped pinion 40 of the planetary gear mechanism, a small sun gear 44 of the planetary gear mechanism, an intermediate member
44-1… Window frame opening
44-1a, 44-1b ... spring seat 44 '... front auxiliary plate 44 "... rear auxiliary plate 46 ... carrier of planetary gear mechanism 46-1 ... carrier plate
46-2… 46-2
54 ... Connecting plate 64 ... Motor output shaft side member 66 ... Inner peripheral side bearing 68 ... Outer peripheral side bearing 80 ... Second elastic body 82 ... Damper mass 88 ... Adjustment clutch

Claims

A rotation fluctuation reducing device that reduces the rotation fluctuation of a motor and transmits the rotation to an output shaft, comprising at least an input member on the motor side and an output member on the output shaft side, and having a torsional rigidity in the rotational direction between the input member and the output shaft. An elastic damper mechanism configured by disposing an elastic body having the carrier, a carrier configured to rotatably support a plurality of pinions, and at least two gears individually meshed with the pinions, A planetary gear mechanism having at least three rotary gear elements, and in addition to the output shaft (hereinafter referred to as a first output shaft), a rotary motion is extracted from the elastic body on the input member side from the elastic body. A second output shaft is branched, one of the rotating elements of the planetary gear mechanism is driven to rotate by the first output shaft, and the other is driven to rotate by the second output shaft, respectively. At least one remaining A rotating element that does not contribute to the power transmission of the planetary gear mechanism functions as a damper mass, and the elastic damper mechanism houses a planetary gear mechanism and forms an oil bath for lubricating oil for lubricating the planetary gear mechanism. A rotation fluctuation reducing device installed outside the housing, and wherein the first output shaft and the second output shaft are connected to corresponding rotating elements of the planetary gear mechanism via a wall surface of the housing.
2. The rotation fluctuation reducing device according to claim 1, wherein the elastic body damper mechanism includes an input member, an output member, and an elastic body that connects the input member and the output member in a rotational direction, and the second member includes: The output shaft of is a rotation fluctuation reduction device branched from the input member.
2. The rotation fluctuation reducing device according to claim 1, wherein the elastic body damper mechanism includes an input member, an output member, an intermediate member installed between the input member and the output member, and an input member and an intermediate member. A first elastic member connecting the intermediate member and the output member in a rotational direction, and a second elastic member connecting the intermediate member and the output member in a rotational direction, wherein the second output shaft is branched from the input member. Fluctuation reduction device.
2. The rotation fluctuation reducing device according to claim 1, wherein the elastic body damper mechanism includes an input member, an output member, an intermediate member installed between the input member and the output member, and an input member and an intermediate member. A first elastic member that connects the intermediate member and the output member in a rotational direction, and a second elastic member that connects the intermediate member and the output member in a rotational direction, wherein the second output shaft is branched from the intermediate member. Fluctuation reduction device.
2. The rotation fluctuation reducing device according to claim 1, wherein the elastic damper mechanism includes an input member, an output member, a first elastic member that connects the input member and the output member in a rotational direction, and a damper mass. 3. A second elastic body that connects the damper mass to the output member so as not to be involved in power transmission, wherein the second output shaft is branched from the input member.
The rotation fluctuation reducing device according to any one of claims 1 to 5, further comprising a clutch that engages and disengages the second output shaft in a housing with respect to a planetary gear mechanism.
The rotation fluctuation reducing device according to any one of claims 1 to 6, wherein the first output shaft and the second output shaft on a wall portion of the housing are connected to corresponding rotation elements of a planetary gear mechanism. A rotation fluctuation reducing device provided with a shaft sealing device for sealing a part.
8. The rotation fluctuation reducing device according to claim 7, wherein the housing that houses the planetary gear mechanism houses a power transmission mechanism that receives and transmits rotation from a motor from an output shaft, and the first output shaft is a power transmission mechanism. And a connecting portion of the second output shaft to the planetary gear mechanism forms a cylindrical shaft concentric with the input shaft of the transmission mechanism, and the shaft sealing device comprises an input shaft and a cylindrical shaft of the transmission mechanism. And a second sealed bearing between the cylindrical shaft and the housing.