JP2010084933A - Torsional vibration reducing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torsional vibration reducing device stabilizing torsional performance. <P>SOLUTION: The torsional vibration reducing device includes retainer plates 6a, 6b rotatable connected to a crankshaft 1; an output plate 10 arranged concentrically with the retainer plates 6a, 6b and rotatably supported and connected to an input shaft of a transmission; and springs 12, 13 connecting the retainer plates 6a, 6b to the output plate 10 circumferentially. Annular spacer members 15 formed of resin are interposed between an axial space between the retainer plates 6a, 6b and the output plate 10, and each spacer member 15 is mounted to the output plate 10. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a torsional vibration reduction device, in which a spacer member is interposed between axial directions of an input member and an output member.

  Some automobiles use an automatic transmission, and a torsional vibration reducing device is used to prevent the torsional vibration caused by torque fluctuations of the engine from being transmitted to the automatic transmission.

As a conventional torsional vibration reduction device, for example, a device described in Patent Document 1 is known. An inner peripheral portion of the input member 13 is coupled to an engine crankshaft via a bolt, and an output member is rotatable between the input member 13 and an auxiliary member 49 having an outer peripheral portion connected to the input member 13 in the axial direction. 21 is provided, the inner peripheral portion of the output member 21 is coupled to the input shaft of the transmission, and the input member 13 and the output member 21 are connected in the circumferential direction by a compression spring 59. In order to hold the output member 21 with no gap between the input member 13 and the auxiliary member 49 in the axial direction, the bearing 19 and the disc spring 53 are provided in the axial direction of the output member 21 with respect to the input member 13. Is regulated.
DE19820503A1

  However, in the torsional vibration reducing device described in Patent Document 1, the biasing force of the disc spring 53 acts in the axial direction. The receiving part may be deformed and the torsional performance may not be stable.

  Further, since the input member 13 and the output member 21 are directly centered via the bearing 31 interposed near the axis between the input member 13 and the output member 21, the crankshaft 1 and the input shaft 83 of the transmission Even if there is misalignment between them, the misalignment cannot be absorbed by the portion of the torsional vibration reducing device that connects them, or all components of the torsional vibration reducing device such as FIG. The ring gear attached to the drive plate 11 and the sensing plate for monitoring engine rotation cannot be accurately centered on the crankshaft 1 on the input side.

  Therefore, an object of the present invention is to provide a torsional vibration reduction device that solves the above-described problems.

  The invention according to claim 1 is a rotatable input member connected to a crankshaft, an output member arranged concentrically with the input member and rotatably supported and connected to an input shaft of a transmission, and the input member And an elastic member that connects the output member in a circumferential direction, and either one of the input member and the output member is configured by connecting a pair of side plates, and the other is an axial direction of the pair of side plates In the torsional vibration reduction device constituted by the central plate disposed between them, an annular spacer member is interposed between the central plate and each side plate in the axial direction, and each spacer member is attached to the central plate. It is mounted on both sides.

  According to this invention, since the spacer member is interposed between the pair of input members and the output member sandwiched between the pair of input members in the axial direction, the contact between the input member and the output member is prevented, Generation of sound and wear due to contact are suppressed.

  According to a second aspect of the present invention, in the torsional vibration reducing device according to the first aspect, the same component is used as each of the spacer members, and each of the spacer members includes an engaging protrusion protruding from one side surface. The engagement holes are arranged along the circumferential direction so that either one of the engagement protrusions faces the other engagement hole in a state where the spacer members are overlapped with each other. It is inserted through a through hole formed in the center plate, is engaged with the engagement hole, and is mounted on both sides of the center plate.

  According to the present invention, the pair of spacer members are arranged so as to sandwich the center plate, and the pair of spacer members are circular so that the engaging protrusion protruding from one of the pair of spacer members faces the other engaging hole. By positioning relative to each other in the circumferential direction, the engaging protrusions of the spacer members are inserted into the through holes formed in the central plate, and the engaging protrusions are fitted into the other engaging holes so that both sides of the central plate are A pair of spacer members are attached to the.

  According to a third aspect of the present invention, in the torsional vibration reduction device according to the first or second aspect, the side plate is formed with an arc surface centered on the axis of the side plate, while the side plate is provided with a cylindrical portion. And a contact portion protruding in the radial direction and contacting the circular arc surface is intermittently formed in the circumferential direction.

  According to this invention, when the shaft center of the input member and the output member is slightly shifted, the contact portion of the spacer member that contacts the arc surface of the side plate is deformed, so that the input member and the output member are assembled. The deformed portion of the contact portion wears with the passage of time thereafter, and misalignment is absorbed. The spacer member functions as a spacer for a relatively long time in the axial direction, while achieving a desired wear in a relatively short time in the radial direction. Can be fulfilled with.

  The invention according to claim 4 is the torsional vibration reduction device according to any one of claims 1 to 3, wherein the annular spacer member is divided in a circumferential direction to form a spacer piece, and the spacer piece is It is characterized by being mounted intermittently at the same circumferential position on both sides of the central plate.

  According to this invention, since the spacer pieces are intermittently mounted along the circumferential direction of the center plate, the material of the spacer pieces is saved, and the manufacturing cost of the torsional vibration reducing device is suppressed. In addition, since the annular spacer member is large, processing accuracy is deteriorated. However, since the spacer member is divided into small spacer pieces, the processing accuracy is improved.

  According to the torsional vibration reducing device of the first aspect, since the spacer member does not have a function of applying a pressing force in the axial direction like a disc spring, the spacer member is rubbed strongly in the axial direction with the input member or the output member. It can be worn as a spacer for a long period of time.

  According to the torsional vibration reducing device of the second aspect, since the same spacer member is provided on both sides of the central plate, it is easy to align both in the circumferential direction, and the assembling work is easy. Moreover, since the same spacer member is used, the complexity is eliminated and the manufacturing cost is suppressed. Further, since the pair of spacer members are provided with the center plate sandwiched therebetween and the pair of spacer members are engaged with each other, once the pair of spacer members are coupled to the center plate, they can be handled integrally.

  According to the torsional vibration reducing device of the third aspect, the contact portion of the spacer member mounted on the center plate contacts the arc surface of the side plate, so that the input member is centered with respect to the output member. When the shaft center is misaligned, the contact portion is deformed and incorporated, and thereafter, the deformed portion is worn and the misalignment is absorbed.

  According to the torsional vibration reducing device according to the fourth aspect, since the spacer pieces are intermittently mounted along the circumferential direction of the center plate, the material of the spacer pieces is saved, and the manufacturing cost of the torsional vibration reducing device is suppressed. The In addition, since the annular spacer member is large, processing accuracy is deteriorated. However, since the spacer member is divided into small spacer pieces, the processing accuracy is improved.

Embodiments of a torsional vibration reducing device according to the present invention will be described below.
(A) Embodiment 1
First, the first embodiment will be described.
(Constitution)
As shown in FIG. 1 (b), a drive plate 2 is coupled to an engine crankshaft 1 via a reinforcing plate 3 by a crank bolt 4. The drive plate 2 is centered on the end surface of the crankshaft 1 via a pin (not shown). A ring gear 5 that is rotationally driven by a cell motor (not shown) when the engine is started is welded to the outer periphery of the drive plate 2. Since the drive plate 2 is centered on the crankshaft 1, the ring gear 5 can function accurately. Instead of the ring gear 5, a sensing member having irregularities in the circumferential direction may be attached in order to sense engine rotation.

  The drive plate 2 is connected with retainer plates 6a and 6b as a pair of side plates constituting an input member. That is, a ring-shaped inertia mass 8 is coupled to the left surface of the drive plate 2 via a drive plate bolt 7, and the outer periphery of the retainer plates 6 a and 6 b arranged on the left side of the inertia mass 8 They are coupled via rivets 9 arranged on the inner side of the drive plate bolt 7. A single output plate 10 serving as a central plate is provided between the axial directions of the retainer plates 6a and 6b. The output plate 10 is configured as shown in FIG. 4. A center hole 10a having spline teeth is intermittently formed at the center of the output plate 10, and the outer peripheral portion of the output hub 11 is press-fitted into the center hole 10a. Thus, the outer peripheral portion of the center hole 10a is assembled and is plastically deformed. For this reason, both are firmly connected in the rotation direction. Spline teeth 11a are formed on the inner peripheral surface of the output hub 11, and an input shaft of a transmission (not shown) is splined.

  In order to connect the pair of retainer plates 6a and 6b and the output plate 10 in the circumferential direction, springs 12 and 13 as elastic members are provided. The springs 12 and 13 are both constituted by nested springs. The spring 12 is constituted by springs 12a and 12b having the same length and different outer diameters. The spring 13 is constituted by springs 13a and 13b having different lengths and outer diameters. It is configured. The springs 12 and 13 are alternately arranged in the circumferential direction so that the rotational balance can be maintained.

  In order to hold the springs 12 and 13 between the retainer plates 6a and 6b in the axial direction, a plurality of windows 6c and 6d facing each other are formed in the retainer plates 6a and 6b along the circumferential direction. Restricting portions 6e and 6f for restricting the springs 12 and 13 in the radial direction are formed on the side and the outer peripheral side, while restricting portions 6g and 6h are formed on the inner peripheral side and the outer peripheral side of the window 6d. . Further, in order to hold the springs 12 and 13 on the single output plate 10, a plurality of slits 10b are provided along the circumferential direction at positions corresponding to the windows 6c and 6d of the output plate 10 as shown in FIG. Is formed. The springs 12 and 13 are fitted into the slits 10b of the output plate 10 and are held at positions corresponding to the windows 6c and 6d of the retainer plates 6a and 6b. The right half of FIG. 1 (a) is a view where one retainer plate 6a exists, and the left half of FIG. 1 (a) is a view where one retainer plate 6a is removed. A spring receiving portion 10e is formed between the slit 10b and the slit 10b in the circumferential direction of the output plate 10, and a spring receiving portion is provided between the windows 6c and 6d and the windows 6c and 6d in the circumferential direction of the retainer plates 6a and 6b. Part 6i.

  As shown in FIG. 4, on the inner peripheral side of the slit 10b of the output plate 10, four elongated holes 10c are formed at substantially equal intervals. The escape hole 10c is not used in the first embodiment, but is used in the second embodiment to be described later.

  An annular spacer member 15 is interposed between the pair of relatively rotating retainer plates 6a and 6b and the output plate 10 which are configured as described above. Reference numeral 15 is attached to the output plate 10. As the spacer member 15, for example, 66 nylon, which is made of a soft material resin and has a relatively high wear resistance, is used in order to function as an axial spacer for a long period of time. Since the same component is used as each spacer member 15, one spacer member 15 will be described with reference to FIG.

  The spacer member 15 has an engagement protrusion 15f and an engagement hole 15g projecting from one side surface along the circumferential direction, and either one of the engagement protrusions 15f in a state where the spacer members 15 are overlapped. It is formed so as to face the engagement hole 15g on the other side. That is, the engagement protrusions 15f are formed at equal intervals every 90 degrees so that the engagement protrusions 15f and the engagement holes 15g are positioned symmetrically with respect to the center line 16 shown in FIG. The engagement holes 15g are formed at equal intervals every 90 degrees. And as shown in FIG. 3, the space | interval of the adjacent engagement protrusion 15f and the engagement hole 15g is set to the pitch P. As shown in FIG. When the engagement protrusion 15f and the engagement hole 15g are formed in such an arrangement, when the spacer members 15 are overlapped so that the center lines 16 coincide with each other, The other engagement hole 15g faces.

  The engagement protrusion 15f is formed with a slit 15h passing through the axis. At the tip of the engagement protrusion 15f, a retaining portion 15i is formed to prevent the engagement protrusion 15f from coming out of the engagement hole 15g formed in the other spacer member 15.

  As shown in FIG. 4, the output plate 10 is formed with a through hole 10d through which the engaging protrusion 15f is inserted. That is, two through holes 10d are formed between the escape hole 10c and the escape hole 10c of the output plate 10 at the same pitch P as the interval between the adjacent engagement projections 15f and the engagement holes 15g. Has been. Engagement projections 15f are inserted into these through holes 10d, and spacer members 15 are mounted on both sides of the output plate 10, respectively.

  As shown in the upper right of FIG. 1A, the pair of retainer plates 6a and 6b is formed with an inner peripheral surface 6m as an arc surface centered on the axis of the retainer plates 6a and 6b. An abutting portion 15 b that abuts the surface 6 m is formed in the spacer member 15. That is, as shown in FIG. 3, the spacer member 15 protrudes in the axial direction along the arc on the inner peripheral side of the surface on the side of the retainer plates 6 a and 6 b that is the surface opposite to the engagement protrusion 15 f. A cylindrical portion 15c is formed, and contact portions 15b that protrude from the cylindrical portion 15c toward the outer peripheral side in the radial direction and contact the inner peripheral surface 6m are intermittently formed in the circumferential direction. The spacer member 15 is formed with a thin flange portion 15d along the circumferential direction. As shown in FIG. 2, the flange portion 15d is inserted between the output plate 10 and the retainer plates 6a and 6b in the axial direction to prevent them from rubbing directly. That is, the flange portion 15d functions as an axial spacer, and the cylindrical portion 15c and the contact portion 15b function as radial spacers.

The spacer member 15 is attached to the output plate 10, and the abutting portion 15b of the spacer member 15 contacts the inner peripheral surface 6m of the retainer plates 6a and 6b so that centering between them is performed. In order to examine the wear rate of the spacer member 15, it should be noted that the contact portion 15b slides on the inner peripheral surface 6m of the retainer plates 6a and 6b and wears. That is, if the wear rate is to be increased, the area of the sliding surface of the contact portion 15b may be reduced. If the wear rate is to be decreased, the area of the sliding surface may be increased. Since the spacer member 15 is in contact with the inner side surfaces of the retainer plates 6a and 6b on the entire surface of the spacer portion 15d between the members in the axial direction (indicated by x in FIG. 3B), the spacer portion 15d It is easy to increase the area of the retainer plates 6a and 6b that contacts the side surfaces on the inner side of the apparatus. Therefore, the sliding surface pressure is low, and it can function as a spacer for a long time. On the other hand, between the members in the radial direction (indicated by y in FIG. 3 (a)), since the contact portions 15b are dotted in the circumferential direction, desired wear can be obtained in a relatively short time. . Since the circumferential width W of the contact portion 15b is substantially constant, the surface pressure is constant and the wear rate is also constant. When the circumferential width of the contact portion 15b is constant, predetermined wear can be reliably achieved within a desired time.
(Function)
Next, the operation of the torsional vibration reducing device will be described.

  A pair of retainer plates 6a, 6b and an output plate 10 are assembled with a pair of spacer members 15 interposed therebetween, and an inertial mass 8 is attached to the pair of retainer plates 6a, 6b via rivets 9, thereby reducing torsional vibrations. To complete. Next, a transmission input shaft (not shown) is spline-coupled to the spline teeth 11 a of the output hub 11, while the drive plate 2 is fixed to the crankshaft 1 by crank bolts 4. Finally, the inertia mass 8 is coupled to the drive plate 2 via drive plate bolts 7. At this time, if there is a deviation of the axial center between the inertia mass 8 and the drive plate 2, the spacer member 15 is deformed to shift the axial centers of the pair of retainer plates 6a, 6b and the output plate 10. As a result, the inertia mass 8 and the drive plate 2 can be assembled.

  During operation of the vehicle, the pair of retainer plates 6a and 6b and the output plate 10 of the torsional vibration reduction device rotate relatively. For this reason, the inner peripheral surfaces 6m of the retainer plates 6a and 6b slide on the contact portions 15b of the spacer member 15 coupled to both sides of the output plate 10. Since the sliding area of the contact portion 15b is small, the contact portion 15b of the spacer member 15 is worn in the radial direction within a relatively short time. On the other hand, there is a flange portion 15d between the pair of retainer plates 6a, 6b and the output plate 10, but since the sliding area between the flange portion 15d and the pair of retainer plates 6a, 6b is large, the flange portion 15d. There is almost no wear.

  According to the present invention, since the spacer member 15 is interposed between the pair of retainer plates 6a, 6b and the output plate 10 sandwiched between the pair of retainer plates 6a, 6b in the axial direction, the retainer plates 6a, The contact between 6b and the output plate 10 is prevented, and the generation of sound and wear due to the contact are suppressed. And since the spacer member 15 does not have a function of applying a pressing force in the axial direction like a disc spring, the spacer member 15 is rubbed strongly with the pair of retainer plates 6a, 6b and the output plate 10 in the axial direction and is quickly worn out. There is nothing, and it can serve as a spacer for a long period of time.

  According to the present invention, the pair of spacer members 15 are arranged so as to sandwich the center plate, and the pair of spacer protrusions 15f protruding from one of the pair of spacer members 15 are opposed to the other engagement hole 15g. The spacer members 15 are relatively positioned in the circumferential direction, the engaging protrusions 15f of the spacer members 15 are inserted into the through holes 10d formed in the center plate, and the engaging protrusions 15f are inserted into the other engaging holes 15g. The pair of spacer members 15 are mounted on both sides of the center plate. Since the same spacer member 15 is provided on both sides of the center plate, it is easy to align the two in the circumferential direction and the assembly work is easy. Further, since the same spacer member 15 is used, the complexity is eliminated and the manufacturing cost is suppressed. Further, since the pair of spacer members 15 are provided and the pair of spacer members 15 engage with each other with the center plate sandwiched therebetween, once the pair of spacer members 15 are coupled to the center plate, they can be handled integrally. .

According to the present invention, when the axial centers of the retainer plates 6a and 6b and the output plate 10 are slightly displaced, the contact portion 15b of the spacer member 15 that contacts the arc surface 6m of the retainer plates 6a and 6b is deformed. As a result, the retainer plates 6a and 6b and the output plate 10 can be assembled, and the deformed portion of the contact portion 15b is worn over time, so that misalignment is absorbed. The spacer member 15 functions as a spacer for a relatively long time in the axial direction, while having a conflicting function in which desired wear can be obtained in a relatively short time in the radial direction. Can be played with parts. And since the contact part 15b of the spacer member 15 with which the output plate 10 was mounted | worn contacts the circular arc surface 6m of the retainer plates 6a and 6b, the retainer plates 6a and 6b are centered with respect to the output plate 10. FIG. If the shaft is misaligned, the contact portion 15b is deformed and incorporated, and thereafter, the deformed portion is worn.
(B) Embodiment 2
Next, a second embodiment will be described. Since the second embodiment is obtained by changing a part of the first embodiment, the description of the same part is omitted, and only a different part is described.

  In this embodiment, an annular spacer member is divided in the circumferential direction to form spacer pieces, and these spacer pieces are formed on both sides of the output plate at the same position in the circumferential direction. The output plates are combined so as to sandwich the output plate. When the spacer member is arranged on the outer peripheral side, even if it is divided, a sufficient size can be obtained as the sliding area of the spacer, so that it is not necessary to connect to the entire ring in a ring shape, so it can be divided. Yes, if divided, the material saving effect is great.

  As shown in FIG. 6, the engagement protrusion 15f is formed at a position offset to the right side by P / 2 with respect to the center line 16 that is the central portion in the circumferential direction of the spacer piece 15P, and offset by P / 2 to the left side. An engagement hole 15g is formed at the position. As shown in FIG. 5, a pair of spacer pieces 15P are mounted so as to sandwich the output plate 10 from both sides. And the engagement protrusion 15f of one spacer piece 15P arrange | positioned at the one side of the output plate 10 is engage | inserted by the engagement hole 15g of the other spacer piece 15P arrange | positioned at the other side.

  In this case, a portion where the spacer piece 15P does not exist is formed on the circumference at a fixed distance from the axis where the spacer piece 15P is disposed. Therefore, a coupling means is provided at this position for restricting the radially inner sides of the retainer plates 6a and 6b from opening using the escape holes 10c of the output plate 10 of FIG.

  The structure of the coupling means will be described below. The inner peripheral surfaces 6m of the retainer plates 6a and 6b are formed with narrow projections 6j and 6k that are directed toward the center every 90 degrees, and the projection 6j is bent in the axial direction so as to approach the projection 6k. The protrusions 6j and 6k are coupled via the rivet 14. Thereby, when the springs 12 and 13 are heavy, the maximum engine speed is high, or the strength of the retainer plates 6a and 6b is insufficient, the inner side in the radial direction of the retainer plates 6a and 6b is opened by centrifugal force. Is regulated.

  According to this invention, since the spacer pieces 15P are intermittently mounted along the circumferential direction of the output plate 10, the material of the spacer pieces 15P is saved, and the manufacturing cost of the torsional vibration reducing device is suppressed. Further, since the annular spacer member 15 is large, the processing accuracy is deteriorated. However, since the spacer member 15 is divided into small spacer pieces 15P, the processing accuracy is improved.

  In the present embodiment, the input member is configured by connecting a pair of side plates and the output member is configured by a single central plate. However, the configuration may be reversed. In this case, spacer members are provided on both sides of the input side member. Moreover, although the same thing was used as a spacer member, you may use the thing of a different shape. Further, while the circular arc surface is formed on the side plate, the side plate is provided with the cylindrical portion and the abutting portion, but a configuration in which these elements are not employed may be employed. Furthermore, although 66 nylon was used as the spacer member, other materials may be used as the material of the spacer member, and further, a material obtained by molding a metal powder or kneaded material into a mold may be used. Good. In addition, when a metal material is used as the spacer member, the contact portion 15b in FIGS. For example, as a component constituting the contact portion 15b, a component that is easily deformed by forming a thin plate in a corrugated shape or forming a thin plate in an arc shape is provided, and the contact portion 15b is formed. It is also possible to couple to a metal spacer member 15 that is not provided.

FIG. 4A is a front view of the torsional vibration reduction device, with partly removed, and FIG. 5B is a view taken along the line A-O-A in FIG. The enlarged view of the principal part of FIG.1 (b) (Embodiment 1). (A) is a front view, (b) is a BOB arrow view of (a) (embodiment 1). (A) is a front view, (b) is a COC arrow view of (a) (embodiment 1). (A) is a partially removed front view showing a torsional vibration reducing device, and (b) is a view taken along the arrow line D-O-D in (a) (Embodiment 2). (A) is a front view, (b) is a right side view, and (c) is a rear view (Embodiment 2).

Explanation of symbols

1 ... Crankshaft 6a, 6b ... Retainer plate (input member, side plate)
6m ... Inner peripheral surface (arc surface)
10 ... Output plate (output member, center plate)
10e ... through hole 12,13 ... spring (elastic member)
DESCRIPTION OF SYMBOLS 15 ... Spacer member 15b ... Contact part 15c ... Cylindrical part 15d ... Flange part 15f ... Engagement protrusion 15g ... Engagement hole 15P ... Spacer piece

Claims (4)

An input member connected to the crankshaft and rotatable, an output member arranged concentrically with the input member and rotatably supported and connected to an input shaft of the transmission, and the input member and the output member An elastic member connected in the direction,
In the torsional vibration reduction device, wherein either one of the input member and the output member is configured by connecting a pair of side plates, and the other is configured by a central plate disposed between the pair of side plates in the axial direction.
An apparatus for reducing torsional vibration, characterized in that an annular spacer member is interposed between the center plate and the side plates in the axial direction, and the spacer members are mounted on both sides of the center plate. The torsional vibration reducing device according to claim 1,
The same component is used as each spacer member, and each spacer member has an engagement protrusion and an engagement hole protruding from one side surface, and one of the spacer members is overlapped on either side. The engagement protrusions are arranged along the circumferential direction so as to face the engagement holes on the other side, and the engagement protrusions are inserted through the through holes formed in the center plate to engage with the engagement holes. And a torsional vibration reducing device mounted on both sides of the central plate. The torsional vibration reducing device according to claim 1 or 2,
The side plate is formed with a circular arc surface centered on the axis of the side plate, and a cylindrical portion is formed to protrude on the side plate side, and the cylindrical portion protrudes in a radial direction and abuts against the circular arc surface. The torsional vibration reducing device, wherein the contact portion is intermittently formed in the circumferential direction. In the torsional vibration reducing device according to any one of claims 1 to 3,
A torsion characterized in that the annular spacer member is divided in the circumferential direction to form a spacer piece, and the spacer piece is intermittently mounted on both sides of the central plate at the same position in the circumferential direction. Vibration reduction device.

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