CN113494563A

CN113494563A - Torsional vibration damper and method for assembling a torsional vibration damper

Info

Publication number: CN113494563A
Application number: CN202110361600.0A
Authority: CN
Inventors: 罗曼·魏森博恩; 费利克斯·格斯特纳; 马丁·赫布斯特里特
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2020-04-07
Filing date: 2021-04-02
Publication date: 2021-10-12
Also published as: DE102020109676A1

Abstract

The invention relates to a torsional vibration damper (100), in particular a dual mass flywheel, comprising: an input part (102) and an output part (104) which have a common axis of rotation about which they can rotate together and in particular can be twisted to a limited extent relative to one another; and a spring damper arrangement acting between the input part and the output part, in particular an output flange part (130) of the output part, having an opening, the input part having an input flange part (114) and a cover disc firmly connected to the input flange part, wherein the cover disc is arranged radially inside the opening of the output part, characterized in that the input flange part and the cover disc are connected to one another in an axially frictionally force-fitting manner by means of at least one plastically deformed rivet projection (120) arranged in a bore in order to structurally and/or functionally improve a torsional vibration damper, and a method for assembling such a torsional vibration damper.

Description

Torsional vibration damper and method for assembling a torsional vibration damper

Technical Field

The invention relates to a torsional vibration damper, in particular a dual mass flywheel, comprising: an input part and an output part, which have a common axis of rotation, about which the input part and the output part can rotate and in particular can be rotated to a limited extent relative to one another; a spring damper device acting between an input part and an output part, the output part, in particular the output flange part of the output part, having an opening, the input part having an input flange part and a cover disk firmly connected to the input flange part, wherein the cover disk is arranged radially inside the opening of the output part. The invention also relates to a method for assembling a torsional vibration damper.

Background

A torsional vibration damper, referred to as a torsional vibration damper, is known from DE 102016213208 a1, which has an input element, an output element and a spring damper arrangement, wherein the output element can be arranged in a torsional manner relative to the input element against a restoring force of the spring damper arrangement. The input element has a bolt opening in the connecting region and is therefore configured to be screwable on the drive side with an element of a drive train of the motor vehicle. The output member may be connected to a downstream transmission, with a cover plate disposed adjacent the connection region, the cover plate having openings aligned with the bolt openings of the input member. The cover disk has a first element projecting in the axial direction and a second element projecting in the axial direction, which are arranged spaced apart from one another in the radial direction. The first projecting element serves to center the output element when the torsional vibration damper is mounted in the drive train.

Disclosure of Invention

The object of the present invention is to improve the torsional vibration damper mentioned at the outset in terms of structure and/or function and to provide a method for producing such a torsional vibration damper. This object is achieved by means of the torsional vibration damper according to the invention.

In order to be able to mount the torsional vibration damper in a drive train without problems, for example with an internal combustion engine, the torsional vibration damper and the transmission, the input part and the output part of the torsional vibration damper must be aligned so that the transmission shaft of the transmission can project into the torsional vibration damper. This is achieved in the torsional vibration damper of the invention as follows: by arranging the cover disk radially inside the opening of the output part, the output part is centered on the input part by means of the cover disk

Since the input flange part and the cover disk are connected to one another in a friction-fit manner in the axial direction by means of at least one plastically deformed rivet projection arranged in the bore, a relatively thick cover disk can be reliably fastened even in the case of thin material thicknesses of the input flange part, whereby a low maximum height of the at least one rivet projection is obtained. No rivet head is required for this purpose.

At least one rivet projection may be formed on the input flange part and the hole may be formed on the cover disk. Such an arrangement can be formed simply and at low cost, in particular because the riveting projections are easily accessible for plastic deformation, preferably compression. At least one riveting projection may be drawn from the input flange part. Drawing is a reliable and mature manufacturing process. Alternatively, the at least one rivet projection can also be formed on the cover disk and the opening on the input flange part. The task of the invention is also solved by the alternative arrangement of the riveting projections and holes on the input flange part and the output flange part. Here, the riveting projections of the input flange part are respectively arranged in holes in the cover disk and vice versa.

The input flange member may be a disc-shaped member. The input flange member may be an annular disc member. The input flange member may be a pot-shaped member. The input flange part may be a part which is largely rotationally symmetrical with respect to the axis of rotation. The input flange member may have a pattern of holes for securing the input member to a component of the powertrain. The input flange member may have a hole pattern with bolt openings for tightening the input member onto a crankshaft of an internal combustion engine of the powertrain.

The cover disc may be a disc-shaped member. The cover disc may be a ring disc shaped member. The cover tray may be a can-shaped member. The cover disk may be a largely rotationally symmetrical component with respect to the axis of rotation. The cover disk may have openings that align with the bolt openings of the input flange member.

The at least one staking protrusion may be disposed entirely within the aperture. The riveting projections then do not project axially from the associated part of the subassembly consisting of the input flange part and the cover disk. Thereby, the installation space required in the axial direction is reduced. All of the riveting projections may be disposed entirely within their associated apertures, respectively.

The height of the at least one staking protrusion may be less than the height of the aperture. The height of the at least one staking protrusion may be less than the height of the hole after compression. This reliably prevents the rivet projections from protruding axially out of the associated parts of the subassembly consisting of the input flange part and the cover disk, also taking into account manufacturing tolerances.

A plurality of staking bosses may be respectively disposed in the apertures associated with each staking boss. The number of riveting projections can thus be adapted to the strength requirements of the subassembly consisting of the input flange part and the cover disk. A plurality of riveting protrusions may be provided on the hole circle. The plurality of riveting projections may be provided on a plurality of hole circles having different diameters. The plurality of riveting projections may be disposed equidistantly or at different pitches or asymmetrically with respect to each other.

A plurality of apertures associated with the plurality of staking protuberances may be disposed on the eyelet. The plurality of holes associated with the plurality of riveting projections may be provided on a plurality of hole circles having different diameters. The holes may be arranged equidistantly or at different spacings or asymmetrically to each other. The holes may have a cylindrical diameter on the side facing the riveting projection and a conically expanding diameter on the side facing away from the riveting projection.

A spring damper device acts between the input and output members. The spring damper arrangement may have a mechanical energy store. The mechanical energy store may be an arcuate spring device disposed in the receiving space. The bow spring of the bow spring arrangement can be embodied as a helical spring. The arcuate spring may be configured as a compression spring. The arcuate spring can be supported on the input part on the one hand and on the output part on the other hand. At least one mechanical energy accumulator can absorb energy when the input part and the output part are twisted relative to each other against the force of the mechanical energy accumulator. The input part and the output part can be twisted back relative to each other again by means of the force stored in the mechanical energy store.

The term torsional vibration damper is also understood to mean a torsional vibration absorber which absorbs vibrations to a large extent or completely undamped. The torsional vibration damper can have a centrifugal pendulum device, whereby the damping is increased. The centrifugal pendulum device may have a pendulum mass. The centrifugal pendulum device may have a plurality of pendulum masses. The output flange component may act as a pendulum mass carrier. The pendulum mass carrier can be integrated into the output flange part. The pendulum mass carrier can carry exactly two pendulum masses. The pendulum mass carrier can carry more than two pendulum masses. The pendulum mass carrier can carry exactly four pendulum masses. The centrifugal force pendulum device may have at least one pendulum mass having two pendulum mass parts connected to one another. The pendulum mass carriers can be arranged axially between the pendulum mass parts, so that the pendulum mass parts are arranged outside the pendulum mass carriers. The centrifugal pendulum device may be a centrifugal pendulum device having an external pendulum mass. The centrifugal force pendulum device may have a plurality of pendulum masses, each having a first pendulum mass part and a second pendulum mass part. The first pendulum mass part and the second pendulum mass part can be firmly connected to one another, in particular riveted. The first pendulum mass part and the second pendulum mass part may be arranged parallel to each other and axially spaced apart from each other. The first pendulum mass part and the second pendulum mass part may be arranged on both sides of the pendulum mass carrier. The pendulum mass carrier can have at least one recess for the rolling body. At least one recess may be used to define the pendulum track. The at least one recess may have a kidney shape.

Torsional vibration dampers may be used in place of the drivetrain. The powertrain may have an internal combustion engine and a transmission. Torsional vibration dampers may be disposed in the power flow between the internal combustion engine and the transmission. A torsional vibration damper may be provided for the crankshaft. A torsional vibration damper may be provided on the friction clutch. Torsional vibration dampers may be used for mounting on the transmission. A torsional vibration damper may be provided between the internal combustion engine and the friction clutch. Torsional vibration dampers may be used in hybrid powertrains. The torsional vibration damper can be configured as a dual mass flywheel. The torsional vibration damper may be adapted to be provided on a torque converter. A torsional vibration damper may be provided on the auxiliary device driver.

The terms "input element" and "output element" relate in particular to the direction of flow of the line from the driving engine (leitsunfusrising). The expressions "axial", "radial" and "circumferential" relate to the direction of extension of the axis of rotation, as long as no further description is given or the context does not indicate otherwise. "axial" corresponds to the direction of extension of the axis of rotation. "radial" is a direction perpendicular to the direction of extension of the axis of rotation and intersecting the axis of rotation. "circumferentially" corresponds to the direction of a circular arc about the axis of rotation.

The object is also achieved by a method for assembling a torsional vibration damper.

Since the input flange part and the cover disk are arranged relative to one another in such a way that the at least one riveting projection to be deformed is arranged in the hole (associated with the at least one riveting projection), the at least one riveting projection can be deformed in such a way that the input flange part and the cover disk can be connected to one another in a friction-fit manner in the axial direction by means of the at least one riveting projection arranged in the hole.

The height of the at least one staking protrusion may be less than the height of the aperture prior to compression. The diameter of the at least one staking protrusion may be slightly smaller than the inner diameter of the associated bore prior to staking. This allows the riveting projection to be easily inserted into the associated hole. In the case of a plurality of riveting projections, the positional tolerances of the riveting projections and the holes can also be compensated.

The at least one riveting lug can be plastically deformed within the bore such that the at least one riveting lug rests at least partially in a friction-fit manner against the circumferential inner face of the bore. In this way, a rivet joint for a form-fitting axial connection between the input flange part and the cover disk can be dispensed with. The at least one riveting projection is therefore preferably plastically deformed without forming a closing head. This makes it possible to save installation space in the axial direction.

The at least one riveting projection can be plastically deformed by means of a tool punch. The at least one riveting projection can be pressed by means of a tool punch. The riveting projections can be plastically deformed one after another using one tool punch. The plurality of riveting projections can be plastically deformed simultaneously using a plurality of tool punches. By using one or more tool punches, the method can be carried out using tools that are known per se and that are low in cost.

In summary and in other words, the invention furthermore provides a method for assembling a torsional vibration damper, in which a cover disk is centered by means of a projection drawn out of a primary flywheel (input part) and is pressed (pressed) by means of a punch, so that the cover disk is held axially (e.g. pre-riveted). The cover plate is inserted onto the primary flywheel. The projections take up the centering of the cover disk until they are deformed by the punch, so that the cover disk is held.

By means of the invention, a cost-optimized torsional vibration damper with fewer components is provided. No additional rivets are required for fastening the cover disk to the input part. Even in the case of thin material thicknesses of the input part, a low maximum height of the riveting projection is thus obtained, and even if the height of the riveting projection is not sufficient to form a closing head, a thicker cover disk can be reliably fastened. In the event of an axial tensile force on the secondary side, for example when the torsional vibration damper is lifted beyond the secondary side, in which the cover disk relieves the force of the disk spring sealing membrane, the cover disk cannot be axially removed and has no axial play.

The method for assembling the torsional vibration damper can also be used in places between the input part and the cover disk where rivets cannot be used, and in torsional vibration dampers in which the hole distribution in the input part is very narrow for the crankshaft to be screwed, so that there is not sufficient installation space for the quincunx riveting.

Drawings

Embodiments of the present invention are described in more detail below with reference to the accompanying drawings. Further features and advantages result from this description. The specific features of this embodiment may represent general features of the invention. Features of this embodiment that are associated with other features may also represent various features of the invention.

They schematically show, by way of example:

figure 1 shows a section through a torsional vibration damper according to the invention in part,

fig. 2 shows a detail view of the joint between the input part and the cover disk of the torsional vibration damper of fig. 1.

Fig. 3 shows, in detail, a cross section of the input part and the cover disk in the region of the rivet projection of the input part before the cover disk is plugged onto the rivet projection during the method for assembling the torsional vibration damper,

FIG. 4 shows a sectional view corresponding to FIG. 3 after the cover disk has been plugged onto the riveting lugs of the input part, and a punch for pressing the riveting lugs, an

Fig. 5 shows a sectional view corresponding to fig. 3 after the pressing of the riveting projection.

Detailed Description

Fig. 1 and 2 show a torsional vibration damper 100 designed as a dual mass flywheel. The torsional vibration damper 100 is used, for example, in a drive train of a motor vehicle, between an internal combustion engine and a friction clutch, in order to reduce torsional vibrations.

Torsional vibration damper 100 has an input member 102 and an output member 104. The input part 102 serves as a primary mass. The output member 104 serves as a secondary mass. The input member 102 and the output member 104 are rotatable together about a common axis of rotation 106 and are limitedly twisted relative to each other. Unless otherwise noted, directional descriptions such as "axial," "radial," and "circumferential" are used in relation to the axis of rotation 106 of the torsional vibration damper 100.

A spring damper device acts between the input member 102 and the output member 104. The spring damper device has an arcuate spring arrangement with an arcuate spring such as 108 and a sliding shell 110. The arc spring 108 is disposed in the accommodation space 112.

The input member 102 has an input flange member 114, a cover disk 116, and an input cover member 118. The input flange member 114 is pot shaped. The input cover member 118 has a doughnut-like shape. The input flange part 114 and the input cover part 118 are firmly connected to each other, in the present case welded. The receiving space 112 is bounded by an input flange member 114 and an input cover member 118. Cover plate 116 serves to center output member 104 during assembly of torsional vibration damper 100 into a powertrain.

The input flange member 114 preferably has a hole pattern, not shown, with bolt openings for screwing the input member 102 onto the crankshaft of an internal combustion engine.

Radially inward, the input flange member 114 circumferentially has a plurality of staking lugs 120. The rivet projection 120 is made of the material of the input flange part 114, in particular drawn out. The staking boss 120 points in the direction of the output member 104. The cover disk 116 has a plurality of, in particular, cylindrical bores 122 in a circumferential manner, which bores 122 are arranged complementary to the rivet projections 120. The holes 122 are arranged on a hole circle, preferably equidistantly or at different spacings or asymmetrically to each other. On the side facing towards the riveting boss 120, the hole 122 has a cylindrical diameter. On the side facing away from the riveting projection 120, the bore 122 has a conically widening diameter. The cover plate 116 is pushed over the staking lugs 120 so that each aperture 122 receives exactly one staking lug 120. The riveting projections 120 are pressed such that a circumferential edge region 124 of each riveting projection 120 bears in a friction-fit manner against a circumferential inner face 126 of the associated hole 122. The cover disk 116 is thereby axially fixed to the input flange part 114 in the direction of the output part 104. In a variant of the embodiment not shown in the figures, at least one riveting lug 120 can additionally be connected to the input flange part 114 in a form-fitting manner.

The input flange part 114 and the input cover part 118 delimit on the input side a receiving space 112 for the bow springs 108, which receiving space 112 is in the present case torus-shaped. A freewheel ring gear 128 is arranged radially outside the input flange part 114, and the freewheel ring gear 128 can be engaged with an electric motor vehicle starter, not shown here, when the torsional vibration damper 100 is in the installed position.

The output member 104 has an output flange member 130, an intermediate ring 132, an output hub 134 and a centrifugal force pendulum device 136. The output flange part 130 serves to support the bow spring 108 on the output side and in the present case also serves as a pendulum mass carrier of the centrifugal force pendulum device 136.

The output flange member 130 is disc-shaped with a central, preferably circular, opening 138 having a central axis aligned with the axis of rotation 106.

The cover plate 116 of the input flange member 114 is disposed within the opening 138 of the output flange member 130. The inner diameter of the opening 138 is slightly larger than the outer diameter of the cover disk 116. A plastic bushing 142 is disposed in the radial gap between the cover disk 116 and the output flange member 130. The plastic bushing 142 may optionally be omitted. The described arrangement of cover disk 116 in output flange part 130 provides a centering device which is effective when torsional vibration damper 100 is installed in the drive train of a motor vehicle. In addition, torsional vibration damper 100 has no other internal support means, i.e., output member 104 is not supported on input member 102 by bearings. Thus, no centering of the output member 104 on the input member 102 by means of another bearing is provided.

An intermediate ring 132 is disposed between the output flange member 130 and the output hub 134. In the present case, the intermediate ring 132 is a separately formed component, but may alternatively also be integrated in the output flange part 130 or the output hub 134. The output flange member 130, the intermediate ring 132 and the output hub 134 are preferably fixedly connected to each other by a plurality of riveted projections. The output hub 134 has a toothing 140, via which toothing 140 the engine torque transmitted via the torsional vibration damper 100 can be transmitted to a shaft, for example a transmission input shaft of a transmission of a drive train.

The input flange part 114 and the input cover part 118 have an adapter (durchtillung) which projects into the receiving space 112 and forms a support for the bow spring 108 on the input side. The output flange part 130 has a radially outward extension, which is not visible in the drawing due to the cross-sectional profile, which extends into the receiving space 112 and forms an output-side support for the bow spring 108.

In the present case, the friction ring 144 also acts between the cover disk 116 and the output part 104. The sealing arrangement seals the annular gap between the input cover member 118 and the output hub 134. The sealing device has a further friction ring 146 and a disk spring 148.

Fig. 3 to 5 show a section through the input flange part 114, the cover disk 116 and the tool punch 150 for pressing the riveting boss 120. Fig. 3 to 5 show method steps of a method for assembling torsional vibration damper 100. The sections respectively extend through the riveting bosses 120. Preferably, all the rivet projections 120 are identical to one another and all the bores 122 are identical to one another, so that the method steps are described below with the aid of the pair of rivet projections 120 and bores 122 visible in cross section.

Fig. 3 shows the input flange member 114 and the cover plate 116 prior to bringing the input flange member 114 and the cover plate 116 together. The combination is carried out as follows: the input flange member 114 and the cover disk 116 are positioned relative to one another such that the staking tabs 120 of the input flange member 114 are disposed within the apertures 122 of the cover disk 116. This may be done, for example, by pushing or inserting the cover plate 116 over the staking tabs 120 and/or inserting the input flange member 114 into the cover plate 116.

When the input flange portion 114 and the cover plate 116 are combined together, the caulking projections 120 are not yet compressed. The riveting projection 120 has a shape that can be disposed in the associated hole 122 with a small clearance. In the present case, the riveting boss 120 which has not yet been pressed is substantially cylindrical and has a diameter 152 which is slightly smaller than the inner diameter 154 of the associated bore 122.

Fig. 4 shows the input flange part 114 and the cover plate 116 after the input flange part 114 has been assembled to the cover plate 116 and before the rivet projections 120 have been pressed. A slight clearance of the riveting projections 120 is provided in the respective associated holes 122. In the present case, the height 156 of the riveting lug 120 is less than the height 158 of the associated hole 122, both in the non-compressed state and in the compressed state of the riveting lug 16. The

heights

156, 158 are measured axially. However, in a variant of embodiment, the height 156 of the riveting projection 120 which has not yet been pressed down can also be approximately equal to the height 158 of the hole 122. The riveting boss 120 is disposed entirely within the associated hole 122, that is, the riveting boss 120 does not protrude from the associated hole 122 in the axial direction.

In order to press the riveting projection 120, the punch 150 is preferably moved toward the riveting projection 120 in the axial direction. The input flange part 114 and the cover plate 116 are held in the device such that the punch 150 can be pressed with great force against the end face of the riveting boss 120. The riveting projection 120 is thereby plastically deformed, in the present case pressed, by the punch. The rivet projection 120 is radially widened by plastic deformation.

Fig. 5 shows the input flange member 114 and cover disk 116 after the staking lugs 120 have been compressed. Due to the plastic deformation, the staking boss 120 has a shape other than a cylindrical shape after compression. In particular, in the region of the end face of the rivet bead 120, the rivet bead 120 widens radially, so that a circumferential edge region 124 of the rivet bead 120 bears in a friction-fit manner against an inner face 126 of the associated bore 122.

List of reference numerals

100 torsional vibration damper

102 input unit

104 output member

106 axis of rotation

108 arc spring

110 sliding shell

112 accommodating space

114 input flange part

116 cover plate

118 input cover member

120 riveting projection

122 hole

124 edge region

126 inner face

128 flywheel gear ring

130 output flange part

132 intermediate ring

134 output hub

136 centrifugal force pendulum device

138 opening

140 tooth part

142 plastic bushing

144 friction ring

146 friction ring

148 disc spring

150 tool punch

152 diameter

154 inner diameter

156 height

158 height

Claims

1. A torsional vibration damper (100), in particular a dual mass flywheel, having: an input part (102) and an output part (104) which have a common axis of rotation (106), about which the input part (102) and the output part (104) can rotate together and in particular can be twisted to a limited extent relative to one another; and a spring damper arrangement acting between the input part (102) and the output part (104), in particular an output flange part (130) of the output part (104), having an opening (138), the input part (102) having an input flange part (114) and a cover disk (116) which is firmly connected to the input flange part (114), wherein the cover disk (116) is arranged radially inside the opening (138) of the output part (104), characterized in that the input flange part (114) and the cover disk (116) are connected to one another in an axial frictional force fit by means of at least one plastically deformable rivet projection (120) arranged in a bore (122).

2. The torsional vibration damper (100) of claim 1, characterized in that the at least one riveting projection (120) is formed on the input flange part (114), in particular drawn out of the input flange part (114), and the hole (122) is formed in the cover disk (116).

3. The torsional vibration damper (100) of at least one of the preceding claims, characterized in that the at least one riveting projection (120) is arranged completely within the bore (122).

4. The torsional vibration damper (100) of at least one of the preceding claims, characterized in that the height (156) of the at least one riveting projection (120) is smaller than the height (158) of the hole (122).

5. The torsional vibration damper (100) as claimed in at least one of the preceding claims, characterized in that a plurality of riveting projections (120) are respectively provided in the holes (122) associated with the respective riveting projections (120).

6. The torsional vibration damper (100) of claim 5, characterized in that the holes (122) are arranged in a hole circle.

7. A method for assembling a torsional vibration damper (100) according to at least one of the preceding claims, characterized in that the input flange part (114) and the cover disk (116) are arranged to one another in such a way that at least one riveting projection (120) to be plastically deformed is arranged in the hole (122).

8. The method according to claim 8, characterized in that the at least one riveting lug (120) is plastically deformed within the bore (122) such that the at least one riveting lug (120) bears at least partially in a friction-fit manner against a surrounding inner face (126) of the bore (122).

9. Method according to claim 8, characterized in that said at least one riveting projection (120) is plastically deformed without constituting a closing head.

10. Method according to claim 8 or 9, characterized in that the at least one riveting projection (120) is plastically deformed, in particular pressed, by means of a tool punch (150).