WO2018072779A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

Info

Publication number
WO2018072779A1
WO2018072779A1 PCT/DE2017/100800 DE2017100800W WO2018072779A1 WO 2018072779 A1 WO2018072779 A1 WO 2018072779A1 DE 2017100800 W DE2017100800 W DE 2017100800W WO 2018072779 A1 WO2018072779 A1 WO 2018072779A1
Authority
WO
WIPO (PCT)
Prior art keywords
input part
torsional vibration
vibration damper
stiffening beads
spring
Prior art date
Application number
PCT/DE2017/100800
Other languages
German (de)
English (en)
Inventor
Mathias Girnus
Hartmut Mende
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112017005304.8T priority Critical patent/DE112017005304A5/de
Publication of WO2018072779A1 publication Critical patent/WO2018072779A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1203—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by manufacturing, e.g. assembling or testing procedures for the damper units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13142—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the method of assembly, production or treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2226/00—Manufacturing; Treatments
    • F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
    • F16F2226/047—Sheet-metal stamping

Definitions

  • the invention relates to a torsional vibration damper, in particular two-mass flywheel, the torsional vibration damper having a cup-shaped input part and an output part with a common axis of rotation about which the input part and the output part rotatable together and rotatable relative to each other are limited, and effective between the input part and the output part spring-damper device.
  • a dual mass flywheel is known with a plastically deformed primary plate and a plastically deformed secondary plate, which are rotatable relative to each other against the action of springs about a rotation axis in which formed between the primary plate and the secondary plate receiving spaces for the springs are clamped between plastically deformed primary impact areas of the primary sheet and plastically deformed secondary impact areas of the secondary sheet.
  • a flangeless damper in particular a dual-mass flywheel, with a primary flywheel and with a secondary flywheel, which are arranged adjacent to one another and with a spring damper device with spring elements the primary flywheel mass is rotatably mounted relative to the secondary flywheel mass by means of a bearing, wherein the primary flywheel mass is rotatable relative to the restoring force of the spring elements, in which at least one wear protection element is arranged between the primary flywheel mass and the spring elements, against which the spring elements are supported radially on the outside ,
  • the German patent application with the file number 10 2016 200 317.8.
  • the teaching of this publication is to be regarded as part of the present document.
  • Features of this publication are features of the present document.
  • the invention has for its object to improve a torsional vibration damper mentioned structurally and / or functionally.
  • the torsional vibration damper may be for placement in a drive train of a vehicle.
  • the drive train may include a prime mover.
  • the prime mover may be an internal combustion engine.
  • the internal combustion engine may have a crankshaft.
  • the powertrain may include a friction clutch device.
  • the drive train may have a transmission.
  • the drive train may have at least one drivable vehicle wheel.
  • the torsional vibration damper may be designed as a dual mass flywheel.
  • the torsional vibration damper may be disposed between the engine and the friction clutch device.
  • the torsional vibration damper can serve to reduce torsional vibrations of the drive train.
  • Input part and output part refer to a line flow direction originating from an engine.
  • the statements “axially”, “radially” and “in the circumferential direction” refer to an extension direction of the rotation axis.
  • “Axial” then corresponds to an extension direction of the rotation axis then a direction perpendicular to the direction of extension of the axis of rotation and intersecting with the axis of rotation.
  • “In the circumferential direction” then corresponds to a circular arc direction about the axis of rotation.
  • the spring device can have at least one mechanical energy store.
  • the at least one mechanical energy store can be supported on the one hand on the input part and on the other hand on the output part.
  • the at least one mechanical energy store may be a helical spring.
  • the at least one mechanical energy store may be a compression spring.
  • the at least one mechanical energy store may be a bow spring.
  • the friction device can have at least one friction disk.
  • the entrance part may have openings.
  • the openings can be arranged on a bolt circle. The openings may serve for receiving fasteners, such as screws or rivets, and / or for a penetration.
  • the entrance part may have a pot-like shape.
  • the input part may have a bottom portion and a wall portion.
  • the wall section can serve as burst protection.
  • the input part can be opened axially towards the output part.
  • the input part can be designed without cover.
  • the input part can limit or limit a receiving space for the at least one mechanical energy store.
  • the input part can have support sections protruding into the receiving space for the at least one mechanical energy store.
  • the input part can have a central dome.
  • the central dome can be arranged radially on the inside.
  • the central dome may extend axially toward the output part.
  • the input part may have an annular bead.
  • the annular bead can be arranged in the radial direction between the central dome and the wall section.
  • the input part with the stiffening beads can be made of a sheet in a stamping-forming process.
  • the input part may have a reduced sheet thickness.
  • the input part may have a support disk.
  • the support disk can serve to support the output part.
  • the input part can also be called a primary flywheel.
  • the output part may have a flange part.
  • the flange part may have a plate-like shape.
  • the flange part can have support sections projecting into the receiving space for the at least one mechanical energy store.
  • the output part may have a flywheel part.
  • the torsional vibration damper may comprise a bearing device.
  • the bearing device can serve for mutual rotatable mounting of the input part and the output part.
  • the bearing device may have at least one sliding bearing.
  • the bearing device may have at least one roller bearing.
  • the stiffening beads can each extend in the radial direction.
  • the stiffening beads may each extend radially outward from the central dome. extend.
  • the stiffening beads may each extend between the central dome and the annular bead.
  • the stiffener beads may each extend between the holes.
  • the stiffening beads may be disposed at the bottom portion.
  • the input part can have six to ten, in particular eight, stiffening beads.
  • the invention provides, inter alia, an increased bursting strength of a primary flywheel.
  • radial star-shaped beads can be introduced to achieve a stiffening. This leads to a better stress distribution and thus to a reduction of maximum occurring stresses in the primary flywheel.
  • a reliability is increased. Burst strength is increased. An effort, such as manufacturing costs and / or cost, is reduced. A weight is reduced.
  • Fig. 1 is a capless dual mass flywheel in sectional view
  • Fig. 2 is an input part with stiffening beads of a capless dual mass flywheel
  • the dual mass flywheel 1 has an input part 2.
  • the input part 2 serves as a primary flywheel or primary flywheel and is, for example, with a crankshaft of a combustion motor or similar. connectable, as screwed.
  • the input part 2 has radially inwardly screwed openings 3, through which screws 4 can be performed in order to screw the input part 2 to a crankshaft.
  • the support disk 6 is placed radially inward on the input part 2 and serves for the screw head support.
  • the support disk 6 is preferably formed as a sheet metal forming part.
  • the input part 2 may preferably be formed as a sheet metal forming part. It can be seen that the input part 2 is bent radially outward in the axial direction. As a result, an area is created which serves to receive spring elements 9 of a spring damper device 10. Radially outside on the input part 2, a ring gear 8 can furthermore be arranged and connected in a rotationally fixed manner.
  • 2 stop elements 1 1 are formed on the input part, which serve the Abstützung of the spring elements 9 of the spring damper device 10. These protrude out of the plane of the input part 2, so that the spring elements 9 can be supported on the end side.
  • the spring elements 9 are preferably formed as bow springs.
  • an output part 12 Adjacent to the input part 2, an output part 12 is arranged.
  • the output part 12 serves as a secondary flywheel or secondary flywheel and is preferably designed as a sheet-metal forming part.
  • the output member 12 is limited to rotate relative to the input part 2 against the restoring force of the spring elements 9, wherein the capless dual mass flywheel 1 about the axis xx is basically rotatable.
  • a bearing 13 is arranged radially inwardly to support the rotational movement of input part 2 to output part 12.
  • the input part 2 and also the output part 12 to a projecting in the axial direction Primadom 14, 15, between which the bearing 13 is arranged.
  • the camp 13 between the two the flywheels, ie between the input part 2 and the output part 12, is preferably a rolling or sliding bearing.
  • the spring elements 9, also referred to as spring-loaded elements, which may preferably be designed as bow springs, are preferably arranged at least in pairs in order to be able to damp a relative rotation of the input part 2 to the output part 12 in both directions of rotation.
  • the spring elements 9 are preferably arranged in a channel 30 filled with grease or lubricant. This further reduces the wear of the spring elements 9 when supporting the spring elements 9 radially on the outside of the input part 2.
  • at least one wear protection element 40 is provided which radially outward between the input part 2 and the spring elements 9 is arranged or are.
  • a cup-like, circumferential and preferably hardened sheet can be arranged.
  • the wear protection element 40 may also be designed as only partially revolving or as a closed circumferential element.
  • at least two hardened sliding shells can be arranged as wear protection elements. It can be seen that the wear protection elements 40 bear radially on the outside of the input part 2 and are formed in the direction of the output part 12 curved radially inwardly.
  • the cup-like, circumferential wear protection element 40 such as a wear guard, for the spring elements, in particular for bow springs, is preferably held axially in both directions, for example by a stop and possibly by
  • the wear protection elements 40 are made narrow. This means that they surround the spring elements 9 radially outside only partially, so only slightly more than to the center of the spring.
  • contours may be present on the wear protection element, such as wear protection plate, which are in engagement with corresponding contours of the input part 2 and create a positive connection in the circumferential direction. These contours can be done by caulking the primary flywheel.
  • Calking can be arranged radially on the outside of the primary flywheel and causes an axial securing of the wear protection element 40.
  • the sliding shells provided as alternative design can also have recesses as wear protection elements 40, with which they engage around the primary-side stops of the spring elements or the bow spring stops at least in regions in order to achieve a securing in the circumferential direction.
  • the sliding cups can be axially supported on the stops of the spring elements or on the bow spring stops and caulking of the primary flywheel.
  • 12 second stop elements 1 1 a are formed on the secondary flywheel, which serve the support of the spring elements 9 of the spring damper device 10. These protrude out of the plane of the output part 12, so that the spring elements 9 can also be supported at the ends on these second stop elements 11a.
  • the spring elements 9 are supported both on the stop elements 1 1 of the input part 2 and on the second stop elements 1 1 a of the output part 12.
  • stop elements 1 1 a arranged on the output part 12 and secured thereto.
  • These may be formed as separate stop elements and spring support, such as the Bogenfederabstützung, be attached to the output part 12, such as by means of molding or material connection, for example by the keyhole principle, by means of deformed warts or by welding.
  • the positive connection is indicated in FIG. 1 by the reference numeral 16; alternatively or additionally, the weld 17 is provided or providable.
  • a resilient sealing member 18 is arranged, which the channel 30, also called fat space, outwardly in Essentially grease-proof seals.
  • the sealing element 18 is preferably designed as a fat-tightly welded to the input part 2 membrane.
  • the weld 19 can be circumferential, for example by laser welding done.
  • the membrane is radially outside fat-tightly connected to the primary flywheel and radially inside the membrane is advantageous under axial bias to the output part 12 at.
  • an additional, resilient supporting element 20 is arranged between the input part 2 and the output part 12.
  • This resilient support element 20 is advantageously designed as a plate spring, which is supported radially on the outside of a shoulder 21 of the output part 12 axially and is supported radially on the inside of a shoulder 22 of the input part 2 axially.
  • the heel 21 of the output part 12 may for example be a retaining tab, which is connected to the output part 12 or molded out of this.
  • the shoulder 22 of the input part 2 may for example be a retaining tab or a shoulder which is connected to or formed out of the primary flywheel mass 2.
  • the shoulder 22 is connected to the support disk 6 and is formed from this.
  • the support disk 6 is screwed to the input part 2.
  • the support plate 6 is thereby formed as a support plate on which the plate spring can be supported as a resilient support member 20.
  • the resilient support member 20 By the resilient support member 20, a defined axial force between the input part 2 and the output part 12 can be impressed.
  • the additional support member 20 may optionally also be omitted if the bearing 13 is formed for example by means of a bearing type, which can support the axial forces by the sealing member 18 securely, such as a ball bearing with interference fit.
  • the spring elements 9 on the stop elements 1 1, 1 1 a it may be advantageous and / or useful if the spring ends of the spring elements are provided with spring cups, so that the spring cups at the spring ends create and the spring cups on the other hand to the stop elements 1 1, 1 1 a supported. This allows a better power transmission between the spring element and the stop elements.
  • the resilient sealing member 18 may be formed as a membrane which is radially inwardly supported on the output member 12 and thereby generates an axial force component in the axial direction towards the output member 12 and thus in the direction of a transmission.
  • the resilient support member 20 such as the diaphragm spring
  • one of the action of the resilient sealing member 18, such as the membrane generates opposite force component which is at least substantially at least as large or larger than the force which the resilient Sealing element, such as the membrane generated.
  • the resilient sealing element could also be formed as a membrane, which is supported radially on the outside of the primary flywheel and thereby generates an axial force component in the axial direction to the primary flywheel.
  • Fig. 2 shows the input part 2 with stiffening beads, such as 23, of the capless dual-mass flywheel 1.
  • the input part has an open axially towards the output part 12 cup-shaped shape with a bottom portion 24 and a wall portion 25.
  • the central dome 14 is arranged radially inwardly and extends axially toward the output part 12. Radially further out the openings 7 are provided for the passage of the screws 4 for screwing the input part 2 to, for example, a crankshaft.
  • annular bead 26 Radially further out, inside the wall portion 25, an annular bead 26 is formed for receiving the spring elements 9.
  • the annular bead 26 is half-shell-like and open to the transmission side, so that the spring elements 9 project toward the output part 12.
  • the annular bead 26 may be divided into two parts, with each annular bead part sweeping over approximately 180 °. Embossments can be provided between the annular bead parts, which serve as stop elements for the spring elements 9, so that the spring elements 9 can be supported on the stop elements in the circumferential direction.
  • Radially outside the wall portion 25 of the input part 2 engages over the spring elements 9 in the annular bead 26.
  • the annular bead 26 forms at least partially a channel in which the spring elements 9 are received and in which, for example, a grease or lubricant filling can be made. Radially inside the stop elements, openings, such as 27, are provided. hen, which can serve the riveting of stop elements on the input part 2.
  • the wall section 25 serves as burst protection, in order to prevent leakage of parts of the dual mass flywheel 1 and thus further defects in the event of a defect.
  • the stiffening beads 23 are disposed on the bottom portion 24, each extending radially from the central diameter 14 between the openings 7 and the openings 27 and terminate in front of the annular bead 26.
  • the input part 2 eight star-shaped stiffening beads 23.
  • the input part may be made of sheet metal having a reduced sheet thickness in a stamping-forming process.
  • the stiffening beads 23 can be incorporated in one operation. Incidentally, reference is additionally made in particular to FIG. 1 and the associated description.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un amortisseur de vibrations de torsion, en particulier un volant bi-masse, l'amortisseur de vibrations de torsion comprenant un élément d'entrée (2) en forme de coque et un élément de sortie munis d'un axe de rotation commun, autour duquel l'élément d'entrée (2) et l'élément de sortie peuvent tourner ensemble et effectuer l'un par rapport à l'autre un mouvement de torsion limité, et un dispositif d'amortissement à ressort agissant entre l'élément d'entrée (2) et l'élément de sortie, l'élément d'entrée (2) comprenant des moulures de renforcement (23) afin d'améliorer l'amortisseur de vibrations de torsion d'un point de vue structural et/ou fonctionnel.
PCT/DE2017/100800 2016-10-21 2017-09-19 Amortisseur de vibrations de torsion WO2018072779A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017005304.8T DE112017005304A5 (de) 2016-10-21 2017-09-19 Drehschwingungsdämpfer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016220674 2016-10-21
DE102016220674.5 2016-10-21

Publications (1)

Publication Number Publication Date
WO2018072779A1 true WO2018072779A1 (fr) 2018-04-26

Family

ID=59982223

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/100800 WO2018072779A1 (fr) 2016-10-21 2017-09-19 Amortisseur de vibrations de torsion

Country Status (2)

Country Link
DE (2) DE102017121644A1 (fr)
WO (1) WO2018072779A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2150654A (en) * 1983-12-01 1985-07-03 Sachs Systemtechnik Gmbh Friction disc clutch
DE4239770A1 (en) * 1991-12-05 1993-06-09 Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De Bearing fitting for flywheel - has one piece retaining seat with shoulder to hold bearing axially. seat face being chamfered for ease of fit
JPH0942378A (ja) * 1995-08-02 1997-02-10 Nissan Diesel Motor Co Ltd 自動車用フライホイール
JP2004052960A (ja) * 2002-07-23 2004-02-19 Nissan Diesel Motor Co Ltd フライホイール
DE102010019536A1 (de) 2009-06-04 2010-12-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Zweimassenschwungrad
US20140353892A1 (en) * 2013-05-28 2014-12-04 Schaeffler Technologies Gmbh & Co. Kg Spring retainer for a torsional vibration damper and method of producing a spring retainer

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017088870A1 (fr) 2015-11-26 2017-06-01 Schaeffler Technologies AG & Co. KG Amortisseur sans bride, notamment volant d'inertie à double masse

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2150654A (en) * 1983-12-01 1985-07-03 Sachs Systemtechnik Gmbh Friction disc clutch
DE4239770A1 (en) * 1991-12-05 1993-06-09 Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De Bearing fitting for flywheel - has one piece retaining seat with shoulder to hold bearing axially. seat face being chamfered for ease of fit
JPH0942378A (ja) * 1995-08-02 1997-02-10 Nissan Diesel Motor Co Ltd 自動車用フライホイール
JP2004052960A (ja) * 2002-07-23 2004-02-19 Nissan Diesel Motor Co Ltd フライホイール
DE102010019536A1 (de) 2009-06-04 2010-12-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Zweimassenschwungrad
US20140353892A1 (en) * 2013-05-28 2014-12-04 Schaeffler Technologies Gmbh & Co. Kg Spring retainer for a torsional vibration damper and method of producing a spring retainer

Also Published As

Publication number Publication date
DE102017121644A1 (de) 2018-04-26
DE112017005304A5 (de) 2019-07-04

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