CN114810941A - Torsional vibration damper with increased basic friction by means of two disk spring diaphragms - Google Patents

Torsional vibration damper with increased basic friction by means of two disk spring diaphragms Download PDF

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Publication number
CN114810941A
CN114810941A CN202111525842.5A CN202111525842A CN114810941A CN 114810941 A CN114810941 A CN 114810941A CN 202111525842 A CN202111525842 A CN 202111525842A CN 114810941 A CN114810941 A CN 114810941A
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CN
China
Prior art keywords
torsional vibration
vibration damper
disk spring
preparation
friction
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Pending
Application number
CN202111525842.5A
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Chinese (zh)
Inventor
帕斯卡尔·斯特拉塞
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Filing date
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Publication of CN114810941A publication Critical patent/CN114810941A/en
Pending legal-status Critical Current

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    • 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
    • F16F15/139—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 friction-damping means
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/1215—Leaf springs, e.g. radially extending
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • 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
    • F16F15/133—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 using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

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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)
  • Mechanical Operated Clutches (AREA)

Abstract

The application relates to a torsional vibration damper (1) which is designed as a dual-mass flywheel and can be used in a drive train of a vehicle driven by an internal combustion engine, comprising a primary part (2) and a secondary part (3), the primary part and the secondary part are jointly rotatable and can be rotated in a limited manner relative to each other and a spring damping device (8) acts between them, the arc-shaped spring (7) of the spring damping device is integrated in the inner space (6), the inner space is surrounded as far as possible by the primary part (2) and the associated cover section (5), and at least two disk spring diaphragms (15, 16) fixed to the secondary part (3) are supported radially on the outside at the cover section (5) by a common friction element or two separate friction elements to form a friction pair.

Description

Torsional vibration damper with increased basic friction by means of two disk spring diaphragms
Technical Field
The present application relates to a torsional vibration damper which defines a drive train for a vehicle driven by an internal combustion engine and which is designed as a dual-mass flywheel.
Background
Torsional vibration dampers of this type are known from motor vehicle drive trains, which serve to isolate rotational irregularities of the internal combustion engine between the crankshaft of the internal combustion engine and the transmission input shaft of the transmission.
Torsional vibration dampers configured as dual-mass flywheels are known for use in the drive train of internal combustion engine-driven vehicles, for example as dual-clutch dampers, hybrid dampers or cvt (continuously Variable transmission) dampers for continuously Variable automatic transmissions. The torsional vibration damper brings about a vibration isolation of torsional vibrations which arise in a principle-dependent manner due to the mode of action in the internal combustion engine. In torsional vibration dampers, a primary part, also referred to as the primary mass, is connected to the crankshaft of the internal combustion engine, and a secondary part, also referred to as the secondary mass, is connected to the output side, in particular to a vehicle clutch or to the transmission input. Between the primary part and the secondary part, a spring damping device acting in the circumferential direction is provided with a bow spring loaded on the input side and the output side, which temporarily stores and outputs torque peaks with a time delay.
As is known, for example, from DE 102007003047 a1, a torsional vibration damper comprises two flywheels mounted so as to be rotatable relative to one another, between which a spring damper arrangement is arranged, which damps the rotation of the two flywheels. In the event of torsional oscillations, phase-shifted energy absorption and energy output of the spring damper device occur, so that the non-uniform profile of the torque of the internal combustion engine is smoothed. In this case, one flywheel, the primary part, is fixedly connected to the crankshaft, and the other flywheel, the secondary part, is connected to the transmission input shaft, for example.
Such a torsional vibration damper is shown in DE 102014218966 a1, in which a disk spring diaphragm is provided between the primary part and the secondary part in addition to a spring damping arrangement comprising an arc spring. The radially inner disk spring diaphragm, which is rotationally rigidly fixed at the support flange of the secondary part, is supported axially preloaded via a radially outer force edge (kraft) in combination with a friction element at the primary part.
Disclosure of Invention
The aim is to provide a structurally and/or functionally improved torsional vibration damper with improved basic friction, wherein the measures proposed for this purpose can be used for mass production with low cost outlay.
This object is achieved by a torsional vibration damper according to the invention. Further preferred embodiments or improvements are evident from the description and the accompanying drawings.
The construction principle is that the torsional vibration damper comprises at least two disk spring diaphragms which are separated from each other and are associated with the secondary part, and the disk spring diaphragms are supported at the cover section of the primary part via a common friction element or two separated friction elements.
In the torsional vibration dampers used hitherto with disk springs, it is necessary that the energy input based on the axial spring force takes into account the boundary of the surface pressure in order to limit an inadmissible heating and excessive wear of the friction elements or friction rings fixed at the support region of the disk spring, which is also referred to as force edge.
In contrast to the known solutions, a significantly higher basic friction or basic hysteresis can be achieved in the rotation between the primary part and the secondary part of the torsional vibration damper by means of a disk spring diaphragm assembly comprising two disk spring diaphragms. Each disk spring diaphragm forms, in conjunction with the associated friction lining, a friction pair, also referred to as a friction contact, with the cover section of the primary part. The two disk spring diaphragms produce an increased axial spring force, which advantageously improves the shifting process while reducing noise development. The torsional vibration damper can also be equipped with more than two disk spring diaphragms, if necessary, in order to achieve an increased spring force.
Furthermore, the disk spring diaphragm, which can be integrated by means of simple mounting, forms a friction pair with the cover section of the primary part within the existing installation space of the torsional vibration damper with little expenditure on cost and in a space-neutral manner. In the installed state, an improved sealing of the torsional vibration damper, which defines the interior space for the spring damper device, occurs via the two disk spring diaphragms.
According to a preferred embodiment, the disk spring diaphragms are supported axially and radially offset from the spring damping device on the side of the cover section oriented toward the interior space via friction elements which are axially offset from one another and are designed as friction rings. Furthermore, the uniformly disk-shaped, curved disk spring diaphragm is directly connected to the driven hub of the secondary part. To avoid installation errors, two disk spring diaphragms having a geometry deviating from one another can be used.
Advantageously, all components of the secondary part, the carrier flange, the disk spring diaphragm and the driven hub are fixedly and permanently coupled to one another, in particular by means of a rivet connection, to form a structural unit. Alternatively, it is suitable for the components to be fixed at the secondary part in a non-positive and/or positive-locking manner, for example by screwing or for the disk spring diaphragm to be offset or separated from the main rivet. Preferably, a disk spring diaphragm is fixed on each side of the driven hub of the secondary part, wherein the inner disk spring diaphragm is positioned between the carrier flange and the driven hub.
Furthermore, it is possible to use two disk spring diaphragms of the torsional vibration damper, which have identical or different spring rates, also referred to as spring constants, from one another. According to a preferred embodiment, the outer disk spring diaphragm oriented toward the output side has a greater spring rate than the disk spring diaphragm disposed behind and directed toward the interior. By means of the measures described in conjunction with the associated friction ring for the outer friction pairing, a more constant coefficient of friction profile can be achieved for the outer friction pairing than for the other inner friction pairing, in particular for dry operation. As a side effect, the design ensures that dirt or moisture is better prevented from entering the interior of the torsional vibration damper.
In order to influence the coefficient of friction profile of the frictional contact formed between the friction lining and the cover section of the primary part in a targeted manner, one or both can be lubricated or loaded with lubricant in a targeted manner if required. For example, the intermediate space between the disk spring diaphragms axially spaced apart from one another is partially filled with lubricant in the installed state.
By the described concept of inserting two disk spring diaphragms together with associated friction elements, a lubricant-tight interior of the torsional vibration damper advantageously occurs on the output side. On the one hand, this prevents lubricant or grease from flowing out of the spring damper located in the interior and, on the other hand, protects the interior against the ingress of water and dirt.
The friction rings or friction elements, which are preferably fastened to the respective disk spring diaphragm, are preferably of identical design and are made of a suitable, wear-resistant plastic. Alternatively, it is provided that the friction ring is fixed at the cover section of the primary part. In order to influence the coefficient of friction, for example to achieve values that differ from one another, it is proposed to use friction rings composed of different materials. As a measure for reducing components, instead of two separate, separately positioned friction elements, friction elements cooperating with two disk spring diaphragms can be used, which are supported on a stepped cover section.
For cost optimization and/or for targeted weight reduction, the disk spring diaphragms formed as plate-shaped components can be produced in particular in a chipless manner from a metal material and can be formed as deep-drawn or stamped parts for this purpose. Alternatively, a disk spring diaphragm made of plastic having high strength and high temperature resistance can be used. Suitable plastics are, for example, polyetheretherketone, wherein the membrane disc is preferably designed as an injection-molded part for cost-effective production.
The described torsional vibration damper is preferably suitable for incorporation into a hybrid powertrain, but is also suitable for incorporation into almost all other powertrains. In hybrid applications, the axle drive of the motor vehicle can be carried out purely via the internal combustion engine or by means of a combined drive, wherein the axle drive comprises a shift clutch. Advantageously, a torsional vibration damper comprising two disk spring diaphragms can also be combined with an integrated centrifugal pendulum (FKP) and/or torque limiter (DMB).
Drawings
The subject matter is explained below with reference to the attached figures according to preferred embodiments. The application is not, however, limited to the described embodiments. Shown here are:
fig. 1 shows a half section of an exemplary embodiment of a torsional vibration damper.
Detailed Description
Fig. 1 shows a torsional vibration damper 1, also referred to as a dual-mass flywheel, which can be used between internal combustion engines in a drive train (not shown) of a motor vehicle, which is intended in particular for hybrid applications consisting of an internal combustion engine and an electric motor. The torsional vibration damper 1 comprises on the internal combustion engine side a primary part 2, also referred to as a primary mass, and on the driven side a secondary part 3, also referred to as a secondary mass, which are jointly rotatable about a rotational axis 4 and are rotatable to a limited extent relative to one another. The flange-like primary part 2, together with the associated cover section 5, delimits an interior space 6, also referred to as a spring channel, which delimits an arcuate spring 7 for a spring absorber device 8, also referred to as a spring damper, of known design and of known mode of action, which forms an energy accumulator. An arc spring 7, which is supported and guided in the primary part 2 via a torsion-resistant slide 9, is supported within the interior 6 by one end at a stop (not shown) and by the other spring end at a carrier flange 10 associated with the secondary flange 3. The relative rotation between the primary part 2 and the secondary part 3 takes place counter to the spring force of the arcuate spring 7.
Radially below the spring damper 8, a centrifugal force pendulum 11 is associated with the support flange 10, said centrifugal force pendulum being designed to accommodate a plurality of pendulum units 12 arranged one behind the other in the circumferential direction. Each pendulum assembly 12 is formed by two axially spaced pendulum masses of identical design, which are each arranged movably in opposite relationship laterally to the support flange 10. The centrifugal force pendulum 11, which is of conventional design and known function, can, in the operating state, effect a relative movement of the pendulum mass 12 relative to the carrier flange 10 in the event of rotational irregularities triggered by the internal combustion engine. The multi-part secondary part 3 is coupled via the driven hub 13, for example, to a transmission input shaft (not shown) which engages in a form-fitting manner in a plug-in toothing of the driven hub 13, which is connected to the carrier flange 10 by means of a riveting device 14, also referred to as a central riveting device.
Via a rivet connection 14, furthermore, two disk spring diaphragms 15, 16 are fastened to the secondary part 3, which is supported with a pretensioning force and force fit via friction elements in the form of friction rings 17, 18 on the cover section 5. The disk spring diaphragms 15, 16 increase the basic friction or the basic hysteresis, as a result of which the shifting process can be improved and the noise level can be reduced. Furthermore, the disk spring diaphragms 15, 16 ensure a seal of the interior 6, so that the spring damper arrangement 8 effectively prevents the ingress of undesirable particles and moisture, and on the other hand prevents grease from flowing out of the interior 6, so that the functionality of the torsional vibration damper 1 is ensured.
In order to achieve axially spaced installation positions of the disk spring diaphragms 15, 16, a disk spring diaphragm 15, 16 is provided on each side of the driven hub 13, which disk spring diaphragms are fastened together with the rivet 14 in a manner coupled to one another as a structural unit. In order to avoid incorrect assembly, the two disk-shaped, curved disk spring diaphragms are formed differently from one another. A friction ring 17, 18 is fastened to each disk spring diaphragm 15, 16 on the outside in each case, said friction ring being supported on the stepped inner side of the cover section 5 in a force-fitting manner axially offset from the centrifugal force pendulum 11. Due to this arrangement, an intermediate space 19 is formed which is axially closed by the disk spring diaphragms 15, 16. Alternatively, it is provided that the friction rings 17, 18 are fixed to the cover section 5 of the primary part 2. As a measure for reducing components, instead of two separate, separately positioned friction elements 17, 18, friction elements cooperating with the two disk spring diaphragms 15, 16 can be used, which are supported on the cover section 5.
List of reference numerals:
1 torsional vibration damper
2 Primary part
3 Secondary part
4 axis of rotation
5 cover section
6 inner space
7 arc spring
8 spring damping device
9 sliding seat
10 load-bearing flange
11 centrifugal pendulum
12 pendulum group
13 driven hub
14 riveting device
15 disc spring diaphragm
16 disc spring diaphragm
17 Friction ring
18 friction ring
19 intermediate space

Claims (10)

1. A torsional vibration damper (1) which is configured as a dual-mass flywheel and can be used in a drive train of a vehicle driven by an internal combustion engine, comprising a primary part (2) and a secondary part (3) which are jointly rotatable and can be rotated in a limited manner relative to one another and between which a spring damping device (8) acts, the arcuate springs (7) of which are integrated in an interior space (6) which is enclosed as far as possible by the primary part (2) and an associated cover section (5), and disc spring diaphragms (15, 16) which are fixed at the secondary part (3) being supported at the cover section (5) on the radially outer side via friction elements to form friction pairs,
it is characterized in that the preparation method is characterized in that,
the torsional vibration damper (1) comprises at least two disk spring diaphragms (15, 16) which are supported on the cover section (5) via a common friction element or two separate friction elements.
2. The torsional vibration damper (1) according to claim 1,
it is characterized in that the preparation method is characterized in that,
disk-shaped disk spring diaphragms (15, 16) are supported via friction elements, which are radially offset from one another and are designed as friction rings (17, 18), on the side of the cover section (5) oriented toward the interior (6) and are jointly fixed to the secondary part (3).
3. The torsional vibration damper (1) of claim 1 or 2,
it is characterized in that the preparation method is characterized in that,
the components of the secondary part (3), the carrier flange (10), the disk spring diaphragms (15, 16) and the driven hub (13) are coupled to one another, in particular, by means of a rivet connection (14).
4. The torsional vibration damper (1) according to claim 3,
it is characterized in that the preparation method is characterized in that,
disc spring diaphragms (15, 16) are fixed at both sides of the driven hub (13) of the secondary part (3).
5. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the disk spring diaphragms (15, 16) of the secondary part (3) have identical or different spring rates.
6. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the disk spring diaphragms (15, 16) seal the interior (6) of the torsional vibration damper (1) on the output side in a lubricant-tight manner.
7. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
in the installed state, a closed intermediate space (19) is formed between the disk spring diaphragms (15, 16) which are axially spaced apart from one another.
8. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the friction rings (17, 18) are combined to form a friction element and are supported on the stepped region of the cover section (5).
9. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the disk spring diaphragms (15, 16) are designed as plate-shaped components and are produced in particular from a metal material without cutting.
10. Torsional vibration damper (1) according to any of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the torsional vibration damper (1) can be used in a hybrid power assembly.
CN202111525842.5A 2021-01-27 2021-12-14 Torsional vibration damper with increased basic friction by means of two disk spring diaphragms Pending CN114810941A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021101723.8 2021-01-27
DE102021101723 2021-01-27

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Publication Number Publication Date
CN114810941A true CN114810941A (en) 2022-07-29

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Application Number Title Priority Date Filing Date
CN202111525842.5A Pending CN114810941A (en) 2021-01-27 2021-12-14 Torsional vibration damper with increased basic friction by means of two disk spring diaphragms

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DE (1) DE102021133271A1 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007003047B4 (en) 2006-02-10 2015-11-19 Schaeffler Technologies AG & Co. KG Dual Mass Flywheel
DE102014218966A1 (en) 2014-09-22 2016-03-24 Schaeffler Technologies AG & Co. KG torsional vibration dampers

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