CN108626310B - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN108626310B CN108626310B CN201810179072.5A CN201810179072A CN108626310B CN 108626310 B CN108626310 B CN 108626310B CN 201810179072 A CN201810179072 A CN 201810179072A CN 108626310 B CN108626310 B CN 108626310B
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- CN
- China
- Prior art keywords
- damper
- spring
- torsional vibration
- circumferential direction
- loading means
- Prior art date
- Legal status (The legal status 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 status listed.)
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Classifications
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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
- F16F15/121—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
- F16F15/123—Wound springs
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
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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
- F16F15/121—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
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
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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
- F16F15/121—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
- F16F15/123—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
- F16F15/12—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
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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 torsional vibration damper (1) has a first damper part (2) arranged so as to be rotatable about a rotational axis (d) and a second damper part (5) which can be rotated in a limited manner about the rotational axis (d) relative to the first damper part (2) against the action of a spring device (4) which has at least one arc spring (8, 9, 10, 11) arranged in the circumferential direction and which has a multi-stage characteristic curve, the arc spring being loaded by means of a first loading means (12, 13, 14) assigned to the first damper part and a second loading means assigned to the second damper part. In order to fully utilize the installation space provided for the spring device, first bow springs (8, 9) and second bow springs (10, 11) which are shorter than the first bow springs are arranged alternately in the circumferential direction, and the first and second bow springs are loaded in series at different torsion angles between the damper parts.
Description
Technical Field
The invention relates to a torsional vibration damper having a first damper part arranged so as to be rotatable about an axis of rotation and a second damper part which can be rotated relative to the first damper part about the axis of rotation in a limited manner against the action of a spring device having at least one arcuate spring arranged in the circumferential direction, wherein the spring device has a multi-stage characteristic curve, and wherein the arcuate spring is loaded by means of a first loading means associated with the first damper part and a second loading means associated with the second damper part.
Background
Torsional vibration dampers are used for torsional vibration isolation, in particular in the drive train of a motor vehicle. In this case, a dual-mass flywheel is advantageous, in particular, on account of the large spring capacity, which has a first and a second damper part (for example input and output) and a spring arrangement acting between them in the circumferential direction, which has arcuate springs mounted in spring channels. In order to further increase the spring capacity, the spring device can be constructed in the manner of arcuate springs nested one within the other.
A torsional vibration damper of this type is known from DE 102009015577 a1, in which a multi-stage characteristic curve is also provided, in that the inner springs of the arcuate springs nested one inside the other are of shorter construction and are therefore acted upon by the loading means only when the torsion angle between the input part and the output part is greater.
Disclosure of Invention
The object of the invention is to develop a torsional vibration damper. The torsional vibration damper should in particular be provided with a spring device which makes full use of the installation space of the spring channel.
This object is achieved by the subject matter of claim 1. The dependent claims of claim 1 give further advantageous embodiments of the subject matter of claim 1.
The proposed torsional vibration damper serves for torsional vibration isolation of torsional vibrations, in particular in a motor vehicle drive train having an internal combustion engine with torsional vibrations. The torsional vibration damper can be designed as a dual mass flywheel having a primary flywheel mass and a directly and/or coupled or downstream connected secondary flywheel mass. The torsional vibration damper can be connected directly to the crankshaft of the internal combustion engine or be arranged in the drive train device, for example inside or outside the housing of the hydrodynamic torque converter.
The torsional vibration damper comprises a first damper part (for example the input part or the output part) arranged so as to be rotatable about the axis of rotation and a second damper part (for example the output part or the input part, respectively) which can be rotated relative to the input part about the axis of rotation in a limited manner against the action of a spring device having an arcuate spring arranged in a spring channel in the circumferential direction. The terms input element and output element can be interchanged in this case, in particular in the context of torques introduced into the torsional vibration damper from both sides (for example drag torques or slip torques), and can be implemented differently in terms of their design, in view of the requirements made of the torsional vibration damper.
In order to provide two damper stages of the torsional vibration damper, the spring device has a multi-stage, at least two-stage characteristic curve. This means that a part of the bow springs is initially engaged at a torsion angle between the damper parts and the remaining bow springs are engaged when a predefined torsion angle or torsion angle range is exceeded. The arcuate springs can each be embodied as individual arcuate springs or as groups of arcuate springs nested one inside the other. The arc springs are loaded by means of the damper parts (e.g. loading devices assigned to the input and output of the torsional vibration damper).
In order to implement a multi-stage characteristic curve without a free angle in the bow spring and at the same time to implement a multi-stage characteristic curve without losing the available installation space, a first bow spring and a second bow spring that is shorter than the first bow spring are arranged alternately in the circumferential direction, wherein a serial loading of the first and second bow springs with different torsion angles between the loading means is provided. This means that all the curved springs are received in the spring channels without free space and thus completely occupying the available installation space. In this case, the free angle of a part of the arcuate spring is controlled outside the spring channel or by means of a corresponding arrangement of the loading means.
In order to provide a soft transition between the damper stages, a transition stage is provided in the transition between the damper stage with a part of the bow springs and the second damper stage with all bow springs. According to an advantageous embodiment of the torsional vibration damper, the control device for the loading can be provided in the output-side loading means, so that two damper stages are provided.
For example, the damper part can have two flange parts which are arranged about the axis of rotation and can be rotated relative to one another about the axis of rotation, said flange parts having output-side loading means which are inserted between the end sides of the arcuate springs adjacent in the circumferential direction. The loading means of the one flange part assigned to the damper part and the loading means of the other flange part alternate in the circumferential direction, and the rotationally locked driving means act between the flange parts after a predefined free angle has been passed.
For example, flange parts for providing a driver are arranged axially adjacent to one another, wherein circular-arc-shaped elongated holes which are distributed in the circumferential direction and which predefine the free angle are provided in one flange part, into which elongated holes an axial projection of the other flange part engages. The first flange part is loaded with, for example, a first longer arcuate spring or an arcuate spring package of arcuate springs nested one inside the other in order to activate the first damper stage. After the free angle predefined by the elongated hole has been exceeded, the first flange part carries the other flange part, which is loaded with the additional bow spring or bow spring group, and the second damper stage with all bow springs is activated.
The proposed transition stage between the two damper stages can be provided, for example, by means of spring elements which are arranged in an active manner on the circumferential side on the oblong holes. The rigidity of these spring elements can be designed as a function of the transitional moment between the two damper stages. The spring element can be, for example, a helical compression spring, a disk spring stack or the like. In order to protect the spring element against overloading, a stop which acts in the circumferential direction can be provided in order to bridge the spring element after the spring element angle of action between the two flange parts has passed.
Alternatively or additionally, the transition stage can be provided by means of a loading means arranged obliquely in the circumferential direction for loading the bow spring to be engaged in the second damper stage. Here, a part of the end face of the arcuate spring is initially loaded with increasing torsion angle, so that the spring action of the arcuate spring is first partially active before the end face begins to be surface-loaded.
According to an alternative embodiment of the torsional vibration damper (instead of controlling the serial loading of the bow springs on the output side), a control device for the loading can be provided on the damper component with the spring channel. For this purpose, for example, the arcuate spring can be received in an arcuate spring carrier arranged so as to float in the circumferential direction relative to the spring channel, and first loading means of this damper component are provided in the arcuate spring carrier and second loading means assigned to the damper component are provided on the spring channel, which are arranged alternately with the first loading means in the circumferential direction. The loading means associated with the other damper part is preferably of the same type, for example in the form of a one-piece flange part with radially extending loading means. The first arcuate spring is loaded by a loading means of the spring channel according to the torsion angle. When a predefined free angle is exceeded, the loading means of the spring channel drives the loading means of the arcuate spring carrier, thereby additionally loading the second arcuate spring.
Drawings
The invention is explained in detail on the basis of the embodiments shown in fig. 1 and 2. Shown here are:
figure 1 is a view of a torsional vibration damper in a schematic view,
and
fig. 2 is a sectional view through the torsional vibration damper of fig. 1 along the sectional line a-a of fig. 1.
Detailed Description
Fig. 1 and 2 show a schematic representation of a torsional vibration damper 1 arranged about a rotational axis d in a view (fig. 1) and in a sectional view along the sectional line a-a of fig. 1 (fig. 2) in a preferred manner for a hydrodynamic torque converter. The first damper part 2, which is designed as an output part here, for example, has a spring channel 3 for receiving a spring device 4. The second damper part 5, which is designed as an input part here, for example, is arranged in a rotationally fixed manner relative to the first damper part 2 about the rotational axis d against the action of the spring device 4 acting in the circumferential direction.
The spring device 4 is formed from two differently long arcuate spring groups 6, 7, which are arranged alternately in the circumferential direction in the spring channel 3 and have arcuate springs 8, 9, 10, 11 nested one inside the other. Instead of the bow spring sets 6, 7, two individual bow springs can be provided.
Loading means 12, which are assigned to the damper part 2, are each arranged on the spring channel 3 and engage between the end sides of the adjacent arcuate springs 8, 9, 10, 11 in the circumferential direction.
The loading means 13, 14 assigned to the second damper part 5 are arranged on different flange parts 15, 16 which are arranged concentrically to one another and to the axis of rotation d and are axially adjacent.The loading means 13 are assigned to the flange part 15 and the loading means 14 are assigned to the flange part 16 and alternate in the circumferential direction. This means that the torque is converted into a drive torque MANWhen introduced into the damper part 5 and the flange part 15, the long arcuate spring package 6 between the loading means 12, 13 is first compressed when the first damper stage is formed. If a predefined torsion angle between the damper parts 2, 5 is exceeded and thus after the free angle has been passed, the flange part 15 drives the flange part 16 by means of the driver 17, so that the short bow spring set 7 between the loading means 12, 14 is additionally and thus compressed in series when the second damper stage is activated.
The driver 17 is formed by an elongated circular-arc-shaped hole 18 introduced into the flange part 15 and an axial projection 19 engaging into said elongated hole. In order to form the transition stage between the two damper stages, spring elements 22, 23 are provided on the circumferential side stops 20, 21 of the oblong hole 18, said spring elements damping the transition from the first damper stage into the second damper stage by the projections 19 elastically striking the stops 20, 21. The spring elements 22, 23 are matched to a transition torque which is less than the maximum torque which can be transmitted by the torsional vibration damper 1 and are preferably protected against damage by bridging the two flange parts 15, 16 by means of stops which are not shown. The spring elements 22, 23 can be provided with different rigidities depending on the different torques introduced into the damper parts 2, 5, for example the drag torque and the slip torque of the drive train.
List of reference numerals
1 torsional vibration damper
2 parts of vibration damper
3 spring channel
4 spring device
5 parts of damper
6 arc spring group
7 arc spring group
8 arc spring
9 arc spring
10 arc spring
11 arc spring
12 loading device
13 loading device
14 loading device
15 Flange part
16 Flange part
17 carrying device
18 long hole
19 projection
20 back stop
21 stop part
22 spring element
23 spring element
d axis of rotation
MANDrive torque
Claims (9)
1. A torsional vibration damper (1) having a first damper part (2) arranged so as to be rotatable about a rotational axis (d) and a second damper part (5) which can be rotated in a limited manner about the rotational axis (d) relative to the first damper part (2) against the action of a spring device (4) having an arcuate spring arranged in a spring channel (3) in the circumferential direction, wherein the spring device (4) has a multi-stage characteristic curve and is loaded by means of first loading means assigned to the first damper part (2) and second loading means assigned to the second damper part (5), characterized in that first arcuate springs (8, 9) and second arcuate springs (10, 10) which are shorter relative to the first arcuate springs (8, 9) are arranged alternately in the circumferential direction, 11) Furthermore, serial loading of the first and second bow springs with different torsion angles between the damper parts (2, 5) is provided, wherein a flexible transition stage is provided in the transition between the damper stage with a part of the bow springs and the second damper stage with all bow springs.
2. A torsional vibration damper (1) as claimed in claim 1, characterized in that a control device for the loading is provided in the second damper part (5).
3. The torsional vibration damper (1) as claimed in claim 1 or 2, characterized in that the second damper part (5) has two flange parts (15, 16) arranged about the axis of rotation (d), the second loading means comprising third and fourth loading means which are embedded between the end sides of arc springs adjacent in the circumferential direction, wherein the third loading means (13) of one flange part (15) and the fourth loading means (14) of the other flange part (16) alternate in the circumferential direction, and wherein a driver (17) acts between the flange parts (15, 16), which driver drives the other flange part (16) by the one flange part (15) after the free angle has been passed.
4. A torsional vibration damper (1) as claimed in claim 3, characterized in that the flange parts (15, 16) are arranged axially adjacent to one another, and in that elongate holes (18) which are distributed over the circumference and which are in the shape of a circular arc and which predefine the free angle are provided in the one flange part (15), into which elongate holes the axial projections (19) of the other flange part (16) engage.
5. The torsional vibration damper (1) as claimed in claim 4, characterized in that the transition stage is provided by means of spring elements (22, 23) which are arranged operatively on the long hole (18) on the circumferential side.
6. Torsional vibration damper (1) as claimed in claim 5, characterized in that a stop acting in the circumferential direction is provided in order to bridge the spring element (22, 23) after the angle of action of the spring element (22, 23) between the two flange parts (15, 16) has passed.
7. Torsional vibration damper (1) according to claim 1, characterized in that the transition stage is provided by means of loading means arranged obliquely in the circumferential direction for loading the bow springs (10, 11) to be engaged in the second damper stage.
8. A torsional vibration damper as claimed in claim 1, characterized in that a control device for the loading is provided in the second loading means.
9. The torsional vibration damper as claimed in claim 1 or 2, characterized in that the arcuate springs are received in arcuate spring carriers which are arranged floating in the circumferential direction relative to the spring channels, and in that first portions of the second loading means are provided in the arcuate spring carriers, and second portions of the second loading means are provided on the spring channels in an alternating arrangement with the first portions in the circumferential direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017106230.0A DE102017106230A1 (en) | 2017-03-23 | 2017-03-23 | torsional vibration dampers |
| DE102017106230.0 | 2017-03-23 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108626310A CN108626310A (en) | 2018-10-09 |
| CN108626310B true CN108626310B (en) | 2022-02-25 |
Family
ID=63450226
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810179072.5A Active CN108626310B (en) | 2017-03-23 | 2018-03-05 | Torsional vibration damper |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN108626310B (en) |
| DE (1) | DE102017106230A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109591531A (en) * | 2018-11-09 | 2019-04-09 | 吴宗泽 | A kind of automobile chassis damping |
| DE102019201217B4 (en) | 2019-01-31 | 2022-10-20 | Audi Ag | Drive device for a motor vehicle |
| DE102019125287A1 (en) * | 2019-09-19 | 2021-03-25 | Schaeffler Technologies AG & Co. KG | Torsional damper with multi-stage main damper characteristic |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4690660A (en) * | 1984-07-31 | 1987-09-01 | Kabushiki Kaisha Daikin Seisakusho | Damper disc |
| DE3931428A1 (en) * | 1988-10-18 | 1990-04-19 | Luk Lamellen & Kupplungsbau | Damper for torsional oscillations - consists of two flywheel sections, with flanged piece and coupling |
| JP2012102817A (en) * | 2010-11-11 | 2012-05-31 | Exedy Corp | Lockup device for torque converter |
| CN104641144A (en) * | 2012-07-06 | 2015-05-20 | 舍弗勒技术股份两合公司 | Torsional vibration damper and arrangement and method for the damping of a drivetrain of a motor vehicle |
| CN105190103A (en) * | 2013-05-16 | 2015-12-23 | 株式会社艾科赛迪 | Lock-up device for torque converter |
| CN105257755A (en) * | 2014-07-11 | 2016-01-20 | Valeo离合器公司 | Damper for a torque transmission device of a vehicle |
| CN105485200A (en) * | 2016-01-15 | 2016-04-13 | 中国重汽集团济南动力有限公司 | Clutch driven disc used for commercial vehicle |
| CN205559688U (en) * | 2016-04-20 | 2016-09-07 | 沈阳平和法雷奥汽车传动系统有限公司 | Dual mass flywheel that spring assembly length is different |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009015577A1 (en) | 2008-04-10 | 2009-10-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Rotational vibration damper for use as divided flywheel in torque converter in internal-combustion engine of motor vehicle, has helical compression spring exhibiting set of sections with spring coils of different spring rigidity |
-
2017
- 2017-03-23 DE DE102017106230.0A patent/DE102017106230A1/en not_active Ceased
-
2018
- 2018-03-05 CN CN201810179072.5A patent/CN108626310B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4690660A (en) * | 1984-07-31 | 1987-09-01 | Kabushiki Kaisha Daikin Seisakusho | Damper disc |
| DE3931428A1 (en) * | 1988-10-18 | 1990-04-19 | Luk Lamellen & Kupplungsbau | Damper for torsional oscillations - consists of two flywheel sections, with flanged piece and coupling |
| JP2012102817A (en) * | 2010-11-11 | 2012-05-31 | Exedy Corp | Lockup device for torque converter |
| CN104641144A (en) * | 2012-07-06 | 2015-05-20 | 舍弗勒技术股份两合公司 | Torsional vibration damper and arrangement and method for the damping of a drivetrain of a motor vehicle |
| CN105190103A (en) * | 2013-05-16 | 2015-12-23 | 株式会社艾科赛迪 | Lock-up device for torque converter |
| CN105257755A (en) * | 2014-07-11 | 2016-01-20 | Valeo离合器公司 | Damper for a torque transmission device of a vehicle |
| CN105485200A (en) * | 2016-01-15 | 2016-04-13 | 中国重汽集团济南动力有限公司 | Clutch driven disc used for commercial vehicle |
| CN205559688U (en) * | 2016-04-20 | 2016-09-07 | 沈阳平和法雷奥汽车传动系统有限公司 | Dual mass flywheel that spring assembly length is different |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102017106230A1 (en) | 2018-09-27 |
| CN108626310A (en) | 2018-10-09 |
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