WO1999060283A1 - Elastische wellenkupplung - Google Patents
Elastische wellenkupplung Download PDFInfo
- Publication number
- WO1999060283A1 WO1999060283A1 PCT/EP1999/003401 EP9903401W WO9960283A1 WO 1999060283 A1 WO1999060283 A1 WO 1999060283A1 EP 9903401 W EP9903401 W EP 9903401W WO 9960283 A1 WO9960283 A1 WO 9960283A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft coupling
- elastomer body
- coupling according
- elastomer
- modules
- Prior art date
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts
- F16D3/74—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts the intermediate member or members being made of rubber or other rubber-like flexible material
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/02—Overheat protection, i.e. means for protection against overheating
- F16D2300/021—Cooling features not provided for in group F16D13/72 or F16D25/123, e.g. heat transfer details
- F16D2300/0212—Air cooling
Definitions
- the present invention relates to an elastic shaft coupling, which has at least one torsion element with an elastically deformable elastomer body as a transmission element, to which axial connecting flanges are firmly attached on the input and output sides.
- connecting flanges are firmly vulcanized onto the axial end faces of at least one rubber body serving as a transmission element.
- the shaft coupling is integrated into the drive train via the connecting flanges, the torque being transmitted exclusively via the rubber material of the elastomer body. Due to their elasticity, these torsion elements are subjected to rotational shear when loaded under the shaft axis. Torque fluctuations are decoupled from the connected drive train by the elasticity of the rubber body (s).
- the problems explained above have been successfully countered by constructive designs, so that rubber couplings have long been regarded as extremely reliable components with advantageous operating properties.
- the local loads are reduced to a harmless level.
- the development of the local mechanical or thermal loads is either immediately restricted and / or effective cooling is ensured.
- Some advantageous measures in this regard are given, for example, in DE 37 10 390 C2.
- the connecting flanges are conical in shape, so that the rubber body is given a V-shaped cross-section which widens linearly towards the outside. Because the axial width of the elastomer body increases radially from the inside out, the outer fibers have a greater elastic length. The resulting lower local expansion is advantageous with regard to the heat development and the stress on the rubber-metal interfaces.
- the heat loss generated is effectively dissipated using other measures, such as the segmented design of the transmission elements and the introduction of continuous cooling windows.
- the invention proposes that the axial width of the elastomer body, seen radially from the inside out, increases disproportionately at least in sections.
- the cross section of the elastomer body has at least one inner and one outer radial region, the axial width increasing faster with increasing radius in the outer region than in the inner region. While the width of the elastomer body in the prior art increases only linearly, ie proportionally, over the entire cross section due to the conical jacket-shaped connecting flanges, the effective elastic width according to the invention increases faster, at least in sections, towards the outside.
- a particularly advantageous embodiment of the invention provides that the cross section of the elastomer body is bell-shaped widened radially from the inside out.
- the bell-shaped design which could also be called a goblet or tulip shape, means a continuously curved, rounded transition between the individual areas. The avoidance of a bent course of the connecting flanges leads to a uniform stress on the rubber-metal interface. Discontinuities are largely avoided.
- the invention can of course be implemented equally on a continuously ring-shaped as well as on a segmented elastomer body.
- the particular advantage of the invention results from the fact that the elastic path length in the outer regions is better matched to the mechanical and thermal stresses occurring there, which increase disproportionately with the radius.
- the outer surface area of the elastomer body is also enlarged to such an extent that there are fewer local expansions and at the same time there is better heat dissipation to the ambient air. This significantly reduces the aging effects mentioned at the beginning. For a given amount of the total cross-sectional area of the elastomer body, the total is one more homogeneous stress.
- the transferable power density is thus increased. This means that the clutch can be smaller for a given torque and thus takes up less installation space. Alternatively, a correspondingly higher output can be transmitted in the case of a coupling with the same dimensions.
- the transmission element to have at least one inner elastomer body and at least one outer elastomer body, the elastomer bodies being arranged coaxially to the coupling axis at a radial distance from one another and a common connecting flange on the input and output sides to have.
- This design according to the invention can be implemented equally in the case of couplings according to the prior art mentioned at the outset, and also in connection with the elastomer bodies which disproportionately widen outwards according to the invention.
- a torsion element designed according to the invention has not only one-piece radial elements, but at least two or more ring-shaped or segment-shaped, separate elastomer bodies, which have a radial spacing from one another, both on the drive side and on the driven side each have a radially continuous, common connection flange.
- a particular advantage of the invention results from the fact that the air-flushed cooling channels which are continuous in the circumferential direction are axially limited by the metal connecting flanges.
- the heat generated in the poorly heat-conducting rubber material of the elastomer body under dynamic loading is dissipated particularly well by the fact that in the cooling channels air flowing along transfers the absorbed heat directly to the heat-conducting connection flanges.
- critical local thermal peak loads in the rubber material can additionally be prevented in the invention by the fact that in particular the heavily stressed outer elastomer bodies are given smaller radial dimensions. For the first time, this enables cooling that is optimally matched to the local thermal loads, which results in advantageous, particularly uniform stressing of the elastomer material. This has the particular advantage that both the transferable power density and the service life are increased.
- the elastomer bodies are attached to common one-piece connecting flanges. This means that several inner and outer elastomer bodies are vulcanized directly onto a radially continuous connecting flange.
- the connecting flange can be designed in the form of a ring in one piece or composed of ring segments. In the latter embodiment, the individual elastomer bodies also have the shape of ring segments.
- a particularly advantageous alternative of the shaft coupling according to the invention provides that the inner and outer elastomer bodies to form transmission element modules are provided with separate connecting flange modules which can be detachably connected to one another radially in succession.
- the particular advantage of this embodiment is that shaft couplings in different sizes can be constructed in a modular manner from standardized modules.
- the connecting flange modules are provided on the circumference with corresponding connecting means, for example with screwable flange bores.
- the transmission element modules can be radially cascaded, the common connecting flanges being formed in their entirety by the connecting flange modules connected to one another.
- the module-like structure has the advantage in production that the transmission element modules can be made available with different radii. Shaft couplings for different performance classes can then be assembled with little effort, without the need for complex and costly special designs.
- Another advantage is that worn-out transmission element modules can be exchanged with little effort during operation, and thus the usability of a damaged coupling can be restored at short notice.
- the connecting flange modules of the transmission element modules are expediently designed to be nestable radially one inside the other.
- the connecting flange modules each project radially beyond the elastomer body.
- the inner and outer modules are matched to one another in such a way that the connecting flanges of one module can be inserted radially between the connecting flanges of the next module that adjoins inwards or outwards.
- the connecting flange modules have corresponding axial flange bores for screwing in the radial edge regions. It is then attached using flange bolts.
- the transmission element modules can alternatively be segmented or continuously annular.
- the connecting flange segments of the outer modules can easily be radially cascaded for assembly.
- the connecting flange modules are designed to be closed in a ring, they must first be assembled in the axial direction for coaxial mounting and then firmly connected to one another using suitable connecting means, for example by screwing. Attachments that can be retrofitted, such as flange rings or the like, can be used for this purpose.
- a particularly advantageous variant which does not require such additional parts and nevertheless enables a symmetrically nested design, provides that the connecting flange modules are designed in a bayonet-like manner.
- the connecting flanges have corresponding inner and outer bayonets with radial ones Recesses and projections so that in the assembly position a flange ring can first be positioned in the axial direction over the next smaller connecting flange and can then be locked axially in the coaxial installation position by a relative rotation. The projections opposite each other in this locked position are then screwed together.
- An outer elastomer body is preferably axially wider than an inner elastomer body. This takes account of the fact that the nominal thrust stress remains constant radially from the inside out.
- the axial width of the inner and outer elastomer bodies increases disproportionately, at least in sections, when viewed from the inside out.
- the radial elastomer cross section thus has a bell-shaped or tulip-shaped cross section, seen radially from the inside out. This can affect both each individual elastomer body and the entirety of the elastomer body in the
- each transmission element can have axially continuous cooling windows.
- cooling elements can be permanently embedded in the elastomer body. These are components made of good heat-conducting material, which run through core areas with maximum heat development and relatively cooler outside areas in the elastomer. They ensure effective heat dissipation from the critical areas.
- these cooling elements are preferably designed as axial cooling plates and extend at least to the outer surface of the respective elastomer body. If they protrude outwards, this has the advantage in terms of production technology that they can be securely and firmly clamped in the above areas when the rubber is injected during vulcanization.
- the connecting flange has axially and / or radially projecting holding shoulders which are encompassed by the elastomer body. These holding shoulders are preferably designed as ring shoulders with a rounded cross section. This results in better adhesion of the vulcanization connection in the particularly stressed edge areas.
- FIG. 1 shows a cross section through a transmission element according to the invention in a first embodiment.
- FIG. 2 shows a cross section through a transmission element according to the invention in a second embodiment
- Fig. 3 shows a cross section through a shaft coupling composed of transmission element modules according to the invention.
- FIG. 1 schematically shows a radial cross section through a torsion element according to the invention, which is provided with the reference number 1 as a whole.
- the coupling axis K is in the view shown in the drawing below.
- the torsion element 1 can be both ring-shaped and segmented.
- the torsion element 1 has axial connecting flanges 2 made of steel, which are axially vulcanized onto rubber bodies 3a, 3b, 3c and 3d.
- the connecting flanges 2 project radially beyond the rubber bodies 3a, 3b, 3c, 3d and are provided with axial flange bores 4 in these areas.
- the transmission element 1 can be incorporated into a drive train - or - several transmission elements 1 of this type can be radially cascaded.
- connection flanges are 2 V-shaped to each other.
- the axial width of the rubber bodies 3a, 3b, 3c, 3d located therebetween increases evenly when viewed radially from the inside out.
- the connecting flanges 2 are swung outward relative to one another, so that the axial width of the rubber body 3 increases disproportionately in this area. This results in the tulip or bell shape according to the invention of the entire elastomer coupling body formed from the rubber bodies 3a, 3b, 3c, 3d.
- Continuous cooling channels 5 run in the circumferential direction between the rubber bodies 3a, 3b, 3c and 3d.
- the connecting flanges 2 are provided with cooling windows 6.
- each individual rubber body 3a, 3b, 3c and 3d is tulip-shaped or bell-shaped, viewed radially from the inside out. H. its axial width increases disproportionately outwards in sections. In addition, the radial thickness of the rubber body decreases towards the outside, which results in cooling that is better matched to the local load.
- each individual rubber body 3a, 3b is therein and 3c are each provided with separate connecting flange modules 2a, 2b and 2c, so that transmission element modules 1a, 1b and 1c are formed.
- the radially outer ones of the transmission element modules 1a, 1b and 1c are each cascaded into the inner ones, whereby the connecting flanges 2a, 2b and 2c each overlap in the area of the flange bores 4 and can be screwed together by means of flange bolts (not shown).
- the rubber bodies 3a, 3b, 3c are designed for each transmission element 1a, 1b, 1c as in FIG. 2 - each tulip- or bell-shaped in cross-section.
- Continuous cooling channels 5 extend in the circumferential direction between the transmission element modules 1a, 1b, 1c which are detachably connected to one another in a modular manner.
- three transmission element modules 1a, 1b, 1c - or just two or more - can be cascaded. This enables the clutch to be optimally adapted to the torque to be transmitted. Standardization of the transmission element modules 1a, 1b, 1c enables particularly efficient production.
- the transmission element modules 1a, 1b, 1c can alternatively be designed in the form of a closed ring or a segment.
- the connecting flanges 2a, 2b, 2c and the elastomer bodies 3a, 3b, 3c are then designed in one piece or divided accordingly.
- the connecting flanges 2a, 2b, 2c are preferably bayonet-like with corresponding radial projections and recesses.
- the transmission elements 1a, 1b, 1c shown in FIG. 3 can be provided with cooling windows 6 or additional cooling channels 5 in the same way as that shown in FIGS. 1 and 2.
- cooling elements (not shown here) can be embedded in the rubber bodies 3.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Motor Power Transmission Devices (AREA)
- Springs (AREA)
- General Details Of Gearings (AREA)
- Gears, Cams (AREA)
- Mechanical Operated Clutches (AREA)
- Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000549865A JP4416099B2 (ja) | 1998-05-15 | 1999-05-17 | 弾性的な軸継ぎ手 |
DE59908655T DE59908655D1 (de) | 1998-05-15 | 1999-05-17 | Elastische wellenkupplung |
US09/700,472 US6623362B1 (en) | 1998-05-15 | 1999-05-17 | Elastic shaft coupling |
EP99952107A EP1078174B1 (de) | 1998-05-15 | 1999-05-17 | Elastische wellenkupplung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19821948.2 | 1998-05-15 | ||
DE19821948A DE19821948C2 (de) | 1998-05-15 | 1998-05-15 | Elastische Wellenkupplung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1999060283A1 true WO1999060283A1 (de) | 1999-11-25 |
Family
ID=7867957
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1999/003401 WO1999060283A1 (de) | 1998-05-15 | 1999-05-17 | Elastische wellenkupplung |
Country Status (8)
Country | Link |
---|---|
US (1) | US6623362B1 (de) |
EP (1) | EP1078174B1 (de) |
JP (1) | JP4416099B2 (de) |
KR (1) | KR100486934B1 (de) |
CN (1) | CN1120945C (de) |
DE (2) | DE19821948C2 (de) |
ES (1) | ES2217820T3 (de) |
WO (1) | WO1999060283A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006016651A1 (de) * | 2006-04-08 | 2007-10-11 | Hackforth Gmbh | Elastische Wellenkupplung mit ungleichen Gummikörpern |
DE102006044109A1 (de) | 2006-09-20 | 2008-03-27 | Zf Friedrichshafen Ag | Verbindung eines ersten mit einem zweiten zylindrischen Bauteil und Verfahren zur Montage des ersten und des zweiten Bauteiles |
DE102008016700A1 (de) | 2008-03-31 | 2009-10-01 | Hackforth Gmbh | Elastische Wellenkupplung |
US8162762B2 (en) * | 2009-07-01 | 2012-04-24 | Hamilton Sundstrand Corporation | Generator flexible drive coupling |
DE102011117154A1 (de) * | 2011-10-28 | 2013-05-02 | Hackforth Gmbh | Verfahren zur Herstellung einer elastischen Wellenkupplung |
CN102654164A (zh) * | 2012-05-10 | 2012-09-05 | 横店集团联宜电机有限公司 | 联轴器 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2295316A (en) * | 1939-05-06 | 1942-09-08 | Lord Mfg Co | Joint |
US2742769A (en) * | 1953-02-16 | 1956-04-24 | Baldwin Lima Hamilton Corp | Coupling |
FR1267022A (fr) * | 1960-09-09 | 1961-07-17 | Metzeler Gummiwerke Ag | Accouplement flexible et libérable pour mécanismes de transmission subissant des accélérations non uniformes |
US3545231A (en) * | 1969-02-07 | 1970-12-08 | Reliance Electric Co | Multiple flexible element coupling |
DE3710390A1 (de) * | 1987-03-28 | 1988-10-13 | Hackforth Gmbh & Co Kg | Elastische wellenkupplung |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1790516A (en) * | 1931-01-27 | Alfeed o | ||
DE675155C (de) * | 1936-02-15 | 1939-05-02 | Getefo Ges Fuer Tech Fortschri | Drehmomentuebertragende elastische Kupplung mittels Gummimetallbauteils |
SU571637A1 (ru) * | 1975-09-29 | 1977-09-05 | Московский Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им. Н.Э.Баумана | Упруго-компенсационна муфта |
US4094520A (en) * | 1977-05-02 | 1978-06-13 | The United States Of America As Represented By The Secretary Of The Army | Self centering flange gasket assembly |
DE3109388A1 (de) * | 1981-03-12 | 1982-09-30 | Hackforth GmbH & Co KG, 4690 Herne | "hochelastische wellenkupplung" |
DE3310695A1 (de) * | 1983-03-24 | 1984-09-27 | Hackforth GmbH & Co KG, 4690 Herne | Hochelastische wellenkupplung |
FR2583486B1 (fr) * | 1985-06-14 | 1989-03-31 | Valeo | Dispositif amortisseur de torsion, notamment pour embrayage de vehicule automobile, a amortissement au moins partiellement du a un element elastomere |
DE19703936A1 (de) * | 1997-02-04 | 1998-08-06 | Hackforth Gmbh & Co Kg | Wellenkupplung |
DE29716048U1 (de) * | 1997-09-08 | 1997-12-04 | Deschler, Gerhard, Dipl.-Ing., 90425 Nürnberg | Elastische Kupplung zum Übertragen von Drehmomenten bei Antriebseinheiten, insbesondere solchen eines Antriebsmotors |
-
1998
- 1998-05-15 DE DE19821948A patent/DE19821948C2/de not_active Expired - Fee Related
-
1999
- 1999-05-17 EP EP99952107A patent/EP1078174B1/de not_active Expired - Lifetime
- 1999-05-17 WO PCT/EP1999/003401 patent/WO1999060283A1/de not_active Application Discontinuation
- 1999-05-17 JP JP2000549865A patent/JP4416099B2/ja not_active Expired - Fee Related
- 1999-05-17 US US09/700,472 patent/US6623362B1/en not_active Expired - Lifetime
- 1999-05-17 CN CN99807415A patent/CN1120945C/zh not_active Expired - Fee Related
- 1999-05-17 KR KR10-2000-7012731A patent/KR100486934B1/ko not_active IP Right Cessation
- 1999-05-17 ES ES99952107T patent/ES2217820T3/es not_active Expired - Lifetime
- 1999-05-17 DE DE59908655T patent/DE59908655D1/de not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2295316A (en) * | 1939-05-06 | 1942-09-08 | Lord Mfg Co | Joint |
US2742769A (en) * | 1953-02-16 | 1956-04-24 | Baldwin Lima Hamilton Corp | Coupling |
FR1267022A (fr) * | 1960-09-09 | 1961-07-17 | Metzeler Gummiwerke Ag | Accouplement flexible et libérable pour mécanismes de transmission subissant des accélérations non uniformes |
US3545231A (en) * | 1969-02-07 | 1970-12-08 | Reliance Electric Co | Multiple flexible element coupling |
DE3710390A1 (de) * | 1987-03-28 | 1988-10-13 | Hackforth Gmbh & Co Kg | Elastische wellenkupplung |
Also Published As
Publication number | Publication date |
---|---|
KR100486934B1 (ko) | 2005-05-03 |
JP2002515572A (ja) | 2002-05-28 |
EP1078174B1 (de) | 2004-02-25 |
CN1120945C (zh) | 2003-09-10 |
CN1305567A (zh) | 2001-07-25 |
DE19821948A1 (de) | 1999-12-02 |
JP4416099B2 (ja) | 2010-02-17 |
US6623362B1 (en) | 2003-09-23 |
DE19821948C2 (de) | 2003-11-27 |
DE59908655D1 (de) | 2004-04-01 |
ES2217820T3 (es) | 2004-11-01 |
KR20010071255A (ko) | 2001-07-28 |
EP1078174A1 (de) | 2001-02-28 |
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