WO2017220582A1 - Accouplement torsio-élastique d'arbres - Google Patents

Accouplement torsio-élastique d'arbres Download PDF

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Publication number
WO2017220582A1
WO2017220582A1 PCT/EP2017/065093 EP2017065093W WO2017220582A1 WO 2017220582 A1 WO2017220582 A1 WO 2017220582A1 EP 2017065093 W EP2017065093 W EP 2017065093W WO 2017220582 A1 WO2017220582 A1 WO 2017220582A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft coupling
chambers
cams
elastically deformable
torsionally
Prior art date
Application number
PCT/EP2017/065093
Other languages
German (de)
English (en)
Inventor
Anton SOKOLOW
Original Assignee
Hackforth Gmbh
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 Hackforth Gmbh filed Critical Hackforth Gmbh
Publication of WO2017220582A1 publication Critical patent/WO2017220582A1/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
    • 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
    • F16D3/64—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 comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • 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
    • F16D3/64—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 comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/68—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 comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being made of rubber or similar material

Definitions

  • the invention relates to a torsionally flexible shaft coupling, in particular for maritime use.
  • Shaft couplings are known in the art in a variety. They are used in particular to correct any existing shaft misalignment, compensate for speed and torque fluctuations and to prevent the transmission of vibrations. For this purpose, they have a drive-side coupling part, which is connected to transmit torque, for example, with a motor, and a driven-side coupling part which, for example, with a work machine torque transmitting connectable. It is generally known that the requirements for torsionally flexible shaft couplings, in particular for boat drives, are special. Here, in particular torsionally flexible shaft couplings are required, which have a progressive characteristic. Among other things, it is required that the shaft coupling should have a rotationally soft behavior with a very low torque or a low rotational speed.
  • a torsionally flexible shaft coupling comprises a hub with axially extending cams, an outer part concentric with the hub and rotatable relative thereto, a plurality of chambers, a plurality of roller bodies disposed in the chambers, and a plurality of elastically deformable elements, which are also arranged in the chambers, and is characterized in that the cams, the roller body and the elastically deformable elements are arranged along a circular arc.
  • the shaft coupling according to the invention has over the prior art to an extremely compact design, so that the coupling according to the invention can also be used in applications with limited space. This will According to the invention achieved in that the elements for transmitting the torque in the circumferential direction, are arranged along a circular arc. Furthermore, it is achieved by the construction according to the invention that the clutch is torsionally elastic at low speeds and is torsionally rigid at higher speeds.
  • the coupling according to the invention thus fulfills the essential requirements for use in the maritime sector.
  • the chambers preferably have an inner and an outer boundary, which are arranged plane-parallel to each other. As a result, a chamber cross-section is obtained which has a constant height substantially over its entire extent. But it is also possible that the chamber cross-section is tapered.
  • the inner and outer boundary approaches each other at least in an outer region or in an edge region of the chamber.
  • the cams can be arranged at different angular distances on the hub. According to the invention, this is to be understood in that the distance between circumferentially adjacent cams is different. The distance between a cam and a neighboring sock on one side can be greater than the distance to a neighboring sock on the other side. By such a configuration, a progressive characteristic of the clutch can be achieved. Some of the cams load only after exceeding a certain angle of rotation of the respective adjacent reel bodies. However, it is also conceivable in principle that the cams are uniformly spaced from each other in the circumferential direction.
  • the cams can be designed differently.
  • the cams may preferably differ from each other in their shape or their outer dimensions. But it is also possible that the cams differ from each other by their internal structure. This can be achieved, for example, in that some cams have a cavity or a recess.
  • the recess preferably extends in the axial direction of the coupling. Since the cams according to the invention can be involved differently in the torque transmission, the strength requirements are correspondingly different to the cam.
  • the hub has an even number of cams. This offers the particular advantage that in at least two different configurations of the cam on the hub, each embodiment in the same number at the shaft coupling exists.
  • At least one cam with one of its circumferentially facing surfaces adjacent to one of the roller body and with another pointing in the circumferential direction surface of one of the elastically deformable elements.
  • the term "adjoining" is not necessarily to be understood as meaning that the cams and the elastic elements or roller bodies must always touch each other, the only essential aspect being that direct contact is established between the cams and the elements adjacent thereto Ideally, such an arrangement is present in each chamber in which an elastically deformable element is located.
  • the roller bodies according to the invention preferably each have a circular cross-section.
  • the roller bodies are preferably elastically deformable.
  • the roller bodies preferably consist of a rubber material.
  • the roller bodies may have a spherical shape. Such a configuration makes it possible to realize a rotationally soft clutch with a progressive characteristic.
  • the roller bodies fill in this embodiment, the corresponding chambers initially not completely. When torque load of the clutch, there is an increasing deformation of the roller body, wherein the rubber material can escape into the free spaces within the chamber. When the material completely fills the space between the cam and the chamber wall, the coupling achieves its maximum rigidity.
  • the roller bodies may be simple cylindrical elements.
  • the characteristic curve of the clutch can by the Shape of the chambers are influenced. In principle, it is also conceivable that a plurality of roller bodies are arranged in each chamber in the circumferential direction one behind the other.
  • the roller body according to the invention may have at least one lip.
  • the lip preferably extends in the axial direction of the roller body.
  • the lip is ideally made of a resilient or elastic material. If the roller body is subjected to pressure during operation, the lip does not prevent the axial extent of the roller body. As a result, the axial forces are kept low during operation, which has a positive effect on the load and wear of the system components.
  • At least one lip can advantageously be arranged on an end face of the roller body. Ideally, the lip extends in regions substantially along the circumference of the reel body.
  • the roller body with the lip is preferably designed such that it completely fills the chamber in the axial direction in the unloaded state of the coupling. It adjoins with its end faces or with an end face and its lip to axial boundaries of the chambers.
  • roller bodies are identical.
  • the roller bodies can have different shapes and / or material properties (eg elasticity).
  • the desired progressive characteristic of the clutch can be achieved.
  • the coupling has roller bodies with a spherical shape and roller bodies with a substantially cylindrical shape, it is advantageous if the ball-shaped roller bodies are arranged in the chambers in such a way that the cams first engage them with a torque when the clutch is acted upon, before further Cams come in contact with the cylindrical roller bodies at higher torques. This ensures that the clutch is rotationally soft at low torque. At higher torques, the clutch is then stiffer.
  • the coupling is designed so that in a non-stressed state of the coupling between the cams and the cylinder-shaped roller bodies, a free space is provided, this space ensures that the engage corresponding cam only from a predetermined by the size of the free space relative angle of rotation of the hub and the outer part of these corresponding cam associated roller bodies.
  • the elastically deformable element is plate-shaped and is preferably located in each second chamber of the outer part.
  • the plate-shaped element advantageously extends in the radial direction of the coupling.
  • the plate-shaped element is attached to the outer part.
  • the outer part may have grooves in which the plate-shaped element engages with its ends.
  • the elastic elements are designed and arranged such that they press the cams against the roller bodies even in a non-rotating state of the coupling.
  • the cams are preferably biased against adjacent roller bodies.
  • the shaft coupling may have a cover, which is designed such that it limits the chambers in an axial direction at least partially.
  • the cover causes the roller bodies and the elastic members can not fall out of the chambers in the axial direction.
  • the cover is designed as a circular ring. It is conceivable that the cover also has radially inwardly projecting holding portions. The holding portions are dimensioned so that they reliably prevent falling out of the roller body or the elastic elements of the chambers.
  • each chamber is assigned exactly one holding section.
  • the cover can be releasably connected to the outer part.
  • the outer part itself can be designed so that it limits the chambers at least partially in an axial direction.
  • the outer part may be annular.
  • the annular part of the outer part is preferably in the axial direction of the roller bodies and on the elastically deformable elements and thus leads them.
  • the outer part is further configured such that it forms the radially inner and outer boundaries of the chambers and preferably also the required for torque transmission limitations of the chambers in the circumferential direction.
  • the inner and outer boundaries can be obtained by the outer part having two substantially cylindrical portions arranged coaxially with each other.
  • the inner portion forms the inner boundary of the chambers and the outer portion of the outer boundary.
  • the sections can also be designed so that the chambers are tapered. In this case, at least the outer portion and the inner portion approach each other in the edge region of the chamber. By such a configuration, the progressive characteristic of the clutch can be further adjusted.
  • At least one section may have a conical shape.
  • FIGS. show a particularly preferred embodiment of the invention.
  • the invention is not limited to the embodiment shown.
  • the invention includes, as far as is technically feasible, any combination of the technical features that are listed in the claims or described in the description as being relevant to the invention.
  • FIG. 1 perspective view of the outer part according to the invention with roller bodies and elastically deformable elements arranged therein
  • Fig. 2 perspective view of a hub according to the invention with
  • FIG. 3 is a perspective view of an outer part according to the invention.
  • FIG. 4 is a perspective view of a shaft coupling according to the invention (without representation of the hub),
  • FIG. 5 perspective view of a roller body according to the invention in one embodiment.
  • Figure 1 shows a perspective view of an outer part 16 of a shaft coupling according to the invention, with roller bodies 20, 21 and elastically deformable elements 22 arranged therein in one embodiment.
  • the outer part 16 has a plurality of chambers 18 in which the roller bodies 20, 21 and the elastically deformable elements 22 are arranged.
  • the chambers 18 are arranged one behind the other in the circumferential direction.
  • the roller bodies 20, 21 are preferably elastically deformable and advantageously consist of a rubber material.
  • a part of the roller body 20 shown in Figure 1 has a spherical shape.
  • the roller bodies 20 do not completely fill the corresponding chambers 18, so that in the case of deformation, the rubber material can in each case escape into the free spaces within the chamber 18.
  • the other roller bodies 21 shown in FIG. 1 have a substantially purely cylindrical shape.
  • the elastically deformable element 22 is preferably made of an elastic material. Furthermore, the elastically deformable element 22 is plate-shaped. It extends in the radial direction of the coupling 10. The elastically deformable element 22 is fastened to the outer part 16. For this purpose, the Outer part 16 grooves 26. By such a configuration, a fixed arrangement of the elastically deformable element 22 is ensured in the shaft coupling 10 and in the outer part 16, wherein it can bend elastically between the end-side brackets.
  • only in every second chamber 18 is an elastically deformable element 22. In the chambers 18 with elastically deformable elements 22 also each a ball-shaped roller body 20 is arranged.
  • FIG. 2 shows a perspective view of the hub 12 according to the invention with roller bodies 20, 21 and elastically deformable elements 22.
  • the hub 12 has a plurality of cams 14, 15 extending in the axial direction of the coupling 10.
  • the cams 14, 15 are arranged circumferentially spaced from each other.
  • the cams 14, 15 engage in the assembled state of the clutch axially into the chambers 18 on the outer part 16 according to Figure 1, in each case in the space between the roller body 20, 21 and elastic element 22, a.
  • the cams 14, 15 are not all the same. While a portion of the cam 14 is solid, the other part of the cam 15 has recesses 24.
  • the cams 14, 15 are arranged at different angular intervals (a, ß) on the hub 12.
  • the distance of a cam 15 to a neighboring cam 14 on one side is greater ( ⁇ ) than the distance to a neighboring cam 14 on the other side (a).
  • some of the cams 15 may abut one of the roller bodies 20 with one of its circumferentially facing surfaces and one of the elastically deformable members 22 with the other circumferentially facing surface.
  • the elastically deformable element 22 is advantageously arranged so that it also engages the cam 15 in a non-rotating state the clutch 10 presses against the roller body 20.
  • the cams 15 preferably engage under prestress against the adjacent roller bodies 20.
  • the coupling according to FIG. 2 is preferably designed so that there is a free space 28 in a non-rotating state between at least one cam 14 and an adjacent roller body 21. This makes it possible that the cam 14 engages only after a certain angle of rotation of the roller body 20.
  • FIG. 3 shows a perspective view of the outer part 16 according to the invention.
  • the outer part 16 is designed such that it delimits the chambers 18 in an axial direction.
  • the outer part 16 is formed substantially circular.
  • the rear wall of the circular ring 42 abuts the roller bodies 20, 21 and the elastically deformable elements 22 in the axial direction and guides or holds them in the axial direction.
  • the outer part 16 may be a cast or milled part, wherein the chambers 18 are formed therein as a kind open as troughs.
  • the outer part 16 has two substantially cylindrical portions 44, 46, which are arranged coaxially with each other.
  • the inner portion 46 forms the inner boundary of the chambers 18 and the outer portion 44, the outer boundary.
  • the sections 44, 46 can also be designed so that the chambers are tapered. As a result, the progressive characteristic of the clutch can be further adjusted. At least one portion 44, 46 may have a conical shape.
  • the sections 44, 46 have a plurality of grooves 26 for receiving the elastically deformable elements 22. Preferably, a groove 26 is assigned to the outer portion of exactly one groove on the inner portion.
  • the chambers 18 also have lateral boundaries. The lateral boundaries are also formed by the outer part 18, by extending in the radial direction of the coupling webs 48 which connect the cylindrical portions 44, 46 with each other. The flanks of the webs 48 facing the chambers in turn engage the roller bodies 20, 21 for torque transmission.
  • FIG 4 shows a perspective view of the shaft coupling 10 according to the invention omitting the hub 12 for the purpose of better visibility.
  • the shaft coupling 10 has a cover 30, which is formed so that it limits the chambers 18 in an axial direction at least partially.
  • the cover 30 ensures that the reel body 20, 21 and the elastic members 22 can not fall out of the chambers 18 in the axial direction and remain safe in these during the use of the clutch 10.
  • the cover 30 is formed substantially as a circular ring and has inwardly 32 and outwardly 34 projecting holding portions.
  • the inner holding portions 32 are dimensioned so that they prevent falling out of the roller body 20, 21 and the elastic members 22 from the chambers 18.
  • each chamber 18 is assigned exactly one inner holding section 32.
  • the cover 30 can be connected to the outer part 16. For this purpose, it has holes 36 for screws, which correspond with corresponding holes 38 in the outer part 16.
  • FIG. 5 shows a perspective view of a roller body 40 according to the invention in one embodiment.
  • the reel body 40 has two lips 50 ', 50 ".
  • the lips 50', 50" extend from an end face of the reel body 40 in the axial direction of the reel body, extending substantially along the circumference of the reel body 40.
  • the lips 50 ', 50 If the roller body is subjected to pressure during operation, then the lip does not prevent the axial expansion of the roller body.
  • roller body (cylindrical shape)

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un accouplement torsio-élastique d'arbres (10) comprenant un moyeu (12) pourvu de cames (14, 15) s'étendant dans la direction axiale, une partie axiale (16), qui est agencée de manière concentrique par rapport au moyeu (12) et qui peut être amenée en rotation par rapport à celui-ci, une pluralité de chambres (18), une pluralité de corps de rouleau (20, 21, 40), qui sont agencés dans les chambres (18), et une pluralité d'éléments (22) déformables élastiquement, qui sont agencés également dans les chambres (18). Les cames (14, 15), les corps de rouleau (20, 21, 40) et les éléments (22) déformables élastiquement sont agencés le long d'un arc de cercle.
PCT/EP2017/065093 2016-06-20 2017-06-20 Accouplement torsio-élastique d'arbres WO2017220582A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016111272.0 2016-06-20
DE102016111272.0A DE102016111272B4 (de) 2016-06-20 2016-06-20 Drehelastische Wellenkupplung

Publications (1)

Publication Number Publication Date
WO2017220582A1 true WO2017220582A1 (fr) 2017-12-28

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Application Number Title Priority Date Filing Date
PCT/EP2017/065093 WO2017220582A1 (fr) 2016-06-20 2017-06-20 Accouplement torsio-élastique d'arbres

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DE (1) DE102016111272B4 (fr)
WO (1) WO2017220582A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB802400A (en) * 1955-12-16 1958-10-01 Croset Louis Paul Improvements in or relating to flexible couplings, dampers, gearwheels, and like devices
EP0626523A1 (fr) * 1993-03-26 1994-11-30 CENTA-ANTRIEBE KIRSCHEY GmbH Accouplement élastique étagé à deux niveaux
DE19613277A1 (de) * 1995-11-21 1997-05-22 Hackforth Gmbh & Co Kg Drehelastische Wellenkupplung
DE102008005257B4 (de) 2008-01-18 2013-06-13 Centa-Antriebe Kirschey Gmbh Drehelastische Wellenkupplung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2505651A1 (de) * 1975-02-11 1976-08-19 Johann Hochreuter Elastische wellenkupplung
DE3621072A1 (de) * 1986-06-24 1988-01-07 Ilie Chivari Elastische kupplung
DE9304497U1 (de) * 1993-03-26 1993-05-13 Centa-Antriebe Kirschey GmbH, 5657 Haan Wellenkupplung
DE102015201403B4 (de) * 2015-01-28 2017-06-22 Schaeffler Technologies AG & Co. KG Rücklaufsperre und Verteilergetriebe mit einer solchen Rücklaufsperre

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB802400A (en) * 1955-12-16 1958-10-01 Croset Louis Paul Improvements in or relating to flexible couplings, dampers, gearwheels, and like devices
EP0626523A1 (fr) * 1993-03-26 1994-11-30 CENTA-ANTRIEBE KIRSCHEY GmbH Accouplement élastique étagé à deux niveaux
DE19613277A1 (de) * 1995-11-21 1997-05-22 Hackforth Gmbh & Co Kg Drehelastische Wellenkupplung
DE102008005257B4 (de) 2008-01-18 2013-06-13 Centa-Antriebe Kirschey Gmbh Drehelastische Wellenkupplung

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Publication number Publication date
DE102016111272A1 (de) 2017-12-21
DE102016111272B4 (de) 2021-12-23

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