CA2293757A1 - Compensating coupling - Google Patents
Compensating coupling Download PDFInfo
- Publication number
- CA2293757A1 CA2293757A1 CA002293757A CA2293757A CA2293757A1 CA 2293757 A1 CA2293757 A1 CA 2293757A1 CA 002293757 A CA002293757 A CA 002293757A CA 2293757 A CA2293757 A CA 2293757A CA 2293757 A1 CA2293757 A1 CA 2293757A1
- Authority
- CA
- Canada
- Prior art keywords
- coupling
- spring
- compensating
- torque
- elements
- 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.)
- Abandoned
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
- F16D3/56—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 metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
Abstract
The invention relates to a compensating coupling transmitting torque in order to compensate for imprecise alignments in machine elements that are to be joined. One disadvantage with prior art is that these couplings are relatively complicated to produce and that the service life of the spring elements used is limited. The spring element in the inventive coupling is characterised in that recesses (7, 8, 11) and threaded holes (10, 12) are provided on the periphery of the flange of the two half-couplings (1, 2) so that the radially rigid springs (9) that are used as connecting elements or other rigid spring elements inserted in the direction of the periphery fit exactly into the recesses or threaded holes in order to transmit the appropriate torque and to compensate for axial and radial alignment errors. The spring (9) that transmits torque is designed in such a way that it compensates for misalignment of shafts and transmits high amounts of torque. The spring (9) also possesses a long service life as a connecting and transmitting element.
Description
1120-002.tr1 Description COMPENSATING COUPLING
The invention relates to a compensating coupling for transferring torque for compensating alignment errors of connected machine elements.
Elastic couplings, such as shaft couplers are known in which one half of the coupling is connected to a stay rod on the free ends of which there are rubber cases applied elastic intermediate members which range into correspond-ingly enlarged bores of the second coupling part. When the stay rod is tightened, a cap screw retains the rubber case at a certain prestressed condition.
Also angularly movable and axially yielding strap type couplings are known for two shaft endings from German patent No. 19,515,101 in which at least three circumferentially distributed straps serve to transfer the torque, which are attached to the ends of the shafts through circumferentially adjacent screw shafts, and connect these in a relatively tiltable manner, whereby the straps connect the screw shafts at unalterable circumferential spacings. The straps are provided with at least one elastic projection which projects radially inwardly, contacting the threaded bolt, for compensating for inaccuracies during assembly.
From German published patent application No. 19,614,267 there is an elastic, axially and angularly movable coupling known for connecting two rotating machine parts with at least one elastic coupling part and at least one firmly rotating coupling part made entirely from steel. In this coupling a machine part is rotatably directed on the elastic coupling part and in a nonbendable manner radially with respect to its rotational axis, while the nonbending coupling part is always axially and angularly movably connected to the elastic coupling part and the other part of the machine.
Apart from the fact that in the case of strap-type couplings each individual spring assembly has a given spring path length, the number of strap assemblies that are distributed on the periphery are limited, because otherwise the required number of individual parts and also the diameter would be unduly increased. This is a disadvantage in the case of the described embodiments with respect to the production requirements and a good durability of use.
It is an objective of the invention to provide a compensating coupling by the use of a larger number of springs distributed about the priphery of the coupling and by an improvement of the spring elements, which will have a greater useful life and a proportional torque notwithstanding any equalization of axial and radial alignment inaccuracies.
These objectives of the invention are solved through an embodiment of the characteristics of claim 1. Further advantageous features can be found in the subclaims. The compensating coupling of the invention has the advantage over the prior art that in spite of compensation of an instantaneous shaft displace-ment in an axial, lateral, and angular direction by employing and arranging of the various slits in the spring, not only high torque can be transferred, but at the same time a long term durability of the of the springs that serve as connecting and transferring elements, is achieved. Also the springs can be produced not only in an economical manner and also enables a long term durability which can be achieved with springs formed as connecting and transferring elements. The spring elements can also be produced from high value steel in greater numbers and can be obtained as predetermined construction series or smaller sizes with a high variance within the instantaneous torque ranges of the coupling. The installation and uninstallation as well as repair of the coupling with the spring of the inven-tion as a connecting element can be simply and quickly accomplished. Through the hollow parts and recesses created in the flanges and the springs mounted and protected therein, the immediately adjacent areas are protected against any flying parts even in the case of a fracture. Due to the predictable fitting accuracy even a burst spring transmits torque and thus contributes to the emergency running properties of the coupling. The loading of the individual springs is small due to the radial stiffness of the individual springs and the possibility of using a greater number of springs, so that spring breakage can hardly occur.
An exemplary embodiment of the invention is shown in the drawing and in the following description, wherein:
Fig. 1 shows a plan view of a side of the compensating coupling;
Fig. 2 shows a side view of Fig. 1 in cross-section;
Fig. 3 shows a side view of the spring;
Fig. 4 shows a plan view of the spring of Fig. 3 in cross-section;
Fig. 5 shows a plan view of the spring according to Figs. 3 and 4.
The compensating coupling of Figs. 1 and 2 has two coupling halves 1, 2 formed as axle flanges. The carrier dog parts 3, 4 are provided with for example with different bores 5, 6 for acceptance of different shafts. Recesses 7, 8 are distributed at regular distances on the front face of the coupling half 1 analogous-ly to the spring 9 to be installed therein. The recesses 7, 8 have centrally a threaded bore 10. Also the front face of the flange of the coupling half 2 is correspondingly provided with recesses 8 as well as additiona'~ recesses 11.
The back side of the flange of the coupling half 2 have threaded bores 12 with a somewhat larger diameter as the recesses 11.
As shown in Figs. 3-5, the springs 9 that are to be mounted in and between the coupling halves 1, 2, as compensating and connecting elements, are cylindrical, and have varying diameters. Thus the central parts of the springs with their external diameter 13 are applied during assembly exactly on the recesses of both coupling halves l, 2, while the applied combined collar 14 ranges into the flange of the coupling half 1 and the larger diameter collar 15 with its abutting surface 16 works with the additional recesses 11 in the coupling half 2.
S For achievement of the compensating effect the spring 9 is formed so that it is of a cylindrical tubular body in that at least two opposed spring elements 18 are created across its longitudinal axis 17, the elements containing four mutually opposed slots 19. The slots in one half of the tubular body are disposed so that the instantaneoulsly outer slots 19 cover the upper half, and the two inner slots 19 cover the lower half, to increase flexibility, and thus to equalize each shaft displacement in axial, lateral and angular directions. The installation takes place exactly in an opposite manner in the opposed halves of the tubular body, so that a sufficient radial stiffness remains in each opposed spring element 18.
Connecting webbings 21 are opened through the overlaps created of the lateral slots 19 in the circumferential direction, and the creation of of axial cross-slots 20 on the fronts of the springs 9 so that there is a Z-shaped connection through the complete ring-shaped connecting ring 22. The connecting ring that presents a respective possibility for adding opposed spring elements 18, is so thin also to serve as an axial spring element in the total spring structure. Installation of the spring 9 can take place, for example, by inseerting the collar 14 of the spring 9 through the recesses 7 of the flange of the coupling half 1, and screwing it into the threaded bore 10 through the a bore 24 of the collar 14 with its abutment surface 25, with a cylindrical-, or hexagonal socket screw 23, wherein the com-bined collar 14 is taken up through the recesses 7 of the flange of the coupling half 1. The spring 9 is also placed into the recesses 8 in the flange of the coupling half 2 and pressed by the larger diameter collar 15 into the recesses 11, an secured by an outer threaded nut 26 wityh inner hexagonal socket, through the threaded bore 12 in the rear of the flange of the coupling half 2.
The invention relates to a compensating coupling for transferring torque for compensating alignment errors of connected machine elements.
Elastic couplings, such as shaft couplers are known in which one half of the coupling is connected to a stay rod on the free ends of which there are rubber cases applied elastic intermediate members which range into correspond-ingly enlarged bores of the second coupling part. When the stay rod is tightened, a cap screw retains the rubber case at a certain prestressed condition.
Also angularly movable and axially yielding strap type couplings are known for two shaft endings from German patent No. 19,515,101 in which at least three circumferentially distributed straps serve to transfer the torque, which are attached to the ends of the shafts through circumferentially adjacent screw shafts, and connect these in a relatively tiltable manner, whereby the straps connect the screw shafts at unalterable circumferential spacings. The straps are provided with at least one elastic projection which projects radially inwardly, contacting the threaded bolt, for compensating for inaccuracies during assembly.
From German published patent application No. 19,614,267 there is an elastic, axially and angularly movable coupling known for connecting two rotating machine parts with at least one elastic coupling part and at least one firmly rotating coupling part made entirely from steel. In this coupling a machine part is rotatably directed on the elastic coupling part and in a nonbendable manner radially with respect to its rotational axis, while the nonbending coupling part is always axially and angularly movably connected to the elastic coupling part and the other part of the machine.
Apart from the fact that in the case of strap-type couplings each individual spring assembly has a given spring path length, the number of strap assemblies that are distributed on the periphery are limited, because otherwise the required number of individual parts and also the diameter would be unduly increased. This is a disadvantage in the case of the described embodiments with respect to the production requirements and a good durability of use.
It is an objective of the invention to provide a compensating coupling by the use of a larger number of springs distributed about the priphery of the coupling and by an improvement of the spring elements, which will have a greater useful life and a proportional torque notwithstanding any equalization of axial and radial alignment inaccuracies.
These objectives of the invention are solved through an embodiment of the characteristics of claim 1. Further advantageous features can be found in the subclaims. The compensating coupling of the invention has the advantage over the prior art that in spite of compensation of an instantaneous shaft displace-ment in an axial, lateral, and angular direction by employing and arranging of the various slits in the spring, not only high torque can be transferred, but at the same time a long term durability of the of the springs that serve as connecting and transferring elements, is achieved. Also the springs can be produced not only in an economical manner and also enables a long term durability which can be achieved with springs formed as connecting and transferring elements. The spring elements can also be produced from high value steel in greater numbers and can be obtained as predetermined construction series or smaller sizes with a high variance within the instantaneous torque ranges of the coupling. The installation and uninstallation as well as repair of the coupling with the spring of the inven-tion as a connecting element can be simply and quickly accomplished. Through the hollow parts and recesses created in the flanges and the springs mounted and protected therein, the immediately adjacent areas are protected against any flying parts even in the case of a fracture. Due to the predictable fitting accuracy even a burst spring transmits torque and thus contributes to the emergency running properties of the coupling. The loading of the individual springs is small due to the radial stiffness of the individual springs and the possibility of using a greater number of springs, so that spring breakage can hardly occur.
An exemplary embodiment of the invention is shown in the drawing and in the following description, wherein:
Fig. 1 shows a plan view of a side of the compensating coupling;
Fig. 2 shows a side view of Fig. 1 in cross-section;
Fig. 3 shows a side view of the spring;
Fig. 4 shows a plan view of the spring of Fig. 3 in cross-section;
Fig. 5 shows a plan view of the spring according to Figs. 3 and 4.
The compensating coupling of Figs. 1 and 2 has two coupling halves 1, 2 formed as axle flanges. The carrier dog parts 3, 4 are provided with for example with different bores 5, 6 for acceptance of different shafts. Recesses 7, 8 are distributed at regular distances on the front face of the coupling half 1 analogous-ly to the spring 9 to be installed therein. The recesses 7, 8 have centrally a threaded bore 10. Also the front face of the flange of the coupling half 2 is correspondingly provided with recesses 8 as well as additiona'~ recesses 11.
The back side of the flange of the coupling half 2 have threaded bores 12 with a somewhat larger diameter as the recesses 11.
As shown in Figs. 3-5, the springs 9 that are to be mounted in and between the coupling halves 1, 2, as compensating and connecting elements, are cylindrical, and have varying diameters. Thus the central parts of the springs with their external diameter 13 are applied during assembly exactly on the recesses of both coupling halves l, 2, while the applied combined collar 14 ranges into the flange of the coupling half 1 and the larger diameter collar 15 with its abutting surface 16 works with the additional recesses 11 in the coupling half 2.
S For achievement of the compensating effect the spring 9 is formed so that it is of a cylindrical tubular body in that at least two opposed spring elements 18 are created across its longitudinal axis 17, the elements containing four mutually opposed slots 19. The slots in one half of the tubular body are disposed so that the instantaneoulsly outer slots 19 cover the upper half, and the two inner slots 19 cover the lower half, to increase flexibility, and thus to equalize each shaft displacement in axial, lateral and angular directions. The installation takes place exactly in an opposite manner in the opposed halves of the tubular body, so that a sufficient radial stiffness remains in each opposed spring element 18.
Connecting webbings 21 are opened through the overlaps created of the lateral slots 19 in the circumferential direction, and the creation of of axial cross-slots 20 on the fronts of the springs 9 so that there is a Z-shaped connection through the complete ring-shaped connecting ring 22. The connecting ring that presents a respective possibility for adding opposed spring elements 18, is so thin also to serve as an axial spring element in the total spring structure. Installation of the spring 9 can take place, for example, by inseerting the collar 14 of the spring 9 through the recesses 7 of the flange of the coupling half 1, and screwing it into the threaded bore 10 through the a bore 24 of the collar 14 with its abutment surface 25, with a cylindrical-, or hexagonal socket screw 23, wherein the com-bined collar 14 is taken up through the recesses 7 of the flange of the coupling half 1. The spring 9 is also placed into the recesses 8 in the flange of the coupling half 2 and pressed by the larger diameter collar 15 into the recesses 11, an secured by an outer threaded nut 26 wityh inner hexagonal socket, through the threaded bore 12 in the rear of the flange of the coupling half 2.
Claims (4)
1. Compensating coupling for transferring of torque for compensating alignment of inaccuracies of machine elements to be connected to each other by use of an elastic connecting element, characterized in that recesses and threaded bores are provided on the diameters of the flanges of coupling halves so that radially stiff springs are disposed in each of them which also serve either at the same time as connecting elements, or other, stiff spring elements accurately inserted into the circumferential direction for transferring appropriate torque and for compensating axial and radial alignment errors.
2. Compensating coupling according to claim 1, characterized in that a spring of a cylindrical tubular body has on its front and rear surface collars of differing diameters for attaching in the flanges of the coupling halves, and is so formed for obtaining the compensating effect that it has at least two opposed spring elements across its longitudinal axis, formed from four opposed slots wherein each otf the two outer slots, for example in the upper half, and the two inner slots in the lower half or respectively in the opposed half analogously, but in reverse, cover each other.
3. Compensating coupling according to claims 1 and 2, characterized in that in addition to the covering side slots, also cross slots are provided in the circumferential direction on the front faces of the springs to the extent that the resulting connecting webbings are so open that a Z-shaped connection results through the completely ring shaped connecting ring, providing at the same time the possibility to add further spring elements.
4. Compensating coupling according to the foregoing claims, characterized in that the spring serves at the same time as a firm connecting element in the assembly of the compensating coupling, in that the attachment of the coupling half takes place for example through hexagonal socket screws and the securing of the coupling half for example with outer threaded nuts with inner sockets.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19812527.5 | 1998-03-21 | ||
| DE1998112527 DE19812527C2 (en) | 1998-03-21 | 1998-03-21 | Differential coupling |
| PCT/DE1999/000887 WO1999047826A1 (en) | 1998-03-21 | 1999-03-18 | Compensating coupling |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2293757A1 true CA2293757A1 (en) | 1999-09-23 |
Family
ID=7861861
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002293757A Abandoned CA2293757A1 (en) | 1998-03-21 | 1999-03-18 | Compensating coupling |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0988460A1 (en) |
| CA (1) | CA2293757A1 (en) |
| DE (1) | DE19812527C2 (en) |
| WO (1) | WO1999047826A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104565100A (en) * | 2015-01-07 | 2015-04-29 | 丹东克隆先锋泵业有限公司 | Metal corrugated pipe pin type coupling |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111911545A (en) * | 2019-05-27 | 2020-11-10 | 中车大同电力机车有限公司 | Transmission mechanism and drive coupling |
| WO2024003861A1 (en) * | 2022-07-01 | 2024-01-04 | 3Dific Societa' A Responsabilita' Limitata | Flexible joint |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1586250A (en) * | 1924-08-23 | 1926-05-25 | Frank L Schwarz Jr | Shaft coupling |
| US1700102A (en) * | 1925-09-18 | 1929-01-22 | Smith & Serrell | Bushed flexible coupling |
| FR722512A (en) * | 1931-09-07 | 1932-03-17 | Elastic coupling | |
| GB416177A (en) * | 1933-08-16 | 1934-09-13 | Uskside Engineering Company Lt | Improvements in or relating to flexible couplings |
| FR1244152A (en) * | 1958-12-31 | 1960-10-21 | Atomatic Mfg Company | Coupling |
| US3042391A (en) * | 1959-09-25 | 1962-07-03 | Garrett Corp | Compression spring |
| JPS5940017A (en) * | 1982-08-27 | 1984-03-05 | Toshiba Corp | Small-size precision coupling |
| DE19515101C1 (en) * | 1995-04-25 | 1996-07-25 | Freudenberg Carl Fa | Mechanical coupling for abutting shaft ends of vehicle drive train |
| DE19614267A1 (en) * | 1996-04-11 | 1997-10-16 | Atec Weiss Gmbh & Co Kg | Elastic, axially and angularly movable coupling |
| DE29805165U1 (en) * | 1998-03-21 | 1998-07-23 | Zahnradwerk Pritzwalk Gmbh | Differential coupling |
-
1998
- 1998-03-21 DE DE1998112527 patent/DE19812527C2/en not_active Expired - Fee Related
-
1999
- 1999-03-18 CA CA002293757A patent/CA2293757A1/en not_active Abandoned
- 1999-03-18 WO PCT/DE1999/000887 patent/WO1999047826A1/en not_active Application Discontinuation
- 1999-03-18 EP EP99923398A patent/EP0988460A1/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104565100A (en) * | 2015-01-07 | 2015-04-29 | 丹东克隆先锋泵业有限公司 | Metal corrugated pipe pin type coupling |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19812527A1 (en) | 1999-09-30 |
| EP0988460A1 (en) | 2000-03-29 |
| DE19812527C2 (en) | 2000-04-27 |
| WO1999047826A1 (en) | 1999-09-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued | ||
| FZDE | Discontinued |
Effective date: 20020318 |