WO1993023684A1 - Kupplung zum kuppeln umlaufender teile - Google Patents
Kupplung zum kuppeln umlaufender teile Download PDFInfo
- Publication number
- WO1993023684A1 WO1993023684A1 PCT/EP1993/001260 EP9301260W WO9323684A1 WO 1993023684 A1 WO1993023684 A1 WO 1993023684A1 EP 9301260 W EP9301260 W EP 9301260W WO 9323684 A1 WO9323684 A1 WO 9323684A1
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- WO
- WIPO (PCT)
- Prior art keywords
- coupling
- intermediate member
- members
- coupling according
- bearing
- Prior art date
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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
- F16D3/60—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 pushing or pulling links attached to both parts
Definitions
- the invention relates to a clutch for coupling rotating parts containing a drive-side coupling half with three radial arms, an output-side coupling half with three radial arms, three mutually concentric, rotatably mounted coupling intermediate members, each having a handlebar with the drive-side coupling half and a further link are connected to the coupling half on the output side.
- Such couplings are known for example from US-A-4,040,270.
- the intermediate coupling members are rings which are mounted concentrically on one another.
- the bearings are mounted on roller bearings.
- plain bearings are provided. These plain bearings consist of a layer of oil-soaked brake pad material.
- EP-A-0 389 647 also describes a clutch of the present type, in which the three rings are mounted on one another via plain bearings.
- Usual rolling bearings are complex. They require high precision. The radial dimensions of the coupling are increased by the races of the roller bearings. This can be critical if, on the one hand, only a limited space is available for the clutch and, on the other hand, a predetermined torque has to be transmitted.
- the plain bearings used in US-A-4,040,270 also require a relatively large amount of space in the radial direction. They have an undesirably high coefficient of friction. This can lead to wear and heat development. Such couplings are poorly suited for applications in which the couplings are supposed to work maintenance-free for a long time. Such applications arise particularly in rail drives.
- the invention has for its object to form a coupling of the type mentioned simple and inexpensive so that it can work maintenance-free for a long time.
- the radial dimensions of the clutch should be as small as possible for a given torque to be transmitted.
- this object is achieved in that the intermediate coupling members are supported on one another by a sliding bearing between steel and a sliding metal.
- Fig.l shows for a clutch of the present type a longitudinal section through the handlebar bearing provided on the drive-side coupling half.
- Fig.2 shows a section A - B of Fig.l.
- Fig. 3 shows a representation similar to Fig.l a modified version of the clutch, in which the plain bearings are constructed with hardened spring steel strips.
- Fig.4 shows a section along the line G - H of Fig.3.
- FIG. 5 shows a longitudinal section of an embodiment in which a second and a third intermediate coupling member are mounted coaxially next to one another on a first intermediate coupling member.
- FIG. 6 shows a longitudinal section of a further embodiment of a coupling for coupling rotating parts.
- FIG. 7 shows an associated cross section similar to FIG. 4.
- 10 is a coupling half on the drive side and 12 on the output side
- the coupling half on the drive side 10 has three radial arms 18 which are angularly offset from one another by 120 °.
- the output-side coupling half 12 also has three radial arms 20 which are angularly offset from one another by 120 °.
- the intermediate coupling members 22, 24 and 26 are arranged concentrically to one another and rotatably supported on one another.
- Each of the coupling links has two diametrically opposed radial arms.
- Fig.l one of the two radial arms 28 of the outermost coupling intermediate member 22 is indicated.
- one of the radial arms 30 of the middle coupling intermediate member 24 is shown in section.
- One of the arms of the intermediate coupling members 22, 24 and 26 is connected to an arm 18 of the drive-side coupling half 10 via a link.
- the respective other arm of each coupling half is connected via a link 34 to an arm 20 of the coupling half 12 on the output side.
- the common axis of the coupling intermediate members 22, 24 and 26 is also aligned with the axes of the coupling halves 10 and 12.
- the radial arms 20 of the output-side coupling half 12 are at 60 ° angularly offset against the arms 18 of the drive-side coupling half 10.
- the arms 28, 30 and 32 of the intermediate coupling members 22, 24 and 26 are each offset by 30 ° relative to that arm of a coupling half 10 or 12 with which the arm of the intermediate coupling member is connected via a link.
- housing-like axial projections 38 are formed on the radial arms 18 and 20 of the coupling halves.
- the lugs 38 have axial openings 40. This is described below in detail on the arm 18 of the drive-side coupling half 10 on the left in FIG.
- the opening 40 has a section 42 which opens at the end facing the clutch half on the output side.
- a shoulder 44 is formed in the opening 40 on the inside of the section 42.
- An extension 46 adjoins the shoulder 44.
- the extension 46 is connected to a section 48 of the opening 40, which extends to the end face of the coupling half 12 on the output side.
- a lateral slot 50 is provided in the lateral surface of the housing-like extension 38.
- the slot 50 starts from the extension 46 and extends essentially in the circumferential direction of the coupling. As will be explained later, part of the handlebar projects through this slot 50.
- the slot 50 is so wide that the handlebar can perform its pivoting movement which occurs when the axis is offset.
- Bearing means 52 are seated in section 42 of opening 40.
- Bearing means 52 are formed by a rubber bearing.
- the bearing means contain a jacket-shaped rubber body 54.
- a metal sleeve 56 is vulcanized onto the outer surface of the rubber body 54.
- a metal sleeve 58 is vulcanized into the inner surface of the rubber body 54.
- the metal sleeve 56 is firmly seated in the section 42 of the opening 40.
- the inner metal sleeve 58 is firmly attached to a pin body 60.
- the pin body 60 forms part of the link 34.
- the pin body 60 forms a collar 62.
- the metal sleeve 56 bears against this collar on the right-hand side in FIG. Following the collar 62, the pin body 60 forms a first pin 64 of reduced diameter.
- the pin 64 has an inner, smooth portion 66 'adjoining the collar 62 and an adjoining, threaded outer portion 68.
- a first tab 70 sits on the portion 66 and forms part of the link 34.
- a nut 72 is screwed onto the outer section 68, through which the tab 70 is tightened against the collar 62.
- a second pin 74 of reduced diameter is provided on the pin body 60.
- the pin 74 also has a smooth inner section 76 and an outer threaded section 78.
- the pin body forms a shoulder 80 between the middle part connected to the metal sleeve 58 and the inner section 78 of the second pin 74.
- a tab 82 sits on the inner section, which also forms part of the link 34. The tab 82 is tightened against the shoulder 80 by a nut 84 seated on the outer portion 78.
- the arm 30 forms an eye 86 with a straight, cylindrical bore 88.
- Bearing means 90 are seated in the bore 88.
- the bearing means 90 are formed, like the bearing means 52, by a rubber bearing.
- the rubber bearing contains a jacket-shaped rubber body 92, similar to the rubber body 54 in Fig.l.
- a metal sleeve 100 is vulcanized onto the cylindrical outer surface of the rubber body 92.
- a metal sleeve 102 is vulcanized into the likewise cylindrical inner surface of the rubber body 92.
- the metal sleeve 100 is seated firmly in the bore 88 of the eye 86.
- the metal sleeve 100 is fastened on a pin body 104 which forms part of the link 34.
- the pin body 104 forms similar to the pin body 60 on the left side in Fig.l. a collar 106.
- the end face of the metal sleeve 102 bears against the collar.
- the pin body 104 has a central axial bore 108.
- a threaded bolt 110 extends through the central bore 108.
- a link 112 of the handlebar is clamped between the head of the threaded bolt 110 and the end face of the pin body 104.
- end face of the pin body 104 is a second tab 114 of the handlebar.
- the tab 114 has a threaded bore into which the threaded end of the threaded bolt engages.
- the handlebars are elastically pivotable via rubber bearings on the one hand to an arm 18 of the drive-side coupling half or an arm 20 of the output-side coupling half 12 and on the other hand to an arm 28, 30 or 32 of a coupling intermediate member 22, 24 or 26.
- the links 34 can move about the axes of the rubber bodies, i.e. swivel in the paper plane of Fig. 2.
- the handlebars can also be pivoted out of this plane of paper to a limited extent and thus compensate for an angular or axial offset of the coupling halves 10 and 12 against one another.
- the bearing means in the arms of the coupling halves and the intermediate coupling members can of course also be designed to match, that is to say both bearing means in the manner of the bearing means 52 or both bearing means in the manner of the bearing means 90.
- the three coupling members 22, 24 and 26 are formed by three rings, the cross sections of which have an elongated rectangular basic shape.
- the three rings are rotatably mounted on each other coaxially.
- the middle ring 24 is made of steel with a hardened, cylindrical outer surface 112 and a likewise hardened, cylindrical inner surface 114.
- the outermost coupling intermediate member 22 is made as a casting.
- the outermost coupling intermediate member 22 is supported with a cylindrical inner surface 116 on the outer surface 112 of the middle coupling intermediate member 24.
- the cast iron bearing on hardened steel is very low in friction and wear. Suitable means, which are described in more detail below in connection with FIG. 2, provide for lubrication of the bearing from a lubricant reservoir.
- the innermost coupling intermediate member 26 is made as a casting.
- the innermost coupling intermediate member has a cylindrical outer surface 118.
- the middle coupling intermediate member 24 is supported with its hardened inner surface 114 on the outer surface 118 of the innermost coupling intermediate member. Lubrication of this bearing from the lubricant reservoir is also ensured here.
- the inner surface 116 of the outermost coupling intermediate member 22 is stepped.
- the inner surface 116 has a central part 120 of smaller diameter. This middle part 120 thus projects inwards.
- Edge parts 122 and 124 adjoin the central part 120 on both sides.
- Ring shoulders 126 and 128 are formed between the central part 120 and the edge parts 122 and 124.
- the middle coupling intermediate member 24 is formed with its outer surface 112 substantially complementary to the inner surface of the outermost coupling intermediate member 22.
- the outer surface 112 has a central part 130 of smaller diameter and edge parts 132 and 134 on both sides of the central part 130. Radial ring surfaces 136 and 138 are formed between the central part 130 and the edge parts 132 and 134.
- the middle part 130 and the ring surfaces 136 and 138 form a wide groove in the outer surface 112 of the middle coupling intermediate member 24.
- the outermost coupling intermediate member 22 and the middle coupling intermediate member 24 are rotatably supported on one another via the middle parts 120 and 130. Due to the shoulders 126 and 128 of the outermost coupling intermediate member 22 and the cooperating annular surfaces 136 and 138 of the middle coupling intermediate member 24, the two are Coupling intermediate members 22 and 24 guided to one another in the axial direction. Axial forces which act on the coupling are absorbed by the shoulders 126, 128 and the annular surfaces 136, 138.
- gaps between the ring shoulders 126, 128 and the ring surfaces 136, 138 are also supplied with lubricant from the lubricant reservoir. Gaps are formed between the edge parts 122, 124 of the outermost coupling intermediate member 22 and the edge parts 132, 134 of the central coupling intermediate member. These gaps are sealed by sealing rings 140 and 142.
- the inner surface 114 of the middle coupling intermediate member has a central part 144 with a smaller diameter and adjoining it on both sides edge parts 146 and 148. Ring shoulders 150 and 152 are formed between the central part 144 and the edge parts 146 and 148.
- the inner surface 114 forms with the central part 144 an inwardly projecting strip.
- the outer surface 118 of the innermost coupling intermediate member 26 is substantially complementary to the inner surface 114 of the central coupling intermediate member 22.
- the outer surface 118 has a cylindrical central portion 154 of enlarged diameter. Edge parts 156 and 158 of smaller diameter adjoin the middle part 154. Ring surfaces 160 and 162 are formed between the middle part 154 and the edge parts.
- the middle part 154 and the ring surfaces 160 and 162 form a wide groove into which the strip formed by the middle part 144 and the ring shoulders 150 and 152 receives.
- the middle coupling intermediate member 24 is rotatably supported on the innermost coupling intermediate member 26 via the middle parts 144 and 154.
- the intermediate coupling members 24 and 26 are axially guided to one another by the annular shoulders 150, 152 and the annular surfaces 160 and 162 cooperating therewith. This guide absorbs axial forces. Gaps are formed between the edge parts 132, 134 and the edge parts 146, 148. These gaps are sealed by sealing rings 164 and 166, respectively. To enable assembly, these are middle coupling intermediate member 24 and innermost coupling intermediate member 26 as shown, the two parts being connected by screws.
- the bearing means 52 in the drive-side and output-side coupling halves are symmetrical about a radial central plane 168.
- the bearing means 90 are also arranged symmetrically about this central plane 168 in the arms of the coupling intermediate members 22, 24 and 26.
- the bearing surfaces of the rings are also symmetrical to the central plane 168.
- the coupling halves 10 and 12 safely absorb the centrifugal forces acting on the link 34 with the housing-like approaches. The same applies to the eyes 88 which sit on the arms of the coupling intermediate links.
- the handlebars themselves have a low mass, since they are practically formed only by the tabs.
- the radial arms of the intermediate coupling members 24 and 26 are formed symmetrically to the central plane 168.
- the arms engage around the outermost or middle and outermost coupling intermediate members 22 or 22 and 24 on both sides.
- the middle coupling intermediate link 24 is composed of two intermediate link halves 170 and 172.
- the dividing line between the intermediate link halves runs in the plane of the annular surface 136.
- the two intermediate link halves 170 and 172 are centered on one another by a circular centering strip 174 of the intermediate link half 170 and a complementary annular groove of the intermediate link half 172.
- the two intermediate link halves 170 and 172 are by screws 175 connected with each other. As can be seen from FIG.
- the centering strip 174 and the complementary annular groove are each interrupted in the area of the screws 175. This ensures that there is sufficient material around the holes drilled for the screws.
- the arms of the middle coupling intermediate link 24 each consist of two halves 176 and 178. One half 176 sits on the intermediate link half 170. The other half 178 sits on the intermediate link half 172. The two halves 176 and 178 grip left and right (in Fig.l ) around the outermost coupling intermediate member 22 and abut each other in the central plane 168. There they form the eyes 88 for receiving the bearing means 90.
- the innermost coupling intermediate link 26 is divided into two intermediate link halves 180 and 182 in the plane of the annular surface 160.
- the intermediate link half 180 has a centering projection 184, which engages in a complementary recess in the intermediate link half 182.
- the two intermediate link halves 180 and 182 are connected to one another by screws 186.
- the arms of the innermost coupling intermediate member 26 are also made up of two halves 188 and 190.
- One half 188 sits on the intermediate link half 180.
- the other half 190 sits on the intermediate link half 182.
- the two halves 180 and 190 grip left and right (in FIG. 1) around the middle and outermost coupling intermediate links 24 and 22 and lie in the central plane 168 to each other.
- These arms also form eyes 88 there for receiving bearing means 90 for the handlebars.
- the innermost coupling intermediate member 26 has a lubricant reservoir 192 in the middle.
- the lubricant reservoir 192 contains a lubricant, preferably grease.
- Three radial channels 194 extend from the lubricant reservoir 192, each of which is angularly offset from one another by 120 °.
- the radial channels 194 run in the innermost Coupling intermediate member and open into its outer surface 118.
- the middle coupling intermediate member 24 with its inner surface 120 is mounted on this outer surface 118.
- axial recesses 196 of semicircular cross section are formed in the inner surface 120.
- the recesses 196 are connected to the radial channels 194.
- the recesses 196 are connected at their ends to flat, crescent-shaped recesses 198, which are formed in the annular shoulders 150 and 152. Lubrication of the guide formed between the ring shoulders 150 and 152 and the ring surfaces 160 and 162 takes place via these recesses 198.
- further axial recesses 200 of semicircular cross section are provided in the outer surface 118 of the innermost coupling intermediate member 26. These recesses 200 are angularly offset by 30 "in each case from the recesses 196 in the central position of the intermediate coupling members 22, 24 and 26.
- the recesses 200 are also connected at their ends to flat, crescent-shaped recesses 202 which are in the ring shoulders 126 and 128 of the innermost one Coupling intermediate member 26 are formed.
- the inner surface 114 of the middle coupling intermediate member 24 has further axial recesses 204, which are offset by 60 ° with respect to the recesses 196.
- the axial recesses 204 are also connected to flat, crescent-shaped recesses 206 in the annular shoulders 150 and 152.
- three radial channels 208 are formed, which are connected to the recesses 204.
- the radial channels 208 like the recesses 204, are each angularly offset from one another by 120 °.
- the channels 208 are offset by 60 ° from the channels 194.
- the radial channels 208 are connected to axial recesses 210 in the illustrated central position of the coupling.
- the recesses 210 are in the inner surface 120 of the outermost coupling intermediate member 22 is provided.
- the axial recesses 210 have a semicircular cross section.
- the recesses 210 are connected to flat, crescent-shaped recesses 212 in the annular shoulders 126 and 128 of the outermost coupling intermediate member 22.
- axial recesses 214 are formed, each offset by an angle of 60 ° with respect to the recesses 210. These recesses 214 are also connected to flat, crescent-shaped recesses 216 in the annular shoulders 126 and 128 of the outermost coupling intermediate member 22. Further axial recesses 218 and 220 are provided in the outer surface 112 of the middle coupling intermediate member 24 between the recesses 210 and 214 in the inner surface 120 of the outermost coupling intermediate member 22. These recesses are each arranged at an angle of 30 ° to the radial channels 194 on both sides of these channels 194. Each of these axial recesses 218 and 220 is connected to flat, crescent-shaped recesses 222 and 224 in the ring shoulders 126 and 128, respectively.
- the lubricant is distributed through the recesses 196 and the recesses 200 over the bearing surface. This happens in particular with a periodic rotary movement of the
- Coupling halves 10 and 12 enters. If that
- Recesses 204 and the channels 212 to the recesses 210 transported. From there, the lubricant is again distributed evenly over the bearing surface between the middle and outermost coupling intermediate members 24 and 22 respectively.
- the crescent-shaped recesses, for example 216 distribute the lubricant over the radial guide surfaces, through which the intermediate coupling members 22, 24 and 26 counter to axial ones Forces are brought together.
- a radial channel 217 is also formed in the extension of one of the channels 194 (with the coupling in the middle position), starting from the associated recess 196 in the inner surface of the middle coupling intermediate member 24 in the middle coupling intermediate member .
- the radial channel 217 is connected to the recess 210 in the inner surface of the outermost coupling intermediate member 22.
- an annular channel 219 connects the recesses 210 and 218 in the middle and outermost coupling intermediate member.
- the innermost and outermost coupling intermediate member can also be made from another sliding metal with low sliding friction, in particular also from steel. It is essential that the intermediate coupling members 22, 24, 26 are mounted directly on top of each other by a sliding bearing with their inner and outer surfaces.
- the coupling according to Fig. 3 and 4 is constructed essentially exactly like the coupling according to Fig.l and 2. Corresponding parts are provided with the same reference numerals as there. 3 and 4, the coupling intermediate members 22, 24 and 26 are manufactured as castings.
- the plain bearing contains hardened, polished spring steel strips 230 and 232.
- the spring steel strip is 230 inserted between the outermost coupling intermediate member 22 and the middle coupling intermediate member 24.
- the spring steel strip 232 is inserted between the middle coupling intermediate member 24 and the innermost coupling intermediate member 26.
- the plain bearing takes place between the hardened and polished surface of the spring steel strip and the cast surface of the intermediate coupling members 22, 24 and 26, which are manufactured, for example, as gray cast iron. The coefficient of friction is very low.
- the spring steel strips have small radial dimensions. The spring steel strips have little wear.
- the spring steel strips are also very inexpensive. In this way, an inexpensive and largely maintenance-free coupling with the smallest possible radial dimensions can be constructed.
- 234 denotes a drive-side coupling half, which can be screwed onto a flywheel or a gear flange, for example.
- An output-side coupling half 236 sits on a shaft 238.
- the input-side coupling half 236 has radial arms 240.
- the radial arms 240 have axially projecting lugs 242.
- the lugs 242 are provided with axial bores 244.
- a bushing 254 is seated in the vibrating metal bearing 246.
- the tabs 250 and 252 bear against the end faces of the bushing 254.
- a threaded bolt 256 with a head 258 extends through an opening in the lug 252 and through the bore of the bush 254.
- the lug 250 has a thickening 260 or a welded-on nut in the region of the bush 254 and the threaded bolt 256.
- Through the lug 250 and Thickening 260 extends a threaded bore 262.
- the threaded end 264 of the threaded bolt 256 is in this threaded bore 262 screwed in.
- the tightening can be done from the right in Fig.5. This is important for applications where the left end of the threaded bolt 254 in FIG. 5 is not accessible, for example, for tightening or holding a nut.
- the tab 250 is held here.
- a coupling intermediate member 266 is provided.
- the coupling intermediate member 266 is a ring surrounding the shaft 238.
- the coupling intermediate member 266 has a cylindrical outer surface 268.
- the coupling intermediate member 268 consists of two ring parts 270 and 272, which are separated from one another by a stepped parting line 274 and screwed together.
- the outer surface 268 is formed by the ring part 270.
- a radial arm 276 and 278 is formed on each of the ring parts 270 and 272.
- the arms 276 and 278 are aligned with one another and are brought together for abutment along a central plane 280.
- the merged arms form an eye (not shown) for receiving a vibrating metal bearing (also not shown).
- the intermediate coupling member 266 is connected to the drive-side coupling half 234 in a manner similar to that in FIG. 1 via the oscillating metal bearings and the tabs 250 and 252.
- a corresponding arrangement offset by 180 ° connects the coupling intermediate member 266 to the output-side coupling half 236.
- a second and a third coupling intermediate element 282 and 284 are mounted on the cylindrical outer surface 268 of the intermediate coupling element 266.
- the second coupling link 282 consists of a ring 286 and a ring 288.
- the third coupling link 284 consists of a ring 290 and a ring 292.
- the ring 290 of the third coupling link 284 lies between the rings 286 and 288 of the second coupling link.
- the ring 288 of the second intermediate coupling member 282 is in turn between the rings 290 and 292 of the third Coupling intermediate member.
- the rings 286 and 288 are connected to one another by bridge members 294 which engage over the ring 290 of the third coupling intermediate member 282.
- the rings 290 and 292 are connected to one another by bridge members which engage over the ring 288 of the second coupling intermediate member.
- the bridge members and the arms (not shown) on the coupling links 282 and 284 are arranged so that they do not interfere with each other in the reciprocating relative rotation of the coupling links.
- Hardened and polished spring steel strips 296 are arranged on the outer surface 268 of the coupling intermediate member 266. These spring steel strips 296 form slide bearings for the intermediate coupling members 282 and 284. Five rings 298 provide sliding guidance in the axial direction. The sliding bearing and sliding guide are sealed off from the outside by seals 300.
- the coupling intermediate members are made in one or two parts, including the radial arms made of the sliding metal, e.g. Made of gray cast iron. Torques are transmitted via the arms, however, so that they are subjected to a constant alternating load. When the arms are made from gray cast iron or another material with sliding properties, there is then a risk of the material becoming fatigued. An oversizing of the arms is therefore necessary. This oversizing increases the weight of the coupling.
- the plain bearing can show wear after a long period of operation.
- the coupling intermediate member would then have to be replaced in a coupling according to the main patent.
- one of the coupling intermediate members contains a lubricant Reservoir and means for distributing the lubricant to the bearing surfaces.
- the bearing surfaces must be sealed to the outside with seals in order to counteract a loss of lubricant and to prevent dirt from penetrating into the plain bearing.
- seals There are problems in letting such seals rest on the surfaces of a coupling intermediate element designed as a cast part. This would lead to a relatively high wear of the seals due to the relative movements.
- FIGS. 6 and 7 is based on the task of further developing a coupling of the type present here in that
- the intermediate coupling members are able to transmit the torques occurring at the lowest possible weight of each intermediate coupling member without fatigue of the material
- the plain bearing can be sealed against the outside, without an impermissibly strong
- the two inner coupling intermediate members each have an annular, inner bearing part made of sliding metal and on both sides of the inner bearing part lateral rings made of steel, which are connected to the inner bearing part by releasable connecting means and have the radial arms.
- the outer coupling intermediate member can be made in one piece from steel.
- One of the intermediate coupling members can again contain a lubricant reservoir and it can Means for distributing the lubricant to the bearing surfaces can be provided.
- ring grooves are formed on the outer lateral surface, in which seals for sealing the bearing surfaces sit outwards.
- the inner lateral surfaces of the outer and the middle coupling intermediate member form ground and hardened surfaces on which the seals bear.
- 310 denotes a drive-side coupling half and 312 a driven-side coupling half.
- the drive-side coupling half 310 has a hub 314.
- the drive-side coupling half 310 has three radial arms 318, which are angularly offset from one another by 120 °.
- the output-side coupling half 312 also has three radial arms 320, which are angularly offset from one another by 120 °.
- the intermediate coupling members 322, 324 and 326 are arranged concentrically to one another and rotatably supported on one another.
- Each of the coupling links has two diametrically opposed radial arms.
- one of the two radial arms 328 of the outermost coupling intermediate member 322 is indicated.
- one of the radial arms 330 of the middle coupling intermediate member 324 is shown in section.
- One of the arms of the intermediate coupling members 322, 324 and 326 is connected to an arm 318 of the drive-side coupling half 310 via a link.
- the respective other arm of each coupling half is connected to an arm 320 of the output-side coupling half 312 via a link 334.
- the alignment is also aligned common axis of the intermediate coupling members 322, 324 and 326 with the axes of the coupling halves 310 and 312.
- the radial arms 320 of the output-side coupling half 312 are offset by 60 ° against the arms 318 of the input-side coupling half 310.
- the arms 328, 330 and 332 of the intermediate coupling members 322, 324 and 326 are each offset by 30 ° relative to the arm of a coupling half 310 or 312 to which the arm of the intermediate coupling member is connected via a link.
- axles of the drive-side and output-side coupling halves 310 and 312 are radially offset from one another, this is compensated for by a displacement of the coupling intermediate links 322, 324 and 326 and by a pivoting of the handlebars, the coupling intermediate links simultaneously executing a reciprocating rotational movement against one another .
- the transmission of the rotary movement from the drive-side coupling half to the driven-side coupling half remains true to the angle.
- a uniform drive movement also leads to a uniform drive movement.
- FIG. 6 shows how the links 334 are articulated on the arms of the coupling intermediate members 322, 324 and 326.
- arm 330 forms an eye 386 with a straight, cylindrical bore.
- Bearing means 90 are seated in the bore.
- the bearing means 90 are formed by a rubber bearing.
- the bearing means 90 hold a pin body 404 which forms part of the link 334.
- the pin body 404 has a central axial bore.
- a threaded bolt 410 extends through the central bore.
- a link 412 of the handlebar is clamped between the head of the threaded bolt 410 and the end face of the pin body 404.
- a second tab 414 of the handlebar 334 bears against the other, on the right in FIG.
- the tab 414 has a threaded bore into which the threaded end of the threaded bolt engages.
- the handlebars can be pivoted elastically via rubber bearings on the one hand to an arm 318 of the drive-side coupling half or an arm 320 of the output-side coupling half 312 and on the other hand to an arm 328, 330 or 332 of a coupling intermediate member 322, 324 or 326.
- the links 334 can pivot about the axes of the rubber bodies, ie in the paper plane of FIG. 7.
- the links can also be pivoted out of this paper plane to a limited extent and thus compensate for an angular or axial offset of the coupling halves 310 and 312 relative to one another.
- the outer, annular coupling intermediate member 322 is in one piece and has a steel ring 416 to which the arms 328 are integrally formed.
- the middle, annular coupling intermediate member 324 is in three parts.
- the coupling intermediate member 324 has an inner bearing part 418 and lateral rings 420 and 422 on both sides of this bearing part 418.
- the arms 330 are in two parts, one half of each arm 330 being formed on one of the side rings 420 and 422, respectively.
- the lateral rings 420 and 422 are centered on the bearing part 418 by arc-shaped centering strips 424 and 426, respectively, which engage in corresponding grooves in the end faces of the bearing part 418. Between the centering strips 424 and 426 and the corresponding grooves, the outer rings 420 and 422 are connected to the bearing part 418 by screws 428.
- the bearing part 418 consists of a sliding material, for example gray cast iron or bronze.
- the side rings 420 and 422 with the arms 330 formed thereon are made of steel.
- Grooves 430 and 432 are provided in the outer lateral surfaces of the two outer rings 420 and 422, respectively.
- Seals 434 and 436 are seated in the grooves 430 and 432.
- the seals 434 and 436 lie against the inner lateral surface of the outer coupling intermediate member 322. This inner lateral surface is in any case hardened and in the area of the seals 434 and 436 ground. This ensures wear-free contact between the seals 434 and 436 and the outer coupling intermediate member 322.
- the radial arms 330 made of steel can absorb the alternating load during the transmission of the torques without oversizing and without fatigue of the material.
- the inner coupling intermediate member 326 also consists of a middle, ring-shaped bearing part 438 and lateral rings 440 and 442.
- the middle bearing part 438 is made of a bearing material such as gray cast iron or bronze.
- the side rings 440 and 442 with the arms 444 formed thereon are made of steel.
- the lateral rings 440 and 442 are centered on the bearing part 438 by edge strips 446 and 448.
- the parts 440, 438 and 442 of the inner coupling intermediate member 326 are connected to one another by screws 450.
- Grooves 452 and 454 are provided in the outer lateral surfaces of the lateral rings 440 and 442. Seals 456 and 458 are seated in the grooves 452 and 454. The seals 456 and 458 bear against the inner lateral surfaces of the side rings 420 and 422 of the middle coupling intermediate member 324. These inner lateral surfaces are hardened and ground in the area of the seals 456 and 458.
- the inner coupling link 326 has a lubricant reservoir 492 in the middle.
- the lubricant reservoir 492 contains a lubricant, preferably grease.
- Radial channels 494 extend from the lubricant reservoir 492 and are angularly offset from one another by 60 °.
- the radial channels 494 run in the inner coupling intermediate member and open into axial grooves 540 in its outer surface 418.
- the inner coupling intermediate member 324 with its inner surface is mounted on this outer surface 418.
- axial recesses 496 of semicircular are in the inner surface Cross section formed.
- the recesses 496 are offset by 30 ° from the recesses 540.
- further axial recesses 500 of semicircular cross section are provided in the outer surface 418 of the inner coupling intermediate member 326. These recesses 500 are offset from one another by 30 ° with respect to the recesses 496 in the central position of the intermediate coupling members 322, 324 and 326.
- three radial channels 508 are formed, which are connected to the recesses 540.
- the radial channels 508, like the recesses 540, are each angularly offset from one another by 60 °.
- the channels 508 are aligned with the channels 494 in the central position.
- the radial channels 508 are connected to axial recesses 510.
- the recesses 510 are provided in the outer surface 420 of the middle coupling intermediate member 324.
- the axial recesses 510 have a semicircular cross section.
- axial recesses 514 are formed, each offset by an angle of 30 ° with respect to the recesses 510.
- the centrifugal force transports lubricant from the lubricant reservoir 492 through the channels 494 into the bearing surface, which is formed between the inner and the middle coupling intermediate members 326 and 324, respectively.
- the lubricant is distributed through the recesses 496 and the recesses 540 over the bearing surface. This occurs in particular when the intermediate coupling members 326 and 324 rotate periodically, as occurs when the axes of the parts to be coupled and the coupling halves 10 and 12 are offset radially. If the lubricant is in this way over the bearing surface between the inner and the middle coupling intermediate member 326 or 324 has distributed, the lubricant is transported further via the channels 508 to the recesses 510.
- the lubricant is again distributed evenly over the bearing surface between the middle and outer coupling intermediate members 324 and 322.
- the crescent-shaped recesses for example 514, distribute the lubricant over the radial guide surfaces, through which the coupling intermediate members 322, 324 and 326 counteract axial forces are brought together.
- the inner and the outer coupling intermediate member can also be made from another sliding metal with low sliding friction, in particular also from steel. It is essential that the intermediate coupling members 322, 324, 326 are mounted directly on one another by means of a sliding bearing with their inner and outer surfaces.
- the plain bearing can contain hardened, polished spring steel strips 530 and 532.
- the spring steel strip 530 is inserted between the outer coupling intermediate member 322 and the middle coupling intermediate member 324.
- the spring steel strip 532 is inserted between the middle coupling intermediate member 324 and the inner coupling intermediate member 326.
- the plain bearing takes place between the hardened and polished surface of the spring steel strip and the cast surface of the e.g. Coupling links 322, 324 and 326 produced as gray cast iron. The coefficient of friction is very low.
- the spring steel strips have small radial dimensions.
- the spring steel strips have little wear.
- the spring steel strips are also very inexpensive. In this way, an inexpensive and largely maintenance-free coupling with the smallest possible radial dimensions can be constructed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5519909A JPH07500177A (ja) | 1992-05-21 | 1993-05-21 | 回転部分の連結のためのカップリング |
EP93912734A EP0596094A1 (de) | 1992-05-21 | 1993-05-21 | Kupplung zum kuppeln umlaufender teile |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DEP4216743.4 | 1992-05-21 | ||
DE19924216743 DE4216743C1 (de) | 1992-05-21 | 1992-05-21 | Kupplung |
DE19934313645 DE4313645C1 (de) | 1992-05-21 | 1993-04-26 | Kupplung |
DEP4313645.1 | 1993-04-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1993023684A1 true WO1993023684A1 (de) | 1993-11-25 |
Family
ID=25915011
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1993/001260 WO1993023684A1 (de) | 1992-05-21 | 1993-05-21 | Kupplung zum kuppeln umlaufender teile |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0596094A1 (de) |
JP (1) | JPH07500177A (de) |
DE (1) | DE4313645C1 (de) |
WO (1) | WO1993023684A1 (de) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4040270A (en) * | 1974-06-29 | 1977-08-09 | Ilie Chivari | Coupling adapted to connect radially offset shafts |
DE3429043A1 (de) * | 1984-08-07 | 1986-02-20 | Ilie 4690 Herne Chivari | Kupplung fuer achsversetzte, umlaufende maschinenteile |
DE3732705A1 (de) * | 1987-09-29 | 1989-04-13 | Ilie Chivari | Wellenkupplung |
-
1993
- 1993-04-26 DE DE19934313645 patent/DE4313645C1/de not_active Expired - Fee Related
- 1993-05-21 EP EP93912734A patent/EP0596094A1/de not_active Withdrawn
- 1993-05-21 WO PCT/EP1993/001260 patent/WO1993023684A1/de not_active Application Discontinuation
- 1993-05-21 JP JP5519909A patent/JPH07500177A/ja active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4040270A (en) * | 1974-06-29 | 1977-08-09 | Ilie Chivari | Coupling adapted to connect radially offset shafts |
DE3429043A1 (de) * | 1984-08-07 | 1986-02-20 | Ilie 4690 Herne Chivari | Kupplung fuer achsversetzte, umlaufende maschinenteile |
DE3732705A1 (de) * | 1987-09-29 | 1989-04-13 | Ilie Chivari | Wellenkupplung |
EP0389647A1 (de) * | 1987-09-29 | 1990-10-03 | Ilie Chivari | Wellenkupplung |
Non-Patent Citations (1)
Title |
---|
HYDRAULIC PNEUMATIC POWER Bd. 21, Nr. 243, März 1975, MORDEN GB Seiten 86 - 87 K. WORTHINGTON 'rubber component couplings' * |
Also Published As
Publication number | Publication date |
---|---|
JPH07500177A (ja) | 1995-01-05 |
DE4313645C1 (de) | 1994-09-15 |
EP0596094A1 (de) | 1994-05-11 |
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