JPH0138973B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a joint for connecting machine parts, such as a boss and a shaft, using frictional force so that they cannot rotate relative to each other. at least one pressure ring coaxially surrounding the pressure ring, the outer conical surface of the pressure ring is in full contact by the inner conical surface of the outer ring, and the outer ring is in contact with the ring-shaped shoulder. The inner cylindrical surface of the pressure ring surrounds the ring-shaped piston of the pressure ring and the ring-shaped pressure chamber that can be loaded with liquid via the supply line, and the outer ring is arranged along the axis of the ring-shaped piston. of the type which is hydraulically supportable in the direction and movable in the axial direction relative to the upwardly inclined outer conical surface of the pressure ring.

The above-mentioned known joint (U.S. Pat. No. 3,865,497, FIG. 4) connects two shaft journals in a mating manner. In this case, a pressure ring with an external conical surface covers both shaft journals and supports at one end a ring piston held immovably in the form of a sleeve nut on the external thread. This ring piston is surrounded by the cylindrical inner circumferential surface of a ring-shaped shoulder formed by the components of the outer ring, the inner conical surface of said outer ring being completely flush with the outer conical surface of the pressure ring. are in contact with. In this case, the ring piston, the pressure ring and the outer ring form a ring-shaped pressure chamber of approximately square cross section, which can be opened to atmospheric pressure via an exhaust valve. At an axial distance from the ring-shaped pressure chamber, in the area of the conical surface in full contact, a radial feed hole is provided which can be loaded with liquid and which feeds into the inner ring of the outer ring. It opens into a ring groove provided on the conical surface.

Known rigid joints (U.S. Pat. No. 3,865,497,
Figure 4) works as follows: The supply hole is pressurized with liquid, which at the same time lubricates the gap between the two conical surfaces and flows through this conical annular gap into the annular pressure chamber. reach. This pressure chamber is closed by an exhaust valve. The feed hole pressure creates a pressure within the ring-shaped pressure chamber that causes the outer ring to move axially relative to the upwardly facing outer conical surface of the pressure ring. When the supply hole pressure is allowed to collapse, the tight axial position of the pressure ring and the outer ring is ensured by a self-locking action. In this case, the tapering of the inner diameter of the pressure ring provides a frictional connection between the two shaft journals.

To release the known coupling, liquid is again forced into the area between the two conical surfaces and the exhaust valve is opened, so that no pressure builds up in the annular pressure chamber. Rather, a pressure is created between the two conical surfaces which, as it were, according to the law of inclined surfaces, causes the outer ring to move from its clamped position relative to the pressure ring in the direction of the ring piston, ie to relax.

Known rigid joints (U.S. Pat. No. 3,865,479,
4) has been found to be disadvantageous for a number of reasons: Since the known coupling operates on the principle of a double-acting cylinder, the construction of this coupling is inherently very expensive. Furthermore, it is extremely difficult to load both shaft journals with approximately the same direct ring tension if necessary. This is because the pressure ring is thinner in the area of one shaft journal and relatively thicker in the region of the other shaft journal. Furthermore, the disassembly of the pressure ring and the outer ring is caused by the fact that the conical surfaces of the pressure ring and the outer ring are in contact with each other with a self-locking effect in the tightened state, and digging in at the connecting surface is inevitable after a relatively long period of time has passed. It is extremely difficult.
The liquid pressure to be applied between the conical surfaces for the splitting usually does not have the ability to lift the outer ring from its clamped position and push it away from the pressure ring. Rather, additional disassembly aids are to be used, for example hydraulic extraction devices. In the known joint, removability is only achieved if both conical surfaces are machined relatively accurately by expensive grinding.

The object of the invention is to proceed from the known coupling of the type mentioned at the outset (US Pat. No. 3,865,497, FIG. The objective is to enable decomposition without To this end, the invention provides an arrangement in which an additional pressure ring is fixedly connected in the axial direction to the pressure ring, the additional pressure ring having outer conical surfaces that are coaxial but slope upwardly in opposite directions. , on the outer conical surface of this additional pressure ring an additional outer ring forming a piston is arranged axially movable in full contact with its inner conical surface, and The supply line for This can be secured using an axially adjustable stop held by a ring.

In accordance with the invention, both outer rings are axially movable relative to the two pressure rings, which are axially fixedly connected to one another, so that they can be tightened, so that the entire connection range can be loaded. A uniform and symmetrical tension is always obtained throughout. In an embodiment of the invention, a particularly simple construction is obtained in that the two pressure rings abut each other in a small diameter range. In such an embodiment, the axially confined pressure chamber between the two outer rings is such that both outer rings can be moved with their inner conical surfaces relative to the corresponding upwardly directed outer conical surfaces of the pressure rings. allows hydraulic expansion of both outer rings.

In an embodiment of the invention, the supply line for the liquid is a gap line between the conical surfaces (US Pat. No. 3,865,497;
(see FIG. 4) directly into the pressure chamber. A direct pressure application by hydraulic forces in the form of a cylinder that acts exclusively in a single-acting manner is possible because the angle of inclination of the conical surfaces in contact with one another is located outside the self-locking action according to the invention. . As soon as the liquid pressure is brought to collapse, the tension created between the respective outer ring and the associated inner ring (pressure ring) can be applied without any auxiliary means - on mutually interdigitated conical surfaces - axially in the direction of disintegration. Produces movement movement in the direction. If, on the other hand, the tension force is to be created and maintained hydraulically, the tensioning position can be simply fixed using an axially adjustable stop, in particular a stop screw. If the clamping position is fixed, for example by a stopper screw, and the pressure chamber is depressurized, the coupling according to the invention becomes completely independent of the fluid pressure; that is, the clamping position eliminates the respective binding action between the corresponding conical surfaces. It is maintained in this state by a stopper screw or a means equivalent to this stopper screw.

Since the corresponding conical surfaces are in contact with each other without self-locking action, i.e. they have a half-cone angle that is usually larger than 8°, the surface machining of the conical surfaces is provided in the self-locking range and is therefore cost-effective. It no longer needs to be done as precisely as on a conical surface, which must be ground with The conical surface according to the invention need only be machined on a lathe.

Advantageous embodiments of the invention are defined in the second patent claim.
It is also possible to combine these embodiments.

Next, embodiments of the present invention will be specifically described using the drawings.

In the drawing, the shaft is designated by 10, the shaft journals are designated by 10a and 10b, and the axis of rotation of the shaft is designated by X. A boss surrounding the shaft 10 is designated by the reference numeral 11, and a boss-like connecting sleeve is designated by the reference numeral 12 surrounding the shaft journals 10a, 10b which are matingly connected to each other.

As shown in FIG.
a is tightened around the boss 11. It is indicated by an additional pressure ring numeral 14a. A seal ring 1 is placed between the inner end faces of both pressure rings 13a and 14a that abut each other within the range of the smaller outer diameter.
5 is provided. The outer ring corresponding to the pressure ring 13a is numbered 16 and the additional outer ring corresponding to the additional pressure ring 14a is numbered 1.
7.

The conical outer circumferential surface of each pressure ring is designated A and the conical inner circumferential surface of each outer ring is designated I.

The inclination of the generatrices of the conical surfaces in contact with each other is such that the half-cone angle α (Fig. 4) of each cone is slightly larger than the friction angle of two perfectly machined and lubricated external surfaces of the cones sliding against each other. It is stipulated as follows.

Both pressure rings 13a, 14a can be screwed into each other (FIG. 1, screws 18) or by screwing both pressure rings inside or in a common intermediate piece. They are thus axially fixedly connected to each other.

The outer ring 16 has a ring-shaped shoulder 19 projecting to one side in the axial direction, and this shoulder is a cylindrical inner surface and forms an inner cylindrical surface 20. cooperates with the cylindrical outer circumferential surface 21 forming the piston surface of the additional outer ring 17.

The additional outer ring 17 has a thread 22 in the extension of the cylindrical outer circumferential surface 21, which external thread is screwed into the internal thread 23 of the sleeve nut 24. The sleeve nut 24 abuts against the ring-shaped shoulder.

Radial pressure surface 2 of additional outer ring 17
5 and the radial pressure surface 26 of the outer ring 16 is a pressure chamber 27 which can be pressurized directly with liquid via the connection hole 28 and the two channels 29, 30. be. Cylinder inner peripheral surface 20
A hydraulically effective ring seal between the outer cylindrical surface 21 and the outer cylindrical surface 21 is indicated at 31.

The embodiment shown in FIG. 2 does not differ significantly from the embodiment shown in FIG. The basic structure and operation are the same in the embodiment shown in FIG. 2 and in all other embodiments.

The embodiment of FIG. 2 differs from the embodiment of FIG. 1 only in that the axially fixed connection between the pressure rings is constructed differently. As can be seen in FIG. 2, the boss 11 is provided on one side with a turning 32 which is bounded by a shoulder 33. In this case, a flange ring 35 is crimped to the boss 11 on the end face side using a screw 34, and a spacer ring 36 is interposed between the two pressure rings 13b,
14b are fixedly axially pressed together.

The assembly process takes place in a similar manner both in the embodiment of FIGS. 1 and 2 as well as in the other embodiments; first the boss 11 is pressed onto the shaft 10, and then the pressure ring 13a, 14a or 1
3b, 14b are pressed onto the boss 11 together with the associated outer rings 16, 17. At this time, the joint between the pressure rings 13a, 14a or 13b, 14b is sealed using the seal ring 15. As already mentioned, the pressure rings 13a, 14
a or 13b, 14b are immovably connected to each other in the axial direction.

Furthermore, the sleeve nut 24 has a ring-shaped shoulder portion 1.
It is screwed in until it comes into contact with the end face of the hole 9, and at this time the outer circumferential surface A and the inner circumferential surface I are in sufficient contact. A secure threaded connection is easily obtained using relatively large tools such as a hammer and chisel. Finally, a hydraulic pump pressure conduit (not shown) is connected to the connection hole 28 and oil or grease is forced into the pressure chamber 27 .

When a predetermined pressure is obtained, the outer ring 16,1
The sleeve nut 24 is tightened against the end face of the annular shoulder 19 as the sleeve nuts 24 move away from each other in the axial direction relative to the corresponding pressure ring. After the liquid pressure has collapsed, the connection hole 28 is closed by a dust plug (not shown).
For disassembly, pressure medium is again introduced into the pressure chamber 27 and the pressure is increased there so that the sleeve nut 24 can be unscrewed from the annular shoulder 19.

By combining the embodiments corresponding to FIGS. 1 and 2, the axial connection approximately as shown in FIGS. 3 and 4 is achieved. A common boss-shaped connecting sleeve 12 connects the shaft journals 10a and 10b to each other. In contrast to the other embodiments, the pressure ring 13c is constructed integrally with the connecting sleeve 12 on both sides of the radial midplane indicated by y and is made of the same material and has an approximately roof-shaped conical slope with opposite directions. It has been placed since then.

In the embodiment according to FIG. 3, the pressure ring 14c is fixedly screwed in the axial direction to the connecting sleeve 12 by means of a sleeve nut 37, whereas the pressure ring 14c in FIG. The connecting sleeve 12 is fitted over the connecting sleeve 12 so as to be movable in the axial direction.

The ring seal (O-ring) 31 in FIG. 3 is fitted within the cylindrical outer peripheral surface 21 of the outer ring 17, whereas the ring seal (O-ring) 31 in FIG. 19 cylindrical inner peripheral surface 2
It is set within 0. In the embodiment of FIG. 4, an intermediate piece (pressure piece or filler piece) 38 allows replacement of the ring seal (O-ring) 31 without disassembly of the pressure ring 14c. Connecting sleeve 1
In order to avoid force concentrations in the central region of the two holes, a ring groove 39 is provided on the inside of the connecting sleeve. This is particularly important, for example, if the transmission is cantilevered and flanged and the shaft ends 10a, 10b are subjected to bending loads.

In the embodiment of FIG. 4, the inner bore of the connecting sleeve 12 is machined to normal H-7 manufacturing tolerances after the shrink fit of the pressure ring 14c. Figures 3 and 4
The illustrated embodiment makes it possible to machine the outer peripheral surface of the shaft end 10a with a manufacturing error of g6 and the outer peripheral surface of the shaft end 10b with a manufacturing error of g6. If, during assembly, the liquid pressure in the pressure chamber 27 on the left in each case in the drawing is approximately 50 bar higher than the pressure in the pressure chamber 27 on the right, then during locking the shaft end 10b in the connecting sleeve 12 first It starts to slide. In this context, couplings are used in practice to connect the shaft journal of a shovel wheel of a shovel wheel excavator to the shaft journal of a transmission. Of course, when tightening the shovel wheel, the transmission shaft (shaft journal 10b) is somewhat easier to replace than the shaft journal 10a of the shaft of a larger shovel wheel.

The embodiments of FIGS. 5 to 7 differ from the previously described embodiments mainly by a simple, small, and inexpensive stopper screw, which is particularly advantageous in connection with large shaft and boss diameters. be.

In FIG. 5, the outer ring 17 is provided with a ring-shaped support shoulder 40. In FIG. When a multi-part intermediate piece 41 or a filler piece between the support shoulder 40 and the ring shoulder 19, approximately in the form of a multi-part shim, creates the required pressure in the pressure chamber 27 during assembly. Fitted in. When the liquid pressure collapses, the multi-part intermediate piece 41 is clamped between the two shoulders 19,40. For disassembly, pressure liquid is again introduced into the pressure chamber 27, and at a predetermined pressure height the multi-part intermediate piece 41 can be easily removed.

In the embodiment of FIGS. 6 and 7, for example, instead of the sleeve nut 24 of FIGS. 1 and 2, axial stop screws 42, 43 are provided which are regularly distributed over the circumference. . The stop screws 42, 43 can be actuated via an inner hexagonal portion 44.

In the embodiment of FIG. 6, each axial hole 45
has an internal thread in the inner axial region for receiving the stop screw 42 and a smooth inner circumferential wall in the outer axial region. Against this smooth inner peripheral wall, a stop screw 42 holds an O-ring 47 in the area of the shaft 46, which is also smooth. In this way, each stop screw 42 is inserted in the associated axial bore 45 in a fluid-tight manner. The sealing of the individual stop screws is such that the outer ring 17 has a ring-flange-like extension 48 in its piston area, which together with the ring seals 31a, 31b seals the pressure chamber 27.
This becomes unnecessary if a liquid sealing action is produced. The stopper screw 43 is connected to the hole 49 to which it belongs.
together with the liquid piston seal area (3
1a, 31b) and can thus be provided with a thread over its entire length in the axial direction. Of course, the stopper screw 44 can be provided with holes 49 in areas corresponding to the shoulders 19 and 40 in FIG.
It can also be placed outside of 31b. The half-cone angle α, which applies to all embodiments, is shown in FIG.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, in which FIG. 1 is a longitudinal sectional view of an embodiment of the shaft-boss joint, and FIG.
The figure is a longitudinal sectional view of another embodiment of the shaft-boss connection, FIG. 3 is a longitudinal sectional view of an embodiment of the connection between two shaft journals, and FIG. FIGS. 5, 6 and 7 are longitudinal sectional views of different embodiments of the connection between the shaft and the boss. 10... Shaft, 10a and 10b... Shaft journal, 11... Boss, 12... Connection sleeve, 13
a, 13b, 13c, 14a and 14b... pressure ring, 15... seal ring, 16 and 17...
...Outer ring, 18...Thread, 19...Shoulder,
20... Cylinder inner circumferential surface, 21... Cylinder outer circumferential surface, 22
... Male thread, 23 ... Female thread, 24 ... Sleeve nut, 25 and 26 ... Pressure surface, 27 ... Pressure chamber, 28 ... Connection hole, 29 and 30 ... Passage, 3
1... Ring seal, 32... Turning part, 34...
Screw, 35...Flange ring, 36...Spacer ring, 37...Sleeve nut, 38...Intermediate piece, 39...Ring groove, 40...Support shoulder, 4
1... Intermediate piece, 42 and 43... Stopper screw,
44... Inner edge hexagonal part, 45... Axial hole, 46
... Shaft, 47 ... O-ring, 48 ... Additional part, 49 ... Hole.

Claims (1)

[Scope of Claims] 1. A joint for connecting machine parts in a relatively rotationally fixed manner by frictional force, comprising at least one pressure ring having an external conical surface and coaxially surrounding the associated machine part. The outer conical surface of the pressure ring is in full contact with the inner conical surface of the outer ring, and the outer ring is connected to the ring piston and the supply conduit by the inner cylindrical surface of the ring-shaped shoulder. enclosing a ring-shaped pressure chamber loadable by a liquid via the ring-shaped pressure chamber and axially hydraulically supportable on the ring piston against an upwardly inclined outer conical surface of the pressure ring. In the axially movable type, the pressure rings 13a, 13
b, an additional ring 1 having an outer conical surface A coaxial with but sloping upward in the opposite direction to 13c;
4a, 14b, 14c are axially fixedly connected, and the outer conical surface A of this additional pressure ring
Above, an additional outer ring 17 forming a piston is arranged axially movable in full contact with its inner conical surface, and the supply line 30 for the liquid is directly under pressure. It opens into the chamber 27, and the inclination angle α of each conical surface is slightly larger than the friction angle between the conical surfaces A and I that contact each other, and is tightened in the axial direction of the outer rings 16 and 17. axially adjustable stops 24, 41, 4 whose position is held by the outer ring 17;
A joint for connecting two mechanical parts in a manner that they cannot rotate relative to each other by frictional force, characterized in that the joint can be secured using the joints 2 and 43. 2 Both pressure rings 13a, 14a; 13b,
2. A joint according to claim 1, wherein 14b; 13c, 14c are brought into contact with each other in the region of a small cone diameter. 3. The outer ring 17 forming the piston has an external thread 22 on the outer circumferential surface of the extension of its piston area for receiving a sleeve nut 24 which is threadably adjustable in the axial direction relative to the annular shoulder 19. The joint according to claim 1. 4 Both pressure rings 13a, 14a; 13c,
The joint according to claim 1, wherein the parts 14c are threadedly connected to each other. 5. Coupling according to claim 1, in which both pressure rings 13c, 14c are screwed together in a coupling ring. 6. Coupling according to claim 1, in which both pressure rings are screwed together on a coupling ring. 7 Both pressure rings 13b and 14b are connected to the boss 11
2. A joint according to claim 1, wherein the joint is axially fixed relative to one another between a shoulder formed by a shoulder 33 and a member 35 screwed onto the boss 11. 8. The outer ring 17 forming the piston forms a ring-shaped support shoulder 40 on the outer periphery of the extension of its piston area, and between this support shoulder and the ring-shaped shoulder 19 there are at least two sections. 2. The joint according to claim 1, wherein a shim 41 consisting of: 9. One of the outer rings 17 is penetrated by axial holes 45 distributed over its circumference, which axial holes form respectively a smooth inner wall section and an internally threaded section, and each of said axes Directional hole 4
5 is penetrated by a screw 42 having an external thread area and a smooth outer circumferential area with a ring seal 47, one end of which screws into the adjacent outer ring 1.
6. The joint according to claim 1, which is supported on the end face of the joint. 10 One of the outer rings 17 is penetrated by an axial internal threaded hole distributed over the circumference, in which a screw 43 is received, one end of which is adjacent ( corresponding) is supported on the end face of the outer ring 16, and each of said internal threaded holes is arranged between the pressure ring 13a, 14a and the area forming the ring-shaped piston of the additional outer ring 17 The joint according to claim 1. 11 Two axis journals 10 that coincide with each other
For the relative rotationally fixed connection of a, 10b, an approximately cylindrical connecting sleeve 12 is provided which surrounds both axle journals 10a, 10b and which extends in the area of each axle journal 10a, 10b. 2. A joint according to claim 1, each having two pressure rings 13c, 14c and a corresponding outer ring 16, 17 clamped to the pressure rings. 12 radial center plane y of coupling sleeve 12
Two pressure rings 13c are provided on either side of the pressure ring 13c arranged approximately in the shape of a house with respect to each other on the outer conical surface A, and an additional pressure ring 14c is inclined upwardly in the opposite direction. 12. A joint according to claim 11, which is connected with an outer conical surface A and is attached directly or indirectly to a connecting sleeve. 13 Radial center plane y of the connecting sleeve 12
12. A joint as claimed in claim 11, characterized in that the pressure rings (13c) arranged on both sides of the connecting sleeve (12) and arranged substantially in the shape of a horn with respect to each other are formed integrally with the connecting sleeve (12) and of the same material. 14. Coupling according to claim 11, in which an additional pressure ring (14c) is attached to the connecting sleeve (12) by means of a screw (37). 15. Coupling according to claim 11, in which an additional pressure ring 14c is connected to the connecting sleeve 12 by a shrink fit.