DE202019003203U1 - Isolation overload clutch with modular design - Google Patents

Abstract

Positive lock-in clutch with re-engagement by external application of force, consisting of an element flange (1) and a bearing (3) rotatably mounted pressure flange (2), wherein the disconnect clutch on a pitch circle of the element flange (1) arranged stepped bores (5), which coaxial arranged on the pressure flange (2), wherein the stepped bores (5) have a transmission region (6) and a receiving region (7), wherein in at least one of the stepped bores (5) a bolt (9), a support disk ( 14), a group of switching segments (16) or switching balls (17), a thrust washer (15), spring elements (18) and an adjusting nut (19) is accommodated, wherein at least in this stepped bore (5) concentrically opposite entraining opening (22) a pressure piece (23) with a recess (24) is received, wherein the at least one bolt (9) by the force of the spring elements (18) in the A recess (24) of the at least one pressure piece (23) is pressed and thereby transmits a torque, characterized in that at least one of the stepped holes (5) is introduced directly into the element flange (1) and forms a one-piece geometry with this.

Description

In the field of industrial drive technology, mechanical overload clutches have become established as reliable machine elements for avoiding damage due to excessive torques.

In particular, the design with force-loaded form-fitting transmission elements is characterized by a high precision in terms of the triggering torque.

• - Durchrast-Überlastkupplungen für einfachere Antriebe.
• - Synchron-Überlastkupplungen mit winkelgetreuer Wiedereinrastung.
• - Freischalt-Überlastkupplungen mit Wiedereinrastung durch Drehrichtungsumkehr.
• - Freischalt-Überlastkupplungen mit Wiedereinrastung durch äußere Kraftbeaufschlagung.

Depending on the technical requirements, different functional concepts can be found in the case of force-loaded mechanical overload clutches working in a positive manner:

• - Snap-through overload clutches for simpler drives.
• - Synchronous overload clutches with full scale re-engagement.
• - Unlock overload clutches with re-engagement by reversing the direction of rotation.
• - Unlock overload clutches with re-engagement by external application of force.

The subject of the invention presented here is a technical improvement for the latter concept of unlocking overload clutches with Wiederereinrastung by external application of force.

Unlocking overload clutches with re-engagement by external application of force are known from the prior art, in which release elements are integrated with associated pressure pieces in a simple construction of two mutually rotatable flanges. Such release elements or such release overload clutches with Wiedereinrastung by external application of force, hereinafter referred to as disconnect couplings, are in EP0156993B1 the applicant described.

Unlocking couplings according to the teaching of EP0156993B1 have the advantage that the unlocking elements used with their element housings can be combined well with existing designs. The disadvantage of this is the high cost and the usually large space requirement by the functional division of the coupling in two areas: A first area consisting of the mutually supported flanges and a second area consisting of arranged on a pitch circle preferably bolted unlocking elements and pressure pieces.

Accordingly, the present invention has for its object to present a possible largely modular design disconnect clutch, which allows a compact design with high power density and which is inexpensive to produce.

To solve this problem, it is proposed to construct the disconnect clutch from an element flange and a concentrically arranged and rotatably mounted pressure flange to this.

The element housings of the release elements of the prior art are integrated into the element flange of the coupling. For this purpose, the internal geometry of the previous element housing is introduced into the element flange in the form of axially or radially directed stepped bores.

In the stepped bores of the element flange torque-transmitting functional parts of the disconnect clutch are incorporated, which are formed by a bolt, a thrust washer, a support disc, a plurality of switching segments or balls, a spring element and an adjusting ring. The spring element may consist of one or more bolts concentrically arranged to the coil springs or a package of layered disc springs.

In the pressure flange coaxial with the stepped holes of the element flange driving openings are introduced, in which pressure pieces are mounted.

The stepped bores and the entrainment openings can be arranged in an advantageous manner at equal angular intervals on a pitch circle.

To adapt the disconnect clutch to the torque to be transmitted, it is possible to equip only a portion of the stepped holes and the entrainment openings with bolts or thrust pieces and to close the unneeded stepped holes, for example, with lids.

Another way to adapt the disconnect clutch to the torque to be transmitted, is to change the bias of the spring elements. For this purpose, the adjusting rings can be designed as adjusting nuts with external threads whose axial position in the provided with corresponding internal threads stepped bores is variable by turning.

The adjusting nuts can be secured against unintentional rotation by frictionally or positively acting elements.

The disconnect clutch transmits the torque from the element flange to the pressure flange by the bolts of the element flange are pressed by the spring elements via pressure plates, support discs and switching segments or balls in the preferably conically shaped recesses of the embedded in driving openings of the pressure flange pressure pieces.

When disengaging the disconnect clutch acting through the torque on the bolts and the thrust pieces circumferential force exceeds a defined by the bias of the spring elements level.

The bolts thus move axially out of the recesses of the pressure pieces and release the rotation between the element flange and the pressure flange.

Due to the special geometric design and arrangement of bolts, thrust washers, support disks, switching segments or balls and spring elements, the bolts remain in their position out of engagement with the pressure pieces and the disconnect clutch can leak without further contact between the bolts and the pressure pieces.

The disengaged or latched state of the disconnect clutch can be detected by a sensor that detects the position of the bolts in the element flange. This detection can be further improved if the bolts are provided with a common indexing disk, whose axial position is then interrogated to the element flange.

To re-engage the disconnect clutch with stationary drive element flange and pressure flange are rotated to each other so that the center axes of the bolts and the pressure pads are aligned.

Then the bolts can be brought by external application of force in the direction of the pressure pieces again in positive engagement with the recesses of the plungers.

To facilitate the alignment of the center axes of bolts and thrust pieces, well-visible index holes or other markings may be provided on the outer circumference of the element flange and pressure flange.

By briefly described here construction and function, a disconnect clutch can be provided, which can transmit high torques in a compact design.

Furthermore, a high degree of modularity and adaptability of the disconnect clutch to required torques can be achieved by integrating the stepped bores in the element flange.

In addition, the disconnect clutch according to the invention allows a simple and reliable detection of the operating state and is very inexpensive to produce.

Further features and advantageous details of the disconnect clutch according to the invention will become apparent from the descriptions of the preferred embodiments shown below.

In this case, in terms of their function matching components in all figures with the same reference numerals.

It goes without saying that the invention is not limited to the feature combinations of the claims or the description.

For the skilled person from the task further meaningful combinations of claims and / or features of the claims and / or the description and / or features of the figures shown.

• 1 einen Längsschnitt A-A und einen Querschnitt B-B durch eine erste erfindungsgemäße axiale Freischaltkupplung mit axial gerichteten Stufenbohrungen im eingerasteten Zustand als Flanschausführung
• 2 eine Detailansicht C als Halbschnitt und eine Detailansicht D der erfindungsgemäßen axialen Freischaltkupplung mit axial gerichteten Stufenbohrungen aus 1
• 3 einen Längsschnitt C-C durch eine zweite erfindungsgemäße axiale Freischaltkupplung mit axial gerichteten Stufenbohrungen im ausgerasteten Zustand, kombiniert mit einer Elastomerkupplung
• 4 eine Detailansicht E der erfindungsgemäßen axialen Freischaltkupplung mit axial gerichteten Stufenbohrungen aus 3 sowie eine durch Projektion aus der Detailansicht E abgeleitete Detailansicht F
• 5 einen Längsschnitt D-D durch eine dritte erfindungsgemäße axiale Freischaltkupplung mit axial gerichteten Stufenbohrungen im eingerasteten Zustand als Ausführung für Hohlwellenmotoren
• 6 einen Längsschnitt E-E durch eine vierte erfindungsgemäße radiale Freischaltkupplung mit radial gerichteten Stufenbohrungen im eingerasteten Zustand, kombiniert mit einer drehsteifen Ganzstahlkupplung.

Show it:

• 1 a longitudinal section AA and a cross section BB by a first inventive axial disconnect clutch with axially directed stepped holes in the engaged state as a flange design
• 2 a detailed view C as half section and a detail view D the axial disconnect clutch according to the invention with axially directed stepped holes 1
• 3 a longitudinal section CC by a second inventive axial disconnect clutch with axially directed stepped holes in the disengaged state, combined with an elastomer coupling
• 4 a detailed view e the axial disconnect clutch according to the invention with axially directed stepped holes 3 and one by projection from the detail view e derived detail view F
• 5 a longitudinal section DD by a third inventive axial disconnect clutch with axially directed stepped holes in the engaged state as a design for hollow shaft motors
• 6 a longitudinal section EE by a fourth inventive radial disconnect clutch with radially directed stepped holes in the engaged state, combined with a torsionally rigid all-steel coupling.

Out 1 is the basic structure of a first axial disconnect clutch according to the invention K1 seen. Here is the element flange 1 with the pressure flange 2 over camp 3 connected and around the axis of rotation R rotatable to the pressure flange 2 stored.

On a to the axis of rotation R concentric circle of the element flange 1 are preferably at equal angular intervals more axially directed stepped holes 5 brought in.

At the pressure flange 2 stand the stepped holes 5 corresponding entrainment openings 22 opposite, in which plungers 23 preferably with conical recesses 24 are included, wherein the central axes of stepped bores 5 and recesses 24 aligned. Here are the plungers 23 by fixing screws 25 in the entrainment openings 22 of the pressure flange 2 attached.

There are only two of the four stepped holes in this example 5 used for torque transmission, the other two stepped holes 5 are through cap 27 locked.

The stepped holes 5 of the element flange 1 consist of a transmission area 6 and a recording area 7 , where the receiving area 7 has a larger diameter than the transmission area 6 ,

Out 1 and in particular 2 with detail D can be seen as in the stepped holes 5 starting from the pressure piece 23 one each with a transmission ball 13 equipped bolt 9 , a support disk 14 , Switching segments 16 , a pressure washer 15 , a spring element 18 in the form of a plate spring package and an adjusting nut 19 are arranged in the order named.

Alternatively to the two-part construction with transfer balls 13 equipped bolt 9 can the bolts 9 be provided at the end of one piece with a grooved ball geometry or a cone.

The torque of the coupling is from the element flange 1 on the pressure flange 2 transfer.

To ensure this, the spring elements 18 through the adjusting nut 19 axially biased and transmit their power to the pressure plate 15 ,

This will cause the switching segments 16 axially between the thrust washer provided with an inner cone 15 and the likewise having an inner cone supporting disc 14 clamped and practice through these inner tapered surfaces a radially against the bolt 9 directed force.

The switching segments 16 lie on a conical surface on the outer circumference of the bolt 9 and push this together with the in a hole of the bolt 9 embedded transmission sphere 13 in the direction of the pressure piece 23 ,

The case between the element flange 1 and the pressure flange 2 occurring and on the bearings 3 acting axial forces are by a with the pressure flange 2 bolted bearing cap 4 collected.

The adjusting nut 19 is through a locking plate 20 secured against unintentional rotation, wherein the locking plate 20 by a twelve-point hexagon shown in detail C the hexagon of the adjusting nut 19 engages positively and wherein the locking plate 20 at the same time by a locking screw 21 on the outer circumference of the element flange 1 is attached. This constellation allows a sensitive adjustment and securing the adjusting nut 19 in increments of 30 degrees.

To the escape of lubricant into the environment and the entry of dirt into the axial disconnect clutch K1 to prevent are between element flange 1 and pressure flange 2 an outer seal 28 and between bearing caps 4 and element flange 1 an inner seal 29 arranged.

For lubrication have bolts 9 via lubrication channels 10 from the outer circumference of the element flange 1 over lubrication nipple 12 and lubrication holes 11 can be supplied with lubricant.

Exceeds this between the element flange 1 and the pressure flange 2 transmitted torque one by the force of the spring elements 18 defined value, element flange begin 1 and pressure flange 2 around the axis of rotation R to turn against each other.

It moves with a transmission ball 13 provided bolts 9 in the direction of the bolt-out direction D1 and the switching segments 16 slide from the conical surface of the bolt 9 on its outer peripheral surface, in contact with the transfer area 6 the stepped bore 5 stands. The axial disconnect clutch K1 is now in the unlocked state, the in 3 as in 4 , Detail E and detail F is shown.

The axial disconnect clutch K1 in 3 as well as in detail E and detail F corresponds to those from in terms of their function 2 , however, is for torque transmission between two shafts additionally with a clutch hub K3 on the element flange 1 and with a positive elastomer coupling K2 at the pressure flange 2 fitted.

Furthermore, the axial disconnect clutch shown has K1 in 3 and in 4 via an annular switching element 30 that made a switching ring 31 and tabs 32 exists and by means of tab screws 33 at the bolt 9 is attached.

When disengaging the axial disconnect clutch K1 complete the bolts 9 together with the switching element 30 an axial lifting movement in the bolt-out direction D1 , wherein the position of the switching element 30 through a sensor 44 can be detected and forwarded to a controller. By the signal, for example, the drive after disengaging the axial disconnect clutch K1 be shut down.

The sensor 44 may be in the form of a mechanical or non-contact switch.

After switching off the drive, the then stationary axial disconnect clutch K1 be locked again.

These are element flange 1 and pressure flange 2 so far twisted to each other that the index holes 26 and with it the bolts 9 and the pressure pieces 23 facing each other in alignment.

In this position, the bolts 9 at her the switching element 30 facing end by hammer blows or axial pressure in bolt locking direction D2 to the pressure pieces 23 moved until they are there again engaged or until the switching segments 16 again on the outer taper surfaces of the bolts 9 lie and these with a defined force to the pressure pieces 23 act on it.

The latching of the bolts 9 can be done individually or with the help of special snap-in groups and groups, wherein the switching element 30 is designed so that it is the occurring deformations of the switching ring 31 and the tabs 32 can absorb resilient. It is possible here, the latching of the bolt 9 by manual intervention or by automated devices.

Also in 5 shown axial hollow shaft clearance clutch according to the invention K4 , which was specially designed for mining applications, corresponds in terms of their function to the previous embodiments.

However, the bearing concept over the previous embodiments is reversed, the bearings 3 with their inner rings on a tubular extension of the element flange 1 sit and above it the pressure flange 2 with the pressure pieces 23 is rotatably mounted.

The on the camps 3 acting axial forces are also here by a bearing cap 4 added.

The pressure flange 2 the axial Hohlwellenfreischaltkupplung K4 is over a cone flange 35 with the hollow shaft 34 a drive, preferably an electric motor connected. It is the one with an outer cone 36 equipped conical flange 35 about one with an inner cone 38 provided with clamping screws 39 acted on clamping ring 37 frictionally engaged on the cylindrical peripheral surface of the hollow shaft 34 clamped.

Alternatively, the peripheral surface of the hollow shaft 34 be formed by an external toothing, in which case the conical flange 35 has a corresponding internal toothing and also by a clamping ring 37 free of play on the hollow shaft 34 can be attached.

The element flange 1 has on its inner diameter via an axial toothing, which with a toothed shaft 40 is in positive connection, wherein the toothed shaft 40 with its shaft radially inside the hollow shaft 34 lies and axially passes through them.

The toothed shaft 40 is by a pull-off screw 43 with a retaining flange 41 connected and secured against axial movement, wherein the retaining flange 41 with retaining screws 42 is fixed in the element flange.

The torque transmission with activated drive runs from the hollow shaft 34 of the drive via the cone flange 35 , the pressure flange 2 , the pressure pieces 23 , the transmission balls 13 , bolts 9 , the transmission area 6 the stepped bore 5 and the element flange 1 to the toothed shaft 40 that drives the torque through the hollow shaft 34 through to one on the other side of the hollow shaft 34 forward output. This output can be formed for example by a gear, preferably a planetary gear.

The basis 5 described axial Hohlwellenfreischaltkupplung K4 has the advantage of being at the free end of the hollow shaft 34 is therefore easily accessible for maintenance and can be easily replaced during regular service work.

6 shows as a last embodiment, a radial disconnect clutch K5 coming from one element flange 1 and a pressure flange 2 exists, in which case the element flange 1 radially outside the pressure flange 2 concentric to this and arranged by bearings 3 is rotatably mounted opposite this.

The radially inner pressure flange 2 has one to the rotation axis R concentric bore 45 for direct attachment to a drive shaft.

In contrast to the previously described examples are the stepped holes 5 in the element flange 1 arranged radially and the bolts 9 are in positive connection with the radially inside in Mitnehmeröffnungen 22 of the pressure flange 2 lying pressure pieces 23 , At the same time have bolts 9 via a one-piece spherical or conical geometry, with which they are in contact with the pressure pieces 23 stand.

Bolts 9 be in this example by spring elements 18 , Pressure washers 15 , Switching balls 17 and support disks 14 in the recesses 24 the pressure pieces 23 pressed, the biasing forces of the spring elements 18 through adjusting nuts 19 can be applied and changed. In this example, the adjustment nuts 19 constructed in two parts and are frictionally engaged in the internal threads by axial spreading apart of the two disc-shaped halves 8th the stepped holes 5 clamped.

The illustrated radial disconnect clutch K5 is used for torque transmission between two shafts, the element flange 1 with a torsionally rigid elastic all-steel coupling K6 connected is. Special advantages of the radial disconnect clutch K5 are the small axial length and the avoidance of forces on the bearings 3 because that's between the bolts 9 and pressure pieces 23 effective forces over the circumference of the radial disconnect clutch K5 cancel.

This allows smaller bearings 3 are used with lower load ratings, allowing for more compact designs and further reducing costs.

Further advantageous features of the invention will become apparent from the following independent and dependent claims.

LIST OF REFERENCE NUMBERS

1

element flange

2

pressure flange

3

camp

4

bearing cap

5

stepped bore

6

Frequency response

7

reception area

8th

inner thread

9

bolt

10

lubrication channel

11

lubrication hole

12

grease nipple

13

transmission ball

14

support disc

15

thrust washer

16

switching segment

17

switching ball

18

spring element

19

adjusting

20

Locking plate

21

locking screw

22

driving opening

23

Pressure piece

24

Recess of the pressure piece

25

Fixing screw of the pressure piece

26

index hole

27

cap

28

Outer sealing ring

29

Inner sealing ring

30

switching element

31

switching ring

32

flap

33

Lasch screw

34

hollow shaft

35

Konusflansch

36

outer cone

37

clamping ring

38

inner cone

39

clamping screw

40

splined shaft

41

retaining flange

42

retention screw

43

Extractor

44

sensor

45

drilling

D1

Bolt Ausrastrichtung

D2

Bolt locking direction

K1

Axial disconnect clutch

K2

elastomer coupling

K3

clutch

K4

Axial hollow shaft disconnect clutch

K5

Radial disconnect clutch

K6

Steel coupling

R

axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 0156993 B1 [0005, 0006]

Claims (12)

Positive lock-in clutch with re-engagement by external application of force, consisting of an element flange (1) and a bearing (3) rotatably mounted pressure flange (2), wherein the disconnect clutch on a pitch circle of the element flange (1) arranged stepped bores (5), which coaxial arranged on the pressure flange (2), wherein the stepped bores (5) have a transmission region (6) and a receiving region (7), wherein in at least one of the stepped bores (5) a bolt (9), a support disk ( 14), a group of switching segments (16) or switching balls (17), a thrust washer (15), spring elements (18) and an adjusting nut (19) is accommodated, wherein at least in this stepped bore (5) concentrically opposite entraining opening (22) a pressure piece (23) with a recess (24) is received, wherein the at least one bolt (9) by the force of the spring elements (18) in the recess (24) of the at least one pressure piece (23) is pressed and thereby transmits a torque, characterized in that at least one of the stepped holes (5) is introduced directly into the element flange (1) and forms a one-piece geometry with this. Unlocking after Claim 1 , characterized in that the at least one stepped bore (5) on the element flange (1) is arranged on a pitch circle, wherein the central axis of the at least one stepped bore (5) with the rotation axis (R) forms an angle of zero angular degree. Unlocking after Claim 1 , characterized in that the at least one stepped bore (5) on the element flange (1) is arranged on a pitch circle, wherein the central axis of the at least one stepped bore (5) with the rotation axis (R) forms an angle of ninety degrees. Unlocking after Claim 1 , characterized in that the at least one stepped bore (5) on the element flange (1) is arranged on a pitch circle, wherein the central axis of the at least one stepped bore (5) with the rotation axis (R) forms an angle between zero angular degree and ninety degree angle. Unlocking clutch according to at least one of the preceding claims, characterized in that the at least one bolt (9) at its the pressure piece (23) facing the end with a transmission ball (13) is fitted. Unlocking clutch according to at least one of the preceding claims, characterized in that the at least one bolt (9) at its the pressure piece (23) facing end is integrally equipped with a spherical or conical transfer geometry. Unlocking clutch according to at least one of the preceding claims, characterized in that the disconnect clutch has at least two bolts (9) and that the bolts (9) are connected at their the pressure piece (23) facing away from the ends with an annular switching element (30), the a switching ring (31) and tabs (32) and its axial position can be queried by a sensor (44). Unlocking clutch according to at least one of the preceding claims, characterized in that the bias of the spring elements (18) by adjusting nuts (19) is variable, which are arranged adjustably in internal threads (8) of the stepped bores (5). Unlocking coupling according to at least one of the preceding claims, characterized in that the adjusting nuts (19) on the element flange (1) by friction or by locking plates (20) and locking screws (21) are positively secured against unintentional rotation. Unlocking coupling according to at least one of the preceding claims, characterized in that only part of the stepped bores (5) of the element flange (1) is equipped with torque-transmitting components and the other part of the stepped bores (5) is closed with closure lids (27). Unlocking coupling according to at least one of the preceding claims, characterized in that the pressure flange (2) via a conical flange (35) is torque-transmitting connected to the hollow shaft (34) of a drive, wherein the element flange (1) via its axial internal toothing torque transmitting with a Toothed shaft (40) is connected, which passes the torque through the hollow shaft (34) on the side facing away from the disconnect clutch of the hollow shaft (34) to an output, preferably to a transmission. Unlocking coupling according to at least one of the preceding claims, characterized in that the pressure flange (2) via a conical flange (35) without play with the hollow shaft (34) is connected to a drive, said provided with an outer cone (36) conical flange (35) with a an inner cone (38) having clamping ring (37) is operatively connected and clamped by clamping screws (39) on the hollow shaft (34).

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