Source: https://patents.google.com/patent/DE102015111809A1/en
Timestamp: 2020-01-20 01:49:29
Document Index: 777979622

Matched Legal Cases: ['art 17', 'art 24', 'art 17', 'art 17', 'art 24', 'art 17', 'art 15', 'art 15', 'art 17', 'art 15', 'art 24', 'art 24', 'art 17', 'art 17', 'art 31', 'art 32', 'arts 31', 'art 28']

DE102015111809A1 - jig - Google Patents
DE102015111809A1
DE102015111809A1 DE102015111809.2A DE102015111809A DE102015111809A1 DE 102015111809 A1 DE102015111809 A1 DE 102015111809A1 DE 102015111809 A DE102015111809 A DE 102015111809A DE 102015111809 A1 DE102015111809 A1 DE 102015111809A1
DE102015111809.2A
2015-07-21 Application filed by MUHR & BENDER KG, Muhr und Bender KG filed Critical MUHR & BENDER KG
2017-01-26 Publication of DE102015111809A1 publication Critical patent/DE102015111809A1/en
The invention relates to a tensioning device for a traction device, comprising: a receiving housing (3); a roller support (4) pivotally connected to the receptacle housing (3); a helical tension spring (6) which is supported on the receiving housing (3) and the roller carrier (4) in the circumferential direction and in the axial direction, wherein the roller carrier (4) and the receiving housing (3) by means of the helical tension spring (6) fixed axially against each other are; a bearing arrangement (5), with which the roller carrier (4) in the receiving housing (3) is rotatably mounted about an axis of rotation; a damping arrangement (7) for damping a rotational movement of the roller carrier (4) relative to the receiving housing (3), wherein the damping arrangement axially spaced from the bearing assembly (5) is arranged and is acted upon by tensile loading of the helical tension spring (6) axially.
The invention relates to a tensioning device for a traction mechanism drive, such as a belt or chain drive. A traction drive usually comprises an endless traction means such as a belt or a chain and at least two discs, one of which can act as a drive and as an output of the traction mechanism. Such traction drives are used, for example, in internal combustion engines of a motor vehicle for driving ancillaries, wherein a first disc is seated on the crankshaft of the internal combustion engine and drives the belt.
Further drive pulleys are assigned to the auxiliary units, such as water pump, alternator or air conditioning compressor, and are driven in rotation by the traction mechanism. In conventional traction drives the ancillaries are designed as consumers, that is, they are driven by the pulley of the crankshaft via the belt. In this case, the Lostrum is formed between the crankshaft and in the circumferential direction of the traction device adjacent aggregate, usually the generator. In order to ensure a sufficient wrap around the traction means around the drive pulley, the belt is biased by means of a tension roller of the tensioning device.
From the EP 1 277 989 A2 a belt tensioning device with a mounting housing and a pivotally connected thereto roller carrier is known. The roller carrier is mounted relative to the mounting housing with a bearing radially and axially and biased with a loaded on train coil spring with respect to this. The roller carrier is thus axially fixed on the mounting housing via the bearing and the coil spring. It is provided a damping device which dampens movements between the roller carrier and the mounting housing such that the damping in the direction of increasing clamping force is greater than in the direction of decreasing clamping force. The damping device has a damping bushing and a band spring, which is fastened with its first end in a rotationally fixed manner to the fastening housing or on the roller carrier and is secured with its second end in a rotationally fixed manner to the damping bushing.
From the DE 196 03 558 C2 a belt tensioning device with a receiving housing, a pivotally connected thereto roller carrier and a bearing and damping device is known. The bearing and damping device comprises a bearing and damping cone, which is biased by a coil spring to train and torsion.
From the EP 0 858 563 B1 a tensioning device for a traction means is known which comprises a housing and a relative to the housing by means of a sliding bearing rotatably mounted clamping arm. The sliding bearing surfaces of the sliding bearing are designed as conical surfaces parallel to each other and concentric with the clamping arm axis. It is a helical spring supported between a support on the clamping arm and a support on the housing with which a torsional bias and an axial bias are applied in the installed state. In this case, an axial force of the helical torsion spring is introduced as a reaction force acting perpendicular to the slide bearing surfaces in the slide bearing, so that the slide bearing surfaces are pressed against each other under the axial force.
Clamping devices with cylindrical damping systems are relatively complex and therefore expensive in terms of manufacturing and assembly. Tensioners with conical damping systems are more susceptible to an undesired obliquity of the clamping arm relative to the housing.
The present invention has for its object to provide a tensioning device for a traction mechanism, which is simple and inexpensive and has a long life.
A solution consists in a tensioning device for a traction means, comprising: a receiving housing; a roller carrier, which is pivotally connected to the receiving housing; a Schraubenzugfeder which is supported on the receiving housing and the roller carrier in each case in the circumferential direction and in the axial direction, wherein the roller carrier and the receiving housing are axially fixed by means of the helical tension spring; a bearing arrangement with which the roller carrier is rotatably mounted in the receiving housing about a rotation axis; a damping arrangement for damping a rotational movement of the roller carrier relative to the receiving housing, wherein the damping arrangement is arranged axially spaced from the bearing assembly and is acted upon axially by tensile loading of the Schraubenzugfeder.
An advantage of the tensioning device is that the roller carrier is securely supported relative to the receiving housing due to the axial distance between the bearing assembly and the damping arrangement against transverse forces. The risk of unwanted tilting of the roller carrier relative to the receiving housing and thus increased wear is minimized. At the same time, the coil spring acts as a tension spring, which acts on the roller carrier in the direction of the receiving housing axially. In other words, the roller carrier and the receiving housing of the Coil spring axially pulled towards each other. The coil spring is supported on the receiving housing and on the roller carrier in opposite directions of rotation. During a pivoting movement of the clamping arm against the circumferentially acting supporting force of the receiving housing, the coil spring is radially expanded, wherein the coil spring is increasingly loaded with increasing radial expansion to train. Thus, an increasing pivoting of the roller carrier relative to the receiving housing to an increasing axial force between said components toward each other, so that the friction torque of the damping assembly increases due to the increasing axial force and thus the damping accordingly. The damping rate is thus functionally dependent on the degree of pivotal movement, which has a favorable overall effect on the damping behavior.
The tensioning device is used for tensioning a traction means of a traction mechanism drive. The traction means may be a belt for a belt drive, wherein the tensioning device would then be a belt tensioning device. But it is also conceivable that the traction means is a chain for a chain drive, which is biased by the tensioning device accordingly.
It is envisaged that the receiving housing can be connected to a stationary component, for example to the engine block of a motor vehicle or to a component connected thereto. For this purpose, the receiving housing has corresponding fastening means, for example for a screw connection. The receiving housing may be cup-shaped with a bottom and a skirt portion within which a receiving space for the roller carrier and the coil spring is formed.
The roller carrier is configured to carry a roller for applying the traction means. For this purpose, the roller carrier has an arm portion on which the roller is rotatably mounted about a roller axis parallel to the pivot axis. In this respect, the roller carrier can also be referred to as a tensioning arm and the role as tensioning roller. The roller carrier can be produced as a casting, for example from a light metal made of aluminum or an aluminum alloy, in particular by way of a die-casting process. This applies equally to the receiving housing.
According to one embodiment, it is provided that the bearing arrangement has a mean bearing diameter which is smaller than a mean diameter of the damping arrangement. In this case, mean diameter means in each case the average diameter between a largest diameter and a smallest diameter of the respective arrangement.
The bearing assembly may comprise a bearing bush which is arranged between a bearing part of the receiving housing and a bearing part of the roller carrier. The bearing bush is designed in particular substantially cylindrical, which should be included with the possibility that the bearing bush has a slightly conical surface of up to 3 ° relative to the pivot axis. By a slightly conical configuration, the corresponding parts can be easily removed from the mold during manufacture. If the bearing assembly is slightly conical, it tapers towards the bottom of the receiving housing. The bearing part of the receiving housing may be designed in the form of a bearing sleeve. In this case, the bearing part of the roller carrier is designed in the form of a bearing pin which is inserted into the bearing sleeve of the receiving housing with the interposition of the bearing bush. The bearing pin can be integrally formed or cast on a hub part of the roller carrier. Alternatively, the bearing pin can also be made as a separate component and pressed or injected into the hub part. As a bearing material for the bearing bush, for example, suitable plastics or coated with friction-reducing material such as PTFE steel bushings can be used. The bushing and the damping bushing can be made of different materials, wherein the damping bush is designed in this case of a material with a higher coefficient of friction than the bearing bush. It is for the design of the bearing assembly in principle, the kinematic reversal conceivable, that is, that the bearing part of the roller carrier is designed as a bearing sleeve. In this case, the bearing pin would be provided at the bottom of the receiving housing.
According to a possible embodiment, a support-free intermediate space is formed axially between the bearing arrangement and the damping arrangement, in which no support of lateral forces introduced via the roller carrier is given by the receiving housing. In other words, the support of the lateral forces introduced by the tensioning roller into the roller carrier takes place solely through the bearing arrangement and the damping arrangement axially spaced therefrom. Preferably, an axial length of the support-free gap is greater than the axial length of the bearing assembly and / or as the axial length of the damping assembly. In this way, a particularly good support against lateral forces.
It is provided in particular that the damping arrangement has at least one friction surface pairing, which is acted upon axially by a tensile force of the helical tension spring. The friction surface pairing can in principle be conical or designed as a radial surface pairing. By acting on the Reibflächenpaarung axial force arises a friction torque, so that a relative rotational movement of the roller carrier relative to the receiving housing is damped. If the friction surface pairing comprises a conical friction surface, provision is made in particular for a cone angle enclosed by the pivot axis to be larger than an angle enclosed between the outer bearing surface of the bearing bush and the pivot axis. About the size of the cone angle, the height of the friction torque and thus the degree of damping of the clamping device can be adjusted. For example, the cone angle can be between 3 ° and 10 °.
In concrete terms, the damping arrangement may comprise a damping bush, which is arranged between an inner conical surface of the receiving housing and an outer annular surface of the roller carrier. The damping bushing preferably has an outer conical friction surface which is in frictional contact with the inner cone surface of the receiving housing. The conical friction surface of the damping bushing and the inner conical surface of the receiving housing form a friction surface pairing of the damping arrangement. A second Reibflächenpaarung can between an outer annular surface of the roller carrier and an inner surface of the bearing bush, which are designed to be the same and in particular cylindrical or conical. Due to the indirect friction surface contact between the receiving housing and the roller carrier by means of the damping bushing, the damping arrangement at the same time also has a radial and axial bearing function between the housing and the carrier. In this respect, the damping arrangement can also be referred to as a combined damping and bearing arrangement.
According to one embodiment, the roller carrier may comprise a hub element and a ring element, wherein the ring element surrounds the hub element radially on the outside and forms the outer annular surface for receiving the damping bush, wherein an annular space is formed between the hub element and the ring element, in which a portion of the coil spring is arranged , In particular, it is provided that hub element and ring element are made in one piece, for example as a cast component, and insofar can also be referred to as a hub portion and ring portion of the roller carrier. The outer ring surface of the ring element may be cylindrical or conical.
According to a preferred embodiment, the coil spring has a first end portion which is supported in the screwed state on the receiving housing in the circumferential direction and in the axial direction, and a second end portion which is supported in the screwed state on the roller carrier in the circumferential direction and in the axial direction.
For axial and rotational support of the coil spring relative to the receiving housing can be provided that the receiving housing has a bottom with thread-like engagement means and a stop at the end of the thread-like engagement means. In this case, the thread-like engagement means are designed so that the coil spring can be screwed into the thread-like engagement means until reaching the stop. In this way, a simple axial fixation and a fixation in the circumferential direction is realized. Separate fasteners are therefore not required.
The same applies to the second end of the coil spring. For this purpose, the roller carrier in a cover portion having thread-like engagement means and a stop at the end of the thread-like engagement means. After insertion of the coil spring in the receiving housing and engage with the engaging means of the roller carrier can be placed on the receiving housing. In this case, the second end portion of the coil spring can be brought into engagement with the thread-like engaging means of the lid by a plugging and rotary movement of the roller carrier relative to the receiving housing. By rotating the roller carrier relative to the coil spring, the second spring end engages increasingly in the thread-like engagement means, wherein the coil spring is axially biased to train.
In fully assembled state, the roller carrier and the receiving housing are axially fixed to each other and axially biased. The coil spring thus fulfills several functions, namely a resilient support of the roller carrier relative to the housing in the direction of rotation, an axial fixation of the roller carrier on the housing, and an axial loading of the friction surface pairing of the damping arrangement. Separate fastening means for connecting the carrier to the housing are not required, so that the clamping device comprises particularly few parts and is simple and inexpensive to produce. Another advantage is that with increasing pivoting of the roller carrier relative to the receiving housing an increasing tensile force from the coil spring acts on the roller carrier toward the housing. That is, the degree of damping of the tensioning device is dependent on the deflection of the roller carrier.
The thread-like engagement means on the receiving housing and the roller carrier may be designed in the form of a thread-like channel, which may be formed by a plurality of webs distributed over the circumference.
1 a clamping device according to the invention in a first embodiment in a perspective exploded view;
2 the tensioning device according to 1 in longitudinal section; and
3 the clamping device according to the invention in a slightly modified second embodiment in an exploded view in side view;
4 the tensioning device according to 3 in longitudinal section; and
5 the receiving housing of the clamping device according to the 3 and 4 in perspective, partially cut.
The 1 and 2 , which will be described together below, show a clamping device according to the invention 2 , The tensioning device is designed for tensioning an endless belt of a belt drive (not shown) and can accordingly also be referred to as a belt tensioning device. It is understood that the tensioning device 2 can also be used or designed for tensioning a chain drive. The belt tensioning device 2 includes a receiving housing 3 , a roller carrier 4 that relative to the receiving housing 3 by means of a bearing arrangement 5 and by means of a damping arrangement 7 is mounted damping around a pivot axis A, and a coil spring 6 with which the roller carrier 4 opposite the receiving housing 3 is resiliently supported in the axial direction and in the circumferential direction. The receiving housing 3 can be attached to a stationary component such as an engine or engine block (not shown) or a component connected thereto. For fastening the receiving housing 3 this has a plurality of radially outwardly projecting mounting portions 36 with holes through which screws or bolts 40 can be pushed through for attachment to the stationary component. The roller carrier 4 and the receiving housing 3 can each be made in one piece, for example as a cast component, wherein a production of a suitable plastic is basically also conceivable.
The roller carrier 4 carries at a free end portion a tension roller 9 which is rotatable about an axis of rotation B parallel to the pivot axis A. The tension roller 9 is on a journal 8th the role carrier 4 rotatably mounted and by means of a screw 13 attached to this. One of the screw 13 on the journal 8th attached and the bearing 12 covering disc 10 protects the camp 12 against the ingress of dirt. The roller carrier 4 is about the bearing assembly 5 and the damping arrangement 7 axially and radially relative to the receiving housing 3 rotatably mounted about the pivot axis A, wherein a relative rotational movement of the roller carrier 4 opposite the receiving housing 3 through in the damping arrangement 7 resulting friction moments is damped. The damping arrangement 7 is axially spaced from the bearing assembly 5 arranged and is characterized by a tensile bias of the coil spring 6 , which on the receiving housing 3 on the one hand and on the roller carrier on the other hand axially supported in opposite axial directions, axially acted upon. In this respect, the coil spring 6 Also referred to as a coil spring.
The coil spring 6 is substantially coaxial with the pivot axis A in between the receiving housing 3 and the roll carrier 4 arranged annulus arranged. The number of turns of the coil spring 6 may for example be between four and eight, and in the present case is about six, it being understood that depending on the size, spring wire diameter and application, other numbers of turns are conceivable. The ratio of length L6 of the coil spring 6 to the nominal diameter D6 may be in the installed state of the coil spring, in which the coil spring is axially biased to train, for example, between 1.0 and 2.5, in particular between 1.5 and 2.0. It is understood that the stated values are not meant to be restrictive and that said ratio of length to spring diameter in the installed state also depends, inter alia, on the wire diameter of the spring wire. The larger the wire diameter, the smaller the axial length of the coil spring can be designed.
A first end section 16 the coil spring 6 is at a bottom part 17 of the receiving housing 3 supported in the circumferential direction and in the axial direction. The opposite second end portion 23 the coil spring 6 is on a lid part 24 the role carrier 4 supported in the circumferential direction and in the axial direction. The coil spring 6 causes a tension of the roller carrier 4 opposite the receiving housing 3 , so that the belt of the belt drive is biased. At the same time is the role carrier 4 by means of the coil spring 6 on the housing 3 axially fixed.
For axial support of the coil spring 6 opposite the receiving housing 3 are at the bottom part 17 the receiving housing thread-like engaging means 18 provided, which are designed so that the coil spring 6 can be screwed in here. The intervention means 18 comprise a plurality of distributed over the circumference and relative to each other axially offset webs 19 which of the first end section 16 the coil spring 6 be engaged behind when screwing in. The webs form 19 an overall thread-like channel whose pitch approximately the slope of the first end portion 16 the coil spring 6 equivalent. At the end of the thread-like channel has the bottom part 17 a stop 20 with which the spring end comes in contact so that the coil spring 6 on the housing 3 is supported in a first direction of rotation. By engaging or screwing in the end section 16 in the von der Stegen 19 formed channel, is the coil spring 6 at the jetties 19 axially supported in both axial directions, that is, on pressure and in particular on train.
The opposite second end portion 23 the coil spring 6 is accordingly at the roll carrier 4 supported in opposite second axial direction and opposite second direction of rotation. For this the roller carrier has 4 in the lid section 24 corresponding thread-like engaging means 25 and a stop 26 at the end of the thread-like engaging means 25 , After inserting and screwing in the coil spring 6 in the receiving housing 3 becomes the role carrier 4 on the receiving housing 3 placed. By a subsequent rotation of the roller carrier 4 relative to the housing 3 in the direction of rotation in which the coil spring 6 on the housing 3 is supported, the second end portion 23 the feather 6 in the thread-like engaging means 25 the lid section 24 engaged. With increasing twisting of the roll carrier 4 opposite the coil spring 6 engages the second end section 23 increasingly in the thread-like intervention means 25 one, the coil spring 6 is biased axially on train. The intervention means 25 of the lid part 24 are designed according to the engagement means on the bottom part and comprise a plurality of distributed over the circumference and relative to each other axially offset webs 27 that of the second end portion 23 the coil spring 6 be engaged behind when screwing in. The webs form 27 an overall thread-like channel whose pitch approximately the slope of the second end portion 16 the coil spring 6 equivalent.
In fully assembled condition are the roller carrier 4 and the receiving housing 3 axially fixed to each other and axially biased. The coil spring 6 fulfills the function of a resilient support of the roller carrier 4 on the housing 3 in the direction of rotation, an axial fixation of the roller carrier 4 on the housing 3 , and an axial loading of the damping arrangement 7 , With increasing pivotal movement of the roller carrier 4 opposite the receiving housing 3 expands the coil spring 6 Increasingly, allowing an increasing pulling force from the coil spring 6 on the roll carrier 4 and the case 3 acts, which acts on the said parts to each other. Thus, the damping of the tensioning device increases 2 with increasing deflection of the roller carrier 4 ,
The receiving housing 3 is particularly cup-shaped and has the bottom part 17 , which may also be referred to as floor section or simply floor, and a jacket part 15 or shell section, within which a receiving space for the roller carrier 4 and the coil spring 6 is formed. At an upper portion of the shell part 15 are the attachment sections 36 integrally formed or molded. In the area of the bottom part 17 is the bearing assembly 5 and in the upper part of the shell part 15 is the damping arrangement 7 which will be discussed in more detail below.
The roller carrier 4 has the lid part 24 , further from the lid part 24 towards the bottom part 17 extending hub element 28 and a coaxial with the hub member 28 arranged ring element 29 on. The hub element 28 is in the bottom part 17 by means of the bearing arrangement 5 rotatably mounted. The ring element 29 forms part of the damping arrangement 7 , Between the hub element 28 and the ring element 29 an annular space is formed, in which an upper portion of the coil spring 6 is arranged.
The bearing arrangement 5 has a bearing bush 30 on, between a designed as a bearing sleeve first bearing part 31 of the receiving housing 3 and designed as a bearing pin second bearing part 32 the role carrier 4 is arranged. The bearing bush 30 or the bearing parts 31 . 32 are cylindrical or slightly conical, with a slightly conical design results in better mold removal during manufacture. The bearing bolt 32 is one piece on the hub part 28 the role carrier 4 molded or molded. As bearing material for the bearing bush 30 For example, a suitable plastic or a friction-reducing material such as PTFE coated steel bush may be used.
The damping arrangement 7 includes a damping bush 33 between an inner cone surface 34 of the receiving housing 3 and an outer annular surface 35 the role carrier 4 is arranged. The damping bush 33 has an outer conical friction surface 37 with the inner cone surface 34 of the receiving housing 3 is in frictional contact. The conical friction surface forms 37 the damping bush 33 and the inner cone surface 34 of the receiving housing 3 a first friction surface pairing of the damping arrangement 7 , A second friction surface pairing is between the outer ring surface 35 the role carrier 4 and an inner ring surface 38 the damping bush 33 formed, both of which are cylindrical. The damping bush 33 and thus the Reibflächenpaarungen be of the tensile force of the coil spring 6 acted upon axially, wherein a friction torque is produced, so that a relative rotational movement of the roller carrier 4 opposite the receiving housing 3 is dampened. At the same time has the damping arrangement 7 also a bearing function for the axial and radial mounting of the roller carrier 4 in the housing 3 so that it can also be referred to as a damping and bearing arrangement. The damping arrangement 7 is designed so that a maximum cone angle of at least one of the Reibflächenpaarungen, which can also be referred to as a damping angle is greater than a maximum angle, the outer surface of the bearing assembly 5 encloses with the pivot axis A.
It is especially in 2 recognizable that axially between the bearing assembly 5 and the damping arrangement 7 a support-free gap is formed. The of the tension roller 9 in the roll carrier 4 introduced transverse forces are thus solely by the bearing assembly 5 and the damping arrangement axially spaced therefrom 7 supported. The length L1 of the support-free gap is greater than the axial length L5 of the bearing assembly 5 or the length L7 of the damping arrangement 7 , so that a particularly good support of shear forces is achieved. It is further contemplated that a mean bearing diameter D5 of the bearing assembly 5 smaller than a mean diameter D7 of the damper assembly 7 , Together with the axial distance between the bearing assembly 5 and the damping arrangement 7 Thus, a good storage, centering and support against tilting moments is achieved.
The 3 to 5 , which will be described together below, show a tensioning device according to the invention 2 in a slightly modified second embodiment. The second embodiment corresponds largely in terms of structure and operation of those according to the 1 and 2 , so that reference is made to the above description in terms of similarities.
The same or corresponding components are provided with the same reference numerals as in the 1 and 2 ,
One difference is that in the embodiment according to the 3 to 5 the length L1 of the support-free gap is smaller than the axial length L5 of the bearing assembly 5 or the length L7 of the damping arrangement 7 , The structure of the clamping device according to the 3 to 5 is somewhat more compact in the axial direction, which also applies accordingly to the required space. Also the shape of the case 3 is a bit stocky. In 3 it can be seen that the damping bush 33 a structured conical friction surface 37 which also for the embodiment according to the 1 and 2 can apply. Incidentally, all details of execution according to 1 and 2 also for the modified second embodiment. In the 3 and 4 is also a locking pin 39 recognizable, which the roller carrier 4 held in a biased position and pulled after assembly of the tensioning device on the belt drive, so that the belt is biased. In 5 , which shows the housing partially cut, are the lower engagement means 18 with their circumferentially distributed bars 19 good to see which of the lower winding portion of the spring 6 be engaged so that the latter is biased to train. This described structure concerning the engaging means 18 and the locking pin 39 applies equally to the embodiment according to the 1 and 2 ,
The clamping devices according to the invention are advantageously simple and inexpensive to produce. Because of the coil spring 6 on train between the receiving housing 3 and the roll carrier 4 is installed, it takes in addition to the resilient support of said parts in the direction of rotation and an axial connection function true. By using a substantially cylindrical bearing arrangement 5 and a conical damping arrangement 7 is a good support against tilting moments allows, or a susceptibility to unwanted obliquity reduced. Another advantage is that the coil spring 6 is increasingly loaded with increasing radial expansion to train, resulting in an increasing axial force on the damping arrangement 7 and thus leads to increased damping.
first end section
second end section
conical friction surface
inner ring surface
EP 1277989 A2 [0003]
DE 19603558 C2 [0004]
EP 0858563 B1 [0005]
Tensioning device for a traction device, comprising: a receiving housing ( 3 ); a roller carrier ( 4 ), which is connected to the receiving housing ( 3 ) is pivotally connected; a helical tension spring ( 6 ) attached to the housing ( 3 ) and the roll carrier ( 4 ) is supported in the circumferential direction and in the axial direction, wherein the roller carrier ( 4 ) and the receiving housing ( 3 ) by means of the helical tension spring ( 6 ) are axially fixed against each other, a bearing assembly ( 5 ), with which the roller carrier ( 4 ) in the receiving housing ( 3 ) is rotatably mounted about a rotation axis; a damping arrangement ( 7 ) for damping a rotational movement of the roller carrier ( 4 ) relative to the housing ( 3 ), wherein the damping arrangement axially spaced from the bearing assembly ( 5 ) is arranged and by tensile loading of the coil spring ( 6 ) is acted upon axially.
Clamping device according to claim 1, characterized in that the bearing arrangement ( 5 ) has a mean bearing diameter (D5) which is smaller than a mean diameter (D7) of the damping arrangement ( 7 ).
Clamping device according to claim 1 or 2, characterized in that axially between the bearing arrangement ( 5 ) and the damping arrangement ( 7 ) a support-free gap is formed.
Clamping device according to claim 3, characterized in that an axial length (L1) of the support-free gap is greater than at least one of the axial length (L5) of the bearing assembly ( 5 ) and the axial length (L7) of the damping arrangement ( 7 ).
Clamping device according to one of claims 1 to 4, characterized in that the bearing arrangement ( 5 ) a bearing bush ( 30 ) between a bearing part ( 31 ) of the receiving housing ( 3 ) and a bearing part ( 32 ) of the roll carrier ( 4 ) is arranged, wherein the bearing bush ( 30 ) is designed substantially cylindrical.
Clamping device according to claim 5, characterized in that the bearing part ( 31 ) of the receiving housing ( 3 ) is designed in the form of a bearing sleeve and that the bearing part ( 32 ) of the roll carrier ( 4 ) is designed in the form of a bearing pin, which in the bearing sleeve of the receiving housing ( 3 ) is inserted.
Clamping device according to one of claims 1 to 6, characterized in that the damping arrangement ( 7 ) at least one friction surface pairing ( 34 . 37 ), characterized by a tensile force of the helical tension spring ( 6 ) is acted upon axially, so that a relative rotational movement of the roller carrier ( 4 ) with respect to the receiving housing ( 3 ) is dampened.
Clamping device according to one of claims 1 to 7, characterized in that the damping arrangement ( 7 ) a damping bushing ( 33 ) formed between an inner cone surface ( 34 ) of the receiving housing ( 3 ) and an outer annular surface ( 35 ) of the roll carrier ( 4 ) is arranged, wherein the damping bushing ( 33 ) an outer conical friction surface ( 37 ), which with the inner cone surface ( 34 ) of the receiving housing ( 3 ) is in frictional contact.
Clamping device according to claim 8, characterized in that the conical friction surface ( 37 ) of the damping bushing ( 33 ) is inclined more strongly relative to the axis of rotation (A) than an outer bearing surface of the bearing bush ( 30 ).
Clamping device according to one of claims 5 to 9, characterized in that the bearing bush ( 30 ) and the damping bushing ( 33 ) are made of different materials.
Clamping device according to one of claims 1 to 10, characterized in that the roller carrier ( 4 ) a hub element ( 28 ) and a ring element ( 29 ), wherein the ring element ( 29 ) the hub element ( 28 ) radially outwardly surrounds and the outer annular surface ( 35 ) for receiving the damping bushing ( 33 ), wherein between the hub member ( 28 ) and the ring element ( 29 ) an annular space is formed, in which a portion of the coil spring ( 6 ) is arranged.
Clamping device according to claim 11, characterized in that the outer annular surface ( 35 ) of the ring element ( 29 ) is cylindrical.
Clamping device according to one of claims 1 to 12, characterized in that the helical spring ( 6 ) a first end portion ( 16 ), which in the assembled state on the receiving housing ( 3 ) is supported in the circumferential direction and in the axial direction, and a second end portion ( 23 ), which in the mounted state on the roller carrier ( 4 ) is supported in the circumferential direction and in the axial direction.
Clamping device according to one of claims 1 to 13, characterized in that the receiving housing ( 3 ) a floor ( 17 ) with thread-like engaging means ( 18 ) and with a stop ( 20 ) at the end of the thread-like engaging means ( 18 ), wherein the coil spring ( 6 ) for mounting in the thread-like engaging means ( 18 ) until reaching the stop ( 20 ) can be screwed.
Clamping device according to one of claims 1 to 14, characterized in that the roller carrier ( 4 ) a lid ( 24 ) with thread-like engaging means ( 25 ) and with a stop ( 26 ) at the end of the thread-like engaging means ( 25 ), wherein the second end portion ( 23 ) of the coil spring ( 6 ) by a plug-in and rotary movement of the roller carrier ( 4 ) with respect to the receiving housing ( 3 ) with the thread-like engaging means ( 25 ) of the lid ( 24 ) is engageable.
DE102015111809.2A 2015-07-21 2015-07-21 jig Pending DE102015111809A1 (en)
PL16178714T PL3121484T3 (en) 2015-07-21 2016-07-08 Clamping device
ES16178714.8T ES2681369T3 (en) 2015-07-21 2016-07-08 tensioning device
EP16178714.8A EP3121484B1 (en) 2015-07-21 2016-07-08 Clamping device
US15/207,775 US9933051B2 (en) 2015-07-21 2016-07-12 Tensioning device
CN201610573689.6A CN106369120A (en) 2015-07-21 2016-07-20 Tensioning device
JP2016143310A JP2017026151A (en) 2015-07-21 2016-07-21 Tensioning device
DE102015111809A1 true DE102015111809A1 (en) 2017-01-26
DE102015111809.2A Pending DE102015111809A1 (en) 2015-07-21 2015-07-21 jig
DE19603558A1 (en) * 1995-12-12 1997-06-19 Muhr & Bender Belt tensioning device with accommodation housing
EP0858563B1 (en) 1995-11-02 1999-12-01 INA Wälzlager Schaeffler oHG Tensioning device for traction means with cone friction bearing
WO2003036130A1 (en) * 2001-10-24 2003-05-01 Ina-Schaeffler Kg Tensioning device
EP1812731A2 (en) * 2004-11-05 2007-08-01 Dayco Products, Llc. Belt tensioner and method for making a belt-tensioner arm and a spring case
US9377090B2 (en) * 2008-10-02 2016-06-28 Litens Automotive Partnership Compact tensioner with sustainable damping
ES2681369T3 (en) 2018-09-12
JP5620763B2 (en) 2014-11-05 Decoupler assembly
JP2005537439A (en) 2005-12-08 Auxiliary belt tension system for controlling reversible torque-loaded pulleys
DE19655377B4 (en) 2009-05-14 tensioner
US20060264280A1 (en) 2006-11-23 Isolator for alternator pulley