GB1565213A - Creation of Inventions and Patents with Artificial Intelligence

GB1565213A – Clamping chuck for a lathe
– Google Patents

GB1565213A – Clamping chuck for a lathe
– Google Patents
Clamping chuck for a lathe

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Publication number
GB1565213A

GB1565213A
GB51909/76A
GB5190976A
GB1565213A
GB 1565213 A
GB1565213 A
GB 1565213A
GB 51909/76 A
GB51909/76 A
GB 51909/76A
GB 5190976 A
GB5190976 A
GB 5190976A
GB 1565213 A
GB1565213 A
GB 1565213A
Authority
GB
United Kingdom
Prior art keywords
teeth
chuck
actuating
adjusting member
clamping chuck
Prior art date
1975-12-13
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)

Expired

Application number
GB51909/76A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

SMW Schneider and Weisshaupt GmbH

SMW Spanneinrichtungen Schneider und Weisshaupt Firma

Original Assignee
SMW Schneider and Weisshaupt GmbH
SMW Spanneinrichtungen Schneider und Weisshaupt Firma
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1975-12-13
Filing date
1976-12-13
Publication date
1980-04-16

1976-12-13
Application filed by SMW Schneider and Weisshaupt GmbH, SMW Spanneinrichtungen Schneider und Weisshaupt Firma
filed
Critical
SMW Schneider and Weisshaupt GmbH

1980-04-16
Publication of GB1565213A
publication
Critical
patent/GB1565213A/en

Status
Expired
legal-status
Critical
Current

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Classifications

B—PERFORMING OPERATIONS; TRANSPORTING

B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR

B23B—TURNING; BORING

B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control

B23B31/02—Chucks

B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means

B23B31/12—Chucks with simultaneously-acting jaws, whether or not also individually adjustable

B23B31/16—Chucks with simultaneously-acting jaws, whether or not also individually adjustable moving radially

B23B31/16045—Jaws movement actuated by screws and nuts or oblique racks

B23B31/16066—Jaws movement actuated by screws and nuts or oblique racks using fluid-pressure means to actuate the gripping means

B23B31/1607—Jaws movement actuated by screws and nuts or oblique racks using fluid-pressure means to actuate the gripping means using mechanical transmission through the spindle

Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION

Y10T279/00—Chucks or sockets

Y10T279/12—Chucks or sockets with fluid-pressure actuator

Y10T279/1208—Chucks or sockets with fluid-pressure actuator with measuring, indicating or control means

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION

Y10T279/00—Chucks or sockets

Y10T279/12—Chucks or sockets with fluid-pressure actuator

Y10T279/1274—Radially reciprocating jaws

Y10T279/1291—Fluid pressure moves jaws via mechanical connection

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION

Y10T279/00—Chucks or sockets

Y10T279/19—Radially reciprocating jaws

Y10T279/1926—Spiral cam or scroll actuated

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION

Y10T279/00—Chucks or sockets

Y10T279/19—Radially reciprocating jaws

Y10T279/1973—Wedge actuated

Description

PATENT SPECIFICATION
( 21) Application No 51909/76 ( 22) Filed 13 Dec 1976 ( 31) Convention Application No 2556227 ( 32) Filed 13 ( 33) Fed Rep of Germany (DE) ( 44) Complete Specification Published 16 Apr 1980 ( 51) INT CL 3 B 23 B 31/12 ( 52) Index at Acceptance B 3 B 2 BX 2 G 1 2 Pl 2 R B 3 T 4 A 6 ( 11) 1 565 213 ( 19) Dec 1975 in ( 54) CLAMPING CHUCK FOR A LATHE ( 71) We, SMW-SCHNEIDER & WEISSHAUPT GMBH of 28 Wiesentalstrasse, 7996 Meckenbeuren, Federal Republic of Germany, a Joint-Stock Company organised under the laws of the Federal Republic of Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the follow-
ing statement:-
This invention relates to a clamping chuck for a lathe, comprising a chuck body, a plurality of base jaws or clamping jaws which are arranged in said body for radial sliding movement and are each drivable by a respective actuating bar guided in the chuck body tangentially to the axis of rotation thereof, the actuating bars being provided with teeth by means of which said bars engage with teeth on the jaws and being slidable to such an extent as to enable the toothed bars to be brought out of engagement from the teeth of the jaws for the purpose of removing the latter from the chuck.
German Patent No 2,007,509 discloses a power-operated clamping device for lathes which is constituted by a clamping chuck at one end of a hollow spindle, the clamping jaws of which chuck are drivable by actuating bars provided with helical teeth and guided tangentially to the axis of rotation of the chuck body, and by a co-rotating pressure medium cylinder fastened to the other end of the spindle In this case the driving member of the clamping chuck is a gearwheel which is provided with helical teeth and connected through the intermediary of a rotary tube, extending through the hollow spindle, to a rotary piston of the pressure medium cylinder Thus when the rotary piston is actuated, it is rotated conjointly with the gearwheel firmly attached to it which, meshing by its teeth with the helical teeth machined on the inside of the actuating bars, displaces said bars.
This known clamping device provides the advantage to effect a rapid exchange of the clamping jaws, because the rotary piston can be brought by means of a control device into a limit position in whih the toothed actuating bars are disengaged from the teeth of the jaws However, the structural and production outlay, more particularly also for the rotary piston and its cylinder provided with three pressure chambers, is extraordinarily high Economic production of this clamping device is thus impossible.
Furthermore, heavy leakage losses occur in the three circular segment-shaped pressure chambers of the cylinder of the rotary piston and it is therefore necessary to accept considerable pressure reductions which are dictated by the large number of gaps to be sealed and the peculiar construction of the parts in mutual contact Consequently reliable sealing cannot be achieved and a pressure accumulator and also a non-return valve, as demanded by the Trade Union for safety considerations cannot be maintained in the cylinder The rotary piston is also unfavourably influenced by torques which suddenly appear during starting up and breaking of the spindle In the extreme case, this can lead to the opening or closing of the clamping chuck Moreover, the cylinder of the rotary piston and the clamping chuck require an entrainment securing means on the intermediate flange and on the chuck direct housing, in order to absorb the high torques during operation.
Above all, however, it is to be regarded as highly disadvantageous in this known clamping device that it is not versatile in use In fact the clamping cylinder equipped with a rotary piston cannot be used for chucks which are operable through an axially sidable actuating member and such chucks are found in large numbers in a m r-4 2 in ro 1 565 213 workshop but this clamping cylinder, together with the chuck, can only be used together in each case The conversion of an NC-machine equipped with such a chuck is thus very time-consuming The use of a different type of chuck is frequently even impossible because the cylinder of the rotary piston is mounted fixed on the machine spindle.
It is further disadvantageous here that the forces acting upon a toothed actuating bar have to be transmitted by one tooth at a time of the gearwheel provided with helical teeth and that the rotary movement of the tube and also of the gearwheel firmly attached thereto causes dirt, more particularly swarf, which may fall through the teeth into the gearwheel, to be entrained therein.
This dictates not only frequent disassembly of the clamping chuck in order to clean it, but also leads in many cases to damage or to an impairment of the circular precision of the jaws, which in turn causes a distortion and uneven load distribution upon the internal parts of the clamping chuck.
It is accordingly an object of the invention to provide a clamping chuck having toothed actuating bars arranged transversely to the chuck axis acting upon the clamping jaws, wherein although the clamping jaws have to be brought out of engagement with the actuating bars, does not suffer from these disadvantages On the contrary, the invention aims at providing a construction in which the actuating bars are operable by means of a piston axially slidable in a clamping cylinder, prefereably subject to the effect of a pressure medium, so that for a small axial length of the chuck powerful clamping forces and highly precise centering are obtained It is further an aim of the invention that the forces and adjustment travels exerted can be stepped up and be kept high for a small structural and production outlay and with high efficiency Above all, versatility of use, more particularly of the clamping cylinder is urequired to exist, in order that the conversion times of a lathe when fitting different types of clamping devices are short.
Accordingly, the present invention consists in a clamping chuck for a lathe, comprising a chuck body, a plurality of base jaws or clamping jaws which are arranged in said body for radial sliding movement and are each drivable by a respective actuating bar guided in the chuck body tangentially to the axis of rotation thereof, the actuating bars being provided with teeth by means of which said bars engage with teeth on the jaws and being slidable to such an extent as to enable the toothed bars to be brought out of engagement from the teeth of the jaws for the purpose of removing the latter from the chuck, characterised in that the actuating bars are driven by an adjusting member slidable axially into predetermined forward and rearward end positions within the chuck body and guided concentrically therein, on which member plane or curved oblique surfaces or teeth are formed or a cylindrical actuating member is provided, and each actuating bar is provided either with a complementary oblique surface which is in contact with the oblique surface of the adjusting member or with the cylindrical actuating member, or is provided with teeth which mesh with the teeth of the adjusting member either directly or via a toothed intermediate member.
It is highly advantageous in this case to provide the adjusting member with projections each extending tangentially to a base circle and on each of which the oblique surface co-operating with an actuating bar or the teeth are formed in the outer region.
According to a different type of construction, the adjusting member may be provided with spur and/or helical teeth into which gearwheels mounted rotatably in recesses of the chuck body engage, which mesh respectively with teeth formed in each actuating bar.
In order to guide the adjusting member non-rotatably, it is advantageous to maintain it securely against rotation by means of projections engaging into recesses of the chuck body, preferably through the projections provided with oblique surfaces The forces acting during the re-direction of force are thus supported directly against the chuck body.
It is moreover advantageous from structural considerations to provide each of the actuating bars with a recess inclined in its longitudinal direction, of which one or both external surfaces are constructed as oblique surfaces co-operating with the projections of the adjusting member, in which case these recesses may have two oblique surfaces inclined with different gradient in the longitudinal direction and respectively associated with a clamping stroke and a rapid stroke, and the projections of the adjusting member may have two complementary surfaces cooperating with the latter.
In this case the adjusting member may be constructed as a sleeve which is connected by a traction rod to a pressure medium actuated piston as actuating element of a servo mechanism But it is also possible, in order to produce a compact assembly, to connect the adjusting member directly to a pressure medium actuated piston as actuating element which is arranged slidingly in the chuck body guiding the actuating bars.
For the automatic limitation of the working range of the adjusting member, there may be associated with the latter, or with the actuating element, in simple manner a 3 1 565 213 3 limit switch which requires to be bridged in order to perform an adjusting movement into the limit position e g in order to exchange the jaws.
In order to prevent the penetration of dirt, the actuating bars may be provided with seal elements on the side provided with the teeth The seal elements of the actuating bars may in this case conveniently be constructed as sealing strips which extend parallel to the guide grooves of the jaws and may be screwed on, stuck on or inserted into machined slits, whilst in each case one of the seal elements of the actuating bars should be arranged directly beside the teeth and the other seal element adjacent to the recess.
In order to reduce the friction, the actuating bars may be provided with a slip lining.
e.g; a molybdenum lining, on their guide faces and/or their contact surfaces of the chuck body It is also possible to arrange linear rolling-contact bearings constituted by balls or rollers between the guide surfaces of the actuating bars and their contact surfaces of the chuck body.
With the same object the oblique surfaces or the teeth of the adjusting member and/or the complementary surfaces of the actuating bars co-operating therewith may also be provided with a slip lining, e g a molybdenum lining, or linear rolling-contact bearings comprising balls or rollers may be arranged between the latter It is furthermore appropriate to provide the contact surface of the adjusting member in the chuck body and/or its complementary surface co-operating with the adjusting member with a slip lining or to arrange a linear rolling-contact bearing comprising balls or rollers between these parts.
It is also possible to arrange on each of the projections of the adjusting member a rolling-contact bearing which co-operates with the oblique surfaces of the actuating bars, while the rolling contact bearings should be arranged on the projections in such a way that the latter are partially in contact with the oblique surfaces of the actuating bars and with the complementary surfaces associated with the adjusting member of the recesses machined in the chuck body Conversely, it is also possible to insert into the actuating bars rolling-contact bearings which co-operate with the oblique surfaces formed on the projections of the adjusting member.
In this case the helix of the teeth of the actuating bars should be chosen so that the teeth of the jaws can be constructed as a spur teeth extending at right angles thereto.
This creates major technical production advantages because the jaws of the clamping chuck can be produced as blocks.
Furthermore, in order to maintain and align the jaws before their teeth come into engagement with the teeth of the actuating bars, a maintaining member should be arranged in each of the actuating bars in extension of one of the toothed bars in the region free from teeth.
In this case the maintaining member should conveniently be formed from a catch pin guided securely against rotation and engaging by oblique surfaces into the teeth of the jaws and a slide block braced against the chuck body, between which a compression spring is inserted, whilst it is further appropriate to associate with the slide block extending in the chuck body in the axial direction of the maintaining member, which is provided with an oblique surface and to equip the slide block with a wedge-shaped complementary surface which co-operates with the oblique surface of the recess when the jaws aare brought into engagement In this case if the spacing between the catch pin and the slide block is dimensioned so that they are in mutual contact when the jaws are engaged, then it is ensured that the force of the springs is not overcome, more particularly when heavy jaws are used, but that the jaws are always locked reliably by the maintaining member.
The clamping chuck constructed according to the invention is characterised not only by a smaller structural outlay and lower production costs than the comparable previously known construction, but provides above all the advantage that by a redirection of the force introduced, said force and also the in-feed travel can be stepped up For if, to drive the actuating bars, an axially slidable adjusting member is used on which oblique faces or teeth co-operating with the actuating bars are formed, then it is possible to transmit the force acting upon an actuating bar through two co-operating oblique surfaces or teeth, namely from the adjusting member through oblique surfaces to the actuating bars and from the latter through the toothed bars to the jaws An amplification of the force introduced is thus immediately possible, also the in-feed travel of the clamping jaws can be made very long or very short, so that adaptation to the particular desiderata is readily possible without difficulty.
It is further advantageous that the forces are transmitted not by rolling movements for reducing friction, but by sliding movements The components participating in the force transmission, or their stressed crosssections, can thus be dimensioned large without creating problems and the specific pressure can be kept low, so that even extremely high forces which are supported against the chuck body can be transmitted.
It is thus possible to use as actuating element in the clamping chuck constructed according to the invention, a customary 1 565 213 1 565 213 commercial clamping cylinder, the piston of which is connected to the axially slidable adjusting member Thus the dynamic actuation of the proven transversely extending actuating bars occurs by axially directed compression and traction forces No sealing problems occur in the customary commercial pressure cylinder Above all, however, versatility of use is obtained in this way, more particularly on NC lathes, because not only is a rapid conversion of the clamping chuck possible by exchanging the jaws, but the actuating bar chuck can also be exchanged in a short time for a finger chuck, a collet chuck or the like, in which case the clamping cylinder is likewise used as servo mechanism In this way the make ready times of a lathe can be considerably shortened.
In this case the redirection of the axially orientated forces and of the axial adjustment travel, whilst the clamping travel can also be subdivided into a clamping stroke and a rapid stroke by differential inclination of the oblique surfaces fitted to the actuating bars, occurs in two mutually separate components, namely through the oblique surfaces of the adjusting member and the teeth of the actuating bars By this means a short overall axial length is obtained and it is ensured that the clamping chuck does not get dirty Thus the clamping chuck of the invention provides not only the advantage of an actuating bar chuck but also makes it possible for a conventional clamping cylinder with axially pressurised actuating element to be used to actuate it.
In order that the invention may be more readily understood, reference is made to the accompanying drawings which illustrate diagrammatically and by way of example embodiments thereof, and in which:Figure 1 is a sectional view of a clamping chuck provided with a servo mechanism; Figure 2 is an elevation partly in section of the clamping chuck of Figure 1:
Figure 3 shows the clamping chuck of Figures 1 and 2 in plan and partly in section along the line III-III of Figures 1 and 2; Figure 4 shows a different configuration of the oblique surfaces fitted to the actuating bars and to the adjusting member in a chuck in a view similar to Figure 3; Figure 5 shows a clamping chuck according to Figure 1 with an actuating piston inserted directly in the chuck body; Figure 6 shows two different methods of mounting an actuating bar and the adjusting member in a view corresponding to Figure 2; Figure 7 shows the arrangement of a rolling-contact bearing in contact with the obique surface of an actuating bar on the adjusting member according to Figure 2; Figure 8 shows in elevation and partly in section another embodiment of clamping chuck according to Figure 1 with gearwheels as intermediate members between the adjusting member and the actuating bars; Figure 9 is a plan view partly in section of the clamping chuck according to Figure 8; Figure 10 shows in section the configuration of the maintaining member provided on the clamping chuck according to Figure 1; and Figure 11 shows another embodiment of the maintaining member.
The clamping chuck 1 illustrated in Figures 1, 2 and 3 comprises a chuck body 2 with housing part into which base jaws 3 provided with teeth 8 are inserted into radially orientated T-shaped grooves 5, upon which clamping jaws 4 acting upon the workpiece not shown, are fixed The mounting of the clamping chuck 1 on a machine (lathe spindle 6) shown by chaindotted lines in Figure 1 is effected by screws 7 which engage through the chuck body or another direct housing.
In this embodiment, three actuating bars 11, which are inserted in grooves 12 orientated tangentially to the axis of rotation, are provided for the radial adjustment of the base jaws 3 The grooves 12 are closed at each of their ends by terminal pieces 13 On the front of the actuating bars 11 are teeth 14 into which the base jaws 3 engage by their teeth 8 Also adjacent to the teeth 14, recesses 15 are provided on each actuating bar 11 in order to permit the base jaws 3 to be disengaged from the teeth 14 as soon as their teeth 8 are out of mesh.
The penetration of dirt, more particularly swarf, is prevented by seal elements 16 and 17 which are arranged adjacent the teeth 14 and the recesses 15 and arranged parallel to the grooves 5 The seal elements 16 and 17 are constituted by sealing strips 18 and 18 ‘ which are fixed by means of screws 19, or stuck on or inserted in slits.
For the operation of the actuating bars 11 which are arranged transversely to the axis of rotation, an axially slidable adjusting member 21 is provided which is connected to a servo mechanism 26 comprising a piston 28 susceptible to the action of a pressure medium and inserted into a clamping cylinder 27 For this purpose the adjusting member 21, which has recesses 23 to enable the base jaws or clamping jaws 3 or 4 to be introduced as far as the centre, is constructed as a sleeve 22 and provided with a screwthread 24 into which a traction rod 25 firmly attached to the piston 28 and penetrating the machine spindle 6 is screwed The clamping chuck l can thus easily be separated from the servo mechanism 26 After an axial sliding of the piston 28 the adjusting member 21 is slid in the same manner.
The adjusting member 21 also has projec1 565 213 5 tions 41 arranged tangentially to a base circle, one of which at a time is associated with an actuating bar 11 To house the projections 41, the chuck body 2 is provided with corresponding recesses 43 As may be seen more particularly from Figure 3 on the projections 41 there are shaped in the external region 41 ‘ oblique surfaces 42 and 42 ‘ which are orientated in the direction of the actuating bars 11 and are inclined to their direction of adjustment The actuating bars 11 are provided with associated oblique surfaces 45, 45 ‘, by virtue of a groove or recess 44 being machined into the latter In the case of an axial sliding of the adjusting member 21 the oblique surfaces 42 42 ‘ and 45, 45 ‘ are in mutual contact so that the actuating bars 11 are slid in the grooves 12.
and the base jaws 3 connected to them are slid radially in the grooves 5.
The supply of pressure medium to the pressure chamber 39 of the clamping cylinder 27 is effected from a pressure medium feed pipe 31 through a rotary distributor 30 arranged on the piston rod 29 of the piston 28 Also fitted on to the piston rod 29 is a cam 32 which co-operates with a limit switch 33 in order to limit the working range A of the piston 28 associated with the clamping range When the contact 34 of the limit switch 33 is opened by the cam 32 then a solenoid valve 36 in the pressure medium feed pipe 31 is closed through a lead 35 so that the supply of pressure medium is blocked and no further adjusting movement is effected beyond the working range A.
However, in order to permit the adjusting member 21 to be brought into a limit position in which the teeth 14 are out of engagement with the teeth 8 of the base jaws 3 so that the latter may be disengaged when their teeth 8 engages in the recess 15.
a switch 38 e g manually operable is located in a branch pipe 37 On actuation of the switch 38, the open contact 34 is bridged and the solenoid valve 36 is thus opened sufficiently to enable the piston 28 to move over the distance Z beyond the working range A into the limit position In this position the actuating bars 11 are slid to the extent that their teeth 14 are out of engagement with the teeth 8 of the base jaws 3 and the latter can thus be extracted from the clamping chuck 2.
The axial adjustment of the piston 28 and of the adjusting member 21 attached thereto is transmitted by the oblique surfaces 42 and 42 ‘ on the adjusting member 21 (if desired.
only one surface need be provided and through the oblique surfaces 45 and 45 ‘ co-operating therewith to the actuating bars 11 Because the bars 11 are connected operatively to the base jaws 3 by means of the teeth 14, the clamping jaws 4 are moved towards or away from a workpiece according to the direction of adjustment of the piston 28 During an axial movement the adjusting member 21 is guided nonrotatably in the chuck body 2 by the projections 41 which engage in the recess 43 so that the forces acting are securely supported.
The transmission of the clamping forces and also of the adjustment travel are thus effected through two sets of co-operating inclined surfaces By an appropriate dimensioning of the inclination of the oblique surfaces 42 and 45 or of the teeth 14 on the bars 11 and the jaw teeth 8 not only can the force produced by increased but it is also possible to modify the clamping stroke of the clamping jaws 4 with reference to the adjustment travel of the adjusting member 21 and to adapt them to requirements Thus a chuck is produced, the actuating bars 11 of which are operable in simple manner by means of the axially displaceable adjusting member 21.
The recesses 44 in the actuating bars 11, which house the terminal region 41 ‘ of the projections 41 provided with the oblique surfaces 42 and 42 ‘, may also be inclined with two different gradients as illustrated in Figure 4 In this way additional oblique surfaces 47 and 47 ‘ are created which are associated with a rapid stroke in order to permit a rapid travel out of the jaw teeth 8.
For this purpose further oblique surfaces 46 and 46 ‘ which co-operate with the oblique surfaces 47 and 47 ‘ during a rapid stroke, are also provided on the projection 41 or its terminal region 41 ‘.
In the embodiment according to Figure 5, the actuating element associated with the adjusting member 21 is again constructed as a piston 51 susceptible to pressure medium but inserted slidablv directly into a recess 52 of the chuck body 2 The piston 51 is attached firmly to the adjusting member 21 by means of screws 53 In order to limit the working range of the adjusting member 21, a cam 55 which co-operates with a limit switch 56 is fitted to the piston 51 on a rod 54 protruding out of the chuck body 2.
Figure 6 shows different means bv which the friction on the mutually adjacent surfaces of the chuck body 2 of the actuating bar 11 and of the adjusting member 21 can be reduced.
For example on the lateral surfaces 61 and 62 of the actuating bars 11 or the lateral surfaces 63 and 64 of the groove 12 accommodating them slip linings 65 and/or 66, e.g of molybdenum, can be fitted Alternativelv it is possible to insert between them a linear rolling-contact bearing 67 formed by rollers or balls.
Furthermore the oblique surface 42 of the projection 41 and/or the oblique surface of the recess 44 may be provided with a 1 565 213 1 565 213 slip lining 68, or a rolling-contact bearing 73 may be arranged between them.
Slip linings 71 and/or 72 may also be fitted on mutually contacting surfaces 69 and 70 of the adjusting member 21 and of the recess 43 of the chuck body 2 on both sides.
According to Figure 7 the external part of the projections 41 may also be constructed as a stud 74 on which a rolling-contact bearing 75 is supported The rolling-contact bearing 75 in this case may conveniently be arranged in such a way that it is in contact not only with the oblique surfaces 45 and 45 ‘ of the actuating bar 11, but also with the lateral surfaces 70 and 70 ‘ of the recess 43.
By this means the adjustment movement of the adjusting member 21 is transmitted and supported by rolling.
In the embodiment of a clamping chuck illustrated in Figures 8 and 9, the axially slidable adjusting member 21 ‘ is operatively connected to the actuating bars 11 through a gearwheel 85 as an intermediate member.
For this purpose teeth 82 are provided on the adjusting member 21 ‘ and the actuating bars 11 are likewise provided with teeth 83, into which the gearwheel 85 mounted rotatably in a recess 84 of the chuck body 2 by means of rolling-contact bearings 98 engages In this case the gearwheel 85 is provided with spur teeth 86 which mesh with the teeth 82 of the adjusting member 21 ‘, and with helical teeth 87 which are in mesh with the teeth 83 of the actuating bars 11.
However the gearwheel 85 may alternatively be provided with only one kind of teeth in the case of an appropriate choice of the teeth for the co-operating elements An adjustment movement of the member 21 ‘ is thus converted through the gearwheel 85 and the actuating bars 11 operatively connected thereto, into a radial in-feed movement of the clamping jaws 4.
In order to align and maintain the base -45 jaws 3 when they are inserted, before they are in engagement with the teeth 14 of the actuating bars 11, the clamping chuck is provided with a maintaining member 91 illustrated in Figures 10 and 11 which is inserted directly into the actuating bars 11, i.e in a recess 90 formed in the latter, and in the region not provided with teeth 14 The maintaining member 91 here consists of a catch piece 92 which is secured against rotation and is provided with oblique surfaces 95 orientated in the direction of alignment of the teeth 14, with a slide block 93 and with a compression spring 94 arranged between these parts which is inserted into a recess 96 of the catch piece 92 The spring 94 is supported against the slide block 93 which is in contact with the chuck body 2, so that by the force of the spring 94 the base jaws 3 are maintained by means of the catch piece 92 engaging in their teeth 8.
In order to anchor even particularly heavy jaws reliably, in the embodiment accordingto Figure 11 there is formed into the chuck body 2 a recess 97 which is provided with an oblique surface 98 The slide block 93 ‘ has an oblique surface 99 constructed in the same manner which co-operates with the surface 98 Thus, during sliding of the actuating bars 11, the oblique surface 99 rides up on the oblique surface 98 so that the slide block 93 ‘ is pushed into the recess 90 and is in contact with the catch piece 92 The catch piece 92 is thereby maintained immovably and cannot be thrust back axially by the jaws.

Claims (24)

WHAT WE CLAIM IS:-

1 A clamping chuck for a lathe, comprising a chuck body, a plurality of base jaws or clamping jaws which are arranged in said body for radial sliding movement and are each drivable by a respective actuating bar guided in the chuck body tangentially to the axis of rortation thereof, the actuating bars being provided with teeth by means of which said bars engage with teeth on the jaws and being slidable to such an extent as to enable the toothed bars to be brought out of engagement from the teeth of the jaws for the purpose of removing the latter from the chuck characterised in that the actuating bars are driven by an adjusting member slidable axially into predetermined forward and rearward end positions within the chuck body and guided concentrically therein, on which member plane or curved oblique surfaces or teeth are formed or a cylindrical actuating member is provided, and each actuating bar is provided either with a complementary oblique surface which is in contact with the oblique surface of the adjusting member or with the cylindrical actuating member, or is provided with teeth which mesh with the teeth of the adjusting member either directly or via a toothed intermediate member.

2 Clamping chuck as claimed in claim 1 wherein the adjusting member is provided with projections each extending tangentially to a base circle and on each of which the oblique surface or the teeth co-operating with an actuating bar are formed in the outer region.

3 Clamping chuck as claimed in claim 1, wherein the adjusting member is provided with a spur and/or helical teeth into which gearwheels mounted rotatably in recesses of the chuck body engage as intermediate members which respectively mesh with teeth formed or provided in each actuating bar.

4 Clamping chuck as claimed in any of claims 1 to 3 wherein the adjusting member is maintained securely against rotation by means of projections engaging in recesses of 1 565 213 the chuck body, through the projections provided with oblique surfaces.

Clamping chuck as claimed in claim 1 or 2, wherein the actuating bars are each provided with a recess inclined in its longitudinal direction, one or both external surfaces of which are constructed as oblique surfaces co-operating with the projections of the adjusting member.

6 Clamping chuck as claimed in claim 5, wherein the recesses in the actuating bars are provided with two oblique surfaces inclined with different gradients in the longitudinal direction and respectively associated with a clamping stroke and with a rapid stroke, and the projections of the adjusting member are provided with two complementary surfaces co-operating therewith.

7 Clamping chuck as claimed in any of the preceding claims, wherein the adjusting member is constructed as a sleeve and is connected through the intermediary of a traction rod to a piston susceptible to pressure medium as actuating element of a servo mechanism.

8 Clamping chuck as claimed in any of claims 1 to 6, wherein the adjusting member is connected directly to a piston susceptible to pressure medium as actuating element which is arranged slidably in the chuck body guiding the actuating bars.

9 Clamping chuck as claimed in any of the preceding claims, wherein limit switches actuatable in the case of an adjustment movement into the end position by means of which the working range of the adjusting member is automatically limited, are associated with the adjusting member or its actuating element.

Clamping chuck as claimed in any of the preceding claims, wherein the actuating bars are provided with seal elements on the side provided with the teeth.

11 Clamping chuck as claimed in claim 10, wherein the seal elements of the actuating bars are constructed as sealing strips which are arranged parallel to the guide grooves of the jaws.

12 Clamping chuck as claimed in claim or 11 wherein one of the seal elements of each of the actuating bars is arranged directly beside the toothed bar and the other seal element is arranged adjacent to the recess.

13 Clamping chuck as claimed in any of the preceding claims, wherein the actuating bars are provided on their guiding surfaces and/or on their contact surfaces of the chuck body with a slip lining, e g a molybdenum lining.

14 Clamping chuck as claimed in any of claims 1 to 12, wherein linear rolling-contact bearings constituted by balls or rollers are arranged between the guide surfaces of the actuating bars and their contact surfaces of the chuck body.

Clamping chuck as claimed in any of the preceding claims wherein the oblique surfaces or the teeth of the adjusting member and/or the complementary surfaces cooperating therewith of the actuating bars are provided with a slip lining, e g with a molybdenum lining, or with a linear rollingcontact bearing consisting of balls or rollers arranged between the same.

16 Clamping chuck as claimed in any of the preceding claims, wherein the contact surface of the adjusting member in the chuck body and/or the complementary surface of the latter co-operating with the adjusting member are provided with a slip lining or with a linear rolling-contact bearing constituted by balls or rollers arranged between the same.

17 Clamping chuck as claimed in any of the preceding claims, wherein rollingcontact bearings which co-operate with the oblique surfaces of the actuating bars are arranged on the projections of the adjusting member.

18 Clamping chuck as claimed in claim 17 wherein the rolling-contact bearings are arranged on the projections in such a way that they are partially in contact with the oblique surfaces of tfie actuating bars andwith the complementary surfaces, associated with the adjusting member of the recesses formed into the chuck body.

19 Clamping chuck as claimed in any of claims 1 to 16 wherein rolling-contact bearings which co-operate with the oblique surfaces shaped on the projections of the adjusting member are located in the actuating bars.

2 t) Clamping chuck as claimed in any of the preceding claims wherein the helix of the teeth of the actuating bars is chosen so that the teeth of the jaws can be constructed as a spur teeth orientated at right angles thereto.

21 Clamping chuck as claimed in any of the preceding claims wherein a maintaining member is arranged in each of the actuating bars in a region free of teeth in an extension of one of the toothed bars.

22 Clamping chuck as clamed in claim 21 wherein the maintaining member is constituted by a catch pin guided securely against rotation and engaging by oblique surfaces into the teeth of the jaws and by a slide block braced against the chuck body, between which a compression spring is located.

23 Clamping chuck as claimed in claim 21 wherein a recess in the chuck body extending in the axial direction of the maintaining member is associated with the slide block and is provided with an oblique surface and the slide block has a wedge1 565 213 shaped counter face which co-operates with the oblique surface of the recess during the engagement of the jaws.

24 Clamping chuck as claimed in claim 22 or 23, wherein the spacing between the catch pin and the slide block is dimensioned so that these parts are in mutual contact when the jaws are engaged.
A clamping chuck for a lathe constructed arranged and adapted to operate substantially as hereinbefore described with reference to and as shown in the accompanying drawings.
VENNER SHIPLEY & CO Chartered Patent Agents.
Rugby Chambers, 2, Rugby Street, London, WC 1 N 3 QU.
Agents for the Applicants.
Printed for Her Majesty’s Stationery Office.
by Crosdon Printing Company Limited Croydon, Surrey, 1980.
Published by The Patent Office 25 Southampton Buildings, London, WC 2 A Il AY, from which copies may be obtained.

GB51909/76A
1975-12-13
1976-12-13
Clamping chuck for a lathe

Expired

GB1565213A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

DE2556227A

DE2556227B2
(en)

1975-12-13
1975-12-13

Chuck

Publications (1)

Publication Number
Publication Date

GB1565213A
true

GB1565213A
(en)

1980-04-16

Family
ID=5964308
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB51909/76A
Expired

GB1565213A
(en)

1975-12-13
1976-12-13
Clamping chuck for a lathe

Country Status (6)

Country
Link

US
(1)

US4094522A
(en)

JP
(1)

JPS5281679A
(en)

DE
(2)

DE2556227B2
(en)

FR
(1)

FR2334455A1
(en)

GB
(1)

GB1565213A
(en)

IT
(1)

IT1074217B
(en)

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Priority date
Publication date
Assignee
Title

DE2631583C3
(en)

1976-07-14
1981-06-25
Röhm, Günter Horst, 7927 Sontheim

Power operated chuck

DE7633955U1
(en)

1976-10-28
1977-07-21
Roehm, Guenter Horst, 7927 Sontheim

CHUCK FOR LATHE WITH RADIALLY MOVABLE JAWS

DE2729939B2
(en)

1977-07-02
1980-10-09
Paul Forkardt Kg, 4000 Duesseldorf

Power operated chuck

JPS582772B2
(en)

1979-11-20
1983-01-18
豊和工業株式会社

mechanical chuck

DE3127527A1
(en)

1981-07-11
1983-02-03
SMW Schneider & Weißhaupt GmbH, 7996 Meckenbeuren

“POWER CHUCK FOR LATHE”

DE3148661A1
(en)

1981-12-09
1983-06-16
SMW Schneider & Weißhaupt GmbH, 7996 Meckenbeuren

POWERED CHUCK FOR LATHE

DE3204529C2
(en)

1982-02-10
1984-03-29
SMW Schneider & Weißhaupt GmbH, 7996 Meckenbeuren

Chuck

US4722536A
(en)

1986-02-07
1988-02-02
Logansport Machine Co., Inc.
Quick change chuck jaw

US6568694B1
(en)

2002-07-12
2003-05-27
Phillip A. White
Adjustable workholding jaw assemblies

JP5244483B2
(en)

2008-07-16
2013-07-24
株式会社ユタカ技研

Chuck device for exhaust gas purification device processing

EP2559507B1
(en)

2011-08-17
2014-11-19
SMW-AUTOBLOK Spannsysteme GmbH
Manually operated chuck

DE102011117883B4
(en)

2011-11-08
2015-04-09
Sms Meer Gmbh

Chuck of a machine tool for machining a tubular, rotating workpiece

EP2835196A1
(en)

2013-08-06
2015-02-11
SMW-AUTOBLOK Spannsysteme GmbH
Collet chuck

PL3028794T3
(en)

2014-12-04
2019-09-30
Hvm Technology Gmbh
Power collet chuck

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Assignee
Title

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(en)

1934-01-27
Schuette Fa Alfred H

Device for wedge chucks with ®Î-shaped guide grooves between chuck jaws and drive piston

DE412837C
(en)

1925-04-28
Forkardt Paul Kg

Chuck

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1922-12-11
Forkardt Paul Kg

Centering device

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1923-02-10
1923-10-31
Forkardt Paul Kg

Centering device

FR1006372A
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1948-01-02
1952-04-22
Forkardt Paul Kg

Lathe chuck

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1948-05-14
1952-03-25
Union Mfg Co
Power actuated chuck

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1951-06-07
1957-02-28
Hermann Brenner

Chuck with axially displaceable threaded ring for adjusting the clamping jaws

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1952-05-17
1955-07-04
Forkardt Paul Kg

Hand-operated jaw chuck for lathe or the like.

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1955-05-23
1958-07-29
Union Mfg Co
Chuck

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1957-04-02
1959-06-18
Forkardt Paul Kg

Power operated chuck for large diameters

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1968-11-07
Forkardt Paul Kg

Multi-jaw chuck for lathe u. like

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1968-10-16
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Chucks for machine tools

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1969-03-07
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1969-08-09
1971-04-15
Forkardt Paul Kg

CHUCK FOR LATHE AND MACHINE TOOLS

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1970-02-19
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Forkardt Paul Kg
Power operated clamping device for machine tools

DE2026208B2
(en)

1970-05-29
1972-05-04
Paul Forkardt KG, 4000 Düsseldorf

CHUCKS FOR LATHE

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1971-03-18
1973-11-13
W Platt
Compound chuck structure

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1972-06-30
1974-01-10
Rudi M Lang

JAW CHUCK FOR MACHINE TOOLS OD. DGL

US3814448A
(en)

1972-10-16
1974-06-04
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Hydraulic chuck

JPS5345988Y2
(en)

1973-06-19
1978-11-02

DE2436529B1
(en)

1974-07-29
1975-10-30
Paul Forkardt Kg, 4000 Duesseldorf

Power operated chuck

1975

1975-12-13
DE
DE2556227A
patent/DE2556227B2/en
active
Granted

1975-12-13
DE
DE7539795U
patent/DE7539795U/en
not_active
Expired

1976

1976-12-01
JP
JP14354276A
patent/JPS5281679A/en
active
Granted

1976-12-06
FR
FR7636655A
patent/FR2334455A1/en
active
Granted

1976-12-13
IT
IT52573/76A
patent/IT1074217B/en
active

1976-12-13
GB
GB51909/76A
patent/GB1565213A/en
not_active
Expired

1976-12-13
US
US05/749,694
patent/US4094522A/en
not_active
Expired – Lifetime

Also Published As

Publication number
Publication date

DE2556227A1
(en)

1977-06-30

IT1074217B
(en)

1985-04-17

US4094522A
(en)

1978-06-13

DE2556227B2
(en)

1979-05-23

FR2334455A1
(en)

1977-07-08

JPS5281679A
(en)

1977-07-08

FR2334455B1
(en)

1980-03-14

JPS5742443B2
(en)

1982-09-08

DE7539795U
(en)

1977-03-31

DE2556227C3
(en)

1988-02-11

Contact information