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
  • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
  • B23B31/26—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle
  • B23B31/261—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle clamping the end of the toolholder shank
  • B23B31/265—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle clamping the end of the toolholder shank by means of collets
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B29/00—Holders for non-rotary cutting tools; Boring bars or boring heads; Accessories for tool holders
  • B23B29/24—Tool holders for a plurality of cutting tools, e.g. turrets
  • B23B29/242—Turrets, without description of the angular positioning device
• • 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
  • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
  • B23B31/26—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle
  • B23B31/261—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle clamping the end of the toolholder shank
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B2231/00—Details of chucks, toolholder shanks or tool shanks
  • B23B2231/04—Adapters
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B2231/00—Details of chucks, toolholder shanks or tool shanks
  • B23B2231/24—Cooling or lubrication means
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B2231/00—Details of chucks, toolholder shanks or tool shanks
  • B23B2231/36—Sealed joints
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B2231/00—Details of chucks, toolholder shanks or tool shanks
  • B23B2231/46—Pins
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
  • B23B—TURNING; BORING
  • B23B2231/00—Details of chucks, toolholder shanks or tool shanks
  • B23B2231/48—Polygonal cross sections
• • 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
  • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
  • B23B31/30—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck
  • B23B31/302—Hydraulic equipment, e.g. pistons, valves, rotary joints

Definitions

• Clamping systems with a hollow shank and a complementary shaped center mount for example according to ISO 12164 or ISO 26623, have proven themselves on the market for many years.
• the hollow shank is part of an adapter that carries, for example, a drill, milling cutter, turning tool or other tool.
• center mounts with a truncated cone that has a polygonal cross-section have been used for decades.
• the hollow shank of the adapter has an outer contour that complements it (hereinafter also referred to as outer polygon).
• the known clamping systems for clamping such a polygonal hollow shank include a collet consisting of several clamping segments.
• the clamping segments are arranged around a draw bolt.
• An axial movement of the tension bolt relative to the clamping segments presses them radially outwards into a groove of the hollow shank. This initially results in a form fit with the hollow shank at the front ends of the clamping segments.
• a further movement of the draw bolt creates an axial clamping force which the clamping segments exert on the hollow shank of the adapter, so that the adapter is pulled into the centering mount.
• An example of such a clamping system is known from EP 2 164 662.
• Other clamping systems are known from EP 1 924 379 B1 and DE 196 18 610 A1.
• the clamping system and the optional cylinder assembly in the spindle must be installed in most cases through the center mount (the inner polygon).
• the invention is based on the object of providing a clamping system that makes it possible to make the best possible use of the installation space available in a rotatably mounted or a stationary spindle.
• the assembly of the clamping system and cylinder assembly should be simple and time-saving. In the event of an overhaul or repair, the clamping system and the cylinder assembly should be able to be easily dismantled.
• a rotatably mounted or fixed spindle having a recess which includes a centering mount, an annular groove and a receiving bore for a clamping system and an optional cylinder structure for actuating the clamping system
• the centering mount being designed as a polygonal inner cone is designed and accommodates an adapter with a polygonal outer contour and hollow shaft
• the clamping system comprising a collar, the collar having a polygonal outer contour or the outer contour being formed by a plurality of lugs distributed over the circumference, the collar being in at least one rotational position by the Centering fit and by turning the collar relative to the spindle in at least one locking position, a form fit is established in at least one axial direction between the collar and the annular groove.
• the space immediately behind the centering mount is designed as an annular groove. There at the transition between center mount and mounting hole has the Center mount their smallest diameter. The space requirement for the locking device according to the invention is therefore minimal.
• the outer diameter of the clamping system and of a cylinder structure possibly arranged behind the clamping system can be maximized. This gives the designer of the clamping system and cylinder structure a degree of freedom in the design, and also increases the actuating forces that the cylinder structure can provide in order to clamp or unclamp the clamping system. to solve, since a cylinder structure with a larger piston diameter can be installed.
• a diameter of the annular groove is the same size as or slightly larger than a circumference of the outer contour of the collar.
• a recess is formed in the collar.
• a locking pin is inserted into a hole (with or without thread) in the spindle, which dips into the recess. In this way, a form-fitting and detachable anti-twist device is created for the collar and thus also for the clamping system relative to the spindle.
• the locking pin can be designed as a threaded pin, for example.
• Other one or two-piece designs can be implemented at any time, as long as the basic function of the form-fitting and detachable anti-twist device is retained.
• the cutout is arranged at a high point of the polygonal collar or a nose of the collar.
• the width of the annular groove is the same size or slightly larger than the width of the collar.
• the axial play with which the clamping system is positioned in the spindle results from the difference in the width of the ring groove and the width of the collar. A very small axial play of less than 0.1 mm can easily be achieved. An axial play of 0.05 mm can also be achieved. If the annular groove is 0.02 mm to 0.05 mm wider than the collar, then this is considered to be "of the same size". The play prevents the collar from jamming in the ring groove and makes assembly easier.
• the mounting hole in the spindle can be designed as a polygon, at least in sections. Then there is even more space inside the spindle for the clamping system and an optional cylinder assembly.
• the piston or pistons of the cylinder structure can also be designed as a polygon.
• the collar or the collar and the housing can be rotated relative to the rest of the clamping system ( 4 ) or the cylinder assembly ( 6 ).
• the collar then functions like a circlip and forms an axial stop in the clamping direction.
• the piston and the rest of the system can then lie flat against the polygonal contour of the bore and utilize the full cross-sectional area of the polygonal receiving bore.
• the optional cylinder assembly includes a piston rod, the piston rod having a central bore for supplying cooling lubricant to a tool clamped in the clamping system, and the piston rod penetrating a seal carrier and ending in a supply chamber of the spindle.
• This seal carrier separates the supply space in which the cooling lubricant is located from the cylinder structure, so that the fluidic working medium of the cylinder structure (such as compressed air or hydraulic fluid) and the cooling lubricant in the supply space do not get into each other contact . Even if cooling lubricant is used in the cylinder structure, it should not mix with the cooling lubricant in the supply space, since higher purity requirements are placed on the cooling lubricant used in the cylinder structure.
• a particularly advantageous embodiment of the invention provides that the seal carrier comprises a flange and a threaded section with an external thread, with an annular groove being formed between the flange and the threaded section.
• a gap is formed between the piston rod and the seal carrier, and at least one bore connects the annular groove and the gap to one another.
• At least one bore is provided in the spindle, which opens into a space delimited by the annular groove and the spindle. Cooling lubricant is fed through this bore to the seal carrier or conveyed by the annular groove.
• At least one seal is arranged in the flange of the seal carrier. This seal seals the piston rod from the supply space.
• a stationary seal can be arranged in the flange be, which seals the flange of the seal carrier to the spindle.
• FIG. 1 shows a first exemplary embodiment of the invention in a longitudinal section
• FIG. 2 shows the first exemplary embodiment from a front view in different (assembly) positions
• FIG. 3 shows another exemplary embodiment of the invention and FIG. 4 shows a greatly simplified representation of a
• the term "adapter” is used as a generic term for all components or assemblies that, with the aid of the clamping system according to the invention, are in a polygonal centering receptacle 7 of a spindle 1 can be stretched. It can be a tool (e.g. drill, milling cutter, lathe tool), an adapter (drill chuck, collet holder, cutting head for inserts), a device and much more.
• a tool e.g. drill, milling cutter, lathe tool
• an adapter drill chuck, collet holder, cutting head for inserts
• the invention is described using a rotatably mounted spindle 1 .
• the spindle 1 can also be a fixed spindle.
• the adapter 2 At its end facing the centering receptacle 7, the adapter 2 has a conical, polygonal outer contour, which is also referred to below as the outer polygon.
• the centering mount 7 is shaped to complement the outer polygon of the adapter 2 .
• the shape of the centering mount 7 is therefore also referred to as an inner polygon. This polygon connection has been established on the market for many years and is standardized in ISO 26623, for example.
• the adapter 2 includes a profiled hollow shank 102 which interacts with a clamping system 4 in the spindle 1 .
• These hollow shaft clamping systems have also been known to the person skilled in the art for many years, for example from the publications mentioned in the introduction to the description.
• the spindle 1 can be part of a power tool holder. D. H . the spindle 1 must be relatively compact in order to fit into the limited space of the tool holder. Therefore, the installation space that is potentially available inside the spindle 1 is limited in the radial direction by the outside diameter and the length of the spindle 1 .
• the clamping system 4 arranged in the spindle 1 must fix an adapter 2 with a hollow shank in the centering mount 7 in such a way that the adapter 2 or of the attached tool is guaranteed at all times.
• the torque required for machining and the radial and axial forces that occur must be reliably transmitted from the adapter 2 to the spindle 1 . Therefore, high clamping forces are required in the axial direction, which clamp the adapter 2 and spindle 1 to one another in order to transfer the resulting forces, torsional and bending moments.
• the clamping system 4 is generally clamped and released by a fluidically (e.g. pneumatically or hydraulically) actuated cylinder assembly 6 , which is also integrated into the spindle 1 . It is arranged behind the clamping system 4 in a stepped receiving bore 9 of the spindle 1 . Any other systems for applying high axial forces can be used as an alternative.
• a fluidically (e.g. pneumatically or hydraulically) actuated cylinder assembly 6 which is also integrated into the spindle 1 . It is arranged behind the clamping system 4 in a stepped receiving bore 9 of the spindle 1 . Any other systems for applying high axial forces can be used as an alternative.
• the cylinder assembly 6 and the clamping system 4 are from the front, d. H . through a center mount 7 (internal polygon) mounted on the spindle 1 .
• the consequence of this is that the maximum diameter of the clamping system 4 and cylinder structure 6 and the maximum diameter of the mounting hole 9 cannot be larger than the smallest inscribed circle of the centering mount 7 .
• the cylinder structure 6 comprises a piston rod 3 which merges into a tie bolt 5 of the clamping system 4 or is connected to him.
• the cylinder structure 6 has to provide comparatively large actuation forces on the piston rod 3 .
• a tried and tested means of increasing the actuating forces is to increase the diameter of the pistons of the cylinder assembly 6 .
• the maximum diameter is predetermined by the diameter of the receiving bore 9 . Therefore the diameter of the receiving bore 9 should be as large as possible.
• FIG. 1 the clamping system 4 and the cylinder assembly 6 are shown in two positions.
• the clamping system 4 is shown in the released position (release position) below the center line.
• the clamping system 4 is shown in the clamped position (clamped position) above the center line.
• the Buchbol zen 5 at least one clamping segment 33 is pivoted.
• the front end of clamping segment 33 is pivoted radially outwards, so that it enters a groove in hollow shaft 102 .
• the front end of the draw bolt 5 serves as a stop for the adapter 2 so that the clamping process can be carried out reliably both manually and automatically.
• the centering mount 7 is designed as an internal polygon. It can be an integral part of the spindle 1 . However, it can also be a separate component that is inserted into the spindle 1 .
• a section of the receiving bore 9 adjoining the centering receptacle 7 accommodates the clamping system 4 .
• Another adjoining section of the receiving bore 9 receives the cylinder structure 6 .
• the receiving bore 9 receives the clamping system 4 and the cylinder structure 6 , it is designed as a cylindrical bore with a shoulder 13 .
• the receiving bore 9 on the right-hand side in FIG. 1 is designed as a blind bore. That doesn't have to be the case, however.
• spindles 1 shown enable the assembly of clamping systems 4 and cylinder assemblies 6 by the polygonal centering mount 7, the outer diameter of clamping system 4 and cylinder structure 6 being approximately the same size as the smallest incircle of centering mount 7. As a result, the outer diameter of clamping system 4 and cylinder structure 6 can be maximized.
• the centering mount 7 is designed as a polygon (e.g. according to ISO 26623). This can be seen on closer inspection of Figure 1 z. B. because the distances between the lines 7.1 and 7.2 of the centering mount 7 are of different sizes from the center line shown in dot-dash lines.
• a shoulder 60 arranged concentrically to the center line is denoted by 60 on the end face of the spindle 1 .
• the points belonging to the lines 7.1 and 7.2 are shown in FIG. 2b.
• annular groove 65 is formed in the spindle 1 following the polygonal centering mount 7 .
• This circular ring groove 65 is arranged concentrically to the center line. It has a diameter that is equal to or larger than the circumference of the smallest internal polygon of the centering mount 7.
• the diameter of annular groove 65 is approximately as large as the diameter of the "high point" of the inner polygon, designated 7.1 in Figure 2b, at the transition between centering receptacle 7 and annular groove 65.
• the diameter of annular groove 65 can be smaller than the circumference of high point 7.1 of the polygon at the transition between centering mount 7 and annular groove 65.
• the diameter the annular groove 65 must in any case be somewhat larger than the inside diameter of the smallest polygon, but the axial forces that can be transmitted in the axial direction between the collar 67 and the annular groove 65 are then smaller. Efforts are therefore made to utilize the entire polygonal shape and to choose the diameter of the annular groove 65 as large as that shown in FIG.
• centering receptacle 7 is an internal polygon.
• the clamping system 4 comprises a spring housing 19.
• a collar 67 is formed at the front end (on the left in FIG. 1) of the spring housing 19. which in this exemplary embodiment also has a polygonal outer contour (see FIGS. 2a to c).
• the outer contour of collar 67 is dimensioned such that it is minimally smaller than the smallest inner polygon of centering mount 7 .
• the outer contour of collar 67 can, for example, be 0.1 mm smaller than the smallest inner polygon of centering mount 7 .
• the spring housing 19 can be inserted with its cylindrical part in a specific rotational position through the centering mount 7 into the part of the receiving bore 9 located behind the annular groove 65 . In this rotational position, the collar 67 fits through the polygonal centering mount 7 . This situation is shown in FIG. 2a.
• FIGS. 7 These figures represent a plan view of the polygonal centering mount 7 .
• the lines belonging to the centering receptacle 7 are designed as dash-two-dot lines.
• the lines belonging to the collar 67 are solid.
• the collar 67 is positioned in such a way that its outer contour has a smaller radius at each point than the smallest inner polygon of the centering receptacle 7 at this point. In the position of the collar 67 illustrated in FIG.
• the angle of rotation is 60° between those shown in FIGS. 2a and 2b turning positions .
• this can vary depending on the polygon shape.
• the width of the annular groove 65 is slightly greater than the width of the collar 67 so that the collar 67 can be rotated in the annular groove 65 .
• a small amount of play e.g. less than 0.1 mm
• the clamping system 4 and the cylinder structure 6 are axially fixed in both directions via the collar 67 and the annular groove 65, very narrow axial tolerances can easily be achieved.
• the width of the annular groove 65 can be made significantly wider than the width of the collar 67 . Only the left-hand shoulder of the ring groove 65 (in the direction of the centering mount 7) then assumes an axial position-determining and force-absorbing function. In the opposite direction, the support between the cylinder structure 6 and the spindle 1 can take place at a different point. For example via the intermediate floor 15 and the step 13 of the receiving bore 9 .
• the axial play depends on the sum of the component tolerances and is somewhat larger than in the exemplary embodiment shown in FIG.
• the existing game can also be set or adjusted as desired in FIG. 1, for example by shims or grinding in a component. be minimized . In the exemplary embodiments shown in FIGS.
• the outer contour of the collar 67 and the inner polygon of the centering receptacle 7 are geometrically similar. That does not have to be that way .
• the collar 67 could, for example, also consist of three lugs offset by 120°. It is important that the collar 67 fits through the smallest inner polygon of the centering mount 7 in a rotational position and that a positive connection in the axial direction is then established between the collar 67 and the spindle 1 by turning.
• the collar 67 is simply rotated counterclockwise by 60° from the rotational position shown in FIG. 2b (as shown in FIG. 2a). The form fit is then canceled and the collar 67 can be removed forwards through the centering mount 7 . Then the clamping system 4 and the cylinder assembly 6 can be removed through the centering mount 7 .
• a recess 69 is provided at a high point of the collar 67 in order to secure this form fit, which is produced by twisting and is formed in at least one axial direction.
• the recess 69 is located at 4:00 p.m. in FIG. 2a. In FIG. 2b it is at 6:00 p.m. This corresponds to the aforementioned angle of rotation of 60°.
• the locking pin 71 is accessible from the front of the spindle 1 .
• the threaded hole (sign without reference) in the spindle 1 runs approximately parallel to the centering mount 7 and ends in the annular groove 65 (see Figure 1).
• the locking pin 71 When the locking pin 71 is inserted far enough into the (threaded) bore, its front end protrudes into the annular groove 65 and dips into the recess 69 of the collar 67 . As long as the locking pin 71 dips into the recess, the spring housing 19 is secured against twisting.
• the screwing or Inserting the locking pin 71 from the face or front of the spindle 1 has several advantages:
• the locking pin 71 is easily accessible and can be reached without dismantling the tool holder, which means maintenance or Repair of the clamping system simplified.
• a particularly important advantage of the type of axial locking according to the invention and explained with reference to FIGS. 1 and 2 is that the diameter of the cylindrical part of the receiving bore 9 is maximized. This can be explained very well using FIG.
• a direct positive consequence of maximizing the diameter of the cylindrical part of the receiving bore 9 is that the space available for the cylinder structure 6 increases. This means that the diameter of the pistons 27 and 31 can be increased and, as a result, greater actuating forces can be provided by the cylinder structure 6 with otherwise the same boundary conditions. In addition, the radial installation space for the clamping system is maximized, which means that it can be built "more robustly”.
• a further advantage of the locking according to the invention via the collar 67 on the spring housing 19 in the spindle 1 is that the number of components is reduced.
• the cylinder structure 6 in FIG. 1 is briefly described below. Starting from shoulder 13 , an intermediate floor 15 and a cylinder sleeve 17 are arranged in receiving bore 9 .
• a spring housing 19 is provided in the receiving bore 9 next to the cylinder sleeve 17 .
• the spring housing 19 belongs to the clamping system 4 .
• the intermediate floor 15 and the cylinder sleeve 17 of the cylinder structure 6 are accordingly fixed axially in the axial direction by the step 13 and the spring housing 19 in the receiving bore 9 .
• the cylinder sleeve 17 also delimits a pressure chamber 37 of the cylinder structure 6 .
• the piston rod 3 protrudes through the opening 21 .
• a seal 23 is formed at the opening 21 and surrounds the piston rod 3 .
• the piston rod 3 has a shoulder 25 . Beginning at shoulder 25 , a piston 27 , a piston rod sleeve 29 and a piston 31 are lined up on piston rod 3 .
• the piston 31 is screwed onto the piston rod 3 at the right-hand end of the piston rod 3 in FIG.
• the piston 31 differs from the piston 27 primarily in two points: it fixes itself in the axial direction on the piston rod 3 and represents an axial security device for the piston 27 and the piston rod sleeves 29 .
• the outside diameter of the piston 31 runs directly in part of the receiving bore 9; there is no cylinder sleeve.
• the intermediate base 15 divides the space delimited by the cylinder sleeve 17 and the receiving bore 9 into two partial chambers.
• a piston 27 , 31 is located in both partial chambers.
• the pistons 27 and 31 in turn each subdivide a partial chamber into a first pressure chamber 35 and a second pressure chamber 37 . Because FIG. 1 shows the cylinder structure 6 and the clamping system 4 in two different positions, the pressure chambers 35 and 37 are of different sizes above and below the center line.
• the intermediate base 15 limits the travel of the piston 31 to the left in FIG. In this end position, the clamping system is open.
• three or more pistons can of course also be used arranged one behind the other on the piston rod 3, thereby further increasing or increasing the actuating force available on the Buchbol zen 5. the fluid pressure required to generate the necessary clamping force can be reduced.
• the pressure chambers 35 and 37 are supplied via control lines 39 , 41 .
• a first control line 39 is formed in the lower part of the spindle 1, which leads via a radial bore or recess (no reference sign) in the spindle 1 and at least one subsequent radial bore (no reference sign) in the cylinder sleeve 17 supplies the first pressure chamber 35 of the piston 27 with pressurized fluid if required.
• the second pressure chambers 37 are supplied with pressurized fluid via a second control line 41 (at the top in FIG. 1) and radially running bores or punctures in the spindle 1 (no reference numbers).
• the supply line is then routed into the pressure chamber 37 via at least one radial bore (unreferenced) in the cylinder sleeve 17 .
• the fluid is conducted into the fluid space 37 via grooves in the intermediate base 15 .
• the first pressure chambers 35 or the second pressure chambers 37 are pressurized and accordingly a force directed to the left or right in Figure 1 acts on the pistons 27 and 31 , which is transferred to the tie bolt 5 via the piston rod 3 .
• control lines 39, 41 there can be pilot operated non-return valves (not shown).
• the check valves like the control lines 39 and 41, are preferably opposite one another, i. H . offset by 180° in the circumferential direction.
• the spindle 1 is very well balanced in spite of the control lines 39 and 41 and the check valves. It also arises at high speeds only a relatively small dynamic imbalance. This can also be compensated for relatively easily by drilling holes in the circumference of the spindle 1 .
• the optionally available pilot operated check valves ensure that the fluid in the first pressure chambers 35 and the second pressure chambers 37 is held there, also against centrifugal forces that arise when the spindle 1 and with it the cylinder assembly 6 rotates. In addition, this keeps the piston rod 3 and the tie bolt 5 coupled to it in their positions. This means additional security for the clamping system 4 against unintentional loosening.
• the piston rod 3 and the tie bolt 5 are hollow drilled, see the through or central bore 47 .
• the seal carrier 59 is screwed into the spindle 1 .
• the seal carrier 59 includes a flange 75 and a threaded portion 77 with an external thread.
• An annular groove 79 is formed between the seal carrier 75 and the threaded section 77 .
• In the area of the threaded portion 77 is between the piston rod 3 and a gap is formed in the seal carrier 59 so that cooling lubricant can flow through one or more bores 81 from the annular groove 79 through the gap into the supply chamber 53 . From there, the cooling lubricant passes through the through-hole or central bore 47 into the area of the centering receptacle 7 or into the hollow shaft of the adapter 2 .
• a movement seal 51 is provided in the seal carrier 75, which interacts with a sealing section of the piston rod 3 and prevents the unintentional escape of cooling lubricant from the supply chamber 53 in the direction of the cylinder assembly 6 and the clamping system 4 and at the same time also the escape of fluid from the first pressure chamber 35 prevented in the supply room 53.
• a stationary seal is also provided between the seal carrier 75 and the spindle 1 . Both seals seal off the first pressure chamber 35 from the supply chamber 53 . They separate the fluid of the cylinder structure 6 from the cooling lubricant.
• This type of seal carrier 59 has several advantages:
• the seal carrier 59 is also very advantageous from a manufacturing point of view; it can be assembled and disassembled very easily.
• the seal carrier 59 is screwed in using a pin wrench, the pins of which move into complementary bores on the end face of the seal carrier 59 .
• FIG. 3 shows a further exemplary embodiment of the invention in a middle position between the opened and clamped state.
• the cylinder structure 6 comprises only one piston 27 which is guided directly in a cylindrical section of the receiving bore 9 and not in a cylinder sleeve 17 .
• This figure shows particularly well that the diameter of the piston 27 is almost as large as the inscribed circle of the centering mount 7 .
• FIG. 3 has fewer components, some details according to the invention can be seen better.
• the diameter D AB of the receiving bore 9 is shown in FIG. One can clearly see that the diameter D AB is just as large as the smallest inscribed circle of the center mount. In other words, based on the incircle diameter of the centering mount 7 specified by standards, the Locking of the clamping system 4 no space in the radial direction.
• the diameter of the mounting hole is significantly smaller than the smallest inscribed circle of the centering mount. Because, for example, there are paragraphs due to threads or stop edges.
• the collar 67 absorbs axial forces in both directions.
• the annular groove 65 is only wider than the collar 67 by a minimum required for production engineering. The axial position of the spring housing 19 and thus of the clamping set 4 can thus be adjusted very precisely.
• the piston 27 runs directly in a section of the stepped receiving bore 9 . It is possible that the piston 27 is not circular but has a polygonal outer contour. Accordingly, the associated section of the stepped receiving bore 9 is also designed as a polygon. As a result, the area of the piston 27 can be increased so that - the same fluid pressure and the same external dimensions of the spindle 1 provided -the actuating forces of the piston 27 are greater.
• FIG. 4 The arrangement of a tool holder 85 which is attached to a turret 83 of a machining center is illustrated with reference to FIG. In FIG. 4, only one place in the turret 83 is occupied by a tool holder 85 .
• the tool holder 85 carries a turning tool.
• the spindle 87 with an indicated jaw chuck carries the workpiece, so that the workpiece can be turned in the configuration shown.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Clamps And Clips (AREA)
• Gripping On Spindles (AREA)
• Cutting Tools, Boring Holders, And Turrets (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=84360231

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Family Cites Families (10)

• 2021
  • 2021-10-15 DE DE102021126778.1A patent/DE102021126778A1/de active Pending
• 2022
  • 2022-10-17 EP EP22808620.3A patent/EP4415906A1/de active Pending
  • 2022-10-17 JP JP2024515696A patent/JP2024537567A/ja active Pending
  • 2022-10-17 CN CN202280069082.8A patent/CN118119467A/zh active Pending
  • 2022-10-17 US US18/700,611 patent/US20250018478A1/en active Pending
  • 2022-10-17 WO PCT/EP2022/078806 patent/WO2023062240A1/de not_active Ceased

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