WO1989007996A1 - Systeme de changement d'outil - Google Patents

Systeme de changement d'outil Download PDF

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Publication number
WO1989007996A1
WO1989007996A1 PCT/DE1989/000098 DE8900098W WO8907996A1 WO 1989007996 A1 WO1989007996 A1 WO 1989007996A1 DE 8900098 W DE8900098 W DE 8900098W WO 8907996 A1 WO8907996 A1 WO 8907996A1
Authority
WO
WIPO (PCT)
Prior art keywords
tool
tool changing
changing system
unit
piston
Prior art date
Application number
PCT/DE1989/000098
Other languages
German (de)
English (en)
Inventor
Gerhard Michler
Herbert Clauss
Thomas Retzbach
Rainer Scherb
Original Assignee
Fritz Schunk Gmbh Fabrik Für Spannwerkzeuge
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.)
Filing date
Publication date
Application filed by Fritz Schunk Gmbh Fabrik Für Spannwerkzeuge filed Critical Fritz Schunk Gmbh Fabrik Für Spannwerkzeuge
Publication of WO1989007996A1 publication Critical patent/WO1989007996A1/fr

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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
    • B23B31/24—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
    • B23B31/305—Chucks characterised by features relating primarily to remote control of the gripping means using fluid-pressure means in the chuck the gripping means is a deformable sleeve
    • 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
    • B23B31/107—Retention by laterally-acting detents, e.g. pins, screws, wedges; Retention by loose elements, e.g. balls
    • B23B31/10741—Retention by substantially radially oriented pins
    • 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
    • B23B31/005—Cylindrical shanks of tools
    • 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
    • B23B31/107—Retention by laterally-acting detents, e.g. pins, screws, wedges; Retention by loose elements, e.g. balls
    • B23B31/1072—Retention by axially or circumferentially oriented cylindrical elements
    • 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
    • B23B31/107—Retention by laterally-acting detents, e.g. pins, screws, wedges; Retention by loose elements, e.g. balls
    • B23B31/1075—Retention by screws
    • B23B31/1076—Retention by screws with conical ends

Definitions

  • the invention relates to a tool changing system with a receiving body for a tool and / or workpiece to be picked up by means of a stretching device, with thin-walled outer wall areas in the mounting which are adjacent to a first chamber system filled with a pressure medium, with a displacement device , with which a hydrostatic pressure can be generated in the first chamber system, whereby the thin wall areas against the one to be absorbed
  • Tools are applied, that the same in the receiving cen- trierbar and / or exciting durable, ben with a first Kol ⁇ and filled with a pressure medium second Kammer ⁇ system that verbun ⁇ flow-connected with the first chamber system 'as well as with the is connected to the first piston in such a way that a pressure can be built up in the second and thus also in the first chamber system by moving this piston. is.
  • Tool changing systems of various types are known in which hydraulic fluid is used as the pressure medium.
  • the tool to be clamped is centered via a holding cone.
  • Another known embodiment uses a cylindrical receptacle, e.g. B. the so-called ABS system.
  • These tool clamping systems are secured and fastened, for example, by means of a bolt system which clamps the tool changing system in the spindle, or by means of a cylinder screw (expansion screw) which is arranged centrally and connects the tool changing system to the spindle.
  • a disadvantage of all previous systems are the poor roundness, due to the functional principle! properties.
  • the previous tool change systems are susceptible to contamination due to their "open" design.
  • ABS system has further disadvantages due to tension in the area and the inadequate controllable influence of the entire tension state.
  • Removable parts such as unsecured screws, represent danger points of previous tool change systems.
  • these clamping systems are unsuitable when it comes to the highest precision in concentricity and repeat accuracy.
  • these properties are of crucial importance, especially for high-speed machining.
  • a tool changing system of the generic type which has a first chamber system with only a single chamber, is not optimal in terms of its centering properties, which in turn has a negative effect on the concentricity and repeat accuracy.
  • there is a high manufacturing cost which places narrow limits on the economic use of such a tool changing system.
  • the invention has for its object to provide a tool changing system of the type mentioned, which is characterized by best concentricity and good repeatability and at the same time opens the way to a simplified and therefore cheaper production.
  • the tool changing system should also be able to be inserted into the receptacle without play. For safety reasons, there should not be any easily removable parts.
  • the Werk ⁇ tool change system should also insensitive against pollution Ver ⁇ "z. B. by cooling water and chips and his ness same time feature a high elasticity and great rigidity, which is absolutely necessary in view of the required high precision.
  • the tool changing system according to the invention is characterized in accordance with claim 1 in that the first chamber System contains several communicating chambers, which are aligned in groups of at least one chamber so that the tool can be centered and / or held in an exciting manner in the receiving body.
  • a very high centering accuracy can be achieved by dissolving the first chamber system into several independent chambers, since it is possible to first center the tool / workpiece specifically over certain contact surfaces and then to clamp it in the receptacle.
  • the tool changing system according to the invention is additionally characterized by a device for locking the tool, which has a particularly advantageous effect when such tool changing systems are used in the context of fully automatic production.
  • the pressure-generating displacement device has at least one first piston in the form of an annular piston, the central longitudinal axis of which coincides with the longitudinal axis of the receiving body, and the first chamber system contains one or more chambers communicating with one another.
  • the independent claim 24 of the body dividend ⁇ consists of 'at least two parts, namely a base unit and a stretching unit.
  • the stretching unit has the receptacle for a workpiece and / or tool to be held and the holding area of the base unit and the stretching unit are designed such that the first chamber system can be produced by joining the base unit and the stretching unit.
  • the basic unit is constructed from an outer base body and an inner base body according to the characterizing features of claim 42, the expansion unit is attached to the inner base body, a spring unit is present between the inner base body and the outer base body, and the outer base body is suitable for inclusion in a machine tool and forms a play-free bearing unit for the inner base body, which is only one Relative displacement activating the spring unit in the longitudinal direction of the axis of rotation of the basic unit enables.
  • the tool changing system is characterized in that a locking device is provided which is present in the locked state with little play, ie floating in the receiving body.
  • This floating bearing ensures that the clamped tool can always be precisely aligned in the base body; when the thin wall regions in the base body holding the tool are expanded, the thin ones that expand inward shift Wall areas the workpiece together with the locking device in the exact position for the workpiece.
  • Such a tool changing system is not only precisely positionable in a simple manner, but also safe to use, since if the pressure built up by the pressure medium drops, the workpiece cannot fall out of the base body due to its locking. Special embodiments for such a locking device can be found in subclaims 46 to 49.
  • Figure 1 is a schematic diagram of the tool changing system.
  • Fig. 2 is a schematic diagram of the cam ring
  • FIG. 3 shows the development of the cam ring according to FIG. 2;
  • FIG. 4 shows a further section through the tool change system according to FIG. 1;
  • Fig. 5 is a sectional view of the tool changing system of FIG. 1, through the expansion chambers in the untensioned
  • FIG. 6 shows a sectional illustration of the tool changing system according to FIG. 1, through the expansion chambers in the clamped state with the workpiece;
  • Fig. 7 is a Schn tdarstel ung 1 "by the tool change - the system of Figure 1, wherein only one expansion chamber.
  • FIG. 8 shows a basic illustration of a further embodiment of the tool changing system
  • FIG. 11 shows a basic illustration of a tool change system which is tensioned via a pull rod
  • FIG. 12 shows a basic illustration of a tool change system which is tensioned via a spring assembly
  • FIG. 13 shows a sectional illustration of a tool change system with a base unit and an expansion unit, the base unit t having an inner and outer base body and the inner base body being mounted in the outer base body;
  • Fig. 14 is a section tdarstel! by a tool changing system with an expansion unit and a base unit, the expansion unit having recesses from its side facing the base unit to form the first chamber system;
  • 15 shows a sectional view through a tool changing system with a base unit, stretching unit and locking device through the stretching unit; 16 shows a sectional view through the tool changing system according to FIG. 15 along the line 16-16.
  • a base body 1 of a tool changing system is firmly connected to a receptacle 3 by means of several screws 2.
  • the receptacle 3 is designed as a steep taper, for example.
  • the screws 2 are secured against unintentional loosening.
  • the connection of receptacle 3 and base body 1 can also be carried out in other ways, for. B. by gluing, soldering, welding or as a one-piece design.
  • the tool 4 is inserted into the receiving bore 5 of the basic body 1, locking pins 7 being pushed radially outward with the insertion part 6 which forms a front-side taper. As a result, locking pins 8 are made
  • the tooling 4 is centered and clamped via a cam ring 12.
  • the cam ring 12 has one or more bevels 13 or 23, the angle of inclination of which can be different.
  • the clamping piston 14, 24 engage in these bevels 13, 23 clamping piston 14, "24 a.
  • the cam ring 12 By rotating the cam ring 12 are these bevels 13, 23 with their D chtungs instituten 15, 25 axially displaced and in each case a specific defined hydrostatic pressure p or p is generated in two separate chamber systems 16 or 26, the chambers 18 and the expansion chambers 28 are thereby produced with the respective pressure via ring channels 17 or 27
  • Each chamber 18 interacts with a clamping bolt 20, which in turn presses against a locking pin 7.
  • the desired pressures p, p can be set as desired by the design dimensioning of the clamping pistons 14, 24 Pressure increase per degree of rotation of the cam ring 12 is determined by the respective angle of inclination of the bevels 13, 23.
  • expansion chambers 28 represent cylindrical indented cutouts and, in accordance with FIGS. 5, 6, are designed such that the pressure p z generated by the actuation of the cam ring 12 causes a certain deformation 29 of the expansion chamber 28, corresponding to FIG. 6.
  • the wall thickness s of the expansion chambers 28 is adapted to the particular clamping task. 5, 6, the tool 4 is centered on the center of the axis. This process can be seen from FIGS. 5, 6, where, for example, four groups of two expansion chambers 28 are circumferentially evenly distributed.
  • expansion chambers 28 can also be carried out.
  • the individual expansion chambers 28 can also be operated separately, i. H. if necessary, different hydrostatic pressures must also be applied. This can be advantageous according to the invention if the tool 4 initially has a certain measurable offset in the tool changing system, which is compensated for by the choice of a certain pressure distribution within the expansion chambers 28.
  • the advantage of the embodiment according to FIGS. 5, 6 is that the tool changing system can be constructed very stiffly due to the large number of expansion chambers 28.
  • the expansion chambers -28 can also be easily manufactured and manufactured is another advantage.
  • the clamping process of the tool 4 is initiated by further turning the cam 12. This is done in analogy to the centering process of the tool already described (cf. FIG. 1).
  • the sealing element 19 and clamping bolt 20 are pressed firmly against the locking pin 7.
  • the locking pins 7 cause a force component in the axial direction, which is greater than the centering force acting in the radial direction, via a bevel 21 of the pin 7 and the annular groove 11. This can be done constructively by specifying the respective chamber pressures p and p.
  • the tool 4 is pressed firmly against the plane system 10 in the longitudinal direction. In accordance with the invention this ensures that the central axis of the tool 4 and the central axis of the tool changing system are aligned in parallel and centered at the same time.
  • the tool 4 is thus securely clamped and centered. Additional mechanical securing in the event of a possible drop in pressure in the hydraulic system 16, 17, 18 is achieved by a plurality of securing balls 22 which limit the paths of the locking pins 7.
  • the tool 4 is thus secured in two ways. This is particularly important in the case of automatically controlled manufacturing processes.
  • a positioning pin 31 is provided according to the invention, which is provided in the area of the plane contact 10 between the tool 4 and the base body 1.
  • a coolant channel is designated 32.
  • the sealing element 33 prevents contamination of the tool changing system.
  • Another embodiment of the tool changing system according to the invention consists in designing the receptacle 3 of a tool changing system in such a way that it can be inserted into a second tool changing system and centered and clamped therein. This makes it possible, for example, to simulate an extension of the drive axis or to hold tools with different clamping diameters. This increases the flexibility of this clamping system with regard to its use.
  • the tool changing system can be operated manually, for example by means of a suitable wrench, or automatically.
  • automatic actuation it makes sense to lock the cam ring 12 by means of gripping pliers and to rotate the cam ring 12 and thus to actuate the tool change system via the spindle drive of the machine.
  • the tool changing system according to the invention can be used for the most varied fields of application. It is conceivable and possible to clamp tools of the most neat kind as well as to hold workpieces for clamping purposes.
  • the symmetrical structure and the rigid design are of decisive advantage, in particular at high rotational frequencies.
  • the system is therefore preferably suitable for high-speed machining.
  • the tool changing system has a vibration-damping effect. This ensures a high surface quality of the workpieces to be machined and a simultaneous increase in tool life. It is therefore readily apparent that an important application of this tool changing system is in the area of modern manufacturing processes. In particular, this is due to the features mentioned such as highest round! Accuracy, double security when clamping, insensitivity to dirt, rigid construction with large clamping forces and increased service life of the insert tools achieved through good vibration damping properties.
  • FIG. 8 is a schematic 'diagram of another Ausure ⁇ tion the tool change system illustrated.
  • a clamping nut 34 meshes on an external thread 35 present on a base body 1.1. By screwing in the clamping nut 34 by means of the thread 35, it is displaced in the axial direction. Contamination of the thread 35 and of an annular piston 36, which corresponds functionally to the tensioning piston 24 and which is present radially symmetrically to the longitudinal axis, is prevented by a sealing element 37. If the clamping nut 34 r is actuated, the annular piston 36 is simultaneously displaced accordingly. To reduce the friction losses, several balls 38 or other friction-reducing elements are provided here.
  • the annular piston 36 generates a hydrostatic pressure in the chamber system 40 via the ring-shaped sealing element 39, which is supplied via capillaries 41 to a centrally arranged expansion chamber 28.1.
  • the deformation and thus the clamping force of the tool change can therefore be achieved via the clamping nut 34 Systems can be adjusted dosed.
  • a tool 4.1 is provided with a shaft 42 slotted at its end.
  • the design of the tool shank 42 ensures that, as a result of the centrifugal force at high rotational frequencies, an additional holding force is generated which acts as an additional dynamic stabilization.
  • FIG. 9 shows the basic illustration of a tool change system which is stretched over a spiral ring.
  • a tool 4.2 is inserted into a base body 1.2, which is clamped and fixed via a spiral ring 43
  • spiral-shaped recesses 44 are machined into the spiral ring 43, in which one or more locking pins 7.1 are guided, which serve to fix the position of a tool 4.2, and further spiral-shaped recesses 45 are used to tension pistons 24.1 and sealing
  • the locking pins 7.1 are here, for example, introduced into the fixing groove 46 of the tool 4.2, the locking pins 7.1 are guided over the spiral recesses 44. 25th
  • tool changing system of FIG. 11 is a tool 4.3 and / or the workpiece via a drawbar '47 which is centrally passed through a spindle 48 of the Werk ⁇ generating machine, tensioned.
  • a thread 49 is provided here as an example to secure the tool 4.3.
  • the tool 4.3 is seated in a base body 1.3, which in turn is to be fastened in the spindle 48. Both the tool in the base body and the base body In the spindle are held by means of the stretching technology.
  • a tensioning piston 24.2 with the sealing element 25.2 is simultaneously axially displaced and a hydrostatic pressure is generated in a chamber system 26.2 in the base body 1.3.
  • This pressure is generated via first capillaries 41.1 fed to a first expansion chamber 28.3, which is present in the outer circumferential area of the base body. Further capillaries 41.2 branch off from this expansion chamber 28.3 to form a further expansion chamber 28.4, which is present in the inner peripheral region of the base body 1.3.
  • the base body can be clamped in the spindle via the first expansion chamber 28.3 and the tool can be clamped in the base body via the second expansion chamber 28.4.
  • the tool 4.3 can also be non-positively centered and clamped.
  • the force required to actuate the tensioning piston 24.3 is applied by a spring assembly 50, in this case, for example, a disk spring assembly, which is introduced into the base body 1.4.
  • the spring assembly 50 transmits its force via an intermediate element 51 to one or more transmission pins 52, which in turn actuate both the tensioning piston 24.3 and the locking pin 7.2.
  • the locking pins 7.2 engage in a fixing groove 46, which is located in a tool 4.4, ' egg n.
  • the spring assembly 50 can be tensioned again, for example.
  • the expansion sleeve 68 designed as a cylindrical sleeve has on its outside an upper annular groove-like recess 70 and a lower annular groove-like recess 71.
  • the expansion sleeve 68 is guided in the first base body 64 by means of a first press fit 72 and a second press fit 74 within a bore 75 present in the first base body 64.
  • a fixing device in the special embodiment example a union nut 76, is provided.
  • the design of the fixing device as a flange ring can be considered.
  • the thread of the union nut 76 engages in an external thread provided on the first base body 64.
  • the thread surfaces of the union nut 76 and those of the external thread can be glued together.
  • the expansion sleeve 68 and the first base body 64 are designed in the end region facing the workpiece to be clamped in such a way that the expansion sleeve 68 is pressed onto the first base body 64 via corresponding contact surfaces 77 when the union nut 76 is screwed in, as a result of which both an axial fixation and a torque ⁇ ment fixation of the expansion sleeve 68 is guaranteed.
  • the wall thickness of the cylindrical sleeve of the expansion sleeve 68 is somewhat reduced.
  • an O-ring is arranged in the wall of the first base body as a sealing means, so that when the expansion sleeve 68 is inserted in the first base body 64, the expansion ring 68 Rings 78 lying outer wall areas of the expansion sleeve 68 and the wall of the bore 75 of the first base body 64, a chamber system is formed.
  • the O-rings 78 are special plastic rings that ensure the tightness of the chamber system even with large pressures.
  • An 'this chamber system includes an existing basic body 64 in the first oil passage 80 on, with about the chamber system
  • Hydraulic oil is supplied.
  • This oil passage 80 is not engaged with one another in Fig. 13 in detail dargestell th 'zwei ⁇ th chamber system in connection which can be acted upon in a conventional manner with pressure, whereby the expansion sleeve in the region between the annular groove-like recesses 70, 71 to the rotational axis R expands the hydraulic expansion chuck and thereby enables centering and / or clamping of a workpiece.
  • a pin can alternatively be provided in the area below the lower annular groove-like recess of the expansion sleeve.
  • a flanged edge is provided in the region of the opening of the bore 75 of the base body 64, which is deformed accordingly after the expansion sleeve has been installed in order to secure the expansion sleeve in its installed position.
  • the end face of the stretching unit could be smooth and with a larger size
  • the expansion sleeve then has, as it were, a circumferential, transversely projecting collar on the end face, through which it can be fastened to the first base body with the aid of, for example, screws, rivets or the like.
  • the expansion unit thus receives an axial fixation as well as a torque fixation.
  • a chamber system is created from the expansion sleeve and base body.
  • the second base body 66 has a conical shape, the outer wall regions 79 of which are inclined in accordance with the cone 1 of the work spindle 20.
  • the first base body 64 is mounted without play, in such a way that a relative displacement between the two base bodies in the direction of the axis of rotation R of the hydraulic expansion chuck 60 is possible, but a relative movement perpendicular to the axis of rotation R is prevented.
  • the first base body 64 has flange regions 82 which protrude beyond the second base body 66 and which at least in regions have outer surfaces 84 which are designed in accordance with the shape of the opposite outer surfaces of the working spindle 62.
  • the above-described mounting of the first base body 64 in the second base body 66 is ensured by means of linear ball bearings 86.
  • a plate spring assembly 87 is arranged symmetrically to the rotation axis R.
  • the hydraulic expansion chuck 60 is introduced, the same is first drawn into the conical recess of the spindle by means of a pull bolt 88.
  • the outer surface 79 of the second base body 66 lies against the inner wall of the spindle cone.
  • the first base body 64 can be drawn further into the spindle by means of the pull bolt 88. This is a in the plate spring assembly 87
  • sealants for example an O-ring 89 present in the wall of the second basic body 66, are present between the first basic body 64 and the second basic body 66.
  • FIG. 14 there is a base body 92 suitable as a taper 1 cone and an expansion sleeve 96 containing the receptacle 94 for a workpiece.
  • the expansion sleeve 96 like the expansion sleeve according to FIG. 13, is fixed in the installed state with respect to the position of the base body 92 by means of a union nut 98.
  • the expansion sleeve 96 is also guided by means of a first press fit 100 and a second press fit 102 in the corresponding contact surfaces of the base body 92.
  • the expansion sleeve 96 From the side facing the base body 92, the expansion sleeve 96 initially has open recesses 104 which are arranged parallel to the axis of rotation R of the expansion chuck 90 and which, when the expansion sleeve 96 is installed, form the first chamber system in the base body 92.
  • this chamber system is formed by an annular recess 104 arranged around the receptacle 94.
  • the sealing This chamber system 104 is operated by means of an O-ring 106 which is introduced into the recess 104 and is, for example, mounted on a support ring 108, this Teflon ring being supported on an inserted steel ring 110.
  • the steel ring In the installed state of the expansion sleeve 96, the steel ring is supported on a correspondingly opposite flat surface of the base body 92.
  • This steel ring 110 is used as an insert and is used to set the active clamping length of the expansion sleeve 96.
  • the recesses 104 are preferably produced by electrical discharge machining.
  • a bore 112 which forms the first half of an oil channel, adjoins the recess 104 and runs obliquely downwards.
  • a corresponding second bore 114 is present in the base body 92 and forms the other half of the oil channel.
  • a further chamber system adjoins this oil channel, which can be loaded with the pressure required for clamping a workpiece, and which is not shown in FIG. 14.
  • a circumferential ring channel 116 is provided on the outside of the expansion sleeve 96 facing the base body 92 at the level of the opening of the first bore 112, so that the expansion sleeve 96 can be installed in any rotated position relative to the base body 92 without the hydraulic Connection of the first half 112 of the oil channel and the second half 114 of the oil channel is interrupted.
  • This ring channel 116 is sealed by means of two 0-rings correspondingly arranged on the outside or inside of the ring channel 116.
  • the base body 122 In the hydraulic expansion chuck 120 shown in FIG. 15, only its upper part, the base body 122, is shown in section.
  • An expansion sleeve 124 is inserted in this base body 122. It is designed in its upper and lower area as a cylindrical sleeve such that it fits snugly in the area of its upper and lower end-side outer wall areas in the longitudinal bore 130 of the base body 122.
  • this expansion sleeve 124 In its central area, this expansion sleeve 124 has a circumferential annular bead 132. Its transverse extent is such that it also fits snugly in the base body 122 with a fit 134 or 136, 138.
  • a pressure sleeve 140 with an L-shaped cross section is used, which rests against the annular bead 132 both from above and laterally. Their pressing contact on the annular bead 132 is ensured by means of a screw 142, which can be screwed 144 into the base body 122 such that it can exert a corresponding pressure on this pressure sleeve 140.
  • the annular bead 132 is thus clamped in the longitudinal direction between the pressure sleeve 140 and the base body 122.
  • annular bead 132 there is an annular gap between the base body 122 and the longitudinal bore 130 such that a lower chamber 146 surrounding the expansion sleeve in a ring-like manner is formed by the latter.
  • This chamber 146 is sealed towards the bottom by an O-ring 148, which in turn is between an upper support ring 149 and a lower support ring.
  • ring 150 is present. The presence of the ring 149 allows the amount of pressure medium in the lower chamber 146 to be reduced.
  • annular bead 132 there is an annular gap which also surrounds this area and which, like the lower chamber 146, represents an upper chamber 152.
  • This chamber 152 is sealed at the top by an O-ring 154, which in turn is supported in a positional manner on a support ring 156.
  • annular groove 162 or 164 which is triangular in cross section in the drawing, and which have a line connection with the lower chamber 146 and with the upper chamber 152.
  • the lower annular groove 162 is connected to an oil supply (not shown in more detail) via a tap hole which represents an oil channel 166.
  • the pressure medium flowing through the oil channel 166 thus passes into the lower annular groove 162 and from there into the lower chamber 146 and through the two longitudinal bores 158 and 160 into the upper annular groove 164 and further into the upper chamber 152 0-rings 148 and 154 prevent this pressure medium from escaping in the longitudinal direction upwards and downwards from the chambers 146 and 152, respectively.
  • An additional 0-rings 168 or 170 between the annular bead 132 and the pressure sleeve 144 or the base body 122 also prevents the pressure medium from escaping in these areas.
  • the walls of the expansion sleeve 124 which are adjacent to the lower chamber 146 or upper chamber 152, are expanded so that a tool inserted into the longitudinal bore 190 of the expansion sleeve 124 in these areas,. H. twice in the longitudinal direction, is held in the base body 122.
  • this transverse bore 172 there is a locking device 174 designed as a rotating part, the outer dimensions of which are smaller than the diameter of the bore, so that it sits in this transverse bore 172 with play.
  • the longitudinal extent of this locking device which is designed as a clamping bolt, ie its extension in the transverse direction, is somewhat smaller than the clear dimensions of the base body 122 in this area, so that it also sits with play in the base body 122 in the transverse direction.
  • this clamping bolt 174 In its intersection with the longitudinal bore 130, this clamping bolt 174 has a longitudinal bore 176.
  • a tool seated in the longitudinal bore 190 can thus be inserted through the clamping bolt 174 unhindered.
  • a snap ring 178 is provided in the lower region of the expansion sleeve 124 and serves as a support for the lower end of a tool.
  • transverse bore 180 in the clamping bolt 174 which is equipped with an internal thread and which ends in the region of the longitudinal bore 176.
  • a clamping screw 184 is screwed into this transverse bore 180.
  • a tool inserted in the longitudinal bore 190 can be held by means of this clamping screw 184. This hold can be ensured by positive and / or non-positive connection with the tool shank.
  • the clamping screw 184 is accessible from the outside through a lateral bore 186 provided in the base body 122. Because the clamping screw 184 is fastened to the clamping bolt 174, but the latter is floatingly supported in the base body 122, the tool locked by the clamping screw 184 is also floatingly supported in the base body.
  • an already locked tool When activating the print medium, an already locked tool can be moved in the transverse direction so that it is exactly aligned axially.
  • the expansion chuck 120 described above has the great advantage that the locking effect caused by the clamping screw 184 is integrated into the expansion sleeve 124 and cannot impair the expansion movements caused by the expansion sleeve 124.
  • the lock is used to secure the tool in the base body in the event of pressure loss in the hydraulic system, for example.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gripping On Spindles (AREA)

Abstract

Un système de changement d'outil comportant un élément de fixation (1) destiné à un outil (4) à fixer au moyen d'un mandrin expansible et/ou à une pièce à usiner, de minces régions de paroi extérieure étant ménagées dans l'élément de fixation, un dispositif de déplacement pour générer une pression hydrostatique en vue de déformer les minces régions de paroi extérieure, avec un premier piston et un second système de chambres rempli d'un milieu hydraulique, est caractérisé en ce que le premier système de chambres renferme plusieurs chambres (28) communiquant entre elles et alignées par groupes d'au moins une chambre de manière à permettre le centrage et/ou le mandrinage de l'outil dans n'importe quelle position dans l'élément de fixation.
PCT/DE1989/000098 1988-02-23 1989-02-22 Systeme de changement d'outil WO1989007996A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3805527.9 1988-02-23
DE3805527A DE3805527A1 (de) 1988-02-23 1988-02-23 Werkzeugwechselsystem

Publications (1)

Publication Number Publication Date
WO1989007996A1 true WO1989007996A1 (fr) 1989-09-08

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Application Number Title Priority Date Filing Date
PCT/DE1989/000098 WO1989007996A1 (fr) 1988-02-23 1989-02-22 Systeme de changement d'outil

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DE (1) DE3805527A1 (fr)
WO (1) WO1989007996A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4015149A1 (de) * 1990-05-11 1991-11-14 Renate Ruf Dehnspannfutter
FR2728818A1 (fr) * 1995-01-03 1996-07-05 Hydra Lock Corp Porte-outil avec et sans outil, et ensemble a porte-outil et mandrin
CN109434532A (zh) * 2018-11-28 2019-03-08 苏州市职业大学 气动式换刀装置

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DE19840606A1 (de) 1998-09-05 2000-04-13 Witzig & Frank Gmbh Werkzeugwechseleinrichtung
DE19957218B4 (de) * 1999-11-27 2005-10-20 Actech Gmbh Adv Casting Tech Anordnung zum automatischen Wechsel von Schaftwerkzeugen an einer Antriebsspindel von Bearbeitungsmaschinen
GB0411686D0 (en) * 2004-05-25 2004-06-30 Westwind Air Bearing Ltd Hydraulic chucks
DE202009000804U1 (de) * 2009-01-22 2010-03-11 Elha-Maschinenbau Liemke Kg Werkzeugmaschine
DE102012111456C5 (de) * 2012-11-27 2017-07-13 Kennametal Inc. Hydraulisches Dehnspannfutter und Verfahren zur Herstellung eines solchen Dehnspannfutters

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FR884305A (fr) * 1942-07-20 1943-08-10 Perfectionnements apportés aux dipositifs de serrage pour machinesoutils
DE745845C (de) * 1939-12-02 1944-05-15 Hans Johann Hofer Einspannvorrichtung fuer Werkzeugmaschinen
DE761210C (de) * 1939-12-02 1953-08-31 Hans Johann Hofer Einspannvorrichtung fuer Werkzeugmaschinen
US2826420A (en) * 1954-01-08 1958-03-11 Karl A Klingler Hydraulic holding means for chucks and the like
FR2181126A5 (fr) * 1972-04-18 1973-11-30 Trois P Prototypes Preci
US4116453A (en) * 1977-05-02 1978-09-26 Andre Eugene R Multi-part pressure chuck
DE2721337A1 (de) * 1977-05-12 1978-11-23 Hans Werner Dipl Ing Loeckmann Klemmring
GB2097300A (en) * 1981-04-24 1982-11-03 Roehm Guenter H Clamping mandrel having a hydraulically expansible clamping sleeve
GB2112677A (en) * 1981-12-09 1983-07-27 Hurth Verwaltungs Gmbh Expansion device for axial and radial clamping of annular member on a mandrel
US4402449A (en) * 1980-08-25 1983-09-06 Dubois Sr Russell E Method of making an expandable mandrel having a thin cylindrical sleeve and a pair of thick wall arcular ends
DE8505534U1 (de) * 1985-02-27 1985-05-30 Messerschmitt-Bölkow-Blohm GmbH, 8012 Ottobrunn Spannvorrichtung an Werkzeugmaschinen
CH649728A5 (en) * 1979-11-29 1985-06-14 Schrepfer Rudolf Fastening device for tools having a cylindrical shank
DE8518206U1 (de) * 1985-06-22 1985-08-01 Ledermann Gmbh + Co, 7240 Horb Antriebseinheit für rotierende Schaftwerkzeuge
EP0227620A2 (fr) * 1985-12-09 1987-07-01 Waco Jonsereds AB Porte-outil avec dispositif de sécurité
DE3612243A1 (de) * 1984-12-19 1987-10-22 Gte Valeron Corp Einrichtung zum verbinden eines auswechselbaren werkzeugkopfes mit einer werkzeugspindel
DE3631445A1 (de) * 1986-09-16 1988-03-17 Praezisions Werkzeug Und Spann Hydraulische dehnspanneinrichtung

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE745845C (de) * 1939-12-02 1944-05-15 Hans Johann Hofer Einspannvorrichtung fuer Werkzeugmaschinen
DE761210C (de) * 1939-12-02 1953-08-31 Hans Johann Hofer Einspannvorrichtung fuer Werkzeugmaschinen
FR884305A (fr) * 1942-07-20 1943-08-10 Perfectionnements apportés aux dipositifs de serrage pour machinesoutils
US2826420A (en) * 1954-01-08 1958-03-11 Karl A Klingler Hydraulic holding means for chucks and the like
FR2181126A5 (fr) * 1972-04-18 1973-11-30 Trois P Prototypes Preci
US4116453A (en) * 1977-05-02 1978-09-26 Andre Eugene R Multi-part pressure chuck
DE2721337A1 (de) * 1977-05-12 1978-11-23 Hans Werner Dipl Ing Loeckmann Klemmring
CH649728A5 (en) * 1979-11-29 1985-06-14 Schrepfer Rudolf Fastening device for tools having a cylindrical shank
US4402449A (en) * 1980-08-25 1983-09-06 Dubois Sr Russell E Method of making an expandable mandrel having a thin cylindrical sleeve and a pair of thick wall arcular ends
GB2097300A (en) * 1981-04-24 1982-11-03 Roehm Guenter H Clamping mandrel having a hydraulically expansible clamping sleeve
GB2112677A (en) * 1981-12-09 1983-07-27 Hurth Verwaltungs Gmbh Expansion device for axial and radial clamping of annular member on a mandrel
DE3612243A1 (de) * 1984-12-19 1987-10-22 Gte Valeron Corp Einrichtung zum verbinden eines auswechselbaren werkzeugkopfes mit einer werkzeugspindel
DE8505534U1 (de) * 1985-02-27 1985-05-30 Messerschmitt-Bölkow-Blohm GmbH, 8012 Ottobrunn Spannvorrichtung an Werkzeugmaschinen
DE8518206U1 (de) * 1985-06-22 1985-08-01 Ledermann Gmbh + Co, 7240 Horb Antriebseinheit für rotierende Schaftwerkzeuge
EP0227620A2 (fr) * 1985-12-09 1987-07-01 Waco Jonsereds AB Porte-outil avec dispositif de sécurité
DE3631445A1 (de) * 1986-09-16 1988-03-17 Praezisions Werkzeug Und Spann Hydraulische dehnspanneinrichtung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4015149A1 (de) * 1990-05-11 1991-11-14 Renate Ruf Dehnspannfutter
FR2728818A1 (fr) * 1995-01-03 1996-07-05 Hydra Lock Corp Porte-outil avec et sans outil, et ensemble a porte-outil et mandrin
CN109434532A (zh) * 2018-11-28 2019-03-08 苏州市职业大学 气动式换刀装置

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