EP0503109B1 - Outil à galeter à rouleaux - Google Patents

Outil à galeter à rouleaux Download PDF

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Publication number
EP0503109B1
EP0503109B1 EP91103818A EP91103818A EP0503109B1 EP 0503109 B1 EP0503109 B1 EP 0503109B1 EP 91103818 A EP91103818 A EP 91103818A EP 91103818 A EP91103818 A EP 91103818A EP 0503109 B1 EP0503109 B1 EP 0503109B1
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EP
European Patent Office
Prior art keywords
support member
groove
tool
tool according
curved surface
Prior art date
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 - Lifetime
Application number
EP91103818A
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German (de)
English (en)
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EP0503109A1 (fr
Inventor
Alfred Ostertag
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.)
Hegenscheidt MFD GmbH and Co KG
Original Assignee
Wilhelm Hegenscheidt GmbH
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
Priority to AT91103818T priority Critical patent/ATE117616T1/de
Application filed by Wilhelm Hegenscheidt GmbH filed Critical Wilhelm Hegenscheidt GmbH
Priority to ES91103818T priority patent/ES2067071T3/es
Priority to DE59104421T priority patent/DE59104421D1/de
Priority to EP91103818A priority patent/EP0503109B1/fr
Priority to HU913596A priority patent/HU207962B/hu
Priority to CS913510A priority patent/CS351091A3/cs
Priority to JP3327817A priority patent/JPH0747264B2/ja
Publication of EP0503109A1 publication Critical patent/EP0503109A1/fr
Application granted granted Critical
Publication of EP0503109B1 publication Critical patent/EP0503109B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B39/00—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor
    • B24B39/02—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor designed for working internal surfaces of revolution
    • B24B39/023—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor designed for working internal surfaces of revolution the working tool being composed of a plurality of working rolls or balls

Definitions

  • the invention relates to tools with a smooth rolling head for machining surfaces on workpieces with a circular cross-sectional circumferential surface, the smooth rolling head having at least three tapered rolling rollers, which are held by a roller cage on a tapered track of a support part, which on the one hand, directly or via other means is connected to a tool holder, and wherein means for generating an actuating force are provided and are connected at least for the axial change in position of the support part relative to the roll rollers, an axial change in position of the support part causing a proportional radial change in position of the roll rollers.
  • Tools of this type are provided for machining bores of cylinder tubes and bores in any workpieces, but also for machining surfaces of shafts and shaft journals, i.e. cylindrical or slightly tapered surfaces and thus surfaces with a circumferential circular surface.
  • a “device for finishing cylindrical surfaces” has been published.
  • This tool is designed in such a way that rolling forces which are exerted on the workpiece by rolling rollers are generated by the relative displacement of a support cone with respect to the rolling rollers.
  • the tool diameter or more precisely its working diameter, is simultaneously set during this shift and is reached when the rolling rollers rest on the workpiece and the rolling force builds up.
  • the tool diameter is thus adapted or adaptable to the respective workpiece diameter at the start of a machining process.
  • a nominal dimension with a tolerance is provided for the pre-machining of workpiece sections that are to be machined with such a tool.
  • Workpiece sections produced according to such a dimension specification are dimensionally stable if the dimension achieved corresponds to the nominal dimension within the specified tolerance.
  • the dimension produced on a workpiece can now be a maximum dimension or a smallest dimension.
  • Such a dimensional difference can exist one or more times on a pre-machined workpiece section if the largest and smallest dimensions occur together.
  • Such a workpiece is quite true to size. If such a workpiece is machined with the tool described at the beginning, it is easy to set the rolling force and also the tool diameter at the beginning of the machining.
  • the rolling force increases undesirably high for bore sections which have a smaller bore diameter because the tapered roller rollers, from the support cone supported, take the largest dimension of the hole and cannot give in radially.
  • the difference in force between the actual rolling force and the rolling force caused by the fluid cylinder exerts an additional force on the supporting cone via the rolling rollers, which is intended to counteract the actuating force of the fluid cylinder and to push back the supporting cone, but because of the friction between the rolling rollers and the raceway of the supporting cone as well as the subsequent hysteresis caused by mutually movable components cannot develop their desired effect.
  • a satisfactory, frictional rolling is not achieved.
  • tools for machining cylindrical surfaces of shafts and shaft journals are known, on which the diameter adjustment is carried out by moving an annularly shaped support cone relative to the rolling rollers. The same problems mentioned above occur with these tools.
  • the object of the invention is to propose tools of the type described in the introduction with which an improved frictional rolling can be achieved.
  • this object is achieved in that, in a generic tool, the support part with a cylindrically curved surface concentric to the tapered raceway is rotatably and axially movably mounted on a receiving piece with an associated cylindrically curved surface, the supporting part and receiving piece being connected to one another by means of a driver , which consists of at least one groove formed in at least one assigned, cylindrically curved surface and extending at a non-self-locking slope to its longitudinal axis and of at least one driver which cooperates with at least one groove and engages in at least one groove, the direction of the slope of the groove and the taper inclination of the tapered raceway are coordinated with one another such that when a torque proportional to the actuating force is exceeded on the supporting part, the supporting part is axially displaced against the direction of the actuating force.
  • a driver which consists of at least one groove formed in at least one assigned, cylindrically curved surface and extending at a non-self-locking slope to its longitudinal axis and of at least
  • the rolling rollers have, in a manner known per se, an inclination which is inverse to the tapering of the supporting part, so that they leave a line contact on the workpiece or a drop-like surface, which is also known per se.
  • the latter is achieved in that the cone angle of the rolling rollers is smaller than the cone angle of the support part by a few minutes.
  • the rolling rollers When machining a workpiece, the rolling rollers roll between the surface of the workpiece to be machined and the tapered raceway of a support part and exert a rolling force on the workpiece.
  • This rolling force is proportional to the actuating force with which the support part is moved axially. Because of the tapered raceway, these axial movements push the roller rollers radially outward with a force that corresponds to the positioning force, taking into account the taper angle of the raceway. The rolling force is therefore proportional to the positioning force.
  • the described movements of the individual tool parts are also possible in the opposite direction. If the bore diameter becomes larger in the case of a bore surface to be machined, the rolling force predetermined by the actuating force decreases. The steep force then shifts the support member on the receiving piece, the support member performing a rotational movement in the manner already described with such a sense of direction that the resulting axial movement in turn moves the rolling rollers radially outward until the desired rolling force is reached again.
  • the hysteresis is significantly reduced, so that the desired rolling force can be maintained much more accurately.
  • This also makes it possible, and this is a crucial aspect, to use an angle of inclination of the tapered raceway which is in the area of self-locking.
  • the actuating forces can be kept very small to generate a specific rolling force, which in turn reduces hysteresis and enables the use of smaller components.
  • the smaller forces that occur at the various transmission elements also ensure less wear on the tool in the area of the components that are not directly involved in the machining of the workpiece.
  • the gen. Entrainment can be designed in a variety of ways in the construction according to the invention without departing from the functional principle shown. It is thus possible to use a component consisting of a threaded bolt and a threaded nut, in which the thread has a non-self-locking angle of inclination (Fig. 4).
  • the necessary thread can also be designed in the form of a spiral groove with a corresponding pitch angle, such a spiral groove being able to be provided in one of the two associated components, while a fixed driver part projecting into the groove is provided with the other component.
  • this one fixed driver part it is also possible to provide a corresponding groove in the assigned component, which runs exactly opposite the first-mentioned groove, and then both grooves e.g.
  • rollers or balls fill up with rollers or balls.
  • one of the two opposing grooves must be longer than the other and only the shorter groove must then be filled with the rollers or balls.
  • a correspondingly wound wire or a similar component can also be inserted.
  • the tool can be built both as an internal machining tool and as an external machining tool.
  • the support part must be designed as a support mandrel, while in the second part it must be designed as a support ring got to.
  • the support mandrel here has an inner cylindrical surface, that is to say a bore which can be pushed onto a correspondingly cylindrical part of the shaft of a receiving piece. If the support part is designed as a support ring, this support ring can have a cylindrical outer surface which is inserted into a corresponding receiving piece which is shaped as a sleeve, so that the support part is movable in this sleeve.
  • the necessary actuating force for displacing the support part can be generated by a spring but also by a fluid cylinder.
  • the spring designed as a helical spring, can have a sufficiently flat characteristic curve so that the axial movements of the support part do not result in any significant change in the spring force and thus the actuating force. It should also be borne in mind here that the axial movements of the supporting part that actually occur are very small, so that the corresponding spring travel and thus the changes in force on the spring are also very small.
  • Another advantage of the solution according to the invention is that the proposed construction allows the production of tools for machining small diameter bores.
  • the tool shown in Figure 1 is intended as a tool for machining bores with larger diameters.
  • the receptacle 1 is connected to a so-called boring bar 2, which does not belong to the tool, via the thread 3.
  • the boring bar 2 is in turn received by a machine tool, not shown here.
  • the receiving piece 1 is also firmly connected to the bearing part 4 by screws, not shown.
  • the thrust bearing 5 is held and supported by the bearing part 4.
  • the thrust bearing 5 in turn supports a ring 6 on which the roller cage 7 is fastened with screws, not shown.
  • the bearing part 4 is rotatably connected to the ring 6 by means not shown to form ring 6.
  • the roller cage 7 carries the tapered roller rollers 8, which roll on the tapered raceway 30 of the support part 9.
  • the support part 9 is slidably received in the cylindrically curved surface 10 designed as a bore by the receiving piece on a corresponding, cylindrically curved surface 121.
  • the support part 9 is held by the thrust bearings 11 and 12 with the disks 19 and 20 on the receiving piece 1 and by the fluid cylinder 15 with cap 16 via thrust piece 14 with the bolts 17, which are firmly connected to the thrust piece 14 and in sleeve 18 engage against the spring 13, which is supported against the end piece 21, which is fastened to the shaft 1 with the screw 22 and the feather key 23.
  • the fluid cylinder 15 is held and clamped between the receiving piece 1 and the boring bar 2 via an adapter 24, which carries the fluid cylinder 15.
  • the processing sequence with such a tool is as follows: In the starting position, as shown in FIG. 1, the tool is brought into contact with a workpiece 25 with the roller rolls 8, the workpiece 25 and tool rotating relative to one another in the working direction.
  • the fluid cylinder 15 is charged via port 27 with a fluid under a defined pressure and the piston rod 28 with cap 16 is under the defined actuating force 29 developed by the fluid cylinder 15 against the Spring 13 moved.
  • the pressure piece 14 with the bolts 17, sleeve 18, disc 20 with thrust bearing 11 and the support member 9 are also moved.
  • the support part 9 moves the tapered rolling rollers 8 radially outwards against the bore wall of the workpiece bore 26, a defined rolling force 31 then building up, which now acts on the bore wall.
  • a defined rolling force 31 then building up, which now acts on the bore wall.
  • an axial feed of the tool is initiated and the bore wall is machined by the rolling rollers 8.
  • the adjustment of this tool to the bore diameter of the workpiece bore 26 is independent of any tool presetting and is carried out directly on the workpiece. If the diameter of the workpiece bore 26 is constant, the support cone remains in the set axial position during the entire machining process. However, if the diameter of the workpiece bore 26 changes, the axial position of the support cone on the receiving piece 1 also changes.
  • the roller rolls 8 become stronger than intended due to the narrowed bore pressed against the raceway 30 of the support part 9. This then increases the friction between the rolling rollers 8 and the raceway 30 of the support part 9 and thus also the torque occurring on the support part.
  • the support member 9 is now rotated by the larger torque on the receiving piece 1 against the direction of rotation of the tool and at the same time axially counter-clockwise by drivers 32 formed as balls, which are embedded in the shaft 1 on the one hand and in the support part 9 in a helical groove 33, 34, respectively the positioning force 29 shifted.
  • the support member 9 is pulled away from the rolling rollers 8 and the rolling force 31 is reduced until the rolling force 31 is again proportional to the actuating force 29.
  • the spring 13 maintains the contact between the thrust bearing 12 and the support part 9 during this displacement movement via the disk 19. So that the balls 32 do not fall out, disks 35, 36 are provided on both sides of the support part 9 and are attached to the support part 9.
  • the groove 33 in the receiving piece 1 must be provided axially with a length such that the axial displacement of the support part 9 is possible without striking the balls 32 in this groove.
  • a machining process begins, for example, at a small diameter of a workpiece bore 26, the diameter of the tool adjusts to this bore diameter and the rolling force 31 builds up proportionally to the intended positioning force 29. If the diameter of the workpiece bore 26 then increases in the course of the length of the workpiece bore 26, the tool is automatically adapted to the new diameter without the rolling force changing inadmissibly. Due to the increasing workpiece bore 26, the rolling force 31 decreases and thus the friction between the rolling rollers 8 and the supporting part 9. The torque occurring on the supporting part is therefore lower than before and no longer proportional to the positioning force 29.
  • the positioning force 29 now displaces the supporting part 9 on the receptacle 1 against the spring 13 until the proportionality between the actuating force 29 and the rolling force 31 of the rolling rollers 8 has been restored.
  • This displacement movement is accompanied by a corresponding rotational movement of the support part 9 on the receiving piece 1, caused by the entrainment.
  • the tool shown in FIG. 2 differs from the tool according to FIG. 1 only in that a smoothing head 38 is assigned a peeling head 37.
  • This peeling head 37 is fastened instead of the end piece 21 on the receiving piece 1 by means of the screw 22 and the feather key 23.
  • bores of cylinder tubes can be peeled to size and machined by the smooth rolling head 38 in the same operation.
  • the combination of a peeling head with a smooth rolling head is known per se in the prior art.
  • the peeling knife 39 is accommodated in the peeling knife holder 40, for example in a radially floating manner, and is set to the intended working diameter outside the peeling head 37.
  • the inside diameter of the raw cylinder tube 41 has such an allowance that the intended working diameter is achieved by peeling.
  • the time at which the fluid cylinder is acted upon by the fluid can be determined by the machine control of the machine tool.
  • the tool according to FIG. 3 is constructed in the same way as the tool according to FIG. 2.
  • the smooth rolling head 38 is also assigned a peeling head 37.
  • This scarf head 37 is in turn attached to a receptacle 43 by means of the screw 22 and the feather key 23.
  • this tool is intended for machining and simultaneously rolling machining of bores.
  • the receiving piece 43 is connected to the boring bar 2 via the thread 3.
  • the boring bar 2 is received by a machine tool, not shown.
  • the receiving piece 43 is firmly connected to the bearing part 4 by screws, not shown.
  • the thrust bearing 5 is held and supported by the bearing part 4.
  • the thrust bearing 5 in turn supports a ring 49 on which the roller cage 44 is fastened with screws, not shown.
  • the bearing part 4 is rotatably connected to the ring 49 via parts not shown to form ring 49.
  • the roller cage 44 carries tapered roller rollers 45 which roll on the tapered track 59 of the support member 46.
  • the support member 46 is slidably received in the cylindrically curved surface 47 designed as a bore by the receiving piece 43 on a corresponding cylindrically curved surface 122.
  • the support part 46 with its large diameter 54 is arranged facing the peeling head 37.
  • the support member 46 is held by the thrust bearings 11 and 12 with the disks 19 and 20 on the receiving piece 43 and by the flow medium cylinder 56 and a pull rod 48 which are guided in the receiving piece 43 and connected to the piston rod 57 of the fluid cylinder 56 by a sleeve 50 is held in the direction of the actuating force 51 given here against the spring 52.
  • the fluid cylinder 56 is carried by the adapter 24. The adapter 24 is clamped between the boring bar 2 and the receiving piece 43 and thus fixed.
  • the pin 53 which is received by the pull rod 48, penetrates the receiving piece 43, which has a slot 62 at this point and transmits the actuating force 51 via disk 19 and thrust bearing 12 to the support member 46, which is now with the larger diameter 54 of the track 59 opposite to the direction of the actuating force 51 represented by the arrowhead 55 and from the spring 52 is supported via the sleeve 18, disc 20 and thrust bearing 11.
  • the processing sequence with this tool is similar to that of the tool according to FIG. 2.
  • the peeling knife 39 of the peeling head 37 which is set to the intended bore diameter and is freely transversely movable, has penetrated so far into the workpiece, which should be a cylinder tube 41, that the Rollers 45 have reached the front edge 42 of the cylinder tube 41 and enter the workpiece bore, the fluid cylinder 56 is acted upon by the connection 58 with fluid under a defined pressure and the piston rod 57 with the attached pull rod 48 exercises via pin 53, disc 19 and Thrust bearing 12 an actuating force 51 in the direction indicated by the arrow tip 55 on the support member 46.
  • the support member 46 is now displaced against the force of the spring 52, the support member simultaneously making a rotary movement due to the entrainment on the receiving piece 43 and thereby displacing the tapered rolling rollers 45 radially outward against the bore wall of the workpiece bore 26, a defined rolling force then occurring 31 builds up, which now acts on the bore wall.
  • the adjustment of the smooth rolling head 38 to the bore diameter of the workpiece bore 26 is also independent of any tool presetting and is carried out directly on the workpiece. If the diameter of the workpiece bore 26 produced by the peeling knife 39 is constant, the support part 46 remains in the set axial position during the entire machining process. However, if the diameter of the workpiece bore 26 changes, the axial position of the support part 46 on the receiving piece 43 also changes.
  • the roller rolls 45 are pressed more strongly against the raceway 59 of the support part 46 by the narrowed bore . This increases the friction between the rolling rollers 45 and the support part 46 and thus also that of the defined rolling force 31, which is determined by the actuating force 51 and is proportional to the actuating force, predetermined torque on the support part.
  • the support member 46 is now rotated by the larger torque on the receiving piece 43 against the direction of rotation of the tool and at the same time axially counter-clockwise by drivers 32 formed as balls, which are embedded on the one hand in the receiving piece 43 and on the other hand in the supporting part 46 in a helical groove 60, 61 the actuating force 51 shifted in the direction of the peeling head 37.
  • the rolling force 31 is reduced until the rolling force 31 is again proportional to the actuating force 51.
  • the spring 52 maintains the contact between the thrust bearing 11 and the support member 46 during this displacement movement.
  • the balls 32 are also secured, as in the tool according to FIG. 2, to prevent them falling out by means of disks 35, 36. This tool reacts to all other machining situations like the tool according to FIG. 2.
  • the tools according to FIGS. 2 and 3 are shown with peeling heads which have rigid peeling knives. However, there is also the option of providing peeling heads with retractable peeling blades. Such peeling heads have been known for a long time and have proven themselves well.
  • the tool according to FIG. 3, like the tool according to FIG. 1, can be designed without a peeling head and only for rolling machining.
  • the tool according to FIG. 4 is a smooth rolling tool for machining bores with small and medium diameters.
  • the support part 63 is connected to the shaft 65 via a thread 64.
  • the shaft 65 has a non-self-locking thread 66 at its thin end and is held by the tool holder 67 in a nut thread provided in a holder 120.
  • the receiving piece 120 is in turn connected to the tool holder 67.
  • a spring 68 which is supported on both sides of the tool holder 67 and on a thrust bearing 69, which rests on the shaft 65, holds the support part 63 in an initial position, as shown in FIG.
  • the spring 68 is biased and the shaft 65 is held against the bias of the spring 68 by a stop screw 70, which uses the nut thread end of the receiving piece 120 as a stop.
  • the diameter adjustment This tool is carried out manually by pulling the sleeve 71 axially away from the smooth rolling head 72 against the force of the spring 73 until the cam 74 comes out of the groove 75 of the disk 76, which is fixed against rotation by the nose 85 in the outer groove 86 of the receiving piece 120 is held, is pulled out. If the sleeve 71 is then rotated, the round nut 77, which is in operative connection with the external thread 78 of the receptacle 120 and in any case has a groove 87, is carried along by the cam 74 and axially adjusted.
  • the sleeve 71 is then pushed back and the cam 74 engages in another groove 75, several of which are provided on the circumference of the disk 76.
  • the pressure bearing 81, the bushing 82, the washer 76, the round nut 77 and the sleeve 71 are held together by the spring 73, which bears against a ring 79 which is held in the sleeve 71 by a retaining ring 80.
  • the working diameter of the tool is increased or decreased or the roller cage 88, which holds the tapered roller rollers 83 on the track 84 of the support part 63, is shifted in the corresponding direction.
  • the tool is received on the tool holder 67 by a machine tool, which is not shown.
  • the tool holder 67 can be designed as a cylindrical shaft, but also as a cone or in some other suitable manner.
  • the tool diameter is set slightly larger than the largest permissible workpiece diameter.
  • roller rollers 83 first touch the bore opening with their rounded leading edge 89. This creates a radial force on the roller rollers which is absorbed by the support part 63. Friction occurs between the rolling rollers 83 rolling on the support part 63 and the raceway 84 of the support part 63, which generates a torque on the support part 63 against the relative direction of rotation of the tool. The support member 63 and the shaft 65 attached to it are now rotated against the relative direction of rotation of the tool.
  • the thread 66 on the shaft 65 is from the nut thread of the receiving piece 120 received and is now rotated in the nut thread and at the same time axially displaced against the force of the spring 68, which exerts a positioning force 90.
  • the support member 63 moves axially, which results in a radial change in position of the roller rolls 83 and a different tool diameter than the manually set one is set until the roller rolls 83 have entered the workpiece bore. If the workpiece bore is machined with the tool diameter set in this way, the position of the roller rolls is constant as long as there is no change in the diameter of the workpiece bore.
  • the rolling force is determined by the force of the spring 68, which is proportional to the rolling force. If the diameter of the workpiece bore decreases, the rolling force increases.
  • the support part 63 is then rotated counter to the relative direction of rotation of the tool and with the support part 63 also the shaft 65.
  • the shaft 65 then rotates relative to the tool holder 67 having the receiving piece 120.
  • the shaft 65 with its thread 66 in the nut thread of the receiving piece 120 is received, changes its axial position with respect to the rolling rollers 83 during the rotation, in such a way that the support part 63 with its track 84 moves radially away from the rolling rollers 83 due to the change in the axial position, the rolling rollers naturally immediately radially changing follow the removing surface.
  • the thread 66 only has to have a corresponding pitch direction.
  • the force of the spring 68 increases due to the compression of the spring and thus also the rolling force of the rolling rollers 83.
  • the increase in the rolling force can be kept within permissible limits, in particular because the displacement path of the support part 63 is small.
  • the rolling force exerted by the rolling rollers 83 decreases.
  • the actuating force 90 of the spring 68 then takes effect and pushes the shaft 65 with the support part 63 attached thereto in the direction of the actuating force 90 against the Rollers 83 and thereby enlarges the envelope of the rollers 83 and thus the rolling force.
  • the sheep 65 in turn rotates in the nut thread 66 of the receiving piece 120.
  • annular lock nut 93 is screwed onto a tool holder 91, which has a thread 92 at one end.
  • a threaded ring 94 which is also received by the thread 92 of the tool holder 91.
  • a receptacle 95 for the threaded ring 94 is rotatable, but not axially displaceable, fastened by means not described further.
  • an annular support part 97 is received in this bore 96 on its outer cylindrically curved surface 98.
  • the receiving piece 95 has a collar 99 at the end of the bore.
  • a groove 100 is provided, in which a key 101 engages.
  • the feather key 101 has a pin 102 which holds the feather key 101 in a bore 103 to prevent it from being coated.
  • this key 101 is received by a further groove 104, which is located in the tool holder 91. Between the tool receptacle 91 and the receptacle 95, this key 101 creates a rotary drive.
  • the tool holder 91 is drilled axially and carries a thrust bearing 105.
  • a ring 106 which is fastened to a roller cage 107, and a spring 108 are supported on this thrust bearing 105.
  • the spring 108 is supported on the other hand on the support member 97.
  • the support part itself is held against the forces of the springs 108 and 110 in a receiving piece 95 by a locking ring 109.
  • the spring 110 which is arranged between the support part 97 and the ring 106, presses the ring 106 with the roller cage 107 axially against the thrust bearing 105.
  • the support part 97 has an inner tapered bore which is designed as a raceway 111 for the tapered roller rolls 112 is.
  • the support member 97 is rotatably and axially movable in the receiving piece 95.
  • the driver 113 designed as balls, which are located opposite each other helical grooves 114 and 115 are embedded act like a thread when the support member 97 is rotated in the receiving piece 95. If the support part 97 is rotated clockwise in the receptacle 95, the support part 97 moves simultaneously against the forces of the springs 108 and 110. The balls 113 are held against falling out by the rings 118 and 119, which are fastened to the support part 97 .
  • the tool on its tool holder 91 is to be clamped in a drive unit. This drive unit is not shown further and can also be a suitable machine tool. However, there is also the possibility of driving the workpiece in rotation and merely picking up and supporting the tool.
  • the tool is adjusted to a machining diameter as follows:
  • the lock nut 93 is loosened so that the threaded ring 94 is freely rotatable.
  • the threaded ring 94 is now rotated relative to the tool holder 91 until the desired machining or tool diameter is set.
  • the threaded ring 94 is then locked with the lock nut 93 and secured in this way against unintentional adjustment.
  • the tool diameter is set slightly smaller than the workpiece diameter.
  • a processing sequence is as follows: Tool and workpiece rotate relative to each other.
  • the workpiece 116 is fed to the tool and the rolled rollers touch the workpiece 116 with their rounded leading edge 117 and rolling forces on the roller rollers 112 build up.
  • the rolling rollers 112 are pressed against the raceway 111 of the support part 97 and friction occurs between the rolling rollers 112 and the raceway 111, which exerts a torque on the support part 97.
  • This torque rotates the support part 97 in the receiving piece 95.
  • the support part 97 is displaced by the balls 113, which serve as drivers, against the forces of the springs 110 and 108.
  • the support part 97 thus wants to move radially away from the rolling rollers 112 with its track 111, which immediately follow this movement, which increases the tool diameter. This enlargement of the tool diameter takes place until the roller rolls 112 encompass the outer surface of the workpiece and bear against it. The forces of the springs 110 and 108 then generate the rolling forces of the rolling rollers 112. However, should the tool diameter increase in the course of machining, the rolling forces increase and the tool mechanism reacts as at the beginning of the machining. However, if the workpiece diameter decreases, the support ring 97 is displaced by the forces of the springs 108 and 110 in the direction of the locking ring 109, as a result of which the roller rollers 112 immediately follow the outer surface of the workpiece 116.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Cutting Tools, Boring Holders, And Turrets (AREA)
  • Tires In General (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Grinding And Polishing Of Tertiary Curved Surfaces And Surfaces With Complex Shapes (AREA)
  • Laminated Bodies (AREA)
  • Moulding By Coating Moulds (AREA)

Claims (14)

  1. Outil comportant une tête de galettage pour l'usinage de la surface externe de pièces à usiner (25, 116), ayant une surface supérieure de section circulaire, étant entendu que la tête de galettage présente au moins trois galets de laminage coniques (8, 45, 112, 83), qui sont maintenus, au moyen d'une cage porte-galets (7, 44, 107, 88), de façon à rouler sur une piste conique de déplacement (30, 59, 11, 84) d'une pièce d'appui (9, 46, 97, 63), laquelle est, d'une part, reliée, directement ou par l'intermédiaire d'autres moyens, à un porte-outil (2, 67, 91), et étant entendu que des moyens (15, 56, 108, 68) sont prévus pour créer une force de réglage (29, 51, 90) et sont reliés à la pièce d'appui (9, 46, 97, 63) en vue d'une modification axiale de la position de cette dernière par rapport aux galets de laminage (8, 45, 112, 83), étant entendu qu'une modification axiale de la position de la pièce d'appui (9, 46, 97, 63) provoque une modification radiale proportionnelle de la position des galets de laminage,
    caractérisé en ce que
    la pièce d'appui (9, 46, 97, 63), comportant une surface à courbure cylindrique (10, 98, 47), concentrique avec la piste de circulation conique (30, 59, 11, 84), est montée tournante et mobile axialement sur une pièce support (1, 43, 95, 120), comportant une surface à courbure cylindrique (122, 121, 98) correspondante, étant entendu que pièce d'appui (9, 46, 97, 63) et pièce support (1, 43, 95, 120) sont reliées entre elles par l'intermédiaire d'un entraîneur, qui est constitué d'au moins une rainure (34, 33; 30, 61; 115, 114), réalisée dans au moins une des surfaces à courbure cylindrique associées, et dirigée par rapport à son axe longitudinal avec une pente non autoblocante, et d'au moins un entraîneur (32, 113) travaillant en coordinationn avec au moins une rainure, et s'engageant dans au moins une rainure, étant entendu que la direction de la pente de la rainure et la pente du cône de la piste de circulation conique sont déterminées l'une par rapport à l'autre de telle façon qu'en cas de dépassement, sur la pièce d'appui (9, 46, 97, 63), d'un couple proportionnel à la force d'appui (29, 51,90), la pièce d'appui coulisse axialement dans le sens opposé à la direction de la force de réglage (29, 51, 90).
  2. Outil suivant la revendication 1, caractérisé en ce que rainure et entraîneur sont réalisés sous la forme d'un écrou fileté et d'un axe fileté, le sommet du filet et la base du filet formant des surfaces à courbure cylindrique.
  3. Outil suivant la revendication 1, caractérisé en ce que les deux surfaces à courbure cylindrique (10, 47, 98; 121, 122, 98) présentent au moins une rainure (33, 60, 114; 34, 61, 115), qui est chaque fois dirigée dans le sens opposé à la rainure située dans l'autre surface à courbure cylindrique, et en ce que, dans l'espace libre compris entre les rainures situées en face l'une de l'autre, est installé au moins un corps d'entraînement, sous la forme d'un entraîneur (32, 113), comportant une section ayant une surface plus grande que la surface de section de l'une des rainures.
  4. Outil suivant la revendication 3, caractérisé en ce qu'une rainure (34, 61) est remplie par des corps d'entraînement, tandis que l'autre rainure (33, 60) est plus longue que la première rainure citée, dans le sens axial, de la quantité voulue pour la mobilité axiale de la pièce d'appui (9, 46).
  5. Outil suivant la revendication 1, caractérisé en ce qu'à la rainure prévue dans l'une des surfaces à courbure cylindrique, est associée, comme entraîneur (32, 113), au moins une came engagée dans la rainure, came qui est reliée de façon fixe à l'autre pièce constitutive.
  6. Outil suivant l'une quelconque des revendications 1 à 5, caractérisé en ce que la pièce d'appui (9, 46, 63) est réalisée sous la forme d'un mandrin d'appui, comportant une piste de circulation extérieure conique (30, 59, 84).
  7. Outil suivant la revendication 6, caractérisé en ce que la pièce d'appui (9, 46) présente, comme surface à courbure cylindrique (10, 47), un alésage cylindrique, tandis que la surface à courbure cylindrique associée de la pièce support (1, 43) est réalisée sous la forme d'une tige, sur laquelle on a glissé la pièce d'appui (9, 46).
  8. Outil suivant l'une quelconque des revendications 1 à 5, caractérisé en ce que la pièce d'appui (97) est réalisée sous la forme d'une bague d'appui, comportant une piste de circulation intérieure conique (111).
  9. Outil suivant la revendication 8, caractérisé en ce que la pièce d'appui (97) présente, comme surface à courbure cylindrique (98), une surface extérieure cylindrique, tandis que la surface à courbure cylindrique associée (96) de la pièce support (95) est réalisée sous la forme d'une douille, dans laquelle on a glissé la pièce d'appui (97).
  10. Outil suivant la revendication 1 et l'une quelconque des revendications 3 à 9, caractérisé en ce que la pente de chaque rainure (33, 60, 114; 34, 61, 115) est de 70° à 84°.
  11. Outil suivant l'une quelconque des revendications 1 à 10, caractérisé en ce que, pour créer la force de réglage , il est prévu au moins un ressort (68, 52,108, 110), qui s'appuie, d'une part, sur un contre-appui fixe (120, 43, 105, 106) et, d'autre part, sur la pièce d'appui (97) ou sur d'autres pièces (65; 18, 20), reliées à la pièce d'appui (46, 63) de façon à coulisser.
  12. Outil suivant l'une quelconque des revendications 1 à 10, caractérisé en ce que, pour créer la force de réglage , il est prévu un vérin (15, 58) commandé par un fluide, qui s'appuie, d'une part, sur un contre-appui fixe (24) et, d'autre part, sur la pièce constitutive (28, 52), pouvant ensuite se déplacer,ou sur d'autres pièces (16, 14, 17, 18, 20, 11; 50,48, 53, 19, 12), reliées à la pièce d'appui (9,46) de façon à coulisser.
  13. Outil suivant la revendication 2, caractérisé en ce que l'écrou fileté est réalisé sur une pièce support (120) et en ce que l'axe fileté est réalisé sur une tige (65), cette dernière étant reliée à la pièce d'appui (63).
  14. Outil suivant la revendication 11, caractérisé en ce qu'un ressort spiral (68), dirigé dans le sens axial, est disposé entre la pièce support (120) et la pièce d'appui (63) de façon que des forces de sens contraire, dirigées sur ces deux pièces, soient exercées par le ressort spiral (68).
EP91103818A 1991-03-13 1991-03-13 Outil à galeter à rouleaux Expired - Lifetime EP0503109B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
ES91103818T ES2067071T3 (es) 1991-03-13 1991-03-13 Herramienta con un cabezal de rodillos laminadores.
DE59104421T DE59104421D1 (de) 1991-03-13 1991-03-13 Werkzeug mit Glattwalzkopf.
EP91103818A EP0503109B1 (fr) 1991-03-13 1991-03-13 Outil à galeter à rouleaux
AT91103818T ATE117616T1 (de) 1991-03-13 1991-03-13 Werkzeug mit glattwalzkopf.
HU913596A HU207962B (en) 1991-03-13 1991-11-18 Tool for burnishing the surface of work piece
CS913510A CS351091A3 (en) 1991-03-13 1991-11-20 Tool with a burnishing head
JP3327817A JPH0747264B2 (ja) 1991-03-13 1991-12-11 平滑化圧延ヘッドを備えた工具

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP91103818A EP0503109B1 (fr) 1991-03-13 1991-03-13 Outil à galeter à rouleaux

Publications (2)

Publication Number Publication Date
EP0503109A1 EP0503109A1 (fr) 1992-09-16
EP0503109B1 true EP0503109B1 (fr) 1995-01-25

Family

ID=8206505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91103818A Expired - Lifetime EP0503109B1 (fr) 1991-03-13 1991-03-13 Outil à galeter à rouleaux

Country Status (7)

Country Link
EP (1) EP0503109B1 (fr)
JP (1) JPH0747264B2 (fr)
AT (1) ATE117616T1 (fr)
CS (1) CS351091A3 (fr)
DE (1) DE59104421D1 (fr)
ES (1) ES2067071T3 (fr)
HU (1) HU207962B (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4939622B2 (ja) * 2010-03-24 2012-05-30 株式会社スギノマシン ピーニング工具および加工方法
JP6173977B2 (ja) * 2014-06-24 2017-08-02 株式会社スギノマシン ローラバニシング工具

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB925385A (en) * 1961-03-21 1963-05-08 E H Thompson & Son London Ltd Apparatus for finishing circular cylindrical walls and bores
US3930294A (en) * 1975-01-24 1976-01-06 Cogsdill Tool Products, Inc. Cylindrical surface finishing device
DE3021101A1 (de) * 1980-06-04 1981-12-10 Madison Industries Gmbh, 6078 Neu Isenburg Vorrichtung zum glattwalzen einer zylindrischen werkstueckflaeche mit einem glattwalzwerkzeug

Also Published As

Publication number Publication date
JPH0747264B2 (ja) 1995-05-24
DE59104421D1 (de) 1995-03-09
EP0503109A1 (fr) 1992-09-16
HU207962B (en) 1993-07-28
ATE117616T1 (de) 1995-02-15
HU913596D0 (en) 1992-02-28
HUT60651A (en) 1992-10-28
ES2067071T3 (es) 1995-03-16
CS351091A3 (en) 1992-09-16
JPH068135A (ja) 1994-01-18

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