HK1022282A1 - Tool head for use in machine tools - Google Patents

Abstract

The invention concerns a tool head for use in machine tools. The tool head substantially comprises a basic body (10), a tool shank (16) which projects axially over the basic body (10) and can be coupled to a machine spindle, a tool holder (18) for a cutting tool (20) and a rotary slide (30) which supports the tool holder (18) eccentrically and can be rotated relative to the basic body (10), with adjustment of the cutting radius of the cutting tool (20), about an eccentric axis (28) parallel with the basic body axis (12). In order to ensure that the cutting geometry is constant during a cutting operation, the tool holder (18) can be adjusted in defined manner relative to the rotary slide (30) as a function of the adjusting angle thereof or of the cutting radius.

Description

The invention relates to a tool head for use in machine tools with a base body, a tool with a machine spindle attached to the base body, a tool holder for a cutting tool and a tool holder outside the center, with a rotary screw that can be rotated, preferably parallel to the axis of the base body, relative to the base body, adjusting the cutting radius of the cutting tool.

In the unpublished DE-A-197 17 172 it was already proposed to apply to a flat-bed rotary head a rotary drive, eccentrically placed on the tool head, which can be rotated by means of a drive winch and a gear rigidly attached to the rotary wheel, under a predominantly radial position of the tool-take.

This state of the art is also a so-called internal state of the art.

The purpose of the invention is to improve the known tool head of the type described above so that the cutting geometry can be traced during the adjustment process.

To solve this problem, the combination of features given in claim 1 is proposed.

The solution of the present invention is based on the idea that the tool beam can be rotated, as defined by the rotation angle of the lathe or the radius of cutting radius in relation to the lathe. This makes it possible to keep the cutting geometry constant when adjusting the cutting radius. This can be done, for example, by the tool beam being adjusted in a defined orientation of the cutting tool relative to the axis of the base body relative to the rotor. This is done conveniently by the tool beam being adjusted in a reference plane connected to the cutting tool parallel to the axis of the base body relative to the rotor.

A preferred design of the invention provides for a radially overlapping and rotatable guide bar around the axis of the base body, against which a reference surface at the tool holder or cutting tool can be aligned when adjusting the rotor.

An alternative design of the invention provides that the lathe and the tool receiver are coupled to each other and to the base by means of gears, the gears being suitably designed as gears.

In the case of a rotary drive, the rotary drive is located in a base-body excentric bore, while the tool receiver is located in a base-body excentric bore. The rotary drive is located between a fixed or machine-side drive and the eccentric cam, while the tool receiver and the base-body machine are located between the tool receiver and the rotary machine. The cutting edge is traced by the three-sided drive and the three-sided gear having a transverse gear.

In order to ensure the smoothest possible transfer of the forces generated during the cutting and adjustment process, the rotor is placed in an axial/radial bearing in the eccentric bore, preferably shaped as a cone roller bearing.

The eccentric arrangement of the cutting tool on the rotor creates an imbalance which can be balanced by balancing masses both in the rotor and in the base. However, an essential advantage of the rotors is that the imbalances can be technically symmetrical. This means that they are mass-symmetrical with respect to their axis of rotation.

According to another embodiment of the invention, a rotary tool is stored in a concentric bore of the base, an eccentric bore of the rotor's rotor and an eccentric bore of the rotor, each rotating the tool receiver, whereby the rotor is moved around the base by means of a fixed or machine-like drive mechanism, with the rotor and the tool receiver attached to it, and between the rotor and the base on the one hand and the tool receiver on the other hand, the defined gear units are arranged in a transverse gear arrangement. As a gear unit, the rotor is moved loosely between the two gear units, in a way that is proportional to its center of mass.

The drive mechanism is advantageously equipped with a rotary gearbox with a rotary axis, which is concentric to the main body axis, and a mechanical drive gearbox with a rotary axis.

In principle, it is possible to provide for separate, electronically interconnected drives for the rotor, the circular rotor and the tool receiver, which allows the adjustment of the tool receiver to be largely arbitrary depending on the rotor position, thus deliberately influencing the spanning, for example when working with workpieces of different materials, and also to favourably influence the cutting time.

For the purpose of adjustment path monitoring, the basic body may include an electronic angular or path measurement system, preferably for measuring the adjustment angle of the rotor or circular saw or the adjustment path of the cutting tool.

A further advantageous design of the invention is to provide for at least two jointly or separately controllable rotors with adjustable toolholders arranged in eccentric holes of the base or the circular shaft.

The following is a detailed description of the invention by means of some examples of the design shown in the diagram. Fig. 1a cutting through a tool head with an eccentric rotor head, designed as a flat-bed;Fig. 1a cutting through the tool head with a tool pick-up;Fig. 1a cutting through the tool head in the gear-wheel area;Fig. 1a cutting through the rotor head;Fig. 2a and a cutting through the tool head, schematically represented in two rotation positions of the rotor;Fig. 3a cutting through an example of a flat-bed cutting in Fig. 1;Fig. 3a cutting through the B-B intersection of Fig. 3a;Fig. 3a cutting through the tool head in Fig. 3b;Fig. 3D cutting through the cutting line in Fig. 3b;Fig. 3D cutting through the cutting line in Fig. 3b;Fig. 3D cutting through the cutting head in Fig. 3b;Fig. 3D cutting through the cutting head in Fig. 3D rotating at 90° opposite the cutting line;Fig. 3D cutting through the cutting head in Fig. 3D rotating at 3° opposite the cutting line.3a;Fig. 4a a cutting through a tool head with a concentric circular and eccentric rotor, as shown in Fig. 1 and 3;Fig. 4b and c a view of the tool head as shown in Fig. 4a in two different angular positions of the circular in schematic representation;Fig. 5a view of a transformed tool head with a direction bar as shown in schematic representation;Fig. 6a three-dimensional graph for calculating the cutting radius and the angle of correction of the cutting plate of a tool with a rotor in simplified rendering;Fig. 6b and c two diagrams s = s (α) and δ (α));Fig. 7a a model for calculating the cutting body (δ) and the cutting plate (δ) in the base angle of the cutting plate (a) and a model for the correction of the cutting plate (δ) in the base angle of the cutting plate (a) in Fig. 6a.

The toolhead shown in the figure is intended as a flat-bed cutting head for use in machine tools. The toolhead consists essentially of a base 12 rotatable around a rotating axis 10, a toolbox which is axially raised above the base and can be coupled with a machine spindle 14 (Fig. 4a), a toolbox 16 for a cutting tool 20, a cutting plate 26 with a cutter 24 located on the cutting tool 20 and a cutting board 18 in an extruder bore 22 with a three-bearing, which is relatively stable to the base, subjecting the cutting radius of the cutting bore 24 to a glide axis parallel to the base 12 through the extruder 28 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder 30 through the extruder. In this case, the base 12 is located in a circular bore 22 (Fig. 34), and the base 34 through the extruder 32 through the extruder 30 through the extruder 30 through the extruder. In the case of a round bore, the base 12 through the extruder is also protected by a rotor 1 through the extruder 32 through the extruder 40 through the extruder. In the case of a round bore, the base 12 through the extruder 32 through the extruder is also protected by a 1 through the extruder 40 through the extruder 32 through the extruder.

As can be seen in particular from Figures 1a, 3c and d and Figures 4b, the eccentric boreholes 22 and 32 in the examples shown have the same eccentricity e. The eccentric arrangement of the cutting tool 20 in the rotor 30 on the one hand and the eccentric arrangement of the rotor 30 in the base 10 or in the circular one 34 on the other, creates an imbalance which can be compensated by compensating masses 44 in the rotor and compensating masses 46 in the base 10 or in the circular one.

A major advantage of the rotor is that the imbalances with respect to the axis of rotation 12 of the base can be balanced mass-symmetrically.

In the examples shown in Figures 1 to 3, the crankshaft 30 is driven by a 12 concentric crankshaft or drive shaft 48 of a machine-side drive mechanism, which comprises a slow-moving gear 45 with the machine-side drive shaft 47 and the head drive shaft 48 coaxially arranged.

The drive shaft 48 has a segmentally formed inner crown 50 at its front end, which is combed with an outer crown 52 of a smaller diameter of the crank 30 and is set free from friction against it. When the crank 30 is turned, the tool handle 18 is carried with it, adjusting the cutting radius of the cutter 24. To compensate for the changing cutting geometry (the orientation of the cutter relative to the axis of rotation 12) when the crank is turned, the crank 18 carries a cutting axis of the crank 18 concentric cutter 54 which is connected to a base plate of a size approximately 54 mm. The crank is rotated at an angle of approximately 54 mm. The crank is rotated at a speed of 25° and at a speed of 25°, and the cutter is moved at a speed of 25° and at a speed of 25°. The crank is rotated at an angle of approximately 54 mm. The average speed of the cutter is set at an angle of approximately 60 mm. The crank is rotated at a speed of 25° and at a speed of 25°. The average speed of rotation is set at an angle of 25° and at a speed of 25°. The average speed of rotation is set at an angle of 25° and at a speed of 25°. The average speed of rotation is set at an angle of 25° and at a speed of 25°.

In the example shown in Figures 4a to c, the drive 34 is rotated concentrically to the base 10 via the drive shaft 48 or the drive shaft 48. The drive shaft 48 is in turn driven by a drive mechanism comprising a machine-side drive 51 and a translational/rotary transformer 47; the shifting motion of the drive 51 in the direction of the double shaft 49 is converted in the drive 47 into the desired rotation of the drive shaft 48 in the direction of the base 53; the drive mechanism and the drives can be constructively incoherent in the base 53 so that a short-speed transformer is obtained. The rotation of the drive 32 is carried out in the direction of the base 18 and the drive 32 is carried out in the direction of the base 30 with the rotor 32 being located in the outer edge of the drill.To adjust the rotor 30 to the rotor 34 and the base 10 the rotor 30 carries an external gear 62 which is combed with a fixed inner gear 64; the tool holder 18 carries an external gear 66 which is concentric to its axis and combed with a loosely mounted gear 68 with a fixed inner gear 70 on the axis 28 of the rotor; the translation ratios of the drives formed by the said gear are so adjusted that when adjusting the cutting radius of the cutting plate 26 the gear 26 connected to the cutting plate 26 is directed backwards to the 12th gear (see Fig. 4 and c.

In the example of a tool head shown in Fig. 5 in a schematic diagram, the rotor 30 rotating around the eccentric axis 28 in the base 10 is also equipped with a tool jack 18 rotating in an eccentric bore 20 of the rotor. The orientation of the reference plane 60 of the cutting plate 26 in relation to the axis 12 of the tool head is done there by a reference bar 72 rotating on the base 10 around the rotor axis 12 and lying with its reference plane 74 against the reference plane 60 of the cutting plate 26, and the tool jack 18 is oriented in this direction when positioned in its reference hole 22. The same function is thus carried out by the reference plate 72 as in Fig. 1.

The example shown in Fig. 6a has a measuring system with a scale 80 attached to the cutting beam and a reading head 82 on the direction bar 72, which allows absolute measurement of the adjustment path of the cutter 24 in relation to the base.

The diagram in Fig. 6a shows the line and angle ratios for the simplified case of the adjustment path of the cutting plate 26 through the axis 12 at the starting point, from which the following formulae for the cutting radius s ((α) and the cutting correction angle δ ((α) can be derived.

The cutting radius in relation to the base axis 12 depending on the angle α of the rotor is in this case: $\text{s(α) = r}\sqrt{\text{2(1 - cosα)}}$ where r is the radius of shear with respect to the eccentricity 28 and the eccentricity 30 of the rotor.

For the correction angle δ, depending on the angle α, the relationship is given by $\text{δ = α/2}$

The relations according to equations (1) and (2) are shown in the graphs shown in Figures 6b and c.

The diagram in Fig. 7 shows the lengths and angles necessary for calculating the cut radius x and the correction angle δ' for the general case of the eccentric centre of gravity.

This results in the relation of the cutting radius x to the rotor angle α of the rotor. $\text{x(α) =}\sqrt{{\text{a}}^{\text{2}}{\text{+ 2r}}^{\text{2}}\text{(1 - cosα) + (4ar sinα(α/2)}}$ where r is the radius of the cutting plate 26 with respect to the eccentric axis 28 of the rotor 30 and a is the smallest cutting radius with respect to the rotor 12. $\text{δ'(α) = α / 2 + 90° - arcsin}\frac{\text{a}\sqrt{\text{1 + cosα}}}{\sqrt{\text{2}}\text{x(α)}}$ where x ((α) is used from equation (3).

The definition of the correction angle δ' differs by 90° from the definition of the correction angle δ according to equation (2).

The additional angles β, γ, ε and the distance s given in the diagram in Fig. 7 are auxiliary for the derivation of the formulas (3) and (4).

In summary, the invention relates to a tool head for use in machine tools. The tool head consists essentially of a base 10, a tool body which is axially overhead, a tool 16 which can be coupled with a machine spindle, a tool holder 18 for a cutting tool 20 and a tool holder 18 which is carried outwards, relative to the base 10 by adjusting the cutting radius of the cutting tool 20 by a parallel to the base 12 axis of the cutting tool 28 rotary rotary 30 to ensure a constant rotation of the cutting center of the cutting drive, the tool holder 18 being defined according to the angle of rotation of the cutting tool 30 or the cutting radius 30 of the rotary rotary opposite the cutting tool.

Claims (28)

1. A tool head for use in machine tools, comprising a base body (10), a tool shank (16) which is disposed on the base body (10) and which is adapted to be coupled to a rotating machine spindle (14), a tool holding fixture (18) for a cutting tool (20), and a rotary slide (30) which eccentrically carries the tool holding fixture (18) and which is rotatable with respect to the base body (10), thereby adjusting the cutting radius of the cutting tool (20), characterized in that the tool holding fixture (18) together with the cutting tool (20) is adapted to be adjusted in a defined manner with respect to the rotary slide (30) dependent on the rotary angle (α) of the rotary slide (30) or on the cutting radius (s, x).
2. The tool head of claim 1, characterized in that the rotary slide (30) is rotatable with respect to the base body (10) about an eccentric axis (28) parallel to the base body axis (12).
3. The tool head of claim 1 or 2, characterized in that the tool holding fixture (18) is adapted to be adjusted with respect to the rotary slide (30) aligning the cutting tool (20) relative to the base body axis (12) in a defined manner.
4. The tool head of one of claim 1 to 3, characterized in that the tool holding fixture (18) is adjustable with respect to the rotary slide (30) with the base body axis (12) under alignment of a reference plane (60) associated with the cutting tool (20).
5. The tool head of one of claims 1 to 4, characterized in that the tool holding fixture (18) is disposed in an eccentric bore (22) of the rotary slide (30) such that it is rotatable about an axis which is parallel to the eccentric axis (28) of the rotary slide.
6. The tool head of one of claims 1 to 5, characterized by an alignment rail (72) which protrudes over the base body axis (12) and which is rotatable about this axis, with respect to which alignment rail a reference plane (60) which is associated with the tool holding fixture (18) or the cutting tool (20) is adapted to be aligned during the adjustment of the rotary slide (30).
7. The tool head of one of claims 1 to 6, characterized in that the rotary slide (30) and the tool holding fixture (18) are coupled to each other and to the base body by transmission means (50, 52, 54, 58; 62 64, 66, 68, 70; 72, 74, 60).
8. The tool head of claim 7, characterized in that the transmission means comprise gears, toothed rings and/or toothed racks.
9. The tool head of claim 7 or 8, characterized in that the transmission means are adapted to be actuated without free play.
10. The tool head of one of claims 7 to 9, characterized in that the transmission means comprise on the drive side a rotary reducing gear unit (47) or a translation-to-rotation conversion gear unit (47').
11. The tool head of claim 10, characterized in that the rotary reducing gear unit (47) is designed to be a planetary gear unit or a harmonic drive gear unit having drive and driven axes (45, 48) which are coaxial with respect to each other.
12. The tool head of claim 10 or 11, characterized in that the reducing gear unit (47) or the conversion gear unit (47') and the transmission means coupled thereto are disposed within the base body, preferably in a radially interpenatrating manner.
13. The tool head of one of claims 1 to 12, characterized in that for the cutting radius of the tool head in dependency of the angle (α) of rotation of the rotary slide (30) about its eccentric axis (28) the relation $\text{x(α) =}\sqrt{{\text{a}}^{\text{2}}{\text{+ 2r}}^{\text{2}}\text{(1 - cosα) + 4ar sin α(α / 2)}}$ and for the correction angle δ'(α) of the reference plane (60) of the cutting tool (20) the relation $\text{δ'(α) = α / 2 + 90°-arcsin}\frac{\text{a}\sqrt{\text{1 + cosα}}}{\sqrt{\text{2}}\text{x(α)}}$ are valid, wherein r denotes the cutting radius with respect to the eccentric axis of the rotary slide (eccentricity) and a denotes the smallest cutting ratio with respect to the base body axis (12).
14. The tool head of one of claims 1 to 13, characterized in that for the cutting edge intersecting the base body axis (12) in a starting position (a = 0) the relation $\text{x(α) = r}\sqrt{\text{2(1 - cosα)}}$ is valid for the cutting radius s in dependency of the angle of rotation α of the rotary slide (30) and $\text{δ = α/2}$ is valid for the correction angle, wherein r denotes the eccentricity of the rotary slide (30).
15. The tool head of one of claims 1 to 14, characterized in that the rotary slide (30) is rotatably borne in an eccentric bore (32) of the base body (10), that the tool holding fixture (18) is rotatably borne in an eccentric bore (22) of the rotary slide (30), that transmission means (50, 52) on the side of the rotary slide are disposed between a base-body-fixed or machine-side drive mechanism (rotary rod, driven shaft 48) and the rotary slide (30), that transmission means (54, 56, 58) on the side of the tool holding fixture are disposed between the tool holding fixture (18) and the base body (10), and that the transmission means on the side of the rotary slide and the transmission means on the side of the tool holding fixture have a defined transmission ratio.
16. The tool head of claim 15, characterized in that the transmission means on the side of the rotary slide comprise a toothed ring which is adapted to be driven by the drive mechanism (rotary rod, driven shaft 48), which is concentric with respect to the base body axis (12), and which is preferably designed to be an internally toothed ring (50), and comprising a toothed ring meshing with the former, which is preferably designed to be a rotary-slide-fixed externally toothed ring (52).
17. The tool head of claim 15 or 16, characterized in that the transmission means on the side of the tool holding fixture comprise a base-body-fixed gear (58) and a tool-holding-fixture-fixed toothed ring meshing therewith and preferably being formed to be an internally toothed ring (54).
18. The tool head of one of claims 1 to 17, characterized in that at least part of the toothed rings and the associated parts are formed segment-like (Fig. 1c).
19. The tool head of one of claims 1 to 14, characterized in that a round slide (34) is rotatably borne in a concentric bore (40) of the base body (10), that the rotary slide (30) is rotatably borne in an eccentric bore (32) of the round slide (34), that the tool holding fixture (18) is rotatably borne in an eccentric bore (22) of the rotary slide (30), that the round slide (34) is rotatable, taking along the rotary slide (30) and the tool holding fixture (18), about the base body axis (12) by means of a base-body-fixed or machine-side drive mechanism (rotary rod, driven shaft 48), that transmission means (62, 64, 66, 68, 70) are disposed between the base body (12) on the one hand and the rotary slide (30) and the tool holding fixture (18) on the other hand, which transmission means are matched to each other by way of a defined transmission ratio.
20. The tool head of claim 19, characterized in that the rotary slide (30) carries a toothed ring (62) which is concentric with respect to it axis of rotation (28), with which it rolls off on a base-body-fixed toothed ring which is preferably formed to by an internally toothed ring (64).
21. The tool head of claim 19 or 20, characterized in that the tool holding fixture (18) carries a toothed ring (66) which is concentric with respect to its axis of rotation, with which it rolls off on a base-body-fixed toothed ring which is preferably formed to be an internally toothed ring (70), if need be over an interposed intermediate gear (68) loosely borne on the rotary slide (30).
22. The tool head of one of claims 15 to 21, characterized in that the drive mechanism comprises a rotary rod which is coaxial with respect to the base body axis (12) and which is driven from the machine side.
23. The tool head of one of claims 15 to 22, characterized in that the drive mechanism comprises an intermediate transmission having a driven shaft (48) which is concentric with respect to the base body axis (12).
24. The tool head of one of claims 19 to 23, characterized in that the eccentricities of the eccentric bores (32, 22) in the round slide (34) and the rotary slide (30) are of equal magnitude.
25. The tool head of one of claims 1 to 24, characterized by an angle or displacement measuring system (80, 82) measuring the adjusting angle of the rotary slide (30) or of the round slide (34) or the displacement of the cutting tool (20).
26. The tool head of one of claims 1 to 25, characterized by balancing weights (44, 46) disposed in the rotary slide (30) and/or the base body (10) and/or the round slide (34) for balancing the tool head with respect to the base body axis (12).
27. The tool head of one of claims 1 to 26, characterized in that separate drive means which can be electronically coupled to each other are provided for the rotary slide (30) and the tool holding fixture (18).
28. The tool head of one of claims 1 to 27, characterized in that at least two rotary slides having adjustable tool holding fixtures are provided, which are disposed in eccentric bores of the base body or of the round slide and which can be driven in unision or seperately.