WO1999008835A2

WO1999008835A2 - Universal grinding spindle with high-speed planetary grinder

Info

Publication number: WO1999008835A2
Application number: PCT/DE1998/002384
Authority: WO
Inventors: Walter Berg
Original assignee: Unislip Gmbh & Co. Kg
Priority date: 1997-08-19
Filing date: 1998-08-17
Publication date: 1999-02-25
Also published as: DE19837218B4; WO1999008835A3; DE19735936C1; DE19837218A1; EP1007274A2

Abstract

The invention relates to a grinding spindle for grinding machines. Said grinding spindle can be used in universal grinding of seats and elements, especially sliders and valves, and comprises a mount (2, 4;50) and a rotationally driven, disc-shaped holder (16; 60; 159) which rotates in relation to said mount. A plurality of driveable planetary grinding discs (19; 63) are distributed on the holder (16; 60; 159), which are driven by a drive system. A first spherical bearing (22, 25; 65, 66) is fitted between the holder (16; 60; 159) and a drive member (25a; 53) for the holder (16; 60; 159), which is arranged on the mount (2, 4; 50). A universal joint (11, 13; 58, 59; 38) having the same central point as the first spherical bearing (22, 25; 65, 66) connects the lateral grinding discs (19; 63) to a drive shaft (7), which extends coaxially in relation to the drive member (25a; 53) or a fixed axis to enable free spherical rotation.

Description

Universal grinding head with high-speed grinding planet

The invention relates to a grinding head for stationary or mobile machines for universal grinding of sealing or seat surfaces. The grinding of sealing or seat surfaces as a working method for the grinding head is also affected

In the state of the art, grinding heads of this type have a flat or disc-shaped carrier on which several (smaller) side grinding discs are distributed in a planet-like manner, i.e. grinding discs or grinding heads with self-adhesive slip rings on the front, which can be rotated individually, while in simpler embodiments the carrier is driven and its Diameter in relation to the diameter of the ring surface has been selected so that the (smaller) grinding wheels have started to rotate solely due to the friction between their grinding surface and the ring surface, the grinding heads have increasingly been designed in such a way that the individual grinding wheels are also driven one would like to achieve a high rotational speed of the grinding surfaces in order to improve the grinding pattern and the grinding accuracy. While many universal grinding heads have provided means which are relatively complicated to handle in order to exactly match the grinding head to the flap to be ground Aligning and fixing it is now more desirable to do without setup and adjustment operations in order to enable efficient grinding, particularly with parallel and wedge slides

A universal grinding head of this type is shown in EP-B 216 769 (Lars-Inge Larsson, LarsLap). Radially extending intermediate shafts are driven via an output gear bevel gear, which in turn drive the disk-shaped carrier for the side grinding wheels via bevel gear. There are several in the carrier Radially extending drive shafts are mounted, the radially inner bevel gears of which roll on a bevel gear fixed to the frame and concentric with the input shaft and drive the shafts of the individual grinding wheels at the other end via bevel gears.With this grinding head, the disk-shaped carrier of the side grinding wheels should automatically move to the plane of the surface to be ground adjust that the auxiliary shafts driven by the input Kegelgetπebe are arranged perpendicular to the input shaft and coaxially to each other and at the same time form a pivot axis about which the disk-shaped carrier can pivot freely with respect to the input shaft The object of the invention is to achieve higher speeds of rotation of the grinding wheels (also called end or "side grinding wheels") and still make the mobility of the support relative to the frame of the grinding head more universal. This object is solved by claim 1 or claim 12.

According to the invention, there is an interlocking double joint which allows the wearer to freely pivot (spherically) on all sides and thus easily and precisely adapt spatially to the plane of the surface to be ground without major adjustment work and installation work.

This double-jointed joint consisting of a spherical bearing and a universal joint - actually two "spherical bearings" - enables the single speed of the carrier and the drive system for the (smaller) grinding wheels to be achieved with only one drive (claim 12). The carrier is driven at a sufficiently low speed despite its spherically free pivotability. Mechanical vibrations or complications are not to be feared due to the robust construction without multiple bevel gear ratios.

Despite this design, the carrier - for grinding surfaces of different diameters - can easily be exchanged for one or more carriers of other dimensions or design.

A higher speed of the side grinding wheels can be achieved with the invention without any problems and transmitted to the disk-shaped carrier via the drive shaft or the fixed axis (claims 3, 5, 8).

Specifically, speed differences of 1: 50 to 1: 100 can be achieved between the input shaft and the slow-running carrier, on which the rotatably arranged side grinding wheels with one opposite the other can be achieved via a high-reduction gearbox, which is arranged coaxially to the drive shaft Turn the speed of the drive shaft increased speed (claim 5.8).

The universal joint, which has the same center as the spherical bearing, can also be designed as a spherical joint or bendable shaft section in the sense of its spherical pivotability on all sides (claim 7). The invention is explained in more detail below with the aid of schematic drawings using several exemplary embodiments.

1 shows, in a section containing the axis of the input shaft 7, a first embodiment of the invention for particularly high-speed drive of side grinding wheels 19 on a disk-shaped carrier 16. A universal joint 11, 13 couples the input shaft 7 and the carrier 16. FIG. 2 shows a partial side view cut, a detail for a modified embodiment of the universal joint from Figure 1. Figure 3 illustrates in the same representation as Figure 1, the application of the detail of Figure 2 in the grinding head of Figure 1. Figure 4 shows a modified version of the embodiment of Figure 1 with stationary axis 51 and hollow cylinder drive shaft 53. FIG. 5 shows the embodiment according to FIG. 1 with the disc-shaped carrier 16 removed for the purpose of exchanging it for another carrier. FIG. 6 shows a sectional illustration and FIG. 7 shows a top view of an embodiment with pivotable arms 156, in particular for grinding surfaces of significantly different diameters.

The grinding head 1, as shown in the sectional view in FIG. 1, has as the drive shaft a driven input shaft 7 with axis 8, on which a pulley 6, for example for a toothed belt 5, is attached, which is perpendicular to the axis of the while 7 extending tubular frame section 4 of the

Grinding head frame 2,3,4 runs. Wedged to the drive shaft is a high-reduction gear 9, 9, which is commercially available (under the name "Harmonie Drive"). The input shaft 7 has at its left end in FIG. 1 a spherical head 11 which is seated in a spherical cap 13 and is drivingly coupled to the latter via a driving pin 12. The driver pin 12 goes through the center of the ball and transmits it

Torque to the calotte 13. This is a spherical joint for the transmission of torque. With the cap 13, an output pin 14 is connected, on which a gear 15 is wedged, which is rotatably supported in a disk-shaped carrier 16 via bearings 21. With an external toothing of the gear wheel 15, three or more gear members, such as gear wheels 18, each of which is connected coaxially and in terms of drive to a side grinding wheel 19, can be engaged. The unit consisting of grinding wheel 19 and gear member 18 is mounted in the carrier 16 by means of bearings 17. The disc-shaped carrier 16 is otherwise covered as a hollow disc body by a corresponding cover 20 to the outside, which only has openings for the grinding wheels 19. The disk-shaped carrier 16 is fixedly connected to the bearing shell 22 of a further spherical bearing via a plurality of screw bolts 23, in which the spherical head 25 of a plate-shaped part 25a is received. The head 25 has a radially extending driver pin or pin 24 which engages in a corresponding recess in the bearing shell 22, as a result of which a torque-related drive connection is formed between the parts of this spherical bearing 22, 25.

The plate-shaped part 25a is mounted in the frame 2, 3, 4 by means of a bearing 27 and in turn has a bearing 26 for the input shaft 7. The plate-shaped part 25a also forms the output of the high-reduction gear 9, 10.

A high input speed n ^ is transmitted via the pulley 6 or a drive wheel to the input shaft 7 and is transmitted by the latter directly to the gear 15 in the disk-shaped carrier 16 via the universal joint 11, 12, 13 which permits spherical movements. The gear members 18 of the grinding wheels 19 reach an output speed ^ which is greater than the input speed n- _j by the transmission ratio between the gear members 15 and 18. As a result, peripheral speeds of the grinding wheels 19 of 10 m / sec or greater are achieved. The carrier 16 for the grinding wheels 19, however, is driven at a speed n ^ which is very small compared to the speed of the gear members 18 and grinding wheels 19, for example by a factor of 50 to 100 less than the input speed n- _j . This speed is derived from the same input shaft 7 and obtained via the high-reduction gear 9, 10 in its output member, the plate-shaped part 25 a with a spherical head 25. The plate-shaped part 25a also has a ring shape.

The design described enables the simultaneous transmission of two very different speeds with different torques with the help of the two spherical transmission elements with the same sphere center. The carrier 16 with the high-speed grinding wheels 19 is nevertheless freely and spherically movable on all sides during a grinding process and adjusts itself automatically and without any additional adjustment in the event of parallelism deviations of the ring-shaped sealing surface to be reground, in particular in the case of sliders. This arrangement can be completed with a corresponding drive motor and guide and fastening elements to form a slide or valve grinding machine and can also be used for stationary grinding work.

Figures 2 and 3 show a modified embodiment, in which the first spherical bearing, which connects the input shaft 7 with the central gear member (the gear 15) in the carrier 16, is replaced by a shaft 35 with a flexible section 38 2 shows, the shaft consists of a first shaft section 36 serving as an input shaft, on which an input gearwheel can be keyed at 37. This shaft section 36 is over a spherical, i.e. H. Section 38, which can be bent out on all sides at an angle 42 and is made of a correspondingly elastically deformable material, is connected to a shaft journal 39 which is connected to the central transmission element 15. The center 40 of the flexible section 38 coincides with the center of the second spherical drive connection 25, 22. Otherwise, the design corresponds to the grinding head according to FIG. 1.

While in the embodiments according to FIGS. 1 to 3 the supply of the driving force and the tubular frame section 4 extend at right angles to the axis 8 of the input shaft 7 and 35, FIG. 4 shows an embodiment in which the driving force is supplied axially and also the frame 50 itself in this

Direction extends. In addition, the device according to FIG. 4 differs from that according to FIG. 1 in that the high-reduction gear 9, 10 of FIG. 1 is omitted. The device has a non-rotatable central shaft 51, the central axis of which is designated 52. On this shaft, a rotatable hollow shaft 53 is mounted by means of bearings 54, which represents the drive shaft and in it

Extension corresponds to part 25a of the device according to FIG. 1. In this embodiment, too, two interlocking spherical bearings or drive connections allowing spatial deflections are provided. Thus, the shaft 51 has at its end a spherical head 58 which is connected in terms of torque to a spherical shell 59, on the coaxial pin 59a of which a central, fixed gear element 62 is arranged within the carrier 60 for the grinding wheels 63 and the gear members 70 thereof. On the hub of the central gear element 62, the support 60 is rotatably mounted by means of a bearing 61, which is screwed non-rotatably to a bearing shell part 66 at 64. The hollow shaft 53 ends in a spherical head 65, which is received in the bearing shell part 66. The ball head 65 has a radially oriented pin 67, which is used for the torque coupling. The shaft 53 is mounted in the housing or frame 50 by means of bearings 55. When the carrier 60 rotates, the gear members 70 of the grinding wheels 63 roll on the circumference of the central gear element 62. Also in this embodiment two distinctly different speeds are realized in the universal grinding head (spherical) on all sides and with free pivotability of the support 60, although in this embodiment the rotational speed difference between n. _| and is not as large as in the embodiment according to FIG. 1. FIGS. 1 and 4 can also be combined to form examples, not shown, in such a way that a drive via a toothed belt 5 or a drive axis perpendicular to the axis 52 of the fixed shaft 51 takes place. Here, the shaft 51 is shortened to a length which corresponds to the drive shaft 7 in FIG. 1. The ball head 65 of FIG. 4 is then arranged on the plate-shaped part 25a of FIG. 1, which is driven directly by the toothed belt 5, with the shaft 7/51 then stationary. The function corresponds to that of FIG. 4, but with an angular drive system or that of FIG. 1, but with an axial drive system and a long drive shaft 7.

FIG. 5 shows the interchangeability of the carrier 16 in a configuration corresponding to FIG. 1. This interchangeability enables the grinding of surfaces of different diameters with the fundamentally the same device. It can be seen that the spherical bearing shell 13 can be removed from the bearing shell part 22 and the ball head 11 after loosening the bolt 23, so that the carrier 16 is released and can be exchanged for another carrier.

The embodiment according to FIGS. 6 and 7 serves the same goal, namely the grinding of surfaces of different diameters, only one removable carrier 159 being shown, the one with its

Bearing shell 13 can be placed directly on the ball head 11, for example the device according to FIG. 1 and FIG. 5. The carrier 159 can be connected to the shell part 22 via the screws 23.

In this embodiment, the carrier 159 corresponds to the disc carrier 16 or 60, which has the bearings for the central gear element as a gear wheel 150. Several, in the example shown four, pivot arms 156 are pivotally mounted on the central support 159 and are arranged distributed in the circumferential direction. The respective pivot axis 158 also forms a shaft which is mounted in the pivot arm 156 by means of bearings. On both ends of the shaft, rollers or wheels 151 and 153 are fastened as gear elements, each of which belongs to a (planetary-wheel-like) belt drive. These can be simple belts, toothed belts or chains. The drive belts 161, which run around the gear element 153, are wrapped around the gear member 154, which is connected at the same axis and rigidly to the grinding wheel 19 via the shaft 155. The belt 160, which is wrapped around the gear member 151, runs over tensioning rollers 162 and at least partially wraps around the central gear wheel 150 in the carrier 159.

Here, the input speed w is again via the bearing shell 13. _| transmitted directly to the central gear wheel 150 and, via w- _j ', correspondingly translated with the speed W3 onto the grinding wheels 19, while the second, substantially lower speed W2 via the second spherical connection and the bearing shell part 22 (see FIG. 5) occurs directly the carrier 159 is transmitted.

The mode of operation of the device according to FIGS. 6 and 7 corresponds to the mode of operation of the device according to FIG. 1.

The position of the swivel arms 156 relative to the radius 164 passing through the articulation axis 158 can be adjusted and ascertained in the direction 165, as a result of which the diameter on which the grinding wheels 19 are arranged changes. This enables easy adaptation to surfaces to be sanded with significantly different diameters.

Claims

Expectations:

1. Grinding head for universal grinding of sealing or seating surfaces of fittings, (a) with a frame (2,4; 50) and a disc-shaped carrier (16; 60; 159) which can be pivoted and driven in relation thereto; (b) with a plurality of rotationally driven side grinding wheels (19; 63) which are arranged in a planetary manner on the carrier (16; 60; 159) and are rotatably mounted; (c) with a spherical bearing (22.25; 65.66) between the

Carrier (16; 60; 159) and a drive member (25a; 53) mounted in the frame (2,4; 50) for the carrier (16; 60; 159); and (d) with a universal joint (11, 13; 58, 59; 38), which has the same center point as the spherical bearing (22, 25; 65, 66) and the side grinding wheels (19; 63) with one coaxial to that

Connects drive member (25a; 53) extending drive shaft (7) or a fixed axis (51) spherically freely pivotable.

2. Grinding head according to claim 1, wherein the drive for the drive member (25a) is derived from the drive shaft (7).

3. Grinding head according to claim 2, wherein a high-reduction gear (9, 10) is arranged between the drive member (25a) and the coaxial drive shaft (7).

4. Grinding head according to claim 3, wherein the high-reduction gear (9, 10) on the drive shaft (7) is arranged coaxially.

5. Grinding head according to one of claims 3 or 4, wherein the transmission ratio of the high-reduction gear (9, 10) is selected so that the translation between the drive shaft (7) and the carrier (16) of the side grinding wheels (19) in Range is between 50: 1 to 100: 1.

6. Grinding head according to one of claims 1 to 5, wherein the drive member (25a; 53) the carrier (16; 60; 159) via a spherical

Bearing (22.25; 65.66) arranged pin (64.67) drives.

7. Grinding head according to one of the preceding claims, in which the universal joint is designed as a ball joint (11, 13) or flexible shaft section (38) on all sides.

8. Grinding head according to one of the preceding claims, in which the

Gear ratio is 2: 1 to 3: 1, between the side grinding wheels (19; 63) and (a) of the rotatable drive shaft (7); or (b) when the central axis (51, 52) is stationary, the drive member (53), which is designed as a hollow shaft or perpendicular to it as an angle drive (25a, 5).

9. grinding head according to one of the preceding claims, wherein the grinding wheels (19; 63) replaceable on a respective unit from a

Gear member and the grinding wheel (18,19) are arranged, which are rotatably mounted in the carrier (16; 60; 159).

10. Grinding head according to one of the preceding claims, wherein each grinding wheel (19; 63) and an associated gear member (154) on a

Swivel holder (156) trained arm is mounted and each swivel holder (156) on the disc-shaped carrier (159) is pivotable about a pivot axis parallel to the axis of rotation of the respective grinding wheel, in particular can be fastened in different pivot positions.

11. Grinding head according to claim 10, in which a drivable central gear member (150) is provided in the disc-shaped carrier (159), the other gear members (151) on the pivot axes of the pivot holder (156) together, preferably with a via a belt drive (160) Gear ratio of 1: 3 or greater, drives each additional

Gear member (151) is connected to the associated grinding wheel (19) via the associated gear member (154) (161).

12. A method of operating a grinding head according to claim 1, wherein

(a) with (only) one drive (5; n- _| ) a disk-shaped carrier (16; 60; 159) and a plurality of grinding disks (19; 63 arranged on the carrier (16; 60; 159) in a planetary manner) ) are driven at different speeds;

(b) two transmission elements lying one inside the other (22.25; 65.66; 11, 13; 58.59; 38) with essentially the same center point simultaneously the particularly significantly different speeds (n ₂ , n3) with correspondingly different torques on the Transfer the carrier (16; 60; 159) and the grinding wheels (19; 63).

13. The method according to claim 12, wherein the lower of the two speeds is transmitted by the radially outer transmission element (22, 25; 65, 66).

14. The method according to claim 12 or 13, wherein the higher of the two speeds is transmitted from the radially inner transmission element (11, 13; 58,59; 38).

15. The method of claim 12, wherein the two are nested

Transmission elements (22, 25; 65, 66; 11, 13; 58, 59; 38) keep the carrier (16; 60; 159) freely pivotable in space, in particular spherically.