JPS6076953A - Cam shaft grinder - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a workpiece table movable on a grinding wheel head towards and away from the grinding head; The present invention relates to a camshaft grinding machine with a work spindle supported and carrying a camshaft to be machined and a master cam or master cam set, and a guide roller associated with this master cam.

Camshaft grinders such as Kono are known (see Ostley Patent No. 108374). This grinding machine is manually operated, and the work is carried out using one master cam, regardless of the shape of the cam. That is, in practice, one master cam is used for all the intake cams and one master cam is used for all the exhaust cams on the camshaft of the engine. Before starting the grinding operation, each master cam is manually adjusted so that its shape axis coincides with the camshaft to be ground. This type of work cannot be done in automatic processing. Known camshaft grinding machines cannot be converted to an automatic mode of operation.

In the camshaft grinding machines for automatic mass machining commonly used today, one master cam set is provided for each master cam, and this master cam set is used for grinding. One master cam is provided for each individual cam of the camshaft. That is, for example 1
Grinding a shaft with two cams (6-gylinder motor) requires a set with 12 mass-cams. The manufacture of such master cam sets is relatively expensive.

In addition to the above, depending on the requirements for the precision of the cam geometry and depending on the given degree of utilization of the grinding wheel, i.e. the degree of wear of the grinding wheel that is permissible in the operation, For the different diameters of the grinding wheels that occur, a master cam set with the same circumferential surface is required in each case. Since it is extremely difficult to install such widely different master cam sets in one camshaft grinder, only limited wear of the grinding wheel is allowed or the requirements for accuracy of the cam shape are forced to be reduced. I don't get it.

Various attempts have already been made to provide an automatic relative rotation between the Yastar cam and the workpiece in camshaft grinding machines, corresponding to the manual adjustment mentioned at the beginning. However, this requires a different construction of the camshaft grinder. That is, the master cam and workpiece must be placed on different axes and separate drives must be used that rotate synchronously but counter to each other by a certain angle. Moreover, this design of the camshaft grinding machine has significant drawbacks and therefore cannot be used in practice (cf. DE 2821 753).

The object of the invention is to configure a camshaft grinding machine of the type described at the outset in such a way that an automatic relative rotation between the master cam and the workpiece is possible before each grinding process is started. .

This problem is solved by the present invention as follows.

That is, the master cam or master cam set is rotatably supported on the work spindle, the clutch mounted on the work spindle is configured to be mechanically disengageable, and the master cam or master cam set is coupled to the work spindle. to do,
The problem is solved by providing means for holding the master cam or master cam set in a constant angular position and by connecting an angle setting mechanism to the work spindle for determining the amount of adjustment of the angular position.

Furthermore, the above-mentioned problem is solved as follows by another configuration of the present invention. That is, a coupling mechanism is provided on the work spindle, which connects the work spindle to the workpiece carrier, mechanically releases this connection, and allows adjustment of the angular position of the master cam relative to the workpiece cam. The problem is solved by providing means for holding the carrier in a constant angular position and by connecting an angle setting mechanism to the work spindle for determining the amount of adjustment of the angular position.

Special features of the invention reside in the features of claims 3 to 11. Basically, a fixing device using a magnet falls under the structure, but in consideration of the requirement for high precision, the subject matter of claim 3.4.5.9 or 11 is a structure that is monolithic in shape. The mechanical structure is excellent in any case. In the embodiments according to patent claims 3, 4 and 5, the fixing device operates in a pivoting position of the workpiece pivoting table remote from the work spindle. This locking device is therefore forced into operation after machining the cam by the oscillating movement of the workpiece oscillating table. The extra time necessary for resetting the shape axes in this casting and the corresponding casting is reduced by choosing the construction according to claim 9. This, of course, requires correspondingly high costs for the mechanical construction and the machine control. However, all mechanical configurations have the advantage of being less prone to failure.

Similar considerations apply to mechanical dissociation of the coupling mechanism. Similarly, electrical mechanisms actuated via mechanical control arrangements or terminal switches are also applicable. However, at present, the mechanical configuration according to claims 6 to 8 or the hydraulic mechanism configuration according to claim 10 are superior. In these mechanical configurations, the coupling mechanism is likewise forcibly disengaged in a swinging position of the workpiece swinging table remote from the work spindle. In this case, the same applies as for fixation devices. Both with the construction of the hydraulic mechanism according to claim 10 and with the fixing device according to claim 11, the extra time for new adjustment of the shape axis is reduced to a minimum. It is also possible to carry out this adjustment completely independently of the oscillation path of the workpiece oscillation table. Of course, the control mechanism costs a lot of money.

The invention will now be explained in more detail with reference to the embodiments illustrated in the accompanying drawings.

In FIGS. 1 and 2, a currently common camshaft grinder has a workpiece swing table 11. As shown in FIGS. This workpiece rocking table has a grinding wheel 14 in two bearings 12 and 13.
It can be swung towards or away from the grinding wheel head in the direction of the arrow 9 on the grinding head shown by. As is well known, this rocking is caused by the master cam 62 of the mask cam set 15 moving towards the guide roller 63.
The rotary drive unit 1 of the work spindle 18 is pressed by this.
The position of the master cam induced by 6 determines the oscillating position, which determines how large the distance between the workpiece axis and the grinding wheel is. As a result, the master cam set 15 and the camshaft 52 to be processed are rotated by the drive unit 16, and at this time, the table 11 is swung according to the direction at that time, and the cam
For example, 17 desired shapes are obtained.

In FIG. 2, the means for holding and rotating the work spindle with master cam and workpiece 17 are omitted. Therefore, this figure shows the workpiece swing table 11 roughly in its working position so that it can be seen clearly. The cam 17, which is driven to rotate in this working position, is ground in accordance with the shape of the master cam 62.

As shown in Fig. 1, the workpiece swing table 11 has a bearing 1.
It carries a work spindle 18 which is rotatably journaled within the machine. A master cam set 15 is provided on the work spindle 18. Facing the workpiece 52, ie the camshaft blank, the work spindle is provided with an alignment point 54. This centering point is the tailstock shaft 57 which is supported by the tailstock 56.
The workpiece 52 is held in a predetermined orientation at the 20th alignment point 54 that is aligned in the same axial direction. To ensure the angular rotation of the workpiece 52, the carrier 19
is equipped with a carrier bolt 58, which cooperates with a corresponding abutment 59 of the workpiece. The drive motor 16 rotates the workpiece 52 and the master cam set 15 in equal motion phase via the workpiece spindle 18. The speed of the motor 16 is controlled by a mechanical control mechanism 61, known per se, which is actuated by an angle signal provided by an angle setting mechanism 29. Mechanical control mechanism 617, for example,
This applies to control mechanisms sold under the name 087-Control Mechanism manufactured by ltron Computer Gm'b'H, Inc.

With known machines, the work is carried out as follows. That is, after the grinding of the cam 17 is completed, the swing table is swung to move to the next cam. That is, the master cam is lifted off the guide roller, and the guide roller and the grinding head are then slid longitudinally in the direction of the new master cam and the next cam to be machined (alternatively, the oscillating table can be moved longitudinally). (can also be slid).

The camshaft grinding machine according to the invention is fundamentally constructed exactly as shown in FIG. Even in this configuration, a workpiece swing table 11', a workpiece drive section 16', and a master cam set 15' are provided. This master cam set is seated on a work spindle 18', which is rigidly connected to a drive 16' in exactly the same way as the work spindle 18 of the known machine shown in FIG. Examples are known and therefore will not be described in detail). This work spindle 18' carries a master cam set 15' and, at the end located on the right in FIG. 3, a workpiece carrier 19' which corresponds to the workpiece carrier 19 in the known grinding machine according to FIG. It carries

Master cam set 151 in the known machine according to FIG.
-j- In some cases, the work spindle is rigidly connected to the work spindle 1B via a master cam carrier (not shown), but in the embodiment according to the invention shown in FIG. A master cam carrier 21 is pressed in the direction of this connecting portion 20 by a spring 22.
is rotatably supported in such a way that the connecting part is rotationally rigidly connected to the corresponding connecting part 23 of the master cam carrier 21.

In the case of the illustrated embodiment, the coupling mechanisms 20-23 are gear clutch mechanisms, one of which allows for highly accurate positioning of the master cam companion relative to the work spindle in the engaged state. conduct. However, the other clutch mechanism is likewise known and can be used as known.

As shown in FIG. 4, the connecting plate 23 of the master cam carrier 21 is provided with an indexing hole 25 in the protrusion 24, and a workpiece spindle box or workpiece slider 64 is inserted into this indexing hole.
An index bolt 26 provided therein engages. This is illustrated schematically in FIG. 4 and is done as follows. That is, the rocking table 11' is rocked sufficiently far from the grinding wheel 14' and away from the grinding head at 75E, as is commonly done when making further connections after the completion of the grinding process. As soon as the master cam carrier 21 is moved, the indexing bolt 26 is inserted into the indexing hole 25 in a constant rotational position of the master cam carrier 21. For this purpose, in the grinding machine according to the invention the drive 16' is stopped at a fixed angular position. Correspondingly controllable and rapidly acting drives are common today, at least if the workpiece feed can be speed programmed, as is customary at present.

As shown in FIG. 5, the connecting portion 23 in the master cam carrier 21 is provided with a wedge-shaped surface 27, and
4 is provided with a correspondingly wedge-shaped wedge body 28. In the embodiment shown, the wedge body 28 and the indexing bolt 26 are identical, and the indexing hole 25 is correspondingly also
It has 7. However, this is not necessarily necessary.

In this way, when the swing table 11' swings at the above-mentioned angular position of the workpiece drive section 16', the index bolt 26
is fitted into the index hole 25, and at the same time the wedge body 28 is inserted into the wedge surface 2.
7. The two connecting parts 20 and 23 are therefore pushed apart against the action of the spring 22. This gives the master cam a very precise angular position and the work spindle 18' can be rotated independently by the drive 16' with a workpiece (not shown) connected via the carrier 19'. The drive 16' is rotated until the profile axis of the next workpiece cam coincides with the profile axis of the associated master cam. The required angular position is a general angle setting mechanism 29
′ is detected. Once the required rotation of the workpiece spindle 18' has taken place, which is confirmed by a control mechanism (not shown) on the basis of signals from the multi-angle setting mechanism 29', the workpiece drive 16' is stopped again and The swing table 11' swings again and engages. At this time, the indexed state of the master cam carriers 21 to 23 is forcibly released, and the spring 22 forms a connection. The next cam is then ground.

Instead of the wedge mechanisms 27-28 for uncoupling, lever mechanisms can also be used. The angle lever mechanism is illustrated in FIG. An angle lever 32 is supported on the work spindle bearing 30 through an arm 31, and in the swung position, this angle lever contacts the contact surface 33 of the work spindle at one end, and at the same time the other end. At its end it abuts the master cam carrier connecting portion 23'.

Another embodiment for uncoupling is shown in Figure 6A. In this figure, a lever 32' is supported on a work spindle box 64. This lever is actuated by the abutment surface 33' of the workpiece table for uncoupling.

Instead of the indexing mechanism according to FIG. 4, the abutment mechanism according to FIGS. 7A and 7B can also be used. No. 71. Connecting portion 23' of the master cam carrier not shown in Figure B
has a contact portion 34. The work spindle box 64 is provided with an associated abutment 35 . With this structure, the work spindle drive section 16' can remain at any position after the grinding process is completed. As soon as the workpiece swing table 11' comes into contact with the swing table abutment part 36,
The work spindle drive 16' is activated again. Connecting part 23
' is forcibly moved by friction until the contact portions of both vehicles come into contact as shown in FIG. 7B. Subsequently, the work spindle is rotated further by the required dimension, as clearly shown in FIG. 7B. At this time, the respective position is again announced by the angle setting mechanism 29' of the control mechanism.

Subsequently, the oscillating table 11' is oscillated again, so that the next cam can be machined.

In FIG. 7A, reference numeral 17 indicates a cam that has just been ground. The master cam 62 is indicated by a chain line in Figure 7, and is similar to this cam 17 in terms of shape and angular position.
corresponds to Cam blanks 67 of the same camshaft whose angular positions differ from those of the machined cam 17 and master cam 62 are indicated with diagonal lines to distinguish them. Here, in order to bring the cam blank 67 to be ground in the next work process to an angular position that matches the master cam 62, the work spindle, together with the master cam and the cam shaft, is moved so that the abutment part 34 is in contact with the abutment part 35-. rotated until they touch. The connecting part 23' carrying the abutting part 34 is connected to the seventh joint together with the master cam 62.
Since it is rotationally rigidly coupled via a cam carrier (see reference numeral 21 in FIG. 3), which is not shown in FIGS. occupy a position. Subsequently, the camshaft (see reference numeral 52 in FIG. 1) is rotated further until the angular position of the cam 67 coincides with the home position of the master cam 62. This correspondence is confirmed by the angle setting mechanism 27' (FIG. 3). The drive part 16' corresponds to the angle setting mechanism.
and stops this drive as soon as the desired angular position is reached. In order to be able to rotate the camshaft 52 without depending on the master cam 62, first the connecting parts 20 to 26 between the work spindle 18 and the master cam 62 are shown in FIGS. 5, 6, 6A and 9. Solve using the method shown in or similar method.

When the tool shaft table 11' is returned to the direction of the grinding wheel 14' and swung, the connection occurs again, and the cam shaft and master cam are driven at equal angles to each other.

In many cases, it is desirable for the oscillating table to have only a very small oscillating movement after the machining of the cam has been completed in order to save time. If the rocking movement is so slight that it does not cause enough rocking for reliable indexing locking and uncoupling, the special configuration according to the invention allows the indexing member 26 and the wedge to 28 or similar mechanical elements (levers, abutments, etc.) are not fixedly provided in the work spindle box, but are placed on the workpiece table, e.g. as shown in FIG. It is movably mounted on a swing 68 which counter-moves during unloading, thereby providing sufficient travel for indexing locking and uncoupling.

In order to move the swing 68, a hydraulic drive 69 consisting of a hydraulic cylinder 71 and a piston 72 is provided. This hydraulic cylinder is connected to a pressurized medium source 73, which is controlled by the machine control mechanism 61 when the workpiece swing table 11' is swung. The swing 68, together with the indexing bolt 26 and the machine body 28, is therefore swung in one direction, and the necessary swiveling distance of the workpiece swiveling table is shortened.

The embodiment according to the invention illustrated in FIG. 9 is fundamentally constructed in the same way as the general tabular camshaft grinding machine illustrated in FIGS. 1 and 2.

In this embodiment as well, a workpiece swinging table 11'', a workpiece drive 16'', a workpiece spindle 18'' that is firmly connected to the workpiece drive 16'', a master cam set 15'' sitting on the workpiece drive 16'', and At the end shown on the right side of FIG. 9, a workpiece carrier 19'' is provided. Even in the embodiment shown in FIG. 9, the master cam set 15" has a spring 22.
On the master cam carrier 21'' which is pressed against the connecting part 20'' at ``, this connecting part 20'' is pressed against the corresponding connecting part 23'' of the master cam carrier 21''
It is seated in such a way that it rotates and is firmly connected.

In the embodiment shown in FIG. 9, the connecting portion 20''~
23", a hydraulic drive 40 is provided, which in the illustrated embodiment is mounted on the swing table 11", that is to say on the body of the right-hand work spindle bearing 48. 1, the hydraulic drive unit 40 is equipped with a piston rod 41, and this piston rod is connected to the hydraulic drive unit 4.
0 in the working position (not shown) abuts against a radially projecting flange 42 of the master cam carrier 21''. A pressure medium source 76' flows in through the pressure medium inlet 43 and assumes the above-mentioned working position when the hydraulic drive 40 is moved against the action of the spring 44.

At the end shown on the left in FIG. 9, the master cam carrier 21'' is likewise provided with a radially projecting flange 45. An indexing bolt 47 is inserted into the extraction hole.This indexing bolt 47
It is assembled as follows. That is, the master cam carrier 21'' moves freely beside the indexing bolt 47 in the working position shown, whereas the master cam carrier 21'' moves freely by the hydraulic drive 40 in the corresponding rotational position, i.e. It is formed so as to fit into the open index hole 46 that is slid in the left direction in FIG.

In this embodiment, the operation is fundamentally the same as in the mechanical embodiments according to FIGS. 1 to 7 and 8. However, at a point in time when the rotational movement of the work spindle 18'' necessary for adjusting the shape axis (rotation axis of the camshaft) is early, that is, the space between the grinding wheel and the cam that has just finished machining is sufficient to allow rotation. The hydraulic drive 40 is activated completely independently of whether or how much the workpiece table 11'' has already been swung back. Therefore, the connecting portions 20'' to 23'' are separated, and the indexing member 46
．． 47 gets involved. As a result, the work spindle 18'' is immediately subsequently swiveled until the desired cam adjustment is achieved.

In place of the indexing members 46, 47, it is of course possible to use any other suitable locking device, i.e., which engages by axial movement of the master cam carrier 21''.

In this embodiment, the coupling mechanism is provided between the work spindle and the master cam carrier.

As an alternative to the above-described arrangement, it is also possible to provide an identical coupling mechanism between the workpiece, in particular the workpiece carrier, and the workpiece spindle. This would be easy for those skilled in the art, and therefore detailed description of this similar configuration is omitted as it is redundant.

In the embodiment according to FIG. 9, a holding force exists between the head of the piston rod 41 and the flange 42, which prevents the master cam carrier 21 from rotating further during the rotation of the camshaft. It is not necessary to provide the indexing bolt 47 and the indexing hole 46 as long as the For example, it is possible to provide the flange 42 with an index recess 74 corresponding to the head of the piston rod 41, as shown in broken lines in FIG.

In FIGS. 3, 5, 6, 6A, and 9, the master cam set is illustrated as an element that gives shape to the cam of the camshaft.

According to the invention, of course, only one master cam is required for the cams with the same shape of the camshaft. The angular position of this master cam is adjusted relative to the cam shaft by means of the invention, so that all equally shaped cams of the cam shaft can be formed with this one master cam.

According to the prior art according to FIG. 1, separate master cams are required for identical cams with different angular positions. therefore,
Every set of master cams has the same master cam at different angular positions. If a master cam set is a problem in the context of the present invention, then a master cam set that has differently formed cams to add differently formed cams on different cam axes is the problem. It is.

If the diameter of the grinding wheel is reduced, it is advantageous to use other master cams of the same set of master cams, the dimensions of which are adapted to the change in the diameter of the grinding wheel. Correspondingly, the master cam set used in the grinding machine proposed according to the invention has the same profile but different dimensions, in addition to different master cams for machining different cams of different cam axes. It is also equipped with a master cam.

According to the prior art, it is necessary to use different sets of master cams for this purpose. Therefore, it is necessary to replace the master cam set when moving to machining a camshaft having a cam of a different shape. Therefore, the grinding machine proposed by the present invention can be used in a variety of ways without the need for additional structural changes to replace the master cam set.

As a workpiece table, such a camshaft 4.degree. grinding machine generally uses a workpiece swinging table which can swing about an axis parallel to the workpiece spindle axis. The grinding machine according to the invention can also be constructed with a workpiece table that can move the grinding wheel unidirectionally or linearly away from the grinding wheel. A hydraulic drive 77 (see FIG. 8) is connected to a pressure medium source 78 to control the workpiece table 11' in reciprocating motion towards and away from the grinding wheel 14. Alternatively, a suitable drive connected to the mechanical control 61 and capable of moving it away from the grinding wheel against the force of the movement may be useful.

Drive motor 1 for work spindle 18.18', j8"
6, 16', 16'', for example, Maschineuwerke Fr.
ankfurt M, W, Ulrich GmbH &
An axial piston motor HMU80 manufactured by Co., Ltd. is used.

[Brief explanation of the drawing]

1 is a schematic diagram of a workpiece rocking table of a known type; FIG. 2 is a side view of the workpiece rocking table according to FIG. 1 during a grinding operation; and FIG. 3 is a modified version according to the invention. Workpiece table 1
The figures correspond to the figures shown in Fig. 3, but in this case, of course, the tool parts are omitted for better visibility. Parts of the workpiece table according to Figures 6 and 6A
The figures correspond respectively to FIG. 5 in a partial plan view of different embodiments of the invention, and FIGS. 7A and 7B correspond to FIG. 4 in two working positions of another embodiment of the invention. 8 is a sectional view corresponding to FIG. 4 of a further embodiment of the invention; FIG. 9 is a sectional view corresponding to FIG. 6 of a further embodiment of the invention with a hydraulic uncoupling device; Figure to do. The symbols in the figure are j5, 15"...Master cam set 20.23, 20", 23"...Connection mechanism 25.26
, 34, 35, 41. 42, 46゜47... Holding means agent Mitsuyoshi Ezaki Agent Mitsufumi Esaki FlG, 7A FlG, 7B Continued from page 1 0 Inventor Josef Siehue Federal Republic of Germany, Le Isen, 26 Schuttgart 7\Herzlesu

Claims (1)

[Claims] 1. A workpiece table movable on the grinding wheel head toward and away from the grinding head, rotatably supported on the workpiece table. In a camshaft grinding machine equipped with a work spindle carrying a camshaft to be machined and a master cam or master cam set, and a guide roller belonging to this master cam, the master cam or master cam set (15':15 ′)
rotatably supported on the work spindle (1B': 18'), and a clutch (20
,2! The master cam set (15', 1
5') with the work spindle (1a';1a'), and the master cam also has 16 holes.The master cam set (15':
15') in a constant angular position.
, 26:34, 35:41, 42:46.47), and the angle setting mechanism (29') was connected to the work spindle (1g', 1a') to determine the amount of adjustment of the angular position. A camshaft grinder characterized by: 2. Workpiece swing table (11”
1. The camshaft grinding machine according to claim 1, wherein the camshaft grinder is provided with: l. 5. The holding means (25, 26') consist of a pin (26), which cooperates with a corresponding hole (25) or groove, which is connected to the workpiece slide (64) on the one hand and to the master cam assembly (26) on the other hand. 15') or workpiece carrier (19')
The camshaft grinding machine according to claim 1 or 2, wherein the camshaft grinder is provided with K. 4. The holding means (s4.55') is the master cam set (15
15') and an abutment member (34:35) provided on the workpiece slider (64). 5 The fixing device (34, 35) is attached to the workpiece carrier (19'
A camshaft grinding machine as claimed in claim 1, comprising: 19') and an abutment (34:35) provided on the workpiece slider (64). & Mechanical disassociation of the coupling part (20, 23) on the one hand to the workpiece slider (64) and on the other hand to the movable coupling part (
23) Two cooperating wedge surfaces formed in (28:27)
A camshaft grinding machine according to any one of claims 1 to 5, characterized in that the grinding is performed by rocking the workpiece table (11') through the camshaft grinding machine. 2. Mechanical disassociation of the connecting parts (20, 23) is carried out by means of a two-armed angle lever (32) bearing on the workpiece rocking table (11'), one arm of which is movable. abuts against the end face of the connecting part (23"),
Claims 1 to 6, wherein the other arm is configured to come into contact with the contact portion (33) on the workpiece slider side when the workpiece slider (11') swings. A camshaft grinder as described in any one of the above. a) Mechanical dissociation of the connecting parts (20, 23') causes contact with the end face of the movable connecting part (23') and also with the abutting part (33') fixed to the workpiece swing table. One arm angle lever bearing on the workpiece slider (64)
(The camshaft grinding machine according to any one of claims 1 to 7, configured to be carried out by a 32' NC. 9 Holding means (25, 26: 34, 35 ), the workpiece slider side portion (26:35) is movable in the lateral direction with respect to the workpiece spindle (1B'), any one of claims 1 to 8. The camshaft grinder described in 1. The mechanical dissociation of the connecting parts (20', 23') is performed by the piston cylinder unit (40, 41, 43) provided on the workpiece swing table (11'). A camshaft grinding machine according to any one of claims 1 to 9. It consists of a pin (47) arranged axially parallel to the pin, which co-operates with a corresponding hole (46) or groove, which on the one hand is connected to the workpiece rocking table (11') and on the other hand Master cam set (15') or workpiece carrier (19')
) as provided in Claims 1 to 10.
A camshaft grinder as described in any one of the preceding paragraphs. 12. Acting against the force of the return spring (75) to move the workpiece table (11', 11') in one direction and away from the grinding wheel, Camshaft grinding machine according to one of the claims 1 to 11, characterized in that it is provided with a drive (77) which is connected to a camshaft grinding machine (61). a workpiece table movable in the direction of and away from the grinding head, rotatably supported on the workpiece table and carrying a camshaft and a master cam or master cam set to be machined; In a camshaft grinding machine equipped with a work spindle and a guide roller belonging to this master cam, this work spindle (
1B': 18") i Workpiece carrier (19', 19
a coupling mechanism (20, 23: 20', 23') that mechanically releases the coupling and allows adjustment of the angular position of the master cam with respect to the cam of the workpiece; Means for holding the carrier (19';19') in a constant angular position (25°26;34,35:4
1, 42: 46, 47) and that the angle setting mechanism (29') is coupled to the work spindle (1B'S 1 B') in order to determine the amount of adjustment of the angular position. Camshaft grinding machine. (11')
The camshaft grinder described in section. 15. The holding means <25.26") consists of a pin (26), the pin cooperating with a corresponding hole (25) or groove;
This connects the workpiece slider (64) on the one hand and the master cam set (15') or the workpiece carrier (19') on the other hand.
) The camshaft grinding machine according to claim 13 or 14, which is provided in a. 16 The holding means (34, 35) are connected to the master cam assembly (15
The camshaft grinding machine according to claim 13, comprising a contact member (34:35) provided on the workpiece slider (64). 1z Fixture @ (54, 35) is the workpiece carrier (19
14. Camshaft grinding machine according to claim 13, comprising an abutment (34:35) provided on the workpiece slider (64). 1a Mechanical disassociation of the connecting part (20, 23) results in two cooperating wedge surfaces (2s: 27) formed on the workpiece slider (64) on the one hand and on the movable connecting part (23) on the other hand.
) A camshaft grinding machine according to any one of claims 13 to 17, characterized in that the grinding is performed by rocking the workpiece table (11') via e. 19 Mechanical disassociation of the connecting parts (20, 23) is carried out by means of a two-armed angle lever (32) bearing on the workpiece rocking table (11'), one arm of which moves The patent claim is configured such that the other arm contacts the end face of the connecting portion (23'), and the other arm contacts the contact portion (33) on the workpiece slider side when the workpiece slider (11') swings. The camshaft grinder according to any one of items 13 to 18. 2α The mechanical dissociation of the connecting parts (20, 23) abuts both the end face of the movable connecting part (23') and the abutment part (33') fixed to the workpiece rocking table. One-arm angle rail bearing on the workpiece slider (64), (-
(32') A camshaft grinding machine according to any one of claims 13 to 19. 21. The workpiece slider side portion (2b:s5) of the holding means (25, 26: 34, 35) is movable in the lateral direction with respect to the workpiece spindle (1B''). Claim 13
The camshaft grinder according to any one of Items 1 to 20. 22 The mechanical disassociation force of the connected portions (20', 2s') 5 is configured to be performed by a piston cylinder unit (40, 41, 43) provided on the workpiece swing table (11'). Claims 13 to 21
The camshaft grinder described in any one of the preceding paragraphs. 25. The holding means (46, 47) consist of pins (47) arranged axially parallel to the work spindle (1B''), the pins cooperating with corresponding holes (46) or grooves, which On the one hand, the workpiece swing table (11'), on the other hand, the master cam set (15') or the workpiece carrier (+9
The camshaft grinding machine according to any one of claims 13 to 22, which is provided in 1. 24 Workpiece table (11', 11'') A drive (77) is provided which acts against the force of the return gear (75) and is coupled to the mechanism control mechanism (61) for movement in the direction and away from the grinding wheel. A camshaft grinder according to any one of claims 13 to 23, wherein