JPH0323287B2 - - Google Patents

Description

Detailed Description of the Invention [Industrial Field of Application] The present invention relates to a method for manufacturing and processing teeth of a straight gear or a helical gear, as defined in the generic concept of claim 1, and Regarding machines.

The prior art of the present invention is the known technology described in West German Patent Application Publication No. 1161465. The West German specifications mentioned above actually include gear shaving,
Theoretically, a polishing method is disclosed, and this polishing method is so-called gear honing, in short, a tooth surface machining method performed in a state where a workpiece and a tool are meshed without consistency. In this machining method, which is performed without a backlash, force acts on the tooth surfaces on both sides of the meshing teeth, unlike the rolling method, which performs machining with a backlash. This force changes depending on how many tooth flanks are momentarily involved in meshing. This changing force (the above-mentioned West German patent publication no.
(referred to as "play of force" in specification No. 1161465)
will result in an error unless the shaving gear is specially designed. Therefore, a guide gear system that meshes and rotates without backlash is useful.

In gear honing, the use of guide gears that mesh and rotate without backlash does not improve the results of the work. Damage to the tool teeth is already repeatedly observed in gear honing without the use of guiding gears. This renders the tool prematurely unusable. This damage is due in part to the aforementioned varying forces and in part to the compression of the tool tooth within the workpiece tooth groove. Various factors are involved in the cause of this compression. Squeezing occurs, for example, when the workpiece has an excessive machining allowance, or when the workpiece has upsetting or distortion caused during heat treatment. However, this damage cannot be prevented with known guide gearing. Due to the complete lack of backlash in the meshing between the tool teeth and the workpiece and the meshing between the guide gears, the entire system consisting of the workpiece, tool, and guide gearing becomes rigid, and as a result, the tool They lose their “place of escape.” Despite the increased tool cost due to premature tool damage, the machining results are unsatisfactory.

OBJECT OF THE INVENTION The object of the invention is therefore to eliminate the above-mentioned disadvantages of machines of the type mentioned at the outset.

[Means for Solving the Problem] The gist of the machine of the present invention that solves this problem is as described in claim 1. In the present invention, the term "wheel-like tooth surface" means an abrasive tooth surface that grinds the tooth surface of a workpiece without cutting edges or the like. (Shaving katsuta does not belong to this category).

Another object of the present invention is to reliably prevent contact between tooth surfaces that should not come into contact during machining.

A machine of the present invention that solves this problem is described in claim 2.

Various embodiments of the machine according to the invention are possible. For example, according to claim 17, instead of the guide gear, friction wheels or friction discs or the like can be used, the manufacture of which is relatively simple. Care only needs to be taken that these have the correct transmission ratio.

In another embodiment of the present invention, claim 18
As described in section 1, a guide gear is used as a guide wheel. In this case as well, it is sufficient to simply match the transmission ratio. There is no need to match the meshing pitch of the tool/workpiece pair with the meshing pitch of the guide gear pair. On the contrary, it is more effective if both engagement pitches are different. This is because even if there is a pitch error caused by the machine, it is compensated for.

If the machine according to the invention is used for mass production, a separate machine can be used for machining the respective right flank or left flank of the workpiece tooth.
Since both machines are then generally arranged in one production line, this does not increase the overall machining time and, on the other hand, makes the machine simpler, cheaper and less prone to breakdowns. With the configuration recited in claim 3, equipment costs are reduced as a whole.

Various embodiments are proposed for this purpose, but the embodiment according to claim 4 is particularly advantageous.

Further advantageous embodiments are described in claim 5. According to this embodiment, there is no need to consider the engagement between the teeth of the tool and the teeth of the workpiece, and moreover, the radial feed during machining only needs to be carried out once or in stages. This effectively eliminates periodic (wavy) deviations in the tooth profile that may occur in the tooth height direction, or deviations in the tooth profile that may occur due to protruding grains. be able to.

A further important embodiment is set out in claim 6. This embodiment likewise serves to improve processing quality.

For simple and inexpensive adjustment in the circumferential direction, the embodiment according to claim 7 is advantageous.

The embodiments according to claims 8 and 9 serve for simple operation for adjusting the tool relative to the workpiece, in particular for automatic machining termination.

The embodiment described in claim 19 is an effective embodiment. This is because cutting can be performed without changing the axis spacing.

The embodiment described in claim 10 is also an effective embodiment. This is because an effect similar to that of a tensile test stand can be obtained. The sheath spring offers the possibility of controlling the contact pressure on the tooth flanks to be machined,
and, in some cases, to make replacement of tooth flanks more flexible.

The quality of the workpiece, especially in relation to periodic deviations of the workpiece tooth flanks, is further improved.

Re-equipment of the machine of the present invention is claimed in claim 11.
This is simplified by the embodiments described in Sections 1 and 12. In this case, the exchange wheel refers to a gear or a friction wheel mounted on a bearing for easy exchange, similar to the exchange gear on a lathe. Known exchange gear systems can also be used in this connection.

In order to simplify the adjustment of the workpiece/tool tooth flanks with respect to the two guide gear tooth flanks or to have the possibility of automating this adjustment, the embodiment according to claim 13 serves.

In order to avoid undesirably changing the tooth contact in the machining method using the machine of the invention and to ensure reliable operation of the switchable clutch according to claim 13, if present, the patent The embodiment according to claim 14 is useful.

Claim 15 indicates an advantageous further embodiment of the invention, in which the working surface, in particular the friction surface in the case of a friction wheel or the tooth surface in the case of a guide gear, is coated with a wear-resistant material, for example titanium nitride. Alternatively, it can be coated with hard chromium or the like, and the guide gear can be coated with a plastic material having good sliding properties. Also advantageous are coating materials that are wear-resistant and at the same time have good sliding properties.

A further advantageous embodiment is shown in claim 16. As a protection device, a casing surrounding the guide wheel may be provided, or a plate for deflecting flying objects and chips may be inserted between the guide wheel pair and the work/tool pair. A combination of both may also be used.

The gist of the method of the present invention is as described in claim 21. An advantageous embodiment of the method according to the invention is defined in claim 22, with which the quality of the processing is further improved.

In the embodiment described in claim 23, the direction of rotation is changed in order to replace the contacting tooth surfaces, and at this time, the sliding direction of the tooth surfaces in the tooth height direction is also changed. In other words, depending on which spindle of the tool/workpiece pair is the driven spindle, the relative movement is from the tip to the root or vice versa ("pushing" or "pulling"). .

According to the embodiment described in claim 24, there is no need to switch the rotation direction, and the machining time may be shortened depending on the case, but the machining accuracy may be improved depending on the case. This is not as good as when In addition, according to this embodiment, when high machining accuracy is desired, the deflection of the teeth must be taken into consideration.

Another advantage of the invention is that the right and left workpiece tooth flanks
Contact with the corresponding tool tooth surface is obtained more quickly and precisely than in known machines, and independently of the varying tooth thickness of the workpiece teeth and independently of the state of wear of the tool teeth.

Front positioning of the workpiece tooth relative to the tool tooth groove is easy. A preselected amount is removed from the workpiece tooth surface very accurately and time-independently. What has been described above also applies to the time of face-dressing using a face-dressing vehicle.

A particular advantage of the invention is that the machining allowance is predetermined. Machining costs no longer depend solely on machining time. Moreover, the tools are protected. This is because the tooth surfaces do not come into contact during starting and braking.

In the device according to the invention, the machining process is not interrupted, so the pressure of the tool tooth on the workpiece tooth is approximately equal to the machining pressure. Furthermore, the tooth surface contact is not interrupted even during deceleration machining conditions.

The present invention operates with so-called single flank contact. In other words, only one side of the meshing teeth makes contact. However, the entire transmission consisting of the tool tooth, workpiece tooth, and both guide teeth meshes with both tooth flanks in contact.In other words, when the tool tooth is in contact with the workpiece tooth, for example on the right tooth flank, the guide tooth They contact each other on the left tooth surface, or vice versa. Therefore, separation of the tooth surfaces due to vibration or other influences is reliably prevented. As a result, the cutting feed is carried out simply by reducing the shaft spacing and, because of this, without the special movements required during non-bundling movements of the guide wheels. On the other hand, due to the one-sided flank contact of the tool teeth, the tooth flanks of the tool teeth can be machined in contact with essentially a large part of the tooth flank.

In the present invention, the concept of "reversible motor" means that when two machines are provided for machining tooth flanks on one side, one motor rotates in one direction of rotation and the other Including the motor rotating in the opposite direction of rotation. In that case, the motor is considered to be switched by transferring the workpiece from one machine to the other.

The guide gear pair must have as large a meshing contact surface as possible. The limit of possible modification of the teeth is up to a point where the tooth tip of the guide gear becomes significantly thinner.

Often one tooth flank of a workpiece has to be cut more or less than another tooth flank. In such a case, the cutting allowance of each tooth flank is individually adjusted by the machine of the present invention.

The present invention is not limited to external gears, but can also be applied to internal gears.

Next, the present invention will be specifically explained with reference to the illustrated embodiments.

A workpiece gear 2 (hereinafter simply referred to as workpiece) and a guide gear 3 are mounted on a workpiece spindle 1 and are coaxial with each other. The workpiece 2 and the guide gear 3 are fixed to the workpiece spindle 1 in a non-rotatable, non-axially movable and replaceable manner. A toothed tool 6 (hereinafter simply referred to as tool) and a guide gear 7 are fixed to the tool spindle 5 in a manner that is likewise non-rotatable, non-axially movable and replaceable. The tool 6 has an abrasive machining surface, that is, a wheel-shaped tooth surface, and meshes with the teeth of the workpiece 2. The guide gear 7 and the guide gear 3 mesh with each other. The axis of the work spindle 1 and the axis of the tool spindle 5 intersect with each other at a distance. The so-called common perpendicular 8 lies either in the area of the workpiece/tool pair, for example in the center or in the area of the guide gear pair, or in their vicinity, for example between the workpiece/tool pair and the guide gear pair. This machine uses the so-called plunge cut method. In short, the tooth flanks of the workpiece teeth are processed, for example, cut, without vertically feeding the tool relative to the workpiece. Therefore, the pitch cylinder of the tool must overlap and mesh with the pitch cylinder of the workpiece in a hyperboloidal manner. Furthermore, the tool tooth must contact the workpiece tooth over its entire width. In FIG. 1, the common normal 8 is located in the center of the workpiece tooth, so that the hyperboloid curve 9 of the tool is illustrated symmetrically with respect to the common normal 8.

FIG. 2 shows an enlarged view of the engagement between the tooth grooves of the guide gear 7 and the teeth of the guide gear 3. The tooth surfaces are in contact on the left side, and there is a break on the right side. Similarly, FIG. 3 shows an enlarged view of the engagement between the tooth grooves of the tool 6 and the teeth of the workpiece 2. In this case, the tooth surfaces are in contact on the right side, and there is a backlash on the left side. In short, in the illustrated example, the right tooth flank of the workpiece is machined, and the left tooth flank of the coaxial guide gear 3 is used to machine the workpiece.
The right tooth flank of the workpiece 2 is prevented from separating from the tooth flank of the tool. When machining the workpiece tooth surface on the other side, exchange the relative positions of both gear pairs,
In short, the tooth surfaces are brought into contact on the right side in Figure 2, and on the left side in Figure 3. The method of replacing this tooth surface will be explained in detail below.

FIG. 4 shows an embodiment of the tool spindle 5. FIG.
The tool spindle 5 is mounted in a tool spindle head 10, which is shown partially cut away. A receiver 11 is fixed in a non-rotatable and axially movable manner on the tool spindle. A tool 6 is supported in the receiver 11 and is fastened non-rotatably by known means (not shown) and axially movably by a tightening nut 12. The tool 6 is engaged with the workpiece 2. A guide gear 7 is positioned within the receiver, the guide gear 7 meshing with another guide gear 3 . The guide gear 7 is rotatably arranged in the receiver, and the tightening device 13 (bolt, disc, nut) and the spring 1
4 is tightened and held in the axial direction. A feed mechanism 15 engages in the receiver 11 on the one hand and in the guide gear 7 on the other hand;
is shown in detail in FIG. The feed mechanism 15 essentially consists of a basic body 16 and a strip 17 provided on its upper surface, which engages in a groove 18 provided in the receiver 11 parallel to the axis of the tool 6. Base 1
A key 19 is provided on the underside of 6, which engages in a groove 20 provided in the boss of the guide gear 7 at an angle to the axis of the tool. Feeding mechanism 1
When 5 moves axially, the guide gear 7 rotates relative to the tool 6. This changes the relative position of the teeth of the guide gear 7 and the teeth of the tool 6 (FIGS. 2 and 3). It is advantageous if a plurality of such feed mechanisms are provided distributed around the circumference. In order to be able to move the feed mechanism, the feed mechanism is provided with a switching ring 21, on which a thrust bearing 22 is arranged so as to be immovable in the longitudinal direction. This thrust bearing is partially surrounded by a switching fork 23. The switching fork is connected via a piston rod to a piston 24, which partitions two chambers 26, 27 in the cylinder 25. These chambers 26, 27 are selectively loaded by a control device 28 via lines 29, 30 with a hydraulic or pneumatic pressure medium. in short,
The control device 28 defines the relative positions of the tooth flanks of the tool and the guide gear, and thus the relative positions of the tooth flanks of the tool and the workpiece. The stroke of the feed mechanism 15 may be limited by stop devices 95, 96.

When high precision is required, it is effective to insert a large number of balls or rollers held at intervals by a cage between the sliding surfaces of the feed mechanism.

The illustrated feeding mechanism is merely one example. Advantageously,
It is best to use helical gears and arrange them so that they can be moved. In that case, the shaft serves as the strip and the helical tooth serves as the key.

6 and 7 show a device for adjusting the displacement of the tooth surfaces of the tool 6 and the guide gear 7 by means of hydraulic or pneumatic rotating pistons. The tool 6 is fixed non-rotatably and axially movably on a tool spindle 31, which is rotatably and axially movably supported on a machine frame 32 or a suitable slide. Rotational drive is provided via shaft 31a. A work spindle not shown in FIG. 6 may be made drivable. A cylinder 33 is rotatably but immovably mounted on the tool spindle. A guide gear 7 is mounted non-rotatably and non-moveably in the longitudinal direction on the outer wall of the cylinder. The tool spindle is designed at one end as a rotating piston 34 (see FIG. 7).

The rotary piston 34 forms two chambers 36, 37 together with the inner shape 35 of the cylinder 33, into which holes 38, 39 open, respectively. In order to be able to supply pressure medium, the cylinder is equipped with a pin part 40 on which a supply bush 41 is rotatably and tightly guided in a known manner. From the supply bush there are conduits 42, 43.
is guided to the control device 44. From the control device are conduits 42, 43, supply bit 41 and hole 3.
Via 8, 39, both chambers 36, 37 are supplied with pressure medium. This drives the rotating piston and changes the relative position of the tooth flanks. This also makes it possible to control the contact pressure on the tool tooth surface. This is because the corresponding tooth flank of the guide gear is supported by the other guide gear (see FIGS. 2 and 3).
Components useful for supplying pressure medium, such as pumps, filters, valves, etc., are not shown for simplicity. Since the control device is also well known, it is not shown.

FIG. 8 shows an electromagnetic drive which can be used in place of the devices described in FIGS. 6 and 7. Instead of a rotary piston, the tool spindle 31 in this case has a lever 45 which engages in an armature 46, which is guided longitudinally displaceably in the cylinder 33a. The mover is controlled by two electromagnets 47,48. Electromagnet 4
7 and 48 are supplied with current through a slip ring mechanism 49.

FIG. 9 shows a tool/guide gear support mechanism in which a pair of guide gears are meshed with each other without backlash. A known slider guide mechanism (dovetail groove guide or prismatic guide mechanism) 52 is provided in a tool carriage 51 that feeds cutting in the radial direction to the workpiece 2. Auxiliary carriage 53 guided radially relative to 2
is provided. This auxiliary carriage is connected to an electric motor 54 via a worm transmission 55, a feed spindle 56, and a feed nut 57 fixed to the auxiliary carriage.
driven by. A tool spindle 58 is rotatably and longitudinally displaceably mounted in the auxiliary carriage. The tool spindle receives a tool 6 in a known manner. A guide gear spindle is rotatably mounted in a tool carriage 51 approximately coaxially or axially parallel to the tool spindle. A rotating piston mechanism is attached to the end face of the guide gear spindle, and this is shown in Figures 6 and 7.
This is as explained in the figure. Rotating piston mechanism 60
The cylinder is fixed to a guide gear spindle 59. This guide gear spindle 59 is hollow, into which a torsion rod spring 61 projects in the axial direction. This torsion rod spring is fastened on the one hand to the tool spindle 58 and on the other hand to the piston of the rotating piston mechanism. This device allows for deviations of the tool axis relative to the guide gear axis. This deviation is extremely small. This is because the torsion rod spring only needs to allow a deviation equal to the amount of cutting feed in the radial direction. The torsion rod spring provides a torque transmission between the tool spindle and the guide gear spindle and at the same time serves for the elastic contact of the tooth flanks. The radial cutting feed is controlled by an electric motor 54. The shaft 61 can also be provided with a clutch.

The tool carriage 51 is supported in the machine frame or in a part 62 connected thereto by a circular guide 63, by means of which it is also possible to adjust the cross-axis angle between the workpiece and the tool. I can do it. A fastening member for fixing is not shown.

If the torsion bar spring is insufficient to accommodate the radial displacement, a clutch 77 can be provided instead to allow translation of the shaft. 10 and 11.
It can consist of a cross-locking clutch as shown in the figure. The cruciform clutch 77 generally consists of two clutch halves 64, 65, each of which is provided with a groove 66, 67 between its end faces extending along a respective centerline. A cross plate 68 is inserted between the two clutch halves and is provided with a mating strip 69, 70 on each end face. The mating conditions are oriented at right angles to each other and fit into the grooves. A large number of balls or rollers may be advantageously inserted between the sliding surfaces (not shown).

In the embodiment shown in FIG. 9, one of the guide gears is designed as a segmented elastic gear in order to mesh the guide gears without backlashing of the tooth surfaces. An example thereof is shown in FIGS. 12 and 13.

The guide gear 71 mainly consists of two halves 72, 73.
Consists of. One half 72 is provided with a positioning boss 74 on which the other half 73 is rotatably supported. Both halves have identical teeth. With the teeth of both halves offset by a predetermined amount, matching holes are drilled through both halves, into which a bushing 7 of elastic material is placed.
5 or a plug is inserted. When both halves try to rotate relative to each other so as to eliminate the misalignment of their teeth, an elastic force acts to return it to its starting position. The half supported on the boss is Natsuto 7
6. Resilient gears are known in various forms, in which leaf springs or coil springs are used as the elastic member.

FIG. 14 shows the working process of the method of the present invention step by step. Reference numeral 80 indicates a tool tooth, and reference numeral 81 indicates a workpiece tooth space. The method of the present invention is carried out in the following steps.

a) Bringing tools closer together. Until the tool tooth 80 reaches the starting position for machining with a crushing in the tooth groove of the workpiece, or vice versa. Introduction of rotational motion.

b) Adjust the tool by moving it laterally in the circumferential direction relative to the workpiece until the tooth surfaces are in contact. Cutting.

c) Radial feed, cutting.

d) Departure approximately to position a.

e) Lateral movement and cutting until contact with the tooth surface of the other workpiece.

f) Radial feed, cutting.

g) Separation movements similar to a and b.

h Stopping the machine and returning it to the starting position.

Processing steps b-g may be repeated or otherwise combined.

The processing procedure described above is an example of a relatively complicated method. Relatively simple processing steps, such as steps a, b, e, h, are also possible.

FIG. 14i shows that by repeated radial feeding, wave-like deviations on the workpiece tooth surface are eliminated, especially when the feeding rhythm corresponds to the wavelength of the deviation.

15 to 18 show another embodiment of the invention. Parts unnecessary for explanation have been omitted. code 2
6 indicates a workpiece, numeral 6 indicates a tool, and numerals 3 and 7 indicate guide gears (see FIG. 1). The workpiece/tool pair 2, 6 and the guide gear pair 3, 7 are shown far apart for clarity, so that the workpiece spindle 1 and the tool spindle 5 are also shown significantly longer. Reference numeral 85 indicates a drive motor. The components shown on the tool spindle 5 are the feed mechanism 15
This feed mechanism exchanges the flank contact from left to right flank and vice versa.

In the embodiment shown in FIG. 16, the tool spindle is stationary. Switching clutch 86 to work spindle
is inserted. One motor 87, 88 is arranged on each side of the work spindle 1,
The motor can also be connected for braking. For example, the motor 88 is used for braking, the guide gear 3 is slightly rotated by the motor 87 with the switching clutch 86 disengaged, and the guide gear pair 3,
The tooth flanks 7 touch for example on the left side as shown in FIG. The rotational movement is then transmitted via the guide gear 7 and the tool spindle 5 to the tool 6, which rotates. Since the guide gear 2 is prevented from rotating by the motor 88, which acts as a brake, the tooth flank of the tool contacts the right flank of the guide gear 2, as shown in FIG. Thereafter, the switching clutch 86 is engaged, the braking action of the motor 88 is eliminated, and a rotary movement is introduced by the motor 87, thereby effecting the machining.

Motor 88 is used for driving, motor 87
When used for braking, by rotating the motor 88 in the same direction of rotation as before, the tooth flank contact is exchanged and the opposite tooth flank of the workpiece tooth is machined.

In the embodiment shown in FIG. 17, only a motor 87 is provided on the left side of the work spindle, and a brake or flywheel 89 is provided on the right side of the work spindle. The driving tooth flank and thus the cutting tooth flank are exchanged by the direction of rotation of the motor and by opening and closing the switching clutch 86. The action of the brake is as explained in the embodiment shown in FIG. If a flywheel is provided, its static inertia provides the braking action.

FIG. 18 shows an embodiment in which the tool spindle and the workpiece spindle each have one switching clutch 90, 91. The work spindle is connected to a motor 85 on the left side and is provided with a brake or flywheel 89 on the other side. The tool spindle is connected to a motor 92 on the right side. This embodiment also effectively controls the tooth surface contact.

In FIG. 18, as an example, friction wheels 93 and 94 are provided in place of the guide gear. The motor is an electric motor or a hydraulic motor.

By switching the rotational direction of the motor or connecting and disconnecting the motor as shown in FIGS. 16 to 18, and further connecting and disconnecting the switching clutches 86, 90, and 91, the tooth surface on the driving side of the system is The cutting tooth flank is thereby also replaced.

In a further embodiment, not shown, the guide gears fastened to the workpiece spindle and to the tool spindle are designed so that they do not mesh with each other. For this purpose, two easily replaceable replacement gears are provided between the two guide gears, which mesh with both guide gears. Instead of this exchange gear, it is also possible, for example, to use exchange gear systems commonly known for lathes and milling machines.

FIG. 19 shows an embodiment for machining an internal gear. This principle can also be used in all other embodiments described for external gears.

In the embodiment shown in FIG. 20, a workpiece 2 and a guide gear 3 are similarly mounted coaxially on a tool spindle 1 in parallel with each other. The workpiece and the guide gear are fixed to the workpiece spindle in a non-rotatable, longitudinally non-movable and replaceable manner by means of a clamping device (not shown). Tool spindle 5 has tool 6
and a guide gear 7 are fixed so as to be non-rotatable and non-movable in the longitudinal direction. The tool spindle 5 is connected at one end to a motor 101, for example an electric motor. The direction of rotation of this motor can be changed by changing the polarity or by means of a transmission (not shown).

The work spindle 1 that is not connected to the motor is equipped with a brake 102 . This brake can be connected and disconnected. This brake 10
The action of 2 will be explained later together with the brakes shown in FIGS. 21 and 22.

In the embodiment shown in FIG. 21, the spindle connected to the motor 101 is, for example, a tool spindle 5, which is additionally provided with a switchable clutch 103 between the guide gear 7 and the tool 6. Therefore, the guide gear 7 and the tool 6 can be separated from each other during operation.

In the embodiment shown in FIG. 22, the spindle connected to the motor 101 is a tool spindle 5, which additionally has a brake 104.
Alternatively, a flywheel is provided at the end opposite to the motor 101. A clutch 103 is inserted into the tool spindle 5 between the tool 6 and the guide gear 2.

The role of the brake 102 shown in FIGS. 20, 21 and 22 is slightly different from that of the previously described brake or flywheel 89, in that it ensures constant contact of the tooth flanks of the guide gear and therefore The contact pressure on the surface is approximately equal to the processing pressure. It is advantageous if the tooth surface contact of the guide gear is not interrupted when the brake is released. The purpose of the brake 104 or flywheel is to increase the frictional torque of the tool spindle 5 upon disengagement of the clutch 103. According to this embodiment, the tooth flanks of the guide gear 7 and the tooth flanks of the tool 6 are brought into contact reliably and with a small preload. The brake 104 or flywheel prevents the tool tooth flanks from undesirably separating.

The operation of the machine shown in FIG. 22 is the same as that of the machine shown in FIG.

FIG. 23 shows the processing procedure of the mechanical method shown in FIG. 22 in various states. Only one tooth or one tooth space in each case of the gear wheel involved in machining is shown.

In FIGS. 23a to 23h, the right tooth flank is designated by the symbol R, and the left tooth flank is designated by the symbol L, respectively. As already mentioned, the guide gear 3 and the workpiece 2 are fixed on a common spindle 1 and are fixedly connected to one another. A switchable clutch 103 is inserted into the other spindle (FIGS. 21 and 22).

In FIG. 23, the roots of the teeth of the guide gear 7 and the tool 6 are connected to each other. This is tool spindle 5
It means that they are connected by. The two thick vertical lines within this coupling line represent the released clutch 103. The two thick vertical lines are not shown when the clutch is engaged.

(FIG. 23a) The workpiece 2 meshes with the teeth of the tool 6 and is clamped onto the workpiece spindle 1.
Clutch 103 is open. The drive device (motor 101) provides a slight rotational movement in any direction. The rotation direction in this example is called "positive".

Therefore, the left flank of the guide gear 7 drives the left flank of the guide gear 3. As a result, the right tooth flanks of the workpiece/tool pair 6, 2 come into contact. The meaning is that the right tooth flank R of the workpiece 2 drives the right tooth flank R of the tool 6. The brake or flywheel 104 is activated. A backlash exists on the opposite tooth surface of the corresponding tooth, for example, backlash A exists on the right tooth surface of the guide gear.

FIG. 23b) Clutch 103 is closed. The axial spacing between the workpiece spindle 1 and the tool spindle 5 is slightly increased, so that deviations in roundness or pitch deviations of the workpiece do not have a detrimental effect (if such deviations exist, the workpiece will not be in the condition shown in FIG. 23a). The workpiece accidentally engages the tool at the minimum radius, and after half a revolution of the workpiece, a jam occurs when the workpiece engages the tool at the maximum radius). The aforementioned tooth polishing increases to B.

FIG. 23c) The drive is driven in the "positive" direction of rotation at the normal working speed. As a result, the left tooth surfaces of the guide gears 3 and 7 come into contact. (This relationship changes slightly if the circular rotation error is large). A brake 102 of the work spindle serves for constant contact of the guide gear tooth flanks.

Fig. 23d) The shaft spacing is reduced (introduction of plunge feed). The backlash of the guide gear decreases to C. The workpiece is cut by D. A predetermined - often short - time passes with this minimum axis spacing "0". They are then spaced apart to the axis spacing shown in Figure 23a. At this time, a bump between the tooth flanks on the right side of the tool/work pair occurs in proportion to the amount of material cut. The drive is stopped. A brake 102 acts on the work spindle so that the tooth surface contact remains unchanged.

FIG. 23e) After the tool spindle and workpiece spindle have stopped, the clutch 103 is released. The drive is gradually rotated in the "negative" direction of rotation. This results in a situation opposite to that shown in FIG. 23a.

Figures 23f to 23h) The next process is 23b.
The procedure shown in FIGS. 23-23d is carried out for the opposite tooth surface.

It is more effective if a controllable residual torque is maintained when the clutch 103 is released. In this way, the guide gear "slips" at the highest point of the round rotation deviation or pitch deviation. As a result, the workpiece gear is machined with a slight contact pressure.

The tool is engaged with the dressing wheel in a procedure corresponding to that of FIGS. 23a to 23h. At this time, a dressing wheel is clamped into the device instead of the workpiece. In this case, the important difference is that FIGS. 23a and 23e
In the procedure shown in the figure, with the clutch open, the tooth flanks are only in contact at a shorter axial spacing than in the procedure for gear machining.

The device according to the invention allows the method to be carried out without a switchable clutch and without a brake or flywheel 104.
It is also possible to implement without it. However, in this case, the effect is somewhat lower than that of the above-mentioned method.

24 to 26 show diagrams of the processing procedure shown in FIGS. 23a to 23h, and the abbreviations used are as follows.

L = Maximum axial spacing between the tool spindle 5 and work spindle 1, M = axial spacing "zero" in the machining procedure shown in Figures 23a, 23e, and 23f, O = minimum axial spacing or axial spacing "zero"", F = clutch 103 open, G = clutch 103 closed, H = brake 102 connected, I = brake 102 disconnected, J = brake 104 connected, K = brake 104 disconnected, n ₁ = rotation direction "positive" Maximum number of rotations, n ₂ = maximum number of rotations in the "negative" direction of rotation, t ₁ , t ₂ = time Instead of the brake 104, a flywheel may be used.

Thick solid lines indicate the function of each member. Dashed lines indicate the beginning of each function.

FIGS. 23-26 are just one example. Needless to say, these functions are changed depending on the specific processing conditions. In particular, when machining the right and left tooth flanks in various ways, the number of revolutions, the time and the axial spacing can also be varied as the case may be. The same can be said about retouching. According to the invention, when determining the final functionality of the device,
Actual experience of driving experiments can be considered.
For example, in FIG. 26, the axis spacing change does not have to be linear. Furthermore, the final axial spacing may vary.

FIG. 27 is a cross-sectional view of the guide gears 3 and 7 that mesh with each other.

The tooth flanks are provided with coatings 201, 202, the material of which is different from that of the bodies 203, 204. If wear resistance is desired on the tooth surface, it can be coated with titanium nitride (TiN) or provided with a hard chromium layer or other suitable coating. When good sliding properties are desired,
It is coated with a suitable material, for example plastic. Furthermore, it is also possible to coat the material with a material that is wear-resistant and at the same time has good sliding properties.

In the embodiment of FIG. 28, the meshing of the two guide gears 3, 7 is protected by a protection device from dirt, such as machining chips or spray fluids. A housing 301 is provided for this purpose, in which the guide gears 3, 7 are accommodated. The housing is designed in such a way that the guide gear can be easily replaced. For example, the casing is formed in the shape of a shell with a dividing surface in a plane passing through the tool spindle and the workpiece spindle. The recesses for the work spindle and the tool spindle 5 are covered by spray shield plates 302, 303, which are fixed to the spindles. Alternatively, the casing on the side facing away from the workpiece 2 may be provided with a seal, as indicated schematically by 304 in FIG. On the side facing away from the tool 6, a recess is provided in the casing for a tool spindle.

Without a housing, only one or two spray shields 305 can be fixed to the workpiece spindle 1 or, if appropriate, also to the tool spindle 5, as shown in FIG. 29.

[Brief explanation of drawings]

Fig. 1 is a schematic diagram of the basic form of the machine of the present invention;
The figure is a partially enlarged view showing the meshing of both guide gears.
The figure is a partially enlarged view showing the engagement between the workpiece and the tool.
4 is a schematic representation of one embodiment of the tool spindle; FIG. 5 is a partially enlarged detail view of the tool spindle shown in FIG. 4; FIG. 6 is a schematic representation of another embodiment of the tool spindle; 6 is a sectional view along the line -, FIG. 8 is a schematic representation of the electromagnetic drive for adjusting the movement of the tool gear relative to the guide gear, and FIG. 9 is a further sectional view of the tool spindle. FIG. 10 is a schematic diagram of the cross-meshing clutch used in the embodiment, FIG. 11 is a perspective view showing the cross plate of the cross-meshing clutch shown in FIG. 10, and FIG. 13 is a cross-sectional view showing an elastic gear, FIG. 13 is an end view seen from the direction of arrow A in FIG. 12, FIG. 14 is a diagram showing a processing procedure for a tool gear, and FIG. 15 is an embodiment of the present invention. FIG. 16 is a schematic diagram showing a combination of the tool gear, both guide gears, motor, clutch, and brake or flywheel; FIG. 16 is a schematic diagram showing another combination similar to FIG. 15; FIG. FIG. 18 is a schematic diagram showing yet another similar combination; FIG. 18 is a schematic diagram showing still another combination similar to FIG. 15; FIG. 19 is a schematic diagram showing another combination similar to FIG. 20 is a schematic representation of an embodiment with a motor on the tool spindle; FIG. 21 is a diagrammatic representation of an embodiment with a clutch 103 on the tool spindle; FIG. 22 is a diagram of an embodiment with a motor on the tool spindle; Schematic representation of an embodiment with clutch and brake or flywheel, No. 23
The figures show the processing procedure, Figures 23a and 23b.
Fig. 23c, Fig. 23d, Fig. 23e, Fig. 2
Figures 3f, 23g, and 23h are diagrams showing each step of the processing procedure, Figures 24, 25, and 26 are diagrams showing the operating diaphragm of the embodiment of the present invention, and Figure 27 is the diagram showing the working diaphragm of the embodiment of the present invention. FIG. 28 is a schematic illustration of another embodiment of the machine according to the invention, and FIG. 29 is a schematic illustration of a further embodiment of the invention. 1... Work spindle, 2... Work gear,
3... Guide gear, 4... Tightening device, 5... Tool spindle, 6... Tool, 7... Guide gear, 8...
Common perpendicular line, 9... Hyperboloid curve, 10...
Tool spindle head, 11... Receptor, 12...
...Tightening nut, 13...Tightening device, 14...Spring, 15...Feeding mechanism, 16...Base, 17...
strip, 18... groove, 19... key, 20... groove,
21...Switching ring, 22...Thrust bearing, 2
3...Switching fork, 24...Piston, 25...
... Cylinder, 26, 27 ... Chamber, 28 ... Control device, 29, 30 ... Conduit, 31 ... Tool spindle, 31a ... Shaft, 32 ... Machine frame, 33, 33a
... Cylinder, 34 ... Rotating piston, 35 ...
Internal shape, 36, 37... chamber, 38, 39... hole, 4
0... Pin part, 41... Supply bush, 42, 4
3... Conduit, 44... Control device, 45... Lever, 46... Mover, 47, 48... Electromagnet, 4
9... Slip spring mechanism, 51... Tool carriage, 52... Slider guide mechanism, 53... Auxiliary carriage, 54... Electric motor, 55... Worm electric device, 56... Feed spindle, 57... Feed. Nut, 58... Tool spindle, 59... Guide gear spindle, 60... Rotating piston mechanism, 61...
...Torsion bar spring, 62...part, 63...circular guide, 64,65...clutch half, 66,67...
... Groove, 68 ... Cross plate, 69, 70 ... Fitting strip, 71 ... Guide gear, 72, 73 ... Half part, 7
4...Positioning boss, 75...Butsuyu, 76...
...Natsuto, 77...Cross mesh clutch, 80...
Tool tooth, 81... Work tooth groove, 85... Drive motor, 86... Switching clutch, 87... Motor, 8
8...Motor, 89...Flake or flywheel,
90, 91...Clutch, 92...Motor, 9
3,94...Friction wheel, 101...Motor, 102
...Brake, 103...Clutch, 104...
Brake or flywheel, 201, 202... layer,
203, 204... Main body, 301... Casing, 302, 303, 305... Spray liquid prevention plate, 304... Packing.

Claims (1)

[Scope of Claims] 1. A machine for manufacturing or processing teeth of a straight gear or a helical gear using a toothed tool having a hyperboloid, globoid or similar shape, the machine comprising: a tooth surface of the toothed tool; The teeth of the toothed tool mesh with the teeth of the workpiece from one end face of the tooth to the other end face of the workpiece, and the axes of the workpiece and the toothed tool intersect. (a) The toothed tool 6 and the workpiece 2 are each connected substantially coaxially to one guide wheel 3, 7; 93, 94, and these two guide wheels are in contact with each other. and has the same transmission ratio as that between the workpiece 2 and the tool 6, and (b) ensures that only the right flank or the left flank of the tool tooth, respectively, comes into contact with the workpiece tooth during one machining process. A machine for producing or processing gears. 2. A reversible motor 101 is connected to the tool spindle 5 or the workpiece spindle 1,
Machine according to claim 1, characterized in that the spindle (5 or 1) not connected to the motor (101) is provided with a brake (102). 3. The machine according to claim 1, further comprising a control device for changing the relative positions of the toothed surfaces of the toothed tool 6 and the workpiece 2. 4. The machine according to claim 3, which is provided with a switching device capable of switching the contact of the teeth of the toothed tool 6 meshing with the teeth of the workpiece 2 from the right tooth surface to the left tooth surface or vice versa. . 5. The machine according to claim 3, further comprising a feed control device that can change the relative positions of the tooth surfaces of the toothed tool 6 and the workpiece 2 in the tooth height direction. 6 Control devices 15, 34, 6 capable of changing the contact pressure between the tooth surface to be machined and the tooth surface to be machined
1. The machine according to claim 1 or 2, wherein: 7. A V-belt transmission 15 or similar is provided between the tool or workpiece or the part connected thereto and the guide wheel 3 or 7 or the part connected thereto, and this V-belt transmission Machine according to claim 4 or claim 6, which is capable and controllable. 8 Drive and control by electromagnetic devices 46 to 50 between at least one of the tool and the workpiece or a part connected thereto and one of the guide wheels 3 or 7 or a part connected thereto. 8. A machine according to claim 4 or claim 7, wherein an adjustable member 45 is provided. 9 A pneumatic or hydraulic device 40 to
Claim 4: Adjustable members 34, 35 driven and controlled by 44 are provided.
The machine described in paragraph 6 or paragraph 6. 10 Claim 6 provides that a spring is provided between at least one of the tool and the workpiece, or a portion coupled thereto, and one of the guide wheels 3 or 7, or a portion coupled thereto. machine. 11. The machine according to claim 1 or 2, wherein both guide cars are replacement cars. 12. The machine according to claim 1 or 2, wherein the guide wheel pair is combined with the exchange wheel pair. 13 The spindle 5 or 1 connected to the motor 101 has a switchable clutch 1 between the guide wheels 7, 3 and the tool 6 or workpiece 2.
The machine according to claim 2, comprising: 03. 14. Machine according to claim 2 or 13, in which the spindle 5, 1 connected to the motor 101 is provided with an additional brake 104 or flywheel. 15 At least on the working surface of at least one guide wheel, a material 20 different from the material of the guide wheel body.
1,202 is covered by claim 1
The machine described in paragraph 2 or paragraph 2. 16 The engagement of both guide wheels 3 and 7 is caused by the protection device 301~
3. A machine as claimed in claim 1 or 2, protected from dirt by 305. 17. A machine according to claim 1 or 2, in which the guide wheels consist of friction wheels 93 in contact with each other. 18. The machine according to claim 1 or 2, wherein both guide wheels are comprised of guide gears meshing with each other. 19. The machine according to claim 18, wherein both guide gears 7, 3 mesh with each other with backlash. 20. Machine according to claim 18, in which both guide gears 3, 7 have a pitch different from the teeth of the tool. 21 In a method of manufacturing or processing the teeth of a straight gear or helical gear using a toothed tool having a hyperboloid, globoid, or similar shape, the workpiece and the tool have an intersecting angle between their axes, (a) A step of bringing the tool and workpiece close to the axis distance corresponding to the start of machining and meshing the teeth of the toothed tool 6 and the tooth of the workpiece with each other with consistency; (b) a step of rotating the workpiece and the toothed tool; (c) A step of relatively moving the toothed tool 6 and the workpiece 2 until one tooth surface of the tool tooth comes into contact with the corresponding tooth surface of the workpiece; (d) A step in which the other tooth surface of the tool tooth contacts the corresponding tooth surface of the workpiece. A gear characterized by comprising a step of relatively moving the toothed tool 6 and the workpiece 2 until they come into contact with corresponding tooth surfaces, and (e) a step of disengaging the tool and the workpiece from meshing and stopping them. A method for manufacturing or processing. 22. The method according to claim 21, wherein during one contact of a tooth flank of a toothed tool, at least one radial feed is carried out on the same tooth flank. 23 Claim 2 which switches the rotational direction of the workpiece and the toothed tool in order to replace the contacting tooth surfaces
The method described in Section 1. 24. The method according to claim 21, wherein the contacting tooth surfaces are replaced by changing the relative speed without changing the direction of rotation.