CA1064262A - Gear finishing - Google Patents
Gear finishingInfo
- Publication number
- CA1064262A CA1064262A CA316,729A CA316729A CA1064262A CA 1064262 A CA1064262 A CA 1064262A CA 316729 A CA316729 A CA 316729A CA 1064262 A CA1064262 A CA 1064262A
- Authority
- CA
- Canada
- Prior art keywords
- carrier
- tool
- axis
- gear
- support
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
Abstract
ABSTRACT
A gear finishing machine comprising a frame, a tool head on the frame, a work slide movable on the frame toward and away from the tool head, a rotary work gear support on the slide with its axis perpendicular to the direction of slide movement, and means for moving the rotary work gear support in back and forth traverse strokes on the slide in a plane perpendicular to the direction of slide movement.
The tool head comprises a fixed mounting member, a pivot support angularly adjustable on the mounting member about an axis parallel to the direction of slide movement. A
tool carrier is pivoted to said pivot support for pivotal movement about an axis perpendicular to the direction of slide movement, and has a rotary tool support thereon having an axis of rotation parallel to the pivot axis of said carrier.
The pivot axis of the carrier is located laterally from the axis of the rotary tool support. Means are provided for driving one of the rotary supports in rotation.
A gear finishing machine comprising a frame, a tool head on the frame, a work slide movable on the frame toward and away from the tool head, a rotary work gear support on the slide with its axis perpendicular to the direction of slide movement, and means for moving the rotary work gear support in back and forth traverse strokes on the slide in a plane perpendicular to the direction of slide movement.
The tool head comprises a fixed mounting member, a pivot support angularly adjustable on the mounting member about an axis parallel to the direction of slide movement. A
tool carrier is pivoted to said pivot support for pivotal movement about an axis perpendicular to the direction of slide movement, and has a rotary tool support thereon having an axis of rotation parallel to the pivot axis of said carrier.
The pivot axis of the carrier is located laterally from the axis of the rotary tool support. Means are provided for driving one of the rotary supports in rotation.
Description
~06426~
SPECIFICATION
The present invention relate~ to certain aspects of our earlier co-pending application Serial No. 257,077 which are not broadly claimed therein.
The present invention relates to a machine for shaving or honing work gears by rotating them in tight mesh with either a gear shaving tool or a gear honing tool.
A gear shaving tool is in the form of a gear con-jugate to the required form of a work gear, but with its teeth at a helix angle such that the work gear and tool mesh with their axes crossed in space, as for example at an angle of 3-30. It is made of tool steel, having serrations or grooves ~ ;
in its teeth, the corners of which constitute cutting or shav- -ing edges capable of removing chips or shavings from the gear teeth. In operation, the gear and shaving cutter are placed in tight mesh, and either the gear or tool is rotated, thereby driving the meshing member. In order to distribute the shaving action from end to end of the gear teeth, a relative traverse is provided between the gear and tool. This may be parallel :.; ~ .
to the axis of the gear or oblique or diagonal with respect thereto. The traverse strokes are back and forth, and between traverse strokes, an incremental feeding motion is made, in a direction parallel to a line perpendicular to and intersecting ~
the axes of both gear and tool. - '! ' ' A gear honing tool is also in the form of a gear conjugate to the required form of the work gear, but its teeth are formed of slightly resilient abrasive material. The gear ~ - .
,:, i-106~Z62 and honing tool are meshed in tight mesh at cros~ed axes, as in shaving, and either the gear or honing tool is driven in rotation. The gear and tool are relatively traversed as in shaving, but in this case the direction of relative traverse is parallel to the axis of the gear. Instead of providing - incremental feed, a relatively small yieldable pressure is applied in a direction having at least a substantial component radial of the gear so that as material is removed from the gear teeth, pressure is maintained.
In accordance with the present inventian, the machine comprises a frame, a tool head on the frame, a work slide movable on the frame toward and away from the tool head, a rotary work gear support on the slide with its axis per-pendicular to the direction of slide movement, and means for moving the rotary work gear support in back and forth traverse strokes on the slide in a plane perpendicular to the direction of slide movement. The tool head comprises a fixed mounting member, a pivot support angularly adjustable on the mounting member about an axis parallel to the direction of slide movement. A tool carrier is pivoted to said pivot support for pivotal movement about an axis perpendicular to the direction of slide movement, and has a rotary tool support thereon having an axis of rotation parallel to the pivot axis of said carrier. The pivot axis of the carrier is located laterally from the axis of the rotary tool support. Means are provided for driving one of the rotary supports in rotation.
1064~Z62 For a better understanding of the invention, one example of a combined gear shaving and honing machine embody-ing the invention will now be described with reference to the accompanying drawingQ in which:
Figure 1 is a side elevation of the tool head with parts broken away;
Figure 2 is a sectional view on the line 2-2, figure , Figure 3 is a fragmentary elevational view in the dire~tion of the arrows 3-3, figure 1;
Figure 4 is a sectional view on the line 4-4, figure 3;
Figure 5 is a fragmentary sectional view on the line 5-5, figure 1;
Figure 6 is a diagrammatic view illustrating the relationship of the tool head shown in the previous figures, with the remainder of a gear finishing machine.
Referring first to figure 6, the tool head in its entirety is illustrated at 10 and includes a tool carrier 12 pivotally mounted at 16 on an angularly adjustable pivot ~`
support 14. The support 14 is mounted for angular adjustment . ~ .
on a fixed base 18 which carries a slide 20 mounted for hori-zontal movement. The slide 20 carries a support 22 including , a rotary support or arbor for mounting a work gear W in mesh -1 with a gear-like tool T carried by the tool carrier 12. Means are provided for moving the slide 20 horizontally to the right , and left as seen in figure 6 to bring the work gear into and out of tight mesh with the tool.
_3_ 10642~Z
In addition, support 22 is mounted on ~lide 20 for slow back and forth traverse movement in a direction parallel to the axis of the gear W, by suitable mechani~m, which as usual in this art i9 screw mechanism, not illustrated.
The pivot support 14 is angularly adjustable on a fixed mounting member about a horizontal axis as will sub-sequently appear, so that the work gear W and tool T may be br~ught into mesh at crossed axes. One of the rotary supports is provided with means (not shown) for driving one of the meshed members in rotation. In addition, means are provided for effecting a relative traverse movement between the gear W and the tool T in a direction parallel to the rotation axis of the work gear W as well as for effecting meshing relation-ship and depth feed where required by movement of the slide 20 horizontally toward and away from the tool head 10.
This may comprise a traverse mechanism for traversing support 22 on slide 20 in a direction paralle' to the axis of gear W.
Referring now to Figures 1-5 the tool support structure comprises stationary mounting member in the form of a column 26 to which the pivot support 14 is mounted for angular adjustment by a cylindrical projectian 28 received in a tubular flanged portion 30 of the column 26. The pivot support 14 is retained in its angularly adjusted position by clamping heads 31 fixed to threaded studs 32 which in turn carry clamping nuts 34.
The pivot 16 connecting the pivoted tool carrier 12 to the pivot support 14 is preferably in the position best illustrated in Figure 1, where it ~111 be noted that it is displaced to the left from the vertical plane passing through the rotation axis of the tool T and is located well above the horizontal plane passing through the rotation axic of the tool T.
A gear shaving operation requires that the relative motions between a gear shaving cutter and a work gear in mesh therewith shall consist of meshed rotation in crossed axes relationship, and a relative traverse between the gear and tool in a plane which is parallel to the axes of both the gear and shaving cutter. The specific direction of traverse may be parallel to the axis of the gear or it may be diagonal or oblique with respect thereto. During each traverse stroke, the radial spacing between the gear and tool axes is maintained -.
by blocking carrier 12 against pivotal movement. In addition, a depth feed is provided between traverse strokes and of course ~ -:, .
a reverse feed or withdrawing motion is provided following termination of the shaving cycle. ~ -On the contrary, a gear honing operation is one in which the gear is rotated under relatively light pressure con- -ditions but in full mesh with an abrasive gear-like honing , tool. Light pressure is maintained between the gear and hone throughout the operation and relative back and forth traverse is provided in a direction parallel to the axis of the gear G.
In order to maintain constant light pressure contact between the teeth of the gear and hone, it is necessary for the hone to float and this condition is met by pivotally mounting the tool carrier 12 which carries the honing tool.
The tool carrier 12 as illustrated in Figure 1, is connected through a pivot link 36 connected internally of a cylinder 38 to a piston (not shown), the link extending beyond the cylinder and carrying an adjusting nut 40 constituting a spring stop for a counterbalance spring 42 which counterbalances the weight of the tool carrier 12. Air pressure i~ supplied to the cylinder, an air connection thereto being indicated at 44.
With this arrangement a relatively light clockwise bias may be applied to the pivoted carrier 12 to maintain a predetermined pressure contact between the teeth of a tool, diagrammatically indicated at T, and a work gear in mesh therewith, a portion ~ .
of which is indicated diagrammatically at W. ~, n order to ensure suitable lateral control of the motion of the tool carrier 12, it is provided with a tongue 50 having flat sides in contact with corresponding flat sides of wear plates 52, the position of each of which is adjusted by a plurality of adjusting screws 54. The screws 54 are adjusted ;~
to remove all play but to permit free sliding movement of the ~`
tongue 50 so that its movement about the axis of the pivot 16 is freely permitted.
Since under other conditions, such as gear shaving, it is desired to eliminate pivotal or rocking movement of the tool carrier 12, means are provided for locking the tool car- ~ -rier 12 in a fixed position and this means comprises screws -56 extending through enlarged openings or slots 5~ and having threaded engagement at their lower ends as indicated at 60.
10642~Z
In addition, slotted blocks or plates 62 are provided, pivoted as indicated at 64 and having laterally extending arcuate slots 66 to receive the screws 56. When the block~ 62 are in the position illustrated in Figure 4 and the screws 56 are tightened down, it will of course be apparent that the tool carrier 12 is firmly locked against movement about the axis of the pivot 16. On the other hand, when the ~crews are loosened and the blocks 62 swung into clearance positions, the tool carrier 12 is freely movable.
In addition to the blocking of the tool carrier 12 against movement about the axis of its pivot 16, preferably additional clamping means are provided which take the form of a pair of clamping levers 70 pivoted as indicated at 72 to a bracket 73 connected to the support 14 and having abutment extensions 74 adapted to engage opposite sides of a rigidly fixed abutment plate 76 carried by pivoted carrier 12. One of ; the levers 70 carries an air cylinder 78 having a piston therein connected to an adjustable abutment screw 80 engageable with the end of the other lever 70, in a relationship best illustrated in Figure 5. When pressure is applied to the piston within the ~~
cylinder 78, the upper ends of the lever 70 are forced apart and the forces exerted by the extensions 74 are thus equalized on opposite sides of the plate 76, thus additionally supporting the tool carrier 12 in fixed position during the gear shaving operation.
Referring now to Figure 2, details of the connection between the support 14 and the tool carrier 12 are illustrated.
, . ... . . .
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As seen in thiC Figure, the pivot 16 is shown as comprising a pin 82 fixed in the tool carrier 12 and preferably journaled at its ends as indicated at 84 in ears 86 on the support 14.
Means for suitably rotatably mounting a tool T is provided in the tool carrier 12 and takes the form of bearings 88 supporting a shaft 90 for rotation about an axis indicated at 91.
Inasmuch as the particular tool head illustrated herein is designed for supporting relatively large tools, - 10 special means are provided for effecting limited angular move-ment of a tool T so as to bring the teeth thereof into proper alignment with the teeth of a work gear. This means comprises a bevel gear 92 fixed to the shaft 90 and a bevel gear 94 fixed to a vertically movable shaft 96 in housing 97 normally retained in clearance relation as illustrated in Figure 2 with respect to the gear 92 by a compression spring 98. A pivot cam 100 is pivoted as indicated at 102 between ears 104 and an operating shaft 106 is slidably movable through an opening 108 provided in an upward extension 110 on the cam 100. The shaft 106 has . 20 an operating knob 112 by means of which the operator may move ~: the knob to the right as illustrated in Figure 2 and thereafter, swing it upwardly to depress the nose of the cam and thereby depress shaft 96 to bring about meshing engagement between the bevel gears 92 and 94. Thereafter, limited rotational movement of the shaft 106 in a hori~ontal plane results in rotation of the shaft 96 and corresponding rotation of the tool support shaft 90.
Referring now again to the location of the pivot indicated generally at 16 in Figure 1 and constituted by the pin 82, it has been found that the precise location of this shaft controls the action resulting from rotation of the gear and a honing tool in mesh. At this time, as previously noted, the tool carrier 12 is mounted for pivotal movement about the axis of pivot 82 forming the pivot support 16 and is urged into pressure engagement with the work gear only by a relatively ~light air pressure applied to the cylinder 38. In practice ~-the total force exerted between the gear and honing tool may be only a few pounds.
In the past it was believed desirable to provide for pivot mounting of the tool carrier which provided for approach and separation between the gear and tool in a position r such that the relative approach took place substantially in a direction parallel to the line joining and perpendicular to the axes of the gear and tool. This corresponded to the direction of movement where the approach and separation was accomplished, not by means of a pivot mounting, but by means of a suitable slide. However, it is much preferred to provide for the re-quired relative movement by means of a pivot mounting.
It was found that when the honing operation was carried out by rotating either the gear or hone in one direction under a given predetermined relatively light radial loading, a smooth hon~ng action took place. However, when the direction or rotation was reversed, the smooth honing action did not take place and it appeared that the difference was attributable to a variation in the sum ofthe forces tending to pivot the pivoted carrier to apply pressure between the tool and gear.
:
' ~
It appears that advantages are obtained by locating the pivot mounting for the pivoted carrier within the acute angle between the lines of action and as close as is reasonably possible to the line perpendicular to the line of centers pa~s-ing through the pitch point.
This i8 the subject matter of prior application Serial No. 257,077, and i9 not claimed herein. The only re-quirement of the structure disclosed herein is that pivot movement of carrier 12 results in movement of the tool in a direction whose major component is parallel to the direction of movement of slide 20.
Referring again to the specific machine design . ~
illustrated in Figure 1, it will be ob~erved that the axis i-of pivot support 16 is located substantially within the acute angle between lineæ of action 124 and 126, and could be located ~ -on the bi~ector of this angle, if found to be neces~ary. ~ -In the actual machine illustratea the pivot mounting ~-for the pivoted carrier 12 is located above its axis, at a position such that pivotal movement of the carrier moves the tool in a direction having a major component radial of the gear. However, ~o far as the principles of the invention are concerned, the pivot mounting 16 might be mounted generally below the pivoted carrier. As a matter of fact, the principles of the present invention would apply if the swinging movement of the pivoted member took place in a horizontally di~posed plane or an oblique plane.
.:
~,, -; : , ~,
SPECIFICATION
The present invention relate~ to certain aspects of our earlier co-pending application Serial No. 257,077 which are not broadly claimed therein.
The present invention relates to a machine for shaving or honing work gears by rotating them in tight mesh with either a gear shaving tool or a gear honing tool.
A gear shaving tool is in the form of a gear con-jugate to the required form of a work gear, but with its teeth at a helix angle such that the work gear and tool mesh with their axes crossed in space, as for example at an angle of 3-30. It is made of tool steel, having serrations or grooves ~ ;
in its teeth, the corners of which constitute cutting or shav- -ing edges capable of removing chips or shavings from the gear teeth. In operation, the gear and shaving cutter are placed in tight mesh, and either the gear or tool is rotated, thereby driving the meshing member. In order to distribute the shaving action from end to end of the gear teeth, a relative traverse is provided between the gear and tool. This may be parallel :.; ~ .
to the axis of the gear or oblique or diagonal with respect thereto. The traverse strokes are back and forth, and between traverse strokes, an incremental feeding motion is made, in a direction parallel to a line perpendicular to and intersecting ~
the axes of both gear and tool. - '! ' ' A gear honing tool is also in the form of a gear conjugate to the required form of the work gear, but its teeth are formed of slightly resilient abrasive material. The gear ~ - .
,:, i-106~Z62 and honing tool are meshed in tight mesh at cros~ed axes, as in shaving, and either the gear or honing tool is driven in rotation. The gear and tool are relatively traversed as in shaving, but in this case the direction of relative traverse is parallel to the axis of the gear. Instead of providing - incremental feed, a relatively small yieldable pressure is applied in a direction having at least a substantial component radial of the gear so that as material is removed from the gear teeth, pressure is maintained.
In accordance with the present inventian, the machine comprises a frame, a tool head on the frame, a work slide movable on the frame toward and away from the tool head, a rotary work gear support on the slide with its axis per-pendicular to the direction of slide movement, and means for moving the rotary work gear support in back and forth traverse strokes on the slide in a plane perpendicular to the direction of slide movement. The tool head comprises a fixed mounting member, a pivot support angularly adjustable on the mounting member about an axis parallel to the direction of slide movement. A tool carrier is pivoted to said pivot support for pivotal movement about an axis perpendicular to the direction of slide movement, and has a rotary tool support thereon having an axis of rotation parallel to the pivot axis of said carrier. The pivot axis of the carrier is located laterally from the axis of the rotary tool support. Means are provided for driving one of the rotary supports in rotation.
1064~Z62 For a better understanding of the invention, one example of a combined gear shaving and honing machine embody-ing the invention will now be described with reference to the accompanying drawingQ in which:
Figure 1 is a side elevation of the tool head with parts broken away;
Figure 2 is a sectional view on the line 2-2, figure , Figure 3 is a fragmentary elevational view in the dire~tion of the arrows 3-3, figure 1;
Figure 4 is a sectional view on the line 4-4, figure 3;
Figure 5 is a fragmentary sectional view on the line 5-5, figure 1;
Figure 6 is a diagrammatic view illustrating the relationship of the tool head shown in the previous figures, with the remainder of a gear finishing machine.
Referring first to figure 6, the tool head in its entirety is illustrated at 10 and includes a tool carrier 12 pivotally mounted at 16 on an angularly adjustable pivot ~`
support 14. The support 14 is mounted for angular adjustment . ~ .
on a fixed base 18 which carries a slide 20 mounted for hori-zontal movement. The slide 20 carries a support 22 including , a rotary support or arbor for mounting a work gear W in mesh -1 with a gear-like tool T carried by the tool carrier 12. Means are provided for moving the slide 20 horizontally to the right , and left as seen in figure 6 to bring the work gear into and out of tight mesh with the tool.
_3_ 10642~Z
In addition, support 22 is mounted on ~lide 20 for slow back and forth traverse movement in a direction parallel to the axis of the gear W, by suitable mechani~m, which as usual in this art i9 screw mechanism, not illustrated.
The pivot support 14 is angularly adjustable on a fixed mounting member about a horizontal axis as will sub-sequently appear, so that the work gear W and tool T may be br~ught into mesh at crossed axes. One of the rotary supports is provided with means (not shown) for driving one of the meshed members in rotation. In addition, means are provided for effecting a relative traverse movement between the gear W and the tool T in a direction parallel to the rotation axis of the work gear W as well as for effecting meshing relation-ship and depth feed where required by movement of the slide 20 horizontally toward and away from the tool head 10.
This may comprise a traverse mechanism for traversing support 22 on slide 20 in a direction paralle' to the axis of gear W.
Referring now to Figures 1-5 the tool support structure comprises stationary mounting member in the form of a column 26 to which the pivot support 14 is mounted for angular adjustment by a cylindrical projectian 28 received in a tubular flanged portion 30 of the column 26. The pivot support 14 is retained in its angularly adjusted position by clamping heads 31 fixed to threaded studs 32 which in turn carry clamping nuts 34.
The pivot 16 connecting the pivoted tool carrier 12 to the pivot support 14 is preferably in the position best illustrated in Figure 1, where it ~111 be noted that it is displaced to the left from the vertical plane passing through the rotation axis of the tool T and is located well above the horizontal plane passing through the rotation axic of the tool T.
A gear shaving operation requires that the relative motions between a gear shaving cutter and a work gear in mesh therewith shall consist of meshed rotation in crossed axes relationship, and a relative traverse between the gear and tool in a plane which is parallel to the axes of both the gear and shaving cutter. The specific direction of traverse may be parallel to the axis of the gear or it may be diagonal or oblique with respect thereto. During each traverse stroke, the radial spacing between the gear and tool axes is maintained -.
by blocking carrier 12 against pivotal movement. In addition, a depth feed is provided between traverse strokes and of course ~ -:, .
a reverse feed or withdrawing motion is provided following termination of the shaving cycle. ~ -On the contrary, a gear honing operation is one in which the gear is rotated under relatively light pressure con- -ditions but in full mesh with an abrasive gear-like honing , tool. Light pressure is maintained between the gear and hone throughout the operation and relative back and forth traverse is provided in a direction parallel to the axis of the gear G.
In order to maintain constant light pressure contact between the teeth of the gear and hone, it is necessary for the hone to float and this condition is met by pivotally mounting the tool carrier 12 which carries the honing tool.
The tool carrier 12 as illustrated in Figure 1, is connected through a pivot link 36 connected internally of a cylinder 38 to a piston (not shown), the link extending beyond the cylinder and carrying an adjusting nut 40 constituting a spring stop for a counterbalance spring 42 which counterbalances the weight of the tool carrier 12. Air pressure i~ supplied to the cylinder, an air connection thereto being indicated at 44.
With this arrangement a relatively light clockwise bias may be applied to the pivoted carrier 12 to maintain a predetermined pressure contact between the teeth of a tool, diagrammatically indicated at T, and a work gear in mesh therewith, a portion ~ .
of which is indicated diagrammatically at W. ~, n order to ensure suitable lateral control of the motion of the tool carrier 12, it is provided with a tongue 50 having flat sides in contact with corresponding flat sides of wear plates 52, the position of each of which is adjusted by a plurality of adjusting screws 54. The screws 54 are adjusted ;~
to remove all play but to permit free sliding movement of the ~`
tongue 50 so that its movement about the axis of the pivot 16 is freely permitted.
Since under other conditions, such as gear shaving, it is desired to eliminate pivotal or rocking movement of the tool carrier 12, means are provided for locking the tool car- ~ -rier 12 in a fixed position and this means comprises screws -56 extending through enlarged openings or slots 5~ and having threaded engagement at their lower ends as indicated at 60.
10642~Z
In addition, slotted blocks or plates 62 are provided, pivoted as indicated at 64 and having laterally extending arcuate slots 66 to receive the screws 56. When the block~ 62 are in the position illustrated in Figure 4 and the screws 56 are tightened down, it will of course be apparent that the tool carrier 12 is firmly locked against movement about the axis of the pivot 16. On the other hand, when the ~crews are loosened and the blocks 62 swung into clearance positions, the tool carrier 12 is freely movable.
In addition to the blocking of the tool carrier 12 against movement about the axis of its pivot 16, preferably additional clamping means are provided which take the form of a pair of clamping levers 70 pivoted as indicated at 72 to a bracket 73 connected to the support 14 and having abutment extensions 74 adapted to engage opposite sides of a rigidly fixed abutment plate 76 carried by pivoted carrier 12. One of ; the levers 70 carries an air cylinder 78 having a piston therein connected to an adjustable abutment screw 80 engageable with the end of the other lever 70, in a relationship best illustrated in Figure 5. When pressure is applied to the piston within the ~~
cylinder 78, the upper ends of the lever 70 are forced apart and the forces exerted by the extensions 74 are thus equalized on opposite sides of the plate 76, thus additionally supporting the tool carrier 12 in fixed position during the gear shaving operation.
Referring now to Figure 2, details of the connection between the support 14 and the tool carrier 12 are illustrated.
, . ... . . .
.. .
As seen in thiC Figure, the pivot 16 is shown as comprising a pin 82 fixed in the tool carrier 12 and preferably journaled at its ends as indicated at 84 in ears 86 on the support 14.
Means for suitably rotatably mounting a tool T is provided in the tool carrier 12 and takes the form of bearings 88 supporting a shaft 90 for rotation about an axis indicated at 91.
Inasmuch as the particular tool head illustrated herein is designed for supporting relatively large tools, - 10 special means are provided for effecting limited angular move-ment of a tool T so as to bring the teeth thereof into proper alignment with the teeth of a work gear. This means comprises a bevel gear 92 fixed to the shaft 90 and a bevel gear 94 fixed to a vertically movable shaft 96 in housing 97 normally retained in clearance relation as illustrated in Figure 2 with respect to the gear 92 by a compression spring 98. A pivot cam 100 is pivoted as indicated at 102 between ears 104 and an operating shaft 106 is slidably movable through an opening 108 provided in an upward extension 110 on the cam 100. The shaft 106 has . 20 an operating knob 112 by means of which the operator may move ~: the knob to the right as illustrated in Figure 2 and thereafter, swing it upwardly to depress the nose of the cam and thereby depress shaft 96 to bring about meshing engagement between the bevel gears 92 and 94. Thereafter, limited rotational movement of the shaft 106 in a hori~ontal plane results in rotation of the shaft 96 and corresponding rotation of the tool support shaft 90.
Referring now again to the location of the pivot indicated generally at 16 in Figure 1 and constituted by the pin 82, it has been found that the precise location of this shaft controls the action resulting from rotation of the gear and a honing tool in mesh. At this time, as previously noted, the tool carrier 12 is mounted for pivotal movement about the axis of pivot 82 forming the pivot support 16 and is urged into pressure engagement with the work gear only by a relatively ~light air pressure applied to the cylinder 38. In practice ~-the total force exerted between the gear and honing tool may be only a few pounds.
In the past it was believed desirable to provide for pivot mounting of the tool carrier which provided for approach and separation between the gear and tool in a position r such that the relative approach took place substantially in a direction parallel to the line joining and perpendicular to the axes of the gear and tool. This corresponded to the direction of movement where the approach and separation was accomplished, not by means of a pivot mounting, but by means of a suitable slide. However, it is much preferred to provide for the re-quired relative movement by means of a pivot mounting.
It was found that when the honing operation was carried out by rotating either the gear or hone in one direction under a given predetermined relatively light radial loading, a smooth hon~ng action took place. However, when the direction or rotation was reversed, the smooth honing action did not take place and it appeared that the difference was attributable to a variation in the sum ofthe forces tending to pivot the pivoted carrier to apply pressure between the tool and gear.
:
' ~
It appears that advantages are obtained by locating the pivot mounting for the pivoted carrier within the acute angle between the lines of action and as close as is reasonably possible to the line perpendicular to the line of centers pa~s-ing through the pitch point.
This i8 the subject matter of prior application Serial No. 257,077, and i9 not claimed herein. The only re-quirement of the structure disclosed herein is that pivot movement of carrier 12 results in movement of the tool in a direction whose major component is parallel to the direction of movement of slide 20.
Referring again to the specific machine design . ~
illustrated in Figure 1, it will be ob~erved that the axis i-of pivot support 16 is located substantially within the acute angle between lineæ of action 124 and 126, and could be located ~ -on the bi~ector of this angle, if found to be neces~ary. ~ -In the actual machine illustratea the pivot mounting ~-for the pivoted carrier 12 is located above its axis, at a position such that pivotal movement of the carrier moves the tool in a direction having a major component radial of the gear. However, ~o far as the principles of the invention are concerned, the pivot mounting 16 might be mounted generally below the pivoted carrier. As a matter of fact, the principles of the present invention would apply if the swinging movement of the pivoted member took place in a horizontally di~posed plane or an oblique plane.
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Claims (10)
OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A gear finishing machine comprising a frame, a tool head mounted in a fixed position on said frame, a work slide movable on said frame toward and away from said tool head, a rotary work gear support on said slide for mounting a work gear for rotation with its axis perpendicular to the direction of movement of said slide, means for moving said rotary gear support in back and forth traverse strokes on said slide in a direction which occupies a plane perpendicular to the direction of slide movement, said tool head comprising a fixed mounting member, a pivot support angularly adjustable on said mounting member about an axis parallel to the direction of slide movement, a tool carrier pivoted to said pivot support for pivotal movement about an axis perpendicular to the direction of slide movement, a rotary tool support on said carrier having its axis of rotation parallel to the pivot axis of said carrier, whereby said rotary supports are operable to support a work gear and gear-like tool in tight mesh with their axes crossed in space, the pivot mounting of said carrier being located laterally from the axis of the rotary tool support to produce movement of a tool carried thereby in a direction having a major component radial of the work gear, and means for driving one of said rotary supports in rotation.
2. A machine as defined in claim 1 comprising selectively operable biasing means connected between said pivot support and said pivoted carrier to provide pressure contact between the teeth of the gear and tool when the machine is used for gear honing.
3. A machine as defined in claim 2, comprising guide bearing means acting between said pivot support and carrier to insure true pivotal movement of said carrier.
4. A machine as defined in claim 3, in which said guide bearing means is located substantially at the opposite side of the axis of rotation of the rotary tool support on said carrier from the pivot axis of said carrier.
5. A machine as defined in claim 2, comprising selectively operable guide means acting between said pivot support and said pivoted carrier, said guide a first member having a tongue slidable between contact surfaces provided on a second member, means for adjusting said contact surfaces to eliminate all lost motion between said tongue and surfaces.
6. A machine as defined in claim 5, said guide means comprising blocking means which comprise screws threaded into one of said members and extending through enlarged open-ings on the other of said members, plates having open ended slots pivoted to one of said members to be swung into position interposed between said members and receiving said screws to provide for locking said members together by tightening said screws.
7. A machine as defined in claim 1, comprising selectively operable blocking means acting between said pivot support and carrier to prevent pivotal movement of said carrier when the machine is used for gear shaving.
8. A machine as defined in claim 1, comprising a manual meshing device on said pivoted carrier to provide limited angular adjustment of a tool on the rotary tool support, comprising gearing including a gear shiftable between operating and idle positions, a spring urging said gear to idle position, and manually operated cam and actuating means to cam said gear into operating position and thereafter effecting limited rotation thereof.
9. In a gear finishing machine, a tool head comprising a fixed mounting member, a pivot support angularly adjustable on said mounting member about a first axis, a tool carrier pivoted to said pivot support for pivotal movement about a second axis perpendicular to said first axis, a rotary tool support on said carrier having its axis of rotation parallel to said second axis, said second axis being located laterally from the axis of the rotary tool support to produce movement of a tool carried thereby in a direction perpendicular to the axis of the tool.
10. A tool head as defined in claim 9, comprising selectively operable means for blocking said pivoted carrier against pivotal movement relative to said pivot support or releasing said carrier for free pivotal movement, and selectively operable means for biasing said carrier for pivotal movement when said blocking means releases said carrier.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA316,729A CA1064262A (en) | 1975-08-04 | 1978-11-23 | Gear finishing |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/601,915 US4050350A (en) | 1975-08-04 | 1975-08-04 | Gear finishing |
| CA257,077A CA1061117A (en) | 1975-08-04 | 1976-07-15 | Gear finishing |
| CA316,729A CA1064262A (en) | 1975-08-04 | 1978-11-23 | Gear finishing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1064262A true CA1064262A (en) | 1979-10-16 |
Family
ID=27164558
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA316,729A Expired CA1064262A (en) | 1975-08-04 | 1978-11-23 | Gear finishing |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1064262A (en) |
-
1978
- 1978-11-23 CA CA316,729A patent/CA1064262A/en not_active Expired
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