US3473267A

US3473267A - Gear-generating machine

Info

Publication number: US3473267A
Application number: US628877A
Authority: US
Inventors: Joseph F Cooper
Original assignee: Kollsman Instrument Corp
Current assignee: Kollsman Instrument Corp
Priority date: 1962-12-13
Filing date: 1967-04-06
Publication date: 1969-10-21
Anticipated expiration: 1986-10-21
Also published as: DE1527115A1

Description

Oct. 21, 1969 J, F. coo ER 3,473,267

GEAR-GENERATING MACHINE Filed April 6, 1967 2 Sheets-Sheet l I.\"VE. JTOR. JOSf/ H F 500F527 as-neui vk, 5 756:, 62:65 JZF/zw ATTUe/VEYS Oct. 21, 1969 J. F. COQPER 3,473,267

GEAR-GENERATING MACHINE Filed April 6, 1967 2 Sheets-Sheet 2 7/5 TU/V [IA 77701 United States Patent 3,473,267 GEAR-GENERATING MACHINE Joseph F. Cooper, Franklin Square, N.Y., assignor to Kollsman Instrument Corporation, Elmhurst, Queens, N.Y., a corporation of New York Continuation-impart of application Ser. No. 244,394, Dec. 3, 1962. This application Apr. 6, 1967, Ser. No. 628,377

Int. Cl. B241) 5/00, 1/00; B23p 1/00 US. Cl. 5152 2 Claims ABSTRACT OF THE DISCLOSURE This application is a continuation-in-part of my copending application Ser. No. 244,394, filed Dec. 13, 1962, now abandoned, entitled Gear Generating Machine, and assigned to the assignee of the present invention.

My invention relates to a novel arrangement for generating a gear-tooth profile in a gear blank, and more specifically relates to a novel machine for gear-tooth profile generation which uses principles taken directly from the involutometry of the spur gear.

In accordance with the novel invention, a tooth space is generated by a cylindrical grinding element which rotates about its axis which axis is parallel to the axis of a rotating gear blank when generating a spur gear. The cutting cylinder of the novel invention is made to address the work tangentially along a path coincident with the line of action of the gear which is ultimately formed. As the gear blank rotates, and the grinding element translates, the relationship between the movement of the grinding element and gear blank is that of the involute tracing point moving along the line of action as the base circle rotates. Thus, the path described through the gear blank by the grinding element is the involute to the base circle of the gear being generated.

Where desired, and in order to assist in the actual metal removal without placing an undue burden on the grinding element which would normally be a very thin grinding wire, the method is preferably adapted to use electrolytic grinding techniques wherein the grinding takes place in the environment of an electrolyte with an electrical current being conducted between the grinding element and the gear blank. In this process, the grinding element will remove approximately of the metal by physical contact while the remaining 90% of the metal is removed by electrical erosion. Thus, the grinding element (and the tooth surface) carry only a fraction of the loads which would ordinarily be imposed under conventional grinding conditions.

The normal grinding technique described above will have very little effect on the surface and sub-surface crystalline structure of the tooth, and it has been found that cold working of the surface will be at an absolute minimum. Moreover, burrs will be reduced to a minimum because of the nature of electrolytic removal techniques which all but eliminates the need for brushing or other means for removing burrs. Thus, the tooth form will not be altered by deburring.

Patented Oct. 21, 1969 Moreover, the electrolytic process permits grinding of non-ferrous metals such as aluminum or copper based alloys in addition to the steels. Furthermore, the surface finish produced by the novel grinding process will be extremely fine.

Where there are grind marks in this high finish, such marks will be parallel to the normal plane instead of transverse to the normal plane of the tooth, as in the case of conventional gear grinding, bobbing, and shaping, which will significantly improve the surface frictional characteristics of the gear and consequently the reliability of the gearing of which it will be a part.

While the novel machine of the invention is generally applicable to the formation of any gear tooth, it is particularly useful in that part of the fine pitch gearing range which would be of the order of DP to DP.

A typical grinding element for this type of gear will be a nickel-plated tungsten wire having a diameter of 0.002 inch which serves as a matrix which receives a very fine grit diamond abrasive. The wire is then tautly mounted between two spindles which are spaced about A3 of an inch from one another, and the spindles rotate the wire at high speed. By way of example, the spindles can rotate at 20,000 rpm.

The optimum feed and speed values will, of course, be a function of material being ground as Well as the electrical characteristics of the system when the electrolytic removal techniques are used.

An accurate indexing device and stepping mechanism which would be apparent to those skilled in the art, will then provide the required movement of the grinding element and work piece. In operation, a single pass of the tool will produce one complete tooth profile (one side). Two passes may be required in order to make a space with the proper profile spacing (two adjacent profiles) depending upon the relationship between the diameter of the grinding wire and the required profile spacing. The device will be provided with means for indexing the gear blank through the required angular increment which will permit generation of the adjacent or exit profile at the required index location with respect to the first or entrant profile.

It has been found that in using the novel machine, a single tooth space in a 180 DP gear will be produced in approximately six seconds. Thus, a 180 DP gear having 220 teeth will be completely ground in 22 minutes and will be virtually burr free.

In order to increase production, it is possible to stack several blanks such as 3 or 4 blanks so that they will be ground together, the limitation on the number of blanks being determined by the mechanical characteristics of the grinding wire and the thickness of the blanks.

It will be obvious to those skilled in the art that the system can be fully automated to provide step-by-step grinding of succeeding teeth where the automation will not aifect the accuracy of grinding of the teeth. Moreover, it is apparent that any desired variation in tooth form can be generated by merely changing the program or relationship between the speed of rotation of the gear blank and speed of traverse of the cutting tool. Indeed, any number of curves and variations thereof may be produced by appropriate programming.

Accordingly, a primary object of this invention is to provide a novel machine for accurately forming a gear tooth profile.

Another object of this invention is to provide a high speed machine for grinding gear teeth to a high order of accuracy and surface finish.

Still another object of this invention is to grind gear tooth profiles in a gear blank by means of a rotating elongated grinding element which moves with respect to a rotating gear blank and moves along the line of action of the gear to be cut.

These and other objects of this invention will become apparent from the following description when taken in connection with the drawings, in which:

FIGURE 1 schematically illustrates the cutting equipment and controls for cutting a gear tooth in accordance with the present invention.

FIGURE 2 schematically illustrates a cylindrical grinding element in nine successive positions with respect to a rotating gear blank and illustrates the progressively formed tooth space.

FIGURE 3 is a perspective diagram illustrating one mechanism for moving the cylindrical grinding element with respect to the rotating gear blank.

FIGURE 4 is a perspective view of the guide block used in FIGURE 3.

Referring now to FIGURE 1, I have illustrated therein a gear blank (which could be several stacked gear blanks) which is carried by an appropriate clamping means 11 which is connected to a motor 12 which causes blank 10 to rotate about its axis of rotation.

A pair of

spindles

13 and 14 then carry a wire 15 which serves as the cylindrical grinding element and could, for example, be a nickel-plated tungsten wire having a diameter of 0.002 inch which is embedded with a fine grit diamond abrasive. The wire may have a length of approximately /8 of an inch between

spindles

13 and 14.

The

spindles

13 and 14 are connected to a motor 16 which causes the spindles to rotate wire 15 at high speed, the actual speed depending upon the nature of the material of blank 10.

An indexing means 17 which can be of any desired construction then controls the speed of motor 12 to determine the rate of rotation of blank 10 and also controls the rate at which a mechanism (to be described immediately below) which carries

spindles

13 and 14 will cause the spindles and thus wire 15 to traverse in a direction perpendicular to the plane of the drawing.

FIGURES 3 and 4 illustrate one mechanical embodiment for moving the cylindrical grinding element 15 with respect to the gear blank 10. Referring to FIGURES 3 and 4, the blank 10 is illustrated as carried on the fixed motor 12 while the cylindrical grinding element 15 and its

spindles

13 and 14 are rotatably carried at the end of spaced links and 31. The motor 16 is physically carried on link 31 and is directly connected to spindle 14 in order to cause rotation of the grinding element 15. The two links 30 and 31 are held in spaced relation to one another by a fixed rod 32 and a rotatable member 33 which is pivotally supported to the rear of links 30 and 31 as illustrated and has a central threaded opening. The central threaded opening of member 33 receives a drive screw 34 which extends from drive motor 35, whereupon rotation of screw 34 by motor 35 in onedirection or the other will cause member 33 to translate along the axis of screw 34, thereby to cause links 30 and 31 and thus grinding element 15 to move in a direction parallel to the axis of screw 34, with the axis of grinder 15 always perpendicular to the plane of blank 10. Note that motor 35 is a reversible motor, as will be described later.

A guide block 36, which is suitably stationarily mounted, has opposing

guide slots

37 and 38 on its opposing surfaces which receive guide fingers 39 and 40 which extends downwardly from links 30 and 31, respectively. The

guide slots

37 and 38 thus cause the accurate axial movement of links 30 and 31 over the range in which the spindle 15 is to engage the gear blank 10.

Once the grinding element 15 has completed its out and has progressed beyond the gear blank 10, the members 39 and 40 clear the end of

slots

37 and 38 and a lifting mechanism comprised of a piston 40 carried in cylinder 41 causes the links 30 and 31 to rotate upwardly, pivoting around rod 33 and the direction of rotation of motor 35 is reversed to cause the entire mechanism to retract. It will be noted that this lifting mechanism includes the

links

42 and 43 which are pivotally connected to one another and are connected to the piston 40, rod 32 respectively, where the connection between link 43 and rod 32 is a pivotal connection.

After the motor 35 has retracted links 30 and 31 and the guide members 39 and 40 have moved to the rear of guide block 36, a suitable piston control 44 permits the dropping of links 30 and 31 such that members 39 and 40 can enter into the rear of

slots

37 and 38, shown in FIGURE 4, with the motor 35 again reversing in direction so that a new tooth form can be cut in blank 10.

The manner in which the. grinding element will operate is best understood from FIGURE 2 which shows the grinding wire 15 in nine successive positions. Thus, in FIGURE 2, the grinding wire 15 (which is shown rotating counterclockwise, as indicated by the arrows) is caused to traverse in the direction indicated by arrows 20 thus undergoing movement in a relative translational straight line manner with respect to the axis of the gear blank such that the axis of the grinding element passes through the gear blank. The gear blank 10 which has an axis of rotation 21 18 caused to rotate in the direction shown by arrow 22.

Accordingly, as the grinding element 15 advances to the third position from the top, it enters the gear blank, as shown, with the axis of rotation of wire 15 falling in the plane of the line of action 23 of the gear to be cut, which is tangent to the base circle 24 of that gear.

As the gear blank continues to rotate and the cylindrical grinding element continues to translate, the tooth space is eventually formed, as illustrated, with a tooth space 25 wherein both profiles of the tooth space are mvolutes of the base circle 24.

In order to cut the next tooth, it is only necessary to reset the mechanism in a manner described above.

The system of the novel invention is particularly useful when the grinding is carried out in the atmosphere of an electrolyte with an electrical current being passed between the grinding element and the gear blank. By way of example, the ordinary coolant used in a grinding operation is replaced by a water solution of non-corrosive electrolytic salts, while an electrical power power supply is connected from the gear blank 10 to one of the spindles such as spindle 14 which is electrically connected to wire 15, while spindle 13 is insulated from this electrical circuit.

Although this invention has been described with respect to its preferred embodiments, it should be understood that many variations and modifications will now be obvious to those skilled in the art, and it is preferred, therefore, that the scope of the invention be limited not by the specific disclosure herein, but only by the appended claims.

The embodiments of the invention in which an exelusive privilege or property is claimed are defined as follows:

1. A gear-generating device comprising support means for carrying a gear blank, grinding means comprising an elongated cylindrical grinding means rotatable about is own axis at high speed, means for rotating said gear blank about the axis of said gear blank, means for translated the axis of rotation of said cylindrical grinding means along a plane tangent to the base circle of a gear to be generated from said gear blank, and means horizontally mounting both said grinding means and said gear blank; said plane of translation of said grinding means intersecting a portion of said gear blank; said gear blank being rotated simultaneously with translating of said cylindrical grinding means when said cylindrical grinding means grinds said blank.

2. A device for machining a predetermined tooth space profile in a gear comprising first positioning means for rotating an elongated wire-like grinding element about 8. central length-wise axis thereof;

second positioning means for rotating a gear blank in for controlling the gear tooth space profile cut by said a gear plane that intercepts the axis of said grinding grinding element. elements;

third positioning means for producing relative moveefer n s Cited mentfibetweeln said first second positioning means 5 UNITED STATES PATENTS to e ect re ative trans ationa stralg t me movement between the axis of said grinding element and fi i g 51 287 the axis of said gear blank such that the axis of the 1964233 6/1934 5 er 5 grinding element passes through said gear blank in 2129O31 9/1938 R 1C 1, X a plane that is tangent to a predetermined interior 1O 7855621 10/1958 gzi X circular locus of the gear blank during said relative translational straight line movement;

and indexing means operably interengaged between A said second and third positioning means for syn- LESTER M'SWINGLEPnmary Examiner chronizing rotational movement of said gear blank 15 US. Cl. X.R. with said relative translational straight line movement 51-287; 204-14 3,046,206 7/1962 Johnson et al 204-143