US2905320A

US2905320A - Gear gauging and sorting apparatus

Info

Publication number: US2905320A
Application number: US466005A
Authority: US
Inventors: Thomas S Gates
Original assignee: National Broach and Machine Co
Current assignee: Nachi Machining Technology Co
Priority date: 1954-11-01
Filing date: 1954-11-01
Publication date: 1959-09-22
Anticipated expiration: 1976-09-22

Description

Sept. 22, 1959 T. s. GATES GEAR GAUGING AND SORTING APPARATUS 4 Sheets-Sheet 1 Filed Nov. 1, 1954 INVENTOR.

THOMAS S. GATES ATTORNEYS Sept. 22, 1959 T. s. GATES GEAR GAUGING AND SORTING APPARATUS Filed Nov. 1 1954 4 Sheets-Sheet 2 INVENTOR.

THOMAS S. GATES ATTORNEYS T. S. GATES GEAR GAUGING AND SORTING APPARATUS Sept. 22, 1959 4 Sheets-Sheet 3 Filed Nov. 1 1954 INVENTOR.

THOMAS S. GATES ATTORNEYS Sept. 22, 1959 s, GATES 2,905,320

GEAR GAUGING AND SORTING APPARATUS Filed Nov. 1, 1954 4 Sheets-Sheet 4 INVENTOR.

THO MAS S. GATES ATTORNEYS GEAR GAUGING AND SORTING APPARATUS Thomas S. Gates, Grosse Pointe Woods, Mich., assignor to National Broach & Machine Company, Detroit, Mich, a corporation of Michigan Application November 1, 1954, Serial No. 466,005

12 Claims. (Cl. 209-88) The present invention relates to gear gauging apparatus.

It is an object of the present invention to provide apparatus adapted to perform a quick and accurate gear gauging operation on a series of gears and to separate the gauged gears into groups which may be classified as correct gears, salvageable gears, and scrap gears.

It is a further object of the present invention to provide Jgear gauging apparatus comprising a pair of relatively :movable master gears, means for preventing rotation of one of said master gears, and means for rotating the other of said master gears so as to roll a work gear between the master gears.

It is a further object of the present invention to pro- "vide gear gauging apparatus comprising a pair of laterally spaced relatively movable master gears, means .for advancing a work gear in the direction of its axis to :a position in which its teeth enter substantially into tooth spaces of the master gears, and means operable .thereafter for initiating rotation of the rotatable master ggear.

It is a further object of the present invention to provide :apparatus as described in the preceding paragraph in combination with means responsive to movement of the work gear to a position in which the ends of its gear :teeth are located inwardly from the ends of the master gear teeth to initiate rotation of the rotatable master gear.

It is a further object of the present invention to provide gear gauging apparatus comprising gauging mechanism through which a work gear is passed in a downward direction, a pair of oppositely extending downwardly inclined trackways, a pivoted gate located beneath said gauging mechanism and having inclined surfaces selectively movable into position to direct a gear onto one or the other of said trackways.

Other objects and features of the invention will become apparent as the description proceeds, especially when taken in conjunction with the accompanying drawings, wherein:

Figure 1 is a side elevational view with the cover partly broken away and removed.

Figure 2 is a plan view with the top cover removed.

Figure 3 is an elevational view looking from the left in Figure 1 with the cover broken away.

Figure 4 is an incomplete rear elevational view looking in the direction of the arrows 4-4, Figure 2.

Figure 5 is a fragmentary plan view looking in the direction of the arrows 55, Figure 1.

Figure 6 is a fragmentary plan view looking in the direction of the arrows 66, Figure 1.

Figure 7 is a. wiring diagram of the gear gauging apparatus.

In the present case, gauging is referred to as by size. Since it is accomplished by meshing with master gears, it is nominally a gauging of pitch diameter. However, other errors or conditions will result in the spread center distance between the gauge or master gears.

2,905,320 Patented Sept. 22, 1959 Thus, teeth incompletely hobbed or shaper-cut have end protuberances and will show up as a size error; so also, if a helix angle error is present. A single thick tooth resulting from incomplete work rotation in shaper cutting will also produce the same indications. Dirt, chips or foreign material on the gear or burrs may also indicate an oversize. Accordingly, where size is referred to it will be understood to encompass any of the aforesaid conditions.

The gear gauging apparatus comprises an internal frame including

side plates

10 and 12 connected by brackets 14 to a floor plate 16. At the forward end of the

plates

10 and 12 they are cut away to provide ledges 18 on which is secured a transversely extending supporting plate 20. Extending upwardly from the plate 20 is a plate 22 adapted to serve as a mounting means for condition limit switches later to be described.

Extending between

plates

10 and 12 is a pivot pin 24 the ends of which are received in bearings indicated generally at 26 provided in suitable openings formed in the

plates

10 and 12. Fixedly secured to the pivot pin 24 by suitable means, such for example, as a set screw indicated at 28 is an amplifying arm or lever 30. The arm 30 includes downwardly extending flanges 32 between which is journaled a master gear 34. In order to retain the master gear 34 against rotation relative to the arm or lever 30 a soft plug 36 is provided which extends in a bore formed in a portion of the arm 30 intermediate the flanges 32. A set screw 38 extends into a tapped opening and engages the soft plug and forces one end of it into engagement with the periphery of the master gear 34. By loosening the set screw 38 the master gear 34 may be slightly rotated and locked in adjusted position, thereby presenting new portions thereof for use in gauging gears.

A second master gear 40 is provided which is located in laterally spaced relation to the master gear 34 with its axis substantially parallel thereto. The master gear 40 is pinned or otherwise rigidly connected to a shaft 42 which extends throug' a journal bearing in the plate 12 and into a journal bearing in an opening in the plate 10. The shaft 42 at its outer end is provided with a pinion 44 in mesh with a rack 46 slidable on a support indicated generally at 48. The rack 46 is connected by a piston rod 50 with a piston located at the interior of an air cylinder 52. Obviously, movement of the piston to the right or left as seen in Figure 1 or 2, will result in rotation of the pinion 44 and hence the master gear 40. It will also be observed that the structure just described provides a mounting for the master gear 40 which is fixed in space. Thus, the master gear 34 is prevented from rotating on its axis, but is movable generally toward and away from the master gear 40 in an arc whose center is the axis of the pivot pin 24.

Means are provided for feeding a series of work gears to be gauged to the apparatus and this means includes a trough or chute 53 through which the work gears are adapted to be advanced in the direction of their axes. As illustrated in Figure 2, the chute 53 is shown as associated with a vibrating type feed device 54. Feed devices of this type are well known under the trade name Syntron, and by a controlled differential vibration are adapted to feed work pieces in a required direction.

From an inspection of Figure 4 it will be observed that the chute 53 is located so as to advance a work gear to be gauged with its axis generally parallel to the axes of the master gears carried by the shaft 42 and pivot pin 24, but located somewhat thereabove. The arrangement is such that as a gear is advanced along the chute 53 toward the

master gears

34 and 40 its teeth are in position to enter substantially into the tooth spaces of both of the

master gears

34 and 40. Accordingly, as a particular work gear is advanced it may be that upon initial contact with the

master gears

34 and 40 the ends of the teeth of the work gear engage the ends of the teeth of the master gears. However, since the type of feed referred to is a vibratory feed, the ends of the teeth of the work gear will almost immediately be vibrated into clearance and the gear will continue to advance into the space between the master gears.

Means are provided to control initiation of a gauging operation. This means includes a pin 56 located in position to be engaged by the advancing end of a work gear when it is in position to be gauged by the

master gears

34 and 40. This position of course is determined when the ends of the teeth of the work gear are flush with or located inwardly from the ends of the teeth of the master gears. The pin 56 is carried by a lever 58, as best seen in Figure 6, the lever 58 being journaled as indicated at 60. to a mounting plate 62 bolted or otherwise secured to the side plate 12. The mounting plate 62 carries a bracket 64 on which is mounted an adjustable abutment 66. The lever 58 carries an adjustable actuating screw 68 adapted to engage the plunger of a position limit switch LS7. In Figure 1 a valve 69 is diagrammatically shown as connected to a solenoid C connected to open the valve when the solenoid is energized to admit fluid to move the piston-cylinder 52 to the left as seen in this figure. Control of the solenoid C is further described in conjunction with the circuit diagram of Figure 7.

Adjacent the end of the arm or lever remote from the axis of the pivot pin 24 are three adjustable switch actuating screws 70 adapted to actuate plungers of condition limit switches LS1, LS2 and LS3 which are secured to the plate 22 previously described. At its outer end the arm 30 is connected by a tension spring 72 and adjusting screw 73 to the plate 20, thus urging the arm in a counterclockwise direction as seen in Figure 1. The arm is also provided with an adjustable abutment screw 74 the end of which engages an abutment block 76 to limit counterclockwise movement of the arm 30. Condition limit switches LS1, LS2 and LS3 are adjusted so that when the screw 74 is in contact with the abutment block 76 all ofthe limit switches are in open condition. When a work gear of approximately the required size but slightly undersize is caused to move downwardly through the space between the master gears 34 and 40, the master gear 34 is moved to the left as seen in Figure 1, thereby rocking the arm or lever 30 in a clockwise direction to a position in which condition limit switch LS1 is actuated as will subsequently be described in conjunction with the wiring diagram. If the gear is somewhat larger and within acceptable limits as to size the arm 30 will swing somewhat further and condition limit switch LS2 will be actuated. 1f; the work gear has a size larger than the upper limit of acceptable tolerance the arm 30 will be swung still further, thereby actuating condition limit switch LS3. As soon as the work gear has moved downwardly through the space between the master gears the spring 72 returns the arm 30 to its idle position with the abutment screw 74 resting on the block 76. Thus, the idle position of arm 30 is at all times the same.

Means are provided under the control of the condition limit switches LS1, LS2 and LS3 for physically separating a series of gears into groups in accordance with size. Thus, all gears of proper size are separated from gears which are oversize and undersize. Moreover, since gears which are undersize are scrap, whereas gears which are oversize may be salvaged by a second gear finishing operation, these gears are also separated. The means for accomplishing this comprises three inclined chutes 80, 82 and 84. By mechanism subsequently to be described, gears which are within acceptable limits as to size pass downwardly through the chute 82 to an external chute 86 which may lead to a storage bin or conveyor. Gear-s which are oversize pass through the chute 80 whence they are directed into a storage bin or conveyor for salvageable gears. Gears which are undersize are directed to the chute 84 whence they pass to a conveyor or receptacle for scrap gears. The means for directing the gauged gears to the proper chute comprises first a selecting gate 88 pivoted between the

plates

10 and 12 on a pivot shaft 90 to which is connected a crank arm 92. A solenoid B has a plunger 94 connected by suitable link means indicated generally at 96 to the crank so that when the solenoid is energized the, gate 88 is rocked from the position illustrated in Figure 4 counterclockwise to a position in which the surface98 thereof overlies the space between the master gears, and hence will guide a gauged gear to the right as seen in Figure 4. It will be appreciated that parts are shown reversed in Figure 1 so that when the solenoid B is not energized a gauged gear moving downwardly between the master gears will roll along the surface 100 to the right as seen in this figure, and hence will be directed to the chute 82. When the solenoid B is energized however, the gauged gear will be directed to the right as seen in Figure 4, or the left as seen in Figure l, to the chute 80.

The chute 82 includes a pivoted trap door 102, this door being secured to a pivot pin 104 from which extends a crank arm 106 as best illustrated in Figure 4. The crank arm 10.6 is connected by link mechanism indicated generally at 108 to the plunger 110 of the solenoid A. When the solenoid A is energized, the trap door 102 is lifted or is swung clockwise about the axis of pivot pin 104 as illustrated in Figure 1. This movement of the trap door blocks movement of a gauged gear along the chute 82 and in addition, exposes a gap or opening through which the gauged gear may drop so as to enter the inclined chute 84. The foregoing solenoids A and B and the mechanism associated therewith thus constitute means for directing gears selectively to the chutes 80, 82 or 84 in accordance with gear characteristics as determined by the gauging mechanism including the master gears.

In order to make the gear gauging apparatus completely automatic and adapted to gauge and separates. series ofgears without requiring the attention of an operator, the chutes 80, 82 and 84 are each provided with means for sensing the passing of a gear therethrough.

Associated with the chute 80 is a position limit switch L 6 and a switch actuator including a movable floor member 112 including a pivot pin 114 carrying an arm 116 to which is secured an adjustable switch actuating screw 118 adapted to actuate position limit switch LS6. Thefree end of the floor member 112 is located slightly above a stopv member 120 and is counterbalanced by a light tension spring 122 so that as a gear rolls along the chute 80, the floor member 112 is rocked in a counterclockwise direction as seen in Figure 1, thus actuating position limit switch LS6. An identical movable switch actuating floor member 124 is provided in association with the trough or chute 86 and includes an arm 126 carrying an adjustable switch actuating screw 12 8 adapted to actuate position limit switch LS5. Thus, a gear directed to the chute 82 actuates position limit switch LS5. Another position limit switch LS4 is provided in association with mechanism adapted to be operated by movement of a gauged gear to the chute 84. A lever 130 is provided in position to be engaged by a gear falling through the gap or opening exposed by upward movement of the trap door 102, this lever having an arm 132 thereon carrying an adjustable abutment screw 134 adapted to actuate position limit switch LS4.

The vibratory feed unit if supplied with a large quantity of gears tends to advance a series of gears in side by side relation and it is essential to separate the leading gear during the gauging operation from the series of gears thereafter. Mechanism for accomplishing this comprises a blade device pinned or otherwise secured to the shaft 42 which carries the pinion 44 and the master gear 40. The blade device comprises a blade 142 carried by an arm 144 at one side thereof, as seen in Figure 2, the blade being located in position to move in behind the gear being gauged and to occupy a position in which is prevents the next following gear entering into engagement with the master gears. This permits the vibratory feeding device to .continue to operate during the gauging cycle and at the same time prevents a following gear from interfering with the gear being gauged. The blade device is returned to the position illustrated in Figure 4 when the master gear 40 is reversely rotated following completion of a gauging cycle.

'An indicator gauge 150 is mounted on the frame and the amplifying arm 30 has-connected thereto a lateral extension 152 carrying an adjusting screw 154 adapted to engage the plunger of the indicator. This mechanism is employed to facilitate initial adjustment of the condition limit switches LS1, LS2 and LS3 and the adjustable abutment screw 74, and does not enter into the automatic operation of the gauging apparatus.

Referring now to Figure 7, there is shown the wiring diagram for the automatic gauging apparatus.

Figure ,7 is a simplified wiring diagram in which the windings of relays are indicated by circles and the contacts of the relays actuated by energization of the windings are indicated throughout the circuit with the same basic reference numerals followed by a small letter to identify different contacts. Thus, a relay designated R1 may have a plurality of contacts which will be designated Rla, R112, etc. Normally open contacts are designated by parallel lines, and normally closed contacts by parallel lines through which an inclined line is drawn.

With the foregoing general explanation in mind, the simplified circuit comprises lines L1 and L2 connected by a line switch SW1 to external lines bearing the same designations. Extending between the lines L1 and L2 in series are a normally closed stop'switch SW2, a normally open start switch SW3, and a main relay M1. Relay M1 includes normally open contacts Mla in line L1, which when closed serve to energize the various limit switches later to'be described. Relay M1 also includes normally open contacts Mlb in parallel with the contacts of the starting switch SW3 and effective to maintain a circuit to relay M1 independent of the contacts of the starting switch SW3.

Condition limit switch LS1, which it will be recalled is actuated by initial movement of the arm 30, is a twoposition switch. In its normal position it is in a circuit between lines L1 and L2 including normally open contacts R1b and the windings of solenoid A. It includes normally open contacts in a branch line which includes in series normally closed contacts R2a, R3a and R4a and relay R1. A parallel holding circuit including contacts Rla is provided around the lower contacts of condition limit switch LS1 and is adapted to maintain the circuit to the relay R1 when this relay has been energized by do sure of the lower contacts of condition limit switch LS1. Condition limit switch LS2 is in a circuit connecting lines L1 and L2 is series with normally closed contacts R3a and R4b and relay R2. Contacts R2b are connected in parallel around condition limit switch LS2 and are adapted to maintain a circuit to relay R2 independent of opening of contacts of condition limit switch LS2.

Condition limit switch LS3 is in a circuit connecting lines L1 and L2 inseries with normally closed contacts R40 and relay R3. Again, a holding circuit is provided around condition limit switch LS3 which includes normally open contacts R30.

Position limit switches LS4, LS5 and LS6 are in a parallel group connecting lines L1 and L2, the group being in series with relay R4.

Solenoid B is connected between lines L1 and L2 in series with normally open contacts R3d. Solenoid C is provided in the circuit between lines L1 and L2 in series with normally open contacts R511. The solenoid C is adapted to control a four-way valve (not shown) to effect reversalof air to the air cylinder 52 which is the motor means for driving the rack 46.

Relay R5 is connected between the lines L1 and L2 in series with position limit switch LS7 and normally closed contacts R4d. A holding circuit independent of position limit switch LS7 is provided around this limit switch and comprises normally open contacts R5a.

With the foregoing description of the circuit in mind the operation will be briefly reviewed. In the illustrated position the gauging apparatus is brought into operation by closing the line switches and momentarily depressing the starting switch SW3 which energizes relay M1, establishes a holding circuit around the normally open contacts of the starting switch SW3, and closes normally open contacts Mia, thus energizing the control circuit to the various instrumentalities of the gauging apparatus.

If a gear which is undersize is advanced into the gear gauging apparatus it eventually reaches a position with the master gears in which it actuates position limit switch LS7 to establish a circuit to relay R5 through normally closed contacts R4d and establishes a holding circuit around position limit switch LS7. Energization of the relay R5 also closes normally open contacts R5b and energizes the solenoid C, thus actuating the valve and admitting air to the air cylinder 52 in a direction to move the piston inwardly and thus to rotate the pinion 44 and master gear 4% in a counterclockwise direction, as seen in Figure 1. This rolls the gear being gauged through the space between the master gears and will rock the arm 3i) to a position dependent upon the pitch diameter of the gear. In the assumed case the gear is undersize and hence, only condition limit switch LS1 is actuated. Actuation of condition limit switch LS1 completes a circuit through normally closed contacts R2a, R311 and R ta and relay R1, thus closing normally open contacts Rla and establishes a holding circuit to: relay R1 independent of condition limit switch LS1. At the same time normally open contacts Rlb are closed, thus energizing solenoid A which has the effect of rocking the trap door 1112 to upward position so that as the gear engages the inclined surface of the gate 88 the gear will fall through the opening vacated by the door 102 and will engage the lever and thence roll out of the gauging apparatus through the chute 84 to be collected with the undersize gears. Engagement of the lever 130 by the gear actuates position limit switch LS4, thus completing a circuit to relay R4. This will open normally closed relay R4a, thus de-energizing relay R1. Also, it will open normally closed contacts R4d, thus deenergizing relay R5 and opening normally open contacts RSb. This in turn de-energizes solenoid C, thus reversing the valve and moving the piston outwardly of the cylinder 52 to rotate the pinion 44 and the master gear 40 clockwise as seen in Figure 1, in preparation for receiving the next successive gear.

In the event that the gear is of proper size the operation is similar except that as the gear passes between the master gears condition limit switches LS1 and LS2 will be actuated in sequence. Closure of condition limit switch LS2 energizes relay R2 through normally closed contacts R3b and R411. Energization of relay R2 establishes a holding circuit through contacts R2b around condition limit switch LS2 and also opens normally closed contacts RZa, thus breaking the circuit to relay R1. During this sequence of operations contacts R11) will have closed upon actuation of condition limit switch LS1 but Wlll again open upon de-energization of relay R1 and since condition limit switch LS1 will not return to its illustrated position until after condition limit switch LS2 has opened and closed, no current passes to solenoid A. Accordingly, the gear passes through the gauging apparatus without energization of either solenoids A or B and the gear accordingly will roll down the inclined surface 100 of the gate 88 and down chute 82 to be collected with the accurate gears. Actuation of position limit switch LS5 operates to return the air cylinder as described in conjunction with position limit switch LS4.

v If the gear being gauged is oversize the sequence of operations is as before except that condition limit switches LS1, LS2 and LS3 are actuated in sequence. Closure of condition limit switch LS3 energizes relay R3 through normally closed contacts R40 and establishes a holding circuit around condition limit switch LS3 through contacts R30. At the same time normally closed contacts R3a and R3b open, thus breaking the circuit to relay R2. T he circuit to relay R1 will have been broken by the prior closing of condition limit switch LS2 as previously described. Accordingly, as relay R3 of the set consisting of relays R1, R2 and R3, remains closed after passage of' the gear between the master gears, energization of relay R3 closes normally open contacts 113d, thus energizing solenoid B and rocking gate 83 to position its surface 98 beneath the master gears to direct the gear into chute or trough 8%). As soon at the oversize gear rolls over lever 112 position limit switch LS6 is closed, thus energizing relay R4 and opening normally closed contacts R40. This in turn de-energizes relay R3, breaking the circuit to the solenoid B through contacts R3d. Energization of relay R4 also opens normally closed contacts R4a, thus breaking the circuit to the relay R5 and opening normally open contacts R51) to solenoid C which results in actuation of the valve and reversal of the air cylinder 52. The mechanism thus described will continue to operate in a fully automatic manner and will separate oversize and undersize gears from each other and from accurate gears within very close limits.

While axial advance of the gears is shown and describedherein, it will be appreciated that the gauging apparatus would work in precisely the same manner if the gears were advanced perpendicular to their axes.

The drawings and the foregoing specification constitute a description of the improved gear gauging apparatus in such full, clear, concise and exact terms as to enable any person skilled in the art to practice the invention, the scope of which is indicated by the appended claims.

What I claim as my invention is:

1. Gear gauging apparatus comprising a first master gear mounted for rotation in a fixed location, a second master gear located in spaced relation to said first master gear with the axes of said master gears parallel, means mounting said second master gear for movement toward and away from said first master gear and for preventing rotation thereof, means urging said second master gear toward said first master gear, means engageable with the mounting means of said second master gear to limit approach of said master gears to an amount not greater than sufiicient to engage both sides of an undersized work gear, motor means for rotating said first master gear, means for advancing a work gear into meshed relation with both of said master gears with its axis parallel to but spaced from the plane containing the axes of said master gears, means responsive to movement of the work gear into said relation to initiate rotation of said first master gear in the direction to drive the work gear through the space between said master gears, means re-. sponsive to displacement of said second master gear away from said first master gear by passage of work gears therethrough to separate them into under, over and proper size.

2. Gear gauging apparatus as defined in claim 1 in which said motor means comprises a piston and cylinder device, a rack connected thereto, and a pinion connected to said first master gear and in mesh with said rack.

3. Gear gauging apparatus as defined in claim 1 in which the means for advancing a gear into position in mesh with both master gears is operative to advance the gear in the direction of its axis.

' 4. Gear gauging apparatus as defined in claim 1 in which the means for advancing the work gear into meshed relation with both of said master gears come prises a chute for receiving a series of axially aligned work gears and means for advancing the series of gears in saidchute, and comprising a member movable with said firstmaster gear into blocking position between a work gear being gauged and the following gears.

-5. In geargauging apparatus, a pair of master gears with their axes substantially parallel and spaced apart a distance such that both master gears mesh fully even with undersized work gears passing therebetween, means mounting said master gears for relative movement, means effective to prevent rotation of one of said master gears, means for selectively rotating the other master gear, means for advancing a work gear to be gauged in the direction of its axis to a position in which its teeth enter to a substantial depth into the tooth spaces of both of said master gears, and means responsive to axial advance of the work gear to gauging position for initiating opera tion of the gear rotating means to roll the work gear between said master gears.

6. In gear gauging apparatus, a pair of master gears with their axes substantially parallel and spaced apart a distance such that both master gears mesh fully even with undersized work gears passing therebetween, means mounting said master gears for relative movement toward and away from each other, means eifective to prevent rotation of one of said master gears, means for selectively rotating the other master gear, means for advancing a work gear to be gauged in the direction of its axis to a position in which its teeth enter to a substantially depth into the tooth spaces of both of said master gears, and means responsive to axial advance of the work gear to gaugingp oSition for initiating operation of the gear rotating mean ro he ork e e n a s e rs mc u as efin d in claim 6 c p s n means operable. during continuous movement of the work gear between said master gears to measure its pitch diameter.

8 StruqmIe as defined in claim 7 comprising means responsive to the measurement of pitch diameter of a series of gears for separating the gears into under, over and proper size gears.

9. In gear gauging apparatus, a pair of master gears with their axes substantially parallel and spaced apart a distance such that both master gears mesh fully even with undersized work gears passing therebetween, means mounting said master gears for relative movement, means efiective to prevent rotation of one of said master gears, means for selectively rotating the other master gear, nonpositive feed means for advancing a series of work gears to be gauged in the direction of their axes to positions in which the teeth of the leading gear of the series enters to a substantialdepth into the tooth spaces of both master gears, means responsive to axial advance of the lead-. ing work gear to gauging position for initiating operation of the. gearrotating means to roll the work gear between said master gears, and means operably connected to said gear rotating means for blocking advance of the following gears into engagement with the master gears during the gauging operation of the leading gear.

10. Structure as defined in claim 9 in which the meansfor selectively rotating the other master gear comprises means for rotating the master gear in a direction to roll the work gear through the space between the master gears to initiate a gauging operation and to reversely rotate the master gear to initial position at the completion of a gauging operation, and in which the means for blocking the advance of the following gears during the gauging operation comprises a blade movable by rotation of the rotatable master gear into blocking position and movable out of blocking position upon reverse rotation o ma t r ar- ;11. Gear gauging apparatus comprising a first master gear mounted for rotation in a fixed location, a second master gear located in spaced relation to said first master gear with the axes of said master gears parallel and spaced aparta distance such that both master gears mesh fully even with der izedw r ge rs passing therebe tween and with the plane containing such axes inclined from the vertical by an angular amount such that gravity operates to retain a work gear in mesh with both of said master gears, means mounting said second master gear for movement toward and away from said first master gear and for preventing rotation thereof, means for ad vancing a work gear into meshed relation with both of said master gears with its axis parallel to but spaced from the plane containing the axes of said master gears, means for rotating said first master gear when a work gear is in mesh with both master gears in the direction to drive the work gear through the space between said master gears, means responsive to displacement of said second master gear away from said first master gear to measure the size of said work gear, and means responsive to the measurement of the size of the work gears for separating them into under, over and proper size.

12. Gear gauging apparatus comprising a first master gear mounted in a fixed location, a second master gear located in spaced relation to said first master gear with the axes of said master gears parallel and spaced apart a distance such that both master gears mesh fully even with undersized work gears passing therebetween and with the plane containing such axes inclined from the vertical by an angular amount such that gravity operates to retain a work gear in mesh with both of said master gears, means mounting said second master gear for movement toward and away from said first master gear, means for advancing a work gear into meshed relation with both of said master gears with its axis parallel to but spaced from the plane containing the axes of said master gears, means for preventing rotation of one of said master gears, means for rotating the other of said master gears when a work gear is in mesh with both master gears in the direction to drive the work gear through the space between said master gears, means responsive to displacement of said second master gear away from said first master gear to measure the size of said work gear, and means responsive to the measurement of the size of the work gears for separating them into under, over and proper size.

References Cited in the file of this patent UNITED STATES PATENTS 2,318,970 Richmond May 11, 1943 2,382,885 Landay et a1 Aug. 14, 1945 2,474,482 Lovick June 28, 1949 2,561,534 Parker et al July 24, 1951 2,591,047 Burge et a1. Apr. 1, 1952 r 2,675,917 Powers Apr. 20, 1954 2,761,560 Pomernacki Sept. 4, 1956 2,803,342 Gates Aug. 20, 1957 OTHER REFERENCES Versatility Accentuated in Continuous Gear Production, by C. E. Scott; Automation April 1955, pp. 47-53.

Continuous Blank Machining in Gear Production, by J. J. McCabe, Automation, June 1955, pp. 26-29.