JPH0634489A - Ball master gear - Google Patents

Abstract

PURPOSE:To obtain a ball master gear for measuring engaged states of two tooth surfaces which can efficiently measure the runout of tooth spaces with high accuracy even when a gear to be measured is a bevel gear. CONSTITUTION:A driving gear 93 is provided on one side of the cylindrical surface 91b of a ball master base 91 and, at the same time, a pressing gear 95 is provided on the other side of the surface 91b and fixed with bolts 92 and 94. The surface 91b of the base 91 becomes a reference driven surface in the radial direction when probe balls 96 are inserted into the tooth space of a gear to be measured without backlash. Each tooth 93a of the driving gear 93 becomes the reference driven surface in the axial direction of the ball 96 and, at the same time, has an about rectangular plane 93d of rotation which enables continuous engaged rotation between the gear 93 and the gear to be measured. The conical space 95b of the gear 95 retains the balls 96 with a gap. The front sections of the gears 93 and 95 are tapered. No-backlash points are produced by inserting the balls 96 arranged on the circumference in the form of a gear into each tooth space of the gear to be measured and the points are read as runout of the tooth spaces.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a ball master gear in which a tracing stylus ball for measuring a runout value of a tooth groove of a bevel gear or the like is formed in a gear shape so as to enable automatic measurement with high accuracy and in a short time. It is about.

[0002]

2. Description of the Related Art As a conventional method for measuring the runout value of a tooth groove, first, there is a method of inserting a single tracing stylus ball into the tooth groove without a back gap. In this method, the tracing stylus ball is provided in a mechanism that is constrained in the axial direction of the gear to be measured and is movable in the radial direction, and the tracing stylus ball is inserted into each tooth groove. In this method, each tooth groove is indexed by manual rotation to manually insert the tracing stylus ball, and as shown below, the tracing stylus ball reciprocates in the radial direction and feeds one tooth of the gear to be measured. There is an automatic continuous measuring method of one contact, one rotation, and one feed by a mechanism having a reciprocating rotation function in combination with a rotary motion.

For example, as shown in FIG. 6 (A), bearings 12 axially supported in two rows on a swing link 11 are provided on both sides of a guide 13 fitted in the swing link 11. A swinging link 11 is movably provided to perform a rolling motion,
Further, the guide 13 is provided so as to be rotatable around a support shaft 14. Therefore, with the turning of the eccentric shaft 16 provided at the eccentric position of the rotary shaft 15, the swing link 11 performs a combined motion of a longitudinal motion and an angular motion, and the tracing stylus ball 17 attached to the tip of You will have a curved movement like this. Since the measured gear W is pushed in the direction of the arrow with a constant pressure and can float back and forth, the tracing stylus ball 17 enters the tooth groove and feeds the measured gear W one tooth at a time, while measuring the measured point at the highest point of the curved movement. The tooth W comes into contact with the tooth surface in the vicinity of the pitch circle, and the radial runout measurement value of the gear W at this time is enlarged and recorded as shown in FIG. 6B. Further, the speed of the curvilinear motion is controlled by the microswitch 18, and the tracing stylus ball 17 is slowly fed near the highest point. In FIG. 6 (B), a indicates the runout value of the tooth space.

There is also a convenient method in which the measurement of meshing of two tooth surfaces between gears is performed, the eccentricity component is calculated from the obtained data, and the deviation value of the tooth space is used. In this two-tooth surface meshing measurement method, as shown in FIG. 7 (A), the gear to be measured W and the gear 19 of the actually used pair are pressed against each other by a measurement pressure without rotation to rotate the gear to be measured W. The amount of fluctuation in the radial direction is measured.
FIG. 7B shows an example of the measurement recording diagram, and the eccentricity component a shows the deflection value of the tooth space. b shows the total meshing error on both tooth flanks, and c shows the one pitch meshing error on both flanks. This two-tooth surface meshing measurement method is different from the measurement method of the tooth groove runout value specified in the standard because the entire meshing tooth surface is in contact, but if a master gear (parent gear) is used for the other party, it is practically an alternative. As it is enough.

Further, there is a tooth groove runout measuring method using a ball master gear that combines the above two methods. In this conventional ball master gear, the tracing stylus balls are arranged like a gear around the circumference, and the measuring stylus balls engage with the gear to be measured to measure two tooth flanks. A back gap point is created, and that point is read and used as the tooth groove deflection value, which is a measurement method specified in the standard. Since two tooth flanks are engaged, the movement of the tracing stylus ball is not measured individually for each tooth space but is measured during continuous rotational movement.

For example, as shown in FIG. 8, in a two-tooth surface meshing measuring machine manufactured by Karlmar Company (West Germany), a tracing stylus ball 21 is arranged on a master cylindrical surface 20 at a predetermined pitch in a gear shape. Hold it by the holding plate 22 from above and below,
The drive rotation is given from the gear W to be measured, and the tracing ball 21 receives the follow-up rotational force. Then, the center of rotation of the master cylindrical surface 20 and the center of rotation of the gear to be measured W are held parallel to each other to engage two tooth surfaces, and the movement of the tracing stylus ball 21 is received by the master cylindrical surface 20. The amount of movement in the radial direction is used as the tooth groove deflection value.

[0007]

Since the tooth groove runout measuring machine with one tooth feed shown in FIG. 6 carries out one tooth feed with one rotation of the tracing stylus ball 17, the measurement is performed at a relatively low speed. It is difficult to support high speed.

In the two-tooth-face meshing type measuring machine shown in FIG. 7, the precision of the master gear (master gear for meshing) in the case of a spur gear and a helical gear is also standardized. Although it is possible to actually measure the accuracy, it is not possible to manufacture a master gear because the bevel gear does not have a standard (standard) for the master gear due to the characteristics of paired use, and the gear to be measured W and the mating gear of the actual pair The further selected and specified gear 19 is used as a substitute for the master gear. Therefore, the bevel gear 2
It is difficult to measure tooth groove runout with high accuracy by the tooth surface meshing measurement method.

The two-tooth surface meshing measuring device using the ball master gear shown in FIG. 8 is used for measuring the runout of the tooth groove of the spur gear because the receiving reference surface of the tracing stylus ball 21 is only the master cylindrical surface 20 (radial direction). Are limited. Further, since only the tracing stylus ball 21 meshes with the gear W to be measured, the rotary motion lacks smoothness, and the variation in the center-to-center dimension is too large to be versatile.

The present invention has been made in view of the above point, and even when the gear to be measured is a bevel gear, a ball for measuring two tooth flanks which can efficiently measure the deviation of the tooth groove with high accuracy. The purpose is to provide a master gear.

[0011]

According to a first aspect of the present invention, each of the tooth grooves of the gear to be measured is obtained by arranging a tracing stylus ball like a gear on the circumference of the gear and measuring two tooth flanks with the gear to be measured. For each ball master gear that creates a gapless point with the tracing ball for each measuring point and uses that point as the runout value of the tooth gap, when inserting the tracing ball into the tooth groove of the gear to be measured without a gap And a ball master table having a cylindrical surface that serves as a radial receiving reference surface, and an axial receiving reference surface for the measuring element ball that is provided on one side of the cylindrical surface of the ball master table and that continuously meshes with the gear to be measured. A ball master gear including a drive gear having an axis-perpendicular plane that enables rotation, and a holding gear that is provided on the other side of the cylindrical surface of the ball master table and that holds the tracing stylus balls through a gap with a gap. .

According to a second aspect of the present invention, the drive gear and the pressing gear of the first aspect are tapered gears.

[0013]

In the ball master gear according to the first aspect of the present invention, the two gear tooth surfaces of the drive gear and the gear to be measured are continuously meshed and rotated. At the tooth groove runout measurement point, there is no back gap point in the tooth groove due to the probe ball, and that point becomes the maximum value in the tooth groove radial direction. Even if the gear to be measured has a non-cylindrical pitch circle such as a bevel gear, the measuring element ball is constrained in the axial direction by the plane perpendicular to the axis of the drive gear, and the radius of the same circle diameter is circumscribed by the cylindrical surface of the ball master table. The runout value of the tooth space is detected as a change in direction.

According to the second aspect of the present invention, the taper of the driving gear prevents interference between the pressing gear and the gear to be measured to ensure continuous meshing rotation.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A ball master gear of the present invention will be described in detail below with reference to an embodiment applied to an automatic sorter.

First, the outline of the automatic sorter shown in FIG. 3 will be described. A work unit 32 for setting a gear to be measured (hereinafter, referred to as a work) G in a central portion of a measurement table 31, and a work unit 32.
A drive unit 33 for rotating the work G set in the work unit 32, and a ball master gear for the rotating work G.
A master unit 35 for measuring the runout value and the like of the tooth space is arranged by 34. A loader 37 for transferring the work G between the conveyor 36 provided on the front surface of the measurement table 31 and the work section 32 for transferring the work is arranged between the two. The loader 37 is a mechanism for moving up and down and rotating the pair of chucks 38.

The work G carried into the conveyor 36 from the left side of FIG.
Is stopped by the cylinder 43, locked at the loading position by the stopper 44 operated by the cylinder 43, loaded on the work part 32 by the loader 37, and rotated by the drive part 33.
The ball master gear 34 of the master unit 35 measures the tooth groove runout value, etc., and after the measurement is completed, the loader 37 conveys it.
The workpiece G of the processing quality that has been unloaded onto the 36 and has reached the standard is carried out from the right end of the conveyor 36, and the workpiece G that has not reached the standard is taken out to the side of the conveyor 36 by the stopper 46 operated by the cylinder 45. It is collected and collected in the bucket 47.

FIG. 4 shows the work part 32 and the drive part 33.
And a master portion 35 including the ball master gear 34.

In the work part 32, a bearing cylinder 52 is fixed on the measurement table 31 via a mounting base 51.
The rotary cylinder 53 is rotatably fitted inside the
The work shaft 54 is fitted in the center of the. And
Rotation is transmitted from the output shaft of the drive unit 33 including the motor 33a and the speed reducer 33b to the rotary cylinder 53 via the timing pulley 55, the timing belt 56 and the timing pulley 57, and is integrally mounted on the upper end of the rotary cylinder 53. The work seat 58 is rotated, and the work (bevel gear) G fitted in the work seat 58 is also integrally rotated.

As shown in FIGS. 4 and 5, the master section 35 has a swing support shaft 62 integrally attached to a support plate 61 standing on the measurement table 31, and the swing support shaft 62 is mounted on the support plate 61. 62
An oscillating plate 63 is fitted to the oscillating plate 63 via a tubular portion 64 so as to be freely oscillating.

Further, as shown in FIG. 4, a bearing cylinder 71 is integrally attached to the upper end plate portion 63a of the rocking plate 63, and a rotary shaft 72 is rotatably fitted to the bearing cylinder 71. The ball master gear 34 is fitted to the taper portion 72a of the rotating shaft 72, and the ball master gear 34 is tightened by the pressing flange 73 screwed to the upper end screw portion 72b of the rotating shaft 72. Retaining ring mated from
74 is fixed to the ball master gear 34 with bolts 75. Further, the upper end plate portion 63a of the rocking plate 63 has a mounting plate 76,
Proximity switches 78 and 79 provided via 77 detect each tooth of the ball master gear 34.

The swing plate 63 is swingably provided between a pair of stoppers 81 and 82 mounted on the support plate 61, and is attached to the lower portion of the support plate 61 via a mounting plate 83. A tension spring 85 stretched between the adjustment screw 84 and the adjustment screw 84 urges the ball master gear 34 against the work G by being urged counterclockwise about the swing support shaft 62. The displacement sensor 86 attached to the support plate 61 is opposed to the lower side surface of the swing plate 63, and the fluctuation of the swing plate 63 at the time of measuring the two tooth surface meshes around the swing support shaft 62 is measured by the sensor 86. To detect.

A cylinder 87 is attached to the support plate 61 for retracting the ball master gear 34 from the work portion 32 during work loading and unloading.
When the work is attached / detached, the rod tip pressing portion 88 of the cylinder 87 presses the pressed portion 89 of the rocking plate 63 to rotate clockwise and separate the ball master gear 34 from the work G.

Next, the details of the ball master gear 34 will be described with reference to FIGS. 1 and 2.

The ball master gear 34 is the rotary shaft
A ball master base 91 fitted to the taper portion 72a of 72,
A drive gear 93 fitted on one side of the flange 91a of the ball master table 91 and fixed by a bolt 92, and a press gear 95 fitted on the other side of the flange 91a of the ball master table 91 and fixed by a bolt 94. , The drive gear 93 and the presser gear
It is constituted by a tracing stylus ball 96 which is held in a gear shape between the circumferential portion and 95, as shown in FIG. 1 (B).

The ball master table 91 has a flange
On the peripheral surface of 91a, there is provided a cylindrical surface 91b serving as a radial receiving reference surface when the tracing stylus ball 96 is inserted into each tooth groove of the work G without a back gap. This radial receiving reference cylindrical surface 91b
In the case where the tip of the workpiece G contacts the measurement position (point) of the workpiece G, a tooth groove is provided so that measurement can be performed near the designated measurement position.

The ball master table 91 is provided with the rotary shaft 72.
Since the axial movement in is not allowed in the measurement, a taper hole 91c fitted into the rotary shaft taper portion 72a is bored at the center, and a screw groove 91d is provided on the upper surface.
The pressing flange 73 is fixed through the fixing ring 74 by the bolt 75 screwed into the 91d, so that the rotary shaft taper portion 72a and the taper hole 91c are securely fitted and fixed.

Since the drive gear 93 has an axis-perpendicular plane 93d on each tooth 93a which serves as an axial receiving reference surface of the tracing stylus ball 96 and enables continuous meshing rotation with the work G, each tooth 93a is formed. With this, continuous meshing rotation with the work G is possible, and the measuring element ball 96 does not directly receive the rotational force of the ball master gear. That is, the specifications and shape are suitable for short-time measurement (high-speed rotation) in the case of fully automatic measurement including work loading and unloading, and capable of withstanding high frequency use.

As shown in FIG. 2, the specifications of the drive gear 93 are such that the radius in one tooth can be surely detected in order to reliably detect the runout value of the tooth groove in units of one tooth during continuous meshing with the work G. In addition to providing a directional movement difference, conversely the movement difference is too large so that a force other than the tooth groove runout measurement pressure is not applied to the tracing stylus ball 96 or discontinuous rotation is applied to taper 93b (= 15 °) and taper.
Perform special processing such as providing 93c (= 30 °).

During the determination of the specifications of the drive gear 93, it is necessary to pay particular attention to the tooth thickness (backlash with the work).
This is the runout measurement of the tooth groove with the tracing stylus ball 96 when the master gear tooth enters the tooth groove of the work G, and when the work tooth enters the tooth groove of the master gear, the radial movement difference is larger than that during measurement. This is because if the difference is too small, the rotation becomes unreasonable, and if it is too small, it becomes difficult to identify the measurement point.

Further, as shown in FIG. 1, the pressing gear 95 has conical grooves 95b provided on each tooth 95a, and holds the unprocessed tracing stylus balls 96 by the respective conical grooves 95b. Further, even if there is an error in the shape of the work G, an error in the gear portion, or a slight error in the mounting position, the tracing stylus ball 96 is inserted into each tooth groove of the work without a gap and can be reliably received by each receiving reference cylindrical surface 91b. So that this feeler ball
96 has the specifications and shape that can hold 96 with a sufficient gap.

That is, as shown in FIG.
In order to ensure that the contact point ball 96 can detect the runout value of the tooth groove, the specifications of 95 are held via a gap 95c between the conical groove 95b and the contact point ball 96, and this presser gear 95 95d (= 15 °) and taper to prevent interference with
Perform special processing such as providing 95e (= 30 °).

While the specifications of the presser gear 95 are being determined, especially the outer diameter,
It is necessary to pay attention to the tooth thickness. That is, the tooth thickness of the presser gear 95 is set to a tooth thickness that is provided with a ball holding function (V-shaped salami, etc.), and the clearance at the time of holding the ball is set as a set with the driving gear tooth thickness. Also, the outer diameter and tooth thickness of the presser gear 95 should not interfere with the work.

Further, the drive gear 93 and the pressing gear 95 are
It is advisable to design the structure so that they can be machined in consideration of their phase alignment, and in consideration of gear cutting, the dislocation coefficient in the involute tooth profile.

When the diameter and pitch of the tracing stylus balls 96 (the diameter of the receiving reference cylindrical surface 91b) are set, the measurement points are specified and calculated and determined on the work drawing. This is because bevel gears, especially automobile differential gears, have special specifications.

As described above, the ball master base 91, the drive gear 93 and the pressing gear 95 are used to hold and receive the tracing stylus ball 96 without using the tracing stylus ball 96.
Is held in the shape of a gear and is inserted into the tooth groove of the work without any back pressure under measurement pressure with the receiving reference surface of the tracing stylus ball 96, and the radial receiving reference surface is the receiving reference cylindrical surface 91b of the ball master table 91.
And the axial receiving reference surface is the plane perpendicular to the axis 93 which is the end surface of the cylinder.
Let d. If necessary, the tracing stylus ball may be processed to be the same.

The axis-perpendicular plane 93d also has specifications and a shape having a function of a driving gear to enable continuous meshing rotation with the work G. The ball master gear drives and rotates and the work is driven. Both rotations are possible.

Next, a procedure for gear cutting of the ball master gear 34 will be described. First, the ball master base 91,
The drive gear 93 and the pressing gear 95 are combined with each other, and the ball master base 91 and the pressing gear 95 are combined with each other, and the drive gear 93 and the pressing gear 95 are phase-marked ( A punch is attached to one tooth, and finally the driving gear 93 and the pressing gear 95 are tapered by tooth grinding.

Next, the operation of this embodiment will be described.

As shown in FIG. 4, the rotation is transmitted from the driving unit 33 to the rotary cylinder 53 via the timing belt 56 and the like, and the work (bevel gear) fitted to the work seat 58 at the upper end of the rotary cylinder 53 is transmitted. ) G is also rotated integrally. The ball master gear 34, which is biased counterclockwise about the swing support shaft 62 by a tension spring 85, is pressed against and meshed with the work G. This ball master gear 34 works G
While rotating in accordance with the rotation of, the rocking is performed around the rocking support shaft 62 at the time of measurement of meshing of two tooth surfaces. The amount of swing about the swing support shaft 62 is detected by a displacement sensor 86 facing the lower side surface of the swing plate 63. The rotation phase of the ball master gear 34 is detected by the proximity switches 78 and 79.

In this way, by detecting the swing amount of the ball master gear 34 and the rotation phase of the driving gear 93 for continuously engaging and rotating the two tooth flanks with the work, the runout value of the tooth groove of the work G is detected. And the relationship between the phase and the phase are measured and recorded, and it is determined whether or not the runout value of the tooth space is within a certain allowable range, and as described above, the standard is reached by the automatic sorter shown in FIG. The unworked work G is collected in the bucket 47.

When the work is attached to or detached from the work part 32 (work seat 58) by the chuck 38 of the loader 37 in the automatic sorter shown in FIG. 3, the rod tip pressing part of the cylinder 87 is used.
The pressed portion 89 of the rocking plate 63 is pressed by 88 to rotate clockwise, and the ball master gear 34 is separated from the work G.

Next, in the measurement of the runout of the tooth groove, the work G is supported on the basis of the center of rotation as described above, and the spherical tracing stylus ball 96 is in contact with both tooth surfaces of the work tooth groove over the entire circumference. It is inserted without a back gap, and the position variation of the tracing stylus ball 96 in the radial direction is measured. That is, at the tooth groove runout measurement point,
The backless point in the tooth space by the tracing stylus ball 96 is obtained, and that point becomes the maximum value in the radial direction in the tooth space.

The measuring contact is made on a designated pitch or a designated point such as on a reference pitch cylinder or on a mesh pitch cylinder, and may be around the designated diameter in consideration of the manufacturing error of the work G. The tooth groove runout error refers to the fluctuation width of one revolution of the work G over all tooth spaces.

When the work G is a bevel gear as shown in FIG. 4, it is necessary to measure the runout value of the tooth groove in the radial direction perpendicular to the pitch cone angle of the bevel gear. That is, the bevel gear has a pitch circle which is not a cylinder but a conical surface having a pitch cone angle, and the pitch and tooth groove width fluctuate along the pitch cone. It is necessary to regulate the axial direction and measure the variation in the radial direction. in short,
For workpieces such as bevel gears whose pitch circles are non-cylindrical,
It is necessary to restrain the tracing stylus ball 96 in the axial direction to capture the radial variation on the same circle diameter. If the direction in which the force is applied is constant, the constraint may be received by the reference receiving surface in that direction.

On the other hand, when the work is a gear having a cylindrical pitch circle such as a spur gear or a helical gear, the runout value of the tooth groove in the radial direction perpendicular to the rotation center reference of the work is measured. With this spur gear, fine movements parallel to the pitch cylinder result in only slight deviations of the measurement points, so even if fine movements in the axial direction occur, simply measuring the fluctuations in the radial direction will result in the measurement of the runout value of the tooth space. Become. If the work is this spur gear or helical gear,
It is also possible to measure the overball size (radius method).

[0047]

According to the first aspect of the present invention, the cylindrical surface of the ball master table serves as the radial receiving reference surface of the tracing stylus ball, and the plane perpendicular to the axis of the drive gear is the axial receiving reference surface of the tracing stylus ball. Therefore, the axial movement of the tracing stylus ball can be restrained and can be grasped as a radial variation on the same circle diameter, and the pitch circle of a bevel gear or the like has a non-cylindrical tooth groove runout of the gear to be measured. Values can be measured with high accuracy. In addition, since the plane perpendicular to the axis of the drive gear rotates continuously with the gear to be measured, the contact point ball does not need to receive the rotational force of the ball master gear directly. It is highly likely. Therefore, it is possible to efficiently and accurately measure the tooth groove runout not only when the gear to be measured is a spur gear but also when it is a bevel gear, and for short time measurement and high frequency use in the case of automatic measurement. Can bear. Further, since the groove of the presser gear holds the measuring element ball through the gap, even if there is an error in the shape of the gear to be measured, mounting position error, etc., the measuring element ball has no gap in each tooth groove of the gear to be measured. It is inserted and reliably received by the cylindrical surface, and the deflection value of the tooth space can be reliably detected by the measuring element ball.

According to the second aspect of the invention, since the drive gear and the pressing gear are tapered gears, interference between these and the gear to be measured can be prevented, and continuous meshing rotation can be ensured.

[Brief description of drawings]

FIG. 1A is a sectional view showing an embodiment of a ball master gear of the present invention. B is the top view.

FIG. 2 is an enlarged sectional view of a main part of the above ball master gear.

FIG. 3A is a front view of an automatic sorter using the same ball master gear as above. B is the top view.

FIG. 4 is a front view of a main part of an automatic sorting machine in which a ball master gear portion is cut away.

5 is a sectional view taken along line VV of FIG.

FIG. 6A is a plan view showing a first example of a conventional tooth groove run-out measuring device. B shows the measurement recording diagram.

FIG. 7A is a sectional view showing a second example of a conventional tooth groove runout measuring device. B shows the measurement recording diagram.

FIG. 8 is a perspective view showing a third example of a conventional tooth groove runout measuring device.

[Explanation of symbols]

 G Gear to be measured 91 Ball master table 91b Cylindrical surface 93 Drive gear 93d Right angle plane 95 Presser gear 95b Groove 95c Gap 96 Stylus ball

Claims (2)

[Claims] 1. A measuring point ball is arranged like a gear around the circumference, and two tooth flanks are measured with the gear to be measured to form a backless point with the measuring point ball for each tooth groove of the gear to be measured. In a ball master gear that reads the point and uses it as the runout value of the tooth groove, a ball having a cylindrical surface that serves as a radial receiving reference surface when the measuring element ball is inserted into the tooth groove of the gear to be measured without a back gap. A master table, and a drive gear provided on one side of the cylindrical surface of the ball master table and having an axis-perpendicular plane which serves as an axial receiving reference surface for the measuring element ball and enables continuous mesh rotation with the gear to be measured. A ball master gear, comprising: a pressing gear which is provided on the other side of the cylindrical surface of the ball master table and which holds the tracing stylus ball through a gap with a gap. 2. The ball master gear according to claim 1, wherein the drive gear and the pressing gear are tapered gears.