JP2008026014A - Spline outer diameter measuring instrument - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spline outer diameter measuring instrument capable of precisely measuring though it is simple. <P>SOLUTION: When a male shaft 101 being the measurement object is arranged between a notch 204a of a first measurement block 204 and a notch 207a of a second measurement block 207, a third cylinder pin 215 is held between a first ball groove 104 and the notch 207a of the second measurement block 207, a first cylindrical pin 213 is arranged between a first ball groove 103 and a measurement piece 210a of a dial gauge 210; a fourth cylindrical pin 216 is kept between a second ball groove 103 and the notch 204a of the first measurement block 204, a second cylinder pin 215 is made to be arranged between the second ball groove 104 and the measuring piece 210a of the dial gauge 210, therefore the outer diameters of over pins of different two points can be measured at once measurement. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a spline outer diameter measuring device, for example, a measuring device capable of measuring the outer diameter of a spline having a ball groove constituting a torque transmission component.

For example, a vehicular steering mechanism is provided with a telescopic spline shaft, which functions to absorb axial displacement generated when the vehicle travels and not transmit the displacement or vibration on the steering wheel. ing. Further, the spline shaft functions so as to allow the steering wheel when the driver moves the shaft in the axial direction in order to obtain an optimal position for driving the vehicle (see Patent Document 1).
JP 2005-313691 A

  Like a ball spline shaft, a mechanically constrained structure by interposing a ball or a cylindrical pin between a spline male shaft having a ball groove on the outer periphery and a spline female shaft having a ball groove on the cylindrical inner surface When assembling machine parts, the standard ball and pin are used for temporary assembly, and then the backlash in the circumferential direction of the spline is measured, and the ball and pin dimensions with the desired machine performance are determined from the measurement results. After the ball used for measurement is taken out again, the assembly has been performed using the ball diameter selected from the measurement result.

  9-11 is a figure which shows the state which measures the outer diameter of the spline male shaft by a prior art. Here, as shown in FIG. 9, when the spline male shaft MS has a pair of symmetrically formed ball grooves BG on the outer periphery, a cylindrical pin CP is engaged in the opposing ball groove BG. It is sufficient to measure the width dimension OPD (overpin outer diameter) with a micrometer or the like.

  However, some types of ball spline shafts have ball grooves BG and BG 'having different shapes as shown in FIG. Here, when the ball grooves having the same shape are not arranged symmetrically across the axis, the exact dimensions cannot be measured by the measurement of FIG. Therefore, as shown in FIG. 10, cylindrical pins CP and CP ′ having different diameters are engaged and arranged in the ball grooves BG and BG ′, and the pin circumscribed circle is obtained by calculation based on the relative positional relationship to calculate the overpin outer diameter. Trying to get.

  However, in actuality, when the positional relationship between the cylindrical pins CP and CP ′ engaged with the ball grooves BG and BG ′ is to be accurately measured, a measurement block having a V-shaped notch as shown in FIG. It is conceivable to mount the spline male shaft MS incorporating the cylindrical pins CP and CP ′ on the MB and measure the position of the vertex of the cylindrical pin CP or CP ′ with a dial gauge DG or the like. It is necessary to perform the measurement by exchanging 'and changing the posture of the spline male shaft MS, which is troublesome.

  The present invention has been made in view of the problems of the prior art, and an object of the present invention is to provide a spline outer diameter measuring device that is simple and can be measured with high accuracy.

The spline outer diameter measuring device of the present invention is a spline outer diameter measurement that measures the outer diameter of a male spline shaft constituting a ball spline shaft, which includes a first ball groove and a second ball groove having different groove widths. In the vessel
A first measuring block having a V-shaped notch;
A first holding member attached to the first measurement block;
A first cylindrical pin having an outer diameter D1 and a second cylindrical pin having an outer diameter D2, which are movably supported by the first holding member;
A second measurement block having a V-shaped notch disposed to face the first measurement block; a second holding member attached to the second measurement block;
A third cylindrical pin having an outer diameter D1 and a fourth cylindrical pin having an outer diameter D2, which are movably supported by the second holding member;
First measuring means comprising a probe for measuring the position of the first cylindrical pin with respect to the second measuring block;
And a second measuring means having a probe for measuring the position of the fourth cylindrical pin with respect to the first measuring block,
When the spline male shaft to be measured is arranged between the cutout of the first measurement block and the cutout of the second measurement block, the third cylindrical pin is connected to the first ball groove and the The first cylindrical pin is disposed between the first ball groove and the measuring element of the first measuring means, and is held between the notch of the second measuring block and the second measuring block. The cylindrical pin is held between the second ball groove and the notch of the first measurement block, and the fourth cylindrical pin is the measuring element of the second ball groove and the second measuring means. It is arranged between the two.

  According to the present invention, when the spline male shaft to be measured is disposed between the cutout of the first measurement block and the cutout of the second measurement block, the third cylindrical pin is The first cylindrical pin is disposed between the first ball groove and the measuring element of the first measuring means. The first cylindrical pin is held between the first ball groove and the notch of the second measuring block. The second cylindrical pin is held between the second ball groove and the notch of the first measurement block, and the fourth cylindrical pin is connected to the second ball groove and the second Therefore, it is possible to easily measure two different overpin outer diameters in one measurement.

  It is preferable that the number of the first cylindrical pin and the number of the fourth cylindrical pin is one, and the number of the second cylindrical pin and the number of the third cylindrical pin are two.

  Providing biasing means for driving the first measurement block and the second measurement block in the approaching direction causes the first measurement block and the second measurement block to approach each other with a predetermined pressure. As a result, the play between the ball groove and the cylindrical pin is eliminated, and accurate measurement can be performed.

  Hereinafter, a steering apparatus according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a side view of a steering mechanism portion of an automobile using a ball spline shaft as a telescopic shaft for vehicle steering.

  In FIG. 1, a steering shaft upper part 3 is attached to a vehicle body VB via an upper bracket 1 and a lower bracket 2. The steering shaft upper part 3 includes a steering column 3A and a steering shaft 3B rotatably held by the steering column 3A. A steering wheel 5 is attached to the upper end of the steering shaft 3B. A steering shaft lower portion 7 is connected to the lower end of the steering shaft 3B via a universal joint 6.

  A pinion shaft 9 is connected to the steering shaft lower portion 7 via a steering shaft joint 8, and the pinion shaft 9 is further connected to a steering rack shaft 12. The steering rack shaft 12 is supported by a steering rack support member 13 fixed to the vehicle body VB ′ via an elastic body 11.

  Here, the steering shaft upper portion 3 and the steering shaft lower portion 7 use the vehicle steering telescopic shaft (hereinafter referred to as the telescopic shaft) according to the embodiment of the present invention. The lower portion 7 of the steering shaft is a fitting of a spline male shaft (hereinafter abbreviated as a male shaft) and a spline female shaft (hereinafter abbreviated as a female shaft). Such a steering shaft lower portion 7 is required to have a performance that absorbs the displacement in the axial direction generated when the vehicle travels and does not transmit the displacement or vibration on the steering wheel 5. In such a performance, the vehicle body has a sub-frame structure, and the vehicle body VB to which the steering shaft upper part 3 is fixed and the vehicle body VB ′ to which the steering rack support member 13 is fixed are separated. This is particularly required in the case of a structure in which the rack support member 13 is fastened and fixed to the vehicle body VB ′ via an elastic body 11 such as rubber.

  Further, when the steering shaft joint 8 is fastened to the pinion shaft 9 at the time of assembly or maintenance, the operator needs to expand and contract because the telescopic shaft is once contracted and then fitted to the pinion shaft 9 and fastened. There is a case. Furthermore, the steering shaft upper part 3 at the upper part of the steering mechanism is also one in which a male shaft and a female shaft are fitted. The steering shaft upper part 3 is optimal for a driver to drive a vehicle. In order to obtain the position, the function of moving the position of the steering wheel 5 in the axial direction and adjusting the position is required, so the function of expanding and contracting in the axial direction is required. In all the cases described above, it is possible to reduce the rattling noise of the fitting portion on the telescopic shaft, to reduce the rattling on the steering wheel 5, and to reduce the sliding resistance when sliding in the axial direction. Required.

  FIG. 2 is a longitudinal sectional view of the telescopic shaft for vehicle steering according to the embodiment of the present invention. 3 is a cross-sectional view of the configuration of FIG. 2 taken along the line III-III and viewed in the direction of the arrow. FIG. 4 is a perspective view of a leaf spring that is an elastic body.

  As shown in FIG. 2, the telescopic shaft 110 for vehicle steering includes a male shaft 101 and a female shaft (also referred to as a spline female shaft) 102 that are non-rotatable and slidable in the axial direction. As shown in FIG. 3, three axial grooves (ball grooves) 103 that are equally arranged at intervals of 120 degrees (phase) in the circumferential direction are formed on the outer peripheral surface of the male shaft 101. Correspondingly, three axial grooves (ball grooves) 115 that are equally distributed at 120 degree intervals (phases) in the circumferential direction are formed to extend on the inner peripheral surface of the female shaft 102.

  A plurality of rigid spherical bodies 107 (second key components) that roll between the ball groove 103 of the male shaft 101 and the ball groove 105 of the female shaft 102 when the shafts 101 and 102 move relative to each other in the axial direction. Rolling elements or balls) are movably interposed. Note that the ball groove 105 of the female shaft 102 has a substantially arc-shaped cross section or a Gothic arch shape. The ball grooves 103 and 105 constitute a second group of ball grooves.

  The ball groove 103 of the male shaft 101 has a substantially trapezoidal cross section, and has a pair of inclined planar side surfaces 103a and a bottom surface 103b formed flat between the pair of planar side surfaces 103a. A leaf spring 109 for contacting and preloading the spherical body 107 is interposed between the ball groove 103 of the male shaft 101 and the spherical body 107.

  As shown in FIG. 4, the leaf spring 109 constituting the preload structure has a substantially arc-shaped spherical body side contact portion 109a that contacts the spherical body 107 at two points, and a predetermined circumferential direction with respect to the spherical body side contact portion 109a. The groove surface side contact portion 109b, which is bent at a distance and can contact the planar side surface 103a of the ball groove 103 of the male shaft 101, and the spherical body side contact portion 109a and the groove surface side contact portion 109b are mutually connected. And an urging portion 109c bent so as to be elastically urged in a direction away from each other, and a flat bottom surface 109d facing the flat bottom surface 103b of the ball groove 103.

  As shown in FIG. 3, the urging portion 109c has a substantially U shape and is bent in a substantially arc shape, and the sphere-side contact portion 109a and the groove are formed by the urging portion 109c having the bent shape. The surface side contact portions 109b can be elastically biased so as to be separated from each other.

  A minute gap (Δ1) is set between the urging portion 109 c or the groove surface side contact portion 109 b and the planar side surface 103 a of the ball groove 103.

  Further, when the leaf spring 109 is bent, the tip of the groove surface side contact portion 109b is bent in the arrow (G) direction so as not to contact the planar side surface 103a of the ball groove 103 as shown in FIG. Yes.

  The largest outer portion of the R shape of the bent portion (the biasing portion 109 c or the groove surface side contact portion 109 b) is set so as to be closest to the planar side surface 103 a of the ball groove 103.

  This is to make the thickness of the bent portion (the urging portion 109c or the groove surface side contact portion 109b) of the leaf spring 109 constant at any location. This is because if the tip of the bent portion (the biasing portion 109c or the groove surface side contact portion 109b) hits unevenly at each location, the torsional rigidity of the preload portion is not stable.

  As shown in FIGS. 3 and 4, in this embodiment, the spherical body side contact portion 109 a that contacts the spherical body 107 is formed in a substantially arc shape larger than the radius of the spherical body 107. Thereby, a contact surface pressure with the spherical body 107 can be lowered rather than a planar shape.

  As shown in FIG. 3, three ball grooves 104 that are equally arranged at intervals of 120 degrees in the circumferential direction (phase) are formed to extend on the outer peripheral surface of the male shaft 101. Correspondingly, three ball grooves 106 that are equally arranged at intervals of 120 degrees in the circumferential direction (phase) are formed to extend on the inner peripheral surface of the female shaft 102.

  A plurality of rigid cylindrical bodies 108 (first key) that slide between the ball groove 104 of the male shaft 101 and the ball groove 106 of the female shaft 102 when the shafts 101 and 102 move relative to each other in the axial direction. A sliding body or needle roller, which is a part, is interposed with a minute gap. These ball grooves 104 and 106 are a first group of ball grooves and have a substantially arc-shaped cross section or a Gothic arch shape.

  A minute gap (Δ2) is set between the cylindrical body 108 and the ball groove 106 of the female shaft 102. However, the ball groove 104 of the male shaft 101, the cylindrical body 108, and the ball groove 106 of the female shaft 102 may always be in contact with each other in the axial direction.

  In FIG. 2, a small diameter portion 101 a is formed at the end of the male shaft 101. The small-diameter portion 101a is provided with a stopper plate 111 that restricts the movement of the cylindrical body 8 in the axial direction. The stopper plate 111 includes an axial preload elastic body 112 (ie, a disc spring) and a pair of flat plates 113 and 113 (ie, plain washers) that sandwich the axial preload elastic body 112.

  In the present embodiment, the stopper plate 111 is fitted to the small diameter portion 101a in the order of the flat plate 113, the axial preloading elastic body 112, and the flat plate 113, and is firmly fixed to the small diameter portion 101a by caulking. Thereby, the stopper plate 111 is fixed in the axial direction. The fixing method of the stopper plate 111 is not limited to caulking, but may be a retaining ring, a screwing means, a push nut, or the like. Further, the stopper plate 111 is configured so that the flat plate 113 is brought into contact with the cylindrical body 108 and can be appropriately preloaded by the axial preloading elastic body 112 so as not to move the cylindrical body 108 in the axial direction.

  In the present embodiment, the six ball grooves 105 and 106 of the female shaft 102 are coaxial with the six ball grooves 103 and 104 on the outer peripheral surface of the male shaft 101 in the axial direction via gaps in the radial direction. Six substantially arc-shaped protrusions 115 formed in the above are fitted.

  Therefore, when the spherical body 107 and the cylindrical body 108 are dropped or damaged from the male shaft 101 for some reason, the projection 115 of the male shaft 101 is fitted into the ball grooves 105 and 106 of the female shaft 102, Thereby, the male shaft 101 and the female shaft 102 can transmit torque, and can play the role of a fail-safe function.

  At this time, since a gap is provided between the ball grooves 105 and 106 and the protruding portion 115, the driver can feel rattling in the steering wheel 5, and malfunction of the steering system, etc. Can be sensed.

  Further, since the protrusion 115 of the male shaft 101 is coaxial with the spherical body 107 and the cylindrical body 108 in the axial direction, it also serves as a stopper for restricting the movement of the spherical body 107 and the cylindrical body 108 in the axial direction. The possibility of the body 107 and the cylindrical body 108 being detached can be reduced, and the fail-safe function can be further improved.

  Further, since the protruding portion 115 of the male shaft 101 is coaxial with the spherical body 107 and the cylindrical body 108 in the axial direction, the radial dimension of the male shaft 101 and the female shaft 102 can be reduced to achieve compactness. it can.

  Further, a lubricant may be applied between the ball groove 103 of the male shaft 101, the ball groove 105 of the female shaft 102, the leaf spring 109, and the spherical body 107. A lubricant may also be applied between the ball groove 104 of the male shaft 101, the cylindrical body 108, and the ball groove 106 of the female shaft 102.

  In the telescopic shaft configured as described above, the spherical body 107 is interposed between the male shaft 101 and the female shaft 102, and the spherical body 107 is preloaded to the extent that the female shaft 102 is not rattled by the leaf spring 109. Therefore, rattling between the male shaft 101 and the female shaft 102 can be reliably prevented, and when the male shaft 101 and the female shaft 102 move relative to each other in the axial direction, there is no stability. It is possible to slide with the sliding load.

  Next, the spline outer diameter measuring device for measuring the spline outer diameter of the spline female shaft of the telescopic shaft according to the present embodiment will be described. 5 is a front sectional view of the spline outer diameter measuring device, FIG. 6 is a view of the configuration of FIG. 5 cut along the VI-VI line and viewed in the direction of the arrow, and FIG. 7 is a spline outer diameter measurement. 8 is a view showing the periphery of the holding member of the vessel, and FIG. 8 is a view of the configuration of FIG. 7 cut along the line VIII-VIII and viewed in the direction of the arrow, with the male shaft 101 to be measured interposed Shown in state.

  In FIG. 5, a lower stage 203 is supported on a base 201 via a pillar portion 202. A first measurement block 204 is mounted on the lower stage 203 with the V-shaped notch 204a facing upward. The first measurement block 204 has a through-hole 204b at the bottom of the notch 204a. A dial gauge 205 as a first measuring means is attached to the lower surface of the lower stage 203 on the lower surface of the first measuring block 204, and the measuring element 205a passes through the through hole 204b and protrudes into the notch 204a. ing.

  A second measurement block 207 is supported by an upper stage 206 fixed to the base 201 by a frame (not shown) so as to be movable in the vertical direction with high accuracy by two linear guide bearings 208. Between the upper stage 206 and the second measurement block 207, spring members 209, which are urging means for urging the second measurement block 207 toward the first measurement block 204, are respectively arranged.

  The second measurement block 207 faces the V-shaped notch 204a of the first measurement block 204 so that the V-shaped notch 207a faces downward. The second measurement block 207 has a through hole 207b at the bottom of the notch 207a. A dial gauge 210 as a second measuring means is attached to the upper surface of the second measurement block 207 on the upper surface side of the upper stage 206, and the measuring element 210a passes through the through hole 207b and enters the notch 207a. It protrudes. Note that the lock is released by turning the handle 220 so that the second measurement block 207 approaches the first measurement block 204.

  In FIG. 5, a pair of first holding members 211 and 211 are disposed at both upper ends of the first measurement block 204. The first holding members 211 and 211 having the same shape are formed of a semicircular plate material, and as shown in FIG. 8, a concave portion 211a is formed on the flat upper surface side. In addition, three bag holes 211b, 211c, and 211d are formed along the edge of the recess 211a.

  Here, the inner diameter of the bag hole 211c is smaller than the bag holes 211b and 211d having the same inner diameter. A second cylindrical pin 212 having an outer diameter D1 is disposed between the holding members 211 and 211 so that the reduced diameter portions 212a and 212a at both ends are inserted into the bag holes 211b and 211d. The inner diameters of the bag holes 211b and 211d are larger than the outer diameters of the reduced diameter portions 212a and 212a, and the second cylindrical pin 212 can move relative to the first holding members 211 and 211 within the range of the difference. It has become. Further, the first cylindrical pins 213 having an outer diameter D2 smaller than the outer diameter D1 are arranged between the first holding members 211 and 211 so that the reduced diameter portions 213a and 213a at both ends are inserted into the bag hole 211c. Yes. The inner diameter of the bag hole 211c is larger than the outer diameter of the reduced diameter portions 213a and 213a, and the first cylindrical pin 213 is movable with respect to the first holding members 211 and 211 within the range of the difference. ing.

  Similarly, in FIG. 5, a pair of second holding members 214 and 214 are arranged at both upper ends of the second measurement block 207. The second holding members 214 and 214 having the same shape are formed of a semicircular plate material, and as shown in FIG. 8, a recess 214a is formed on the flat lower surface side. Further, three bag holes 214b, 214c, and 214d are formed along the edge of the recess 214a. In addition, it is preferable to form reliefs 214e and 214f on the outer sides of the bag holes 214b and 214d because interference with the male shaft 101 to be measured can be avoided.

  Here, the inner diameter of the bag hole 214c is larger than the bag holes 214b and 214d having the same inner diameter. A fourth cylindrical pin 215 having an outer diameter D2 is disposed between the second holding members 214 and 214 so that the reduced diameter portions 215a and 215a at both ends are inserted into the bag holes 214b and 214d. The inner diameters of the bag holes 214b and 214d are larger than the outer diameters of the reduced diameter portions 215a and 215a, and the third cylindrical pin 215 can move relative to the second holding members 214 and 214 within the range of the difference. It has become. Further, a third cylindrical pin 216 having an outer diameter D1 larger than the outer diameter D2 is disposed between the second holding members 214 and 214 so that the reduced diameter portions 216a and 216a at both ends are inserted into the bag hole 214c. Yes. The inner diameter of the bag hole 214c is larger than the outer diameter of the reduced diameter portions 216a and 216a, and the fourth cylindrical pin 216 is movable with respect to the holding members 214 and 214 within the range of the difference.

  The measurement using the spline outer diameter measuring device concerning this Embodiment is demonstrated. First, the handle 220 is operated to raise the second measurement block 207 so as to be separated from the first measurement block 204. Thereafter, the male shaft 101 to be measured is inserted between the notch 207a of the second measurement block 207 and the notch 204a of the first measurement block 204. When the handle 220 is further operated, the second measurement block 207 approaches the first measurement block 204 due to the biasing force or gravity of the spring member 209. At this time, as shown in FIG. 8, the cylindrical pins 212 and 216 having the outer diameter D1 are engaged with the wide second ball groove 103 of the male shaft 101, and the outer diameter of the narrow first ball groove 104 is engaged. The cylindrical pins 213 and 215 of D2 are engaged.

  Here, since the second cylindrical pins 212 and 212 are stably supported on both slopes of the V-shaped notch 204a of the first measurement block 204, the fourth cylindrical pin 216 is supported by the upper dial gauge 210. By measuring the height position, the relative positional relationship between the second cylindrical pins 212 and 212 and the fourth cylindrical pin 216 can be accurately measured, thereby calculating the overpin diameter OPD2 (see FIG. 2). Can be sought.

  On the other hand, since the third cylindrical pins 215 and 215 are stably supported on both slopes of the V-shaped notch 207a of the second measurement block 207, the lower dial gauge 205 is used for the first cylindrical pin 213. By measuring the height position, it is possible to accurately measure the relative positional relationship between the third cylindrical pins 215 and 215 and the first cylindrical pin 213, thereby obtaining the overpin diameter OPD1 (see FIG. 2) by calculation. be able to.

  According to the present embodiment, when the male shaft 101 to be measured is disposed between the notch 204a of the first measurement block 204 and the notch 207a of the second measurement block 207, the third cylindrical pin 215 is provided. Is held between the first ball groove 104 and the notch 207 a of the second measurement block 207, and the first cylindrical pin 213 is interposed between the first ball groove 103 and the probe 210 a of the dial gauge 210. The second cylindrical pin 215 is held between the second ball groove 103 and the notch 204a of the first measurement block 204, and the fourth cylindrical pin 216 is held in the second ball groove 104. Since it is arranged between the dial gauge 210 and the probe 210a of the dial gauge 210, it is possible to measure two different overpin outer diameters in one measurement.

  As described above, the present invention has been described in detail with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be appropriately changed and improved without departing from the spirit thereof. Of course there is.

1 is a side view of a steering mechanism portion of an automobile to which a telescopic shaft for vehicle steering according to an embodiment of the present invention is applied. It is a longitudinal cross-sectional view of the telescopic shaft for vehicle steering which concerns on embodiment of this invention. It is sectional drawing which cut | disconnected the structure of FIG. 2 by the III-III line | wire and looked at the arrow direction. It is a perspective view of the leaf | plate spring which is an elastic body. It is front sectional drawing of a spline outer diameter measuring device. It is the figure which cut | disconnected the structure of FIG. 5 by the VI-VI line and looked at the arrow direction. It is a figure which shows the periphery of the holding member of a spline outer diameter measuring device. It is the figure which cut | disconnected the structure of FIG. 7 by the VIII-VIII line, and looked at the arrow direction. It is a figure which shows the state which measures the outer diameter of the spline male shaft by a prior art. It is a figure which shows the state which measures the outer diameter of the spline male shaft by a prior art. It is a figure which shows the state which measures the outer diameter of the spline male shaft by a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Upper bracket 2 Lower bracket 3 Steering shaft upper part 3A Steering column 3B Steering shaft 5 Steering wheel 6 Universal joint 7 Steering shaft lower part 8 Steering shaft joint 9 Pinion shaft 11 Elastic body 12 Steering rack shaft 13 Steering rack support member 101 Male shaft 101a Small diameter Part 102 Female shaft 103 Ball groove 103a Flat side surface 103b Bottom surface 104 Ball groove 105 Ball groove 106 Ball groove 107 Spherical body 108 Column body 109 Leaf spring 109a Spherical body side contact portion 109b Groove surface side contact portion 109c Energizing portion 109d Bottom surface 110 Expansion / contraction Shaft 111 Stopper plate 112 Axial direction preload elastic body 113 Flat plate 115 Protrusion 201 Base 202 Column 203 Lower stage 204 First Fixed block 204a Notch 204b Through hole 205 Dial gauge 205a Measuring element 206 Upper stage 207 Second measuring block 207a Notch 207b Through hole 208 Linear guide bearing 209 Spring member 210 Dial gauge 210a Measuring element 211 Holding member 211a Recessed part 211b Bag hole 211c Bag Hole 212 Second cylindrical pin 212a Reduced diameter portion 213 First cylindrical pin 213a Reduced diameter portion 214 Holding member 214a Recess 214b Bag hole 214c Bag hole 214e Escape 215 Third cylindrical pin 215a Reduced diameter portion 216 Fourth cylindrical pin 216a Reduced diameter portion 220 Handle OPD1 Overpin diameter OPD2 Overpin diameter VB, VB '

Claims (3)

In a spline outer diameter measuring device for measuring an outer diameter of a spline male shaft constituting a ball spline shaft, comprising a first ball groove and a second ball groove having different groove widths,
A first measuring block having a V-shaped notch;
A first holding member attached to the first measurement block;
A first cylindrical pin having an outer diameter D1 and a second cylindrical pin having an outer diameter D2, which are movably supported by the first holding member;
A second measurement block having a V-shaped notch disposed to face the first measurement block; a second holding member attached to the second measurement block;
A third cylindrical pin having an outer diameter D1 and a fourth cylindrical pin having an outer diameter D2, which are movably supported by the second holding member;
First measuring means comprising a probe for measuring the position of the first cylindrical pin with respect to the second measuring block;
And a second measuring means having a probe for measuring the position of the fourth cylindrical pin with respect to the first measuring block,
When the spline male shaft to be measured is arranged between the cutout of the first measurement block and the cutout of the second measurement block, the third cylindrical pin is connected to the first ball groove and the The first cylindrical pin is disposed between the first ball groove and the measuring element of the first measuring means, and is held between the notch of the second measuring block and the second measuring block. The cylindrical pin is held between the second ball groove and the notch of the first measurement block, and the fourth cylindrical pin is the measuring element of the second ball groove and the second measuring means. Spline outer diameter measuring device, characterized in that it is arranged between and.   2. The spline exterior according to claim 1, wherein each of the first cylindrical pin and the fourth cylindrical pin is one, and each of the second cylindrical pin and the third cylindrical pin is two. Diameter measuring instrument. The spline outer diameter measuring device according to claim 1, further comprising an urging unit that drives the first measurement block and the second measurement block in a direction approaching each other.

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