JP2020106387A - Shape measuring device - Google Patents

Abstract

To provide a shape measuring device that realizes the heightened level and high durability of movement accuracy of a movable element.SOLUTION: The shape measuring device comprises: a movable element that moves in the vertical direction along a drive shaft integrally with a measurement arm; a linkage mechanism for moving a counterweight in a direction opposite the movable element in linkage with the movement of the movable element in the vertical direction; a pair of revolving shafts for sandwiching the movable element and counterweight movement path from the vertical direction and being parallel to a second direction; a sheet winding member that rotates in accordance with the rotation of the revolving shafts; a rope one end of which is wound to the revolving shafts in accordance with the rotation of the revolving shafts and unwound from the revolving shafts in accordance with the rotation of the revolving shafts in a rope unwinding direction opposite a rope winding direction, the other end being connected to the counterweight; a sheet one end of which is wound to a sheet winding member in accordance with the rotation of the revolving shafts in the rope unwinding direction and fed out from the sheet winding member in accordance with the rotation of the revolving shafts in the rope winding direction; and a connecting part for connecting the other ends of both of sheets together.SELECTED DRAWING: Figure 3

Description

The present invention relates to a shape measuring device including a measuring arm that moves in the vertical direction.

Various shapes (roundness, straightness, surface) of the work can be obtained by moving the detector relative to the work while the contact type detector such as a stylus is in contact with the work surface to be measured. Profile measuring machines for measuring roughness (including roughness, waviness, size, etc.) are known. Further, a shape measuring machine that measures various shapes of a work by using a non-contact type detector such as an optical probe instead of the contact type detector is also well known.

Such a shape measuring machine is provided with a linear drive mechanism that vertically moves a measuring arm that holds the detector. As the linear drive mechanism, a ball screw mechanism using a ball screw (see Patent Document 1), a linear motor mechanism using a linear motor (see Patent Document 2), and the like are well known. Then, the linear drive mechanism moves the carriage (movable element) holding the measurement arm in the vertical direction, thereby moving the measurement arm in the vertical direction integrally with the carriage.

The linear drive mechanism is usually covered with a housing (cover) from the viewpoint of safety. In addition, a gap (notch) is formed in the housing along the movement path (movement range) of the measurement arm that moves in the vertical direction. The gaps are formed on the upper side and the lower side of the measurement arm, and the respective gaps are covered with a sheet (screen and cover).

As such a sheet, there is known a so-called bellows type sheet in which one end side is fixed to a carriage and the other end side is fixed to an end portion of the above-described movement path. The bellows-type seat expands and contracts following the vertical movement of the measuring arm to constantly cover the above-mentioned gaps.

Further, Patent Document 3 describes a constant load spring type roll screen device. If this roll screen device is applied to a linear drive mechanism of a shape measuring machine, one end of a sheet is fixed to a carriage and the other end is connected to a constant force spring. In this case, since the sheet is always pulled by the constant force spring with a constant force, one end side of the sheet can be moved following the vertical movement of the measurement arm, and as a result, the above-mentioned gaps are always covered with the sheet. be able to.

JP, 10-154012, A JP, 11-98886, A JP, 2003-301677, A

When a bellows type sheet is used, the amount of expansion and contraction of each sheet above and below the carriage changes as the carriage moves in the vertical direction. Moreover, since the expansion and contraction amounts of the respective sheets are different from each other, the magnitude and direction of the force applied to the carriage from the upper and lower sheets are also different from each other. As a result, the forces applied to the carriage from the upper and lower sheets cannot be balanced, which may adversely affect the movement accuracy (positional accuracy) of the measurement arm and the like. Further, particularly when the linear drive mechanism is a linear motor, since the holding force for holding the position of the carriage is weak, the position of the carriage moves due to the weight of the bellows type sheet and the restoring force (tension, pressing force), etc. As a result, the movement accuracy (positional accuracy) of the carriage may be adversely affected.

Further, when the roll screen device described in Patent Document 3 is used, since the life of the constant load spring is about several thousand to tens of thousands of reciprocations, it is durable when used in a situation where the carriage is frequently moved in the vertical direction. I have a problem.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide a shape measuring device capable of achieving high accuracy in moving the mover and high durability.

A shape measuring device for achieving the object of the present invention is a measurement arm that holds a drive shaft parallel to the vertical direction and a contact type or non-contact type detector, and that is perpendicular to the vertical direction. A measuring arm having an arm body extending in one direction; a mover holding the arm body and moving vertically along the drive shaft together with the measuring arm; A counter weight that is provided in a position displaced in a second direction that is perpendicular to both of the one direction, and that is movable in the up and down direction, connects the mover and the counter weight, and is linked to the up and down movement of the mover. An interlocking mechanism that moves the counterweight in the opposite direction to the mover, a pair of rotary shafts that sandwich the moving path of the mover and the counterweight from above and below, and that is parallel to the second direction, and is provided for each rotary shaft. A sheet winding body that is rotated about a rotation center parallel to the rotation axis according to the rotation of the rotation axis, and a cord provided for each rotation axis. One end side is wound around the rotary shaft in response to the rotation of the rotary shaft in the cord winding direction, and is unwound from the rotary shaft in response to the rotation of the rotary shaft in the cord feeding direction opposite to the cord winding direction. A cord provided with an end side connected to a counterweight, and a sheet provided for each rotating shaft, one end side of which is wound up by a sheet winding body according to the rotation of the rotating shaft in the extending direction of the cord and of the rotating shaft. A connection part that connects the sheet fed from the sheet winding body in accordance with the rotation of the rope winding direction and the other end sides of both of the sheets, and has an insertion opening through which the arm main body part is inserted. And

According to this shape measuring apparatus, by interlocking with the vertical movement of the counterweight to integrally rotate the rotary shaft and the sheet winding body, the connecting portion can be moved vertically with the movable element. ..

In a shape measuring device according to another aspect of the present invention, a cord winding body that is externally fitted to each of the rotating shafts and rotates integrally with the rotating shafts is provided. The cord is wound in accordance with the rotation of the cord winding direction, and the cord is paid out in accordance with the rotation of the rotary shaft in the cord feeding direction. Accordingly, the rotating shaft and the sheet winding body can be integrally rotated in association with the vertical movement of the counterweight.

In the shape measuring device according to another aspect of the present invention, the rope winding body is formed in a taper shape in which the diameter of the rope winding body gradually increases from one direction in the second direction to the other direction. When the body winding body rotates in the rope winding direction, the winding position of the rope body by the rope winding body gradually shifts in one direction, and the rope winding body rotates in the line feeding direction. In this case, the winding position gradually shifts in the other direction. As a result, a minute error that occurs between the amount of winding/unwinding of the rope by the winding member and the amount of winding/winding of the sheet by the sheet winding member is reduced.

In the shape measuring apparatus according to another aspect of the present invention, the sheet winding body is fitted onto the rotation shaft and rotates integrally with the rotation shaft.

In a shape measuring apparatus according to another aspect of the present invention, a drive winding body that is externally fitted to each rotation shaft and rotates integrally with the rotation shaft, wherein the drive winding body is wound with a sheet. And a sheet winding body contacting the driving winding body through the sheet wound around the driving winding body, and the driving winding body is driven by the driving winding body according to the rotation of the driving winding body. And the one end side of the sheet is wound in a roll shape by the sheet winding body that rotates in the opposite direction to the drive winding body in response to the rotation of the rotation shaft in the cord extending direction, and the rotation shaft The sheet is fed from the sheet winding body that rotates in the direction opposite to the driving winding body according to the rotation of the cord winding direction through the driving winding body. As a result, the above-mentioned minute error is reduced.

In the shape measuring apparatus according to another aspect of the present invention, the cord and the counterweight are connected via a tension spring. As a result, the above-mentioned minute error is reduced.

In the shape measuring apparatus according to another aspect of the present invention, the connecting portion is provided separately from the mover. Thereby, the moving accuracy (positional accuracy) of the mover can be improved.

In the shape measuring apparatus according to another aspect of the present invention, the connecting portion is a mover.

INDUSTRIAL APPLICABILITY According to the present invention, it is possible to realize high accuracy in moving the mover and high durability.

It is a side view of a roundness measuring device. It is the front view which looked at the case from the table side. It is the front view which looked at the linear drive mechanism in the housing, the counter weight mechanism, and the roll screen mechanism from the table side. FIG. 4 is an enlarged schematic view of the counterweight, the yarn winding drum, the gut, and the tension spring shown in FIG. 3, as viewed from the arrow A1 direction side in FIG. 3. FIG. 4 is an enlarged schematic view of the sheet winding drum, roll sheet, and connecting portion illustrated in FIG. 3 as viewed from the arrow A2 direction side in FIG. 3. FIG. 11 is an explanatory diagram for explaining the action of the roll screen mechanism when the carriage is moved downward in the Z-axis direction. FIG. 11 is an explanatory diagram for explaining the action of the roll screen mechanism when the carriage is moved upward in the Z-axis direction. FIG. 6 is an explanatory diagram for explaining a change in the outer diameter of a roll sheet wound in a roll on a sheet winding drum. It is an enlarged view of the yarn winding drum of the roll screen mechanism of 2nd Embodiment. It is a schematic diagram of a roll screen mechanism of a 3rd embodiment. It is explanatory drawing for demonstrating the roll screen mechanism of 4th Embodiment. It is explanatory drawing for demonstrating the modification of the rope winding direction and the rope feeding direction.

[First Embodiment]
FIG. 1 is a side view of a roundness measuring device 10 corresponding to the shape measuring machine of the present invention. The X-axis direction (corresponding to the second direction of the present invention), the Y-axis direction (corresponding to the first direction of the present invention), and the Z-axis direction (corresponding to the vertical direction of the present invention) in the drawing are mutually They are orthogonal. Moreover, the X-axis direction and the Y-axis direction are directions parallel to the horizontal direction.

As shown in FIG. 1, the roundness measuring device 10 measures the straightness and roundness (cylindricity) of a cylindrical or cylindrical work W. The roundness measuring device 10 includes a base 12, a table rotating mechanism 14, a table 16, a linear driving mechanism 18, a measuring arm 20, a detector 22, and a housing 24.

The base 12 is a support base (base) that supports each part of the roundness measuring device 10. Although not shown, the table rotation mechanism 14 includes an air bearing that rotatably holds the table 16 about an axis C parallel to the Z-axis direction, and a rotational drive such as a motor that rotates the table 16 about the axis C. And a mechanism. As a result, the table rotating mechanism 14 rotates the table 16 about the axis C.

The table 16 has a disk shape, and is held on the air bearing of the table rotation mechanism 14 so that the center thereof coincides with the axis C. A work W is placed on the upper surface of the table 16. The work W is placed on the upper surface of the table 16 so that the position of the center of its shape substantially coincides with the axis C.

As the linear drive mechanism 18, various known mechanisms such as the ball screw mechanism described in Patent Document 1 or the linear motor mechanism described in Patent Document 2 are used. In the present embodiment, the linear motor mechanism is used. Will be described as an example. As the linear drive mechanism 18, the one described in the specification of Japanese Patent Application No. 2018-17273 filed by the present applicant may be used.

The linear drive mechanism 18 includes a drive shaft 26 (also referred to as a shaft axis or a column) that is a stator and a carriage 28 that is a mover.

The drive shaft 26 is provided on the base 12 at a position shifted from the table 16 in the Y-axis direction, and has a shape extending in the Z-axis direction perpendicular to the base 12. The drive shaft 26 has a structure in which a plurality of permanent magnets (not shown) are joined in a known arrangement.

The carriage 28 has a substantially cylindrical shape into which the drive shaft 26 is inserted, and is supported by the drive shaft 26 so as to be movable in the Z-axis direction in a non-contact manner. The carriage 28 is provided with a plurality of coils spirally wound around the drive shaft 26 along the Z-axis direction. When a current is applied to each coil of the carriage 28, a thrust force (driving force) for moving the carriage 28 along the Z-axis direction is generated by the interaction between the magnetic flux generated from each magnet of the drive shaft 26 and the current flowing through each coil. Force) is generated. Since the structure and function of the linear drive mechanism 18 (linear motor mechanism) are known technology, detailed description thereof is omitted here.

The carriage 28 holds the arm body 20a of the measurement arm 20 movably in the Y-axis direction, and moves integrally with the measurement arm 20 in the Z-axis direction.

The measurement arm 20 includes an arm body portion 20a which is held by the carriage 28 and extends in the Y-axis direction (parallel), and a holding portion which is provided at the tip end side of the arm body portion 20a and holds the detector 22. .. The measuring arm 20 can be appropriately changed in shape of other portions as long as it has the arm body portion 20a extending in the Y-axis direction.

The detector 22 is a contact type having a stylus 22a (also referred to as a stylus or a stylus) and a displacement detection unit such as a differential transformer (not shown), and the stylus that moves back and forth along the Y-axis direction. The displacement of 22a is detected. That is, the detector 22 has sensitivity in the Y-axis direction. Then, the detector 22 outputs a displacement detection signal (electrical signal) indicating the displacement of the stylus 22a to a data processing device (not shown). The detector 22 may be a non-contact type such as an optical probe (laser probe).

When measuring the straightness of the work W, the linear drive mechanism 18 and the measurement arm 20 are driven to bring the stylus 22a into contact with the outer peripheral surface of the work W. Next, the linear drive mechanism 18 is driven to move the carriage 28 in the Z-axis direction, so that the outer peripheral surface of the work W is traced along the Z-axis direction by the stylus 22a. As a result, the detector 22 outputs a displacement detection signal for one trace to a data processing device (not shown). In this case, the data processing device analyzes the detection signal input from the detector 22 by a known method to calculate the straightness of the work W.

When measuring the roundness of the work W, the stylus 22a is brought into contact with the outer peripheral surface of the work W as in the straightness measurement. Next, by rotating the table 16 and the work W by the table rotating mechanism 14, the outer peripheral surface of the work W is traced along the circumferential direction by the stylus 22a. As a result, the detector 22 outputs a displacement detection signal for one rotation of the work W to a data processing device (not shown). In this case, the data processing device analyzes the detection signal input from the detector 22 by a known method to calculate the roundness (cylindricity) of the work W.

FIG. 2 is a front view of the housing 24 as seen from the table 16 side. As shown in FIG. 2, a housing 24 (also referred to as a cover) is provided on the base 12 so as to cover the linear drive mechanism 18, a counterweight mechanism 30 and a roll screen mechanism 40 (see FIG. 3) described later. Has been.

An opening 24a for passing the measurement arm 20 (arm body portion 20a), which is moved in the Z-axis direction by the linear drive mechanism 18, to the outside of the housing 24 is formed on the side surface of the housing 24 facing the table 16. ing. The opening 24a has a substantially rectangular shape extending in the Z-axis direction along the movement path (movement range) of the measurement arm 20 moving in the Z-axis direction.

When the measurement arm 20 moves upward in the Z-axis direction, the gap (space) generated between the measurement arm 20 and the upper end of the opening 24a in the Z-axis direction shrinks in the Z-axis direction, and the measurement arm 20 and the opening 24a in the Z-axis direction. A gap generated between the lower end and the lower end expands in the Z-axis direction. Conversely, when the measurement arm 20 moves downward in the Z-axis direction, the gap generated between the measurement arm 20 and the upper end of the opening 24a in the Z-axis direction expands in the Z-axis direction and the measurement arm 20 and the opening 24a in the Z-axis direction. The gap between the lower end and the lower end shrinks in the Z-axis direction. Then, these gaps are always covered with roll sheets 54A and 54B described later.

FIG. 3 is a front view of the linear drive mechanism 18, the counterweight mechanism 30, and the roll screen mechanism 40 in the housing 24 as viewed from the table 16 side.

As shown in FIG. 3 and FIG. 1 described above, the counterweight mechanism 30 includes a top plate 32, a Z-axis guide 34, a counterweight 36, and an interlocking mechanism 38.

The top plate 32 is fixed to the upper surface of the drive shaft 26. The top plate 32 has a shape extending in the X-axis direction so as to extend in the X-axis direction along the movement path of the measurement arm 20 and the movement path of the counterweight 36 described later.

The Z-axis guide 34 is provided at a position displaced in the X1 direction, which is one direction of the X-axis direction, with respect to the drive shaft 26, and has a shape extending in the Z-axis direction. The lower end of the Z-axis guide 34 in the Z-axis direction is fixed to the base 12, and the upper end of the Z-axis guide 34 is fixed to the top plate 32.

The counterweight 36 is held by the Z-axis guide 34 so as to be movable in the Z-axis direction. That is, the counterweight 36 is held by the Z-axis guide 34 so as to be movable in the Z-axis direction at a position displaced in the X1 direction with respect to the drive shaft 26. The weight of the counterweight 36 is determined based on the weight of each elevating member that ascends and descends in the Z-axis direction along the drive shaft 26 such as the measuring arm 20, the detector 22, and the carriage 28.

The interlocking mechanism 38 connects the carriage 28 and the counterweight 36, and moves the counterweight 36 in the direction opposite to the carriage 28 in conjunction with the movement (elevation) of the carriage 28 in the Z-axis direction. The detailed structure of the interlocking mechanism 38 is a known technique (see, for example, Japanese Patent Application Laid-Open No. 2015-55515), and a detailed description thereof will be omitted here. By thus interlocking the carriage 28 and the counterweight 36, the counterweight 36 can balance the weights of the above-described lifting members.

The roll screen mechanism 40 includes a pair of rotary shafts 42A and 42B, rotary shaft holding members 44A and 44B, yarn winding drums 46A and 46B, gussets 48A and 48B, tension springs 50A and 50B, and a sheet winding drum 52A. , 52B, roll sheets 54A and 54B, and a connecting portion 56.

The pair of rotary shafts 42A and 42B have a shape extending (parallel) in the X-axis direction so as to extend over the movement paths of both the measurement arm 20 and the counterweight 36 described above in the X-axis direction. The rotary shaft 42A is rotatably held by a rotary shaft holding member 44A at a position on the upper side in the Z-axis direction of both moving paths about a rotation center parallel to the X-axis direction. Further, the rotary shaft 42B is rotatably held by a rotary shaft holding member 44B at a position on the lower side in the Z-axis direction of both moving paths about a rotation center parallel to the X-axis direction. As a result, both movement paths are sandwiched by the rotating shafts 42A and 42B from the vertical direction.

A plurality of rotary shaft holding members 44A are provided along the X-axis direction, for example, on the side surface (or the upper surface) of the top plate 32, and rotatably hold the rotary shaft 42A. A plurality of rotation shaft holding members 44B are provided on the upper surface of the base 12 along the X-axis direction, and hold the rotation shaft 42B rotatably.

The yarn winding drums 46A and 46B correspond to the cord winding body of the present invention. The yarn winding drum 46A is externally fitted and fixed to the end of the rotary shaft 42A on the X1 direction side, and rotates integrally with the rotary shaft 42A. The yarn winding drum 46B is externally fitted and fixed to the end of the rotary shaft 42B on the X1 direction side, and rotates integrally with the rotary shaft 42B. The positions of the yarn winding drums 46A and 46B in the X-axis direction and the Y-axis direction are the same (including substantially the same, the same applies hereinafter).

The yarn winding drum 46A winds the below-described teg 48A when it rotates integrally with the rotation shaft 42A in the below-described Tegs winding direction RA1 (corresponding to the cord winding direction of the present invention), and conversely When it is rotated integrally with 42A in the Tegu's feeding direction RA2 (corresponding to the cord feeding direction of the present invention) described later, the Tegu 48A is fed downward in the Z-axis direction. In addition, the yarn winding drum 46B winds the below-described teg 48B when it rotates integrally with the rotary shaft 42B in the below-described teg winding direction RB1 (corresponding to the rope winding direction of the present invention), and conversely. When rotated integrally with the rotary shaft 42B in a Tegs feeding direction RB2 (corresponding to the cord feeding direction of the present invention) described later, the Tegu 48B is fed upward in the Z axis direction.

Tegus 48A and 48B correspond to the cord of the present invention. Note that the cord includes a thread made of a single wire or a twisted wire, a wire, a cord, a cable, a rope, and the like.

One end of the Tegs 48A is fixed to the yarn winding drum 46A, and a tension spring 50A is connected to the other end thereof. Further, one end of the Tegs 48B is fixed to the yarn winding drum 46B, and a tension spring 50B is connected to the other end thereof.

One end of the tension spring 50A is connected to the Tegs 48A and the other end thereof is connected to the upper end portion of the counterweight 36. As a result, the gut 48A and the counterweight 36 are connected via the tension spring 50A. Further, one end of the tension spring 50B is connected to the gut 48B and the other end thereof is connected to the lower end of the counterweight 36. As a result, the gut 48B and the counterweight 36 are connected to each other via the tension spring 50B. As a result, the Tegs 48A and the Tegs 48B are connected via the tension spring 50A, the counterweight 36, and the tension spring 50B.

FIG. 4 is an enlarged schematic view of the counterweight 36, the yarn winding drums 46A and 46B, the gussets 48A and 48B, and the tension springs 50A and 50B shown in FIG. 3 viewed from the arrow A1 direction side in FIG.

As shown in FIG. 4, when the counterweight 36 moves upward in the Z-axis direction via the interlocking mechanism 38, the Tegus 48A is pushed upward in the Z-axis direction via the counterweight 36 and the tension spring 50A. The yarn winding drum 46A is rotated integrally with the rotating shaft 42A in the Tegus winding direction RA1. As a result, the yarn take-up drum 46A winds the gut 48A into a roll. It should be noted that it is preferable to use Tegs 48A (also Tegs 48B) having a strong rigidity so that the Tegs 48A will not be bent between the yarn winding drum 46A and the counterweight 36.

At the same time, when the counterweight 36 moves upward in the Z-axis direction, the bobbin 48B is pulled upward in the Z-axis direction via the counterweight 36 and the tension spring 50B, so that the yarn winding drum 46B is integrated with the rotary shaft 42B. Then, it is rotated in the Tegus feeding direction RB2. As a result, the teg 48B is fed upward from the yarn winding drum 46B in the Z-axis direction. In the present embodiment, the Tegus winding direction RA1 and the Tegus feeding direction RB2 are the same direction.

On the other hand, when the counterweight 36 moves downward in the Z-axis direction via the interlocking mechanism 38, the bobs 48A are pulled downward in the Z-axis direction via the counterweight 36 and the tension spring 50A, so that the yarn winding drum 46A moves. It is rotated integrally with the rotary shaft 42A in the TEGS feeding direction RA2 opposite to the TEGS winding direction RA1 described above. As a result, the teg 48A is fed downward from the yarn winding drum 46A in the Z-axis direction.

At the same time, when the counterweight 36 moves downward in the Z-axis direction, the bobbin 48B is pushed downward in the Z-axis direction via the counterweight 36 and the tension spring 50B, so that the yarn winding drum 46B is integrated with the rotary shaft 42B. Then, it is rotated in the Tegs winding direction RB1 opposite to the Tegs feeding direction RB2. As a result, the yarn take-up drum 46B winds the gut 48B into a roll. In this embodiment, the Tegus winding direction RA1 and the Tegus winding direction RB1 are opposite to each other.

As described above, in the present embodiment, the rotation of the rotary shaft 42A in the Tegs winding direction RA1 and the rotation shaft 42B in the Tegs feeding direction RB2 are performed in accordance with the movement (elevation) of the counterweight 36 in the Z-axis direction. Alternatively, rotation of the rotation shaft 42A in the Tegs feeding direction RA2 and rotation of the rotation shaft 42B in the Tegus winding direction RB1 are performed.

1 and 3, the sheet winding drums 52A and 52B correspond to the sheet winding body of the present invention. The sheet winding drum 52A is externally fitted and fixed to an end portion on the X2 direction side which is the other direction of the rotation shaft 42A in the X axis direction (direction opposite to the X1 direction), and is integrated with the rotation shaft 42A and the yarn winding drum 46A. Rotate to. The sheet winding drum 52B is externally fitted and fixed to the end of the rotating shaft 42B on the X2 direction side, and rotates integrally with the rotating shaft 42B and the yarn winding drum 46B. The positions of the sheet winding drums 52A and 52B in the X-axis direction and the Y-axis direction are the same.

The sheet winding drum 52A winds a roll sheet 54A, which will be described later, when the sheet winding drum 52A rotates integrally with the rotating shaft 42A in the Tegs feeding direction RA2, and conversely, when the sheet winding drum 52A rotates integrally with the rotating shaft 42A in the Tegs winding direction RA1. Then, the roll sheet 54A is fed downward in the Z-axis direction. Further, the sheet winding drum 52B feeds a roll sheet 54B, which will be described later, upward in the Z-axis direction when it rotates integrally with the rotating shaft 42B in the Tegs winding direction RB1, and conversely, integrally with the rotating shaft 42B, the Tegs feeding direction. When it is rotated to RB2, the roll sheet 54B is wound up.

The roll sheet 54A has one end fixed to the sheet winding drum 52A and the other end connected to the connecting portion 56. The roll sheet 54B has one end fixed to the sheet winding drum 52B and the other end connected to the connecting portion 56.

The connecting portion 56 is supported by the roll sheets 54A and 54B at a position shifted in the Y-axis direction (table 16 side) with respect to the carriage 28. That is, the connecting portion 56 is provided separately from the carriage 28. The roll sheet 54A is connected to the upper end of the connecting portion 56, and the roll sheet 54B is connected to the lower end of the connecting portion 56. As a result, the other ends of the roll sheets 54A and 54B are connected to each other via the connecting portion 56. Therefore, the connecting portion 56 moves in the Z-axis direction integrally with the other end sides of both the roll sheets 54A and 54B.

The connecting portion 56 is formed with an insertion opening 56a through which the arm body portion 20a of the measurement arm 20 is inserted. The opening shape of the insertion port 56a is a shape obtained by enlarging the cross-sectional shape of the arm body portion 20a. As a result, the arm body portion 20a is inserted (inserted in a non-contact manner) with a gap in the insertion opening 56a. The connecting portion 56 may be integrally formed with at least one of the roll sheets 54A and 54B.

5 is a view of the sheet winding drums 52A and 52B, the roll sheets 54A and 54B, and the connecting portion 56 shown in FIG. 3 as seen from the arrow A2 direction side in FIG. 3 (the same direction side as FIG. 4 described above). FIG.

As shown in FIG. 5 and FIG. 4 described above, the winding direction of the roll sheet 54A around the sheet winding drum 52A and the winding direction of the Tegs 48A around the yarn winding drum 46A are opposite to each other. Further, the winding direction of the roll sheet 54B with respect to the sheet winding drum 52B and the winding direction of the Tegs 48B with respect to the yarn winding drum 46B are opposite to each other.

When the sheet winding drum 52A rotates in the Tegs winding direction RA1, the roll sheet 54A is fed downward from the sheet winding drum 52A in the Z-axis direction, and conversely, when the sheet winding drum 52A rotates in the Tegs feeding direction RA2, the sheet winding is performed. The roll sheet 54A is wound into a roll by the take-up drum 52A. When the sheet winding drum 52B rotates in the Tegs winding direction RB1, the roll sheet 54B is fed upward from the sheet winding drum 52B in the Z-axis direction, and conversely, when the sheet winding drum 52B rotates in the Tegs feeding direction RB2. The roll sheet 54B is wound into a roll by the sheet winding drum 52B.

When the sheet winding drum 52A rotates in the Tegs winding direction RA1 and the sheet winding drum 52B rotates in the Tegs feeding direction RB2 in accordance with the movement of the counterweight 36 on the upper side in the Z-axis direction, the connecting portion 56 rotates. , And moves to the lower side in the Z-axis direction integrally with the other ends of the roll sheets 54A and 54B. On the contrary, in the connecting portion 56, the sheet take-up drum 52A rotates in the Tegs feeding direction RA2 and the sheet take-up drum 52B moves in the Tegs winding direction RB1 in accordance with the movement of the counterweight 36 on the lower side in the Z-axis direction. When rotated, the roll sheets 54A and 54B move integrally with the other ends of the roll sheets 54A and 54B upward in the Z-axis direction. As a result, the connecting portion 56 moves in the direction opposite to the counterweight 36, that is, in the same direction as the carriage 28, in conjunction with the movement of the counterweight 36 in the Z-axis direction.

At this time, the moving speed of the connecting portion 56 in the Z-axis direction (moving amount per unit time) matches the moving speed of the carriage 28 in the Z-axis direction (moving amount per unit time). As described above, the outer diameters of the yarn winding drums 46A and 46B and the sheet winding drums 52A and 52B are adjusted. As a result, the connecting portion 56 moves in the Z-axis direction integrally with the carriage 28. As a result, the state where the connecting portion 56 faces the carriage 28 is always maintained before and after the movement of the carriage 28 in the Z-axis direction.

In addition, due to various factors (for example, the difference between the thickness of the tegs 48A and 48B and the thickness of the roll sheets 54A and 54B), the winding of the tegs 48A and 48B by the yarn winding drums 46A and 46B when the rotary shafts 42A and 42B rotate. A minute error occurs between the amount of take-up/take-out and the amount of take-up/take-up of the roll sheets 54A, 54B by the sheet take-up drums 52A, 52B. This minute error is absorbed by the tension springs 50A and 50B described above.

FIG. 6 is an explanatory diagram for explaining the action of the roll screen mechanism 40 when the carriage 28 is moved downward in the Z-axis direction.

As shown in FIG. 6, when the carriage 28 moves downward in the Z axis direction, the counterweight 36 moves upward in the Z axis direction via the interlocking mechanism 38. In accordance with the movement of the counterweight 36, the yarn winding drum 46A and the rotation shaft 42A are integrally rotated in the Tegs winding direction RA1 via the Tegs 48A and the like, and the yarn winding drum 46B and the rotation are rotated via the Tegs 48B and the like. The shaft 42B is integrally rotated in the Tegu's feeding direction RB2.

Then, the sheet winding drum 52A rotates integrally with the rotating shaft 42A in the Tegs winding direction RA1, whereby the roll sheet 54A is fed from the sheet winding drum 52A downward in the Z-axis direction. At the same time, the sheet winding drum 52B rotates in the Tegs feeding direction RB2 integrally with the rotating shaft 42B, so that the sheet winding drum 52B winds the roll sheet 54B into a roll. As a result, the connecting portion 56 moves integrally with the other ends of the roll sheets 54A and 54B toward the lower side in the Z-axis direction at the same speed as the carriage 28.

FIG. 7 is an explanatory diagram for explaining the operation of the roll screen mechanism 40 when the carriage 28 is moved upward in the Z axis direction.

As shown in FIG. 7, when the carriage 28 moves upward in the Z axis direction, the counterweight 36 is moved downward in the Z axis direction via the interlocking mechanism 38. In accordance with the movement of the counterweight 36, the yarn winding drum 46A and the rotation shaft 42A are integrally rotated in the Tegs feeding direction RA2 via the Tegs 48A and the yarn winding drum 46B and the rotation shaft are rotated via the Tegs 48B and the like. 42B is integrally rotated in the Tegus winding direction RB1.

Then, the sheet winding drum 52A rotates integrally with the rotation shaft 42A in the Tegs feeding direction RA2, whereby the roll sheet 54A is wound into a roll by the sheet winding drum 52A. At the same time, the sheet winding drum 52B rotates integrally with the rotary shaft 42B in the Tegs winding direction RB1, whereby the roll sheet 54B is fed from the sheet winding drum 52B upward in the Z-axis direction. As a result, the connecting portion 56 moves integrally with the other ends of the roll sheets 54A and 54B toward the upper side in the Z-axis direction at the same speed as the carriage 28.

In this way, the state in which the connecting portion 56 faces the carriage 28 is maintained before and after the movement of the carriage 28 in the Z-axis direction. As a result, before and after the movement of the carriage 28 in the Z-axis direction, the gap (space) between the measurement arm 20 and the upper end of the opening 24a (see FIG. 2) in the Z-axis direction is covered with the roll sheet 54A. The state in which the gap formed between the measurement arm 20 and the lower end of the opening 24a in the Z-axis direction is covered with the roll sheet 54B is maintained.

[Effects of this embodiment]
As described above, in the present embodiment, the connecting portions 56 are connected to the carriage 28 by integrally rotating the rotating shafts 42A and 42B and the sheet winding drums 52A and 52B in conjunction with the movement of the counterweight 36 in the Z-axis direction. It can be moved integrally in the Z-axis direction. As a result, unlike the case where a bellows type sheet that applies a restoring force to the carriage 28 is used, it is possible to prevent the movement accuracy (position accuracy) of the carriage 28 or the like from being adversely affected. Therefore, even when the linear drive mechanism 18 has a low position holding force of the carriage 28 like a linear motor, it is possible to prevent the movement accuracy of the carriage 28 and the like from being adversely affected. Further, since a mechanism such as a constant load spring having a limited number of times of use is not used, high durability of the roll screen mechanism 40 is secured. As a result, it is possible to improve the accuracy of movement of the carriage 28 and ensure high durability of the roll screen mechanism 40.

Further, in the present embodiment, since the connecting portion 56 (roll sheets 54A and 54B) is provided separately from the carriage 28, it is possible to prevent a force from being applied to the carriage 28 from the connecting portion 56 and the like. It As a result, even when the linear driving mechanism 18 has a low position holding force of the carriage 28 like a linear motor, it is possible to prevent the movement accuracy of the carriage 28 and the like from being adversely affected.

Further, in this embodiment, since the rotary shafts 42A and 42B and the sheet winding drums 52A and 52B are integrally rotated in association with the movement of the counterweight 36 in the Z-axis direction, the sheet winding drums 52A and 52B are rotated. There is no need to provide an independent drive source for.

[Second Embodiment]
FIG. 8 is an explanatory diagram for explaining changes in the outer diameters of the roll sheets 54A and 54B wound in a roll shape on the sheet winding drums 52A and 52B.

As shown in FIG. 8, the diameter of the sheet winding drums 52A and 52B is D, the thickness of the roll sheets 54A and 54B is t, and the number of windings of the roll sheets 54A and 54B with respect to the sheet winding drums 52A and 52B is n. In this case, the outer diameter of the roll-shaped roll sheets 54A and 54B is represented by "D+2nt". That is, as the number of turns n increases, the outer diameter increases by 2t. Therefore, when the thickness of the tegs 48A, 48B is smaller than t, the winding amount/feeding amount of the tegs 48A, 48B by the yarn winding drums 46A, 46B and the sheet winding drums 52A, 52B are increased as the winding number n increases. The minute error caused between the roll-out amount and the roll-up amount of the roll sheets 54A and 54B due to is large.

Further, in the first embodiment, the tension springs 50A and 50B absorb the above-mentioned minute error, but in the second embodiment, the roll screen mechanism 40 is provided with means for reducing the occurrence of the minute error.

FIG. 9 is an enlarged view of the yarn winding drums 60A and 60B of the roll screen mechanism 40 of the second embodiment. The roll screen mechanism 40 according to the second embodiment is different from the roll screen mechanism 40 according to the first embodiment except that it has thread winding drums 60A and 60B having a different shape from the thread winding drums 46A and 46B according to the first embodiment. The configuration is basically the same as 40. Therefore, the same functions or configurations as those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

The yarn winding drums 60A and 60B are formed in a tapered shape whose diameter gradually increases from one direction in the X-axis direction (here, either the X1 direction or the X2 direction is possible) to the other direction. When the yarn winding drums 60A and 60B are rotated in the Tegus winding directions RA1 and RB1, respectively, the winding positions of the Tegs 48A and 48B by the yarn winding drums 60A and 60B are located on one side in the X-axis direction (small diameter side). ). On the contrary, when the yarn winding drums 60A and 60B are rotated in the Tegus feeding directions RA2 and RB2, respectively, the winding positions of the tegs 48A and 48B by the yarn winding drums 60A and 60B are the other side (larger direction) in the X-axis direction. It gradually shifts toward the radial side).

In order to gradually shift the winding positions of the tegs 48A, 48B in the X-axis direction in accordance with the rotation of the yarn winding drums 60A, 60B, a spiral groove or the like is formed on the outer peripheral surface of the yarn winding drums 60A, 60B. Good.

As described above, in the second embodiment, the winding positions of the tegs 48A, 48B by the yarn winding drums 60A, 60B are set in the other direction of the X-axis (larger diameter) in accordance with an increase in the outer diameter of the roll-shaped roll sheets 54A, 54B. Can be shifted to the side). Further, in the second embodiment, the winding positions of the tegs 48A, 48B by the yarn winding drums 60A, 60B are set in one direction (small diameter side) in the X axis direction according to the decrease in the outer diameter of the roll-shaped roll sheets 54A, 54B. It can be shifted. As a result, the outer diameters of the roll sheets 54A and 54B wound around the sheet winding drums 52A and 52B and the outer diameters of the tegs 48A and 48B wound around the yarn winding drums 60A and 60B can be matched. As a result, the occurrence of the minute error described above is reduced, so that the movement accuracy of the carriage 28 is ensured.

[Third Embodiment]
FIG. 10 is a schematic view of the roll screen mechanism 40 of the third embodiment. In the second embodiment described above, the yarn winding drums 60A and 60B reduce the occurrence of the minute errors described above, but the roll screen mechanism 40 of the third embodiment reduces the occurrence of the minute errors described above in the sheet winding. It is provided with take-off mechanisms 70A and 70B.

The roll screen mechanism 40 of the third embodiment has basically the same configuration as the roll screen mechanism 40 of the first embodiment except that the sheet winding mechanisms 70A and 70B are provided. Therefore, the same functions or configurations as those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

As shown in FIG. 10, the sheet winding mechanism 70A includes a rotary shaft holding member 72A, a drive drum 74A, a guide holding member 76A, a Y-axis guide 78A, a winding drum holding member 80A, a compression coil spring 82A, and a sheet winding drum. 52A. The sheet winding mechanism 70B includes a rotary shaft holding member 72B, a drive drum 74B, a guide holding member 76B, a Y-axis guide 78B, a winding drum holding member 80B, a compression coil spring 82B, and a sheet winding drum 52B.

The rotary shaft holding member 72A is provided on the top end of the top plate 32 on the table 16 side, and rotatably holds the rotary shaft 42A. The rotary shaft holding member 72B is provided on the upper surface of the base 12 and holds the rotary shaft 42B rotatably. The positions of the rotary shafts 42A and 42B in the Y-axis direction are the same.

The drive drums 74A and 74B correspond to the drive winding body of the present invention. The drive drum 74A is externally fitted and fixed to the end of the rotary shaft 42A on the X2 direction side (see FIG. 3), and rotates integrally with the rotary shaft 42A and the yarn winding drum 46A. The drive drum 74B is externally fitted and fixed to the end of the rotary shaft 42B on the X2 direction side, and rotates integrally with the rotary shaft 42B and the yarn winding drum 46B. The roll sheet 54A is wound around the drive drum 74A, and the roll sheet 54B is wound around the drive drum 74B.

The guide holding member 76A is provided on the upper surface of the top plate 32 and at a position shifted in the Y-axis direction with respect to the rotary shaft holding member 72A. The guide holding member 76B is provided on the upper surface of the base 12 and at a position shifted in the Y-axis direction with respect to the rotary shaft holding member 72B.

The Y-axis guides 78A and 78B have a shape extending in a direction parallel to the Y-axis direction. The Y-axis guides 78A and 78B are configured by, for example, upper and lower guides arranged at intervals in the Z-axis direction. Two sets of Y-axis guides 78A (upper and lower guides) are provided in the X-axis direction so as to sandwich a sheet winding drum 52A, which will be described later, and Y-axis guides 78B (upper and lower guides) are provided in the X-axis direction, which will be described later. Two sets are provided so as to sandwich the drum 52B.

One end of the Y-axis guide 78A in the Y-axis direction is fixed to the rotary shaft holding member 72A, and the other end of the Y-axis guide 78A in the Y-axis direction is fixed to the guide holding member 76A. Further, one end of the Y-axis guide 78B in the Y-axis direction is fixed to the rotary shaft holding member 72B, and the other end of the Y-axis guide 78B in the Y-axis direction is fixed to the guide holding member 76B.

The take-up drum holding member 80A is movably supported in the Y-axis direction along the Y-axis guide 78A for each pair of two Y-axis guides 78A spaced in the X-axis direction. The take-up drum holding member 80B is movably supported in the Y-axis direction along the Y-axis guide 78B for each pair of two Y-axis guides 78B spaced in the X-axis direction. Then, each winding drum holding member 80A rotatably holds the sheet winding drum 52A, and each winding drum holding member 80B rotatably holds the sheet winding drum 52B.

The compression coil spring 82A is externally fitted to the Y-axis guide 78A between the guide holding member 76A and the winding drum holding member 80A, and biases the winding drum holding member 80A toward the drive drum 74A. The compression coil spring 82B is externally fitted to the Y-axis guide 78B between the guide holding member 76B and the winding drum holding member 80B, and urges the winding drum holding member 80B toward the drive drum 74B. As a result, the sheet winding drum 52A is biased toward the driving drum 74A, and the sheet winding drum 52B is biased toward the driving drum 74B.

The sheet winding drum 52A of the third embodiment is rotatably held between the pair of winding drum holding members 80A, and the sheet winding drum 52B of the third embodiment is arranged between the pair of winding drum holding members 80B. It is rotatably held in. The positions of the two Y-axis guides 78A are adjusted so that the positions of the sheet winding drum 52A and the driving drum 74A coincide with each other, and the sheet winding drum 52B and the driving drum 74B move in the X-axis direction. The positions of the pair of Y-axis guides 78B are adjusted so that the positions match.

The sheet winding drum 52A comes into contact with the driving drum 74A via the roll sheet 54A wound around the driving drum 74A by the bias of the compression coil spring 82A via the winding drum holding member 80A. Therefore, the sheet winding drum 52A rotates in the opposite direction to the drive drum 74A in response to the rotation of the drive drum 74A.

Further, the sheet winding drum 52B comes into contact with the driving drum 74B via the roll sheet 54B wound around the driving drum 74B by the bias of the compression coil spring 82B via the winding drum holding member 80B. Therefore, the sheet winding drum 52B rotates in the opposite direction to the drive drum 74B in response to the rotation of the drive drum 74B.

One end side of the roll sheet 54A of the third embodiment is wound around the driving drum 74A and then fixed to the sheet winding drum 52A. Therefore, when the drive drum 74A rotates in the Tegs feeding direction RA2, the roll sheet 54A is pulled upward by the drive drum 74A in the Z-axis direction and is fed toward the sheet winding drum 52A. Then, the sheet winding drum 52A is rotated by the driving drum 74A in the direction opposite to the driving drum 74A, that is, in the Tegs winding direction RA1. As a result, the sheet winding drum 52A winds the roll sheet 54A sent from the driving drum 74A into a roll.

Conversely, when the drive drum 74A rotates in the Tegs winding direction RA1, the drive drum 74A rotates the sheet winding drum 52A in the opposite direction to the drive drum 74A, that is, in the Tegs feeding direction RA2. Therefore, the drive drum 74A pulls out the roll sheet 54A from the sheet take-up drum 52A and feeds the pulled roll sheet 54A downward in the Z-axis direction.

One end of the roll sheet 54B of the third embodiment is wound around the drive drum 74B and then fixed to the sheet winding drum 52B. Therefore, when the drive drum 74B rotates in the Tegus feeding direction RB2, the roll sheet 54B is pulled downward by the drive drum 74B in the Z-axis direction and is fed toward the sheet winding drum 52B. Then, the sheet winding drum 52B is rotated by the driving drum 74B in a direction opposite to the driving drum 74B, that is, in the Tegs winding direction RB1. As a result, the sheet winding drum 52B winds the roll sheet 54B sent from the drive drum 74B into a roll.

Conversely, when the drive drum 74B rotates in the Tegs winding direction RB1, the sheet winding drum 52B is rotated by the drive drum 74B in the opposite direction to the driving drum 74B, that is, in the Tegs feeding direction RB2. Therefore, the drive drum 74B pulls out the roll sheet 54B from the sheet take-up drum 52B and feeds the pulled roll sheet 54B upward in the Z-axis direction.

As described above, in the third embodiment, the sheet winding drums 52A and 52B and the drive drums 74A and 74B are separately provided, so that the outer diameters of the drive drums 74A and 74B are always constant. Therefore, the feed amount/take-up amount of the roll sheet 54A by the drive drum 74A and the sheet take-up drum 52A and the feed amount/take-up amount of the roll sheet 54B by the drive drum 74B and the sheet take-up drum 52B are always constant. Become. As a result, it is possible to reduce a minute error between the take-up amount/take-out amount of the tegs 48A, 48B and the take-up amount/take-up amount of the roll sheets 54A, 54B, so that the movement accuracy of the carriage 28 is ensured. To be done.

[Fourth Embodiment]
FIG. 11 is an explanatory diagram for explaining the roll screen mechanism 40 of the fourth embodiment. In the first embodiment, the other ends of the roll sheets 54A and 54B are connected to each other by the connecting portion 56 that is provided separately from the carriage 28. However, as shown in FIG. In the embodiment, the other ends of both the roll sheets 54A and 54B are connected to each other via the carriage 28.

The roll screen mechanism 40 of the fourth embodiment has basically the same configuration as the roll screen mechanism 40 of the first embodiment, except that the carriage 28 functions as the connecting portion of the present invention. Therefore, the same functions or configurations as those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted. Further, reference numeral 90 in the drawing is an insertion port provided in the carriage 28 and through which the arm main body portion 20a of the measurement arm 20 is inserted.

A connecting portion 92A that is connected to the other end side of the roll sheet 54A is provided on the upper end portion of the carriage 28 of the fourth embodiment. Further, a connecting portion 92B that is connected to the other end side of the roll sheet 54B is provided at the lower end portion of the carriage 28 of the fourth embodiment.

As described above, in the fourth embodiment, the other ends of the roll sheets 54A and 54B are connected to each other via the carriage 28. Therefore, similarly to the first embodiment, before and after the movement of the carriage 28 in the Z-axis direction. Thus, the state where the gap of the opening 24a is covered with the roll sheets 54A and 54B is maintained. As a result, the same effect as the first embodiment can be obtained. In order to improve the movement accuracy (positional accuracy) of the carriage 28 and the like, it is preferable to provide the connecting portion 56 separated from the carriage 28 as in the first embodiment.

[Other]
FIG. 12 is an explanatory diagram for explaining a modified example of the Tegus winding directions RA1, RB1 and the Tegus feeding directions RA2, RB2. In the above embodiment, the Tegus winding directions RA1 and RB1 are opposite to each other, and the Tegus feeding directions RA2 and RB2 are opposite to each other. On the other hand, as shown in FIG. 12, the winding direction of the Tegs 48A with respect to the yarn winding drum 46A and the Tegus winding directions RA1 and RB1 are the same as each other and the Tegs feeding directions RA2 and RB2 are the same. The winding direction of the teg 48B with respect to the yarn winding drum 46B may be adjusted. In this case, the winding direction of the roll sheet 54A with respect to the sheet winding drum 52A and the winding direction of the roll sheet 54B with respect to the sheet winding drum 52B are similarly adjusted.

In each of the above-described embodiments, the rotating shafts 42A and 42B can rotate independently of each other. For example, the rotating shafts 42A and 42B are bridged with an endless belt, or both are connected via a gear train (not shown). For example, both may be rotated synchronously. As a result, the rotary shaft 42A is reliably rotated in the Tegus winding direction RA1 in conjunction with the upward movement of the counterweight 36 in the Z-axis direction, or is interlocked with the downward movement of the counterweight 36 in the Z-axis direction. The shaft 42B can be reliably rotated in the Teguth winding direction RB1.

In each of the above-described embodiments, as an example of the shape measuring apparatus that measures the shape of the work W, the roundness measuring apparatus 10 that measures the roundness and straightness of the work W has been described as an example. The present invention can be applied to a shape measuring device for measuring other shapes such as parallelism, squareness, surface roughness, waviness, and size of the workpiece W.

10... Roundness measuring device,
12... Base,
18... Linear drive mechanism,
20... Measuring arm,
20a... arm body,
24... Case,
26... Drive shaft,
28... Carriage,
30... Counterweight mechanism,
36...Counter weight,
38... interlocking mechanism,
40...Roll screen mechanism,
42A, 42B... rotary shaft,
46A, 46B... yarn winding drum,
48A, 48B...Tegus,
50A, 50B... tension spring,
52A, 52B... Sheet winding drum,
524, 54B... Roll sheet,
56... connecting part,
56a... insertion port,
60A, 60B... Thread winding drum,
70A, 70B... Sheet winding mechanism,
74A, 74B... Drive drum,
92A, 92B... Connection part

Claims (8)

A drive axis parallel to the vertical direction,
A measurement arm that holds a contact-type or non-contact-type detector, and a measurement arm that has an arm body portion that extends in a first direction perpendicular to the vertical direction,
A mover which holds the arm body and moves in the up-down direction along the drive shaft integrally with the measurement arm;
A counter weight that is provided in a position displaced in a second direction perpendicular to both the vertical direction and the first direction with respect to the drive shaft and is movable in the vertical direction;
An interlocking mechanism that connects the mover and the counterweight, and moves the counterweight in a direction opposite to that of the mover in conjunction with the vertical movement of the mover;
A pair of rotary shafts sandwiching the moving path of the mover and the counterweight from the vertical direction and parallel to the second direction;
A sheet winding body provided for each of the rotating shafts, wherein the sheet winding body rotates around a rotation center parallel to the rotating shaft according to the rotation of the rotating shaft,
A cord provided for each of the rotating shafts, wherein one end side is wound around the rotating shaft according to rotation of the rotating shaft in the winding direction and the winding direction of the rotating shaft is A cord that is fed from the rotating shaft in accordance with the rotation in the opposite cord feeding direction, and the other end side is linked to the counterweight,
A sheet provided for each of the rotating shafts, one end side of which is wound around the sheet winding body according to the rotation of the rotating shaft in the rope winding-out direction and which is in the winding body winding direction of the rotating shaft. A sheet that is unwound from the sheet winding body according to rotation,
A connecting portion that connects the other end sides of both of the sheets, the connecting portion having an insertion opening through which the arm body portion is inserted,
A shape measuring device provided with. For each of the rotating shafts, a cord winding body that is externally fitted to the rotating shaft and rotates integrally with the rotating shaft,
The rope winding body winds the rope according to rotation of the rotary shaft in the rope winding direction, and unwinds the rope according to rotation of the rotary shaft in the rope feeding direction. Item 1. The shape measuring device according to item 1. The rope winding body is formed in a taper shape in which the diameter of the rope winding body gradually increases from one direction of the second direction to the other direction,
When the rope winding body is rotated in the rope winding direction, the winding position of the rope by the rope winding body is gradually displaced toward the one direction, and the rope winding body is The shape measuring device according to claim 2, wherein the winding position is gradually shifted toward the other direction when the winding position is rotated in the feeding direction. The shape measuring device according to any one of claims 1 to 3, wherein the sheet winding body is fitted onto the rotation shaft and rotates integrally with the rotation shaft. A drive winding body that is externally fitted to the rotation shaft for each rotation shaft and rotates integrally with the rotation shaft, the drive winding body having the sheet wound around the drive winding body,
The sheet winding body contacts the driving winding body via the sheet wound around the driving winding body, and is driven by the driving winding body according to the rotation of the driving winding body. It is rotated in the opposite direction to the winding body,
One end side of the sheet is wound into a roll by the sheet winding body that rotates in a direction opposite to the drive winding body in accordance with the rotation of the rotation shaft in the cord extending direction, and the rotation shaft includes: 4. The sheet is fed out from the sheet winding body that rotates in a direction opposite to the driving winding body according to the rotation of the rope winding direction through the driving winding body. The shape measuring device described in 1. The shape measuring apparatus according to claim 1, wherein the cord body and the counterweight are connected to each other via a tension spring. The shape measuring device according to claim 1, wherein the connecting portion is provided separately from the mover. The shape measuring apparatus according to claim 1, wherein the connecting portion is the mover.

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