JP3133466B2 - Detector connection structure of tire balance measuring device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lower rim mounted on a rim rotation support shaft vertically and rotatably supported by a bearing connected to a detector for detecting a displacement load, and opposing the lower rim. With the upper rim that can be raised and lowered and rotatably provided on the upper side, the test tire is held and rotated by
In a tire balance measuring device, a detector detects a displacement load of a bearing caused by rotation due to an unbalance of the weight of a test tire by a detector, and measures a dynamic balance of the test tire based on the detection result. And a detector connection structure for connecting the bearing and the detector.

[0002]

2. Description of the Related Art Conventionally, as a measuring device for measuring a dynamic balance of a tire, a lower rim mounted on a rim rotation support shaft vertically and rotatably supported by bearings, and a vertically moving upper and lower side facing the lower rim. An upper rim provided rotatably and rotatably holds and rotates the tire to be inspected, and detects a displacement load of each of the upper and lower ends of the bearing with a detector, and calculates a dynamic balance from the detection result. Some are configured. The bearing is supported with high rigidity in directions other than the direction of detecting the displacement load by the detector, and is supported with low rigidity in the direction of detecting the displacement load by the detector so that the detector can detect the displacement load. That is, it is supported so that it can move (vibrate) in the displacement load detection direction by the detector and does not move in other directions as much as possible. The bearing and the detector are firmly connected so that the vibration of the bearing is transmitted to the detector in a good manner.

[0003]

However, it is actually impossible to support the detector so as not to move at all except in the direction of detecting the displacement load by the detector, and the detector detects movement (vibration) other than the detection direction. This causes measurement errors. or,
When the test tire is attached or detached, a vertical impact is applied to the bearing, but this impact acts on the detector, which causes a problem or causes a decrease in measurement accuracy.

[0004]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a tire balance which can efficiently transmit vibration in a direction of detecting a displacement load by a detector and can avoid transmission of vibration in another direction to the detector. It is an object of the present invention to provide a detector connection structure of a measuring device.

[0005]

For this reason, in the detector connection structure of the tire balance measuring device according to the present invention, the bearing and the detector have high rigidity in the detection direction of the detector, and have a high rigidity in a direction other than the detection direction of the detector. Are connected via a low-rigid connection member. Further, the connecting member is configured such that a mounting seat to the bearing is formed at one end of the elongated rod-shaped connecting shaft portion, and a mounting seat to the detector is formed at the other end.

[0006]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view of a tire balance measuring device to which an embodiment of a detector connection structure and a connecting member of the tire balance measuring device according to the present invention is applied, and FIG.
It is a top view corresponding to A sectional drawing. In the illustrated tire balance measuring apparatus, a cylindrical spindle 10 as a rim rotation support shaft having a lower rim 13 fixed to an upper end is rotatably supported by a bearing 12 supported on a frame 11 in a vertical state. An upper rim 14 is provided above the lower rim 13.
Are disposed and supported by a lifting mechanism (not shown).

[0007] The bearing 12 is framed by a torsion bar 15 disposed in parallel (vertically) on both sides of the bearing 12.
1, the upper and lower ends are connected to the frame 11 by torsion bars 16 disposed horizontally in the left-right direction. It is supported with high rigidity, and the front-back direction (FIG.
Of the torsion bars 15 and 16 can be vibrated by elastic deformation of the torsion bars 15 and 16. L-shaped connecting brackets 18 are fixed at one end to both front and rear surfaces of upper and lower ends corresponding to the connection position of the torsion bar 16 of the bearing 12, respectively, and the other end of the connecting bracket 18 and one end of the load cell 17 are connected to each other. They are connected by a joint 19 as a connecting member.

The load cell 17 has a rectangular parallelepiped outer shape, an opening formed in the center in the longitudinal direction, and a strain gauge adhered to the inner surface of a portion thinned by the opening. The amount of deformation of the thin part can be detected by a change in the electric resistance of the strain gauge caused by the deformation of the thin part. One end of the thin part is fixed to the frame 11, and the direction perpendicular to the plane of FIG. It is arranged in parallel with the horizontal torsion bar 16 so that the amount of deformation (up and down direction in FIG. 2) can be detected. As shown in an enlarged view in FIG. 3, the joint 19 has disk-shaped mounting seats 19B, 19B each having a predetermined diameter in a state orthogonal to the connecting shaft 19A, which are integrally formed at both ends of a substantially cylindrical connecting shaft 19A. And the axial direction (buckling direction) of the connecting shaft 19A.
The rigidity is high, and the rigidity is low in the direction in which the connecting shaft 19A is bent, so that the elastic member can be elastically deformed relatively easily.
Incidentally, the vicinity of the mounting seats 19B, 19B of the connecting shaft 19A is gradually thickened like a taper.

Then, one of the mounting seats 19B is connected to the connecting fitting 1
8 and the other end of the mounting seat 19B is fixed to the side surface of the load cell 17 at the other end.
7 and the bearing 12 (connection fitting 18). That is, the joint 19 is fixed to one side surface of the tip of the load cell 17, and the other end of the joint 19 is connected and fixed to the connection fitting 18 fixed to the bearing 12, respectively, so that the joint 19 has a high rigidity direction (connection). Shaft 19A
Of the bearing 12 coincides with the direction in which the rigidity of the bearing 12 supported by the torsion bars 15 and 16 is low. And this can be detected.

The spindle 10 has a support shaft portion 20 supported by a bearing 12, a chuck bracket 30 fixed to a flange portion 21 of the support shaft portion 20 projecting upward from the bearing 12, and Chuck claws 40, 40 as a pair of engagement claws pivotally supported at the lower end, a cylindrical ring shaft 50 connected and fixed to the upper side of the chuck bracket 30, and mounted on the upper end of the ring shaft 50. Guide sleeve 60,
It is constituted by.

The support shaft 20 has a hollow cylindrical shape having a large-diameter flange 21 on which a chuck bracket 30 is mounted at the upper end, and is rotatably supported by the bearing 12 via a bearing. . A pulley 22 is fixed to a lower end projecting below the bearing 12, and an encoder 23 is further mounted below the pulley 22. An operation shaft 70 as an operation shaft is fitted and slidably fitted in the hollow interior in the axial direction. A belt 82 is stretched between the pulley 22 and a pulley 81 fixed to a spindle of a motor 80 which is a rotation drive source (not shown in FIG. 1) provided in parallel with the bearing 12 on the side of the frame 11. And motor 8
0, the pulley 22 (that is, the spindle 1
0) is rotationally driven.

The chuck bracket 30 is fixed to the upper surface of the flange portion 21 of the support shaft portion 20, and a ring shaft 50 is fixed to the upper surface, as shown in FIG. And the chuck pawl 40
Is swingably supported at its lower end. Chuck pawl 40
Although not shown in detail, a lock shaft 9 described later
Reference numeral 0 denotes a shape obtained by vertically dividing a penetrable cylinder into two parts. The two chuck claws 40, 40 are opposed to each other, and are pivotally attached to the chuck bracket 30 at the lower ends thereof.
On the inner periphery of the upper end, two rows of right-angled triangular claws 41 are formed so that the upper surface is directed downward and the lower surface is horizontal and the horizontal lower surface is a predetermined interval (0.5 inch).

Although not shown, a cam follower is rotatably mounted on the chuck pawl 40 at substantially the center in the vertical direction on both front and rear sides parallel to the swing direction thereof, and the cam follower is supported by a support shaft of the spindle 10. Slidably fitted in cam grooves formed in a cam plate (not shown) fixed to the upper end of the operation shaft 70 inserted through the portion 20 and disposed adjacent to the front and rear sides of the chuck pawl 40, respectively. As a result, the swing of the chuck pawl 40 is restricted, and when the operation shaft 70 is located at the lower end of the elevating stroke as shown in the drawing, the chuck pawl 40 is in the upright state. The chuck pawl 40 is swingably operated to the side where the tip is separated.

The operating shaft 70 has a hollow shaft shape and is fitted into the supporting shaft portion 20 of the spindle 10 so as to be slidable in the axial direction by a predetermined stroke. 20 protrudes downward from the lower end thereof, and a spring 72 is provided between the lower end and the support shaft 20.
The operating ring 73 is fixed via the spring 72, and is urged downward by the spring 72. A rotary joint 7 connected to a compressor (not shown) is provided at the lower end.
4 is attached, and compressed air can be supplied to the hollow interior while allowing the operation shaft 70 to rotate.

A drive ring 7 is provided below the operation ring 73.
5 is supported by a spindle of an air cylinder 76 fixed to the frame 11 so as to be able to ascend to a position where it interferes with the operation ring 73 by a predetermined amount.
The operating ring 73 (that is, the operating shaft 70) can be moved upward by a driving ring 75 driven upward by the driving ring 75 against the urging force of the spring 72, and the operating shaft 70 is raised by the air cylinder 76. By being driven, the chuck pawls 40, 40 are driven to swing to the side where their tips are separated.

The ring shaft 50 has a large-diameter cylindrical shape and houses therein the chuck pawl 40 so as to be able to swing by a predetermined amount, and a guide sleeve 60 is mounted on the upper end thereof.
Reference numeral 51 in FIG. 1 denotes a window made of a transparent acrylic resin that is hermetically mounted. The guide sleeve 60 has a small-diameter guide portion 62 formed to project vertically from a flange portion 61 fixed to the upper end of the ring shaft 50.
A liner 63 is fitted and mounted in an insertion hole formed to penetrate through 2 and has a predetermined inner diameter. A vent 61A communicating with the inside and outside of the ring shaft 50 is formed in the flange 61, and the upper surface of the flange 61 is
The lower rim 13 is mounted. The lower rim 13 has a disk shape, and a plurality of (three types in the figure) rims having different diameters are formed in a stepped shape on an outer peripheral portion thereof.

The upper rim 14 is disposed above the lower rim 13 as described above. The upper rim 14 is a disc-shaped body integrally formed with a plurality of rims having different diameters similarly to the lower rim 13, and is fixed via an adapter 93 to a holder 92 supported by a support mechanism (not shown) so as to be able to move up and down. It is provided so as to be able to ascend and descend at a position facing the lower rim 13. Note that the holder 92 is gripped by a clamp provided in the support mechanism and cannot be rotated, and
It becomes rotatable by releasing the grip.
Further, a lock shaft 90 as a fitting shaft fixed to the holder 92 at the upper end thereof is suspended at the center position. The lock shaft 90 can be fitted to the guide portion 62 of the guide sleeve 60 with a predetermined tolerance, and has a tapered upper end corresponding to the hook of the chuck jaw 40 and a lower surface directed toward the center at the tip. Are formed at a distance (0.5 inch) equal to the distance between the claws 41 of the chuck pawl 40.

Here, the engagement projection 9 of the lock shaft 90
1 and the pawl 41 of the chuck pawl 40, the lock rim 90 is inserted through the guide portion 62 of the guide sleeve 60, and the rim width of the tire corresponds to the interval between the plurality of rims of the upper rim 14 and the lower rim 13. Is set so as to correspond to the engageable state. That is, the engaging projections 91 of the lock shaft 90
In a state where the first rim is engaged, the rim distance between the upper rim 14 and the lower rim 13 corresponds to the rim width of the tire that can be supported. When the operating shaft 70 is located at the lower end of the elevating stroke and the chuck pawl 40 is in the vertical state, the pawl 41 of the chuck pawl 40
When the operating shaft 70 is moved up by a predetermined stroke by the driving of the air cylinder 76 to swing the chuck pawl 40 from this state, the engagement of the pawl 41 with the engaging protrusion 91 is started. It is to be released.

In the tire balance measuring device configured as described above, the test tire is held by the lower rim 13 and the upper rim 14 and the balance is measured by the following operation. First, from the state where the lock shaft 90 is fitted into the guide portion 62 of the guide sleeve 60 as shown in FIG.
The operation shaft 70 is driven upward by the driving of the air cylinder 76 to release the engagement between the chuck pawl 40 and the engagement projection 91, and the upper rim 14 is locked by the lock shaft 90 with respect to the lower rim 13 as shown in FIG. Raise it to a position that is far enough apart that it will not interfere with mounting. When the lock shaft 90 is raised, the holder 92 (that is, the lock shaft 90 and the upper rim 14) is clamped and cannot rotate.

Next, after the tire to be tested, which has been transported in a horizontal state by a conveyor (not shown), is placed on the lower rim 13 so that the center thereof is aligned, the upper rim 14 is lowered to lock the lock shaft 90 with the guide sleeve 60. The air cylinder 76 is stopped in a state where the rim interval between the upper rim 14 and the lower rim 13 matches the rim width of the tire to be inspected. Thereby, the spring 72
The operating shaft 70 is lowered by the urging force of the chuck claw 40, and the chuck pawl 40 swings to the side where the tip thereof approaches,
The pawls 41, 41 are engaged with the engaging projections 91 of the lock shaft 90 to securely bite the lock shaft 90, so that the test tire is supported by the upper rim 14 and the lower rim 13. At this time, the engagement protrusion 91 and the claw 41 of the chuck claw 40
Are in the corresponding positions as described above and smoothly engaged. Even when the rim widths of the test tires are different, the engagement protrusions 91 with which the claws 41 of the chuck pawls 40 are displaced can cope with 0.5 inch intervals according to the test tires.

Thereafter, compressed air of a predetermined pressure is supplied into the hollow shaft of the operation shaft 70 via the rotary joint 74. The compressed air passes from inside the hollow shaft of the operation shaft 70 to the inside of the chuck bracket 30 and the ring shaft 50, and passes through the ventilation holes 61 of the flange portion 61 of the guide sleeve 60.
A is supplied into the test tire via A, and the test tire is inflated at a predetermined internal pressure. At this time, the internal pressure of the test tire acts to widen the rim distance between the upper rim 14 and the lower rim 13, but this is surely the engagement between the chuck claw 40 in the engaged state and the engagement protrusion 91 of the lock shaft 90. At the same time, the distance (rim width) between the upper rim 14 and the lower rim 13 is accurately maintained by the engagement between the chuck pawl 40 and the engagement protrusion 91 of the lock shaft 90. Then, the clamp of the lock shaft 90 is released to be rotatable, and the rotation of the motor 80 causes the spindle 10 and the lower rim 1 to rotate.
3. The test tire and the upper rim 14 (holder 92, lock shaft 90) are integrally rotatable and drivable, and are rotated at a predetermined number of revolutions in this state, and the bearing 12 is detected by the load cell 17 during the rotation. The balance of the test tire is measured based on the displacement load and the rotation angle information from the encoder 23.

In this measurement, although the bearing 12 has high rigidity, it can vibrate also in the axial direction of the torsion bars 15 and 16 (that is, in the vertical direction and the direction perpendicular to the plane of FIG. 1). The vibration is in a direction in which the rigidity of the joint 19 is low, is absorbed by the elastic deformation of the connecting shaft 19A, does not reach the load cell 17, and does not cause a detection error. After the measurement is completed, the beat portion of the test tire sticks to the lower rim 13 so that a strong force is required to remove the test tire from the lower rim 13. Although a strong impact force acts on the load cell 17, it is also absorbed by the joint 19 and does not reach the load cell 17, so that it is possible to prevent the accuracy of the load cell 17 from deteriorating due to breakage or excessive input. That is, the joint 19 has high rigidity in the direction of the displacement load of the bearing 12 to be detected and transmits the vibration to the load cell 17 well, and absorbs vibration in directions other than the detection direction by elastic deformation of the connecting shaft 19A. , And does not act on the load cell 17.

[0023]

According to the detector connection structure of the tire balance measuring device according to the present invention as described above, the bearing 12 and the detector have high rigidity in the detection direction of the detector, and the bearing 12 and the detector have a rigidity other than the detection direction of the detector. In the direction, the connection member is connected via a low-rigidity connection member, so that the connection member efficiently transmits vibration in the direction of displacement load detection by the detector, and absorbs vibration in other directions by deformation and detects it. Since no vibration is transmitted to the detector, vibrations other than the detection direction, which is an error component, are not detected, and a highly accurate detection result can be obtained.
In addition, the detector can be protected from an impact applied when the test tire is attached or detached.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a tire balance measuring device to which an embodiment of a detector connection structure of a tire balance measuring device according to the present invention is applied.

FIG. 2 is a plan view corresponding to the AA cross-sectional view of FIG.

FIG. 3 is an enlarged view of a joint.

FIG. 4 is a view showing a state in which an upper rim is retracted upward from FIG. 1;

[Description of Signs] 13 Lower rim 14 Upper rim 19 Joint (connection member) 19A Connection shaft (connection shaft) 19B Mounting seat 20 Spindle (rim rotation support shaft)

Claims (3)

(57) [Claims] 1. A lower rim mounted on a rim rotation support shaft vertically and rotatably supported by a bearing to which a detector for detecting a displacement load is connected, and a vertically movable and rotatable upper side opposed to the lower rim. A freely provided upper rim, holding and rotating the test tire by, detecting the displacement load of the bearing caused by the rotation due to the unbalance of the weight of the test tire by the detector, In a tire balance measuring device that measures a dynamic balance of the test tire based on the detection result, the bearing and the detector have high rigidity in a detection direction of the detector, and a detection direction of the detector. A detector connection structure for a tire balance measuring device, wherein the detector connection structure is connected to the other direction via a low-rigidity connection member. 2. The connecting member, wherein a mounting seat for the bearing is formed at one end of an elongated rod-shaped connecting shaft portion, and a mounting seat for a detector is formed at the other end. The detector connection structure of the tire balance measuring device according to claim 1, wherein: 3. The detector connection structure for a tire balance measuring device according to claim 2, wherein the mounting seat of the connection member is formed as a plane orthogonal to the connection shaft portion.