JP2019144068A - Unloading load measurement device of stud pin - Google Patents

Abstract

An object of the present invention is to measure a detachment load of a stud pin in a direction other than the axial direction. A stud pin detachment load measuring device (1) includes a tire support (10) for supporting a pneumatic tire (8) having a stud pin (7) embedded therein, a load cell (64) disposed behind the stud pin (7), a stud pin (7) and a load cell. A connection member 66 connecting the stud pins 7 to the rear of the pneumatic tire 8 via the connection member 66 to measure a detachment load by the load cell 64. The load cell 64 is configured so that the position in the left-right direction can be adjusted so as to face the stud pin 7 located apart from the tire axis TC in the left-right direction. [Selection] Figure 2

Description

  The present invention relates to a stud pin pull-out load measuring device.

  A pneumatic tire having a stud pin embedded in a tread portion is known. The stud pin is embedded in a stud pin hole formed in the tread portion, and is held by a pressing force by the inner peripheral wall surface. In some cases, the resistance of a stud pin from coming out from a stud pin hole is evaluated by a pull-out load when the stud pin is pulled out from a pneumatic tire.

  FIG. 11 is a diagram conceptually illustrating a method for measuring a pull-out load of a stud pin according to a conventional example. As shown in FIG. 11, the pull-out load of the stud pin is not evaluated in a state where the pneumatic tire 150 in which the stud pin 100 is embedded is attached to an actual vehicle, but is evaluated as a single tire. Specifically, a hook 120 attached to the top of the stud pin 100 by, for example, screwing is pulled in the axial direction of the stud pin 100, and the load load when the stud pin 100 is pulled out is measured by the load measuring device 130. To do. Based on the measured pull-out load of the stud pin, the pull-out resistance of the stud pin 100 is evaluated.

  However, in the state where the tire is mounted on the actual vehicle, the stud pin has a force acting in the axial direction, a force in the tangential direction (tire circumferential direction) from the road surface, and in the tire width direction during turning. Force acts. For this reason, for example, when the stud pin is difficult to pull out in the axial direction while it is easy to pull out in the tire circumferential direction, the evaluation based on the pulling-out load in the axial direction may not be able to accurately evaluate the stud pin pull-out resistance in the actual vehicle. is there.

  The present invention has been made in view of the above problems, and an object thereof is to provide a stud pin drop load measuring device capable of measuring a stud pin drop load in a direction other than the axial direction.

The present invention
A tire support that supports a pneumatic tire with stud pins embedded therein;
For the pneumatic tire, a load measuring instrument disposed at a position separated in a second direction orthogonal to the first direction, which is the extending direction of the tire axis,
A connection member for connecting the load measuring instrument and the stud pin in the second direction;
In the state where the pneumatic tire is supported by the tire support portion, the load measuring device is separated from the tire support portion in the second direction, and the stud pin is connected to the pneumatic tire via the connection member. A stud pin pull-out load measuring device, in which a load drop at the time of withdrawal from the stud pin is measured by the load measuring instrument,
A direction perpendicular to each of the first direction and the second direction is a third direction.
When the tire support part side is viewed in the second direction from the load measuring instrument side, the load measuring instrument faces the stud pin positioned away from the tire axis in the third direction. The position in three directions can be adjusted.

  According to the present invention, the position of the load measuring instrument in the third direction is adjusted so that the load measuring instrument is positioned corresponding to the stud pin positioned away from the tire axis in the third direction when viewed from the second direction. . Here, since the stud pin is disposed at a position separated from the tire axis in the third direction when viewed from the second direction, the axial direction of the stud pin extending in the radial direction of the pneumatic tire is directed toward the tire inner diameter side. Inclining toward the tire axis with respect to the second direction.

  As a result, the connecting member is disposed to extend in the second direction so as to have an angular difference with respect to the axial direction of the stud pin. As a result, the stud pin is pulled out in the second direction inclined from the axial direction, and the pull-out load of the stud pin in the inclined second direction is measured. In other words, the pull-out load of the stud pin can be measured in a direction different from the radial direction in the portion where the stud pin is embedded.

  Preferably, when the tire support part side is viewed from the load measuring instrument side in the second direction, the load measuring instrument is positioned opposite to both ends in the third direction of the tire from a position facing the tire axis. Up to this point, the position in the third direction can be adjusted.

  According to this configuration, when the load measuring unit is disposed at a position facing the tire axis, it is possible to measure the slipping load in the axial direction of the stud pin (that is, the radial direction with respect to the tire). In addition, when the load measuring unit is disposed at a position facing both ends of the pneumatic tire in the third direction, it is possible to measure the pull-out load of the stud pin in the tire circumferential direction. That is, when the stud pin is arranged at an arbitrary position in the third direction of the pneumatic tire when viewed from the second direction, the load of the stud pin is measured in an arbitrary direction from the radial direction to the tire circumferential direction. can do.

  Preferably, the tire support portion is configured to rotate the pneumatic tire supported here around the tire axis and to hold the pneumatic tire at a desired rotation position.

  According to this configuration, the stud pin can be easily arranged at a position spaced in the third direction from the tire axis when viewed from the second direction with the pneumatic tire attached to the tire support portion.

Preferably, the apparatus further includes a movement amount measuring unit that measures a movement amount of the load measuring instrument in the second direction,
The movement amount measuring unit measures the movement amount in synchronization with the measurement of the dropout load by the load measuring device.

  According to this configuration, by measuring the pull-out load and displacement of the stud pin in synchronization, when the displacement is small, it can be judged that the stud pin hole has high rigidity and the stud pin holding force is high, and the displacement is large. However, if there is a holding force, it can be determined that the stud pin hole bottom is well engaged and the stud pin holding force is high. In addition, when the displacement is large and the pull-out load is small, it can be determined that the rigidity of the land portion where the stud pin is embedded is low, so the stud pin is embedded in the portion of the land portion where the rigidity is high. By changing to, the pull-out load of the stud pin can be improved. That is, the buried position of the stud pin in the land portion can be evaluated.

  Preferably, the tire support portion is configured to be rotatable around a first axis parallel to the third direction.

  According to this configuration, the connecting member can be inclined in the tire width direction with respect to the stud pin by rotating the tire support portion around the first axis. Thereby, the pull-out load of the stud pin can be measured in the direction inclined in the tire width direction.

  Preferably, the tire support portion includes a first axis first rotation position in which the tire axis extends in the first direction, and a first axis second rotation in which the tire axis extends in the second direction. The rotation about the first axis is fixed at the position.

  According to this configuration, by positioning the tire support portion at the first shaft second rotation position, the stud pin pull-out load can be measured in the tire width direction perpendicular to the axial direction.

  Preferably, the tire support portion can be held at an arbitrary rotation position between the first axis first rotation position and the first axis second rotation position around the first axis. It is configured.

  According to this configuration, the pull-out load of the stud pin can be measured in an arbitrary direction from the radial direction to the tire width direction. By rotating the tire support around the first axis, it is possible to realize a tire posture that simulates the camber angle when the first direction is the vertical direction of the actual vehicle, and the stud pin is pulled out in a state closer to the actual vehicle mounted state. The load can be measured.

  Preferably, the tire support portion is configured to be rotatable around a second axis parallel to the first direction.

  According to this configuration, the connecting member can be inclined in the tire circumferential direction and / or the tire width direction with respect to the axial direction of the stud pin by rotating the tire support portion around the second axis. Thereby, the pull-out load of the stud pin can be measured in a direction inclined in the ground plane.

  Preferably, the tire support portion includes a second axis first rotation position in which the tire axis extends in the second direction, and a second axis second rotation in which the tire axis extends in the third direction. The rotation around the second axis is fixed at the position.

  According to this configuration, by positioning the tire support portion at the second shaft second rotation position, it is possible to measure the pull-out load of the stud pin in the direction inclined in the tire circumferential direction.

  Preferably, the tire support portion is configured to be fixed at an arbitrary rotation position between the second shaft first rotation position and the second shaft second rotation position around the second axis. Has been.

  According to this configuration, the pull-out load of the stud pin can be measured in any direction from the tire width direction to the tire circumferential direction. In addition, by rotating the tire support portion around the second axis, it is possible to realize a tire posture that simulates the slip angle and the time of steering, and it is possible to measure the pull-out load of the stud pin in a state closer to the actual vehicle mounted state.

  According to the stud pin drop load measuring device according to the present invention, the stud pin drop load can be measured in a direction other than the axial direction.

FIG. 3 is a side view of the stud pin pull-out load measuring apparatus according to the first embodiment. The top view of FIG. The top view which shows the measurement of the pulling-out load of the stud pin in various positions. The side view of the falling load measuring device of the stud pin concerning a 2nd embodiment. The top view which shows the periphery of the tire support part which concerns on the modification of 2nd Embodiment. The side view which shows the pulling-out load measurement of a stud pin when a tire support part is located in the vicinity of the 1st axis | shaft 2nd rotation position. The top view of the measuring device of the pull-out load of the stud pin concerning a 3rd embodiment. The side view which shows the periphery of the tire support part which concerns on the modification of 3rd Embodiment. The side view which shows the periphery of the tire support part which concerns on the further modification of 3rd Embodiment. The top view which shows the removal load measurement of a stud pin when a tire support pillar is located in the vicinity of the 2nd axis | shaft 1st rotation position. FIG. 6 is a plan view showing a stud pin pull-out load measurement when a tire support column is positioned in the vicinity of a second shaft second rotation position. The conceptual diagram which shows the measuring method of the pull-out load of the stud pin which concerns on a prior art example.

  Embodiments according to the present invention will be described below with reference to the accompanying drawings. In addition, the following description is only illustrations essentially and does not intend restrict | limiting this invention, its application thing, or its use. Further, the drawings are schematic, and the ratio of each dimension is different from the actual one.

(First embodiment)
FIG. 1 is a side view of a stud pin drop load measuring device 1 according to an embodiment of the present invention, and FIG. 2 is a plan view of the same. In the following description, the up-down direction and the left-right direction in FIG. 1 are referred to as the up-down direction and the front-rear direction, respectively, and the left-right direction and the up-down direction in FIG. Each is called.

  As shown in FIG. 1, the falling load measuring device 1 includes a device frame 2 extending in the front-rear direction, a tire support portion 10 disposed at the front end portion, and a load measurement disposed at the rear end portion of the device frame 2. Part 30. The pneumatic tire 8 in which the stud pin 7 (see FIG. 2) is embedded is supported by the tire support portion 10 in a posture in which the tire axis TC extends in the vertical direction, and the pull-out load of the stud pin 7 from the pneumatic tire 8 is loaded. It is measured by the measuring unit 30.

  Referring also to FIG. 2, the apparatus frame 2 has a pair of left and right main frames 3 extending in the front-rear direction, and a pair of left and right front pillars 4 extending upward at each front end.

  The tire support part 10 is attached between a pair of left and right front pillars 4 and extends forward, a tire support pillar 12 extending upward from the front end part, and a tire support pillar at the upper end part. A tire fixing hub 13 rotatably provided to the tire support pillar 12 and a brake device 14 fixed to the upper portion of the tire support pillar 12 via a bracket are provided. The 1st housing | casing 11 is being fixed to the front pillar 4 so that relative displacement is impossible.

  The tire fixing hub 13 has a disk-like shape whose axial center extends in the vertical direction, and a brake disk 15 having an enlarged diameter is integrally provided on the lower surface thereof. On the upper end surface of the tire fixing hub 13, the pneumatic tire 8 is fixed and supported by fastening means (not shown) via the wheel 9 in a state where the tire axis TC coincides with the shaft core.

  The brake device 14 is provided so as to sandwich the brake disc 15 in the thickness direction (vertical direction in FIGS. 1 and 2). The rotational position around 12 is fixed. That is, by operating the brake device 14, the tire fixing hub 13 is fixed so as not to rotate around the tire support column 12 via the brake disk 15.

  The load measuring unit 30 is attached to the rear ends of the pair of left and right main frames 3 and extends upward. The vertical movement unit 40 is provided so as to be vertically movable with respect to the front surface of the base 31. A left-right direction moving unit 50 provided to be movable in the left-right direction with respect to the upper surface of the up-down direction moving unit 40, and a front-rear direction moving unit 60 provided to be movable in the front-rear direction with respect to the upper surface of the left-right direction moving unit 50. And have.

  The base 31 has a rectangular parallelepiped housing 32, a vertical ball screw 33 that extends in the vertical direction inside the housing 32 and is supported so as to be rotatable around an axis, and a vertical ball screw 33 that is disposed on the upper surface of the housing 32. The handle 34 is connected to the upper end of the housing 32 and rotates integrally therewith, and a pair of left and right vertical slide rails 35 fixed to the front surface of the housing 32 and extending in the vertical direction.

  The vertical movement unit 40 is fixed to a rectangular parallelepiped housing 41, a pair of left and right carriages 42 fixed to the rear surface of the housing 41, a nut receiver 43 disposed between the left and right directions, and an upper surface of the housing 41. And a table 44. Each of the pair of left and right carriages 42 is guided by a pair of left and right vertical slide rails 35 and moves in the vertical direction. The nut receiver 43 protrudes to the inside of the housing 32 of the base 31 and has a female screw portion extending in the vertical direction. The vertical ball screw 33 penetrates the female screw portion so as to penetrate vertically. The table 44 extends in the horizontal direction.

  That is, by rotating the handle 34 of the base 31, the vertical movement unit 40 is moved up and down with respect to the base 31 by the vertical ball screw 33 via the nut receiver 34, and this movement causes the carriage 42 to move. And is guided by the vertical slide rail 35.

  On the table 44, a pair of front and rear left and right slide rails 45 extending in the left and right direction, a left and right ball screw 46 extending in the left and right direction and supported rotatably around the axis, and a left and right ball screw 46 are provided. A handle 47 that is connected to the left end portion and rotates integrally therewith is disposed.

  The left / right moving unit 50 includes a table 51 extending in the horizontal direction, a pair of front and rear carriages 52 fixed to the lower surface of the table 51, and a nut receiver 53 disposed between these front and rear directions. Each of the pair of front and rear carriages 52 is guided by the pair of front and rear left and right slide rails 45 and moves in the left and right direction. The nut receiver 53 has a female screw portion extending in the left-right direction, and a left-right ball screw 46 is threaded through the female screw portion in the left-right direction.

  That is, by rotating the handle 47 of the vertical movement unit 40, the horizontal movement unit 50 is moved in the horizontal direction with respect to the vertical movement unit 40 by the left and right ball screw 46 via the nut receiver 53, and The movement is guided by the left and right slide rail 45 through the carriage 52.

  On the table 51, a pair of left and right front / rear slide rails 54 extending in the front / rear direction, a front / rear ball screw 55 extending in the front / rear direction and supported rotatably around the axis, and a front / rear ball screw 55 A motor 56 connected to the rear end is disposed. The motor 56 has an output shaft extending in the front-rear direction, and is arranged such that the axis of the output shaft coincides with the axis of the front-rear direction ball screw 55. When driven, the motor 56 rotates the output shaft around an axis extending in the front-rear direction.

  The front-rear direction moving unit 60 has a table 61 extending in the horizontal direction, a pair of left and right carriages 62 fixed to the lower surface of the table 61, and a nut receiver 63 disposed between these left and right directions. The pair of left and right carriages 62 are guided by the pair of left and right front and rear slide rails 54 and move in the front and rear direction. The nut receiver 63 has a female screw portion extending in the front-rear direction, and a front-rear direction ball screw 55 is threaded through the female screw portion in the front-rear direction.

  That is, by driving the motor 56, the front / rear direction moving unit 60 is moved in the front / rear direction with respect to the left / right direction moving unit 50 by the front / rear direction ball screw 55 via the nut receiver 63, and this movement causes the carriage 62 to move. It is guided by the slide rail 54 in the front-rear direction.

  A load cell (load measuring device) 64 is fixed on the table 61. A connecting portion 65 to which a connecting member 66 described later is connected is provided at the front end portion of the load cell 64. The load cell 64 measures the load input to the connecting portion 65 via the connection member 66. In addition, you may employ | adopt what measures only the front-back direction component of a load as the load cell 64. FIG.

  The connection member 66 is a linear member that connects the stud pin 7 embedded in the pneumatic tire 8 supported by the tire support portion 10 and the connecting portion 65 of the load cell 64 in the front-rear direction, and is a member that does not easily extend in the axial direction. In this embodiment, a metal chain is used. In addition, a suitable connection means can be employ | adopted for the connection of the connection member 66, and the connection part 65 and the stud pin 7 of the load cell 64, respectively. For example, you may comprise so that a hook part or a ring part may be provided in the top part of the stud pin 7, and the connection part 65, and it may connect with the connection member 66 using a carabiner etc.

  The drop load measuring device 1 further includes a control device 5. The control device 5 is configured by a known computer including a CPU, a memory, a storage device, and an input / output device, and software installed in the computer. The control device 5 controls the driving of the motor 56 and inputs the measurement result by the load cell 64.

  Specifically, the control device 5 controls the number of rotations (rpm) per unit time of the motor 56 and the rotation amount is input. Accordingly, the moving speed in the front-rear direction of the front-rear moving unit 60 can be controlled, and the amount of movement in the front-rear direction can be measured.

  Furthermore, the measurement result of the load by the load cell 64 is input to the control device 5 in synchronization with the measurement of the movement amount of the front-rear direction moving unit 60. That is, the control device 5 synchronously measures the load input to the load cell 64 via the connection member 66 and the amount of movement of the front-rear direction moving unit 60 in the front-rear direction.

  Hereinafter, measurement of the removal load of the stud pin 7 by the removal load measuring device 1 will be described.

  As shown in FIG. 2, the pneumatic tire 8 is used as a tire support portion 10. At this time, when the tire support 10 side is viewed in the front-rear direction from the load cell 64 side, the stud pin 7A that is the measurement target of the pull-out load is positioned so as to be spaced apart in the left-right direction with respect to the tire axis TC. The pneumatic tire 8 is disposed at a rotational position around the tire axis TC. By operating the brake device 14 in this state, the pneumatic tire 8 is fixed in the rotational direction around the tire support column 12.

  Next, the vertical movement unit 40 and the horizontal movement unit 50 are moved up and down by the vertical movement unit 40 and the horizontal movement unit 50 so that the connecting portion 65 of the load cell 64 is positioned opposite to the top of the stud pin 7A to be measured. Adjust the direction and left / right direction. For example, a laser irradiation device (not shown) that irradiates a position where the connecting portion 65 of the load cell 64 faces in the front-rear direction is provided in the front-rear direction moving unit 60, and the light irradiated by the laser irradiation device is the top of the stud pin 7A to be measured. Adjustment work can be facilitated by adjusting the position of the front-rear direction moving unit 60 so as to irradiate.

  Next, the connecting stud 66 connects the stud pin 7A to be measured and the connecting portion 65 of the load cell 64 in the front-rear direction. Here, since the connecting portion 65 of the load cell 64 is positioned facing the top of the stud pin 7A to be measured in the front-rear direction, the connecting member 66 connecting them extends in the front-rear direction.

  Next, the control device 5 drives and controls the motor 56 to move the front-rear direction moving unit 60 rearward, and applies a pulling force from the pneumatic tire 8 to the stud pin 7 </ b> A via the connecting member 66. At this time, the control device 5 records the pull-out load of the stud pin 7 </ b> A measured by the load cell 64 in synchronization with the rearward movement amount of the front-rear direction moving unit 60 until the stud pin 7 </ b> A is pulled out.

  In other words, according to the present embodiment, the position of the load cell 64 in the left-right direction is adjusted so as to be positioned corresponding to the stud pin 7A positioned to the right side from the tire axis TC when viewed from the front-rear direction. . Here, since the stud pin 7A is disposed at a position spaced rightward from the tire axis TC when viewed from the front-rear direction, the axial direction of the stud pin 7A extending in the radial direction of the pneumatic tire 8 is on the tire inner diameter side. Inclined to the left side toward the tire axis.

  As a result, as shown in FIG. 3, the connecting member 66 is arranged to extend in the front-rear direction so as to have an angle difference X with respect to the axial method of the stud pin 7A. The load at the time of pulling in the front-back direction inclined from the direction is measured. In other words, the falling load of the stud pin 7A can be measured in a direction inclined at an angle difference X with respect to the radial direction in the portion where the stud pin 7A is embedded.

  Further, the tire support portion 10 is configured to rotate the pneumatic tire 8 around the tire axis TC and to be held at a desired rotation position by the brake device 14. Thereby, when viewed from the front-rear direction, the position of the stud pin 7 in the left-right direction with respect to the tire axis TC can be easily adjusted with the pneumatic tire 8 attached to the tire support portion 10. Moreover, the position of the front-rear direction moving unit 60 is configured to be movable in the left-right direction and the up-down direction so that the connecting portion 65 of the load cell 64 faces the stud pin 7 in the front-rear direction.

  For example, as shown in FIG. 3, when the stud pins 7B and 7C are positioned at both ends in the left-right direction of the pneumatic tire 8 when viewed from the front-rear direction, the axial direction (radial direction) of the stud pins 7B and 7C However, the connecting member 66 extends in the front-rear direction perpendicular to the left-right direction. That is, with respect to the stud pins 7B and 7C, it is possible to measure the slipping load in the direction orthogonal to the radial direction of the pneumatic tire 8, that is, in the direction along the tire circumferential direction.

  When the stud pin 7D is positioned facing the tire axis TC of the pneumatic tire 8 in the front-rear direction when viewed from the front-rear direction, the axial direction (radial direction) of the stud pin 7D is directed in the front-rear direction. This coincides with the direction in which the connection member 66 extends. That is, with respect to the stud pin 7D, it is possible to measure the slipping load in the radial direction of the pneumatic tire 8.

  Therefore, the stud pin 7 is positioned at an arbitrary position in the left-right direction with respect to the tire axis TC of the pneumatic tire 8 when viewed from the front-rear direction, so that the axis of the stud pin 7 and the direction in which the connecting member 66 extends The angle between them can be set to an arbitrary angle from 0 ° to 90 °. Thereby, the pull-out load of the stud pin 7 can be measured in an arbitrary direction within a plane orthogonal to the tire axis TC.

  Further, by measuring the pull-out load and displacement of the stud pin 7 in synchronization, it can be determined that the rigidity of the stud pin hole is high and the holding force of the stud pin 7 is high when the displacement is small. If there is a holding force, it can be determined that the stud pin hole bottom is well meshed and the stud pin 7 holding force is high. Further, when the displacement is large and the pull-out load is small, it can be determined that the rigidity of the land portion where the stud pin 7 is embedded is low, so that the embedded position of the stud pin 7 is embedded in the portion of the land portion where the rigidity is high. By changing so as to do, it is possible to improve the removal load of the stud pin 7. That is, the buried position of the stud pin 7 in the land portion can be evaluated.

(Second Embodiment)
With reference to FIGS. 4-6, the stud pin drop load measuring device 70 according to the second embodiment will be described. The slip load measuring device 70 is different from the slip load measuring device 1 according to the first embodiment in that the tire support portion 10 is configured to be rotatable in a plane parallel to the front-rear direction and the up-down direction. Yes. In the following description, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 4 is a side view of the stud pin removal load measuring device 70. As shown in FIG. 4, in the load release device 70, the tire support portion 10 is attached to a first shaft 71 that extends in the left-right direction and penetrates the first housing 11 left and right, and a pair of left and right front pillars 4. And a first bearing 72 that rotatably supports the first shaft 71 around the axis. That is, the tire support portion 10 is configured to be rotatable with respect to the front column 4 in a plane parallel to the front-rear direction and the vertical direction around the first axis 71.

  In the present embodiment, the tire support portion 10 is configured such that the tire axis TC of the pneumatic tire 8 supported by the first housing 11 rotates about the first shaft 71 with respect to the front column 4. The first shaft first rotation position extending in the up-down direction and the first shaft second rotation position in which the tire axis TC extends in the front-rear direction are configured to be movable. The tire support 10 is provided with a stopper (not shown) so that the first housing 11 is held at the first axis first rotation position and the first axis second rotation position with respect to the front column 4. I have.

  In the case where the tire support portion 10 is held at the first shaft first rotation position as shown by a two-dot chain line in FIG. 4, as in the first embodiment, the load from the stud pin 7 is set to the tire axis TC. It is possible to measure in an arbitrary direction in a plane orthogonal to.

  In addition, when the tire support portion 10 is held at the first shaft second rotation position as shown by a solid line in FIG. 4, the stud pin 7 has a radial shape of the pneumatic tire 8 in a plane perpendicular to the front-rear direction. The connecting member 66 extends in the front-rear direction while extending in the direction. In this case, the connecting member 66 is arranged so as to extend perpendicular to the axial direction (radial direction) of the stud pin 7, that is, in the tire width direction. Therefore, the pull-out load of the stud pin 7 can be measured in the tire width direction.

  FIG. 5 is a plan view of a stud pin pull-out load device 75 according to a modification of the second embodiment, and shows the periphery of the tire support portion 10. As shown in FIG. 5, the drop load device 75 further includes a first positioning motor 76. The first positioning motor 76 is connected to the left end portion of the first shaft 71 with the output shaft aligned with the axis of the first shaft 71. The first positioning motor 76 is configured to be controlled by the control device 5 so as to hold the output shaft at an arbitrary rotational angle position, and for example, a stepping motor can be employed.

  According to the stud pin pull-out load device 75, the tire support 10 can be held at an arbitrary angular position between the first shaft first rotation position and the first shaft second rotation position. For example, in the side view shown in FIG. 6, when the vertical direction is the vertical direction of the actual vehicle, the tire axis TC is inclined downward toward the rear of the pneumatic tire 8 supported by the tire support portion 10. It is also possible to simulate the camber angle Y with the actual vehicle mounted. That is, it is possible to measure the pull-out load of the stud pin in a state closer to the actual vehicle mounted state.

(Third embodiment)
With reference to FIGS. 7 to 10, a stud pin drop load measuring device 80 according to the third embodiment will be described. The slip load measuring device 80 differs from the slip load measuring device 70 according to the second embodiment in that the tire support column 12 of the tire support portion 10 is configured to be rotatable in the horizontal direction. In the following description, the same components as those in the first and second embodiments are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 7 is a plan view of the stud pin removal load measuring device 80. As shown in FIG. 8, in the load release device 80, the tire support portion 10 is attached to the first housing 11 and the second shaft 81 that extends in the vertical direction and penetrates the tire support pillar 12 up and down. And a second bearing 82 that supports the two shafts 81 to be rotatable around the axis. That is, in the tire support portion 10, the tire support column 12 is configured to be rotatable around the second shaft 81 in the horizontal direction with respect to the first housing 11.

  In the present embodiment, the tire support portion 10 has the tire axis TC of the pneumatic tire 8 supported by the tire support column 12 rotating around the second shaft 81 with respect to the first housing 11. It is configured to be movable between a second shaft first turning position extending in a plane parallel to the front-rear direction and the up-down direction and a second shaft second turning position where the tire axis TC extends in the left-right direction. The tire support 10 is provided with a stopper (not shown) so that the tire support column 12 is held at the second axis first rotation position and the second axis second rotation position with respect to the first housing 11. I have.

  As indicated by a two-dot chain line in FIG. 7, the tire support column 12 is held at the second shaft first rotation position in a state where the tire support portion 10 is positioned at the first shaft second rotation position. In this case, as with the second embodiment, the pull-out load of the stud pin 7 can be measured in the tire width direction.

  Further, when the tire support column 12 is held at the second shaft second rotation position in a state where the tire support portion 10 is positioned at the first shaft second rotation position as indicated by a solid line in FIG. The stud pin 7 extends in the radial direction of the pneumatic tire 8 in a plane perpendicular to the left-right direction, whereas the connecting member 66 extends in the front-rear direction. In this case, the connecting member 66 is arranged so as to extend with an angular difference in a plane perpendicular to the left-right direction, that is, perpendicular to the tire axis TC, with respect to the axial direction (radial direction) of the stud pin 7. Therefore, it is possible to measure the unloading load of the stud pin 7 in an arbitrary direction in a plane perpendicular to the tire axis TC.

  FIG. 8 is a side view of the stud pin pull-out load measuring device 85 according to a modification of the third embodiment, and shows the periphery of the tire support portion 10. As shown in FIG. 8, the missing load measuring device 85 further includes a second positioning motor 86. The second positioning motor 86 is connected to the lower end portion of the second shaft 81 with the output shaft aligned with the axis of the second shaft 81. The second positioning motor 86 is configured to be controlled by the control device 5 so as to hold the output shaft at an arbitrary rotational angle position, and for example, a stepping motor can be employed.

  According to the removal load measuring device 85, the tire support column 12 can be held at an arbitrary angular position between the second axis first rotation position and the second axis second rotation position.

  In addition to this, a first positioning motor 76 and a second positioning motor 86 may be provided as in a stat pin drop load measuring device 90 according to a further modification shown in FIG. Accordingly, the tire support column 12 can be held at an arbitrary angular position around the second axis 81 while the tire support 10 is held at an arbitrary angular position around the first axis 71. Thereby, the pull-out load of the stud pin can be measured in further various directions.

  For example, as shown in FIG. 10A, the tire support 10 is rotated around the second shaft 81 in a state where the tire support portion 10 is located at the first shaft second position, so that the tire axis TC of the pneumatic tire 8 is Thus, the slip angle may be reproduced when the left-right direction is the traveling direction so as to have a very small angle difference Z1 (for example, 5 ° or less). In this case, the connecting member 66 extending in the front-rear direction extends in the width direction (of the vehicle) orthogonal to the traveling direction of the pneumatic tire 8, and the stud pin is removed in the tire width direction in consideration of the slip angle. The load can be measured.

  Further, as shown in FIG. 10B, the tire support portion 10 is rotated around the second shaft 81 in a state where the tire support portion 10 is positioned at the first shaft second position, so that the tire axis TC of the pneumatic tire 8 is in the left-right direction. Therefore, the slip angle may be reproduced when the forward / backward direction is the traveling direction so as to have a very small angle difference Z2 (for example, 5 ° or less). In this case, the connecting member 66 extending in the front-rear direction extends in the traveling direction of the pneumatic tire 8, and can measure the slipping load of the stud pin in the tire circumferential direction in consideration of the slip angle.

  That is, by rotating the tire support column 12 around the second shaft 81, the pull-out load of the stud pin can be measured in any direction from the tire width direction to the tire circumferential direction. Stud pin pull-out load can be measured in consideration of the angle and turning situation.

  In 1st Embodiment, although the tire support part 10 was demonstrated taking the case where the tire axial line TC was extended in the up-down direction, it was not restricted to this. That is, the tire support portion 10 may have the tire axis TC extending in the left-right direction. In this case, what is necessary is just to comprise each member of the said embodiment by replacing the up-down direction and the left-right direction. Further, even if the tire support portion 10 does not include the first shaft 71, the tire support portion 10 may be configured to include the second shaft 81. In this case, the tire support portion 10 is positioned at the first shaft second position. The tire support column 12 may be configured to be rotatable around the second shaft 81 in a fixed state.

  In the above embodiment, the connection member 66 and the connecting portion 65 of the stud pin 7 and the load cell 64 are connected by using a hook, a carabiner, or the like. The outer cylindrical surface near the top of the stud pin may be gripped by the gripping means, and the gripping means may be connected to the connection member 66.

  In addition, this invention is not limited to the structure described in the said embodiment, A various change is possible.

DESCRIPTION OF SYMBOLS 1 Outgoing load measuring apparatus 4 Front part pillar 5 Control apparatus 7 Stud pin 8 Pneumatic tire 10 Tire support part 11 1st housing | casing 12 Tire support pillar 30 Load measurement part 31 Base 40 Vertical movement unit 50 Left and right direction movement unit 60 Front and rear Direction moving unit 64 Load cell 66 Connection member 71 First shaft 76 First positioning motor 81 Second shaft 86 Second positioning motor

Claims (10)

A tire support that supports a pneumatic tire with stud pins embedded therein;
For the pneumatic tire, a load measuring instrument disposed at a position separated in a second direction orthogonal to the first direction, which is the extending direction of the tire axis,
A connection member for connecting the load measuring instrument and the stud pin in the second direction;
In the state where the pneumatic tire is supported by the tire support portion, the load measuring device is separated from the tire support portion in the second direction, and the stud pin is connected to the pneumatic tire via the connection member. A stud pin pull-out load measuring device, in which a load drop at the time of withdrawal from the stud pin is measured by the load measuring instrument,
A direction perpendicular to each of the first direction and the second direction is a third direction.
When the tire support part side is viewed in the second direction from the load measuring instrument side, the load measuring instrument faces the stud pin positioned away from the tire axis in the third direction. A stud pin pull-out load measuring device configured to be adjustable in position in three directions. When the tire support part side is viewed in the second direction from the load measuring instrument side, the load measuring instrument extends from a position facing the tire axis to a position facing both ends in the third direction of the tire. The position in the third direction is configured to be adjustable,
The stud pin drop load measuring device according to claim 1. The tire support portion is configured to rotate the pneumatic tire supported here around the tire axis and to be held at a desired rotation position.
The stud pin dropout load measuring device according to claim 1 or 2. A movement amount measuring unit for measuring a movement amount of the load measuring instrument in the second direction;
The movement amount measuring unit measures the movement amount in synchronization with the measurement of the unloading load by the load measuring device,
The stud pin dropout load measuring device according to any one of claims 1 to 3. The tire support portion is configured to be rotatable around a first axis parallel to the third direction.
The stud pin pull-out load measuring device according to any one of claims 1 to 4. The tire support portion includes a first axis first rotation position where the tire axis extends along a first direction, and a first axis second rotation position where the tire axis extends along a second direction. The rotation around the first axis is fixed,
The stud pin dropout load measuring device according to claim 5. The tire support portion is configured to be held at an arbitrary rotation position between the first shaft first rotation position and the first shaft second rotation position around the first axis.
The stud pin dropout load measuring device according to claim 6. The tire support portion is configured to be rotatable around a second axis parallel to the first direction.
The stud pin dropout load measuring device according to any one of claims 1 to 7. The tire support portion includes a second axis first rotation position where the tire axis extends along a second direction, and a second axis second rotation position where the tire axis extends along a third direction. The rotation about the second axis is fixed,
The stud pin dropout load measuring device according to claim 8. The tire support portion is configured to be fixed at an arbitrary rotation position between the second shaft first rotation position and the second shaft second rotation position around the second axis.
The stud pin dropout load measuring device according to claim 9.

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