DE10160643A1 - Grindstone for tire inspection machine, has lock assembly which selectively combines supporting structure with frame when supporting structure exists in actuated position - Google Patents

Abstract

A frame (F) has a central shaft for receiving a tire (T) to be tested. A grinder adjoins a supporting structure (12) which is pivotably mounted on the frame. A lock assembly selectively combines the supporting structure with the frame when the supporting structure is in actuated position. A grinding head (30) supported on the edge of the supporting structure, has motors (35,35') connected with the grindstones (32,34). An Independent claim is included for inclination adjuster.

Description

In tire dressing machines, one tire is rotated at different Speeds checked to ensure that the manufacture and function of the tire are within the quality standards. The tire rotates during this test process driven, and the tire dressing machine checks the shape of the tire and the Surface features with high accuracy. Sometimes the tire planer recognizes irregularities in the tire during the test. Any irregularity of the tire The surface and shape can be removed by removing material at suitable points of the tire are corrected.

The known tire dressing machines use a for material removal Grinding device with a single cylindrical grinding wheel, which is in relation to the Rotation of the tire turns. When the tire rotates, the grinding wheel is used Material removal selectively brought into contact with the tire.

In known grinding devices, the grinding wheel is used in rotating way. A typical grinding device has a swivel arm on which the grinding wheel and its drive motor are attached. Often, the To be able to control the speed and the direction of rotation of the grinding and gearbox arrangement used. The motor is then with the grinding wheel or the gearbox over belts and chains as well as a number of pulleys or Sprockets connected. As can be seen, the engine is the number of belts and chains, as well as the gear box voluminous, and the space available for the arrangement of this unit is limited. In fact, a typical motor housing protrudes to such a degree that the outer dimensions of the tire planer are not allow the grinding wheel to be operated linearly. To overcome this deficiency in known tire dressing machines, the motor is removed from the grinding device attached to an arm that encloses the drive belt or chain. In this Way the motor is away from the gauges, the load wheel and others Devices that must be located near the tire to be tested, where more space is available. The arm is attached to a joint so that it is Can move housing radially in a limited space. The joint is between that Motor and the grinding wheel arranged, and the arm is driven by the force of one hydraulic cylinder pivoted, which with the arm on one side of the joint connected is. The typical hydraulic cylinder acts in the transverse direction of the arm and is therefore separate from the frame element around which the arm swings Frame element attached. The hydraulic cylinders attached in this way obstruct the view and access to the grinder and to the space surrounding the grinder.

As a result of the pivoting of the arm, the grinder cannot go directly to the center of the tire. In other words, the centerline and the Point of contact of the arcuate movement of the grinding device in Match to tangentially touch the tire. It is understandable that it is difficult with this initial contact with the tire to get a good, accurate one Establish contact in a repeatable way. Furthermore, the housing of the Grinder can be adjusted to fit the machine housing and try to get one to allow good contact between the grinder and the tire. specially the grinder housing is often connected to a vacuum port to To remove particles that arise from the grinding process, and this housing must seal tightly around the grinding wheel. Because the housing holds the grinding wheel in this device tightly, the simple swiveling of the arm can lead to that the housing touches the rotating tire. It is understandable that such Touch damage the grinder considerably and also damage the tire can inflict.

To avoid such contact and the position of the grinding wheel To improve material removal, the position of the housing and the grinding wheel is adjusted relative to the arm by rotating the housing. Around To make adjustment, known devices have a number of joints. In In some cases, no fewer than five joints are used. As a result of Manufacturing tolerances make every joint a potential source of error. If multiple joints used, the number of these errors adds up, which is accurate in terms of Removal of the tire material is of great importance. It is through these mistakes difficult to make good contact with the tire.

If two grinding wheels are used, there is practically none Possibility of both discs touching the tire at the same time; and in some cases will a disc has no contact with the T tire. Often a second disc is used to try to remove a lip or other irregularities caused by the first disc are caused, as will be described in more detail below should. If the joint defects cause the trailing disc to not be in contact with the tire, the trailing disc cannot perform a corrective function exercise.

In known grinding devices, the amount or the amount of material removal Often measured by the tire as a function of the current of the only motor which is the Disk or drives the disks. It is not for a device with two disks possible by measuring the current of the single motor information about the dimension the percentage removal of each grinding wheel, and thus the condition remains undetected if a pane completely gets out of contact. Furthermore, the Components that connect the motor to the grinding wheels, such as. B. straps or Chains, to additional errors in this measurement.

With regard to the removal of material from the tire, the known devices typically use an essentially cylindrical grinding wheel which rotates about a central axis of rotation. As best seen in the prior art illustration in Fig. 1, the radial profile of the cylindrical grinding wheel at the front leaves any interruption on the periphery of the tire on the tire elements E with which the grinding wheel comes into contact Direction of rotation of the grinding wheel a lip L. It is assumed that the lip L is formed by the rotation of the grinding wheel. Because the grinding wheel strikes the tire elements E, which are separated from one another by the interruptions in the periphery of the tire T, the radial force of the wheel causes the tire element E to deform in the radial direction. At the same time, the force of the disk acting tangentially on the relatively soft, essentially flexible tire element E causes the tire element E to bend in the direction of the rotation of the disk. As a result, the front area of the tire element E is ground to a lesser extent because it is bent away from the grinding wheel. As soon as the element is behind the grinding wheel, the bent element returns to its rest position and has an irregular profile, as can be seen in FIG. 2. This irregularity is often referred to as lip L.

In a device with a single grinding wheel, an attempt was made to pass the lip through Reversing the direction of rotation of the tire and by grinding in the opposite direction to remove. Unfortunately, this reversal led to a lip on the other side of the Tires element. An attempt was made to introduce double grinding wheels with the second grinding wheel to remove the lip. As described above stands however, the error that arises from the joints affecting the position of the grinding head adjust against proper contact of the grinding wheel, resulting in a incomplete removal of lip L. Or in cases where the second If the grinding wheel does not touch the tire, the lip L remains intact.

For devices with one as well as with double grinding wheels, the swiveling fastening of the arms, which hold the grinding wheels, cause of the Inaccuracy when grinding the tire. As previously explained, the Grinding wheel typically arranged on an arm, which swivels with one of the frame elements is connected so that the grinding wheel is in contact with the Tire is pivoted. Typically, the arms that extend the Hold the grinding wheels and guide them back to the pivot point when the grinding wheels are in contact with the tire, at an angle from the pivot point. The forces on the grinding wheels are transferred to the pivot point via these arms. It's clear, that the moments acting on the joint caused by these forces increase proportionally with the length of the arm. If the joint is not extraordinary is rigid, these forces can cause the arm or the Move the grinding head itself so that the grinding wheels do not have the required Remove the amount of material. To avoid inaccuracies caused by this movement a more stable system for holding the grinding wheel is required.

It is an object of the present invention to provide a more stable holding device for a To create grinding wheel in a tire dressing machine.

Another object of the present invention is to provide a grinder create, which has a motor-driven swivel adjustment.

Generally, the present invention provides a grinder in one Tire dressing machine created, which has a frame with a first lateral frame part and has a second side frame part, and the frame has a tire for testing receives, which has a central axis, wherein the grinding device comprises: a Drive, which is pivotally connected to the first side frame part, and one Locking device next to the drive, the second side frame part selectively couples the drive to the second side frame part when that Drive is in the working position; a grinding head, which at one end of the Drive is held, the grinding head has at least one grinding wheel and at least one motor which is coupled to the grinding wheel and its rotation causes.

The present invention also provides pivot adjustment in one Tire dressing machine which inspects a tire on its circumference, the tire dressing machine has a grinding head which is held on an arm with a joint and around a Swivel axis is pivotable, which is parallel to a tangent on the joint Circumference of the tire extends, and the pivot adjustment comprises a motor assembly, which is held on the arm and is functionally coupled to the grinding head, the Activation of the motor assembly causes the grinding head to pivot.

Accordingly, the manufacture of an improved tire dressing machine with the characteristics described above are the main object of this invention, and other tasks will become better as you read the following brief description understandable, which takes into account and explains the attached drawings.

Brief description of the drawings

Fig. 1 is a prior art illustration schematically showing the lip formed by a typical grinding device with a grinding wheel.

Figure 2 is a schematic side view of a tire showing the lip left by a prior art grinder.

Fig. 3 is a schematic view of a grinding device according to the invention, which shows the removal of the material from the tire.

Fig. 4 is a plan view of a grinding apparatus according to the invention in a Reifenabrichtmaschine.

Fig. 5 is a front view of this grinder.

FIG. 6 is a rear view of the grinder as seen from the direction of line 6-6 in FIG. 5.

Fig. 7 is a sectional view of the grinders as taken along section line 7-7 in Fig. 4.

Fig. 8 is a plan view of a grinder according to the invention, showing a grinder with a single grinding wheel held on a pair of frame members.

Fig. 8A is a plan view of an inventive grinding apparatus, showing a grinding apparatus, which has two grinding wheels, which are held on a pair of frame parts.

Fig. 9 is an enlarged side view of a grinder which is similar to the grinder shown in Fig. 8A and which partially shows the end of the grinder, its grinding head and a pivot adjustment which pivots the grinding head.

Fig. 10 is a partial top plan view of a tire and grinder, which is the same as the one shown in Fig. 9 and shows the details of the grinder head and pivot adjustment assembly in greater detail.

Fig. 11 is a partial, enlarged plan view of a first embodiment of a grinder according to the invention, showing a frame part of a tire dressing machine, a portion of the drive of the grinder, and a threaded locking device used to connect the frame part to the drive.

Figure 11A is a partial, enlarged plan view of a second embodiment of a grinder according to the present invention, showing a frame of a tire planer, part of the grinder drive, and a latching type locking device used to connect the frame to the drive.

Fig. 12 is a plan view of a centering grinder according to the present invention, showing a grinder pivotally supported on a frame member and fixed to an opposite frame member by a locking device.

FIG. 13 is a partially sectioned side view of the centering grinder of FIG. 12.

A grinding device according to the invention is designated overall by the reference number 10 in the attached drawings. The grinder 10 is used to remove material from a tire T. The tire T is arranged in a tire dressing machine (not shown) and is accordingly rotatably fastened within the tire dressing machine about a central axis CA. During operation of the tire dressing machine, the tire T can be driven in rotation by a suitable drive mechanism, so that the tire T rotates about a central axis CA. The tire dressing machine rotates the tire T in order to evaluate the shape of the tire T including its surface properties.

For this purpose, a load wheel is brought into and out of contact with the circumference of the tire T and various sensors are used to obtain information about the integrity of the tire, its shape and the quality of its surface. Irregularities in the surface S of the tire T can be corrected by appropriately removing material from the surface S. In order to remove material, the grinding device 10 is selectively brought into contact with the surface S of the tire T.

The grinder 10 is suitably placed in the vicinity of the tire T z. B. held by a frame F to enable this contact. The frame F can be an independent bracket or, as shown, part of the tire planer. The grinding device 10 essentially comprises a drive 12 which is attached to the frame F. As shown in FIG. 4, the carriage 12 can be provided with a joint 14 in order to enable a radial adjustment of the carriage 12 relative to the frame F. The pivoting of the carriage 12 allows the grinder 10 to be aligned with the tire to ensure good contact between the grinder 10 and the tire T. The center line CL of the grinding device 10 can be aligned with the central axis CA of the tire T in order to achieve simultaneous contact of double grinding wheels of the grinding device 10 .

Once the grinder 10 is aligned, it can be locked in place so that it remains aligned during the grinding process.

For this purpose, the drive 12 can be provided with a pivot stop 11 , which starts from the holder 12 . Furthermore, a buffer 13 and a disk 15 can be provided between the frame and the drive 12 in order to adjust the distance. It can be seen that the adjusting disk 15 and the buffer 13 can be arranged between the frame F and the swivel stop 11 . As a result, the radial position of the drive 12 can be adjusted by changing the size of the disk 15 , and then the grinding device 10 can be locked in relation to the frame F. Alternatively, a dynamic adjustment system can be provided which has suitable sensors for determining the position of the grinding device 10 relative to the tire T and its center line CL and a suitable actuator which reacts to the sensors to determine the radial position of the grinding device 10 by moving the drive 12 to change relative to frame F. In this way, the grinding device 10 can be appropriately aligned with respect to the tire T. The center line CL of the grinding device 10 is preferably aligned with the axis CA of the tire T.

One or more arms 16 are kept spaced apart by the drive 12 . The arms 16 are held in bearings 18 which facilitate a substantially linear movement of the arms 16 towards and away from the tire T. The bearings 18 , as shown in FIG. 6, are linear bearings and may have rollers 19 which are suitably attached to the carriage 12 . The rollers 19 are vertically adjusted to receive the edges 21 of the arms 16 . The staggered bearings 18 as shown in FIG. 6 can be located on either side of the edges 21 of the arm 16 and used to help counteract the forces acting on the arm 16 and the position of the arm 16 to keep. The bearings 18 shown in FIGS . 4 and 5 can be arranged in front of and behind the holding parts and aligned in the longitudinal direction in order to guide the arm 16 when actuated.

The arms 16 are by a suitable linear actuator, which bears the reference number 20 , z. B. driven by fluid operated actuators such as hydraulic or pneumatic cylinders, motor operated actuators, electrical actuators or the like. In the illustrated embodiment, the actuator 20 includes a pair of cylinders 22 that expand to move the arms 16 toward the tire T or to pull the arms 16 away from the tire T.

As stated above, the movement of the grinder 10 can be controlled by various methods known in the art. For example, hydraulic or pneumatic cylinders 22 can be used to advance or retract the arm 16 that supports the grinding head 30 . In such a case, supply lines (not shown) that supply a fluid from a fluid source can be used to supply fluids to the cylinders 22 and to exert a driving force. The activation of these cylinders 22 can be coordinated by a sensor 37 which is arranged with respect to the tire T or to the grinding head 30 . The sensor 37 is connected to a controller 39 , which controls the fluid supply to the cylinders 22 . In the illustrated embodiment, a control valve 41 is used to control the flow of the fluid flowing through a manifold 43 that supplies the cylinders 22 . As a result of the flow control, the position of the grinding head 30 relative to the tire T is controlled.

In addition, the position of the grinding heads 30 relative to each other and to the tire T can be adjusted if required for a particular tire T. For this purpose, the arms 16 are provided with a distance adjustment 24 and a swivel adjustment 26 , which act on the ends 28 of the arms 16 . The ends 28 can be designed to be pivotable in order to allow the grinding heads 30 to be spaced apart from one another or from the arms 16 . In order to provide a further influence on the grinding head 30 , the grinding head 30 can be pivotably attached to the ends 28 of the arms 16 .

As can best be seen in FIG. 4, the grinding head 30 can be pivotally fastened between the spaced parts 29 of the ends 28 and rotated or pivoted between them, as will be described in more detail below. While the grinding device 10 can be aligned in any position and the pivoting can be changed accordingly, the grinding wheel 32 lies in a plane parallel to the plane of the tire T. When the grinding wheel 32 is pivoted, the grinding wheel 32 deviates from this plane and pivots between a plane which is substantially parallel to that of the tire T and a plane which is substantially perpendicular to that of the tire T. It will be appreciated that the amount of pivotal movement can be limited by suitable stops or limitations, and the pivotal adjustment 26 can control the amount and amount of pivotal movement. The pivotal adjustment 26 extends from the arm 16 or to the extent of pivotal movement to control the end 28 of the grinding head 30 of the grinding head 30th In order to limit the range of motion of the grinding head 30 , an adjustable swivel lock 31 can interact with the grinding head 30 . In this way, the adjustment elements 24 , 26 can be used to change the distance of the grinding head 30 or to pivot the grinding heads 30 relative to the tire T and the arms 16 . Various adjustment elements 24 , 26 can be used, e.g. B. mechanical actuators, ie threaded parts, gears, pawl elements, fluid cylinders or cams; or electrical actuators such. B. Linear rails. Alternatively, the spacing and the pivoting can be adjusted by moving the grinding heads 30 on the frame F, the arm 16 or the carriage 12 .

The grinding heads 30 are held at the ends 28 of the arms 16 . The ends 28 may have a pair of spaced portions 29 that sandwich the grinding head 30 therebetween. The grinding heads 30 essentially comprise a pair of grinding wheels 32 , 34 which are driven by at least one motor 35 . As can be seen in FIG. 4, each grinding wheel 32 , 34 can be driven directly by a motor 35 , 35 ', which are arranged next to each grinding wheel 32 , 34 . The motor 35 is held next to the grinding wheels 32 , 34 and can be attached to the ends 28 of the arms 16 or to the cover 40 itself. The grinding wheels 32 , 34 are functionally connected to the motor 35 and can be driven directly by this. Each grinding wheel 32 , 34 can be driven by its own individual motor 35 . When using a motor 35 for each grinding wheel 32 , 34 , the size of the motors 35 , 35 'is reduced. Driving each grinding wheel 32 , 34 directly can further reduce motor size compared to known systems that require belt or sprocket drive means. Furthermore, the current required for grinding, and thus the function of each grinding wheel for each motor, can be measured to determine the percentage ratio of work performed by each motor.

When the grinding wheels 32, 34 are driven directly, the inertia of the drive system in comparison to prior art systems which have a large motor, which is disposed away from the grinding wheels with a number of belts or chains, which connect the motor to a gear box, which controls the direction of the grinding wheels. The reduced inertia of a directly driven system improves the speed and the initiation of a reversal of the grinding wheels 32 , 34 . By rapidly reversing the grinding wheels 32 , 34 , a directly driven system can significantly reduce the process time if reversal is required.

As best shown in FIG. 7, the motor 35 can be attached next to the cover 40 . The shaft 42 of the motor 35 extends through an opening formed within the cover and leads into the grinding chamber 44 which is formed through the cover 40 where it is coupled to the grinding wheel 32 , 34 . The energy is supplied to the motor 35 in a conventional manner by cables which are connected to the motor 35 via a connection box 46 . In order to protect the components of the motor 35 , a housing 48 is provided which essentially covers the outer surfaces of the motor 35 . To help collect and remove the particles, the cover 40 seals tightly around the grinding wheels 32 , 34 . The cover 40 can essentially form an opening 50 , which is arranged radially outward of the axes of rotation of the grinding wheels 32 , 34 and is spaced from them in such a way that the grinding surfaces 52 , 54 of the grinding wheels 32 , 34 are exposed. Furthermore, cover 40 may form an opening 55 that is axially spaced from grinding wheels 32 , 34 to allow access to interior 44 of cover 40 for cleaning, repair, or replacement of grinding wheels 32 , 34 . During operation, the axially spaced opening 55 can be closed by a suitable cover 58 .

The cover 40 can be provided with a suction nozzle 60 which is connected to a vacuum source and which opens into the interior of the cover 40 for the purpose of removing particles which arise during the grinding process. If the cover 40 has a curved wall 61 , as shown in FIG. 4, the nozzle 60 can open tangentially into the chamber 44 , as can best be seen in FIG. 5. A nozzle 60 may be integrally molded with the cover 40 and fluidly connected to the vacuum source through a hose 62 . To further aid in the removal of particles, a nozzle 64 may contain a fluid, e.g. B. Air, directly to the tire T to try to remove particles hanging within the profile of the tire T or on the surface S of it. The nozzle 64 is in fluid communication with a source remote from the grinding wheel 32 . The nozzle 64 can be arranged outside or inside the cover 40 . Preferably, the nozzle 64 is located near the tire T and can be positioned to be centered within the vacuum flow generated by the vacuum source, as described in a co-pending application mentioned above.

The cover 40 is open towards the tire T and leaves a region of the grinding wheels 32 , 34 towards the tire T. Sensor 37 may be attached to or near cover 40 to determine the amount of material that has been removed from tire T. The sensor 37 is connected to the controller 39 , which controls the movement of the grinding wheels 32 , 34 accordingly.

As material is removed from the tire T, the front grinding wheel 32 is brought into contact relative to the rotation of the tire T, and the trailing grinding wheel 34 located behind the front grinding wheel 32 comes into contact with the tire T shortly thereafter. The grinding wheels 32 , 34 can rotate about their respective axes of rotation in the same direction, or they can rotate in opposite directions to each other. For example, as shown in FIG. 2, the front grinding wheel 32 can rotate clockwise and the trailing grinding wheel counterclockwise. Depending on the respective tire T, the rotation of the grinding wheels 32 , 34 can be changed relative to the direction of rotation of the tire T. For example, each grinding wheel 32 , 34 may have its own motor 35 , with each motor driving the grinding wheel 32 , 34 either clockwise or counterclockwise. Alternatively, belts, gears, or other known means can be used to control the direction of rotation of both grinding wheels 32 , 34 when a single motor is used.

As previously mentioned, the position of the arms 16, and thus the grinding heads 30 , can be controlled by selectively extending or retracting the arms using the linear actuator 20 . The extension of the arms 16 can be used to simultaneously bring both grinding wheels 32 , 34 of the grinding head into contact with the surface S of the tire T. In this way, the grinding head 30 , which is directly driven by a single actuator 20 , is brought into contact with the tire T. Once contact is made, the front and trailing grinding wheels 32 , 34 remove material from the tire T in a sequential manner. The front grinding wheel 32 can remove most of the material, and the trailing grinding wheel 34 removes any lip L or irregularity left by the front grinding wheel 32 . As soon as enough material has been removed from the tire T, the linear actuator 20 pulls the arm 16 back, pulling the grinding wheels 32 , 34 away from the tire T. When the axes of the grinding wheels are laterally aligned, the grinding wheels 32 , 34 are retracted from the surface S of the tire T substantially simultaneously.

Because grinding may be required on the profile, on the side wall or on the shoulder located therebetween, the grinding head, which has a cover 40 and a motor 35 , is arranged pivotably about an axis 70 . In the illustrated embodiment, end 28 of arm 16 is connected to cover 40 of grinding head 30 at a pair of hinge points 72 , 74 located on either side of cover 40 . As Fig. 5 shows, the pivot points 72, be arranged aligned 74 generally near the base 76 of the motor 35 and substantially to the upper portion 78 of the cover 40 can. A pivot adjustment 80 can be arranged between the arm 16 and the housing of the motor 35 , the deflection of the pivot adjustment pivoting the grinding head 30 about the axis 70 , which is formed by the pivot points 72 , 74 . In this way, the grinding wheels 32 , 34 can be rotated to contact the side wall, the shoulder or the profile, if necessary, substantially parallel to the surfaces. It can be seen that, depending on the type of irregularity which is to be removed from the tire T, the grinding surfaces 52 , 54 of the grinding wheels 32 , 34 with the swivel adjustment 80 can be arranged at different angles.

It may be desirable to obtain different surface properties for different tires or for areas of them. Accordingly, a differentiated grinding of the tires T may be required if different tires T are checked in the tire dressing machine. To create the differences in the T tires, the speed and direction of rotation of the grinding wheels 32 , 34 as a whole and relative to each other can be controlled either by controlling the speed of the motors 35 or by using other known means, e.g. B. can be varied by pulley or gear differentials. Alternatively, grinding wheels 32 , 34 with different grain sizes can be selected in order to obtain the desired surface properties.

It can also be seen that the grinding head 30 and the motor head 35 can be retrofitted to existing grinding devices with little or even no changes.

An alternative grinding device, which is generally designated by reference number 110 , is shown in FIGS. 8 to 11A. The grinder 110 includes an arm 116 that has an end 128 that has a pair of spaced apart parts 129 that are pivotally connected to the arm 116 at an articulation point. A grinding head 130 is arranged essentially between the parts 129 , 129 and is pivotably held on these. Each part 129 has a joint 172 , e.g. B. with bolt 171 to which the head 130 is attached, which forms a pivot axis 170 about which the grinding head 130 pivots.

The pivoting of the grinding head 130 can be motor-driven by using a motor-operated swivel adjustment 180 . The swivel adjustment 180 is coupled to the grinding head 130 or the joints 172 in order to pivot the grinding head 130 about the axis 170 .

For this purpose, the swivel adjustment 180 has a motor assembly, which is provided overall with the reference number 185 . The motor assembly 185 includes a motor 186 that has a shaft 188 that can be directly coupled to the grinding head 130 . In such a configuration, motor 186 may be located on grinding head 130 or on part 129 on each joint 172 .

Alternatively, as shown in FIGS. 8 and 10, the motor 186 may be remote from the hinge 172 and coupled to the grinding head 130 by a coupler 187 , which may include a suitable linkage, cam, chain, or belt. Coupler 187 allows motor 186 to be placed virtually anywhere within the tire planer. If a belt is used, the belt can be guided in a conventional manner by various wheels or pulleys. As shown in FIG. 9, a belt can be placed between the pulleys, which are attached to a bolt 171 and a motor shaft 188 .

As previously mentioned, the motor assembly 185 can be attached substantially anywhere within the tire planer 10 , taking into account the surrounding components and the movement of the grinding head 130 . A suitable location is on arm 116 . As shown in FIG. 10, motor 186 may be located at the end of arm 116 . As shown, motor 186 is attached to one of the parts 129 that hold grinder 130 . The motor 186 can be mounted between the parts 129 behind the grinding head 130 in order to avoid a collision with the movement of the grinding head 130 . In order to rule out a collision with a vacuum hose originating from the grinding head 130 , the motor assembly can be fastened below or radially outside the path of movement H of the hose.

In the embodiment shown in Fig. 10, the motor 186 is attached to the inner surface 129 A of the part 129 and spaced from the grinding head 130 to the rear. Because parts 129 are spaced apart to a greater extent than the walls of a vacuum hose, motor 186 cannot collide with the hose.

In order to receive the motor 186 inside while the coupling of the motor 186 to the grinding head 130 takes place outside the part 129 , the part 129 can be provided with a shaft bore 189 which enables the motor shaft 188 to face the outer surface 129 B of the part 129 to lead. As shown in FIG. 10, the coupler 187 can be secured between the shaft 188 and a bolt 171 , the motor shaft 188 and the bolt 171 extending to the outer surface 129 B to realize the coupling of the motor 186 to the grinding head 130 , whereby the Rotation of the motor shaft 188 causes the grinding head 130 to pivot proportionally. It will be appreciated that the amount of movement can be controlled by the choice of coupler 187 or by changing the diameter of the shafts, bolts or pulleys when using a belt or similar coupler 187 .

Once the grinding head 130 has been brought into a desired position, it can be held in this position by the motor 186 or a suitable braking device. A braking device, which is denoted overall by reference numeral 190 , has a brake 191 . The brake 191 may be located adjacent the grinding head 130 or the joints 172 , 174 to directly apply the braking force and to hold the head 130 in place. Mechanically advantageously, the brake 191 can be arranged at a distance from the pivot axis 170 in that the braking force is exerted via a lever arm which is generated by the brake part 192 .

The brake member 192 may be secured to the grinding head 130 and extending from the grinding head 130 to the brake 191st In the illustrated embodiment, the brake member 192 is connected to the cover 140 side, extends rearward from the grinding head 130, and is located between the pad 193 and the brake 191 . If the brake 191 does not move with the pivoting of the head 130 , e.g. B. when attached to an object that is stationary with respect to the grinding head 130 , e.g. B. on arm 116 or on part 129 , the brake part 192 can be provided with an extension 194 which is in a position in which the brake 191 can exert force on the part 192 when the head 130 is pivoted. For this purpose, the extension 194 extends outward from the brake part 192 to form a surface 196 on which the brake 191 can act. It can be seen that the extension 194 need not be continuous and simply forms a number of tabs that correspond to the set positions.

In the embodiment shown, the extension 194 and the brake part 192 are combined to form an approximately casual-shaped part with a coherent curved outer edge 197 . The contiguous nature of the edge 197 of the extension 194 creates an indefinite number of points along the extension 194 to which the braking force can be applied. The curved edge 197 is formed along a constant radius from the axis 170 , which provides a distance for the rotation of the extension 194 relative to the axis 170 between the blocks 193 . The arc length of the edge 197 is determined by the range of motion required for the grinding head 130 or, in other words, by the required size of the pivoting. It can be seen that with the extension 194 , which lies between the blocks 193 over the entire range of motion of the grinding head 130 , the grinding head 130 can be held in place at any point therein by applying a braking force to the braking part 192 .

It can be seen that the brake assembly 190 can be arranged at almost any location with a suitable guidance of the brake part 192 . As shown, the brake 191 is arranged next to the motor 186 on the inside 129 A of the part 129 . For a good fastening of the brake part 192 to the grinding head 130 , the blocks 193 and the brake part 192 are arranged such that the distance 195 between the blocks 193 lies in the same plane as the brake part 192 . In this way, the brake member 192 can move freely when it is pivoted with the grinding head 130 .

In operation, the grinding head 130 can be in a rest position, which is shown with solid lines. By activating the motor assembly 185 , the grinding head 130 can be in a pivoted position, e.g. B. are moved to position 130 '. In order to hold the grinding head 130 in the rest position or in the pivoted position, the brake assembly 190 can exert a braking force directly on the grinding head 130 or on the braking part 192 . When a brake member 192 is used that is attached to the grinding head 130 , the brake 191 applies the braking force to the brake member 192 . In the illustrated embodiment, in which the brake part 192 is attached directly to the grinding head 130 , the pivoting of the grinding head 130 into the pivoted position 130 ′ causes the brake part 192 to also be pivoted into a pivoted position 192 ′. When the brake member 192 rotates, the extension 194 remains between the pads 193 and allows the braking force to act thereon. Thus, when the grinder 130 reaches the appropriate position, the pads 193 can engage the extension 194 to hold the extension 194 and the grinder 130 in a selected position. In this way, the grinding head 130 can be pivoted and held in a number of positions by the pivot adjustment 180 .

Because the parts 129 are also pivotally attached to the end 128 of the arm 116 , a similar motor and brake assembly can be used to adjust the distance between the opposing grinding heads 130 , 130 . In any case, the amount of pivoting or leveling of the grinding head 130 for a particular tire can be automatically adjusted by connecting these assemblies to the controller C of the tire dressing machine. The controller C can command the motor assembly 185 to adjust the pan and distance, and this adjustment can be automated using feedback from the various sensors in the tire planer to ensure proper positioning.

As explained above, the grinding device 110 can be held on a frame F. As in the aforementioned embodiment, the grinding device 110 can be connected to the frame F by a drive 112 . Drive 112 may be provided with a hinge 114 to which grinder 110 is pivotally coupled to facilitate access to the assemblies of grinder 110 . If e.g. For example, if the grinding wheels 132 , 134 need to be replaced, the grinding device 110 can be pivoted away from the tire T around the joint 114 in order to gain access to the grinding wheels 132 , 134 .

An alternative retention system may be used to provide access to the grinding wheels 132 , 134 and to improve the stability of the grinding device 110 . For example, the grinder 110 may be coupled to a tire dressing machine 110 at more than one point. As FIG. 8A shows, a holding device 100 with a first frame part 101 is, for. B. connected by screws 102 and provided with a joint 103 with which the drive 112 is pivotally coupled. The drive 112 can be provided with a first holding part 104 , which has a joint 114 at its end 105 , which connects the drive 112 to a joint part 103 , which is fastened to the frame part 101 , or extends from it and a first point for coupling for forms the grinder 110 . A second holding part 106 extends opposite the first holding part 104 from the drive 112 to a second frame part 107 . The second holding part 106 forms an additional fastening point, which can be designed to be detachable in order to enable the grinding device 110 to be pivoted, as described above. For this purpose, the second holding part 106 is provided with a stop part 108 , which can have a buffer B for the purpose of contact with the second frame part 107 . The stop part 108 can be provided with an extended region 109 which extends over the outer surface of the second frame part 107 in order to obtain an additional surface for fastening the drive 112 to the second frame part 107 by means of a suitable locking device, as described above.

Any number of possible devices can be used to clamp the stop part 108 to the second holding part 106 with the second frame part 107 or to fix it in another way. The second holding part 106 can directly with the frame F z. B. be fastened by screws in a similar manner to the holding device 100 . As shown in Figs. 8, 8A, 11, 11A and 12, a locking device can be used for this purpose. A locking device, which is designated overall by the reference numeral 200 , may have a holding part 201 , which on the frame part 107 z. B. is fixed by welding or by connectors which have a receptacle 202 . A locking element 203 , which is held by the second holding part 106 , has a functional connection to the receptacle 202 in order to couple the second holding part 106 to the second frame part 107 .

In one embodiment, shown in FIG. 11, the locking element 203 comprises a threaded area 208 . In this locking device 200 , as soon as the second holding part 106 has been brought into engagement with the frame part 107 , this is locked by screwing the locking element 203 into the receptacle 202 . The locking member 203 may be provided with a clamping part 204 which has been fitted on the stop 108, that the screwing of the locking element exerts 203 into the receptacle 202, a clamping force between the abutment and the receptacle 202 that the second holding part 106 locked to the frame part 107 , To the application of clamping forces to facilitate means of the threaded locking element 203, the locking member may be provided with a handling 209 203, which extends from the threaded stop 108 to the outside, in order to improve the mechanical handling. It can be seen that other locking assemblies, e.g. B. a C-bracket can be used in the same way. In order to facilitate this type of attachment, the stop 108 can be provided with an elongated region 109 which extends over a plane which is formed by the sides of the second frame part 107 , and the holder 201 can be on the side of the frame part opposite the extended area 109 of the stop 108 are fastened in such a way that the clamping forces are exerted between the holder 201 and the extended area 109 of the stop 108 .

An alternative locking device 200 'is shown in FIG. 11A. Like the locking device 200 , the locking device 200 'comprises a holder 201 which is connected to the second frame part 107 . The alternative locking device 200 'is a latching assembly. In this case, however, the locking element 203 is an arm 250 , which is used to exert the clamping force on the stop 108 . The locking element 203 'comprises a handle 209 ', an arm 250 and a connection 251 which is interposed between the arm 250 and the handle 209 '. Actuation of the handle 209 'causes the link 251 in the manner of a driver to bring the arm 250 into contact with the stop 108 in order to exert a clamping force thereon. In the embodiment shown in FIG. 11A, the arm 250 is provided with a roller 252 , which is suitably attached to the locking element 203 ', e.g. B. is held by a screw 253 and a nut 254 . In this way, the clamping force is exerted by the locking element 203 'via the roller 252 . The roller 252 may allow the grinder 110 to be vertically adjusted while the locking device 200 'is engaged. As can best be seen from FIG. 8, the first holding part 104 can be displaced with the first adjusting part 101, for. B. by a socket-like construction or by a rail assembly 257 , such as. B. THK rails to allow such vertical adjustment of the grinding device 110 . The vertical adjustment of the grinding device 110 can be carried out manually or automatically. For automatic adjustment, an actuator 258 , e.g. B. a linear actuator or an electric or pressure actuated cylinder act on the drive 112 to raise or lower the grinder 110 . As can be seen from FIG. 8, a cylinder, which is shown schematically as a circle, interacts with a part 259 of the drive 112 next to the first side frame part 101 . The cylinder 259 acts in a vertical direction to adjust the position of the grinder 110 and can continuously adjust this position based on feedback from the controller C. A brake assembly, generally designated 260 , may be used to hold the grinder 110 in the desired vertical position. To facilitate the use of the brake assembly 260 , a vertically oriented part 261 may extend outwardly from a frame part, e.g. B. a second frame part 107 to cooperate with the brake assembly 260 . Generally, the brake assembly includes a brake 262 having a seat 263 through which the vertical member 261 can pass and brake pads adjacent the seats 263 to apply a braking force to the vertical member 261 . While, as shown in FIG. 8, the brake 262 on the grinder 110 , e.g. B. can be held by a second bracket 106 , it can be seen that the positions of the brake 262 and the vertical part 261 can be reversed. In this case, the grinder 110 absorbs the braking force to hold it in place. A fail-safe brake 260 can be used to provide additional safety. It can e.g. For example, a pneumatic or hydraulic brake 262 can be used which has brake pads that remain engaged when the pressure conditions within the brake 262 are zero. As a result, when the system loses pressure, the brake 262 remains engaged and the grinder is held in place. To release the brake, a suitable source, e.g. B. an initiator, which can be attached to the frame F or the grinding device 110 and has a fluid connection to the brake 262 , exerted a pressure.

With regard to the functional conditions, the brake assembly 260 must be released before the vertical adjustment of the grinding device 110 is carried out or before the grinding device 110 is pivoted out about the joint 114 . It should be noted that the clamping force exerted by the locking device 200 'must be removed before the grinding device 110 can be pivoted out. In Fig. 11A best seen that when the locking device 200 '(which is in dashed lines) in the released position, the locking member 203' and the roller are pivoted away 252 of the second bracket 106, to provide clearance for pivoting the grinder to create hinge 104 . Specifically, the roller 252 is pivoted away from the second holder 106 such that the stop 109 releases the roller 252 when the grinding device is pivoted about the joint 104 , e.g. B. is pivoted to replace the grinding wheels 32 , 34 .

As can be seen, the grinding device 110 is held on the frame F with greater stability when the first and second holding parts 104 , 106 are coupled to the first and second frame parts 101 , 107 . Furthermore, by fastening to the first and second lateral frame parts 101 , 107, the grinding device 110 can be centered between the frame parts 101 , 107 and the grinding head 130 can be used to tire T along a line L, which runs relative to the frame parts 101 , 107 , and passes through the central axis CA of the tire T, are passed directly to the tire T. In this way, the grinding head 130 is guided linearly to the tire, which improves the ability of the two grinding wheels to make contact with the tire T substantially simultaneously. Any adjustment of the fastening direction of the grinding wheels can be carried out by adjusting the locking device 200 or by inserting wheels between the frame parts 101 , 107 and the holding device 100 and the stop 108 .

An alternative grinder 310 , which is similar to grinders 10 and 110 , is shown in FIGS. 12 and 13. The grinding device 310 comprises a drive 312 which is held on the frame F and is provided with a joint 314 and which enables the radial adjustment of the drive 312 and the pivoting of the grinding device 310 in the radial direction in order to gain access to the grinding head 330 . As in the previous embodiments, the grinding head 330 may have a first grinding wheel 332 and a second grinding wheel 334 or a single grinding wheel 332 . The grinding wheels 332 , 334 are equipped with one or more motors 335 z. B. coupled via a belt B. It can be seen that the grinding wheels 332 , 334 can be driven directly, as described above.

The grinder 310 shown in Figures 12 and 13 is often referred to as a CARE grinder (classifying and eccentricity reducing grinder) or a centering grinder, and due to its location within the frame F, it can be in a substantially fixed position relative to Tires T are kept. As a result, it may not be necessary to drive the grinding wheels 332 , 334 of the grinding device 310 toward the tire T or away from it. For this reason, as shown, the grinding head 330 can be held in a substantially fixed axial position, with some manual adjustments being possible through the stops 336 located on the rails 338 . Alternatively, the grinder 310 can be moved toward or away from the tire T, as described in the previous embodiments. In addition, as previously mentioned, the grinding device 310 can be designed to be movable in the vertical direction.

As in the previous embodiments, the grinding device 310 can be provided with a first holding part 304 which is pivotally attached to the first frame part 301 with a joint 314 . A second holding part 306 can extend from the drive 312 on the side opposite the joint 314 in order to be connected to a second frame part 307 . In accordance with the previous embodiments, the second holding part 306 can be provided with a locking device 400 . For the details of the locking device 400 , reference is made to the locking devices described above, which are illustrated in FIGS. 11 and 11A. As shown in FIG. 12, when the center drive 312 of the grinder is larger, the latch 400 may be held on one side of the drive 312 . In this embodiment, the second holding part 306 is omitted. As described in connection with the previous embodiments, the use of two frame parts 301 , 307 for holding the drive 312 creates a more stable and secure holding system for the grinding device 310 . The centering grinder 310 also has the advantage of being pivotable so that a user has access to the grinding head 330 to perform repairs or to replace the grinding wheels 332 , 334 .

Claims (26)

1. Grinding device ( 10 , 110 , 310 ) in a tire dressing machine, which has a frame (F) with a first side frame part ( 101 ; 301 ) and a second side frame part ( 107 ; 307 ), and the frame (F) has a tire (T) for testing, which has a central axis (CA), the grinding device ( 10 , 110 , 310 ) comprising: a drive ( 12 , 112 , 312 ) which is pivotally connected to the first side frame part ( 101 ; 301 ) and a locking device ( 200 , 200 ', 400 ) adjacent to the drive, the second side frame member ( 107 ; 307 ) selectively coupling the drive ( 12 , 112 , 312 ) to the second side frame member ( 107 ; 307 ) when the drive ( 12 , 112 , 312 ) is in the working position; a grinding head ( 30 , 130 , 330 ) which is held at one end of the drive ( 12 , 112 , 312 ), the grinding head ( 30 , 130 , 330 ) having at least one grinding wheel ( 32 , 34 ; 132 , 134 ; 332 , 334 ) and has at least one motor ( 35 , 35 ', 335 ) which is coupled to the grinding wheel ( 32 , 34 ; 132 , 134 ; 332 , 334 ) and causes its rotation. 2. Grinding device ( 10 , 110 , 310 ) according to claim 1, wherein the locking device ( 200 , 200 ', 400 ) has a locking element ( 203 , 203 ') and a receptacle ( 202 ) which can be selectively brought into engagement, to lock the drive ( 12 , 112 , 312 ) with the second side frame part ( 107 ; 307 ), either the receptacle ( 202 ) or the locking element ( 203 , 203 ') on the second side frame part ( 107 ; 307 ) or the drive ( 12 , 112 , 312 ) are held. 3. Grinding device ( 10 , 110 , 310 ) according to claim 2, in which the locking element ( 203 , 203 ') is held by means of a thread in the receptacle ( 202 ), the locking element ( 203 , 203 ') comprising a threaded region and a Handling ( 209 , 209 '), which facilitates the rotation of the thread area. 4. Grinding device ( 10 , 110 , 310 ) according to claim 1, wherein the locking device ( 200 , 200 ', 400 ) comprises a locking assembly which has a handling element ( 209 , 209 ') which is functional with the locking element ( 203 , 203 ') is coupled, the locking element ( 203 , 203 ') selectively exerting a tensioning force on the drive ( 12 , 112 , 312 ) and the frame (F), and the application of the tensioning force on the drive ( 12 , 112 , 312 ) Holds frame (F). 5. Grinding device ( 10 , 110 , 310 ) according to claim 4, wherein the locking element ( 203 , 203 ') holds a roller ( 252 ), wherein the clamping force is exerted on the roller ( 252 ) and the roller ( 252 ) so aligned is that a vertical movement of the drive ( 12 , 112 , 312 ) is possible. 6. Grinding device ( 10 , 110 , 310 ) according to claim 5, wherein the drive ( 12 , 112 , 312 ) is movable in the vertical direction and the grinding device ( 10 , 110 , 310 ) further comprises a vertical locking device ( 200 , 200 ', 400 ), which has a brake assembly ( 260 ) which is held on the drive ( 12 , 112 , 312 ) or the side frame part, and a vertical locking element which on the other, ie the drive ( 12 , 112 , 312 ) or the side frame member, the vertical locking member being received in the brake assembly ( 260 ) and the brake assembly ( 260 ) selectively applying braking force thereon to adjust the vertical position of the drive ( 12 , 112 , 312 ) relative to the side Fix the frame part. 7. Grinding device ( 10 , 110 , 310 ) according to claim 6, wherein the brake assembly ( 260 ) has a fail-safe brake. 8. Grinding device ( 10 , 110 , 310 ) according to claim 6, wherein the drive ( 12 , 112 , 312 ) is coupled to at least one of the side frame parts by a straight rail to prevent movement of the drive ( 12 , 112 , 312 ) to allow in the vertical direction. The grinder ( 10 , 110 , 310 ) of claim 6, further comprising an actuator that acts on the drive ( 12 , 112 , 312 ) to cause it to move vertically. 10. Grinding device ( 10 , 110 , 310 ) according to claim 9, wherein the actuator is in communication with a controller which feeds back its position, whereby the vertical position of the grinding device ( 10 , 110 , 310 ) is automatically adjusted. 11. Grinding device ( 10 , 110 , 310 ) according to claim 1, wherein the drive ( 12 , 112 , 312 ) comprises a first and a second holding part, which from opposite sides of the drive ( 12 , 112 , 312 ) to the outside extend the first and second lateral parts, whereby the first holding part ( 104 , 304 ) is pivotally connected to the first frame part ( 101 ; 301 ) and the second holding part ( 106 , 306 ) faces the second frame part ( 107 ; 307 ), when the drive ( 12 , 112 , 312 ) is in a working position, whereby the locking device ( 200 , 200 ', 400 ) fixes the second holding part ( 106 , 306 ) to the second lateral frame part ( 107 ; 307 ). 12. The grinder ( 10 , 110 , 310 ) of claim 11, further comprising a stop ( 108 ) disposed at one end of the second support member ( 106 , 306 ), a portion of the stop ( 108 ) extending from one plane extends outwards, which is formed by one side of the second frame part ( 107 ; 307 ); and a holder extends from the second lateral frame part ( 107 ; 307 ), which lies opposite at least a region of the stop, as a result of which the locking device ( 200 , 200 ', 400 ) couples the region of the stop to the holder in order to secure the second holding part ( 106 , 306 ) on the second side frame part ( 107 ; 307 ). 13. Grinding device ( 10 , 110 , 310 ) according to claim 12, further comprising a buffer, which is arranged between the second lateral frame part ( 107 ; 307 ) and the stop ( 108 ). The grinding device ( 10 , 110 , 310 ) according to claim 11, further comprising an arm held on the drive, the grinding head ( 30 , 130 , 330 ) being held on the arm, whereby the grinding head ( 30 , 130 , 330 ) is pivotally attached to the arm about an axis, and the grinder further comprises a pivot adjustment ( 80 , 180 ) held on the arm having a motor assembly ( 185 ) operatively coupled to the grinding head, wherein the activation of the Motor assembly ( 185 ) causes the grinding head ( 30 , 130 , 330 ) to pivot about the axis. The grinder ( 10 , 110 , 310 ) of claim 14, further comprising a brake assembly having a brake that is operable to hold the grinder head ( 30 , 130 , 330 ) in a selected position. 16. Swivel adjustment ( 80 , 180 ) in a tire dressing machine, which checks a tire (T) on its circumference, the tire dressing machine having a grinding head ( 30 , 130 , 330 ) which is held on an arm with a joint, and around a Is pivotable, which extends through the joint parallel to a tangent to the circumference of the tire, and the pivot adjustment ( 80 , 180 ) comprises a motor assembly ( 185 ) which is held on the arm and functional with the grinding head ( 30 , 130 , 330 ) is coupled, wherein the activation of the motor assembly ( 185 ) causes the grinding head ( 30 , 130 , 330 ) to pivot about the pivot axis. 17. The swivel adjustment ( 80 , 180 ) of claim 16, wherein the hinge includes at least one pin about which the grinding head ( 30 , 130 , 330 ) pivots, and the motor assembly ( 185 ) comprises a motor with a motor shaft, the pin and the motor shaft are coupled by a clutch. 18. swivel adjustment ( 80 , 180 ) according to claim 17, wherein the coupling consists of a belt having a first end which is functionally connected to the motor shaft, and a second end which is functionally connected to the bolt. 19. Swivel adjustment ( 80 , 180 ) according to claim 18, wherein the belt at each of its ends is attached to the bolt and the shaft by a pair of pulleys, respectively. 20. pivot adjustment ( 80 , 180 ) according to claim 16, wherein the coupling is arranged on an outer surface of the arm. 21. The pivot adjustment ( 80 , 180 ) of claim 16, wherein the arm has a pair of spaced apart portions and the grinding head ( 30 , 130 , 330 ) is secured between the pair of spaced apart portions and the motor assembly ( 185 ) is attached to at least one the parts are fixed and spaced from the hinge, the motor assembly ( 185 ) being coupled to the grinding head ( 30 , 130 , 330 ) by a coupling extending from the motor to the grinding head ( 30 , 130 , 330 ) outside of one of the spaced apart Parts extends. 22. Swivel adjustment ( 80 , 180 ) according to claim 21, wherein the motor is attached to an inner surface of one of the spaced parts; one of the spaced parts forming a bore for receiving a motor shaft extending from the motor to the outside of the spaced part, and the shaft being coupled to the grinding head ( 30 , 130 , 330 ) through the coupling. 23. The swivel adjustment ( 80 , 180 ) of claim 16, further including a brake assembly operable to hold the grinding head ( 30 , 130 , 330 ) in a selected position; and the brake assembly includes a brake that is selectively coupled to the grinding head ( 30 , 130 , 330 ), and the brake assembly exerts a braking force on the grinding head ( 30 , 130 , 330 ) through the clutch. 24. Swivel adjustment ( 80 , 180 ) according to claim 17, wherein the brake assembly further includes a braking element extending from the grinding head ( 30 , 130 , 330 ) to the brake, whereby the brake exerts the braking force on a portion of the braking element. 25. swivel adjustment ( 80 , 180 ) according to claim 24, wherein the braking element is coupled such that the braking element pivots with the grinding head ( 30 , 130 , 330 ); wherein the braking element has an extension that extends radially outward from the braking element; and the braking force is applied to this extension in such a way that the braking force is applied to several points on this projection which correspond to different pivoting angles of the grinding head ( 30 , 130 , 330 ). 26. Swivel adjustment ( 80 , 180 ) according to claim 24, wherein the extension has a curved edge that has a constant radius with respect to the pivot axis of the grinding head ( 30 , 130 , 330 ).