Dynamic balancer with frameless motor drive

Abstract

To collect and process detected forces in a meaningful manner to properly identify the position and amount of tire imbalance.SOLUTION: A dynamic balancer includes an outer housing and a spindle assembly rotatably mounted to the outer housing. A frameless motor assembly is connected to selected components of the spindle assembly. A chuck assembly receives a locking member to capture a tire therebetween. The chuck assembly and the locking member are captured within the spindle assembly and rotated by the frameless motor assembly. A spring-biased return cylinder may be used with the dynamic balancer to assist in capturing and releasing the locking member with respect to the chuck assembly. An adjustable encoder assembly may be associated with the motor assembly to monitor a rotational position of the tire and / or the spindle assembly.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] [Cross - Reference to Related Applications] This application claims priority to U.S. Provisional Patent Application No. 62 / 731,238, filed on September 14, 2018. This application is hereby incorporated by reference herein in its entirety.

[0002] [Technical Field] The present invention relates to a dynamic balancer. In particular, the present invention relates to a dynamic balancer that uses a frameless motor drive unit when determining the balance state of a tire rotated by the balancer.

Background Art

[0003] Generally, manufactured tires are subjected to certain inspections before being released to the market for public sale. Such inspections include rotating the tire at high speed to measure the balance of the tire. The mechanical device used to measure the balance of the tire needs to fix the tire in a predetermined position, inflate it, and then detect the force during the rotation of the tire while rotating the tire at high speed.

Summary of the Invention

Problems to be Solved by the Invention

[0004] Conventional devices typically use a load cell to detect axial forces relative to the rotation of the tire. Although effective for the aforementioned purposes, it is considered possible to obtain a more accurate determination value for the balanced state. For example, a common problem with conventional dynamic balancers results from the mechanism used to rotate the tire to determine the balance state. Almost all balancers utilize a laterally mounted motor that rotates a belt coupled to a spindle assembly that rotates the tire. The laterally mounted drive motor is effective, but it introduces a radial force into the spindle assembly, which must be compensated for so as not to adversely affect the sensors that determine the balance state of the tire. This compensation can be done by applying a balancing force, or by using a computer process that uses sensors to determine the added force and adjusts the measured force, or by a combination of both. Some dynamic balancers avoid the use of laterally mounted motors by employing a drive motor housing and an armature. However, such configurations still employ opposing suspension springs, which become unbalanced after minimal use and introduce forces into the spindle assembly, which must be compensated for, and each of which results in distortion in the load cell measurement.

[0005] Another drawback of conventional dynamic balancers is the manner in which the tire is fixed to the mechanical device before rotation. Conventional chuck locking mechanisms employ ball bearings between an outer sleeve and an inner sleeve to hold the tire in place. Unfortunately, the bearings can easily become misaligned, and the sleeves may not engage with each other.

[0006] Accordingly, there is a need in the art for an improved tire balancer that detects forces in the horizontal plane relative to the rotation of the tire. There is also a need to collect and process the forces detected in a meaningful manner to appropriately identify the location and amount of the unbalanced state of the tire.

Means for Solving the Problems

[0007] In view of the above, a first aspect of the present invention is to provide a dynamic balancer having a frameless motor drive unit.

[0008] Another aspect of the present invention is an outer housing, a spindle assembly rotatably attached to the outer housing, a frameless motor assembly connected to a selected component of the spindle assembly, a chuck assembly for receiving a locking member to capture a tire therebetween, comprising wherein the chuck assembly and the locking member are captured within the spindle assembly and rotated by the frameless motor assembly characterized by a dynamic balancer, and is to provide.

[0009] Yet another aspect of the present invention is a drive brake air mechanism configured to be used with a dynamic balancer having a locking shaft having an air supply hole for inflating a tire received by the dynamic balancer, a coupling fitting adapted to be received within the air supply hole, a system housing holding a manifold having an air coupling portion at one end, a linear actuator coupled to the manifold for selectively moving the air coupling portion in and out of engagement with the coupling fitting, comprising wherein the air coupling portion is selectively connected to the coupling fitting, both the air coupling portion and the coupling fitting are sealed when disengaged from each other and released when coupled to each other characterized by a drive brake air mechanism, and is to provide.

[0010] Yet another aspect of the present invention is A chuck assembly capable of engaging with a locking shaft, a lower rim having a shaft opening for receiving the locking shaft and at least one tooth cavity, at least one wedge-shaped jaw movable radially within a corresponding one of the at least one tooth cavity, the wedge-shaped jaw having jaw teeth engageable with the locking shaft when received within the shaft opening on one side, at least one wedge-shaped sleeve slidably engageable with the opposite side of the at least one wedge-shaped jaw, comprising, axial movement of the at least one wedge-shaped sleeve moves the at least one wedge-shaped jaw in and out of engagement with the locking shaft characterized in that it provides a chuck assembly.

[0011] Yet another aspect of the present invention is, a spring-biased return cylinder configured to be used with a dynamic balancer having a spindle shaft extending axially through a rotatable spindle assembly, a main cylinder having a shaft opening for receiving the spindle shaft and an outer radial shelf, an outer cylinder surrounding the main cylinder and having an inner spring shelf, having, the inner spring shelf faces the outer radial shelf and forms an annular spring cavity for receiving a cylindrical spring therebetween, the main cylinder is configured to be axially movable to axially move the spindle shaft characterized in that it provides a spring-biased return cylinder.

[0012] Yet another aspect of the present invention is, a motor assembly having a motor housing with a stator fixed and a rotor rotatably received within the stator, An attachment plate fixed to the motor housing and having plate notches, An encoder ring coupled to the rotor and rotating with the rotor, An adjustment mechanism that is maintained within the plate notches and holds a reading head movable relative to the encoder ring, and an encoder assembly characterized by including the same.

[0013] These and other features and advantages of the present invention will be better understood in connection with the following detailed description, the appended claims, and the accompanying drawings.

Brief Description of the Drawings

[0014]

Figure 1

Figure 1A

Figure 2

Figure 3A

Figure 3B

Figure 3C

Figure 4

Figure 5A

Figure 5B

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

DETAILED DESCRIPTION OF THE INVENTION

[0015] Referring to the drawings, and in particular to FIGS. 1, 2, 3A, 3B and 3C, a dynamic balancer is generally indicated by reference numeral 20. Whenever any part of the specification is read, these specific drawings should be referred to. Where appropriate, individual specific references are also made to the relevant drawings. It will be understood that any of the drawings may illustrate the item being described. As will be understood by those skilled in the art, the dynamic balancer tests toroidal bodies such as pneumatic tires. Generally, the balancer 20 includes a floor support frame 22 (partially shown) with suitable structural features such as legs and cross members for holding the balancer. Those skilled in the art will understand that the frame can be bolted or otherwise fixed to the floor to minimize exposure to external forces.

[0016] An outer housing 24 can be held by the frame 22 and supports the main components of the dynamic balancer. At least one load cell 26 can be interposed between the frame 22 and the outer housing 24. In this embodiment, four load cells 26 can be spaced around the outer housing - substantially every 90° or in other suitable manners - and are used to detect and collect force measurement data during rotation of the tire by the balancer, as will be described in detail as the description proceeds. The configuration and arrangement of the load cells relative to the frame can be as described and shown in U.S. Patent Application No. 15 / 345,648, filed November 8, 2016. This document is hereby incorporated by reference into this specification. In this embodiment, the operating interface of the load cells between the balancer 20 and the frame 22 is the only intentional interface between the two in order to substantially eliminate the application of external forces to the operating balancer. As a result, the balance state of the tire can be obtained while minimizing interfering external forces incorporated into the balance measurement by the load cells.

[0017] The main components of the balancer 20 may include a locking member 30 associated with and positioning one side of the tire (T), particularly the tire bead. FIG. 2 shows the locking member 30 being received in the chuck (chucking) assembly. The chuck assembly is generally indicated by reference numeral 32. The chuck assembly grips the locking member and positions and captures the bead on the opposite side of the tire. And the chuck assembly 32 can be attached between the locking member and the chuck assembly and housed within a spindle assembly 34 that rotates the chuck assembly and the tire. The spindle assembly 34 can be rotated by a frameless motor assembly 40, and the rotational position of the rotating tire is detected and monitored by an encoder assembly 42 coupled to the frameless motor assembly 40. A spring-biased return cylinder 46 is associated with the frameless motor assembly and assists in releasing and capturing the locking member 30 in conjunction with the chuck assembly 32, as will be described in detail.

[0018] As best shown in FIG. 3A, the locking member 30 includes a locking shaft 50 that provides an outer (outward) taper portion 52 at one end. Those skilled in the art will understand that a dry brake air system (described below) can be connected to the taper portion 52 and / or adjacent portions of the shaft 50 for the purpose of moving the locking member in and out of the chuck assembly 32 to inflate / deflate (deflate) the tire. The locking shaft moves vertically in and out of the chuck assembly 32 as the description progresses. At the outward taper end, an air supply hole 54 extends axially within the shaft. Extending through the locking shaft 50 and intersecting and adjacent to the air supply hole 54 is a transverse hole 56. At the end opposite the outward taper portion 52 is a distal end 60.

[0019] In some embodiments, the locking shaft 50 may have a non-circular cross-section, as best shown in FIGS. 4, 5A, and 5B. Such a feature facilitates the engagement and locking between the chuck assembly that receives the shaft and the shaft. Subsequently, both the shaft and the chuck assembly are rotated by the spindle assembly during the balancing operation. In such embodiments, care must be taken to properly angle-adjust the chuck assembly to receive the locking shaft, which can be facilitated by the adjustment between the encoder assembly 42 and the motor assembly 40, as will be described later. In any case, the locking shaft of the present embodiment provides a generally square cross-section, and the shaft 50 provides a plurality of locking side surfaces 63, and each locking side surface is labeled with a corresponding alphabet A-D. Each of the locking side surfaces 63A-D provides a plurality of shaft teeth 64A-D, and gaps 66A-D are provided between each tooth. As a result, the locking side surfaces 63A-63D provide shaft teeth 64 that extend from approximately the midpoint of the shaft 50 to the distal end 60 of the shaft on the side opposite the outward taper portion 52. And the teeth 64 are provided on a plurality of straight surfaces that effectively form the square cross-section of the locking shaft. Thereby, in the present embodiment, the locking shaft provides four side surfaces that facilitate engagement with the chuck assembly 32, as described.

[0020] As best shown in FIGS. 3A, 5A, and 5B, a shaft collar 72 may extend radially from the shaft 50 at a position between the transverse hole 56 and the outward taper portion 52. The shaft collar 72 may be attached to the shaft flange 74 with a fastener, and the shaft flange 74 may be attached to the upper rim 78 that rotates when the locking shaft is rotated with a fastener. The outer annular surface of the upper rim 78 may provide a plurality of radially inner steps 80 to accommodate various tire bead diameters.

[0021] Generally, as is apparent from FIGS. 3A, 7, and 8, the chuck assembly 32 receives and holds the tire by engaging with the locking member 30. When the locking member 30 and the chuck assembly 32 fix the tire therebetween, they are collectively fixed within the spindle assembly 34. Air is transmitted through the air supply hole and the transverse hole 56 to inflate the tire, and then the spindle assembly 34 rotates the captured tire to determine the balance state and other characteristics of the tire.

[0022] Referring now to FIG. 1A, a drive brake air system is shown generally at 500 and is operatively coupled to the dynamic balancer 20. The balancer 20 accommodates a coupling adapter (coupling mate) 504 to accommodate connection to the air system 500. The coupling adapter 504 is received within the air supply hole 43 of the locking shaft 50. As will become apparent as the detailed description proceeds, the coupling adapter 504 is selectively coupled to the brake air system 500 for the purpose of directing compressed air into and out of the air supply hole 43 and the transverse hole 56 to inflate and deflate the tire at the appropriate times.

[0023] The air system 500 includes a system housing 508 that provides the structure necessary to hold the components of the system 500. One of these components is a manifold 512 that provides a conduit 516 for receiving compressed air, as will be described later. At one end of the conduit 516 is an air coupling 520 that is selectively coupled to the coupling adapter 504. Exemplary coupling adapters 504 and air couplings 520 can be provided by Staubli of Switzerland. Their SPC family of connectors provides an exemplary connection system that can be employed.

[0024] Referring to FIG. 1A, one end of the manifold 512 may provide a sealing skirt 524 that partially surrounds the air coupling 520. The sealing skirt 524 includes a sleeve 528 and a bushing 532. The sleeve 528 and the bushing 532 allow for the sliding movement of the air coupling 520 within the manifold 512 at an appropriate timing. A shroud 540 extends from the lower end of the housing 508, which substantially surrounds the sealing skirt 524 to prevent debris from entering the coupling adapter 504 or the air coupling 520. An interface collar 544 is connected to and extends from the lower edge of the shroud 540. The collar 544 includes a mounting shelf 548 that is fixed to the lower end of the shroud 540 by a suitable fastener. A conical flange 552 extends inwardly from the shelf 548 to provide a flange inner surface 556 sized to fit around the tapered portion 52 of the locking shaft. As will be described in detail later, those skilled in the art will understand that the flange inner surface 556 contacts the tapered portion 52 only when the locking shaft is lifted away from the chuck assembly. On the other hand, when the locking shaft is received within the chuck assembly, the flange inner surface is in a non-contact and spaced relationship from the tapered portion 52, and no direct force is applied to the tapered portion. As a result, no external force from the conical flange 552 is applied to the spindle assembly 34 during the balancing operation. In other words, the non-contact relationship between the conical flange 552 and the tapered portion 52 is made such that no force is transmitted between the interfaces of these two parts during the rotation of the locking shaft.

[0025] System 500 may include a linear actuator 564 that can be coupled to an end of the manifold 512 on the opposite side of the sealing skirt 524. An actuator rod 568 extends from the linear actuator 564, and the movement of the actuator rod is controlled by a controller as described hereinafter. In any case, the actuator rod 568 moves the manifold in the vertical or vertical direction. The downward movement of the rod 568 results in the connection of the air coupling 520 to the coupling fitting 504. The upward movement of the actuator rod 568 results in the disconnection of the connection from the coupling fitting 504 of the air coupling 520. Those skilled in the art will understand that the coupling fitting 504 and the air coupling are configured such that both are sealed when disengaged from each other and air can flow between the two in either direction only when they are firmly seated or coupled to each other.

[0026] During operation, at an appropriate timing, the actuator 564 is energized to lower the actuator rod 568 to engage the coupling fitting 504 of the air coupling 520. Generally simultaneously, as described hereinafter, the locking shaft 50 is lowered and locked by the conical flange. Once the air coupling 520 is engaged with the coupling fitting 504, the collar 544 is lowered by an incremental amount and the inner surface 556 of the flange no longer contacts the tapered portion 52. Next, air and / or some other type of gas, which may be compressed, is sent through the manifold conduit 516 into the air supply holes 54 and the lateral holes 56 to seat the tire beads on their respective rims and pressurize the tire under test. When the inflation of the tire is complete, the air coupling 520 is disengaged from the coupling fitting 504, and the tire maintains the pressurized state by the closure of the coupling fitting. Even when the air coupling 520 is disengaged from the coupling fitting 504, the flange surface 556 does not contact the tapered portion 52.

[0027] During rotation of the locking shaft, the tapered portion 52 is close to the flange inner surface 556 but is no longer in contact with the flange inner surface 556. Therefore, no mechanical or other forces are exerted on the rotating parts of the dynamic balancer 10 by the air system 500. When the balancing test is completed, the air coupling disengages from the coupling mating portion 504 and releases the air inside the tire to the surroundings. Next, at an appropriate timing, the actuator rod 568 is lifted, the flange inner surface 556 engages with the tapered surface 52, and the locking shaft is lifted out of the chuck assembly.

[0028] Referring now to FIGS. 3A and 4 through 8, the chuck assembly 32, in most embodiments, includes a lower rim 86 that is substantially a mirror image of the upper rim 78. The lower rim 86 provides a plurality of radially inner steps 88 that conform to the steps 86 of the upper rim so as to accommodate various bead diameters of various tires that can be tested by a dynamic balancer. An inner flange 90 may be connected to the rim 86 by a fastener, may extend radially inwardly from the rim 86, and may provide a shaft opening 92 therethrough for receiving the locking shaft 50. An upper retainer 96 may be fixed or formed as part of the underside of the inner flange 90. The lower surface of the upper retainer 96 provides a plurality of tee cavities 97A - 97D, the number of cavities 97 corresponding to the number of shaft sides 63. Each cavity 97 may provide a pair of opposing undercut tee ridges (T-shaped ridges) 98. Corresponding upper tees 99 are slidably received within the tee cavities 97 at 90-degree increments or other suitable angular increments, depending on the number of shaft sides 63. Each tee 99 has indices A - D, which correspond to the number of sides of the locking shaft 50 that provide the shaft teeth 64A - 64D. Each tee 99 has an outer extending side rail 100 that defines a corresponding side groove 101. Also, each tee 99 has an opening 102 therethrough. And the tee ridges 98 of each corresponding cavity 97 are slidably received within the side grooves 101. Thereby, each upper tee 99 is linearly movable along the lower surface of the upper retainer. In fact, each upper tee is radially movable relative to the locking shaft.

[0029] As best shown in FIGS. 3A and 4 through 8, each upper tee 99 is connected to a corresponding wedge-shaped jaw portion 103A-D, which provides a jaw body portion 104A-D connected to the upper tee 99 by a fastener 107 received within an opening 102. Each jaw body portion 104 has a tee surface 105 at its upper end, and a pair of opposing tee ridges 106 may extend from the side surfaces of the tee surface 105. Thereby, the ridges 106 prevent left and right movement of the upper tee 99 relative to the jaw body portion 104. The jaw body portion 104 also provides a plurality of jaw teeth 108A-D that fit within corresponding gaps 66A-D provided by the shaft teeth 64A-D. In other words, the jaw teeth 108A-D provide a gap 109 therebetween for receiving the corresponding shaft teeth 64. The wedge-shaped jaw portions 103A-D are engaged by the shaft side surfaces 63A-D, whereby the locking member 30 is fixed within the chuck assembly 32. There are jaw inclined surfaces 110A-D on surfaces arranged opposite or at an angle from the jaw teeth 108A-D. Each inclined surface 110 may provide a recess pocket 111 sized to receive a backup plate 112. As best seen in FIG. 5B, an outer extending shelf 113 extends from the longitudinal side surfaces of the plate 112. The outer extending shelf 113, together with the inclined surface 110, forms a gap therebetween. A fastener 114 may extend through the plate 112 for attachment to the jaw body portion 104.

[0030] The wedge-shaped sleeve 117 can be provided with a predetermined number of segments and can be connected to slidably receive adjacent wedge-shaped jaws 103, as best shown in FIGS. 6 through 8, providing structural support thereto when the locking shaft is received within the chuck assembly and also allowing sliding movement within the spindle assembly. As seen in the drawings, two wedge-shaped sleeves of similar shape can be provided and received within the spindle assembly 34 as seen in FIG. 3A, and each wedge-shaped sleeve 117 can be associated with a pair of wedge-shaped jaws 103. In other words, the wedge-shaped sleeve 117A can be associated with the wedge-shaped jaws 103A and 103B, and the wedge-shaped sleeve 117B can be associated with the wedge-shaped jaws 103C and 103D.

[0031] Referring again to FIGS. 6 through 8, each wedge-shaped sleeve 117 provides a sleeve body 118. The sleeve body 118 can be semi-circular in shape and can be sized such that both (two) sleeve bodies 118 are received within the spindle assembly 34 in the manner described. Each sleeve body 118 provides an outer semi-circular surface (semi-cylindrical surface) 119 on one side and a jaw surface 120 that faces inwardly on the opposite side of the semi-circular surface 119. The jaw surface 120 is configured to receive a corresponding wedge-shaped jaw portion and, in particular, provides two wedge-shaped jaw pockets 122, each pocket slidably receiving a corresponding wedge-shaped jaw portion 103. The wedge-shaped jaw pocket 122 includes a plate ramp 123 that slidably receives and is supported by the backup plate 112. An edge ramp 124 extends from one or both sides of the plate ramp 123 but is not as deeply recessed as the plate ramp 123. Each edge ramp 124 extends from both sides of the plate ramp 123 and can form a rail 125 that is received within the gap between the ramp surface 110 and the extending shelf 113. The edge ramp 124 can slidably support and be supported by the side surface of the ramp surface 110 that is not covered by the backup plate 112. Those skilled in the art will understand that the angles of the ramps 123, 124 correspond to the angles of the ramp surface 110 and the received backup plate 112. In particular, the extending shelf 113 can be received within the gap between the rail 125 and the plate ramp 123 and can be supported by the plate ramp 123. Further, it will be understood that when the wedge-shaped sleeve 117 moves within the spindle assembly in a manner described in more detail later, the wedge-shaped jaw portions 103 and their respective connected upper ties 98 (connected to the upper surface of the jaw body portion 104) move slidably relative to the upper retainer 96.

[0032] As best shown in FIGS. 1, 2, 3A, 3B, 3C and 13, the spindle assembly 34 is coupled to the chuck assembly 32 at one end and to the frameless motor assembly 40 at the opposite end. The spindle assembly 34 is externally supported by the outer housing 24 and is rotatable therein, as will be described later. The main components of the spindle assembly 34 may include a main spindle 130. The main spindle 130 may be fixed at one end to the upper retainer 96 of the lower rim 86 and at the other end to the drive spindle assembly 200, which is a rotatable component of the motor assembly 40. Inside the main spindle 130, an inner sleeve 132 is maintained that may be coupled at one end to a wedge sleeve 117. A locking device spring 134 may be interposed between the inner sleeve 132 and a component of the motor assembly.

[0033] As best shown in FIGS. 3A through 3C, the main spindle 130, which can be in a substantially tubular form, includes a main spindle body 140 having an outer surface 142 opposite an inner surface 144. A body opening 146 extends through the main spindle body 140 and receives at least a portion of the chuck assembly 32, although the locking member 30 may or may not be received therein. The main spindle body 140 provides a spindle rim 148 at its upper end, which can be connected and fixed to the upper retainer 96 by suitable fasteners. The outer surface 142 provides a step edge 152 that extends inwardly substantially perpendicular to a step surface 154 having a smaller diameter than the outer surface 142. In the illustrated embodiment, a spacer tube 158 can be received on and in contact with the step surface 154. One of ordinary skill in the art will understand that the spacer tube 158 rotates with the main spindle body 140. An upper bearing 160 is disposed and captured between the step edge 152 and one end of the spacer tube 158. The outer race of the upper bearing is positioned and thereby captured against the inner surface of the outer housing 24, and the inner race of the upper bearing is positioned against the step edge 152 and the step surface 154. A bearing retainer 186 can be fixed to the outer housing 24 to hold the upper bearing in place and prevent contaminants from entering the outer housing and the spindle assembly. Similarly, the inner race of the lower bearing 162 is captured between the other end of the spacer tube 158 and the step surface 154, and the outer race of the lower bearing 162 is positioned adjacent to the inner surface of the outer housing 24. The main spindle body 140 provides a spindle end face 166 on the side opposite the spindle rim 148 that connects the outer surface 142 to the inner surface 144.

[0034] Referring again to FIGS. 1, 2, and 3A, the inner sleeve 132 is rotatable and axially slidable within the main spindle body 14. The inner sleeve 132 is part of the chuck assembly 32. The inner sleeve 132 includes a sleeve body 170 that provides an outer collar 172 extending radially outward at one end and a shaft seat 174 extending radially inward at the opposite end to provide a substantially closed shaft seat. The outer collar 172 is fixed to one end of the sleeve body 118 positioned on the opposite side of the lower rim 86. A radial rim 178 extends radially outward from the sleeve body 170 near the shaft seat 174. A sleeve opening 180 sized to receive a locking member, particularly the locking shaft 50, extends from the outer collar 172 into the sleeve body 170. A shaft hole 182 extends through the shaft seat 174, which may be threaded. A shaft seat dish hole 183 may extend into the shaft seat 174 and may be concentrically aligned with the shaft hole. One end of the locking device spring 134 may be received around the shaft seat 174, and one edge of the spring 134 may be supported by a radially extending surface of the radial rim 178.

[0035] The frameless motor assembly 40 can be coupled to the spindle assembly 34, as best shown in FIGS. 1, 2, 3A - 3C, and 13. Specifically, the assembly 40 can be connected to the main spindle 130 and the outer housing 24. The frameless motor assembly 40 is generally used to rotate the upper rim, the lower rim, and the attached tire by connection through the spindle assembly 34 and the chuck assembly 32. The assembly 40 provides a motor housing 190 that includes a radially extending housing rim 192 that can be attached and fixed to the flange of the outer housing 24. In some embodiments, the motor housing 190 can be provided with external radial cooling fins 193 to assist in dissipating the heat generated during the operation of the motor assembly. A stator 194 is maintained within the motor housing, and the stator 194 is fixed to the inner surface of the motor housing 190 by an epoxy or other suitable adhesive material. Either or both of the outer surface of the stator 194 and the inner surface of the motor housing can be grooved or otherwise modified to facilitate a secure adhesive connection between the two parts. Further, the epoxy can be filled within a number of laterally extending pipe plugs 195. In most embodiments, the pipe plug 195 can be a transverse hole filled with a thermally conductive epoxy that aids in heat transfer from the interior of the motor assembly to the surroundings.

[0036] As best shown in FIGS. 1, 3B, 3C, and 13, at least one discharge port 196 extends laterally through the housing near the housing rim 192. The discharge port 196 can be oriented and inclined downwardly with respect to the rim. In some embodiments, a plurality of discharge ports can be spaced around the housing rim in substantially equal increments. An annular frustoconical deflector shield 199 can be positioned within the motor housing below the spindle assembly, and the outer edge of the shield can be substantially aligned with at least one discharge port 196. Any lubricating oil or other fluid that can pass from the spindle assembly or chuck assembly is deposited on the shield and passes through the port to prevent their entry into the motor assembly. Operably associated with the stator 194 is a drive spindle assembly, generally designated by reference numeral 200.

[0037] Referring again to FIGS. 1, 2, 3A - 3C and 13, the drive spindle assembly 200 includes a rotor 204 that rotates when current is applied to the stator, as is well known in the art. Fixed to the inner surface and / or end face of the rotor 204 is the lower spindle 208. The lower spindle 208 includes a lower spindle body 210 having an outer surface 212 opposite the inner surface 214. As is apparent in the drawings, the rotor 204 is positioned adjacent to but not in contact with the inner surface of the stator 194. The body 210 can also provide a radial rotor flange 220. This extends radially from the outer surface 212 such that a fastener 222 can be used to connect the radial rotor flange 220 to the end of the rotor 204. A spindle flange 228 extends axially and radially from the lower spindle body 210. The spindle flange 228 receives a fastener 230 that connects the flange to the spindle end face 166 of the main spindle body 140. The lower spindle body 210 and the main spindle body 140 together form the main spindle 130. A support ring 231 can be fixed to the flange 228 by the fastener 230 and can support the inner race of the lower bearing 162. Thus, when the rotor 204 rotates, the drive spindle assembly 200 rotates with the main spindle 130, and the main spindle 130 rotates the lower rim 86 and the locking shaft 50. When received within the chuck assembly 32, it also rotates the upper rim simultaneously. The spindle flange 228 provides a flange surface 234 that supports a locking device spring 134 at one end, and the other end of the spring is supported by a radial rim 178 of the inner sleeve 132.

[0038] As best shown in FIGS. 1, 2, 3A-3C, 9 and 13, a spindle shaft, generally designated by reference numeral 250, is received through a shaft opening 216 in a lower spindle body 210. As will be appreciated as the description proceeds, the lower spindle body 210 rotates with the spindle shaft 250 and is supported by at least two bearings 252 positioned at opposite ends of an inner surface 214 of the lower spindle body. And, at an appropriate timing, the spindle shaft 250 may be axially movable within the lower spindle body. Thereby, one of ordinary skill in the art will understand that the spindle shaft 250 is used to support the rotation of the lower spindle body and the rotor 204. The spindle shaft 250 provides a sleeve end 254 having a shaft tip 256 that may be externally threaded. This extends into a shaft hole 182 in an inner sleeve 132 such that a portion of the shaft 250 can extend into a dish hole 183. Thereby, the spindle shaft is fixed to the inner sleeve 132 such that axial movement and rotational movement of the spindle shaft result in corresponding axial movement and rotational movement of the inner sleeve 132 and a wedge sleeve 117 attached thereto. Further, it will be understood that the spindle shaft 250 may be axially movable within a locking device spring 134, which is a coil spring in the illustrated embodiment. However, other biasing devices may be employed.

[0039] As best shown in FIGS. 1, 2, 3A-3C, and 9-13, an opposite end of the spindle shaft 250 includes a cap end 260. From the cap end 260, a cap tip 262 extends axially. The cap tip 262 provides a male threaded surface 264. The male threaded surface 264 may receive a shaft cap 268. A hex nut 272 may be used to secure the shaft cap 268 to the cap tip 262 of the spindle shaft.

[0040] As shown in FIGS. 1, 2, 3A - 3C, and FIGS. 9 - 13, the encoder assembly 42 is positioned between a frameless motor assembly and a spring - biased return cylinder 46. The encoder assembly 42 includes a mounting plate 280 that extends from and is connected to the motor housing 190. A plate opening 282 extends through the mounting plate 280 to allow the spindle shaft 250 to pass through it. The mounting plate 280 may provide at least one plate notch 283. The encoder assembly 42 may also include an encoder ring stand - off 291 that provides a tubular body 292 through which the spindle shaft 250 passes. The ring stand - off 291 may include a spindle end 294 that is connected to the drive spindle assembly 200, specifically the rotor 204 and / or the lower spindle body 210. Opposite the spindle end 294 is a mounting end 296. An encoder ring 290 is fixed to the mounting end 296 and, as a result, extends axially away from the mounting plate 280. Thus, the rotation of the spindle assembly, specifically the rotor 204, results in a corresponding rotation of the encoder ring stand - off 291 and the encoder ring 290. A cylindrical attachment portion 286 may be part of the encoder assembly 42. The cylindrical attachment portion 286 may provide a mounting body 288 that has an opening for receiving the shaft 250. A mounting flange 289 extends radially from one end of the body 288 and is used to fix the attachment portion 286 to the mounting plate 280.

[0041] The sensor attachment portion, best shown in FIGS. 9 and 10, is generally indicated by reference numeral 300 and is juxtaposed with the encoder ring 290. The sensor attachment portion 300 holds a reading head 302. The reading head 302 is aligned (positioned) with the plate notch 283 and detects the rotational position of the rotor and the spindle assembly by monitoring the rotational position of the encoder ring 290.

[0042] The locking bar 304, best shown in FIGS. 9 and 10, is utilized to movably hold the position of the read head 302 on the mounting plate 280 such that it is in a desired position relative to the encoding 290. This is accomplished by use of an adjustment mechanism 306 that may include an adjustment bar 308 that is slidably receivable within the plate notch 283. An adjustment knob 310 having a shaft that may extend within the adjustment bar 308 moves the adjustment bar to properly position the read head 302 relative to the encoding 290. The adjustment knob 310 extends through a plate 311 fixed to the radial edge of the mounting plate 280. The locking bar 304 will hold the adjustment bar 308 in a predetermined position once the position of the read head is set. One skilled in the art will understand that the sensor mounting portion is removable to allow for replacement, adjustment and / or servicing of the read head 302 without completely disassembling the other parts of the balancer 20.

[0043] An appropriate position signal is generated by the read head 302 upon detection of movement of the encoding and transmitted to a control system (not shown) that adjusts or correlates the rotational position of the tire during rotation of the main spindle. This information is utilized, along with other sensor information obtained during rotation of the tire by the spindle assembly, to determine the radial balance position of the tire under test. In other words, using data generated from the load cell and the encoder, the position of the angular displacement of the rotation of the heavy or light spot of the tire can be obtained.

[0044] The spring-biased return cylinder 46, best shown in FIGS. 9 and 11 through 13, can be held by or attached to the cylindrical mounting portion 286 and surrounds one end of the spindle shaft 250 without contacting the spindle shaft. The cylinder 46 includes a main cylinder 320 having a shaft opening 322 therethrough. An outer diameter radial shelf 324 extends from the main cylinder 320, providing a spring surface 326 on one side and a shelf surface 327 on the opposite side. The main cylinder 320 also includes a cap surface 329 that connects the inner and outer surfaces of the main cylinder and faces the shaft cap 268. Surrounding the main cylinder 320 annularly is an outer cylinder 330 having a cylinder wall 332. From the outer cylinder 330, an inner diameter radial shelf 336 extends radially inward, which in the default state is positioned adjacent to the shelf surface 327 and in some embodiments is in contact with the shelf surface 327. An inner spring shelf 333 also extends radially inward from the cylinder wall 332. A mounting bracket 340 extends axially from the outer cylinder 330, extending between the cylinder wall 332 and the inner diameter radial shelf 336 and is fixed to the mounting body 288 by a fastener or other means. Further, the inner diameter radial shelf 336 has a shelf seal surface 342. This seals around the outer surface 343 of the main cylinder 320. The main cylinder 320 and the outer cylinder 330 together form an annular spring cavity 344 between the outer surface of the main cylinder 320 and the inner surface of the outer cylinder 330 and between the spring surface 326 and the inner spring shelf 333. A plurality of fasteners 346 extend axially through the cylinder wall 332, connecting the mounting bracket 340 to the inner diameter radial shelf 336 and the lower edge of the mounting cylinder 288. Disposed within the annular spring cavity 344 is a coil spring 350 biased between the outer cylinder and the main cylinder, particularly between the spring surface 326 and the inward-facing spring shelf 333.

[0045] As best seen in FIG. 9, port 334 extends through the main cylinder wall through which compressed air can be supplied. As best seen in FIGS. 9, 11 and 12, the port delivers compressed air between an inner radial shelf 336 and a shelf surface 327 adjacent thereto. The inner radial shelf 336, the shelf surface 327, the outer surface of the main cylinder 320, and the inner surface of the outer cylinder 330 form an annular cavity 337 that receives the compressed air delivered through port 334. When air is delivered to cavity 337 through the port, the outer radial shelf 324 of the main cylinder moves from its default position, compressing cylinder spring 350. The cylinder spring 350 then drives the cap surface 329 axially away from the motor housing. The cap surface 329 engages the shaft cap 268 and moves it, axially moving the spindle shaft 250 away from the motor assembly so as to move the spindle shaft to the release position. Release of air from cavity 337 allows the spring to expand, whereby the driving force of the cap surface 329 is removed from the shaft cap 268. Thereby, the spindle shaft returns to its normal default position. One skilled in the art will understand that the return cylinder can disengage the chuck assembly 32 from the locking shaft 50 and remove the tire from the balancer by merely applying force to the spindle shaft 250 and the dynamic balancer. The return cylinder applies no force during rotation of the spindle assembly. As a result, no external force is applied to the balancer 20 by the return cylinder during the tire balancing operation.

[0046] Here, referring to FIG. 14, the control system is shown as a whole by reference numeral 400 and is utilized to operate the dynamic balancer 20. This is shown schematically. However, reference should also be made to all other drawings and the foregoing description. The control system 400 includes a controller 404, which provides the necessary hardware, software, and memory to control the various components of the balancer and facilitate its operation. The controller 404 receives input signals and transmits output signals to the various components of the balancer to control and adjust specific operations. A compressed air supply source 406 is coupled to the return cylinder 46, and the compressed air is utilized to operate the chuck assembly 32. The air supply source 406 is controlled by the controller 404 via a control signal indicated by a capital letter A.

[0047] The dry air brake mechanism 500 can be selectively coupled to the locking member 30 for the purpose of inserting the locking shaft into the chuck assembly at an appropriate timing to capture the tire and perform a balancing test, and for the purpose of withdrawing the locking member when the balancing test is completed. The mechanism 500 is controlled by the controller 404 via a control signal indicated by a capital letter B. A compressed air supply source 410 is coupled to the locking member via the mechanism 500 for the purpose of supplying compressed air to the tire when it is captured between the upper and lower rims. The compressed air supply source 410 is operably controlled by the controller via a control signal indicated by a capital letter C. After the balancing operation is completed, the tire is contracted and air is discharged through the mechanism 500 as described above.

[0048] A power source 412 is coupled to the motor assembly 40 for the purpose of supplying power to rotate the rotor and spindle components at an appropriate timing and speed. The controller 404 transmits and receives control signals indicated by a capital letter D to and from the power source.

[0049] The rotation of the rotor and spindle components is detected by the encoder assembly 42, specifically the read head 302. The controller 404 receives a position signal, indicated by the capital letter E, generated by the read head.

[0050] At least one load cell 420, four load cells in the illustrated embodiment, may be used and may be positioned around the outer periphery of the outer housing 24, may be positioned in an operable relationship with the frame 22, and may communicate with the controller 404 via a control signal F. The load cells detect the force generated by the rotating tire, and the force is utilized to determine whether the tire is out of balance and, if so, the extent and location of the out-of-balance condition of the tire. When the operation of the balancer is complete, the out-of-balance position of the tire may be determined, and the controller 404 operates the marking system 424 to mark the appropriate spot on the sidewall of the tire in accordance with the position signal generated by the read head 302, indicating the position and balance state of the tire. The marking system 424 is controlled via a signal indicated by the capital letter G.

[0051] During operation, referring to FIG. 14, the balancer is shown in the locked default state in FIGS. 1 and 11 and in the unlocked position in FIGS. 12 and 13. In the default state, the locking member 30 is received within the chuck assembly 32 and is locked in place so that an external force cannot separate the locking member from the chuck assembly. To operate the balancer, the controller 404 sends a signal to the air supply source 406, whereby compressed air is sent to the spring-biased return cylinder 46. This compressed air compresses the main cylinder against the cylinder spring 350, causing the cap surface 329 to engage the shaft cap 268, which then axially moves the spindle shaft 250 through the lower spindle 208. This axial movement causes the inner sleeve 132 attached to the spindle shaft to axially move and compress the locking device spring 134. Next, this axial movement causes the inner sleeve 132 to axially move the wedge-shaped sleeve 117 within the main spindle body 140. This axial movement of the wedge-shaped sleeve causes a radially outward movement of the wedge jaws 103 and the upper tee 99, as shown in FIG. 8. As a result, the jaw teeth 108 disengage from the shaft teeth 64. The jaw teeth 108 were previously received within the corresponding gap 66 (see FIG. 8). This disengagement enables the locking shaft to be axially removed from the chuck assembly by the mechanism 500 as described above. The air coupling 520 and the coupling adapter 504 are re-engaged to contract the tire. Next, the linear actuator 564 retracts, causing the flange inner surface 556 to engage and lift the tapered portion 52, lifting the locking shaft 50 out of the chuck assembly.

[0052] This axial removal separates the upper rim from the lower rim, and the tire that was received between them can be moved to the next manufacturing station, allowing the next tire to be received and tested by the balancer. When the next tire is preliminarily positioned between the two rims, the controller 404 determines the angular directions of the locking member and the chuck assembly via the encoder assembly. The encoder assembly knows the angular positions of the chuck assembly, the spindle assembly, and the motor assembly. Next, the controller 404 adjusts the position of the spindle assembly via the motor assembly so that a home position where the locking member can always be received is obtained. This ensures the consistency of the test results of the dynamic balancer. Next, the controller activates mechanism 500 to allow the actuator rod 568 to gradually lower the manifold 512 and the air coupling 520. As a result, in a controlled manner, the air coupling 520 mates with the coupling fitting 504, and the locking shaft 50 is lowered to an appropriate position within the chuck assembly. In other words, the locking shaft is lowered by a specified distance to capture a tire having a known bead width between the two rims. The locking shaft is simultaneously received within the chuck assembly in the unlocked position.

[0053] Next, the controller withdraws compressed air from the return spring cylinder. Thereby, to capture the new tire between the upper and lower rims, the chuck assembly fixes the locking shaft in place. Specifically, when air is withdrawn from the return spring cylinder, the spindle shaft returns to its default position, and then the chucking assembly is re-engaged with the locking member. In fact, the wedge-shaped sleeve 117 is allowed to return to its original position, whereby the upper tee moves into an engaged state with the shaft (see FIG. 7). When the chuck assembly re-engages with the spindle assembly, the controller instructs the air supply source to inflate the tire, further lowering the inner surface 556 so that it no longer contacts the tapered portion 52, and the tire maintains a compressed state, disengaging the air coupling portion 520 from the coupling mating portion 504. Next, the power supply 412 supplies power to the motor 40, and the motor 40 starts the rotational movement of the rotor and related main spindle components. Accordingly, the motor assembly rotates the rotor at a desired speed, and the rotational position is monitored by the encoder. At the same time, the load cell 420 detects the force generated by the specific tire received between the rims, and this information is correlated with the rotational position information provided by the encoder. When the test rotation by the spindle assembly is completed, the controller determines whether the balance of the tire is off, and instructs the marking system 424 to mark the appropriate position on the tire. Those skilled in the art will understand that the controller can send an accurate signal to the motor 40 to properly position the tire under the marking device of the marking system 424. When the marking operation is completed, the process is repeated to release the tire and move the tire to the next manufacturing operation.

[0054] The balancer disclosed in this specification provides many distinct advantages. First, the locking member is provided with a non-circular cross-section, in this embodiment a square cross-section, so that the locking member can be securely gripped in a specific orientation. This allows a large gripping force to be applied to the locking member by the chuck assembly, enabling rotation at a significant speed without applying excessive vibration and / or stress to other components of the balancer. In this embodiment, a home position can be utilized so that the locking member is always received in the chuck assembly in the same direction. Those skilled in the art will understand that this minimizes the determination of the characteristic forces of the locking assembly when rotated at a speed corresponding to any specific force peculiar to the balancer.

[0055] A further advantage of the present invention is that a frameless motor assembly is utilized to rotate the spindle assembly. This is important in that minimal external force is introduced by the motor assembly since the spindle assembly is not driven by a belt mechanism or other rotating mechanism that applies an external force during force detection by the load cell. A further advantage of the present invention is the use of a return air cylinder that enables secure engagement with the locking member by the chuck assembly. This is further facilitated by the non-circular cross-section of the locking member and the use of teeth that securely engage between the chuck assembly and the locking member. These teeth easily engage with each other. The motor assembly is also advantageous in that in its configuration, cooling fins and thermally conductive epoxy are used to dissipate the heat generated by the motor, allowing higher power to be applied to rotate the rotor assembly and the spindle assembly at a significantly higher speed than in other dynamic balancers.

[0056] Accordingly, it can be understood that the object of the present invention is satisfied by the structure presented above and its method of use. In accordance with the patent law, only the best mode and preferred embodiments have been presented and described in detail, but it is understood that the present invention is not limited thereto. To understand the true scope and breadth of the present invention, reference should be made to the following claims.

Claims

1. An outer housing, a spindle assembly rotatably attached to the outer housing, a frameless motor assembly connected to a selected component of the spindle assembly, and a chuck assembly for receiving a locking member to capture a tire therebetween, wherein the chuck assembly and the locking member are captured within the spindle assembly and rotated by the frameless motor assembly characterized in that it is a dynamic balancer.

2. further comprising a spindle shaft extending through the frameless motor assembly wherein one end of the spindle shaft axially moves the chuck assembly to engage and disengage the locking member within the spindle assembly characterized in that it is the dynamic balancer according to claim 1.

3. The frameless motor assembly has a stator coupled to the outer housing, and a rotor rotatably received within the stator, wherein the balancer further comprises an encoder assembly, the encoder assembly has an encoder ring connected to the rotor, and a read head held in a fixed position to detect the rotational positions of the encoder ring and the stator wherein characterized in that it is the dynamic balancer according to claim 2.

4. The encoder assembly further has an adjustment mechanism for selectively positioning the read head with respect to the encoder ring characterized in that it is the dynamic balancer according to claim 3.

5. The frameless motor assembly has a stator coupled to the outer housing, and a rotor rotatably received within the stator, wherein the spindle shaft extends through the rotor, the spindle shaft has an end cap extending radially, the balancer further comprises a spring-biased return cylinder associated with the rotor, the spring-biased return cylinder has a shaft opening for receiving the spindle shaft, and a main cylinder having a shelf surface, a spring surface, and a cap surface, and an outer cylinder coupled to the main cylinder and having an inner radial shelf facing the shelf surface and an inner spring shelf facing the spring surface a cylinder spring disposed between the inner spring shelf and the spring surface; having; compression of the cylinder spring results in engagement with an end cap extending in the radial direction of the cap surface, axially moving the spindle shaft, and disengaging the chuck assembly from the spindle shaft The dynamic balancer according to claim 2, characterized in that.

6. The frameless motor assembly includes; a stator coupled to the outer housing; a rotor rotatably received within the stator; having; The spindle assembly includes; a main spindle having a main spindle body with a body opening extending therethrough; at least one bearing disposed between the main spindle body and the outer housing; an inner sleeve received within the body opening and connected to the chuck assembly, having a sleeve opening for receiving the locking member and a shaft seat connected to the spindle shaft; a locking device spring interposed between the shaft seat and the rotor; having; One end of the main spindle body is connected to the lower rim of the chuck assembly; The other end of the main spindle body is connected to the rotor. The dynamic balancer according to claim 2, characterized in that.

7. further comprising an upper rim from which the locking member extends axially; having; The locking member has a locking shaft having a plurality of shaft teeth; The chuck assembly has a lower rim; The lower rim has an inner flange having a shaft opening therethrough and a wedge-shaped jaw portion having a plurality of jaw teeth; The shaft opening receives the locking shaft; The jaw teeth engage with the shaft teeth to hold the locking shaft in place for rotation with the spindle assembly. The dynamic balancer according to claim 1, characterized in that.

8. a drive brake air mechanism operably coupled to the locking member for selectively raising and lowering the locking member inside and outside the chuck assembly and selectively expanding and contracting the tire during capture; The dynamic balancer according to claim 2, further comprising.

9. The drive brake air mechanism is disengaged from the locking member and the spindle assembly during their rotation. The dynamic balancer according to claim 8, characterized in that.

10. A drive brake air mechanism configured to be used together with a dynamic balancer provided with a locking shaft having an air supply hole for inflating a tire received by the dynamic balancer, A coupling fitting portion adapted to be received within the air supply hole, A system housing for holding a manifold having an air coupling portion at one end, A linear actuator coupled to the manifold for selectively moving the air coupling portion in and out of engagement with the coupling fitting portion, Comprising, The air coupling portion is selectively connected to the coupling fitting portion, Both the air coupling portion and the coupling fitting portion are sealed when disengaged from each other and released when coupled to each other The drive brake air mechanism is characterized in that.

11. A flange coupled to the manifold for selectively engaging the locking shaft Further comprising, The linear actuator raises the manifold and the flange to withdraw the locking shaft from the balancer, The linear actuator lowers the manifold so that the flange is in a non-contact relationship during rotation of the locking shaft by the dynamic balancer The drive brake air mechanism according to claim 10, characterized in that.

12. A chuck assembly engageable with a locking shaft, A lower rim having a shaft opening for receiving the locking shaft and at least one tooth cavity, At least one wedge jaw radially movable within a corresponding one of the at least one tooth cavity, the wedge jaw having jaw teeth engageable with the locking shaft when received within the shaft opening on one side, At least one wedge sleeve slidably engageable with the opposite side of the at least one wedge jaw, Comprising, Axial movement of the at least one wedge sleeve moves the at least one wedge jaw in and out of engagement with the locking shaft The chuck assembly is characterized in that.

13. The at least one wedge sleeve forcibly engages the at least one wedge jaw with the locking shaft to rotate the locking shaft The chuck assembly according to claim 12, characterized in that.

14. A spring-biased return cylinder configured to be used with a dynamic balancer having a spindle shaft extending axially through a rotatable spindle assembly, a main cylinder having a shaft opening for receiving the spindle shaft and an outer radial shelf, an outer cylinder surrounding the main cylinder and having an inner spring shelf, and having, wherein the inner spring shelf faces the outer radial shelf and forms an annular spring cavity therebetween for receiving a cylindrical spring, the main cylinder being configured to be axially movable to axially move the spindle shaft, characterized in that it is a spring-biased return cylinder.

15. The outer cylinder has a port configured to receive compressed air to move the outer radial shelf from a default position toward the inner spring shelf to move the main cylinder to move the spindle shaft to a release position. The spring-biased return cylinder according to claim 14, characterized in that.

16. The release of the compressed air allows the cylindrical spring to move the main cylinder from the release position to the default position. The spring-biased return cylinder according to claim 15, characterized in that.

17. A motor assembly having a motor housing with a stator fixed and a rotor rotatably received inside the stator, a mounting plate fixed to the motor housing and having a plate notch, an encoder ring coupled to the rotor and rotating with the rotor, and an adjustment mechanism maintained in the plate notch and holding a reading head movable relative to the encoder ring. An encoder assembly characterized by comprising.

18. An adjustment bar received in the plate notch, a locking bar removably fixed to the mounting plate, and comprising, one end of the adjustment bar holding the reading head, the opposite end of the adjustment bar being coupled to an adjustment knob, rotation of the adjustment knob adjusting the position of the reading head relative to the encoder ring, and fixing of the locking bar to the mounting plate holding the adjustment bar in a fixed position. The encoder assembly according to claim 17, characterized in that.

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