Dry brake air mechanism, clamp assembly, return cylinder and encoder assembly

Abstract

The present invention relates to the field of dynamic balancers and discloses a dry brake air mechanism, clamp assembly, return cylinder and encoder assembly, the dry brake air mechanism is applicable to a dynamic balancer, the dynamic balancer has a locking shaft, the locking shaft has an air supply hole passing therethrough to inflate a tire received by the dynamic balancer, the mechanism comprises: a connection fitting adapted to be received in the air supply hole; a system housing carrying a manifold having an air connector at one end, the air connector being selectively connected to the connection fitting; and a linear actuator connected to the manifold to selectively move the air connector into engagement with and out of engagement with the connection fitting, wherein the air connector and the connection fitting are sealed when out of engagement with each other and open when in engagement with each other.

Description

[0001] This application is a divisional application of Chinese patent application No. 201910872788.8, filed on September 16, 2019, entitled "Dynamic Balancer with Frameless Motor Drive".

[0002] Cross-references to related applications

[0003] This application claims priority to U.S. Provisional Application No. 62 / 731,238, filed September 14, 2018, which is incorporated herein by reference. Technical Field

[0004] This invention relates to a dynamic balancer. More specifically, the invention relates to a dynamic balancer that uses a frameless motor to determine the balance state of a tire rotated by the balancer. Background Technology

[0005] Tires manufactured typically undergo certain tests before being sold to the public. One such test involves measuring the tire's balance by spinning it at high speed. The machine used to measure tire balance must hold the tire in place, inflate it, and then spin it at high speed while detecting the forces acting on it during rotation.

[0006] Existing devices typically utilize force sensors to detect forces axially related to the rotation of the tire. While effective for their stated purposes, more accurate determination of the balance state is believed to be possible. For example, a common problem with existing dynamic balancers arises from the mechanism used to rotate the tire to determine the balance state. Most balancers employ a side-mounted motor that rotates a belt connected to the main shaft assembly, which in turn rotates the tire. While effective, the side-mounted drive motor introduces radial forces into the main shaft assembly, which must then be compensated for to avoid adversely affecting the sensors determining the tire's balance. This compensation can be achieved by applying an anti-balancing force, using sensors to determine additional forces, and computer processing to adjust the measured forces, or a combination of both. Some dynamic balancers avoid using a side-mounted motor by employing a drive motor housing and armature. However, this configuration still utilizes opposing suspension springs, which become unbalanced after minimal use and introduce forces that must be compensated for into the main shaft assembly, both of which contribute to distortion in the force sensor measurements.

[0007] Another drawback of existing dynamic balancers is the way the tire is secured to the machine before rotation. One existing chuck locking mechanism uses ball bearings between the outer and inner sleeves to hold the tire in place. Unfortunately, the bearings are prone to misalignment, and the sleeves do not engage with each other as they should.

[0008] Therefore, there is a need in the art for an improved tire balancer capable of detecting forces in a horizontal plane relative to tire rotation. Furthermore, the detected forces need to be collected and processed in a meaningful manner to accurately identify the location and number of tire imbalances. Summary of the Invention

[0009] In view of the above, a first aspect of the present invention is to provide a dynamic balancer with frameless motor drive.

[0010] Another aspect of the invention provides a dynamic balancer, including a housing; a spindle assembly rotatably mounted on the housing; a frameless motor assembly connected to a selected portion of the spindle assembly; and a clamping assembly receiving a locking member to capture a tire between the clamping assembly and the locking member, the clamping assembly and the locking member being captured in the spindle assembly and rotated by the frameless motor assembly.

[0011] Another aspect of the invention provides a dry brake air mechanism adapted for a dynamic balancer having a locking shaft having an air supply port therethrough for inflating a tire received by the dynamic balancer, the mechanism comprising: a connecting fitting adapted to be received in the air supply port; a system housing carrying a manifold having an air connector at one end, the air connector selectively connected to the connecting fitting; and a linear actuator connected to the manifold to selectively move the air connector into the connecting fitting for engagement and disengagement from the connecting fitting, wherein the air connector and the connecting fitting are sealed when disengaged and open when engaged.

[0012] Another aspect of the invention provides a clamping assembly for engaging a locking shaft, the clamping assembly comprising: a lower edge having a shaft opening therethrough for receiving the locking shaft, the lower edge having at least one T-shaped cavity; at least one wedge-shaped claw, the at least one wedge-shaped claw being radially movable in a corresponding one of the at least one T-shaped cavities, the at least one wedge-shaped claw having a side surface with claw teeth that engage with the locking shaft when the locking shaft is received in the shaft opening; and at least one wedge-shaped sleeve, the at least one wedge-shaped sleeve being slidably engaged with the opposite side of the at least one wedge-shaped claw, wherein axial movement of the at least one wedge-shaped sleeve causes the at least one wedge-shaped claw to move into engagement with the locking shaft and disengage from engagement with the locking shaft.

[0013] Another aspect of the invention is to provide a spring-biased return cylinder suitable for a dynamic balancer having a spindle extending axially through a rotatable spindle assembly. The spring-biased return cylinder includes: a main cylinder having a shaft opening therethrough, the shaft opening receiving the spindle, the main cylinder having an outer radial flange; and an outer cylinder surrounding the main cylinder, the outer cylinder having an inward spring flange, wherein the inward spring flange faces the outer radial flange and forms an annular spring cavity between the inward spring flange and the outer radial flange, the annular spring cavity accommodating a cylindrical spring, and wherein the main cylinder is adapted to move axially to move the spindle axially.

[0014] Another aspect of the present invention provides an encoder assembly comprising: a motor assembly having a motor housing having a stator fixed thereon and a rotor rotatably accommodated within the stator; a mounting plate fixed to the motor housing having a plate recess; an encoder ring connected to the rotor for rotating together with the rotor; and an adjustment mechanism held in the plate recess and capable of moving a read head relative to the encoder ring. Attached Figure Description

[0015] These and other features and advantages of the invention will be better understood in conjunction with the following description, the appended claims and the accompanying drawings, wherein:

[0016] Figure 1 This is a cross-sectional view of a dynamic balancer in the locked position according to the concept of the present invention;

[0017] Figure 1A This is a partial cross-sectional view of a dry braking air system related to a dynamic balancer according to the concept of the present invention.

[0018] Figure 2 This is an exploded perspective view of a dynamic balancer according to the concept of the present invention;

[0019] Figure 3A 3B and 3C are dissected views of a dynamic balancer according to the concept of the present invention;

[0020] Figure 4 This is a lower perspective view of the locking member received through the lower edge, which is part of the clamping assembly of the dynamic balancer conceived according to the present invention;

[0021] Figure 5A This is a perspective view of selected components of the locking member and clamping assembly according to the concept of the present invention;

[0022] Figure 5B This is another perspective view of selected components of the locking member and clamping assembly according to the concept of the present invention;

[0023] Figure 6 It is a perspective view of a wedge sleeve, showing a wedge claw housed within the wedge sleeve, wherein the wedge sleeve and the wedge claw are part of a clamping assembly used according to a concept of the present invention;

[0024] Figure 7 This is a cross-sectional view of a locking member housed in a clamping assembly in its default position, according to the concept of the present invention.

[0025] Figure 8 This is a cross-sectional view of a locking member housed in a clamping assembly in the unlocked position, according to a concept based on the present invention.

[0026] Figure 9 This is a perspective view of the encoder assembly and the spring-biased return cylinder used in a dynamic balancer according to the concept of the present invention.

[0027] Figure 10 This is an end view of the encoder assembly and the spring-biased return cylinder according to the concept of the present invention;

[0028] Figure 11 This is an enlarged cross-sectional view of a spring-biased return cylinder in its default position according to the concept of the present invention;

[0029] Figure 12 This is an enlarged cross-sectional view of a spring-biased return cylinder in the unlocked position according to the concept of the present invention;

[0030] Figure 13 This is a cross-sectional view of a dynamic balancer in the unlocked position according to the concept of the present invention; and

[0031] Figure 14 This is a schematic diagram of a control system for operating a dynamic balancer according to the concept of the present invention. Detailed Implementation

[0032] Now refer to the attached diagram, especially Figure 1 , 2 As can be seen from 3A, 3B, and 3C, dynamic balancers are typically designated by the number 20. These specific figures should be consulted when reading any part of the specification. Specific reference may be made to the relevant figures where appropriate, but it should be understood that any figure may illustrate the described item. As is well known in the art, dynamic balancers test annular bodies, such as pneumatic tires. Typically, the balancer 20 includes a floor support frame 22 (partially shown) with appropriate structural features, such as legs and lateral members supporting the balancer. Those skilled in the art will understand that the frame may be bolted or otherwise secured to the floor to minimize external forces acting upon it.

[0033] The housing 24 can be carried and supported by the frame 22 for the main components of the dynamic balancer. At least one force sensor 26 can be inserted between the frame 22 and the housing 24. In this embodiment, four force sensors 26 may be suitably spaced around the housing in substantially equal 90° increments or otherwise and used to detect and collect force measurement data during tire rotation by the balancer, as will be described in detail below. The configuration and placement of the force sensors relative to the frame can be as described and illustrated in U.S. Patent Application Serial No. 15 / 345,648, filed November 8, 2016, which is incorporated herein by reference. In this embodiment, the operating interface of the force sensors between the balancer 20 and the frame 22 is the only intentional interface between them, so as to substantially eliminate any external forces applied to the balancer during operation. As a result, the tire's balanced state can be obtained, and minimal external interference forces are incorporated into the balance measurement of the load cells.

[0034] The main components of the balancer 20 may include a locking member 30, which is associated with and disposed on one side of the tire (T), particularly the bead. Figure 2 The locking member 30 is shown being received in a clamping assembly, typically designated 32. The clamping assembly clamps the locking member and positions and captures the opposing bead of the tire. The clamping assembly 32 can be housed in a spindle assembly 34, which rotates the clamping assembly and the tire mounted between the locking member and the clamping assembly. The spindle assembly 34 can be rotated via a frameless motor assembly 40, wherein the rotational position of the rotating tire is detected and monitored by an encoder assembly 42 connected to the frameless motor assembly 40. A spring-biased return cylinder 46 is associated with the frameless motor assembly and, as will be discussed in detail, facilitates the release and capture of the locking member 30 together with the clamping assembly 32.

[0035] like Figure 3A As best shown, the locking member 30 includes a locking shaft 50, which has an outwardly tapered portion 52 at one end. Those skilled in the art will understand that a dry brake air system (described herein) can be connected to the tapered portion 52 and / or an adjacent portion of the shaft 50 to move the locking member into and out of the clamping assembly 32 and to inflate / deflate the tire. The locking shaft moves vertically into and out of the clamping assembly 32 in a manner described in the following description. An air supply port 54 extends axially into the shaft at the outwardly tapered portion 52. A lateral port 56 extends through the locking shaft 50, intersecting and abutting the air supply port 54. A distal end 60 is located at the end opposite the outwardly tapered portion 52.

[0036] In some embodiments, the locking shaft 50 may have a non-circular cross-section, such as... Figure 4 5A and 5B are best shown. This feature facilitates engagement and locking of the shaft with the clamping assembly of the receiving shaft, which is then rotated by the spindle assembly during balancing operations. In such an embodiment, the clamping assembly must be carefully angularly aligned to receive the locking shaft, and this can be easily accomplished through coordination between the encoder assembly 42 and the motor assembly 40, as will be discussed. In any case, the locking shaft in this embodiment provides a substantially square cross-section, wherein the shaft 50 provides a plurality of locking sides 63, and wherein each locking side is provided with a corresponding letter suffix AD. Each locking side 63A-D provides a plurality of shaft teeth 64A-D, wherein a gap 66A-D is provided between each tooth. As a result, the locking sides 63A-D are provided with shaft teeth 64, which extend from approximately the midpoint of the shaft 50 to the distal end 60 of the shaft opposite the outwardly tapered portion 52. And the shaft teeth 64 are disposed on a linear surface, effectively forming the square cross-section of the locking shaft. Thus, in this embodiment, the locking shaft provides four sides for engagement with the clamping assembly 32, as described below.

[0037] like Figure 3A As best shown in 5A and 5B, the collar 72 extends radially from the shaft 50 at a location between the transverse bore 56 and the outwardly tapered portion 52. The collar 72 can be fastened to the shaft flange 74, which can be fastened to an upper edge 78 that rotates when the shaft is locked. The outer circular surface of the upper edge 78 can provide multiple radially inward steps 80 to accommodate various tire bead diameters.

[0038] like Figure 3A , Figure 7 and Figure 8 As clearly shown, the clamping assembly 32 receives and holds the tire by engaging with the locking member 30. When the locking member 30 and the clamping assembly 32 secure the tire between them, they are collectively held within the spindle assembly 34. As will be discussed in due course, air is supplied through the air supply port and the lateral port 56 to inflate the tire, and the spindle assembly 34 then rotates the captured tire to determine its balance and other characteristics.

[0039] Now refer to Figure 1AAs can be seen, the dry brake air system is typically indicated by the number 500 and is operatively connected to the dynamic balancer 20. The balancer 20 provides connection to the air system 500 via a connecting fitting 504. The connecting fitting 504 is received in the air supply port 54 of the locking shaft 50. As will become apparent as the detailed description proceeds, the connecting fitting 504 is selectively connected to the brake air system 500 to introduce pressurized air into the air supply port 54 and the lateral port 56 and to draw air out of the air supply port 54 and the lateral port 56 to inflate and deflate the tires at appropriate times.

[0040] The air system 500 includes a system housing 508, which provides the necessary structure for holding the components of the system 500. One of these components is a manifold 512, which provides a conduit 516 for receiving pressurized air, as will be discussed. At one end of the conduit 516 is an air connector 520, which selectively connects to a connection fitting 504. Exemplary connection fittings 504 and air connectors 520 are available from Staubli of Switzerland, whose SPC series connectors provide exemplary connection systems that can be used.

[0041] See also Figure 1A One end of manifold 512 provides a sealing skirt 524, which partially surrounds air connector 520. Sealing skirt 524 includes a sleeve 528 and a bushing 532. The sleeve 528 and bushing 532 allow space connector 520 to slide within manifold 512 at appropriate times. A shield 540 extends from the lower end of housing 508 and substantially surrounds sealing skirt 524 to prevent debris from entering connection fitting 504 or air connector 520. An interface collar 544 is attached to and extends from the lower edge of shield 540, and includes a connecting flange 548 secured to the lower end of shield 540 by suitable fasteners. A tapered flange 552 extends inwardly from the connecting flange 548, and the tapered flange 552 provides an inner flange surface 556, the dimensions of which are adapted to mate around the tapered portion 52 of the locking shaft. Those skilled in the art will understand that when the locking shaft is lifted away from the clamping assembly, the inner flange surface 556 contacts only the tapered portion 52, as will be described in detail later. However, when the locking shaft is received in the clamping assembly, the inner flange surface and the tapered portion 52 are in a non-contact spaced relationship, such that no direct force is applied to the tapered portion. As a result, during balancing operations, no external force from the tapered flange 552 is applied to the spindle assembly 34. In other words, a non-contact relationship is established between the tapered flange 552 and the tapered portion 52, such that no force is transmitted between the interfaces of these two portions during rotation of the locking shaft.

[0042] System 500 may include a linear actuator 564, which may be connected to one end of manifold 512 at the end opposite to sealing skirt 524. An actuator rod 568 extends from the linear actuator 564, wherein movement of the actuator rod is controlled by a controller, as will be discussed. In any case, actuator rod 568 causes the manifold to move in an up / down or vertical direction. Downward movement of rod 568 results in engagement of air connector 520 with connection fitting 504. Upward movement of actuator rod 568 results in disengagement of air connector 520 from connection fitting 504. Those skilled in the art will understand that connection fitting 504 and air connector 520 are configured such that both are sealed when they are disengaged from each other, and that air can flow between them in only one direction when both are securely seated or connected to each other.

[0043] During operation, at the appropriate time, actuator 564 is actuated, causing actuator rod 568 to lower air connector 520 to engage with connecting fitting 504. Slightly simultaneously, locking shaft 50 is lowered by the tapered flange and locked, as described in detail later. Once air connector 520 is engaged with connecting fitting 504, collar 544 descends by an increment, so that the inner surface 556 of the flange is no longer in contact with the tapered portion 52. Next, air and / or some other type of gas (which may be pressurized) can be supplied through manifold conduit 516 and into supply port 54 and lateral port 56 to position the tire bead into the corresponding edge and pressurize the tire to be tested. Once the tire is fully inflated, air connector 520 disengages from connecting fitting 504, and the tire remains pressurized by the closure of the connecting fitting. Disengagement of air connector 520 from connecting fitting 504 does not cause the flange surface 556 to contact the tapered portion 52.

[0044] During the rotation of the locking shaft, the tapered portion 52 is no longer in contact with the inner flange surface 556, although it is adjacent to it. Thus, the air system 500 does not apply mechanical or other forces to any rotating portion of the dynamic balancer 10. After the balancing test is completed, the air connector re-engages with the connection fitting 504 to release air from the tire into the surrounding environment. Next, at the appropriate time, the actuator rod 568 is raised, causing the inner flange surface 556 to engage the tapered surface 52 and lifting the locking shaft out of the clamping assembly.

[0045] Now for reference Figure 3A and Figure 4-8As can be seen, the clamping assembly 32 includes a lower edge 86, which in most embodiments is essentially a mirror image of the upper edge 78. The lower edge 86 provides a plurality of diametrically inward steps 88 that mate with the steps 86 of the upper edge to accommodate various bead diameters of various tires that can be tested by a dynamic balancer. An inner flange 90 can be fastened to and extends radially inward from the edge 86, and provides a shaft opening 92 through which a locking shaft 50 extends to receive the locking shaft 50. An upper retainer 96 is secured to or formed as part of the lower side of the inner flange 90. The lower side of the upper retainer 96 provides a plurality of T-shaped cavities 97A-D, wherein the number of cavities 97 corresponds to the number of shaft sides 63. Each cavity 97 provides a pair of opposing undercut T-shaped ridges 98. The corresponding upper T-shaped member 99 is slidably received in the T-shaped cavity 97, and in increments of 90 degrees or other suitable angular increments depending on the number of axial sides 63, wherein each T-shaped member 99 has a suffix AD corresponding to the number of sides of the locking shaft 50, which provides shaft teeth 64A-D. Each T-shaped member 99 has an outwardly extending side rail 100 defining a corresponding side groove 101. And each T-shaped member has an opening 102 extending through it. And the T-shaped ridge 98 of each corresponding cavity 97 is slidably received in the side groove 101. Thus, each upper T-shaped member 99 can move linearly along the lower side of the upper retainer. In fact, each upper T-shaped member can move radially relative to the locking shaft.

[0046] like Figure 3A and Figure 4-8 As best shown, each upper T-shaped member 99 is connected to a corresponding wedge-shaped claw 103A-D, which has a claw body 104A-D connected to the upper T-shaped member 99 by a fastener 107 received in an opening 102. Each claw body 104 has a T-shaped surface 105 at its apex, wherein a pair of opposing T-shaped ridges 106 extend from the sides of the T-shaped surface 105. Thus, the ridges 106 prevent lateral movement of the upper T-shaped member 99 relative to the claw body 104. The claw body 104 also provides a plurality of claw teeth 108A-D, which engage in corresponding gaps 66A-D provided by shaft teeth 64A-D. In other words, the claw teeth 108A-D provide a gap 109 between them, which receives the corresponding shaft teeth 64. With the wedge-shaped claws 103A-D engaged at the shaft sides 63A-D, the locking member 30 is secured to the clamping assembly 32. On the surfaces opposite to or at an angle to the claw teeth 108A-D are claw-inclined surfaces 110A-D. Each inclined surface 110 may provide a recessed portion 111, the dimensions of which are adapted to accommodate the abutment plate 112. Figure 5BAs shown in the optimal configuration, an outwardly extending protrusion 113 extends from the longitudinal side of the plate 112, forming a gap between the protrusion 113 and the inclined surface 110. A fastener 114 can extend through the plate 112 to connect to the claw body 104.

[0047] It is best to see Figure 6-8 As shown, the wedge sleeve 117 can be provided in a predetermined number of segments and can be connected to slidably receive adjacent wedge claws 103 to provide structural support for the locking shaft when it is received in the clamping assembly and also allow it to slidably move within the spindle assembly, as will be described. As shown, two similarly shaped wedge sleeves can be provided and accommodated within the spindle assembly 34, as... Figure 3A As shown, each wedge sleeve 117 can be associated with a pair of wedge claws 103. In other words, wedge sleeve 117A can be associated with wedge claws 103A and 103B, and wedge sleeve 117B can be associated with wedge claws 103C and 103D.

[0048] Refer again Figure 6-8 Each wedge-shaped sleeve 117 provides a sleeve body 118, which may be semi-circular in shape and sized such that two sleeve bodies 118 are received in the spindle assembly 34 in a manner to be discussed. Each sleeve body 118 provides an outer semi-circular surface 119 on one side and an inner surface facing a claw surface 120 opposite to the semi-circular surface 119. The claw surface 120 is configured to receive a corresponding wedge claw, specifically providing two wedge claw recesses 122, each recess 122 slidably receiving a corresponding wedge claw 103. The wedge claw recess 122 includes a plate bevel 123 that slidably receives and abuts against a plate 112. An edge bevel 124 extends from one or both sides of the plate bevel 123, and the edge bevel 124 is not as deeply recessed as the plate bevel 123. Each edge bevel 124 extends from both sides of the plate bevel 123 and can form a track 125, which is received in the gap between the inclined surface 110 and the extended protrusion 113, wherein the edge bevel 124 can slidably support and abut against the side of the inclined surface 110 not covered by the abutment plate 112. Those skilled in the art will understand that the angles of the bevels 123 and 124 correspond to the angles of the inclined surface 110 and the receiving abutment plate 112. Specifically, the extended protrusion 113 can be received in the gap between the track 125 and the plate bevel 123, and can also abut against the plate bevel 123. It should also be understood that as the wedge sleeve 117 moves within the spindle assembly in a manner to be discussed in detail, the wedge claws 103 and their respective connected upper T-shaped members 98 (the upper T-shaped members 98 are connected to the top of the claw body 104) will also be slidably moved relative to the upper retainer 96.

[0049] like Figure 1As best shown in 2, 3A, 3B, 3C, and 13, the spindle assembly 34 is connected at one end to the clamping assembly 32 and at the opposite end to the frameless motor assembly 40. The spindle assembly 34 is externally supported by the housing 24 and is rotatable within the housing, as will be discussed. Major components of the spindle assembly 34 may include a spindle 130, one end of which is fixed to an upper retainer 96 at a lower edge 86, and the other end of which is fixed to a drive spindle assembly 200, a rotatable component of the motor assembly 40. An inner sleeve 132 is held within the spindle 130, one end of which is connectable to a wedge sleeve 117. A locking spring 134 may be inserted between the inner sleeve 132 and a component of the motor assembly, as will be discussed.

[0050] like Figure 3A As best illustrated in the example, spindle 130 may be a substantially tubular construction, comprising a spindle body 140 having an outer surface 142 opposite an inner surface 144. Extending through spindle body 140 is a body opening 146 receiving at least a portion of a clamping assembly 32, which may or may not accommodate a locking member 30. Spindle body 140 is provided with a spindle edge 148 at its apex, which may be connected and secured to an upper retainer 96 by suitable fasteners. The outer surface 142 is provided with a stepped edge 152 extending substantially vertically inward to a stepped surface 154, the diameter of which is smaller than that of the outer surface 142. In the illustrated embodiment, a spacer tube 158 may be accommodated on and in contact with the stepped surface 154. Those skilled in the art will understand that the spacer tube 158 rotates together with spindle body 140. An upper bearing 160 is disposed and captured between the stepped edge 152 and the end of the spacer tube 158, wherein the outer race of the upper bearing is positioned and captured by the inner surface of the housing 24, and the inner race of the upper bearing is positioned against the stepped edge 152 and the stepped surface 154. A bearing retainer 186 is fastened to the housing 24 to hold the upper bearing in place and prevent contaminants from entering the housing and spindle assembly. In a similar manner, the inner race of the lower bearing 162 is captured between the other end of the spacer tube 158 and the stepped surface 154, and the outer race of the bearing 162 is positioned near the inner surface of the housing 24. The spindle body 140 is provided with a spindle end face 166, which faces the spindle edge 148 and connects the outer surface 142 to the inner surface 144.

[0051] Refer again Figure 12 and 3A, rotatable and axially slidable within the spindle body 140 is an inner sleeve 132, which is part of the clamping assembly 32. The inner sleeve includes a sleeve body 170, which has a radially outwardly extending outer ring 172 at one end and a radially inwardly extending and substantially closed bearing seat 174 at the opposite end. The outer ring 172 is secured and fastened to one end of the sleeve body 118 positioned opposite the lower edge 86. A radial edge 178 extends radially outwardly from the sleeve body 170 near the bearing seat 174. Extending from the outer ring 172 into the sleeve body 170 is a sleeve opening 180, which is sized to receive a locking member, specifically a locking shaft 50. Extending into the bearing seat 174 is a shaft bore 182, which may be internally threaded, and a countersunk bore 183 may also extend into the bearing seat 174 and be concentrically aligned with the shaft bore. One end of the locking device spring 134 can be received around the bearing 174, wherein one edge of the spring 184 can be supported by the radially extending surface of the radial edge 178.

[0052] The frameless motor assembly 40 can be connected to the spindle assembly 34, such as Figure 1 The best representation is shown in 2, 3A-C, and 13. Specifically, assembly 40 can be connected to spindle 130 and housing 24. Frameless motor assembly 40 is typically used for rotating the upper and lower edges and connecting the tire, which is connected via spindle assembly 34 and clamping assembly 32. Assembly 40 is provided with a motor housing 190, which includes radially extending housing edges 192 that can be connected and secured to a flange of housing 24. In some embodiments, motor housing 190 may be provided with external radial cooling fins 193, which help dissipate heat generated during operation of the motor assembly. Stator 194 is held within the motor housing and is secured to the inner surface of motor housing 190 by epoxy resin or other suitable adhesive material, wherein either or both of the outer surface of stator 194 and the inner surface of motor housing may be grooved or otherwise modified to facilitate a strong adhesive connection between the two components. Additionally, epoxy resin may be filled into a plurality of laterally extending plugs 195. In most embodiments, the plug 195 may be a transverse hole filled with thermally conductive epoxy resin, which helps to transfer heat from the inside of the motor assembly to the external environment.

[0053] like Figure 1As best shown in 3B, 3C, and 13, near the housing edge 192 and extending laterally through the housing is at least one discharge port 196, which may be oriented and angled downward relative to the edge. In some embodiments, a plurality of discharge ports may be spaced apart around the housing edge in substantially equal increments. Positioned within the motor housing and below the spindle assembly is an annular and truncated conical deflector shroud 199, wherein the outer edge of the shroud is substantially aligned with at least one discharge port 196. Any lubricating oil or other fluid from the spindle assembly or clamping assembly may deposit on the shroud and through the ports to prevent them from entering the motor assembly. Operable in conjunction with the stator 194 is a drive spindle assembly, generally indicated by reference numeral 200.

[0054] Referring again to 1, 2, 3A-C and 13, the drive shaft assembly 200 includes a rotor 204 that rotates as is known in the art when current is applied to the stator. A lower spindle 208 is fixed to the inner and / or edge surfaces of the rotor 204. The lower spindle 208 includes a lower spindle body 210 having an outer surface 212 opposite to an inner surface 214. Extending through the lower spindle body 210 is a shaft opening 216 defined by the inner surface 214. As clearly shown in the figures, the rotor 204 is adjacent to but does not contact the inner surface of the stator 194. The body 210 may also be provided with a radial rotor flange 220. The radial rotor flange 220 extends radially from the outer surface 212, wherein fasteners 222 are available for attaching the radial rotor flange 220 to one end of the rotor 204. Extending axially and radially from the lower spindle body 210 is a spindle flange 228. The spindle flange 228 receives a fastener 230 that connects the flange to the spindle end face 166 of the spindle body 140, wherein the lower spindle body 210 and the spindle body 140 together form the spindle 130. A support ring 231 can also be secured to the flange 228 by the fastener 230 to support the inner ring of the lower bearing 162. Thus, when the rotor 204 rotates, the drive shaft assembly 200 rotates together with the spindle 130, which in turn rotates the lower edge 86 and the locking shaft 50, which, when received in the clamping assembly 32, simultaneously rotates the upper edge. The spindle flange 228 provides a flange surface 234 that supports a locking device spring 134 at one end, the other end of which is supported by the radial edge 178 of the inner sleeve 132.

[0055] The spindle shaft, typically represented by the number 250, is received through the shaft opening 216 of the lower spindle body 210, such as... Figure 1As shown in 2, 3A-C, 9, and 13, as will be understood from the description to come, the lower spindle body 210 rotates together with the spindle 250 and is supported by at least two bearings 252 positioned at corresponding ends of the inner surface 214 of the lower spindle body. The spindle 250 is axially movable within the lower spindle body when appropriate. Therefore, those skilled in the art will understand that the spindle 250 is used to support the rotation of the lower spindle body and the rotor 204. The spindle 250 is provided with a sleeve end 254 having a shaft end 256, which may be externally threaded and extend into the shaft bore 182 of the inner sleeve 132, and a portion of its central shaft 250 may extend into a countersunk bore 183. Thus, the spindle is fixedly connected to the inner sleeve 132 such that axial and rotational movement of the spindle results in corresponding axial and rotational movement of the inner sleeve 132 and the connected wedge sleeve 117. It should also be understood that the spindle 250 can move axially within the locking device spring 134, which in the illustrated embodiment is a helical spring, although other biasing devices may be used.

[0056] like Figure 1 As best shown in 2, 3A-C and 9-13, the opposite ends of the spindle 250 include a cap end 260, a cap tip 262 extending axially from the cap end 262, and the cap tip 262 providing an external threaded surface 264. The threaded surface 264 receives a spindle cap 268. A hex nut 272 can be used to secure the spindle cap to the cap tip 262 of the spindle.

[0057] Encoder assembly 42 is located between frameless motor assembly and spring-biased return cylinder 46, as... Figure 1As shown in Figures 2, 3A-C, and 9-13, encoder assembly 42 includes a mounting plate 280 extending from and connected to motor housing 190, with a plate opening 282 extending through the mounting plate 280 to allow a spindle 250 to pass through. Mounting plate 280 may provide at least one plate notch 283. Assembly 42 may also include an encoder ring support 291, which provides a tubular body 292 through which a central shaft 250 extends. Ring support 291 may include a spindle end 294 connected to drive spindle assembly 200 and specifically connected to rotor 204 and / or lower spindle body 210. Opposite spindle end 294 is mounting end 296. Encoder ring 290 is secured to mounting end 296 and thus extends axially away from mounting plate 280. Therefore, rotation of the spindle assembly, and particularly rotor 204, causes corresponding rotation of encoder ring support 291 and encoder ring 290. A cylindrical mount 286 may also be part of encoder assembly 42. The cylindrical mount 286 may provide a mounting body 288 having an opening therethrough to receive the spindle 250. A mounting flange 289 extends radially from one end of the body 288, wherein fasteners are used to secure the mount 286 to the mounting plate 280.

[0058] Figure 9 and Figure 10 In the best-in-class display, the sensor bracket is typically digitized as 300. The sensor bracket 300 is arranged side by side with the encoder ring 290, wherein the sensor bracket holds the read head 302, which is aligned with the plate notch 283 and detects the rotational position of the rotor and spindle assembly by monitoring the rotational position of the encoder ring 290.

[0059] Figure 9 and 10 As best shown, locking lever 304 is used to movably hold the position of read head 302 on mounting plate 280 in the desired position relative to encoder ring 290. This is achieved by using adjustment mechanism 306, which may include adjustment lever 308 slidably received in plate recess 283. Adjustment knob 310 has a shaft extending into adjustment lever 308, and adjusts the adjustment lever to properly position read head 302 relative to encoder ring 290. Adjustment knob 310 extends through plate 311, which is secured to the radial edge of mounting plate 280. Once the read head position is set, locking lever 304 holds adjustment lever 308 in place. Those skilled in the art will understand that the sensor mount is removable to allow replacement, adjustment, and / or maintenance of read head 302 without completely disassembling any other part of balancer 20.

[0060] When encoder ring movement is detected, the read head 302 generates an appropriate position signal and transmits it to a control system (not shown) that coordinates or correlates the tire's rotational position during spindle rotation. This information, along with other sensor information acquired during tire rotation by the spindle assembly, is used to determine the radial equilibrium position of the tire under test. In other words, using data generated from the force sensor and encoder, the position of the tire's focal point or spot's rotational angular displacement can be obtained.

[0061] exist Figure 9 and 11 As best shown in -13, the spring-biased return cylinder 46 can be carried by or mounted to a cylindrical mount 286 and surround one end of the spindle 250, but does not contact the main shaft. Cylinder 46 includes a main cylinder 320 having a shaft opening 322 passing through it. Extending from the main cylinder 320 is an outer radial flange 324, which provides a spring surface 326 on one side and a flange surface 327 on the opposite side. The main cylinder 320 also includes a cap surface 329 connecting the inner and outer surfaces of the main cylinder and facing the shaft cap 268. Annularly surrounding the main cylinder 320 is an outer cylinder 330 having a cylinder wall 332, from which an inner radial flange 336 extends radially inward. In the default state, the inner radial flange 336 is positioned near the flange surface 327, and in some embodiments, the inner radial flange 336 contacts the flange surface 327. Also extending radially inward from the cylinder wall 332 is the inward spring flange 333. A mounting bracket 340 extends axially from the outer cylinder 330, extending between the cylinder wall 332 and the inner radial flange 336, and is secured to the mounting body 288 by fasteners or other means. Furthermore, the inner radial flange has a flange sealing surface 342 that seals around the outer surface 343 of the master cylinder 320. Together, the master cylinder 320 and the outer cylinder 330 form an annular spring cavity 344 between the outer surface of the master cylinder 320 and the inner surface of the outer cylinder 330, as well as between the spring surface 326 and the inward spring flange 333. A plurality of fasteners 346 extend axially through the cylinder wall 332 and connect the mounting bracket 340 to the inner radial flange 336 and the lower edge of the mounting body 288. A cylindrical spring 350 is disposed in an annular spring cavity 344. The spring 350 is biased between the outer cylinder and the main cylinder, and particularly between the spring surface 326 and the inward spring flange 333.

[0062] like Figure 9 As shown in the optimal configuration, port 334 extends through the main cylinder wall, through which pressurized air can be supplied. (As shown in the image) Figure 9As best shown in 11 and 12, the port delivers pressurized air between the inner radial flange 336 and the adjacent flange surface 327. The inner radial flange 336, flange surface 327, the outer surface of the master cylinder 320, and the inner surface of the outer cylinder 330 form an annular cavity 337, which receives the pressurized air delivered through the port 334. Delivering air through this port and into the cavity 337 causes the outer radial flange 324 of the master cylinder to move from its default position and compress the cylindrical spring 350, which in turn axially drives the cap surface 329 away from the motor housing. Surface 329 engages and moves the shaft cap 268, which in turn moves the spindle 250 axially away from the motor assembly to move the spindle to a release position. Releasing air from the cavity 337 allows the spring to expand and thus removes the driving force from the cap surface 329 away from the shaft cap 268. This returns the spindle to its normal default position. Those skilled in the art will understand that the return cylinder applies force only to the spindle 250 and the dynamic balancer to disengage the clamping assembly 32 from the locking shaft 50, which allows the tire to be removed from the balancer. The return cylinder does not apply any force during spindle assembly rotation. As a result, the return cylinder does not apply any additional force to the balancer 20 during tire balancing operations.

[0063] Now refer to Figure 14 As can be seen, the control system, typically represented by the number 400, is used to operate the dynamic balancer 20, as schematically illustrated. However, all other accompanying drawings and the description above should also be consulted. The control system 400 includes a controller 404, which provides the necessary hardware, software, and memory to control and facilitate the operation of the various components of the balancer. The controller 404 receives input signals and sends output signals to the various components of the balancer 20 to control and coordinate their specific operations. A pressurized air supply 406 is connected to the return cylinder 46, where pressurized air is used to operate the clamping assembly 32. The air supply 406 is controlled by the controller 404 via a control signal designated by the capital letter A.

[0064] The dry air braking mechanism 500 is selectively connected to the locking member 30 to insert the locking shaft into the clamping assembly at appropriate times to capture the tire and run a balancing test, and to retract the locking member after the balancing test is completed. Mechanism 500 is controlled by controller 404 via a control signal specified by capital letter B. A pressurized air supply 410 is connected to the locking member via mechanism 500 to deliver pressurized air to the tire when it is captured between the upper and lower edges. Pressurized air supply 410 is operatively controlled by controller via a control signal typically specified by capital letter C. After the balancing operation is completed, the tire is deflated and air is expelled through mechanism 500, as described above.

[0065] Power supply 412 is connected to motor assembly 40 to supply electrical energy to the motor assembly 40, which causes the rotor and spindle components to rotate at appropriate times and speeds. Controller 404 sends and receives control signals to and from the power supply designated by the capital letter D.

[0066] The rotation of the rotor and spindle components is detected by the encoder assembly 42, and in particular by the read head 302. The controller 404 receives the position signal generated by the read head, which is represented by the uppercase letter E.

[0067] At least one force sensor 420 can be used, and in the illustrated embodiment, four force sensors can be used. The force sensors 420 are located around the outer circumference of the housing 24, wherein the force sensors are operatively connected to the frame 22 and communicate with the controller 404 via a control signal F. The force sensors detect the force generated by the rotating tire, which is used to determine if the tire is unbalanced, and if so, to determine the degree and location of the imbalance on the tire. Once the balancer has completed its operation, the location of the tire imbalance can be determined, and the controller 404, in conjunction with the position signal generated by the read head 302, will activate the marking system 424 to mark appropriate points on the tire sidewall to indicate the tire's position and balance. The marking system 424 is controlled by a signal designated by the capital letter G.

[0068] During operation, refer to Figure 14 The balancer is Figure 1 and 11 It is shown in the default locked state, and in Figure 12 and 13 The image is shown in the unlocked state. In the default state, the locking member 30 is received within the clamping assembly 32 and locked in place, so that no external force can separate the locking member from the clamping assembly. To operate the balancer, the controller 404 sends a signal to the air supply 406, and pressurized air is then delivered to the spring-biased return cylinder 46. This pressurized air causes the master cylinder pressure spring 350 to engage the cap surface 329 with the shaft cap 268, which in turn causes the spindle 250 to move axially through the lower spindle 208. This axial movement causes the inner sleeve 132 connected to the spindle to move axially to compress the locking device spring 134. This axial movement then causes the inner sleeve 132 to move the wedge sleeve 117 axially within the spindle body 140. This axial movement of the wedge sleeve causes the wedge claw 103 to move radially outward, which in turn causes the upper T-shaped member 99 to move radially outward, as... Figure 8 As shown. The result is that the claw tooth 108 disengages from the shaft tooth 64, where the claw tooth was previously received in the corresponding gap 66 (see...). Figure 8This disengagement allows the locking shaft to be axially removed from the clamping assembly via the mechanism 500 as described above. The air connector 520 and the connecting fitting 504 re-engage to deflate the tire. Next, the linear actuator 564 retracts, which causes the inner surface 556 of the flange to engage and lift the tapered portion 52, thereby lifting the locking shaft 50 out of the clamping assembly.

[0069] This axial removal separates the upper and lower edges, allowing any tire received between the upper and lower edges to move to the next manufacturing station and allowing the balancer to receive the next tire to be tested. Once the next tire is initially positioned between the two edges, the controller 404 determines the angular orientation of the locking member and clamping assembly via the encoder assembly—this indicates the angular position of the clamping assembly, spindle assembly, and motor assembly. The controller 404 then adjusts the position of the spindle assembly via the motor assembly so that the original position is obtained whenever the locking member is received. This ensures the consistency of the dynamic balancer test results. Next, the controller actuates the mechanism 500 to allow the actuator rod 568 to gradually lower the manifold 512 and air connector 520. As a result, the air connector 520 engages with the connecting fitting 504 in a controlled manner, and the locking shaft 50 is lowered to the appropriate position within the clamping assembly. In other words, the locking shaft is lowered a specified distance to capture the tire, which has a known bead width between the two edges. The locking shaft is simultaneously housed in the clamping assembly, which remains in the unlocked position.

[0070] Next, the controller extracts pressurized air from the return spring cylinder, which causes the clamping assembly to hold the locking shaft in place so that the new tire is captured between the upper and lower edges. Specifically, extracting air from the return spring cylinder allows the spindle to return to its default position, which in turn re-engages the clamping assembly with the locking member. In effect, it allows the wedge sleeves 117 to return to their original positions, which in turn engages the upper T-shaped member with the shaft (see...). Figure 7Once the clamping assembly re-engages with the spindle assembly, the controller instructs the air supply to inflate the tire and further lowers the inner surface 556 to no longer contact the tapered portion 52 and disengages the air connector 520 from the connecting fitting 504, thus maintaining tire pressure. Next, the power supply 412 delivers power to the motor 40, which then initiates the rotational movement of the rotor and related components of the spindle. The motor assembly thus rotates the rotor at the desired speed, and the rotational position is monitored by an encoder. Simultaneously, the force sensor 420 detects the force generated by the specific tire received between the edges, and this information is correlated with the rotational position information provided by the encoder. Upon completion of the test rotation via the spindle assembly, the controller determines whether the tire is unbalanced and then instructs the marking system 424 to mark the tire at the appropriate position. Those skilled in the art will understand that the controller can send precise signals to the motor 40 to correctly position the tire under the marking device of the marking system 424. Upon completion of the marking operation, the above process is repeated to release the tire and transfer it to the next tire manufacturing operation.

[0071] The balancer disclosed herein offers several advantages. First, the locking member has a non-circular cross-section, and in this embodiment, a square cross-section, to allow the locking member to actively clamp in a specific direction. This allows significant clamping forces to be applied to the locking member via the clamping assembly, enabling it to rotate at significant speeds without generating excessive vibration and / or stress on other components of the balancer. In this embodiment, the original position can be utilized such that the locking member is always received within the clamping assembly in the same orientation. Those skilled in the art will understand that this minimizes the determination of the characteristic forces of the locking member as it rotates at speeds, in order to accommodate any specific forces specific to the balancer.

[0072] Another advantage of the invention is the use of a frameless motor assembly for the rotating spindle assembly. This is important because the motor assembly introduces minimal external force when the spindle assembly is not driven by a belt mechanism or other rotating features that apply force as detected by a force sensor. Another advantage of the invention is the use of a return cylinder, which allows the clamping assembly to actively engage with the locking member. This is further facilitated by the non-circular cross-section of the locking member and the use of form-fitting teeth between the clamping and locking members, where these teeth readily engage with each other. The structure of the motor assembly is also advantageous, utilizing heat sinks and thermally conductive epoxy to dissipate the heat generated by the motor, thereby allowing for the application of higher power, enabling the rotor assembly and spindle assembly to rotate at speeds significantly higher than other known dynamic balancers.

[0073] Therefore, it can be seen that the objective of the present invention is achieved through the above-described structure and its method of use. Although only the best mode and preferred embodiments have been described in detail in accordance with patent law, it should be understood that the present invention is not limited thereto or thereby restricted. Therefore, for a true understanding of the scope and breadth of the present invention, reference should be made to the following claims.

Claims

1. A dynamic balancer, comprising: shell; A spindle assembly rotatably mounted on the housing; A frameless motor assembly, the frameless motor assembly being connected to the spindle assembly; A clamping assembly adapted to receive a locking member to capture a tire between the clamping assembly and the locking member, the clamping assembly and the locking member being captured in the spindle assembly and rotated by the frameless motor assembly; The locking member has a locking shaft, which is provided with a plurality of shaft teeth; The clamping assembly includes: The lower edge has a shaft opening therethrough to receive the locking shaft, and the lower edge has at least one T-shaped cavity; At least one wedge-shaped claw, the at least one wedge-shaped claw being radially movable in a corresponding one of the at least one T-shaped cavities, the at least one wedge-shaped claw having a side surface with claw teeth that engage with the shaft teeth of the locking shaft when the locking shaft is received in the shaft opening; and At least one wedge sleeve, the at least one wedge sleeve being slidably engaged with the opposite side of the at least one wedge claw, wherein axial movement of the at least one wedge sleeve causes the at least one wedge claw to move into engagement with the locking shaft and disengage from engagement with the locking shaft.

2. The dynamic balancer according to claim 1, wherein the at least one wedge sleeve drives the at least one wedge claw to engage with the locking shaft and rotate the locking shaft.

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