CN118209252B

CN118209252B - A wheel hub dynamic balancing measuring device and wheel hub measuring equipment

Info

Publication number: CN118209252B
Application number: CN202410299702.8A
Authority: CN
Inventors: 房振峰; 邓媞; 袁高鹏; 胡然; 孙玉洁; 朱月强; 陈长昊
Original assignee: Jike Science and Technology Co Ltd
Current assignee: Jike Science and Technology Co Ltd
Priority date: 2024-03-15
Filing date: 2024-03-15
Publication date: 2025-01-24
Anticipated expiration: 2044-03-15
Also published as: CN118209252A

Abstract

A wheel hub dynamic balance measuring device includes: a frame; a spindle mechanism, the spindle mechanism has a spindle, the spindle is used to install the wheel hub and drive the wheel hub to rotate; a first support rod, the first support rod is an elastic component, the first support rod connects the frame and the spindle mechanism; a sensor, the sensor is fixed on the frame, the detection end of the sensor is connected to the spindle mechanism, and detects the force when the spindle mechanism shakes. From the above, the spindle mechanism is connected to the frame through the first support rod. When the spindle mechanism drives the wheel hub to rotate, if the center of gravity of the wheel hub is not at the axis center position, the spindle will cause the wheel hub and the spindle mechanism to shake due to the center of gravity offset when driving the wheel hub to rotate. The force generated by the shaking will be transmitted to the detection end, so as to detect the centrifugal force when the wheel hub rotates. Therefore, the dynamic balance of the wheel hub can be detected by detecting the centrifugal force, and the position and number of balancing blocks added to the wheel hub can be determined so that the center of gravity of the wheel hub is at the axis center position of the wheel hub.

Description

Hub dynamic balance measuring device and hub measuring equipment

Technical Field

The application relates to the technical field of hub detection, in particular to a hub dynamic balance measuring device and hub measuring equipment.

Background

Some moving bodies rotating at high speed such as wheels, turntables, fans and the like have more or less uneven mass distribution, processing level deviating from design values and the like due to various problems such as material quality, processing technology, assembly quality and the like, so that the principal axis of inertia of the center of mass of the rotating body is not overlapped with the rotating shaft represented by the actual rotating center. When rotating, a centrifugal force acts on the rotating shaft, and this inertial centrifugal force must act on its support (bearing, etc.) through the rotating shaft and thus be transmitted to the machine body. The wheel is an extremely important component in the motion of the automobile, and the dynamic balance of the hub is an extremely important performance index, which affects the running stability and safety of the automobile, so that a hub dynamic balance measuring device and a hub measuring equipment are needed to be capable of detecting the dynamic balance parameters of the hub.

Disclosure of Invention

The application provides a hub dynamic balance measuring device and a hub measuring device which are easy to detect hub dynamic balance.

In order to achieve the aim, the first aspect of the application provides a hub dynamic balance measuring device which comprises a frame, a main shaft mechanism, a first support rod and a sensor, wherein the main shaft mechanism is provided with a main shaft which is vertically arranged and is used for installing a hub and driving the hub to rotate by taking a vertical axis as a center, the first support rod is a shaft-shaped spring steel piece and is horizontally arranged and connected with the frame and the main shaft mechanism to support the main shaft mechanism in a cantilever manner, the sensor is fixed on the frame, a detection end of the sensor is connected with the main shaft mechanism, and the detection direction of the detection end is perpendicular to the axial directions of the first support rod and the main shaft.

From the above, spindle unit passes through first bracing piece to be connected in the frame, and when spindle unit driven wheel hub rotated, if wheel hub's focus was not in the axle center position, the main shaft was when driving wheel hub rotation, can make wheel hub and spindle unit take place to rock because of the focus skew. Because the sensor is fixed in the frame, the detection end of sensor is connected with spindle unit, and when wheel hub and spindle unit rock, the force that rocks and produce can transmit to the detection end to detect the centrifugal force when wheel hub rotates. Therefore, the dynamic balance of the hub can be detected by detecting the centrifugal force, and the positions and the number of the weights added on the hub are determined so that the center of gravity of the hub is positioned at the axle center of the hub.

In addition, according to the application, the main shaft is arranged vertically, so that the hub can be kept in a horizontal state when the hub is placed on the main shaft. Therefore, when the hub is conveyed between two adjacent stations of the hub dynamic balance measuring device, the hub can be conveyed in a horizontal state, and the influence on conveying safety due to hub rolling during vertical conveying of the hub can be avoided. At the same time, by having the spindle arranged vertically, the hub can be easily placed on the spindle.

After the hub is placed on the main shaft, the hub can be automatically horizontally positioned under the action of dead weight, so that the convenience of installing the hub is improved. Simultaneously, the main shaft can also conveniently center the hub in a mode of expanding the expansion claw, and the like, so that the convenience of installing the hub is further improved. In addition, as the main shaft is vertically arranged, the hub is horizontally arranged on the main shaft, the center of the hub coincides with the center of the main shaft no matter how the size and the specification of the hub change, so that the center is unique, and the dynamic balance calculation can be facilitated.

Meanwhile, due to the fact that the main shaft is arranged vertically, the hub rotates in the horizontal plane after being mounted on the main shaft. If the first support bar supports the spindle mechanism in a vertical manner, the hub moves the spindle mechanism and the hub in a circular motion (more precisely, in a conical motion with the apex downward) due to the shift of the center of gravity when the hub rotates with the spindle, thereby making it difficult to detect the dynamic balance. In the application, the first support rod is horizontally arranged, and the movement direction of the main shaft mechanism can be limited in the axial direction through the first support rod, so that the movement of the main shaft mechanism and the hub can be changed into fan-shaped swing during dynamic balance detection, or the movement direction is enabled to be virtually or approximately horizontally shifted, and therefore, the dynamic balance data can be conveniently detected.

In the present application, the detection direction of the detection end is perpendicular to the axial direction of the first support rod and the spindle, so that the detection direction of the detection end can be identical to the shaking direction of the spindle mechanism. Therefore, the detection precision of the hub dynamic balance measuring device can be further improved.

As a possible implementation manner of the first aspect, the extending direction of the first supporting rod is perpendicular to the axial direction of the main shaft.

By the aid of the structure, the extending direction of the first supporting rod is perpendicular to the axial direction of the main shaft, so that the main shaft mechanism is more stable when the driving wheel hub rotates, and the offset of the main shaft mechanism when the main shaft mechanism shakes along with the wheel hub is reduced.

As a possible implementation manner of the first aspect, the sensor is disposed at a position close to the first support rod.

By arranging the sensor at a position close to the first support rod, the difference between the force received by the end of the sensor and the shaking force received by the first support rod can be reduced when the spindle mechanism shakes along with the hub. Thus, the detection accuracy of the hub dynamic balance measuring device can be improved.

As a possible implementation manner of the first aspect, the first support rod is provided with a plurality of support rods.

By last, through setting up a plurality of first bracing pieces, can improve spindle unit's stability, reduce spindle unit and rock the range of rocking when rocking along with the wheel hub, avoid rocking the range too big and cause the damage to equipment.

As a possible implementation manner of the first aspect, the sensor is provided with a plurality.

By providing a plurality of sensors as described above, the shift direction and the shift amount of the center of gravity of the hub can be determined from the data detected by the plurality of sensors. Thus, the detection accuracy of the hub dynamic balance measuring device can be improved.

As a possible implementation manner of the first aspect, a plurality of the first support rods are disposed on two sides of the spindle mechanism in a rectangular shape on average.

By arranging the plurality of first support rods on the two sides of the main shaft mechanism in a rectangular shape on average, the main shaft mechanism can be supported at a plurality of positions on the two sides of the main shaft mechanism, and the constraint of the main shaft mechanism in the axial direction of the first support rods can be improved. Therefore, the fan-shaped swing of the spindle mechanism during dynamic balance detection of the hub can be enabled to be more close to left-right translation, and therefore the detection precision of dynamic balance can be improved.

As a possible implementation manner of the first aspect, the device further comprises a supporting plate, wherein two ends of the supporting plate are detachably and fixedly connected with the frame and the spindle mechanism respectively.

Therefore, when the hub dynamic balance measuring device is transported and installed, the main shaft mechanism can shake greatly, and if the shake amplitude is too large, the sensor can be damaged. According to the application, the support plate which is detachably connected is arranged between the frame and the main shaft mechanism, so that the support plate can be detached to avoid influencing detection when the dynamic balance of the hub is detected. And when the dynamic balance measuring device of the hub is transported and installed and the like, and the dynamic balance detection of the hub is not needed, the supporting plate is installed between the main shaft mechanism and the frame, so that the stability of the main shaft mechanism can be improved, and the phenomenon that the sensor is damaged due to overlarge shaking amplitude of the main shaft mechanism is avoided.

As a possible implementation manner of the first aspect, the spindle is vertically arranged, and the device further comprises a second supporting rod, wherein the second supporting rod is vertically arranged, the upper part of the second supporting rod is fixedly connected with the spindle mechanism, and the lower end of the second supporting rod is abutted to the frame.

From the top, through the vertical second bracing piece that sets up, support spindle unit by the second bracing piece in vertical direction to can reduce when first bracing piece rocks along with spindle unit, the deformation that takes place in vertical direction can make spindle unit carry out the fan-shaped swing of dynamic balance detection time to wheel hub and more be close horizontal translation. Therefore, the swaying direction of the main shaft mechanism is closer to the detection direction of the detection end of the sensor, so that the detection precision of the sensor can be improved, and the detection precision of the hub dynamic balance measuring device can be improved.

As a possible implementation manner of the first aspect, the bottom end of the second supporting rod is provided with a ball, and/or the second supporting rod is a spring steel piece.

By the above, through set up the ball in the bottom of second bracing piece to can become sliding friction and roll, thereby can reduce the frictional force of second bracing piece and frame, and then can reduce the influence of second bracing piece to rocking range when spindle unit rocks along with wheel hub, thereby can improve detection precision. Through making the second bracing piece be spring steelwork, can make the second bracing piece carry out deformation on the horizontal direction to can reduce the influence of second bracing piece to rocking amplitude when spindle unit rocks along with wheel hub, thereby can improve detection accuracy.

As one possible implementation manner of the first aspect, the device further comprises a conveying mechanism, wherein the conveying mechanism comprises two conveying belts, a first driving cylinder and a second driving cylinder, the two conveying belts are arranged and are arranged at two sides of the main shaft in parallel and used for driving the wheel hub to move in the horizontal direction so as to enable the wheel hub to move above the main shaft, and the first driving cylinder is connected with the conveying belts and drives the conveying belts to move up and down.

Therefore, the hub can be conveyed to the upper side of the main shaft through the conveying belt, and the conveying belt can be driven to descend through the first driving cylinder, so that the hub can be lowered onto the main shaft, and the main shaft drives the hub to rotate.

As one possible implementation manner of the first aspect, the centering mechanism further comprises a centering roller, wherein the centering roller is provided with a plurality of centering rollers, the centering rollers are vertically arranged above the main shaft and are arranged around the main shaft, and the second driving cylinder is in transmission connection with the centering rollers and drives the centering rollers to approach towards the axis of the main shaft.

From the above, can drive the centering roller through the second actuating cylinder and be close to towards the axle center of main shaft to can push the axle center coincidence of wheel hub and the axle center of main shaft, so that after the first actuating cylinder drive conveying roller descends, make things convenient for wheel hub to install on the main shaft. Meanwhile, when the hub rotates along with the main shaft, the hub can rotate around the axle center of the hub, so that the detection precision of balance detection can be improved.

The second aspect of the application provides hub measurement equipment, which comprises a hub dynamic balance measurement device, a hub runout measurement device and a control device, wherein the hub dynamic balance measurement device is any one of the hub dynamic balance measurement devices in the first aspect of the application, and the hub runout measurement device is used for measuring a runout parameter when the hub rotates.

Compared with the prior art, the hub dynamic balance measuring device and the hub measuring equipment have the advantages that at least the hub dynamic balance can be detected through detecting centrifugal force, and the detection precision of the hub dynamic balance measuring device can be improved.

These and other aspects of the invention will be apparent from and elucidated with reference to the embodiment(s) described hereinafter.

Drawings

The various features of the application and the connections between the various features are further described below with reference to the figures. The figures are exemplary, some features are not shown in actual scale, and some features that are conventional in the art to which the application pertains and are not essential to the application may be omitted from some figures, or additional features that are not essential to the application may be shown, and the combination of features shown in the figures is not meant to limit the application. In addition, throughout the specification, the same reference numerals refer to the same. The specific drawings are as follows:

FIG. 1 is a schematic layout of a hub measurement apparatus according to the present application;

FIG. 2 is a schematic front side elevation view of the hub runout measuring device of FIG. 1;

FIG. 3 is a schematic view of the front projection structure of the hub runout measuring device shown in FIG. 1;

FIG. 4 is a schematic perspective view of the hub runout measuring device shown in FIG. 1 with a portion omitted;

FIG. 5 is a schematic side elevation view of the moving mechanism and the detecting mechanism in FIG. 4;

FIG. 6 is a schematic diagram of a three-dimensional structure of the moving mechanism and the detecting mechanism in FIG. 4;

FIG. 7 is a schematic side elevation view of the detection mechanism of FIG. 6;

FIG. 8 is a schematic top front projection of the detection mechanism of FIG. 6;

FIG. 9 is a schematic perspective view of the detection mechanism of FIG. 6;

FIG. 10 is a schematic side elevation view of the dynamic balance measuring apparatus of FIG. 1;

FIG. 11 is a schematic perspective view of the hub dynamic balance measuring device of FIG. 10 with a part of the structure omitted;

FIG. 12 is a schematic side elevation view of the mounting structure of the second spindle mechanism of FIG. 10;

FIG. 13 is a schematic perspective view of a mounting structure of the second spindle mechanism of FIG. 10;

fig. 14 is a schematic perspective view of the blanking device in fig. 1;

FIG. 15 is a rear side elevational view of the buffer stop of FIG. 1;

FIG. 16 is a front side elevational view of the buffer stop of FIG. 1;

FIG. 17 is a schematic side elevation view of the buffer stop of FIG. 1;

FIG. 18 is a schematic perspective view of the buffer stop device of FIG. 1;

fig. 19 is a partial cross-sectional view of the shock absorber stop device A-A of fig. 15.

Description of the reference numerals

10 Hub measurement equipment; 100 wheel hub runout measuring device, 110 moving mechanism, 111 first sliding rail, 112 second sliding rail, 113 first driving motor, 114 second driving motor, 115 first lead screw, 116 second lead screw, 120 detecting mechanism, 121 first mounting piece, 121a third sliding rail, 121b limit part, 121c screw hole, 122 second mounting piece, 122a first mounting piece, 122b second mounting piece, 122c sliding block, 123 first displacement sensor, 124 third mounting piece, 124a dust cover, 124b notch, 125 second displacement sensor, 126 measuring head, 127 first elastic piece, 128 measuring head pin, 129 limit piece, 130 first main shaft mechanism, 131 first main shaft, 140 first conveying mechanism, 141 first conveying belt, 142 first driving cylinder, 150 first centering mechanism, 151 first centering roller, 200 wheel hub dynamic balance measuring device, 210 frame, 220 second main shaft mechanism, 221 second main shaft, 222 connecting piece, 230 first supporting rod, 240 force sensor, 250 second supporting rod, ball 260, 260 second conveying mechanism, 261 second conveying belt, 262, 340 second conveying belt, 340, second main shaft, 320 second damping roller, 320, and 360 first damping roller, and 35.

Detailed Description

The terms first, second, third and the like in the description and in the claims, are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order, and it is understood that the specific order or sequence may be interchanged if permitted to implement embodiments of the application described herein in addition to those illustrated or described herein.

The term "comprising" as used in the description and claims should not be interpreted as being limited to the list hereafter, it does not exclude other elements. It should thus be construed as specifying the presence of the stated features, integers or components as referred to, but does not preclude the presence or addition of one or more other features, integers or components, or groups thereof. Thus, the expression "a device comprising means a and B" should not be limited to a device consisting of only components a and B.

Reference in the specification to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the invention. Thus, appearances of the phrases "in one embodiment" or "in an embodiment" in various places throughout this specification are not necessarily all referring to the same embodiment, but may. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments as would be apparent to one of ordinary skill in the art from this disclosure.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. If there is a discrepancy, the meaning described in the present specification or the meaning obtained from the content described in the present specification is used. In addition, the terminology used herein is for the purpose of describing embodiments of the application only and is not intended to be limiting of the application.

In order to accurately describe the technical content of the present application and to accurately understand the present application, the following explanation or definition is given for terms used in the present specification before explaining the specific embodiments.

Dynamic balance, namely, the phenomenon that the mass distribution of a moving body rotating at a high speed is uneven, and the mass distribution deviates from the processing level of a design value due to various problems such as materials, processing technology and assembly quality, and the like, so that an inertial main shaft at the center of a rotating body is not overlapped with an actual rotating main shaft, unbalanced moment is generated to vibrate, and therefore, dynamic balance is also called dynamic unbalance.

Run out, the difference between the maximum and minimum readings measured by the fixed position indicator in a given direction, when the reference axis makes one revolution.

Hereinafter, a detailed description will be given of a specific structure of the hub measurement apparatus 10 in the present application with reference to the accompanying drawings.

Fig. 1 is a schematic layout of a hub measurement apparatus 10 according to the present application. As shown in fig. 1, the hub measurement device 10 in the present application includes a hub runout measurement device 100, a hub dynamic balance measurement device 200, a buffer stop device 300, a first roller conveyor 400, and a blanking device 500. Wherein, the two blanking devices 500 are arranged, and the first conveying roller way 400, the wheel hub runout measuring device 100, the wheel hub dynamic balance measuring device 200 of the blanking device 500 and the blanking device 500 are arranged in a straight line. The first rollgang 400 is used for conveying the hub to the hub runout measuring device 100, and the hub runout measuring device 100 is used for performing runout detection on the hub. The blanking device 500 behind the wheel hub runout measuring device 100 is used for conveying the wheel hub detected by the wheel hub runout measuring device 100 to the wheel hub dynamic balance measuring device 200, the wheel hub dynamic balance measuring device 200 carries out dynamic balance detection on the wheel hub, and the blanking device 500 behind the wheel hub dynamic balance measuring device 200 conveys the wheel hub to the next process after the detection is completed.

The buffer stop device 300 is provided with two, is located the wheel hub corresponding position on two unloader 500 respectively, and when wheel hub dynamic balance measuring device 200 detects with wheel hub and beats measuring device 100 and two unloader 500 respectively and carry the preset position, buffer stop device 300 can detect the information of in place of wheel hub. When the buffer blocking device 300 detects the in-place information of the hub, the corresponding control blanking device 500 stops conveying the hub, so that the hub stops at a preset position, and the roller on the blanking device 500 continues to rotate to scratch the hub after the hub stops in place under the blocking of the buffer blocking device 300. When the hub runout measuring device 100 is qualified in the detection result of the hub, the blanking device 500 behind the hub runout measuring device 100 can convey the hub to the hub dynamic balance measuring device 200, and the hub dynamic balance measuring device 200 detects the dynamic balance of the hub. When the hub runout measuring device 100 detects that the hub is unqualified, the blanking device 500 behind the hub runout measuring device 100 can push the unqualified hub onto the blanking roller way through the push plate to recycle the hub. Similarly, when the hub dynamic balance measuring device 200 is qualified as the hub detection result, the blanking device 500 behind the hub dynamic balance measuring device 200 can send the hub to the next process. When the hub dynamic balance measuring device 200 detects that the hub is unqualified, the blanking device 500 behind the hub dynamic balance measuring device 200 can push the unqualified hub on the blanking device 500 onto the blanking roller way through the push plate to recycle the hub.

Hub runout measuring device 100

Fig. 2 is a schematic front-side orthographic view of the hub runout measuring device 100 in fig. 1, fig. 3 is a schematic right-side orthographic view of the hub runout measuring device 100 in fig. 1, and fig. 4 is a schematic perspective view of the hub runout measuring device 100 in fig. 1 with parts omitted. As shown in fig. 2 to 4, the hub runout measuring device 100 of the present application includes a moving mechanism 110, a detecting mechanism 120, a first spindle mechanism 130, a first conveying mechanism 140 and a first centering mechanism 150. The first conveying mechanism 140 conveys the hub sent from the first conveying roller table 400 to a position above the first spindle mechanism 130, and then the first centering mechanism 150 centers the hub. The hub is then placed on the first spindle mechanism 130 by the first conveying mechanism 140, and the hub is driven to rotate about the hub axis by the first spindle mechanism 130. The moving mechanism 110 drives a measuring head 126 of the detecting mechanism 120, which will be described below, to contact the outer peripheral surface of the hub, and detects runout of the hub.

As shown in fig. 2 to 4, the first spindle mechanism 130 has a first spindle 131 vertically disposed, and after the hub is placed on the first spindle 131, the first spindle 131 may be engaged with the hub. The first main shaft 131 may drive the hub to rotate around the axle center of the hub under the driving of the motor.

As shown in fig. 2 to 4, the first conveying mechanism 140 includes a first conveying belt 141 and a first driving cylinder 142. The first conveyor belts 141 are disposed in two parallel on two sides of the first main shaft 131, and extend along the front-rear direction, and are used for driving the hub to move back and forth in the horizontal direction, so that the hub moves above the first main shaft 131. The first driving cylinder 142 is connected to the first conveyor 141 below the first conveyor 141, and drives the first conveyor 141 to move up and down. Accordingly, the hub can be conveyed to the upper side of the first main shaft 131 by the first conveying belt 141, and the first conveying belt 141 can be driven to descend by the first driving cylinder 142, so that the hub can be lowered onto the first main shaft 131, the first main shaft 131 can rotate with the hub, and the detection mechanism 120 can detect runout of the hub.

As shown in fig. 2 and 3, the first centering mechanism 150 includes a first centering roller 151 and a second driving cylinder (not shown). The four first centering rollers 151 are vertically disposed above the first main shaft 131, and are disposed around the first main shaft 131 in a square shape. The second driving cylinder is connected to the plurality of first centering rollers 151 by a link transmission, and drives the four first centering rollers 151 to approach toward the axis of the first main shaft 131 in a vertical state. Therefore, the first centering roller 151 can be driven by the second driving cylinder to approach towards the axis of the first main shaft 131, so that the axis of the hub can be pushed to coincide with the axis of the first main shaft 131, and the hub can be conveniently mounted on the first main shaft 131 after the first driving cylinder 142 drives the conveying roller to descend. Meanwhile, when the hub rotates along with the first main shaft 131, the hub can be rotated by taking the axle center of the hub as the center, so that the detection precision of runout detection can be improved.

Fig. 5 is a schematic side front projection structure of the moving mechanism 110 and the detecting mechanism 120 in fig. 4, and fig. 6 is a schematic perspective view of the moving mechanism 110 and the detecting mechanism 120 in fig. 4. As shown in fig. 5 and 6, the moving mechanism 110 includes a first slide 111, a second slide 112, a first driving motor 113 and a second driving motor 114. The first slide rail 111 is disposed at a position on one side of the first spindle mechanism 130, and extends in a radial direction of the hub. The second sliding rail 112 is disposed on the first sliding rail 111 and extends along the vertical direction, and the second sliding rail 112 is slidably connected with the first sliding rail 111, so that the second sliding rail 112 can move on the first sliding rail 111 along the radial direction of the hub. The first mounting member 121 of the detection mechanism 120, which will be described below, is disposed on the second slide rail 112 and slidably connected to the second slide rail 112, so that the detection mechanism 120 can move in the up-down direction on the second slide rail 112. The two detection mechanisms 120 are arranged, and in the waiting state, the two detection mechanisms 120 are respectively positioned at the upper end and the lower end of the second slide rail 112. The first driving motor 113 is fixed on the first sliding rail 111 and is located at one end of the first sliding rail 111. The driving rod of the first driving motor 113 is connected with a first screw rod 115 extending along the first sliding rail 111, and the first screw rod 115 and the second sliding rail 112 form a screw transmission structure. The first driving motor 113 can drive the second slide rail 112 to slide along the first slide rail 111 in a direction approaching/separating from the hub by forward/reverse rotation. The second driving motors 114 are provided in two and fixed to the upper ends of the second slide rails 112. The respective driving rods of the two second driving motors 114 are respectively connected with a second screw rod 116 extending along the second slide rail 112, the two second screw rods 116 respectively form a screw transmission structure with a first mounting member 121 of a detection mechanism 120, which will be described below, and the second driving motors 114 drive the detection mechanism 120 to slide up/down on the second slide rail 112 through forward rotation/reverse rotation. Thus, the second slide rail 112 is driven to slide along the first slide rail 111 by the first driving motor 113, so that the detection mechanism 120 on the second slide rail 112 can be moved in the horizontal direction, and the detection mechanism can be moved toward/away from the hub. The detection mechanism 120 is driven to slide along the second slide rail 112 by the second driving motor 114, so that the detection mechanism 120 can be moved in the vertical direction. Thus, the position of the detection mechanism 120 can be adjusted, so that a detection head of the detection mechanism 120, which will be described below, is brought into contact with the position to be detected of the hub, and runout detection is performed on the hub. By providing two detection mechanisms 120, the runout amounts at two different positions of the hub can be detected simultaneously. Thus, the detection efficiency can be improved and the detection time can be shortened.

Fig. 7 is a schematic side orthographic view of the detection mechanism 120 in fig. 6, fig. 8 is a schematic top orthographic view of the detection mechanism 120 in fig. 6, and fig. 9 is a schematic perspective view of the detection mechanism 120 in fig. 6. As shown in fig. 7 to 9, the detection mechanism 120 includes a first mount 121, a second mount 122, a first displacement sensor 123, a detection arm 124, a second displacement sensor 125, and a measurement head 126. The first mounting member 121 is mounted on the second sliding rail 112 and is slidably connected to the second sliding rail 112. The first mounting member 121 is in screw connection with the second driving motor 114, and the second driving motor 114 can drive the first mounting member 121 to move up and down along the second sliding rail 112. The second mounting member 122 is mounted on the first mounting member 121, and is slidably connected to the first mounting member 121 in the radial direction of the hub (left-right direction in fig. 7). Specifically, a third slide rail 121a is disposed on the first mounting member 121 along the radial direction of the hub, and a first mounting portion 122a of the second mounting member 122, which is described below, is slidably connected to the third slide rail 121 a. The third slide rail 121a is further provided with a limiting portion 121b at both end positions, and the limiting portion 121b is configured to limit the sliding range of the first mounting portion 122a and prevent the first mounting portion 122a from being separated from the third slide rail 121 a. The first displacement sensor 123 is fixed to the first mounting member 121 on the side of the spacing portion 121b away from the hub, so that it is unnecessary to provide a special mounting member for mounting the first displacement sensor 123, thereby reducing the number of parts and making the structure more compact. The first displacement sensor 123 is disposed along the radial direction of the hub, and the detection end of the first displacement sensor 123 abuts against an intermediate position of the first mounting portion 122a of the second mounting member 122, which is opposite to the end of the hub. When the second mounting member 122 slides along the radial direction of the hub, the detection end of the first displacement sensor 123 can be directly pushed to move along the radial direction of the hub. Thus, not only the size of the detection mechanism 120 in the radial direction of the hub can be reduced, but also the radial runout parameter of the hub can be directly detected by detecting the displacement of the second mounting member 122, so that the detection accuracy can be improved. As shown in fig. 7 to 9, the first displacement sensor 123 is located in a space between the first mounting member 121 and the detecting arm 124, and the first displacement sensor 123 overlaps the detecting arm 124 when viewed from the side as shown in fig. 7, so that the first displacement sensor 123 can be located at a central position for detection when detecting the radial runout of the hub transmitted by the detecting arm 124, so as to improve the detection accuracy of the radial runout.

The sensing arm 124 extends in the radial direction of the hub, and the sensing arm 124 is hinged to the second mounting member 122 at an intermediate position so that the sensing arm 124 can swing (rotate) up and down. The second displacement sensor 125 is provided on the second mount 122, and the second displacement sensor 125 is provided along the axial direction (up-down direction) of the hub, and the detection end of the second displacement sensor 125 abuts against the detection arm 124. When the detection arm 124 swings, the detection arm 124 may push the detection end of the second displacement sensor 125 to move, thereby detecting the rotation amplitude of the detection arm 124. A measurement head 126 is provided on the test arm 124 towards the hub end for abutment with the hub. The measuring head 126 is a roller, and the axis of the measuring head 126 and the extending direction of the detecting arm 124 form a certain angle, when the measuring head 126 is abutted against the part to be detected on the outer peripheral surface of the hub, the axis of the measuring head 126 can be parallel to the tangent line of the part to be detected. Thus, when the size of the portion to be inspected fluctuates in the radial direction, the second mount 122, the inspection arm 124, can be pushed by the measuring head 126 to move in the radial direction of the hub. When the size of the portion to be inspected fluctuates in the axial direction, the inspection arm 124 can be pushed to rotate in the axial direction of the hub by the measuring head 126. As shown in fig. 7, the distance between the position where the detection end of the second displacement sensor 125 abuts against the detection arm 124 and the position where the detection arm 124 is hinged is greater than the distance between the position where the measurement head 126 abuts against the hub and the position where the detection arm 124 is hinged, so that when the detection arm 124 transmits the axial runout through rotation, the runout value detected by the second displacement sensor 125 can be amplified, and the axial runout can be detected more easily.

From above, the displacement mechanism moves detection mechanism 120 to the testing position and makes measuring head 126 and wheel hub butt, when measuring the runout of wheel hub, through making second mounting piece 122 and first mounting piece 121 along the radial sliding connection of wheel hub, when the wheel hub changes in radial size, can promote second mounting piece 122 to slide on first mounting piece 121 through measuring head 126 to detect the displacement of second mounting piece 122 through first displacement sensor 123, thereby can detect the runout of wheel hub in radial. By the detection arm 124 being hinged to the second mounting member 122, when the dimension of the hub in the axial direction is changed, the detection arm 124 can be pushed to rotate on the second mounting member 122 by the measurement head 126, and the rotation amount of the detection arm 124 can be detected by the second displacement sensor 125, so that the runout amount of the hub in the axial direction can be detected. Therefore, the runout of the hub in the radial direction and the axial direction can be detected. Further, by providing the detection arm 124 to the second attachment 122 and providing the measurement head 126 to the detection arm 124, the runout of the hub in the radial direction and the axial direction can be detected at the same time after the measurement head 126 is brought into contact with the hub. Thus, the structure of the detection mechanism 120 can be simplified, and the structure of the detection mechanism 120 can be made more compact.

Meanwhile, when the hub is subjected to runout measurement, the requirements on the stability and the detection precision of the detection are very high, so that the sliding connection mode is adopted, the sliding connection mode needs to have a large enough matching length between the sliding block and the sliding rail, namely, the first mounting part 122a (the sliding block 122 c) and the third sliding rail 121a are required to be set to be large in size, the sliding stability can be ensured, and the detection precision is improved. Therefore, the size of the sliding connection structure between the first and second mounting pieces 121 and 122 is large. If the detection in the radial direction of the hub is also provided in a sliding connection, even if the detection arm 124 is slidably connected to the second mounting member 122, the size of the sliding connection structure between the detection arm 124 and the second mounting member 122 also needs to be provided in a large structure to satisfy the requirements of the stability of the sliding and the detection accuracy. In the present application, by hinging the detection arm 124 with the second mount 122 at its intermediate position, as shown in fig. 7 and 8, the size of the hinge structure can be adapted to the size of the first mount 122a, and it is not necessary to protrude from the first mount 122a, so that the size of the connection structure between the detection arm 124 and the second mount 122 can be reduced, thereby making the structure more compact.

In the present application, the radial runout measurement is performed by sliding the second mount 122 left and right (radial runout) on the first mount 121, and the axial runout measurement is performed by rotating the detection arm 124 up and down (axial runout) on the second mount 122. Therefore, the axial runout and the radial runout can be directly detected simultaneously. If the structure opposite to the structure is adopted (namely, radial runout adopts left-right rotation and axial runout adopts up-and-down sliding), the axial runout and the radial runout are detected, and the sliding direction is changed along with the change of the rotating direction, so that the accuracy of runout measurement is affected. Meanwhile, when the opposite structure is adopted, since the detecting arm 124 needs to slide up and down on the second mounting member 122, the extending direction of the detecting arm 124 is different from the sliding direction thereof, so that the detecting arm 124 needs to be provided with a turning structure, which affects the compactness of the structure. Even with the above structure of the present application, not only the stability of the motion during the runout detection can be improved, but also the compactness of the structure can be improved.

Further, as an example, the first displacement sensor 123 and the second displacement sensor 125 each have a sensor body and a spindle attached to the sensor body, the spindle being telescopically movable in the axial direction relative to the sensor body, and a spring is attached therebetween, and the spring biases the spindle so as to be capable of restoring movement in the axial direction. The 'detection end' is positioned on the measuring rod.

As shown in fig. 7 and 8, the first displacement sensor 123 is mounted at a position where the axis thereof perpendicularly intersects with the rotation axis of the detection arm 124, and a notch 124b is provided in the detection arm 124 so as to avoid the mounting screw (screw hole 121c is shown in the drawing and no screw is shown) of the first displacement sensor 123. Thus, when the first displacement sensor 123 is mounted, the screw can be conveniently mounted in the screw hole 121c from the position of the notch 124b to fix the first displacement sensor 123.

As shown in fig. 7-9, the second mount 122 includes a first mount portion 122a and a second mount portion 122b. The first mounting portion 122a is a square block-shaped member as a whole, and one side surface of the first mounting portion 122a is slidably connected to the first mounting member 121. The second mounting portion 122b is provided on the other side surface of the first mounting portion 122a, and the detection arm 124 is also provided on the other side surface of the first mounting portion 122a, hinged to the first mounting portion 122 a. The second mounting portion 122b is located on a plane on which the detection arm 124 rotates, and is parallel to the detection arm 124 that is not in the detection state. The second displacement sensor 125 is fixed to the second mounting portion 122b, and is also positioned on a plane on which the detection arm 124 rotates (swings), and the extending direction of the second displacement sensor 125 is perpendicular to the extending direction of the second mounting portion 122b, so that the measuring rod of the second displacement sensor 125 abuts against the detection arm 124.

As shown in fig. 7-9, the detection mechanism 120 further includes a first elastic member 127 and a probe pin 128. Wherein, the gauge head pins 128 are provided in two and made of cemented carbide. One gauge head pin 128 is screwed to the second mounting member 122, and is positioned at a position corresponding to the detection end of the first displacement sensor 123 and abuts against the first displacement sensor 123. The other probe pin 128 is screwed to the detection arm 124, and is positioned at a position corresponding to the detection end of the second displacement sensor 125 and abuts against the second displacement sensor 125. By providing the probe pin 128, the second attachment 122 can be brought into contact with the first displacement sensor 123 via the probe pin 128, and the detection arm 124 can be brought into contact with the second displacement sensor 125 via the probe pin 128. By using the stylus pin 128 harder than the second mounting member 122 and the detection arm 124, compared with a case where the first displacement sensor 123 and the second displacement sensor 125 directly abut against the second mounting member 122 and the detection arm 124 to detect, the detection accuracy can be prevented from being affected by the occurrence of pits due to the abrasion of the second mounting member 122 and the detection arm 124. In addition, since the probe pin 128 is detachably connected to the second attachment 122 and the detection arm 124, when the probe pin 128 affects the detection result due to abrasion, the probe pin 128 can be replaced, and the detection accuracy of the runout detection can be improved.

As shown in fig. 7 to 9, the first elastic member 127 is a spring, and one first elastic member 127 is disposed between the first mounting member 121 and the second mounting member 122, and is sleeved outside the first displacement sensor 123 and the probe pin 128 corresponding thereto, so as to apply a force in a direction of pushing the second mounting member 122 away from the first displacement sensor 123. The other first elastic member 127 is provided between the second mounting portion 122b (second mounting member 122) and the detection arm 124, and is fitted over the second displacement sensor 125 and the corresponding stylus pin 128, and biases the detection arm 124 away from the second displacement sensor 125. By providing such a first elastic member 127, the impact force received by the first displacement sensor 123 and the second displacement sensor 125 can be reduced, and the service lives of the first displacement sensor 123 and the second displacement sensor 125 can be prolonged. In addition, by sleeving the spring on the first displacement sensor 123, the second displacement sensor 125 and the corresponding measuring head pin 128, the spring can be positioned by the first displacement sensor 123, the second displacement sensor 125 and the measuring head pin 128, and deflection of the spring in the deformation process is prevented from affecting the measurement result. This can improve the measurement accuracy of the hub runout measuring device 100.

As shown in fig. 7-9, the detection mechanism 120 further includes a limiting member 129, and the limiting member 129 is a limiting bolt. Two limiting members 129 are provided, and one limiting member 129 is disposed on the first mounting member 121 and is in threaded connection with the first mounting member 121. When the second mount 122 slides to a predetermined position, the end of the stopper 129 abuts against the second mount 122. Another stop 129 is provided on the second mount 122 in threaded engagement with the second mount 122. When the detection arm 124 rotates to a predetermined position, the end of the stopper 129 abuts against the detection arm 124. Thus, by providing the stopper 129 on the first mounting member 121 and the second mounting member 122, the movement and the rotation range of the second mounting member 122 and the detection arm 124 can be restricted, and the first displacement sensor 123 and the second displacement sensor 125 can be prevented from being damaged due to the excessive movement and rotation range of the second mounting member 122 and the detection arm 124. Thus, the safety and stability of the hub runout measuring device 100 can be improved.

As shown in fig. 7 to 9, the detecting arm 124 is hinged to the second mounting member 122 through a structure such as a rotation shaft and a bearing, so that friction force of the detecting arm 124 during rotation is reduced, and detection accuracy is improved. The detection arm 124 is also provided with a dust cap 124a at a hinge position with the second mount 122. Because the wheel hub detects workshop environment abominable, consequently can protect parts such as pivot, the bearing of detecting arm 124 in articulated position with second installed part 122 through shield 124a, avoid entering debris such as dust and influence detection precision.

Here, the rotation shaft, the bearing (housing accommodating the bearing), and the like constitute the hinge mechanism, and the length of the third slide rail 121a is larger than the dimension of the hinge mechanism in the hub axial direction, that is, the dimension of the detection mechanism in the hub axial direction is determined by the slide mechanism constituted by the third slide rail 121a as a whole, not by the hinge mechanism described above, and if the hinge mechanism is changed to the up-down slide structure in accordance with the dimension of the slide mechanism, the dimension of the detection mechanism in the hub axial direction will be increased. That is, the structure of the present embodiment is adopted to miniaturize the detection mechanism.

In the present embodiment, the third slide rail 121a is an inner slide rail, and it is needless to say that the first mounting portion 122a side, that is, the slider 122c, has an outer slide rail, and the outer slide rail or the slider 122c has a dimension in the hub axial direction (up-down direction) that is larger than the dimension of the hinge mechanism in the up-down direction, and it is understood that the dimension of the outer slide rail or the slider 122c in the hub axial direction (up-down direction) is the total span of the slide rail mechanism in the up-down direction. According to such a size, if the hinge mechanism is changed to a slide rail structure that slides up and down, the first mounting portion 122a needs to have a sufficient size in the hub radial direction (left-right direction in fig. 7) in order to secure the detection accuracy, securing the span size of the up-down slide rail. Therefore, with the present embodiment, the first attachment piece 122a can be reduced in size in the hub radial direction, that is, in the extending direction of the third slide rail 123a, and further miniaturization can be achieved.

Referring to fig. 7, in the present embodiment, the dimension of the first mounting portion 122a in the hub radial direction (left-right direction in fig. 7) is smaller than the dimension of the slider (and the first mounting portion 122 a) that is engaged with the third slide rail 121a in the hub axial direction (up-down direction), so that the third slide rail 121a has a smaller dimension in the hub radial direction (left-right direction in fig. 7), further achieving miniaturization.

Hub dynamic balance measuring device 200

Fig. 10 is a schematic side elevation view of the hub dynamic balance measuring device 200 in fig. 1, fig. 11 is a schematic perspective view of a part of the hub dynamic balance measuring device 200 in fig. 10, fig. 12 is a schematic side elevation view of the mounting structure of the second spindle mechanism 220 in fig. 10, and fig. 13 is a schematic perspective view of the mounting structure of the second spindle mechanism 220 in fig. 10. As shown in fig. 10 to 13, the hub dynamic balance measuring device 200 includes a frame 210, a second spindle mechanism 220, a first support bar 230, and a force sensor 240. The second spindle mechanism 220 has a second spindle 221 vertically arranged, and after the hub is placed on the second spindle 221, the second spindle 221 can be fastened and connected with the hub by expanding the expansion claw, etc. The second spindle 221 may drive the hub to rotate around the axle center of the hub under the driving of the motor. The first support bar 230 is a shaft-like spring steel, which may be made of 65Mn, for example. The first support rod 230 is horizontally disposed and connected to the frame 210 and the second spindle mechanism 220, and is configured to support the second spindle mechanism 220, support the second spindle mechanism 220 in a cantilever manner, and flexibly connect the second spindle mechanism 220 with the frame 210, where when the second spindle mechanism 220 rotates with the driving hub, the second spindle mechanism 220 may shake with the hub when the hub has a problem of center of gravity offset. The force sensor 240 is fixed to the frame 210, and a detection end of the force sensor 240 is connected to the second spindle unit 220 to detect a centrifugal force when the second spindle unit 220 is rocked. The rotating shaft generates reciprocating displacement change with certain amplitude and the same frequency as the rotating speed, and can be simplified into single-degree-of-freedom forced vibration. The unbalance amount of the rotor can be obtained by accurately measuring the centrifugal force through the vibration (force) measuring sensor. Thus, the detection of the dynamic balance of the hub can be achieved by detecting the centrifugal force. The positions and the number of the balance weights added on the hub are determined so that the center of gravity of the hub is positioned at the axle center of the hub.

In addition, by vertically disposing the second main shaft 221, the hub can be maintained in a horizontal state when the hub is mounted on the second main shaft 221. Therefore, when the hub is conveyed on the blanking device 500 between two adjacent stations of the hub dynamic balance measuring device 200, the hub can be conveyed in a horizontal state, and the influence on conveying safety due to hub rolling when the hub is vertically conveyed can be avoided. Meanwhile, by vertically disposing the second main shaft 221, the hub can be easily placed on the second main shaft 221.

After the hub is mounted on the second main shaft 221, the hub can be automatically horizontally positioned under the action of self weight, thereby improving the convenience of mounting the hub. Meanwhile, the second main shaft 221 can conveniently center the hub in a mode of expanding by the expansion claw, and the like, so that the convenience of installing the hub is further improved. In addition, since the second main shaft 221 is vertically disposed, the hub is horizontally installed on the second main shaft 221, and thus, the center of the hub coincides with the center of the second main shaft 221 regardless of the variation of the size and specification of the hub, so that the center is unique, and thus, the calculation of dynamic balance can be facilitated.

Meanwhile, since the second main shaft 221 is vertically disposed, the hub is rotated in a horizontal plane after being mounted on the second main shaft 221. If the first support bar 230 supports the second spindle unit 220 in a vertical manner, the hub moves the second spindle unit 220 and the hub in a circular motion (more precisely, a conical motion with the apex downward) due to the center of gravity shift when rotating with the second spindle 221, thereby making it difficult to detect the dynamic balance. In the present application, the first support bar 230 is horizontally arranged, and the movement direction of the second spindle mechanism 220 can be limited by the first support bar 230 in the axial direction, so that the movement of the second spindle mechanism 220 and the hub during dynamic balance detection can be changed into fan-shaped swing, or the movement direction is substantially or approximately translated left and right, thereby facilitating the detection of dynamic balance data.

In the present application, the detection direction of the detection end of the force sensor 240 is perpendicular to the axial direction of the first support rod 230 and the second spindle 221, so that the detection direction of the detection end of the force sensor 240 can be the same as the shaking direction of the second spindle mechanism 220. This can further improve the detection accuracy of the hub dynamic balance measuring device 200.

As shown in fig. 12 and 13, four first support rods 230 are horizontally arranged, the four first support rods 230 are arranged in a square shape, and two upper and lower support rods are respectively arranged at two sides of the second spindle mechanism 220. Thus, the second spindle mechanism 220 can be supported at a plurality of positions on both sides of the second spindle mechanism 220, and the restriction of the second spindle mechanism 220 in the first support rod axial direction can be improved. Therefore, the fan-shaped swing of the spindle mechanism during dynamic balance detection of the hub can be more close to left-right translation, so that the detection precision of dynamic balance can be improved, and the flexible connection between the second spindle mechanism 220 and the frame 210 is more stable.

As shown in fig. 12 and 13, the force sensor 240 is provided in two upper and lower positions near the two first support rods 230, respectively. Thus, when the second spindle unit 220 is swung with the hub, the difference between the force received by the end of the force sensor 240 and the swinging force received by the first support rod 230 can be reduced. Thus, the detection accuracy of the hub dynamic balance measuring device 200 can be improved.

As shown in fig. 12 and 13, the two first support rods 230 corresponding to each other are disposed at positions apart from each other, so that the two force sensors 240 corresponding to the two first support rods can be separated from each other, and the influence of the up-down twisting motion generated synchronously when the second spindle mechanism 220 swings left and right on the detection degree can be reduced.

As shown in fig. 13, the force sensor 240 is fixed on a surface of the frame 210 facing the second spindle mechanism 220, and a detection direction of a detection end of the force sensor 240 is perpendicular to an axial direction of the first support rod 230 and the second spindle 221, that is, the same as a shaking direction of the second spindle mechanism 220 along with the hub when the hub is rotated. The second spindle mechanism 220 is further fixedly provided with a connecting piece 222, the connecting piece 222 extends to a position on one side of the detection end of the sensor 240 towards the frame 210, and is fixedly connected with the detection end through a screw and a nut, so that the detecting end of the sensor 240 can be pushed and pulled upwards in the axial direction of the screw when the connecting piece 222 shakes along with the second spindle mechanism 220. A plurality of nuts are provided on the screw so that the connection piece 222 is held fixed with the detection end of the sensor 240, thereby improving the detection accuracy.

As shown in fig. 12 and 13, the hub dynamic balance measurement device 200 further includes a second support rod 250, where the second support rod 250 is a spring steel member, and the second support rod 250 extends in a vertical direction and connects the frame 210 and the second spindle mechanism 220. Specifically, the second support rod 250 is disposed at a position far away from the first support rod 230, the upper end and the middle position of the second support rod 250 are fixedly connected with the second spindle mechanism 220, and the lower end of the second support rod 250 is abutted with the frame 210 or directly abutted with the ground of the factory building. By arranging the second support rod 250, the second support rod 250 supports the second spindle mechanism 220 in the vertical direction, so that the deformation of the first support rod 230 in the axial direction of the second spindle 221 can be reduced when the first support rod 230 shakes along with the second spindle mechanism 220, and the fan-shaped swing of the second spindle mechanism 220 during dynamic balance detection of the hub can be more approximate to left-right translation. Thus, the direction in which the second spindle mechanism 220 is swung can be made closer to the detection direction of the detection end of the force sensor 240, so that the detection accuracy of the force sensor 240 can be improved, and the detection accuracy of the hub dynamic balance measuring apparatus 200 can be improved. Through making the second bracing piece 250 be spring steel, can make the second bracing piece 250 carry out deformation in the horizontal direction to can reduce the influence of second bracing piece 250 to rocking amplitude when second spindle unit 220 rocks along with the wheel hub, thereby can improve detection accuracy.

Further, the balls 251 are disposed at the bottom end of the second support rod 250, so that the friction force between the second support rod 250 and the frame can be reduced, and further, the influence of the second support rod 250 on the shaking amplitude can be reduced when the second spindle mechanism 220 shakes along with the hub, so that the detection precision can be improved.

As shown in fig. 12 and 13, the hub dynamic balance measuring device 200 further includes a support plate 280 having a rectangular plate-like member. The two support plates 280 are respectively located at two sides of the second spindle mechanism 220 and are detachably and fixedly connected with the second spindle mechanism 220 and the frame 210. Therefore, when the hub dynamic balance measuring device 200 is transported and mounted, the support plate 280 is provided between the second spindle mechanism 220 and the frame 210, so that the stability of the second spindle mechanism 220 can be improved, and the damage to the force sensor 240 due to the excessive shaking amplitude of the second spindle mechanism 220 can be avoided. In detecting the dynamic balance of the hub using the hub dynamic balance measuring device 200, the support plate 280 may be removed to detect the dynamic balance of the hub.

As shown in fig. 10 and 11, the hub dynamic balance measuring device 200 further includes a second conveying mechanism 260, and the second conveying mechanism 260 has the same structure as the first conveying mechanism 140 described above, and includes a second conveying belt 261 and a third driving cylinder 262. The second conveying belts 261 are arranged at two sides of the second main shaft 221 in parallel, and are used for driving the hubs to move in the horizontal direction so that the hubs move above the second main shaft 221. The third driving cylinder 262 is connected to the second conveyor 261 and drives the second conveyor 261 to move up and down. Thereby, the hub can be conveyed to the upper side of the second main shaft 221 by the second conveying belt 261, and the second conveying belt 261 can be driven to descend by the third driving cylinder 262, so that the hub can be lowered onto the second main shaft 221, so that the second main shaft 221 drives the hub to rotate.

As shown in fig. 10, the hub dynamic balance measuring apparatus 200 further includes a second centering mechanism 270, and the second centering mechanism 270 has the same structure as the first centering mechanism 150 described above, and includes a second centering roller 271 and a fourth driving cylinder (not shown). The second centering rollers 271 are vertically disposed above the second main shaft 221, and are disposed around the second main shaft 221 in a square shape. The fourth driving cylinder is connected to the plurality of second centering rollers 271 by a link transmission, and drives the four second centering rollers 271 to approach toward the axial center of the second main shaft 221 in a vertical state. Therefore, the second centering roller 271 can be driven by the fourth driving cylinder to approach the axis of the second main shaft 221, so that the axis of the hub can be pushed to coincide with the axis of the second main shaft 221, and the hub can be conveniently mounted on the second main shaft 221 after the conveying roller is driven by the fourth driving cylinder to descend. Meanwhile, when the hub rotates with the second main shaft 221, the hub can be rotated with the axis of the hub as the center, so that the detection accuracy of the dynamic balance detection can be improved.

Blanking device 500

Fig. 14 is a schematic perspective view of the blanking apparatus 500 in fig. 1. As shown in fig. 14, the blanking device 500 in the present application includes a second conveying roller table 510, a third centering mechanism 520, a push plate (not shown) and a marker 530. The second conveying roller way 510 conveys the wheel hub through motor driving roller rotation, a pause station is arranged in the middle of the second conveying roller way 510, and the wheel hub is paused after being conveyed to the pause station. The third centering mechanism 520 has the same structure as the first centering mechanism 150 described above, and includes a third centering roller 521 and a sixth driving cylinder (not shown). The third centering rollers 521 are vertically arranged at the upper position of the pause station and are arranged around the pause station in square distribution. The sixth driving cylinder is connected with a plurality of third centering rollers 521 through a link transmission, and drives the four third centering rollers 521 to approach toward the center of the pause station in a vertical state. The marker 530 is disposed above the second roller table 510 and located at a position corresponding to the pause station, and can mark the hub located at the pause station. The push plate is arranged at one side of the pause station and can move along the direction perpendicular to the conveying direction of the second conveying roller way 510, and the hub of the pause station is pushed to the blanking roller way.

Buffer stop 300

Fig. 15 is a rear front projection structure of the buffer stop 300 of fig. 1, fig. 16 is a front projection structure of the buffer stop 300 of fig. 1, fig. 17 is a side front projection structure of the buffer stop 300 of fig. 1, fig. 18 is a perspective structure of the buffer stop 300 of fig. 1, and fig. 19 is a partial cross-sectional view of the buffer stop 300A-A of fig. 15. As shown in fig. 15 to 19, the buffer stop device 300 of the present application includes a first stop plate 310, a second stop plate 320, and a proximity switch 330 (sensor). The first blocking plate 310 is a rectangular plate-shaped member, and can move between a blocking position and a unblocking position, and in the blocking position, the first blocking plate 310 is vertically disposed on the second conveying roller table 510 and is located at an intermediate position between two adjacent conveying rollers, and the first blocking plate is perpendicular to the conveying direction of the second conveying roller table 510, so that further movement of the hub on the second conveying roller table 510 can be blocked. The second blocking plate 320 is a rectangular plate-shaped member, and is disposed on the first blocking plate 310 and located at the feeding side of the conveying roller way, the lower edge of the second blocking plate 320 is hinged to the first blocking plate 310, and the upper edge of the second blocking plate 320 is flush with the upper edge of the first blocking plate 310. The proximity switch 330 is provided on the first blocking plate 310, and when the movement of the second blocking plate 320 to a predetermined position is detected, the buffer blocking device 300 controls the second roller table 510 to stop and moves the first blocking plate 310 to the unblocking position. Specifically, the proximity switch 330 is in an OFF state in a state in which the second blocking plate 320 is separated from the first blocking plate 310, and the proximity switch 330 is in an ON state when the second blocking plate 320 is rotated to a predetermined position, for example, in abutment with the first blocking plate 310, by the pushing of the hub.

From the above, when the second rollgang 510 pauses the station S (the predetermined position) of the wheel hub conveying channel, and the wheel hub is required to be stopped and positioned, the first blocking plate 310 is arranged between two adjacent conveying rollers of the second rollgang 510, so that the first blocking plate 310 is perpendicular to the conveying direction of the corresponding second rollgang 510, and therefore, when the wheel hub is conveyed to the pause station S where the first blocking plate 310 is positioned by the second rollgang 510, the first blocking plate 310 blocks the wheel hub, and the wheel hub stops at the pause station S under the blocking of the first blocking plate 310, so that the wheel hub cannot be accurately positioned due to continuous forward movement due to inertia when the second rollgang 510 stops due to heavy weight and heavy inertia, and the positioning accuracy of the wheel hub can be improved, and the reliable and accurate positioning of the wheel hub can be realized. By arranging the second blocking plate 320 and the proximity switch 330 in a hinged manner on the first blocking plate 310, when the first blocking plate 310 blocks and positions the hub, the proximity switch 330 detects that the second blocking plate 320 rotates, that is, determines that the hub reaches the pause station S. At this time, by controlling the second conveying roller way 510 to stop, it is possible to avoid scratches caused to the surface of the hub by the continuous rotation of the conveying roller of the second conveying roller way 510 when the hub stops at the pause station S under the blocking of the first blocking plate 310.

In addition, if the proximity switch 330 directly detects whether the hub reaches the pause station S, since the detection range of the proximity switch 330 is limited, when the size specification of the hub is changed, the proximity switch 330 cannot detect the hub, and thus there is a possibility that missed detection occurs. In the application, the first blocking plate 310 is arranged at the middle position between the two conveying rollers, and the second blocking plate 320 is arranged on the side of the first blocking plate 310 facing the incoming material, so that the hub can be abutted against the second blocking plate 320 when reaching the pause station S, the second blocking plate 320 is pushed to rotate, and the proximity switch 330 can determine whether the hub reaches the pause station S by detecting the rotation of the second blocking plate 320. Therefore, the adaptation range of the hub size specification can be increased, and the possibility of missed detection is avoided.

In addition, when the proximity switch 330 is triggered, that is, when a predetermined position of the hub is detected, the control mechanism causes the marker 530 to operate, and the marking on the hub can be performed according to the detection result of the runout or dynamic balancing process. In addition, according to the detection result of the jumping or dynamic balancing process, when the hub is considered to be a defective product, the marking is not performed, the hub is moved in a direction perpendicular to the conveying direction of the second conveying roller way 510 by the push plate and further moved to the discharging roller way to be conveyed to the scrap station, and when the hub is considered to be a defective product, the hub is conveyed to the next process (specific structure is described below) by the second conveying roller way 510 after the marking is completed.

As shown in fig. 16 and 19, a square groove for mounting the proximity switch 330 is provided in the middle of the upper edge of the first blocking plate 310, and the proximity switch 330 is mounted in the groove of the first blocking plate 310. Specifically, the detection end of the proximity switch is located inside the groove, i.e. hidden in a surface of the first blocking plate 310 facing the second blocking plate 320. Therefore, when the second blocking plate 320 rotates towards the first blocking plate 310 to be abutted against the first blocking plate under the pushing of the hub, the second blocking plate 320 is prevented from directly contacting the proximity switch 330, and the second blocking plate 320 is prevented from damaging the proximity switch 330.

As shown in fig. 15, 17 and 18, the second blocking plate 320 is hinged to the middle position of the first blocking plate 310 at the lower side edge position, and the proximity switch 330 is disposed at the middle position near the upper side edge of the first blocking plate 310. Thereby, the size of the second blocking plate 320 can be reduced, making the structure simpler. By disposing the proximity switch 330 at a position away from the hinge, the distance between the second blocking plate 320 and the proximity switch 330 can be increased when the hub does not reach the predetermined position, thereby avoiding the false triggering sensing of the proximity switch 330. Thereby, the detection accuracy of the buffer stop device 300 can be improved.

As shown in fig. 17, the buffer stop device 300 further includes a positioning member 340, wherein the positioning member 340 is disposed on the second stop plate 320, and when the second stop plate 320 rotates to a predetermined position, the positioning member 340 abuts against the first stop plate 310. Specifically, the first blocking plate 310 is provided with a positioning hole 311, and the positioning hole 311 is disposed at a position corresponding to the positioning piece 340. The positioning piece 340 includes a main body portion 341 and an abutting portion 342, where the main body portion 341 is columnar and is inserted into the positioning hole 311, the abutting portion 342 is disposed on the main body portion 341 and is away from one end of the second blocking plate 320, and the size of the abutting portion 342 is larger than that of the positioning hole 311, so that when the second blocking plate 320 rotates to make the upper side edge of the second blocking plate 320 far away from the proximity switch 330 of the first blocking plate 310, the abutting portion 342 can be abutted with the positioning hole 311 at a proper position. Therefore, the positioning piece 340 can position the second blocking plate 320, so that the second blocking plate 320 is prevented from rotating too much, and the wheel hub cannot abut against the second blocking plate 320 when reaching the preset position along with the conveying roller way. Therefore, the success rate of in-place detection of the hub can be improved.

As shown in fig. 16, the positioning hole 311 is a long hole, and the extending direction of the positioning hole 311 is perpendicular to the hinge axis direction between the second blocking plate 320 and the first blocking plate 310. Since the positioning member rotates with the second blocking plate 320, the position where the main body portion 341 intersects the first blocking plate 310 moves on the first blocking plate 310 in a direction perpendicular to the axis of the hinge between the second blocking plate 320 and the first blocking plate 310. Therefore, in the present application, the positioning hole 311 is provided as a long hole extending in the direction perpendicular to the axis of the hinge between the second blocking plate 320 and the first blocking plate 310, so that the positioning member is prevented from being locked in the positioning hole 311, and the rotation of the second blocking plate 320 is prevented from being affected.

As shown in fig. 17, the buffer stop 300 further includes a second elastic member 350, and the second elastic member 350 pushes the second blocking plate 320 away from the proximity switch 330. Therefore, when the hub does not reach the preset position, the second elastic member 350 pushes the second blocking plate 320 away from the proximity switch 330, so as to avoid the situation that the proximity switch 330 is triggered by mistake. Thereby, the detection accuracy of the buffer stop device 300 can be improved.

As shown in fig. 17, the second elastic member 350 is a spring, and is sleeved on the main body 341 and located between the first blocking plate 310 and the second blocking plate 320. Therefore, the spring can be prevented from deflecting during deformation, so that the stability of the spring can be improved, and the success rate of in-place detection of the hub is improved. Meanwhile, the spring is sleeved on the main body 341 to buffer and reset the second blocking plate 320, so that a mounting structure of the spring can be avoided, the number of parts of the buffer blocking device 300 can be reduced, and the structure is simpler.

As shown in fig. 16, two positioning members 340 are provided, and the proximity switch 330 is located at a position on the second blocking plate 320 away from the hinge side, and at a position intermediate the two positioning members 340. Therefore, by arranging the proximity switch 330 at the middle position of the two positioning members 340, the stability of the proximity switch 330 in sensing the second blocking plate 320 can be improved, and the success rate of in-place detection of the hub can be improved.

As shown in fig. 15 and 17, the buffer stop 300 further includes a buffer pad 360, and the buffer pad 360 is disposed on the second blocking plate 320 on a surface of a side remote from the first blocking plate 310. The cushion pad 360 is made of a softer material such as polyurethane, rubber, or silicone. Therefore, the second blocking plate 320 can be abutted with the hub through the buffer pad 360, so that the buffer pad 360 can provide buffer to avoid damage to the hub and the second blocking plate 320.

As shown in fig. 15 to 18, the buffer stop device 300 further includes a fifth driving cylinder 370, and a driving rod of the fifth driving cylinder 370 is connected to the first blocking plate 310 to drive the first blocking plate 310 to move up and down. Thus, the first blocking plate 310 can be driven to move up and down by the fifth driving cylinder 370, so that the first blocking plate 310 is positioned on the second conveying roller table 510 at a position corresponding to the hub. When the hub reaches the pause station S, the hub is abutted against the second blocking plate 320 on the first blocking plate 310, so that the second blocking plate 320 can be pushed to rotate while the positioning blocking of the hub is realized, the proximity switch 330 can determine that the hub reaches the pause station S after detecting the rotation of the second blocking plate 320, and the corresponding second conveying roller table 510 is controlled to stop, so that the hub is prevented from being scratched. Thereafter, the first blocking plate 310 is driven to move up and down by the fifth driving cylinder 370, so that the first blocking plate 310 is separated from the second roller conveyor 510 at a position corresponding to the hub. Then, based on the proximity switch 330 detecting that the hub reaches the pause station S, the control mechanism may control the operation of the marker 530 to mark the hub according to the detection result of the runout or dynamic balancing process. In addition, according to the detection result of the jumping or dynamic balancing process, when the hub is considered as a defective product, marking is not performed, and the hub is moved in a direction perpendicular to the conveying direction of the second conveying roller way 510 by the push plate, and then moved to the discharging roller way to be conveyed to the scrap station. When the hub is considered to be a qualified product, after the marking is completed and the station of the next process has no hub, the hub is transported to the next process by the second rollgang 510.

Note that the above is only a preferred embodiment of the present application and the technical principle applied. It will be understood by those skilled in the art that the present application is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the application. Therefore, while the application has been described in connection with the above embodiments, the application is not limited to the above embodiments, but may include many other equivalent embodiments without departing from the spirit of the application, which fall within the scope of the application.

Claims

1. A wheel hub dynamic balance measuring device, characterized by comprising:

A frame;

the main shaft mechanism is provided with a main shaft which is vertically arranged, and is used for installing the wheel hub and driving the wheel hub to rotate by taking the axis in the vertical direction as the center;

The first support rods are shaft-shaped spring steel parts, are horizontally arranged and are connected with the frame and the spindle mechanism to support the spindle mechanism in a cantilever manner, and are arranged on two sides of the spindle mechanism in a rectangular average manner;

The upper part of the second support rod is fixedly connected with the spindle mechanism, and the lower end of the second support rod is in butt joint with the frame;

The sensor is fixed on the frame and is arranged at a position close to the first supporting rod, the detection end of the sensor is connected with the main shaft mechanism, and the detection direction of the detection end is perpendicular to the axial direction of the first supporting rod and the main shaft.

2. The hub dynamic balance measuring device according to claim 1, wherein the first support rod is provided in plurality horizontally, and the sensor is provided in plurality.

3. The hub dynamic balance measurement device of claim 1, further comprising:

And two ends of the supporting plate are detachably and fixedly connected with the frame and the main shaft mechanism respectively.

4. The hub dynamic balance measurement device of claim 1, further comprising a conveying mechanism, the conveying mechanism comprising:

The two conveying belts are arranged at the two sides of the main shaft in parallel and used for driving the wheel hubs to move along the horizontal direction so that the wheel hubs move above the main shaft;

The first driving cylinder is connected with the conveying belt and drives the conveying belt to move up and down.

5. The hub dynamic balance measurement device of claim 4, further comprising a centering mechanism, the centering mechanism comprising:

the centering rollers are arranged in a plurality, are vertically arranged above the main shaft and are arranged around the main shaft;

The second driving cylinder is in transmission connection with the centering rollers and drives the centering rollers to approach the axis of the main shaft.

6. A hub measurement apparatus, comprising:

a hub dynamic balance measurement device, which is the hub dynamic balance measurement device according to any one of claims 1 to 5;

the wheel hub runout measuring device is used for measuring the runout parameters when the wheel hub rotates.