阅读说明：本技术 一种具有悬臂梁与简支梁共存的动平衡机轴系 (Dynamic balancing machine shafting with coexisting cantilever beam and simply supported beam ) 是由 王成贵 吴启 刘万峰 张云奎 于 2020-05-21 设计创作，主要内容包括：一种具有悬臂梁与简支梁共存的动平衡机轴系,涉及平衡机技术领域。为解决现有的车轮动平衡机轴系受到外悬臂梁结构的限制时,平面分离性能不佳,长期使用时,压电传感器的性能会发生变化,由于力的关联效应,导致分离精度降低,设备的稳定性较差,并且现有的装置通用性较差的问题。底座的上表面均匀的设有一号摆架和二号摆架,且一号摆架和二号摆架同轴设置,传动组件的一端依次穿过一号摆架和二号摆架,与机械制动单元连接,二号摆架侧面的一端设有电磁制动单元,二号摆架另一侧面一端通过螺栓与光电板支架连接,光电板支架上设有光电板。本发明适用于针对车轮动平衡的检测。(A dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexists relates to the technical field of balancing machines. The device aims to solve the problems that when an existing wheel dynamic balancing machine shafting is limited by an outer cantilever beam structure, the plane separation performance is poor, when the device is used for a long time, the performance of a piezoelectric sensor can be changed, the separation precision is reduced due to the force correlation effect, the stability of the device is poor, and the universality of the existing device is poor. The upper surface of base is even is equipped with a rocker and No. two rockers, and a rocker and No. two coaxial settings of rocker, and No. one end of drive assembly passes a rocker and No. two rockers in proper order, is connected with the mechanical braking unit, and the one end of No. two rocker sides is equipped with the electromagnetic braking unit, and No. two rocker another side one end is passed through the bolt and is connected with the photoelectricity board leg, is equipped with the photoelectricity board on the photoelectricity board support. The invention is suitable for detecting the dynamic balance of the wheel.)

1. The utility model provides a dynamic balancing machine shafting with cantilever beam and coexistence of simple beam which characterized in that: the device comprises a transmission assembly (1), a first swing frame (2), a second swing frame (3), a mechanical braking unit, an electromagnetic braking unit, a photoelectric plate support (4), a photoelectric plate (5) and a base (13);

the upper surface of base (13) is even be equipped with rocker (2) and No. two rockers (3), and rocker (2) and No. two coaxial settings of rocker (3), the one end of drive assembly (1) passes rocker (2) and No. two rockers (3) in proper order, be connected with mechanical braking unit, the one end of No. two rockers (3) side is equipped with the electromagnetic braking unit, No. two rockers (3) another side one end is passed through the bolt and is connected with photoelectricity board support (4), be equipped with photoelectricity board (5) on photoelectricity board support (4).

2. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simply supported beam as claimed in claim 1, wherein: the transmission assembly (1) comprises a flat shaft (1-1), a matcher (1-2) and a transmission shaft (1-3); one end of the transmission shaft (1-3) is fixedly connected with one end of the flat shaft (1-1), the other end of the flat shaft (1-1) is connected with the mechanical brake unit, and the other end of the transmission shaft (1-3) is provided with a matcher (1-2).

3. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simply supported beam as claimed in claim 1, wherein: the mechanical brake unit comprises a grating disc (6), a brake disc (7), a brake force adjusting nut (14), a backstop washer (15) and a wave spring (16);

the other end of a flat shaft (1-1) of the transmission component (1) sequentially penetrates through the brake disc (7), the wave spring (16), the retaining washer (15) and the braking force adjusting nut (14) and is fixedly connected with the center of the grating disc (6).

4. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simple beam as claimed in claim 3, wherein: the brake disc (7) comprises a first brake pressing sheet (17), a first friction sheet (18), a brake sheet (19), a second friction sheet (20) and a second brake pressing sheet (21);

a first brake pressing sheet (17), a first friction sheet (18), a brake sheet (19), a second friction sheet (20) and a second brake pressing sheet (21) are sequentially arranged on the flat shaft (1-1) from left to right and are coaxially arranged, and a plurality of through holes are formed in the end face of the brake sheet (19) in the circumferential direction.

5. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simply supported beam as claimed in claim 1, wherein: the electromagnetic braking unit comprises an electromagnet bracket (8), a braking bolt (9), a spring (10), a braking pin (11) and an electromagnet (12);

electromagnet support (8) is L type support, the minor face terminal surface of electromagnet support (8) is equipped with circular through-hole, the one end of No. two rocker (3) side is equipped with the through-hole, the path end of brake bolt (9) passes the through-hole on electromagnet support (8) and the through-hole of the one end of No. two rocker (3) side in proper order, with nut fastening connection, the big footpath end of brake bolt (9) is equipped with the cavity along the axis direction, spring (10) are passed to the one end of brake pin (11), insert in the cavity of brake bolt (9), the other end of brake pin (11) and the electromagnet shaft contact of electro-magnet (12), and the lower surface of electro-magnet (12) and the long limit upper surface fixed connection of electromagnet support (8).

6. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simply supported beam as claimed in claim 1, wherein: the other end lower part of No. two rocker (3) be equipped with the through-hole, the other end of No. two rocker (3) side is equipped with the cavity, inside second steel ball (22), piezoelectric sensor (23) and first steel ball (24) of being equipped with from left to right in proper order of cavity, and coaxial setting, the through-hole of the other end lower part of No. two rocker (3) is passed to the one end of concave end holding screw (25), with the sphere contact of first steel ball (24).

7. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simply supported beam as claimed in claim 1, wherein: the first swing frame (2) and the second swing frame (3) are identical in mechanical structure.

8. The dynamic balancing machine shafting with the coexistence of the cantilever beam and the simple beam as claimed in claim 7, wherein: the distance between the first swing frame (2) and the end face of the matcher (1-2) is 110-230 mm.

Technical Field

The invention relates to the technical field of balancing machines, in particular to a dynamic balancing machine shaft system with a cantilever beam and a simply supported beam which coexist.

Background

The existing dynamic balancing machine shaft system of the wheel belongs to a cantilever beam structure, and the cantilever beam structure is a vibration system structure with two correction planes of a test workpiece positioned at the outer sides of two supporting points. This is usually achieved in two ways, one in which the piezoelectric transducer is of a t-shaped configuration and the other in which the piezoelectric transducer is of a straight configuration, with both support points of the shaft system being on one side of the test workpiece.

To sum up, when the existing dynamic wheel balancer shafting receives the restriction of outer cantilever beam structure, the plane separation performance is not good, and when long-term use, piezoelectric sensor's performance can change, because the associated effect of power leads to the separation precision to reduce, and the stability of equipment is relatively poor to the relatively poor problem of current device commonality.

Disclosure of Invention

The invention provides a dynamic balancing machine shaft system with a cantilever beam and a simply supported beam, aiming at solving the problems that when the conventional wheel dynamic balancing machine shaft system is limited by an outer cantilever beam structure, the plane separation performance is poor, the performance of a piezoelectric sensor is changed during long-term use, the separation precision is reduced due to the force correlation effect, the equipment stability is poor, and the universality of the conventional device is poor.

The invention relates to a dynamic balancing machine shafting with a cantilever beam and a simply supported beam, which comprises a transmission component, a first swing frame, a second swing frame, a mechanical braking unit, an electromagnetic braking unit, a photoelectric plate support, a photoelectric plate and a base, wherein the transmission component is arranged on the first swing frame;

the upper surface of the base is uniformly provided with a first swing frame and a second swing frame which are coaxially arranged, one end of the transmission assembly sequentially penetrates through the first swing frame and the second swing frame and is connected with the mechanical braking unit, one end of the side surface of the second swing frame is provided with the electromagnetic braking unit, one end of the other side surface of the second swing frame is connected with the photoelectric plate support through a bolt, and the photoelectric plate support is provided with a photoelectric plate;

furthermore, the transmission assembly comprises a flat shaft, a matcher and a transmission shaft; one end of the transmission shaft is fixedly connected with one end of the flat shaft, the other end of the flat shaft is connected with the mechanical brake unit, and the other end of the transmission shaft is provided with a matcher;

furthermore, the mechanical brake unit comprises a grating disc, a brake force adjusting nut, a backstop washer and a wave spring;

the other end of the flat shaft of the transmission assembly sequentially penetrates through the brake disc, the wave spring, the retaining washer and the braking force adjusting nut and is fixedly connected with the center of the grating disc;

furthermore, the brake disc comprises a first brake pressing sheet, a first friction sheet, a brake sheet, a second friction sheet and a second brake pressing sheet; a first brake pressing sheet, a first friction sheet, a brake pad, a second friction sheet and a second brake pressing sheet are sequentially arranged on the flat shaft from left to right and are coaxially arranged, and a plurality of through holes are formed in the end face of the brake pad along the circumferential direction;

furthermore, the electromagnetic braking unit comprises an electromagnet bracket, a braking bolt, a spring, a braking pin and an electromagnet;

the electromagnet support is an L-shaped support, a circular through hole is formed in the end face of the short side of the electromagnet support, a through hole is formed in one end of one side face of the second swing frame, the small-diameter end of the brake bolt sequentially penetrates through the through hole in the electromagnet support and the through hole in one end of the side face of the second swing frame and is fixedly connected with the nut, a cavity is formed in the large-diameter end of the brake bolt along the axis direction, one end of the brake pin penetrates through the spring and is inserted into the cavity of the brake bolt, the other end of the brake pin is in contact with an electromagnet shaft of the electromagnet, and the lower surface of the electromagnet is;

furthermore, a through hole is formed in the lower portion of the other end of the second swing frame, a cavity is formed in the other end of the side face of the second swing frame, a second steel ball, a piezoelectric sensor and a first steel ball are sequentially arranged in the cavity from left to right and are coaxially arranged, and one end of a concave end set screw penetrates through the through hole in the lower portion of the other end of the second swing frame and is in contact with the spherical surface of the first steel ball;

furthermore, the mechanical structures of the first swing frame and the second swing frame are the same;

furthermore, the distance between the first swing frame and the end face of the matcher is 110-230 mm;

further, when the wheel is used, the wheel is installed on the transmission assembly, when the width of the wheel is large, the back space (the distance from a hub installation surface to the inner edge of a rim) of the wheel exceeds a first swing frame and enters a measurement state in which a simply supported beam and a cantilever beam coexist, when the width of the wheel is small, the back space of the wheel does not exceed the first swing frame and enters the measurement state in which the cantilever beam is arranged, the wheel is rotated by a motor or manually, the angular speed of the grating disc is detected by the system through a photoelectric plate, when the angular speed reaches a certain value, the balancing machine is in a sliding sampling stage, the dynamic unbalance of the wheel causes the transmission assembly to vibrate, the first swing frame and the second swing frame are driven to vibrate, and the dynamic unbalance of the wheel can be calculated by collecting the vibration quantity through the two piezoelectric sensors. After sampling is finished, the electromagnet is electrified to push the brake pin to act, the tail end of the brake pin extends into the through hole in the end face of the brake pad to stop the brake pad from rotating, the first brake pressing sheet and the second brake pressing sheet can rotate along with the transmission assembly, the first friction sheet generates friction force between the first brake pressing sheet and the brake pad, and the second friction sheet generates friction force between the second brake pressing sheet and the brake pad to stop the transmission assembly from rotating;

when the width of the wheel is small, the inner side correction plane does not exceed the first swing frame, the vibration system still belongs to a cantilever beam structure, and the dynamic balance of the wheel is still calculated according to the original cantilever beam form. When the width of the wheel is larger, the inner side correction plane exceeds the first swing frame and is positioned between the two swing frames, the vibration system is a structure with a cantilever beam and a simply supported beam, and the calculation principle of the dynamic unbalance of the wheel is explained by combining the six-eight drawings;

the specific dynamic balance calculation method is as follows: the support rigidity of the dynamic wheel balancer is very high, close to the bearing rigidity of the rotor, and the balance working condition can be similar to the actual working condition of the wheel. The rotor has two calibration planes, so it is necessary to convert the imbalance force signal measured at the bearing plane to two calibration planes. As shown in the sixth attached figure:

F₁，F₂dynamic pressure on two bearing planes

f₁，f₂Centrifugal forces generated by unbalanced masses on the correction plane of the wheel

m₁，m₂Correcting the unbalanced masses on two planes separately for the wheel

a, b, c-the distance between the relevant positions in the figure (b being the thickness of the rotor)

r₁，r₂Radius correction of rotor plane, i.e. unbalance mass m for correction₁、m₂To the axis of rotation

Omega-angular velocity of rotation of the main shaft

Based on the structure, the requirement of the upper graph force system is satisfied according to the statics principleEquilibrium conditions (Representing moment) of force, respectively taken at the O2 and O1 fulcrums of the drawings, then:

it is rewritten as:

when the test wheel is stationary, the dimensions of a, b, c are known, let:

K₁₁＝(c-a)/c

K₁₂＝(b-a+c)/c

K₂₁＝a/c

K₂₂＝-(b-a)/c

equation (2) can be written as:

the formula (3) can solve the following problems:

in the formula (4)The centrifugal force generated for the unbalance, namely:

therefore:

the above calculations show that if the geometric parameters of the rotor and the equilibrium rotational speed are determined, the amount of unbalance on the two correction planes of the rotor and the correction mass m (g) to be applied can be calculated from the measurement signals of the piezoelectric sensors.

Compared with the prior art, the invention has the following beneficial effects:

the invention overcomes the defects of the prior art, the wheel is arranged on the transmission assembly, the wheel is rotated by a motor or manually, the angular speed of the grating disk is detected by the system through the photoelectric plate, when the angular speed reaches a certain value, the balancing machine is in a sliding sampling stage, the dynamic unbalance of the wheel causes the transmission assembly to vibrate, and the vibration quantity is collected by the two piezoelectric sensors, so that the balance state of the shafting can be accurately measured, the separation accuracy is improved, and the stability of the device is improved.

The invention overcomes the defects of the prior art, the swing frame at the front end of the shaft system can extend into the rim of the wheel to be tested, the distance between the two swing frames can be effectively utilized, the base can also strengthen the strength of the shaft system, the requirements of testing the wheels of cars, coaches and trucks can be met, the universality is improved, and the stability of the system is enhanced.

Thirdly, the invention has simple operation and convenient use.

Drawings

FIG. 1 is a schematic three-dimensional view of a dynamic balancing machine shaft system with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 2 is a front view of a dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 3 is an enlarged schematic view of A-A in a dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 4 is a three-dimensional exploded view of a dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 5 is a front view of a first swing frame in a dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 6 is a schematic diagram of the wheel stress of a dynamic balancing machine shafting with a cantilever beam and a simply supported beam coexisting according to the present invention;

FIG. 7 is a schematic diagram of a stress on a simply supported beam of a dynamic balancing machine shafting with a cantilever beam and the simply supported beam coexisting according to the present invention;

fig. 8 is a schematic diagram of the cantilever beam stress of the dynamic balancing machine shaft system with the coexistence of the cantilever beam and the simply supported beam.

Detailed Description