CN111504554B - Dynamic balancing machine shafting with cantilever beam and simply supported beam coexist - Google Patents
Dynamic balancing machine shafting with cantilever beam and simply supported beam coexist Download PDFInfo
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- CN111504554B CN111504554B CN202010438294.1A CN202010438294A CN111504554B CN 111504554 B CN111504554 B CN 111504554B CN 202010438294 A CN202010438294 A CN 202010438294A CN 111504554 B CN111504554 B CN 111504554B
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- 238000005259 measurement Methods 0.000 claims description 12
- 229910000831 Steel Inorganic materials 0.000 claims description 11
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- 238000005070 sampling Methods 0.000 claims description 9
- 238000000926 separation method Methods 0.000 abstract description 7
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- 210000001503 joint Anatomy 0.000 abstract 1
- 238000012360 testing method Methods 0.000 description 9
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/22—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables
- G01M1/225—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables for vehicle wheels
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/02—Details of balancing machines or devices
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Abstract
A dynamic balancing machine shafting with cantilever beam and simple beam coexistent relates to the technical field of balancing machines. In order to solve the problems that when the existing wheel dynamic balancing machine shafting is limited by an outer cantilever beam structure, the plane separation performance is poor, the performance of a piezoelectric sensor can change when the existing wheel dynamic balancing machine shafting is used for a long time, the separation precision is reduced due to the force correlation effect, the stability of equipment 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 rocker, and a rocker and No. two rocker coaxial settings, and transmission assembly's one end passes a rocker and No. two rocker in proper order, is connected with mechanical braking unit, and No. two rocker side's one end is equipped with electromagnetic braking unit, and No. two rocker another side one end passes through bolt and photoelectric plate leg joint, is equipped with the photoelectric plate on the photoelectric plate leg. The invention is suitable for detecting dynamic balance of the wheel.
Description
Technical Field
The invention relates to the technical field of balancing machines, in particular to a dynamic balancing machine shafting with a cantilever beam and a simple supporting beam which coexist.
Background
The existing wheel dynamic balancing machine shafting 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. The test is usually realized in two forms, one is that the piezoelectric sensor is of a T-shaped structure, and the other is that the piezoelectric sensor is of a straight structure, and two supporting points of a shaft system are arranged on one side of a test workpiece.
In summary, when the existing dynamic wheel balancer shafting is limited by the outer cantilever beam structure, the plane separation performance is poor, and when the dynamic wheel balancer shafting is used for a long time, the performance of the piezoelectric sensor can change, the separation precision is reduced due to the force correlation effect, the stability of equipment is poor, and the universality of the existing device is poor.
Disclosure of Invention
The invention provides a dynamic balancing machine shafting with cantilever beams and simple beams, which aims to solve the problems that when the existing dynamic balancing machine shafting of a wheel is limited by an outer cantilever beam structure, the plane separation performance is poor, the performance of a piezoelectric sensor can change when the dynamic balancing machine shafting is used for a long time, the separation precision is reduced due to the force correlation effect, the stability of equipment is poor, and the universality of the existing 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 assembly, a first swing frame, a second swing frame, a mechanical braking unit, an electromagnetic braking unit, a photoelectric plate bracket, a photoelectric plate and a base, wherein the cantilever beam and the simply supported beam coexist;
The upper surface of the base is uniformly provided with a first swing frame and a second swing frame, the first swing frame and the second swing frame 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 an electromagnetic braking unit, one end of the other side surface of the second swing frame is connected with the photoelectric plate bracket through a bolt, and the photoelectric plate bracket is provided with a photoelectric plate;
Further, 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 braking unit, and the other end of the transmission shaft is provided with a matcher;
Further, the mechanical braking unit comprises a grating disc, a brake disc, a braking force adjusting nut, a stopping washer and a wave spring;
the other end of the flat shaft of the transmission component sequentially passes through the brake disc, the wave spring, the stop washer and the braking force adjusting nut and is fixedly connected with the center of the grating disc;
Further, 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; the flat shaft is sequentially provided with a first brake pressing sheet, a first friction sheet, a brake sheet, a second friction sheet and a second brake pressing sheet from left to right, and is coaxially arranged, and the end face of the brake sheet is provided with a plurality of through holes along the circumferential direction;
Further, the electromagnetic braking unit comprises an electromagnet bracket, a braking bolt, a spring, a braking pin and an electromagnet;
The electromagnetic bracket is an L-shaped bracket, a round through hole is formed in the end face of the short side of the electromagnetic bracket, 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 electromagnetic bracket and the through hole in one end of the side face of the second swing frame and is fixedly connected with a nut, a cavity is formed in the large-diameter end of the brake bolt along the axial direction, one end of the brake pin penetrates through a spring and is inserted into the cavity of the brake bolt, the other end of the brake pin is in contact with an electromagnetic shaft of the electromagnetic, and the lower surface of the electromagnetic is fixedly connected with the upper surface of the long side of the electromagnetic bracket;
Further, 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, the second steel ball, the piezoelectric sensor and the first steel ball 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;
Further, the first swing frame and the second swing frame have the same mechanical structure;
further, the distance between the first swing frame and the end face of the matcher is 110 mm-230 mm;
Further, when the wheel is used, the wheel is arranged on the transmission assembly, when the width of the wheel is large, the back space (the distance from the hub mounting surface to the inner edge of the rim) of the wheel exceeds a first swinging frame to enter a measurement state where the simple supporting beam and the cantilever beam coexist, when the width of the wheel is small, the back space of the wheel does not exceed the first swinging frame to enter the cantilever beam measurement state, the wheel is rotated by a motor or manually rotating the wheel, the system detects the angular speed of the grating disk through the photoelectric plate, when the angular speed reaches a certain value, the balancing machine is in a sliding sampling stage, the dynamic unbalance quantity of the wheel causes vibration of the transmission assembly to drive the first swinging frame and the second swinging frame to vibrate, and the dynamic unbalance quantity of the wheel can be calculated by collecting vibration quantities 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 stretches into the through hole on the end face of the brake block, the brake block stops rotating, the first brake pressing piece and the second brake pressing piece rotate along with the transmission component, the first friction piece generates friction force between the first brake pressing piece and the brake block, and the second friction piece generates friction force between the second brake pressing piece and the brake block, so that the transmission component stops rotating;
When the width of the wheel is smaller, the inner correction plane does not exceed the first swing frame, the vibration system still belongs to the cantilever structure, and the dynamic balance of the wheel is calculated still according to the original cantilever form. When the width of the wheel is large, the inner correction plane exceeds the first swing frame and is positioned between the two swing frames, the vibration system at the moment is a structure in which the cantilever beam and the simple support beam coexist, and the calculation principle of the wheel movement unbalance is described by combining the six to eight of the attached drawings;
The specific calculation method of dynamic balance is as follows: the dynamic wheel balancer has high bearing rigidity, and is similar to the bearing rigidity of the rotor, so that the balance working condition is similar to the actual working condition of the wheel. The rotor has two correction planes, so that it is necessary to convert the unbalance force signal measured at the bearing plane to the two correction planes. As shown in the sixth drawing:
F 1,F2 -dynamic forces acting on the two supporting planes respectively
F 1,f2 -centrifugal forces generated by unbalanced masses in the wheel-correction plane, respectively
M 1,m2 -unbalance masses on two correction planes of the wheel respectively
A, b, c-the distance between the relevant positions in the figure (b is the rotor thickness)
R 1,r2 -correction radius of rotor plane, i.e. distance from position of unbalanced mass for correction m 1、m2 to axis of rotation
Angular velocity of ω -spindle rotation
From this structure, according to the principle of statics, the upper diagram force system should satisfyBalance condition [ ]Representing moment), the moment is taken from the O2 fulcrum and the O1 fulcrum of the drawing respectively, and then:
It is rewritten as:
The dimensions of a, b, c are all known when the test wheel is stationary, let:
K11＝(c-a)/c
K12＝(b-a+c)/c
K21＝a/c
K22＝-(b-a)/c
Formula (2) can be written as:
From the equation (3), it can be solved that:
In (4) Centrifugal force generated for unbalance, namely:
So that:
The above calculations show that if the geometric parameters of the rotor and the balancing rotational speed are determined, the unbalance amounts and the added correction masses m (g) on the two correction planes of the rotor can be calculated from the measurement signals of the piezoelectric sensors.
Compared with the prior art, the invention has the following beneficial effects:
1. The invention overcomes the defects of the prior art, adopts the method that the wheels are arranged on the transmission assembly, the motor or the manual wheel rotation is used for rotating, the system detects the angular speed of the grating disk through the photoelectric plate, when the angular speed reaches a certain value, the balancing machine is in a sliding sampling stage, the dynamic unbalance quantity of the wheels causes the vibration of the transmission assembly, and the two piezoelectric sensors collect the vibration quantity, 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.
2. The invention overcomes the defects of the prior art, the front end swing frame of the shafting can extend into the rim of the test wheel, the distance between the two swing frames can be effectively utilized, the base can also strengthen the strength of the shafting, the requirements of testing the wheels of cars, buses and trucks can be met at the same time, the universality is improved, and the system stability is enhanced.
3. The invention has simple operation and convenient use.
Drawings
FIG. 1 is a three-dimensional schematic diagram of a dynamic balancer shafting with cantilever beam and simply supported beam coexistence according to the present invention;
FIG. 2 is a front view of a dynamic balancer shafting with cantilever beam and simply supported beam coexistence according to the present invention;
FIG. 3 is an enlarged schematic view of A-A in a dynamic balance machine shafting with cantilever beam and simple beam coexistence according to the present invention;
FIG. 4 is a three-dimensional exploded view of a dynamic balancer shafting with cantilever beam and simply supported beam coexistence according to the present invention;
FIG. 5 is a front view of a first rocker in a dynamic balance machine shafting with cantilever beam and simple beam coexistence according to the present invention;
FIG. 6 is a schematic illustration of the wheel load of a dynamic balancer shafting with cantilever beam and simply supported beam coexistence according to the present invention;
FIG. 7 is a schematic illustration of a load bearing profile of a dynamic balancing machine shafting with cantilever beam and simple beam coexistence according to the present invention;
Fig. 8 is a schematic diagram of cantilever beam stress of a dynamic balancing machine shafting with cantilever beam and simple beam coexistence according to the present invention.
Detailed Description
The first embodiment is as follows: referring to fig. 1 to 5, a dynamic balancing machine shafting with cantilever beam and simple beam coexistence according to the present embodiment is described, where the dynamic balancing machine shafting for wheels includes 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 bracket 4, a photoelectric plate 5 and a base 13;
The upper surface of the base 13 is uniformly provided with a first swing frame 2 and a second swing frame 3, the first swing frame 2 and the second swing frame 3 are coaxially arranged, one end of the transmission assembly 1 sequentially penetrates through the first swing frame 2 and the second swing frame 3 and is connected with the mechanical braking unit, one end of the side surface of the second swing frame 3 is provided with an electromagnetic braking unit, one end of the other side surface of the second swing frame 3 is connected with the photoelectric plate bracket 4 through a bolt, and the photoelectric plate bracket 4 is provided with a photoelectric plate 5;
In this embodiment, when in use, the wheel 36 is mounted on the transmission assembly 1, when the width of the wheel 36 is larger, the back space of the wheel 36 exceeds the first swing frame 2 to enter a measurement state where the simple beam and the cantilever beam coexist, when the width of the wheel 36 is smaller, the back space of the wheel 36 does not exceed the first swing frame 2 to enter a cantilever beam measurement state, the motor or the manual wheel is used for rotating, the system detects the angular velocity of the grating disk 6 through the photoelectric plate 5, when the certain angular velocity is reached, the balancing machine is in a sliding sampling stage, the dynamic unbalance of the wheel causes the vibration of the transmission assembly 1, the first swing frame 2 and the second swing frame 3 are driven to vibrate, the vibration quantity is acquired by the two piezoelectric sensors 23, and the dynamic unbalance of the wheel can be calculated. After sampling, the electromagnet 12 is electrified to push the brake pin 11 to act, the tail end of the brake pin 11 stretches into the through hole on the end face of the brake block 19, the brake block 19 stops rotating, the first brake pressing piece 17 and the second brake pressing piece 21 rotate along with the transmission component, the first friction plate 18 generates friction between the first brake pressing piece 17 and the brake block 19, and the second friction plate 20 generates friction between the second brake pressing piece 21 and the brake block 19, so that the transmission component stops rotating.
The second embodiment is as follows: the present embodiment is further limited to the dynamic balancer shafting according to the first embodiment, and the dynamic balancer shafting with cantilever beam and simple beam coexistence according to the present embodiment is described with reference to fig. 1 to 4, where the transmission assembly 1 includes 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 braking unit, and the other end of the transmission shaft 1-3 is provided with the matcher 1-2.
And a third specific embodiment: the present embodiment is further limited to the dynamic balancer shafting according to the first embodiment, and the dynamic balancer shafting with cantilever beam and simple beam coexistence according to the present embodiment is described with reference to fig. 2 and fig. 4, and the mechanical brake unit includes a grating disk 6, a brake disk 7, a brake force adjusting nut 14, a stop washer 15 and a wave spring 16;
the other end of the flat shaft 1-1 of the transmission assembly 1 sequentially passes through a brake disc 7, a wave spring 16, a stop washer 15 and a braking force adjusting nut 14 and is fixedly connected with the center of the grating disc 6;
In the specific embodiment, the other end of the flat shaft 1-1 of the transmission assembly 1 sequentially passes through the brake disc 7, the wave spring 16, the anti-return washer 15 and the braking force adjusting nut 14 and is fixedly connected with the center of the grating disc 6, so that the braking force of a shaft system is improved, and the stability is improved.
The specific embodiment IV is as follows: the present embodiment is further limited to the dynamic balance machine shaft system according to the third embodiment, and the dynamic balance machine shaft system with cantilever beam and simple beam coexistence according to the present embodiment is described with reference to fig. 2 and fig. 4, where the brake disc 7 includes a first brake pad 17, a first friction plate 18, a brake pad 19, a second friction plate 20 and a second brake pad 21; the flat shaft 1-1 is provided with 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 in sequence from left to right, and is coaxially arranged, and the end face of the brake sheet 19 is provided with a plurality of through holes along the circumferential direction;
In the specific embodiment, by adopting the arrangement, the braking force of the shafting is improved, and the stability is improved.
Fifth embodiment: the present embodiment is further limited to the dynamic balancer shafting according to the first embodiment, and the dynamic balancer shafting with cantilever beam and simple beam coexistence according to the present embodiment is described with reference to fig. 1 and fig. 4, and the electromagnetic braking unit includes an electromagnet bracket 8, a braking bolt 9, a spring 10, a braking pin 11 and an electromagnet 12;
The electromagnet bracket 8 is an L-shaped bracket, a round through hole is formed in the end face of the short side of the electromagnet bracket 8, a through hole is formed in one end of one side face of the second swing frame 3, the small-diameter end of the brake bolt 9 sequentially penetrates through the through hole in the electromagnet bracket 8 and the through hole in one end of the side face of the second swing frame 3 and is fixedly connected with a nut, a cavity is formed in the large-diameter end of the brake bolt 9 along the axial direction, one end of the brake pin 11 penetrates through the spring 10 and is inserted into the cavity of the brake bolt 9, the other end of the brake pin 11 is in contact with an electromagnet shaft of the electromagnet 12, and the lower surface of the electromagnet 12 is fixedly connected with the upper surface of the long side of the electromagnet bracket 8;
In the specific embodiment, by adopting the arrangement, the braking force of the shafting is improved, and the stability is improved.
Specific embodiment six: the present embodiment is further limited to the dynamic balance machine shafting according to the first embodiment, and the dynamic balance machine shafting with coexistence of the cantilever beam and the simply supported beam according to the present embodiment, wherein a through hole is formed at the lower part of the other end of the second swing frame 3, a cavity is formed at the other end of the side surface of the second swing frame 3, a second steel ball 22, a piezoelectric sensor 23 and a first steel ball 24 are sequentially formed inside the cavity from left to right, and are coaxially arranged, and one end of a concave end set screw 25 passes through a through hole at the lower part of the other end of the second swing frame 3 and contacts with the spherical surface of the first steel ball 24;
According to the special embodiment, the front end swing frame of the shafting can extend into the rim of the test wheel, the distance between the two swing frames can be effectively utilized, the base can further strengthen the strength of the shafting, the requirements of testing wheels of a car, a passenger car and a truck can be met, the universality is improved, and the system stability is enhanced.
Seventh embodiment: the present embodiment is further limited to the dynamic balance machine shafting according to the first embodiment, and the dynamic balance machine shafting with the coexistence of the cantilever beam and the simply supported beam according to the present embodiment has the same mechanical structure as the first swing frame 2 and the second swing frame 3, described with reference to fig. 3;
in the specific embodiment, the mechanical structures of the first swing frame 2 and the second swing frame 3 are the same, and the replacement is convenient after a certain time of use.
Eighth embodiment: the present embodiment is further limited to the dynamic balance machine axis system according to the seventh embodiment, and the dynamic balance machine axis system with cantilever beam and simple beam coexistence according to the present embodiment is described with reference to fig. 3, where the distance between the first swing frame 2 and the end face of the matcher 1-2 is 110 mm-230 mm;
In this embodiment, the distance between the first swing frame 2 and the end face of the matcher 1-2 is 110 mm-230 mm, so that the wheels 36 are mounted on the transmission assembly 1, when the width of the wheels 36 is large, the back space of the wheels 36 exceeds the first swing frame 2 to enter a measurement state where the simple beam and the cantilever beam coexist, and when the width of the wheels 36 is small, the back space of the wheels 36 does not exceed the first swing frame 2 to enter the cantilever beam measurement state.
Detailed description nine: the present embodiment is further limited to the dynamic balancing machine shafting according to the first embodiment, and the dynamic balancing machine shafting with cantilever beams and simple beams described in the present embodiment is further limited by referring to fig. 6 to 8, when the width of the wheel is smaller, the inner correction plane does not exceed the first swing frame, the vibration system still belongs to the 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 large, the inner correction plane exceeds the first swing frame and is positioned between the two swing frames, the vibration system at the moment is of a structure in which the cantilever beam and the simple beam coexist, and the calculation principle of the wheel movement unbalance in the state is described by combining with the accompanying drawing;
The calculation method of the dynamic balancing machine shafting is as follows: the dynamic wheel balancer has high bearing rigidity, and is similar to the bearing rigidity of the rotor, so that the balance working condition is similar to the actual working condition of the wheel. The rotor has two correction planes, so that it is necessary to convert the unbalance force signal measured at the bearing plane into two correction planes;
as shown in the sixth drawing:
F 1,F2 -dynamic forces acting on the two supporting planes respectively
F 1,f2 -centrifugal forces generated by unbalanced masses in the wheel-correction plane, respectively
M 1,m2 -unbalance masses on two correction planes of the wheel respectively
A, b, c-the distance between the relevant positions in the figure (b is the rotor thickness)
R 1,r2 -correction radius of rotor plane, i.e. distance from position of unbalanced mass for correction m 1、m2 to axis of rotation
Angular velocity of ω -spindle rotation
From this structure, according to the principle of statics, the upper diagram force system should satisfyBalance condition [ ]Representing moment), the moment is taken from the O2 fulcrum and the O1 fulcrum of the drawing respectively, and then:
It is rewritten as:
The dimensions of a, b, c are all known when the test wheel is stationary, let:
K11＝(c-a)/c
K12＝(b-a+c)/c
K21＝a/c
K22＝-(b-a)/c
Formula (2) can be written as:
From the equation (3), it can be solved that:
In (4) Centrifugal force generated for unbalance, namely:
So that:
The above calculations show that if the geometric parameters of the rotor and the balancing rotational speed are determined, the unbalance amounts and the added correction masses m (g) on the two correction planes of the rotor can be calculated from the measurement signals of the piezoelectric sensors.
Principle of operation
When the wheel 36 is used, the wheel 36 is arranged on the transmission assembly 1, when the width of the wheel 36 is large, the back space of the wheel 36 exceeds the first swing frame 2 to enter a measurement state where the simple beam and the cantilever beam coexist, when the width of the wheel 36 is small, the back space of the wheel 36 does not exceed the first swing frame 2 to enter the cantilever beam measurement state, the wheel is rotated by a motor or manual rotation, the system detects the angular speed of the grating disk 6 through the photoelectric plate 5, 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 vibration of the transmission assembly 1, and the dynamic unbalance of the wheel can be calculated by collecting the vibration quantity through the two piezoelectric sensors 23. After sampling, the electromagnet 12 is electrified to push the brake pin 11 to act, the tail end of the brake pin 11 stretches into the through hole on the end face of the brake block 19, the brake block 19 stops rotating, the first brake pressing piece 17 and the second brake pressing piece 21 rotate along with the transmission component, the first friction plate 18 generates friction between the first brake pressing piece 17 and the brake block 19, and the second friction plate 20 generates friction between the second brake pressing piece 21 and the brake block 19, so that the transmission component stops rotating.
Claims (2)
1. A dynamic balancing machine shafting with cantilever beam and simple beam coexist, its 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 bracket (4), a photoelectric plate (5) and a base (13);
The upper surface of the base (13) is uniformly provided with a first swing frame (2) and a second swing frame (3), the first swing frame (2) and the second swing frame (3) are coaxially arranged, one end of the transmission assembly (1) sequentially penetrates through the first swing frame (2) and the second swing frame (3) and is connected with the mechanical braking unit, one end of the side surface of the second swing frame (3) is provided with the electromagnetic braking unit, one end of the other side surface of the second swing frame (3) is connected with the photoelectric plate bracket (4) through a bolt, and the photoelectric plate bracket (4) is provided with the photoelectric plate (5); when the width of the wheel is relatively large, the back space of the wheel exceeds a first swing frame (2) to enter a measurement state where a simple beam and a cantilever beam coexist, when the width of the wheel is relatively small, the back space of the wheel does not exceed the first swing frame (2) to enter the cantilever beam measurement state, a motor or a manual wheel is used for rotating, the system detects the angular speed of a grating disc through a photoelectric plate (5), when the angular speed reaches a certain value, a balancing machine is in a sliding sampling stage, the dynamic unbalance quantity of the wheel causes the vibration of the transmission assembly (1), the first swing frame (2) and the second swing frame (3) are driven to vibrate, and the vibration quantity is collected by two piezoelectric sensors, so that the dynamic unbalance quantity of the wheel can be calculated; after sampling is finished, the electromagnet is electrified to push the brake pin to act, the tail end of the brake pin stretches into the through hole on the end face of the brake block, the brake block stops rotating, the first brake pressing piece and the second brake pressing piece rotate along with the transmission component (1), the first friction piece generates friction between the first brake pressing piece and the brake block, and the second friction piece generates friction between the second brake pressing piece and the brake block, so that the transmission component (1) stops rotating; when the width of the wheel is smaller, the inner correction plane does not exceed the first swing frame (2), and the vibration system still belongs to a cantilever beam structure;
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 braking unit, and the other end of the transmission shaft (1-3) is provided with a matcher (1-2);
The mechanical braking unit comprises a grating disc (6), a brake disc (7), a braking force adjusting nut (14), a stopping washer (15) and a wave spring (16);
The other end of the flat shaft (1-1) of the transmission assembly (1) sequentially passes through a brake disc (7), a wave spring (16), a stop washer (15) and a braking force adjusting nut (14) and is fixedly connected with the center of the grating disc (6);
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) along the circumferential direction;
the electromagnetic braking unit comprises an electromagnet bracket (8), a braking bolt (9), a spring (10), a braking pin (11) and an electromagnet (12);
The electromagnet support (8) is an L-shaped support, a round through hole is formed in the end face of the short side of the electromagnet support (8), a through hole is formed in one end of one side face of the second swing frame (3), the small-diameter end of the brake bolt (9) sequentially penetrates through the through hole in the electromagnet support (8) and the through hole in one end of the side face of the second swing frame (3) and is fixedly connected with a nut, a cavity is formed in the large-diameter end of the brake bolt (9) along the axial direction, one end of the brake pin (11) penetrates through the spring (10) and is inserted into the cavity of the brake bolt (9), the other end of the brake pin (11) is in contact with an electromagnet shaft of the electromagnet (12), and the lower surface of the electromagnet (12) is fixedly connected with the upper surface of the long side of the electromagnet support (8);
The lower part of the other end of the second swing frame (3) is provided with a through hole, the other end of the side surface of the second swing frame (3) is provided with a cavity, a second steel ball (22), a piezoelectric sensor (23) and a first steel ball (24) are sequentially arranged in the cavity from left to right and are coaxially arranged, and one end of a concave end set screw (25) penetrates through the through hole of the lower part of the other end of the second swing frame (3) and is in contact with the spherical surface of the first steel ball (24);
The distance between the first swing frame (2) and the end face of the matcher (1-2) is 110 mm-230 mm.
2. A dynamic balancing machine shafting with cantilever beam and simply supported beam coexistence as claimed in claim 1, wherein: the first swing frame (2) and the second swing frame (3) have the same mechanical structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010438294.1A CN111504554B (en) | 2020-05-21 | 2020-05-21 | Dynamic balancing machine shafting with cantilever beam and simply supported beam coexist |
Applications Claiming Priority (1)
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| CN201138268Y (en) * | 2007-12-28 | 2008-10-22 | 张云奎 | Dynamic wheel balancer axes set with hard support structure of outer cantilever |
| CN101608964B (en) * | 2009-08-03 | 2011-08-17 | 北京科基中意软件开发有限公司 | Balancer driven by disc electromagnetic driving device |
| CN202057456U (en) * | 2011-04-27 | 2011-11-30 | 中意泰达(营口)汽车保修设备有限公司 | Large-sized balancing machine detecting device |
| ITMO20120192A1 (en) * | 2012-07-31 | 2014-02-01 | Sicam Srl | BALANCING MACHINE FOR WHEEL BALANCING OF VEHICLES |
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