CN214373118U

CN214373118U - High-speed dynamic balancing machine supporting swing frame

Info

Publication number: CN214373118U
Application number: CN202120596558.6U
Authority: CN
Inventors: 盛德恩; 赵梦梦; 孟庆慈; 马建军
Original assignee: Hengchao Test Beijing Technology Co ltd
Current assignee: Hengchao Test Beijing Technology Co ltd
Priority date: 2021-03-24
Filing date: 2021-03-24
Publication date: 2021-10-08
Anticipated expiration: 2031-03-24

Abstract

The utility model provides a high-speed dynamic balancing machine supporting swing frame, its constitution mainly includes parts such as swing frame body, integral rigidity frame, inside and outside sector plate, side cap board, swing frame upper cover, additional rigidity device, attenuator, vibration sensor. The core of the device is that an integral rigidity frame is adopted, and the rigidity frame consists of a bearing seat lower shoe seat, a support rod spring and a rigidity frame bottom support. The bearing hole and the excircle of the rigidity frame bottom support are coaxially processed, and the excircle of the rigidity frame bottom support is matched with the cylindrical surface of the swing frame body, so that the concentricity between the two swing frames is improved. The utility model discloses a high-speed dynamic balancing machine supporting swing span has reduced the quality of participating in shaking, has expanded the operating speed scope, has avoided the intensity weak point of bearing the weight of the structure spare, has improved dynamic load bearing capacity greatly, is showing and is reducing manufacturing cost, has improved signal test quality.

Description

High-speed dynamic balancing machine supporting swing frame

Technical Field

The utility model relates to a high-speed dynamic balance of rotor and overspeed test field particularly, is a high-speed dynamic balancing machine supporting rocker, and this supporting rocker is the most core part of high-speed dynamic balancing machine for by balanced rotor through the slide bearing supporting, survey get with the corresponding dynamic vibration signal of rotor unbalance amount. The main technical requirements are that the dynamic characteristics of the rotor in the working state are kept as much as possible, the mechanical vibration sensitivity is sufficient, and the mechanical vibration sensor is widely applicable to various rotors. The advantages and disadvantages of the design of the supporting swing frame directly influence the performance and service life of the high-speed dynamic balancing machine, the accuracy of measurement and the balancing efficiency.

Background

The equipment for dynamic balance and overspeed test of the flexible rotor is called a high-speed dynamic balancing machine, wherein a swinging frame for supporting the flexible rotor is the most critical and most central component of the high-speed dynamic balancing machine. Aiming at the special balance task of dynamic balance of the flexible rotor, the design of the swing frame has the following technical characteristics.

1) Hard support requirements. There are two implications: on one hand, under the condition of hard support, the vibration mode of the measured rotor on the balancing machine can be kept consistent with the vibration mode under the working state, so that correct balance measurement and correction can be carried out; on the other hand, the first-order natural frequency of the supporting swing frame system is required to be higher than the highest working rotating speed of the measured rotor, so that the critical rotating speed vibration peak value encountered in the whole measuring rotating speed range is ensured to be originated from the measured rotor and not from the equipment.

2) Radial direction equal rigidity of the supporting swing frame is required. The rigidity of the supporting pendulum in the vertical direction and the horizontal direction is approximately equal, so that each stage of critical rotating speed vibration of the measured rotor has only one peak value in the speed increasing and decreasing process, and the phenomenon that the vibration is divided into two parts due to unequal rigidity is avoided, and the measurement is influenced.

3) Spherical elastic support is required. The high-speed dynamic balancing machine is designed for supporting a rotor by a sliding bearing, and the bearing has a certain axial length, so that the additional even unbalance influence generated by the bearing is reduced, the bearing can follow the deflection deformation of the rotor, the edge pressure of the bearing is reduced, the torsional rigidity of a bearing seat of a supporting swing frame around a vertical shaft and a horizontal shaft is required to be low, and the bearing seat has elastic deformation capacity similar to spherical bearing.

4) Higher concentricity requirement. Because the actual distance between the supporting pendulums depends on the distance between the two bearings of the actual measured rotor, the variation range of the measured rotor with different lengths is large; and because the same high-speed balancing machine is often required to be provided with a plurality of pairs of supporting swing frames with different specifications, the requirement on the concentricity between the supporting swing frames is very high, so that the rotors to be tested with different lengths between the supporting swing frames and the same pair of supporting swing frames can work in a better centering state.

5) The ability to withstand higher dynamic loads. Because the measured rotor needs to pass through the critical rotating speed in the measuring process, the measured rotor is easy to generate part displacement or elastic-plastic deformation at high rotating speed, and huge centrifugal dynamic load can be generated, and the dynamic load can be several times of static load. In addition to the additional stiffness as an effective safety measure for the support rocker, the basic structure should also have a high dynamic load carrying capacity, so that the normal operation of the measurement can be ensured.

The supporting swing frame of the high-speed dynamic balancing machine seen in the current market is the most representative of the supporting swing frame imported by a certain company in Germany, and the use practice of decades proves that the supporting swing frame can better meet the measurement requirement of the high-speed dynamic balance of the flexible rotor, the main reason is that the first three technical requirements are better met, but the product design has some defects and places worth improvement, and the following aspects are mainly provided.

1) The concentricity of the supporting swing frame is poor. The concentricity between the same pair of supporting swing frames is poor, and the concentricity between the supporting swing frames with different specifications arranged on the same lathe bed is poor. The main reason is that the position of the bearing seat hole center of each supporting swing frame is realized by an assembly process instead of a machining process, and the assembly process can only control the error of the hole center in the vertical direction and cannot control the error of the hole center in the horizontal direction.

2) The structural design and the assembly process are too complex, the manufacturing cost of parts is high, and the assembly workload is large.

3) Due to the structural design characteristics, the key bearing parts are provided with weak parts such as threads and tool withdrawal grooves, the load bearing capacity of the bearing swing frame is greatly reduced, safety equipment such as dynamic load monitoring is required, and the problem of premature fatigue failure is still difficult to avoid sometimes.

4) Due to the structural design characteristics, under the condition that the specification and the model are determined (the weight and the shaft diameter of the measured rotor are fixed), the highest working rotating speed of the supporting swing frame is difficult to increase, and the requirement of a user on continuously increasing dynamic balance rotating speed is difficult to adapt. Under the condition that the weight and the rotating speed of the rotor are determined, the requirement of a user for enlarging the diameter of the shaft hole (such as installing a tilting pad) is difficult to meet.

5) The requirement for a specially-made relative vibration velocity sensor and a complicated connecting mechanism increases the manufacturing cost and the spare part cost. After the sensor and the connecting mechanism parts are replaced, the support swing frame and the whole measuring chain are often required to be calibrated and checked again.

6) Due to the structural design characteristics, the vibration of the bearing seat of the supporting swing frame is rigid plane motion, the measurement signal is actually a signal synthesized by two sensors forming an included angle of 45 degrees with a vertical axis, and is not a pure vibration signal in the vertical direction, the influence is obvious by the vibration in the horizontal direction, and particularly, the actual measurement precision is influenced before a stable oil film is established on the sliding bearing of the measured rotor and during the over-critical rotating speed of the rotor.

SUMMERY OF THE UTILITY MODEL

To the above-mentioned problem that current supporting rocker exists, the utility model provides a high-speed dynamic balancing machine supporting rocker of novel structure, its leading features have following several aspects.

1) The core part is an integrated part consisting of the bearing seat lower shoe seat 1, the supporting rod spring 14 and the rigidity frame bottom support 17, is processed by a blank without any other connecting piece, and is called as the rigidity frame hereinafter.

2) The structure of the stiffness frame can be described as that the bearing seat lower shoe 1 is supported on the stiffness frame bottom support 17 through the support rod spring 14, and the stiffness of the support rod spring 14 and the mass of the bearing seat lower shoe 1 are calculated and designed according to the specification parameters (mainly the highest working rotating speed) of the support swing frame. The number of the support rod springs 14 is four, two are arranged on each side, an included angle of 45 degrees is formed between each side and the vertical axis, and the support rod springs are symmetrically distributed on two sides of a 45-degree line, so that approximately equal rigidity in the vertical direction and the horizontal direction is realized, and the friction torque of the rotor sliding bearing to be tested can be borne during working. The aperture of the bearing seat and the diameter of the rigid frame bottom support 17 are determined according to the specification and the size of the supporting swing frame.

3) And because the supporting swing frames are always manufactured in pairs and used in pairs, the rigid frame can also be manufactured in pairs, a full-circle structure is machined from the same blank, and then the blank is cut into a final fan shape. Thus, the concentricity of the bearing hole and the excircle of the rigid frame bottom support 17 is easy to ensure, and the concentricity precision between the two support swinging frames is also easy to ensure.

4) Because the rigidity frame is an integral piece, connecting pieces are not arranged between the support rod spring 14 and the bearing seat lower shoe 1 and the rigidity frame bottom support 17, and weak parts such as threads and tool withdrawal grooves are not arranged, the bearing capacity of the rigidity frame is greatly improved.

5) And on the same principle, the bearing covers 4 of the two supporting swing frames can also be processed in pairs and are connected with the bearing seat lower bearing bush seat 1 through the first screws 2, and the whole bearing seat is used for supporting the sliding bearing of the detected rotor.

6) The rigid frame bottom support 17 is connected with the pendulum frame body 10 through a fourth bolt 13. The inner side of the swing frame body 10 is a cylindrical surface and is matched with the outer circle of the rigid frame bottom support 17, so that the position precision of the center of the bearing hole of the whole swing frame is ensured. The pendulum supports 10 may also be machined in pairs and then cut to final shape and size to ensure centering accuracy between the two pendulum supports.

7) The two sides of the steel plate of the swing frame body 10 and the swing frame base 11 are welded into a whole, and the swing frame base 11 is provided with bolt holes for installing the swing frame on the high-speed dynamic balancing machine body through third bolts 12.

8) The inner sector plate 9 and the outer sector plate 21 are respectively arranged on two sides of the swing frame body 10 and are connected with the swing frame body 10 through second screws 22. The inner sector plate 9 and the outer sector plate 21 are provided with central holes along the center for the rotor shaft to pass through, and are provided with oil slingers and oil slingers which are equipped by users according to the specific geometrical size of the measured rotor. And an oil return pipe interface 18 is arranged at the bottom of the outer sector plate 21 and is used for bearing lubricating oil to flow back. Install including oil slinger and oil slinger on the outer sector plate, rather than installing at the bearing frame both ends, this is also the utility model discloses an one of the important characteristics can reduce the bearing frame quality greatly like this, the quality of shaking of participating of vibration system promptly to can improve the highest operating speed of pendulum frame easily and not reduce measurement sensitivity.

9) And flange plates are welded on two side edges of the inner sector plate 9 and the outer sector plate 21 and are used for being connected with the side cover plate 8 and connected through a second bolt 7. The side cover plate 8 is used for blocking oil and enhancing the integral rigidity of the swing frame, so that resonance of the structure is avoided.

10) The upper edges of the inner sector 9 and the outer sector 21 also contain flange plates for connection with the rocker upper cover 3, by means of the first bolts 5. The upper cover of the swing frame is used for oil blocking at the upper part, and the side surface and the inner sector plate and the outer sector plate form an oil blocking ring interface complete circle together.

11) And the vibration measuring sensor 19 is arranged at the lower part of the bearing seat lower tile seat 1, directly measures the vibration in the vertical direction and can measure the vibration by adopting a general vibration speed sensor. The vibration signal is not affected by the vibration of the bearing seat in the horizontal direction and the torsional vibration around the rotating shaft.

12) And in order to ensure safety and expand the test range, the swing frame is provided with an additional rigidity plate spring 16 and an additional rigidity action oil cylinder 15.

13) Two first vibration dampers 6 around the vertical axis and a second vibration damper 20 around the horizontal axis are provided in order to reduce additional vibrations when the bearing block passes the critical rotational speed in the non-measuring direction. The damper comprises a connecting rod connected with the bearing seat lower tile seat 1 and a friction device arranged on the outer side of the outer sector plate 21.

14) And the swing frame is provided with an oil pipe for providing bearing lubricating oil, high-pressure jacking oil and variable-rigidity high-pressure oil.

15) And a dynamic load monitoring sensor is not arranged on the swing frame, and a broadband vibration signal of the vibration measurement sensor 19 is used for monitoring a vibration speed effective value and is used as safety protection.

Drawings

Fig. 1 is a schematic view of a supporting swing frame of a high-speed dynamic balancing machine according to the present invention.

The vibration testing device comprises a bearing seat lower tile seat 1, a first screw 2, a swing frame upper cover 3, a bearing cover 4, a first bolt 5, a first vibration damper 6, a second bolt 7, a side cover plate 8, an inner fan-shaped plate 9, a swing frame body 10, a swing frame base 11, a third bolt 12, a fourth bolt 13, a support rod spring 14, an additional rigidity action oil cylinder 15, an additional rigidity plate spring 16, a rigidity frame bottom support 17, an oil return pipe interface 18, a vibration testing sensor 19, a second vibration damper 20, an outer fan-shaped plate 21 and a second screw 22.

Detailed Description

The utility model discloses an idea is the high-speed dynamic balancing machine supporting rocker of design a novel structure, makes its dynamic characteristic that keeps the rotor to present under its operating condition as far as possible, has sufficient mechanical vibration sensitivity to and the extensive suitability to various rotors. The specific embodiment is as follows.

The core part is an integrated part consisting of the bearing seat lower shoe 1, the support rod spring 14 and the rigidity frame bottom support 17, is processed by a blank without any other connecting piece, and is called as the rigidity frame hereinafter.

The structure of the stiffness frame can be described as bearing housing lower shoe 1 supported on stiffness frame shoe 17 by support bar springs 14, the stiffness of support bar springs 14 and the mass of bearing housing lower shoe 1 being calculated and designed according to the support pendulum frame specification parameters (mainly the highest operating speed). The number of the support rod springs 14 is four, two are arranged on each side, an included angle of 45 degrees is formed between each side and the vertical axis, and the support rod springs are symmetrically distributed on two sides of a 45-degree line, so that approximately equal rigidity in the vertical direction and the horizontal direction is realized, and the friction torque of the rotor sliding bearing to be tested can be borne during working. The aperture of the bearing seat and the diameter of the rigid frame bottom support 17 are determined according to the specification and the size of the supporting swing frame.

Since the supporting rocker frames are always produced in pairs and used in pairs, the rigid frames can also be produced in pairs, from the same blank a full circle structure is produced and cut into the final sectors. Thus, the concentricity of the bearing hole and the excircle of the rigid frame bottom support 17 is easy to ensure, and the concentricity precision between the two support swinging frames is also easy to ensure.

Because the rigidity frame is an integral piece, no connecting piece is arranged between the support rod spring 14 and the bearing seat lower shoe 1 and the rigidity frame bottom support 17, and weak parts such as threads and tool withdrawal grooves are not arranged, the bearing capacity of the rigidity frame is greatly improved.

In the same way, the bearing covers 4 of the two bearing swinging frames can also be processed in pairs and are connected with the bearing seat lower shoe seat 1 through the first screws 2, and the whole bearing seat is used for supporting the sliding bearing of the tested rotor.

The rigid frame bottom support 17 is connected with the pendulum frame body 10 through a fourth bolt 13. The inner side of the swing frame body 10 is a cylindrical surface and is matched with the outer circle of the rigid frame bottom support 17, so that the position precision of the center of the bearing hole of the whole swing frame is ensured. The pendulum supports 10 can also be machined in pairs and then cut to final shape and size, thus ensuring the centering accuracy between the two pendulum supports.

The two sides of the steel plate of the swing frame body 10 are welded with the swing frame base 11 into a whole, and the swing frame base 11 is provided with bolt holes for installing the swing frame on the high-speed dynamic balancing machine body through third bolts 12.

The inner sector plate 9 and the outer sector plate 21 are respectively arranged on two sides of the swing frame body 10 and connected with the swing frame body 10 through second screws 22. The inner sector plate 9 and the outer sector plate 21 are provided with central holes along the center for the rotor shaft to pass through, and are provided with oil slingers and oil slingers which are equipped by users according to the specific geometrical size of the measured rotor. And an oil return pipe interface 18 is arranged at the bottom of the outer sector plate 21 and is used for bearing lubricating oil to flow back. Install including oil slinger and oil slinger on the outer sector plate, rather than installing at the bearing frame both ends, this is also the utility model discloses an one of the important characteristics can reduce the bearing frame quality greatly like this, the quality of shaking of participating of vibration system promptly to can improve the highest operating speed of pendulum frame easily and not reduce measurement sensitivity.

Flange plates are welded on two side edges of the inner sector plate 9 and the outer sector plate 21 and are used for being connected with the side cover plate 8 through second bolts 7. The side cover plate 8 is used for blocking oil and enhancing the integral rigidity of the swing frame, so that resonance of the structure is avoided.

The upper edges of the inner sector 9 and the outer sector 21 also contain flange plates for connection with the upper swing frame cover 3, by means of the first bolts 5. The upper cover of the swing frame is used for oil blocking at the upper part, and the side surface and the inner sector plate and the outer sector plate form an oil blocking ring interface complete circle together.

The vibration measuring sensor 19 is arranged at the lower part of the bearing seat lower shoe 1, directly measures the vibration in the vertical direction, and can measure the vibration by adopting a general vibration speed sensor. The vibration signal is not affected by the vibration of the bearing seat in the horizontal direction and the torsional vibration around the rotating shaft.

In order to ensure safety and expand the test range, the swing frame is provided with an additional rigidity plate spring 16 and an additional rigidity action oil cylinder 15.

In order to reduce additional vibrations in the bearing blocks in the non-measuring direction past the critical speed, two first vibration dampers 6 are provided about the vertical axis, and one second vibration damper 20 is provided about the horizontal axis. The damper comprises a connecting rod connected with the bearing seat lower tile seat 1 and a friction device arranged on the outer side of the outer sector plate 21.

The swing frame is provided with an oil pipe for providing bearing lubricating oil, high-pressure jacking oil and variable-rigidity high-pressure oil.

A dynamic load monitoring sensor is not arranged on the swing frame, and a broadband vibration signal of the vibration measuring sensor 19 is used for monitoring a vibration speed effective value and is used as safety protection.

The utility model discloses a high-speed dynamic balancing machine supporting swing span has improved the concentricity between two swing spans, has expanded the operating rotation speed scope, has avoided the intensity weak point of bearing the weight of the structure, is showing and is reducing manufacturing cost, has improved signal test quality.

Claims

1. A supporting swing frame of a high-speed dynamic balancing machine comprises a bearing seat lower shoe seat (1), first screws (2), a swing frame upper cover (3), a bearing cover (4), first bolts (5), a first vibration damper (6), second bolts (7), a side cover plate (8), an inner fan-shaped plate (9), a swing frame body (10), a swing frame base (11), a third bolt (12), a fourth bolt (13), a supporting rod spring (14), an additional rigidity action oil cylinder (15), an additional rigidity plate spring (16), a rigidity frame bottom support (17), an oil return pipe interface (18), a vibration measuring sensor (19), a second vibration damper (20), an outer fan-shaped plate (21) and second screws (22), and is characterized in that the bearing seat lower shoe seat (1) is supported on the rigidity frame bottom support (17) through the supporting rod spring (14), the supporting rod springs (14) are four in total, and each side is two, and the included angle of 45 degrees is formed between the rigid frame and a vertical shaft, the rigid frame is symmetrically distributed on two sides of a 45-degree line, and the rigid frame consisting of a bearing seat lower shoe seat (1), a supporting rod spring (14) and a rigid frame bottom support (17) is an integrated piece.

2. The high-speed dynamic balancing machine supporting swing frame according to claim 1, wherein the separate oil slinger and oil slinger are mounted on the inner sector plate (9) and the outer sector plate (21) instead of being mounted at both ends of the bearing housing.

3. The high-speed dynamic balancing machine supporting pendulum frame of claim 1, wherein the vibration sensor (19) is installed at the lower portion of the bearing seat lower shoe (1) to directly measure the vibration in the vertical direction.

4. The high-speed dynamic balancing machine supporting swing frame of claim 1, characterized in that the rigid frame bottom support (17) is connected with the swing frame body (10) through a fourth bolt (13), and the inner side of the swing frame body (10) is a cylindrical surface and has a matching relation with the outer circle of the rigid frame bottom support (17).