阅读说明：本技术 一种高速动平衡机支承摆架 (High-speed dynamic balancing machine supporting swing frame ) 是由 盛德恩 赵梦梦 孟庆慈 马建军 于 2021-03-24 设计创作，主要内容包括：本发明提供了一种高速动平衡机支承摆架,其组成主要包括摆架体、整体式刚度架、内外扇形板、侧盖板、摆架上盖、附加刚度装置、阻尼器、振动传感器等部件。其核心是采用了整体式刚度架,它由轴承座下瓦座、支承杆簧和刚度架底托组成。轴承孔与刚度架底托外圆同轴加工,刚度架底托外圆与摆架体柱面配合,提高了两摆架间的同心度。本发明的高速动平衡机支承摆架,减小了参振质量,扩展了工作转速范围,避免了承载结构件的强度薄弱点,大大提高了动载荷承载能力,显著降低了制造成本,改善了信号测试质量。(The invention provides a high-speed dynamic balancing machine supporting swing frame which mainly comprises a swing frame body, an integral rigidity frame, inner and outer fan-shaped plates, a side cover plate, a swing frame upper cover, an additional rigidity device, a damper, a vibration sensor and the like. 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 high-speed dynamic balancing machine supporting swing frame reduces the vibration quality, expands the working rotating speed range, avoids the weak strength of a bearing structural member, greatly improves the dynamic load bearing capacity, obviously reduces the manufacturing cost and improves the signal testing quality.)

1. A supporting swing frame of a high-speed dynamic balancing machine comprises a bearing seat lower shoe seat (1), a screw (2), a swing frame upper cover (3), a bearing cover (4), a bolt (5), a vibration damper (6), a bolt (7), a side cover plate (8), an inner fan-shaped plate (9), a swing frame body (10), a swing frame base (11), a bolt (12), a 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 vibration damper (20), an outer fan-shaped plate (21) and a screw (22), and is characterized in that the rigidity frame consisting of the bearing seat lower shoe seat (1), the supporting rod spring (14) and the rigidity frame bottom support (17) is an integral piece and is processed by a blank without any other connecting piece.

2. A supporting swing frame for high-speed dynamic balancing machine features that the separated oil-blocking ring and oil-blocking plate are installed to sector plate instead of two ends of bearing seat.

3. A high-speed dynamic balancing machine supporting swing frame is characterized in that a vibration measuring sensor (19) is arranged at the lower part of a lower pad seat (1) of a bearing of the swing frame and directly measures the vibration in the vertical direction.

4. A supporting swing frame of a high-speed dynamic balancing machine is characterized in that a rigid frame bottom support (17) and the inner side of a swing frame body (10) are in cylindrical surface matching relation.

Technical Field

The invention relates to the field of high-speed dynamic balance and overspeed tests of rotors, in particular to a supporting swing frame of a high-speed dynamic balancing machine, which is the most core part of the high-speed dynamic balancing machine and is used for supporting a balanced rotor through a sliding bearing and measuring a dynamic vibration signal corresponding to the unbalance of the rotor. 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.

Disclosure of Invention

Aiming at the problems of the prior supporting swing frame, the invention provides a supporting swing frame of a high-speed dynamic balancing machine with a novel structure, which is mainly characterized by comprising the following 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, no connecting piece is arranged between the support rod spring 14 and the bearing lower bush seat 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 screws 2, and the whole bearing seat is used for supporting the sliding bearing of the tested rotor.

6) The rigid frame bottom support 17 is connected with the pendulum frame body 10 through a 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.

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 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 screws 22. The sector plate is provided with a central hole along the center for the rotor shaft to pass through, and is provided with an oil deflector ring and an oil deflector plate which are equipped by a user according to the specific geometric dimension 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. The oil deflector ring and the oil deflector plate are arranged on the sector plate instead of two ends of the bearing seat, which is one of important characteristics of the invention, so that the mass of the bearing seat, namely the vibration participating mass of a vibration system, can be greatly reduced, and the highest working rotating speed of the pendulum frame can be easily improved without reducing the measurement sensitivity.

9) And flange plates are welded on two side edges of the sector plate and are used for being connected with a side cover plate 8 through 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.

10) The upper edge of the sector plate also contains a flange plate for connection with the upper swing frame cover 3 by means of bolts 5. The upper cover of the swing frame is used for blocking oil at the upper part, and the side surface and the 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 lower bearing bush seat 1 of the swing frame bearing, directly measures the vibration in the vertical direction and can measure the vibration by adopting a universal 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 vertical axis vibration dampers 6 and one horizontal axis vibration damper 20 are provided in order to reduce additional vibration when the bearing block passes a critical rotational speed in a non-measuring direction. The damper comprises a connecting rod connected with the bearing seat and a friction device arranged on the outer side of the sector plate.

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 diagram of a high-speed dynamic balancing machine supporting swing frame.

The device comprises a bearing seat lower shoe seat 1, a screw 2, a swing frame upper cover 3, a bearing cover 4, a bolt 5, a vibration damper 6, a bolt 7, a side cover plate 8, an inner fan-shaped plate 9, a swing frame body 10, a swing frame base 11, a bolt 12, a 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 measurement sensor 19, a vibration damper 20, an outer fan-shaped plate 21 and a screw 22.

Detailed Description

The invention relates to a bearing swing frame of a high-speed dynamic balancing machine with a novel structure, which keeps the dynamic characteristics of a rotor in a working state as much as possible, has enough mechanical vibration sensitivity and wide applicability 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 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 pad holder 1 through the screws 2, and the whole bearing seat is used for supporting the sliding bearing of the rotor to be tested.

The rigid frame bottom support 17 is connected with the pendulum frame body 10 through a 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 bolts 12.

The inner sector plate 9 and the outer sector plate 21 are respectively arranged on two sides of the pendulum frame body 10 and are connected with the pendulum frame body 10 through screws 22. The sector plate is provided with a central hole along the center for the rotor shaft to pass through, and is provided with an oil deflector ring and an oil deflector plate which are equipped by a user according to the specific geometric dimension 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. The oil deflector ring and the oil deflector plate are arranged on the sector plate instead of two ends of the bearing seat, which is one of important characteristics of the invention, so that the mass of the bearing seat, namely the vibration participating mass of a vibration system, can be greatly reduced, and the highest working rotating speed of the pendulum frame can be easily improved without reducing the measurement sensitivity.

And flange plates are welded on two side edges of the sector plate and are used for being connected with a side cover plate 8 through 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 edge of the sector plate also contains a flange plate for connection to the upper swing frame cover 3, by means of bolts 5. The upper cover of the swing frame is used for blocking oil at the upper part, and the side surface and the sector plate form an oil blocking ring interface complete circle together.

The vibration measuring sensor 19 is arranged at the lower part of the lower pad holder 1 of the swing frame bearing, directly measures the vibration in the vertical direction, and can measure the vibration by adopting a universal 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 the additional vibrations of the bearing block in the non-measuring direction past the critical rotational speed, two vertical axis vibration dampers 6 and one horizontal axis vibration damper 20 are provided. The damper comprises a connecting rod connected with the bearing seat and a friction device arranged on the outer side of the sector plate.

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 high-speed dynamic balancing machine supporting swing frame improves the concentricity between the two swing frames, expands the working rotating speed range, avoids the strength weak point of a bearing structural member, obviously reduces the manufacturing cost and improves the signal testing quality.