A squeeze film damper capable of segmentally controlling the oil film width

Abstract

The present invention discloses an squeeze film damper capable of segmentally controlling the oil film width, belonging to the technical field of damper design; it includes a damper oil film inner ring, a damper housing and a sealing end cover. A plurality of pads are arranged between the damper housing and the damper oil film inner ring. An oil film cavity is provided between the outer side of the pad and the outer circumferential surface of the damper oil film inner ring. The electromagnetic mechanism includes an exciting coil, a C-shaped electromagnet iron core and a permanent magnet. A permanent magnet mounting groove is protrudingly arranged on the radially outer end surface of the pad. Two permanent magnets with opposite poles are fixedly connected in the permanent magnet mounting groove. The two magnetic poles of the C-shaped electromagnet iron core are respectively arranged corresponding to the two axial end surfaces of the permanent magnet mounting groove, and a spring is connected between the C-shaped electromagnet iron core and the axial end surface of the permanent magnet mounting groove. The device of the present invention can independently adjust the axial width of the oil film at each position in the circumferential direction, provide an appropriate damping for the rotor system, and improve the vibration reduction effect.

Description

Technical Field

[0001] The present invention relates to a squeeze film damper that can be actively controlled, and more particularly to a squeeze film damper that can control the film width in segments, belonging to the technical field of damper design. Background Art

[0002] With the continuous improvement of the operating parameters of rotating machinery, the operating speeds of some rotating machinery are above the critical speeds of their shafting. In addition, due to the limitations of their manufacturing and assembly precision and the influence of complex working conditions, during the operation of the rotating shaft, especially when exceeding its critical speed, it will cause severe vibration of the rotor system, seriously affecting the working life and stability of the rotor system. As an effective vibration reduction device, the squeeze film damper has been widely used in various equipment. It changes the original interference fit between the bearing and the bearing housing to a clearance fit, and the gap is used as an oil film cavity to introduce lubricating oil to form an oil film. During the vibration process of the rotor, the rotor squeezes the oil film, and the kinetic energy transmitted by the rotor to the support is converted into the internal energy of the lubricating oil, thereby achieving the effect of vibration reduction.

[0003] The squeeze film damper provides good vibration reduction effects for large rotating machinery with a small volume occupation and a compact structure. However, the structural parameters of the traditional squeeze film damper are fixed, and it is essentially a non-linear damper. The optimal stiffness damping value required by the rotor is a function of the vibration frequency, and there are different optimal stiffness damping values corresponding to different vibration modes. The narrow steady-state working area of the squeeze film damper makes its fixed parameter structure only able to achieve effective vibration reduction effects under specific working conditions. And under a large unbalance response, non-linear oil film forces appear, and the non-linearity is more prominent in the oil film stiffness. Moreover, with the increase of the squeezing effect, the degree of non-linearity also increases. Non-linear problems such as "locking", "bistable response", "non-coordinated precession" and even "chaotic motion" are extremely likely to occur under conditions of unreasonable parameter design, high speed, large load, sudden addition of unbalance, etc. At this time, not only the vibration reduction effect cannot be achieved, but it will also pose a threat to the operating safety of the rotor system. At the same time, the traditional squeeze film damper has high requirements for the precision of manufacturing and assembly, and these problems have greatly limited the vibration reduction effect and application range of the squeeze film damper.

[0004] At present, in order to improve the performance of squeeze film dampers and avoid a series of problems caused by strong nonlinear characteristics, many experts and scholars have improved traditional squeeze film dampers and proposed new structural forms. For example: 1) The public literature [1] Ma Yanhong, Hong Jie, Zhao Fuan. Theoretical research on the vibration reduction mechanism of adaptive squeeze film dampers [J]. Journal of Beijing University of Aeronautics and Astronautics, 2004(01):5-8. DOI:10.13700 / j.bh.1001-5965.2004.01.002. proposed an adaptive squeeze film damper with metal rubber in series on the outer ring of the oil film, which can relieve the drastic change of the oil film thickness with the shaft diameter displacement through the deformation of the metal rubber. However, due to the manufacturing process, durability and stability of the new material, this type of squeeze film damper is restricted in practical applications; 2) The public literature [2] Wang Jianxiao, Meng Guang, Chen Yunxi. Extrusion type magnetorheological fluid damper - dynamic characteristics and control of rotor system [J]. Chinese Journal of Mechanical Engineering, 2004(03):76-83. controls the viscosity of the magnetorheological fluid by applying an external magnetic field to change the nonlinear characteristics of the squeeze film damper. However, the magnetorheological fluid itself has unsatisfactory stability, high cost and is vulnerable to the working environment; and 3) The public literature [3] Zhang Jin, Wang Xiaojing, Dong Jian, Chen Chao, Shen Yifan, Shen Jiexi. Experimental study on vibration characteristics of controllable squeeze film damper [J]. Lubrication Engineering, 2018, 43(10):111-115. adjusts the stiffness and damping of the squeeze film damper by controlling the oil supply pressure of the squeeze film damper. However, it has high requirements for the oil supply pressure, requires an additional oil supply device, and occupies a large space. The above improvement forms have some structural devices that are too complex and large, some materials are immature, and their stability needs to be studied. At the same time, the application scenarios are strictly restricted and are not suitable for specific application environments. In addition, the common squeeze film dampers currently available need to be strictly designed according to the usage requirements, and the geometric parameters cannot be changed after manufacturing. However, the accumulation of errors in the actual manufacturing and assembly process may have a serious impact on the final usage effect. Therefore, high processing accuracy is required for it.

[0005] Therefore, there is an urgent need to design an actively controllable squeeze film damper, which can change the stiffness and damping values by changing the oil film width. Summary of the Invention

[0006] The object of the present invention is to overcome the deficiencies existing in the prior art and provide a squeeze film damper capable of segmentally controlling the oil film width. This damper divides the outer ring of the traditional complete circular oil film into several independent tiles, and independently adjusts the axial position of each tile through an electromagnetic mechanism connected to the tile, so as to change the oil film width of the corresponding area, enabling it to adjust the oil film characteristics of each position according to the system structure and working state, and achieving a good vibration reduction effect.

[0007] To achieve the above object, the present invention adopts the following technical solutions: An squeeze film damper capable of segmentally controlling the oil film width, comprising a damper oil film inner ring sleeved on the outer ring of the bearing, and a damper housing and a sealing end cover sleeved on the outer ring of the damper oil film inner ring. A plurality of pads are evenly distributed along the circumferential direction between the damper housing and the damper oil film inner ring. An electromagnetic mechanism is connected to the outer side of the pad, and an oil film cavity is provided between the inner side surface and the outer circumferential surface of the damper oil film inner ring;

[0008] The electromagnetic mechanism includes an excitation coil, a C-shaped electromagnet iron core and a permanent magnet. A permanent magnet mounting groove is protrudingly provided on the radially outer end surface of the pad. Two permanent magnets with opposite poles are fixedly connected in the permanent magnet mounting groove. The two magnetic poles of the C-shaped electromagnet iron core are respectively arranged corresponding to the two axial end surfaces of the permanent magnet mounting groove, and a spring is connected between the C-shaped electromagnet iron core and the axial end surface of the permanent magnet mounting groove. The excitation coil is wound around a section of the C-shaped electromagnet iron core corresponding to the permanent magnet in the radial direction;

[0009] Circumferentially protruding guide sliders are provided on the two radial sides of the permanent magnet mounting groove. A plurality of pad mounting openings for clamping the pads are evenly distributed along the circumferential direction on the damper housing. Axially extending pad guide chutes are provided on the two side walls of the pad mounting opening. The outer edge of the pad is axially fitted in the damper housing through the cooperation of the guide slider and the pad guide chute.

[0010] A gap for lubricating oil to flow through is provided between two adjacent pads. An oil inlet hole is provided on the outer side wall of the damper housing in the radial direction, and the oil inlet hole is communicated with the gap between the pads.

[0011] Circumferentially extending circumferential oil guide grooves are provided on the inner arc-shaped surface of the pad. The gap between the circumferential oil guide grooves and the outer circumferential surface of the damper oil film inner ring constitutes the oil film cavity.

[0012] An electromagnet cover plate is provided in the gap between the C-shaped electromagnet iron core and the pad mounting opening on the damper housing. The electromagnet cover plate includes an electromagnet right cover plate and an electromagnet left cover plate symmetrically arranged left and right along the circumferential direction; A first cover plate fixing groove and a second cover plate fixing groove for clamping and fixing the electromagnet cover plate are respectively provided on the end surface of the damper housing corresponding to the bottom of the pad mounting opening and the inner end surface of the sealing end cover.

[0013] A set screw hole is provided on the pad located on one axial side of the permanent magnet mounting groove. The permanent magnet is fixedly connected in the permanent magnet mounting groove through the cooperation of the set screw and the set screw hole.

[0014] One end of the damper housing is a housing flange, which is fixedly connected to an external load-bearing member through the housing flange. A plurality of threaded counterbores are evenly distributed along the circumferential direction on the other end surface of the damper housing away from the housing flange; a plurality of through holes are evenly distributed along the circumferential direction on the sealing end cover, and the sealing end cover is fixedly connected to the damper housing through fixing screws passing through the through holes and being in threaded fit with the threaded counterbores.

[0015] An annular groove is provided on the inner circumferential surface of the sealing end cover, and a first sealing ring is fitted and connected in the annular groove. The outer edge surface of the inner ring of the damper oil film is hermetically connected to the sealing end cover through the first sealing ring.

[0016] An inner flange of the housing is provided axially inward along the housing flange on the damper housing. An annular groove is provided on the inner circumferential surface of the inner flange of the housing, and a second sealing ring is fitted and connected in the annular groove. The outer edge surface of the inner ring of the damper oil film is hermetically connected to the inner flange of the housing through the second sealing ring.

[0017] The inside of the inner ring of the damper oil film is connected to a bearing and a rotor through a bearing installation hole. An elastic support and an installation base are provided at one end away from the bearing installation hole, and are fixedly connected to an external load-bearing member through the installation base; one side of the inner ring of the damper oil film where the bearing installation hole is provided is of a stepped shape, and the diameter of the outer circumferential surface of a section where the inner ring of the damper oil film forms a seal with the sealing end cover is smaller than the diameter of the section where the inner ring of the damper oil film forms an oil film cavity with the shoe.

[0018] The beneficial effects of the present invention are as follows:

[0019] 1) The device of the present invention drives each shoe to perform axial displacement through electromagnetic force, thereby controlling the axial width of the oil film formed between the damper shoe and the inner ring of the damper oil film, realizing the adjustment of the damper oil film parameters, and thus realizing the control of the damping and stiffness characteristics of the squeeze film damper, providing the rotor with stiffness damping characteristics that vary with the rotational speed and load and the optimal damping values corresponding to different vibration modes, and further being able to effectively control the vibration of the rotor within the full rotational speed range, and at the same time being able to eliminate the influence of the design, manufacturing and assembly errors of the squeeze film damper on its vibration reduction effect.

[0020] 2) A plurality of shoes evenly distributed around the inner ring of the damper oil film in the device of the present invention can apply appropriate current magnitudes and directions to each electromagnet by an external controller according to different vibration modes of the rotor system, so that different adjustments of the oil film width in each circumferential section can be generated in a very short time in the working state, so that the rotor can receive different damping forces in different directions of the circumference according to the amplitude, frequency and phase of its vibration, realizing more effective vibration control of the rotor system. Description of the Drawings

[0021] Figure 1Structural sectional view of the present invention;

[0022] Figure 2 Axonometric semi-sectional structural schematic diagram of the present invention;

[0023] Figure 3 is Figure 1 Partial enlarged view at position B in

[0024] Figure 4 is Figure 1 Cross-sectional view in the A-A direction in

[0025] Figure 5 is Figure 2 Structural schematic diagram of the shoe in

[0026] Figure 6 is Figure 2 Structural schematic diagram of the damper housing in

[0027] Figure 7 is Figure 2 Axonometric semi-sectional structural schematic diagram of the inner oil film ring of the damper in

[0028] In the figure, 1 - damper housing, 101 - housing flange, 102 - first cover fixing groove, 103 - threaded counterbore, 104 - oil inlet hole, 105 - shoe mounting opening, 1051 - shoe guiding chute, 106 - inner flange of the housing, 2 - shoe, 201 - circumferential oil guiding groove, 202 - guiding slider, 203 - permanent magnet mounting groove, 204 - set screw hole, 3 - exciting coil, 4 - C-shaped electromagnet iron core, 5 - sealing end cover, 501 - second cover fixing groove, 6 - inner oil film ring of the damper, 601 - mounting base, 602 - elastic support, 603 - bearing mounting hole, 7 - bearing, 8 - oil film cavity, 9 - first sealing ring, 10 - set screw, 11 - permanent magnet, 12 - spring, 13 - second sealing ring, 14 - fixing screw, 15 - gap between shoes, 16 - right cover of the electromagnet, 17 - left cover of the electromagnet. Detailed implementation manners

[0029] The present invention will be further explained below with reference to the accompanying drawings and specific embodiments.

[0030] Embodiment: As Figure 1-7As shown in the figure, the present invention provides an squeeze film damper capable of segmentally controlling the oil film width, which includes a damper oil film inner ring 6 sleeved on the outer ring of a bearing 7, and a damper housing 1 and a sealing end cover 5 sleeved on the outer ring of the damper oil film inner ring 6. Six pads 2 are evenly distributed along the circumferential direction between the damper housing 1 and the damper oil film inner ring 6. The outer side of the pad 2 is connected to an electromagnetic mechanism. A circumferential oil guiding groove 201 is formed along the circumferential direction on the inner arc surface of the pad 2. The gap between the circumferential oil guiding groove 201 and the outer circumferential surface of the damper oil film inner ring 6 forms an oil film cavity 8.

[0031] A gap 15 for lubricating oil to flow through is left between two adjacent pads 2. An oil inlet hole 104 is formed on the outer side wall of the damper housing 1 along the radial direction, and the oil inlet hole 104 is communicated with the gap 15 between the pads, and then enters the oil film cavity 8 through the circumferential oil guiding groove 201 for lubrication.

[0032] A permanent magnet mounting groove 203 is convexly provided on the radially outer end surface of the pad 2. Guide sliders 202 protruding along the circumferential direction are provided on the two radial sides of the permanent magnet mounting groove 203. Six pad mounting openings 105 for clamping the pads 2 are evenly distributed along the circumferential direction on the damper housing 1. Pad guide chutes 1051 are axially formed on the two side walls of the pad mounting opening 105. The outer edge of the pad 2 is axially slidably connected in the pad mounting opening 105 of the damper housing 1 through the cooperation of the guide sliders 202 and the pad guide chutes 1051, and is axially limited through the cooperation of the guide sliders 202 and the pad guide chutes 1051.

[0033] The electromagnetic mechanism includes an exciting coil 3, a C-shaped electromagnet iron core 4 and a permanent magnet 11. Two permanent magnets 11 with opposite poles facing each other (N pole inward and S pole outward) are fixedly connected in the permanent magnet mounting groove 203. A set screw hole 204 is formed on the pad 2 on one axial side of the permanent magnet mounting groove 203. The permanent magnet 11 is fixedly connected in the permanent magnet mounting groove 203 through the cooperation of a set screw 10 and the set screw hole 204; the two magnetic poles of the C-shaped electromagnet iron core 4 are respectively installed corresponding to the two axial end faces of the permanent magnet mounting groove 203, and a pre-compressed spring 12 is connected between the C-shaped electromagnet iron core 4 and the axial end face of the permanent magnet mounting groove 203. The exciting coil 3 is wound around a section of the C-shaped electromagnet iron core 4 corresponding to the permanent magnet 11 in the radial direction.

[0034] An electromagnet cover plate is installed in the gap between the C-shaped electromagnet iron core 4 and the tile mounting opening 105 on the damper housing 1. The electromagnet cover plate includes an electromagnet right cover plate 16 and an electromagnet left cover plate 17 that are symmetrically installed left and right along the circumferential direction. On the end face of the damper housing 1 corresponding to the bottom of the tile mounting opening 105 and on the inner end face of the sealing end cover 5, a first cover plate fixing groove 102 and a second cover plate fixing groove 501 are respectively clamped. The two ends of the electromagnet cover plate are respectively embedded in the first cover plate fixing groove 102 and the second cover plate fixing groove 501 for axial fixation.

[0035] One end of the damper housing 1 is a housing flange 101, and it is fixedly connected to an external load-bearing member through the housing flange 101. Six threaded counterbores 103 are evenly distributed along the circumferential direction on the other end face of the damper housing 1 away from the housing flange 101. Six through holes are evenly distributed along the circumferential direction on the sealing end cover 5. The sealing end cover 5 is fixedly connected to the damper housing 1 by fixing screws 14 passing through the through holes and being in threaded cooperation with the threaded counterbores 103.

[0036] An annular groove is provided on the inner circumferential surface of the sealing end cover 5, and a first sealing ring 9 is connected in the annular groove in a matching manner. The outer edge surface of the inner ring 6 of the damper oil film is hermetically connected to the sealing end cover 5 through the first sealing ring 9.

[0037] An inner flange 106 of the housing is axially arranged inward along the housing flange 101 on the damper housing 1. An annular groove is formed on the inner circumferential surface of the inner flange 106 of the housing, and a second sealing ring 13 is connected in the annular groove in a matching manner. The outer edge surface of the inner ring 6 of the damper oil film is hermetically connected to the inner flange 106 of the housing through the second sealing ring 13.

[0038] The inside of the inner ring 6 of the damper oil film is connected to a bearing 7 and a rotor through a bearing mounting hole 603 opened. One end away from the bearing mounting hole 603 is connected to an elastic support 602 and a mounting base 601, and is fixedly connected to an external load-bearing member through the mounting base 601.

[0039] One side of the inner ring 6 of the damper oil film where the bearing mounting hole 603 is provided is of a stepped shape, and the diameter of a section of the outer circumferential surface of the inner ring 6 of the damper oil film where it forms a seal with the sealing end cover 5 is smaller than the diameter of the inner ring 6 of the damper oil film where it forms an oil film cavity 8 with the tile 2.

[0040] Working principle:

[0041] Inside the bearing mounting hole 603 of the inner ring 6 of the damper oil film, there is a bearing 7 and a rotor installed. On the outside, there is a damper housing 1. The damper housing 1 is fixed to the external load-bearing member through the damper housing flange 101. Six tile mounting openings 105 on the circumferential direction of the damper housing 1 are respectively equipped with tiles 2 and electromagnets composed of a C-shaped electromagnet iron core 4 and an excitation coil 3 wound around it. The tiny gap between the tile 2 and the inner ring 6 of the damper oil film forms an oil film cavity 8. There is also a gap 15 left between two adjacent tiles 2 for the lubricating oil to flow through. The damper housing 1 has a radial oil inlet 104 at the position of the gap between two tiles 2. The lubricating oil enters from the oil inlet 104 into the gap 15 between the tiles and fills the oil film cavity 8 between the tile 2 and the inner ring 6 of the damper oil film through the circumferential oil guiding groove 201 of the tile 2, forming the damper oil film. When the vibration generated by the rotor is transmitted to the inner ring 6 of the damper oil film through the bearing 7, the inner ring 6 of the damper oil film generates a tiny radial displacement to squeeze the damper oil film to generate a reaction force.

[0042] The end of the damper housing 1 is fixedly connected with a sealing end cover 5 through a fixing screw 14. The electromagnet right cover plate 16 and the electromagnet left cover plate 17 above the tile mounting opening 105 and the sealing end cover 5 seal the tile mounting opening 105 and the oil film cavity 8. The tile 2 located in the tile mounting opening 105 realizes axial guidance through the cooperation of its own guiding slider 202 and the tile guiding chute 1051.

[0043] The two magnetic poles of the electromagnet composed of the C-shaped electromagnet iron core 4 and the excitation coil 3 wound around it are located at both ends of the permanent magnet mounting groove 203. There is a pre-compressed spring 12 installed between the magnetic poles and the tile 2. The tile 2 can move along the guiding chute 1051 between the two magnetic poles of the electromagnet, generating a displacement of up to about 10 mm. The excitation coil 3 is connected to an external controller. By controlling the magnitude and direction of the direct current applied to the electromagnet through the controller, different magnitudes and directions of electromagnetic fields can be generated between the two magnetic poles of the electromagnet. Using the electromagnetic force received by the permanent magnet 11 in the electromagnetic field, the tile 2 generates an axial displacement to change the axial width of the damper oil film formed between the inner ring 6 of the damper oil film and the tile 2.

[0044] When the external controller applies current to the electromagnet, making its left end the N pole and the right end the S pole, the tile 2 moves to the left, reducing the axial width of the oil film; when the external controller applies the opposite current to the electromagnet, the direction of the electromagnetic field changes, and the tile 2 moves to the right, increasing the axial width of the oil film.

[0045] According to the different magnitudes of the current applied by the external controller, the magnitude of the electromagnetic force received by the permanent magnet 11 in the electromagnetic field changes, and the spring 12 between the shoe 2 and the electromagnet pole reaches different stretching or compression amounts, resulting in different degrees of displacement of the shoe in the axial direction. The axial width of the oil film directly affects the stiffness damping characteristics of the squeeze film damper. As the axial position of the shoe 2 changes, the axial width of the damper oil film formed between the inner ring 6 of the damper oil film and the shoe 2 changes, providing different damping forces for the support of the rotor.

[0046] In the device of the present invention, by controlling the magnitude and direction of the current applied to the excitation coil, the axial width of the damper oil film can be adjusted within an extremely short time during the working state, which can eliminate the influence of the design, manufacturing, and assembly errors of the damper and the sudden change of working conditions on the damper performance; at the same time, the rotor system can change the oil film characteristics according to the working state, obtain high damping when passing through the critical speed, ensure the safety of the system; when operating at other speeds, it is subject to less damping, reducing the external transmission force on the support, thereby improving the stability of the system and extending the service life.

[0047] The above is only used to illustrate the technical solution of the present invention and not to limit it. Other modifications or equivalent replacements made by those of ordinary skill in the art to the technical solution of the present invention, as long as they do not depart from the spirit and scope of the technical solution of the present invention, shall be covered by the scope of the claims of the present invention.

Claims

1. An squeeze film damper capable of segmentally controlling the oil film width, characterized in that: It includes a damper oil film inner ring (6) sleeved on the outer ring of a bearing (7), a damper housing (1) and a sealing end cover (5) sleeved on the outer ring of the damper oil film inner ring (6). A plurality of shoe blocks (2) are evenly distributed along the circumferential direction between the damper housing (1) and the damper oil film inner ring (6). An oil film cavity (8) is arranged between the outer side of the shoe block (2) and the outer circumferential surface of the damper oil film inner ring (6) and is connected to an electromagnetic mechanism; The electromagnetic mechanism includes an exciting coil (3), a C-shaped electromagnet iron core (4) and a permanent magnet (11). A permanent magnet mounting groove (203) is convexly arranged on the radially outer end surface of the shoe block (2). Two permanent magnets (11) with opposite poles are fixedly connected in the permanent magnet mounting groove (203). Two magnetic poles of the C-shaped electromagnet iron core (4) are respectively arranged corresponding to the two axial end surfaces of the permanent magnet mounting groove (203), and a spring (12) is connected between the C-shaped electromagnet iron core (4) and the axial end surface of the permanent magnet mounting groove (203). The exciting coil (3) is wound around a section of the C-shaped electromagnet iron core (4) corresponding to the permanent magnet (11) in the radial direction; Guide sliders (202) protruding along the circumferential direction are arranged on the two radial sides of the permanent magnet mounting groove (203). A plurality of shoe block mounting openings (105) for clamping the shoe block (2) are evenly distributed along the circumferential direction on the damper housing (1). Shoe block guide chutes (1051) are arranged along the axial direction on the two side walls of the shoe block mounting opening (105). The outer edge of the shoe block (2) is axially fitted in the damper housing (1) through the cooperation of the guide slider (202) and the shoe block guide chute (1051); 2. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1, characterized in that: A gap (15) for lubricating oil to flow through is arranged between two adjacent shoe blocks (2). An oil inlet hole (104) is arranged on the outer side wall of the damper housing (1) in the radial direction, and the oil inlet hole (104) is communicated with the gap (15) between the shoe blocks; 3. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1 or 2, characterized in that: A circumferential oil guide groove (201) is arranged along the circumferential direction on the inner arc-shaped curved surface of the shoe block (2). The gap between the circumferential oil guide groove (201) and the outer circumferential surface of the damper oil film inner ring (6) forms the oil film cavity (8); 4. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1, characterized in that: An electromagnet cover plate is arranged in the gap between the C-shaped electromagnet iron core (4) and the shoe block mounting opening (105) on the damper housing (1). The electromagnet cover plate includes an electromagnet right cover plate (16) and an electromagnet left cover plate (17) symmetrically arranged left and right along the circumferential direction. A first cover plate fixing groove (102) and a second cover plate fixing groove (501) for clamping and fixing the electromagnet cover plate are respectively arranged on the end surface of the damper housing (1) corresponding to the bottom of the shoe block mounting opening (105) and on the inner end surface of the sealing end cover (5); 5. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1, characterized in that: A set screw hole (204) is arranged on the shoe block (2) on one axial side of the permanent magnet mounting groove (203). The permanent magnet (11) is fixedly connected in the permanent magnet mounting groove (203) through the cooperation of a set screw (10) and the set screw hole (204).

6. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1, characterized in that: One end of the damper housing (1) is a housing flange (101), and it is fixedly connected to an external load-bearing member through the housing flange (101). A plurality of threaded counterbores (103) are evenly distributed along the circumferential direction on the other end face of the damper housing (1) away from the housing flange (101); a plurality of through holes are evenly distributed along the circumferential direction on the sealing end cover (5), and the sealing end cover (5) is fixedly connected to the damper housing (1) through the fixing screws (14) passing through the through holes and being in threaded fit with the threaded counterbores (103).

7. The squeeze film damper capable of segmentally controlling the oil film width according to claim 6, characterized in that: An annular groove is provided on the inner circumferential surface of the sealing end cover (5), and a first sealing ring (9) is connected in the annular groove in a mating manner. The outer edge surface of the damper oil film inner ring (6) and the sealing end cover (5) are hermetically connected through the first sealing ring (9).

8. The squeeze film damper capable of segmentally controlling the oil film width according to claim 6, characterized in that: A housing inner flange (106) is provided axially inward along the housing flange (101) on the damper housing (1). An annular groove is provided on the inner circumferential surface of the housing inner flange (106), and a second sealing ring (13) is connected in the annular groove in a mating manner. The outer edge surface of the damper oil film inner ring (6) and the housing inner flange (106) are hermetically connected through the second sealing ring (13).

9. The squeeze film damper capable of segmentally controlling the oil film width according to claim 1, characterized in that: The inside of the damper oil film inner ring (6) is connected to a bearing (7) and a rotor through a bearing installation hole (603). Elastic supports (602) and an installation base (601) are provided at one end away from the bearing installation hole (603), and it is fixedly connected to an external load-bearing member through the installation base (601); one side of the damper oil film inner ring (6) where the bearing installation hole (603) is provided is of a stepped type, and the diameter of a section of the outer circumferential surface of the damper oil film inner ring (6) where it forms a seal with the sealing end cover (5) is smaller than the diameter of the damper oil film inner ring (6) where it forms an oil film cavity (8) with the shoe (2).

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