A thrust bearing, method of making the same, and a rotor system

Abstract

The application provides a thrust bearing, a manufacturing method thereof and a rotor system, wherein the thrust bearing comprises: a thrust disc, one end surface of the thrust disc is used for being connected with one end of a rotating shaft, and a magnetic bearing is arranged on the side of the thrust disc away from the rotating shaft; a first stator and a second stator are respectively arranged on the two sides of the thrust disc, the first stator is sleeved on the magnetic bearing, and the second stator is sleeved on the rotating shaft; and the thrust disc can move in the axial direction of the rotating shaft under the magnetic force of the magnetic bearing. By arranging the bearing gap and the magnetic bearing in the thrust bearing, the thrust bearing forms a gas-magnetic hybrid thrust bearing, the dynamic performance and stability of the thrust bearing in the high-speed operation state can be improved, the anti-disturbance ability is high, and the carrying capacity of the thrust bearing is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of bearings, in particular to a thrust bearing, a manufacturing method thereof and a rotor system. BACKGROUND

[0002] A gas turbine mainly comprises a compressor, a combustion chamber and a turbine. After entering the compressor, air is compressed into high-temperature and high-pressure air, and then is supplied to the combustion chamber to mix and burn with fuel. The high-temperature and high-pressure gas generated by the combustion is expanded in the turbine to do work. When the rotor rotates at a high speed, the rotor will be subjected to an axial force. In order to limit the axial movement of the rotating shaft, a thrust bearing needs to be installed in the rotor system. The conventional thrust bearing is a common contact bearing. With the increase of the rotating speed of the rotor, especially when the rotating speed of the rotor exceeds 40,000 rpm, the common contact bearing cannot meet the demand of the working speed due to the existence of large mechanical wear. Therefore, a non-contact bearing needs to be used to replace the contact bearing.

[0003] In the prior art, the non-contact bearing generally comprises a magnetic bearing and an air bearing. However, the magnetic bearing has the problems of too large energy consumption and heat generation when it is turned on for a long time. When the surface linear speed of the air bearing approaches or exceeds the speed of sound, a shock wave will be generated, which will cause the instability of the bearing and even catastrophic consequences such as shaft collision. It can be seen that the above two kinds of non-contact bearings cannot be applied to high-speed gas turbines or gas turbine combined units.

[0004] Therefore, it is urgent to provide a new thrust bearing and a rotor system to solve the above problems. SUMMARY

[0005] The present application provides a thrust bearing, a manufacturing method thereof and a rotor system to solve the above problems.

[0006] In a first aspect, the present application provides a thrust bearing for being installed on a rotating shaft, the thrust bearing comprising:

[0007] a thrust disc, one end surface of the thrust disc being used for being connected with the rotating shaft, and a side of the thrust disc away from the rotating shaft being provided with a magnetic bearing;

[0008] a first stator and a second stator respectively provided on two sides of the thrust disc, the first stator and the thrust disc having a first gap therebetween, the second stator and the thrust disc having a second gap therebetween, the first stator being sleeved on the magnetic bearing, and the second stator being sleeved on the rotating shaft;

[0009] wherein the thrust disc is capable of moving in the axial direction of the rotating shaft under the magnetic force of the magnetic bearing.

[0010] In a second aspect, the present application provides a manufacturing method of a thrust bearing, comprising:

[0011] The thrust disc and the stator are manufactured, and the stator comprises a first stator and a second stator;

[0012] The thrust disc is fixedly installed with the rotating shaft to form a thrust disc rotating shaft assembly;

[0013] The thrust disc rotating shaft assembly is processed to make the end surface of the thrust disc and the circumferential surface of the rotating shaft have a perpendicularity within 0.1 microns;

[0014] The first stator is assembled to the bearing shell, and is installed into the thrust disc rotating shaft assembly, and the second stator is sleeved on the rotating shaft.

[0015] In a third aspect, the present application provides a rotor system, comprising:

[0016] A rotating shaft;

[0017] A thrust bearing, one end surface of a thrust disc of the thrust bearing is connected with one end portion of the rotating shaft, a magnetic bearing is arranged on the side of the thrust disc away from the rotating shaft, one stator of the thrust bearing is sleeved on the rotating shaft, and another stator of the thrust bearing is sleeved on the magnetic bearing;

[0018] A first radial bearing, a motor, a compressor, a second radial bearing and a turbine are sequentially arranged on the rotating shaft, and the first radial bearing is located on the rotating shaft close to the thrust bearing, and the first radial bearing and the second radial bearing are both non-contact radial bearings.

[0019] In a fourth aspect, the present application provides another rotor system, comprising:

[0020] A first rotating shaft;

[0021] A thrust bearing, one end surface of a thrust disc of the thrust bearing is connected with one end portion of the first rotating shaft, a magnetic bearing is sleeved on a shaft coupling connector arranged on the end surface of the thrust disc away from the rotating shaft, one stator of the thrust bearing is sleeved on the first rotating shaft, and another stator of the thrust bearing is sleeved on the magnetic bearing;

[0022] A compressor, a first radial bearing and a turbine are sequentially arranged on the first rotating shaft, the compressor is located on the first rotating shaft close to the thrust bearing, and the thrust bearing is spaced apart from the compressor by a predetermined distance, so that the thrust bearing does not block the air inlet of the compressor;

[0023] A second rotating shaft, one end portion of the second rotating shaft is connected with the shaft coupling connector through a shaft coupling;

[0024] A second radial bearing, a motor and a third radial bearing are sequentially arranged on the second rotating shaft.

[0025] The first radial bearing, the second radial bearing and the third radial bearing are all non-contact radial bearings.

[0026] In the present application, the bearing gap and the magnetic bearing are arranged in the thrust bearing, so that the thrust bearing forms a gas-magnetic hybrid thrust bearing. Thus, as the gas bearing and the magnetic bearing can work cooperatively, the dynamic performance and stability of the thrust bearing under high-speed operation state can be improved, the anti-disturbance ability is strong, and the carrying capacity of the thrust bearing is improved. It can be seen that the thrust bearing of the present application can meet the needs of high-speed gas turbines or gas turbine generator combined units. BRIEF DESCRIPTION OF DRAWINGS

[0027] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings needed to be used in the description of the embodiments of the present application will be briefly introduced. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor.

[0028] Figure 1 is a structural schematic diagram of a thrust bearing provided by the embodiment of the present application;

[0029] Figure 2 is a structural schematic diagram of another thrust bearing provided by the embodiment of the present application;

[0030] Figures 3-4 is a structural schematic diagram of a dynamic pressure generating groove;

[0031] Figure 5 is a structural schematic diagram of another thrust bearing provided by the embodiment of the present application;

[0032] Figures 6-7 is a structural schematic diagram of a bearing damper adjusting member;

[0033] Figures 8-19 is a structural schematic diagram of a rotor system provided by the embodiment of the present application. DETAILED DESCRIPTION

[0034] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only some embodiments of the present application, not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the present application.

[0035] As Figure 1As shown, the embodiment of the present application provides a thrust bearing 700, which comprises:

[0036] A thrust disc 710, one end surface of the thrust disc 710 is used for connecting with one end of the rotating shaft 100, and a magnetic bearing 740 is arranged on the side of the thrust disc 710 away from the rotating shaft 100;

[0037] A first stator 720 and a second stator 730 are arranged on both sides of the thrust disc 710 respectively, the first stator 720 has a first gap with the thrust disc 710, and the second stator 730 has a second gap with the thrust disc 710, the first stator 720 is sleeved on the magnetic bearing 740, and the second stator 730 is sleeved on the rotating shaft 100;

[0038] Wherein, the thrust disc 710 can move in the axial direction of the rotating shaft 100 under the magnetic force of the magnetic bearing 740.

[0039] The thrust disc 710 can be provided with a magnetic component, for example, a magnetic component can be arranged on the end surface of the thrust disc 710 facing the magnetic bearing 740; or the thrust disc 710 is made of a magnetic conductive material, for example, 40CrMo.

[0040] The connection between the thrust disc 710 and the rotating shaft 100 can be realized by a matching connection structure, or by welding, one-piece forming process, or by a connecting piece, a fastener and the like.

[0041] As shown in the embodiment of the present application, Figure 2 As shown in the embodiment of the present application, Figure 1 On the basis of the thrust bearing 700 shown in the embodiment of the present application, the end surface of the thrust disc 710 close to the magnetic bearing 740 is provided with a shaft coupling connecting piece 712, the magnetic bearing 740 is sleeved on the shaft coupling connecting piece 712, and the shaft coupling connecting piece 712 is used for connecting a shaft coupling.

[0042] Wherein, the shaft coupling connecting piece 712 can be fixedly connected with the thrust disc 710, or can be integrally formed with the thrust disc 710.

[0043] In this way, the thrust bearing 700 of the embodiment of the present application can be applied to a single-shaft rotor system, and the thrust bearing 700 is arranged at one end of the rotor system; or can be applied to a double-shaft rotor system connected by a shaft coupling, and the thrust bearing 700 is arranged between the two rotating shafts 100 of the rotor system.

[0044] In the embodiment of the present application, the gaps between the thrust disc 710 and the first stator 720 and the second stator 730 form a gas bearing, the gas bearing and the magnetic bearing work cooperatively to form a gas-magnetic hybrid bearing, thereby improving the carrying capacity of the thrust bearing, and the bearing has high movement precision and is easy to control, and the structure and control system are simple.

[0045] The following other embodiments of the thrust bearing are applicable to Figure 1 The thrust bearing shown in the figure is also applicable to Figure 2 The thrust bearing shown in the figure, and has the same beneficial effects.

[0046] Optionally, the end surface of the thrust disc 710 is provided with a protruding shaft connecting part 711, and the thrust disc 710 is connected with the shaft 100 through the shaft connecting part 711.

[0047] The shaft connecting part 711 can be fixedly connected with the thrust disc 710, or can be integrally formed with the thrust disc 710. The connection between the shaft connecting part 711 and the shaft 100 can be achieved by using a matching connection structure, or can be achieved by using welding, integral molding and the like, or can be achieved by using a connecting piece, a fastener and the like.

[0048] Optionally, the end of the shaft 100 is provided with a connecting hole, and the shaft connecting part 711 is inserted into the connecting hole to achieve the connection between the thrust disc 710 and the shaft 100.

[0049] The connection mode of inserting the shaft connecting part 711 into the connecting hole of the shaft 100 can improve the stability of the connection between the shaft connecting part 711 and the shaft 100, thereby improving the connection strength between the thrust disc 710 and the shaft 100.

[0050] Optionally, the magnetic bearing 740 includes a coil 741 electrically connected with a controller 742, and the controller 742 is used to control the on-off and size of the current in the coil 741.

[0051] Here, the controller 742 can pre-store a control program for controlling the magnetic bearing 740, or can control the magnetic bearing 740 by detecting various parameters detected by a detection element.

[0052] Optionally, the controller 742 is used to control the on-off and size of the current in the coil 741 according to a preset control program.

[0053] The controller 742 can pre-store a control program for controlling the magnetic bearing 740, and the controller 742 controls the on-off and size of the current in the coil 741 according to the preset control program during the entire working process of the thrust bearing. This can be understood as that the magnetic bearing 740 in the thrust bearing of the embodiment of the application adopts open-loop control, and compared with the control mode by detecting parameters, the open-loop control is beneficial to simplify the control system.

[0054] In the embodiment of the application, the gas bearing of the thrust bearing 700 can be a static pressure gas bearing, or can be a dynamic pressure gas bearing, or can be a dynamic-static pressure hybrid gas bearing.

[0055] When the gas bearing of the thrust bearing 700 is a static pressure gas bearing, as shown in Figures 1-2 a first static pressure air inlet throttle hole 721 is arranged on the first stator 720 to connect the external air source with the first gap, and a second static pressure air inlet throttle hole 731 is arranged on the second stator 730 to connect the external air source with the second gap.

[0056] The flow diameters of the first static pressure air inlet throttle hole 721 and the second static pressure air inlet throttle hole 731 can be adjusted according to the actual working conditions such as the air volume requirement.

[0057] When the gas bearing of the thrust bearing 700 is a dynamic pressure gas bearing, the end face of the thrust disc 710 facing the first stator 720 and the second stator 730, or the end face of the first stator 720 and the second stator 730 facing the thrust disc 710 is provided with a dynamic pressure generation groove.

[0058] When the thrust disc 710 rotates at a high speed, the flowing gas existing in the bearing gap (including the first gap and the second gap) is pressed into the dynamic pressure generation groove, so as to generate pressure, thereby realizing the non-contact retention of the thrust disc 710 in the axial direction. The size of the pressure generated by the dynamic pressure generation groove varies with the angle, groove width, groove number, length, depth and flatness of the dynamic pressure generation groove. In addition, the size of the air dynamic pressure generated in the dynamic pressure generation groove is also related to the rotation speed of the thrust disc and the bearing gap. The parameters of the dynamic pressure generation groove can be designed according to the actual working conditions.

[0059] In the embodiment of the present application, as shown in Figures 3-4 the dynamic pressure generation groove 741 can be arranged in a radial manner or a concentric circular manner. In this way, it is beneficial to make the gas film more uniformly distributed in the bearing gap.

[0060] In the embodiment of the present application, the dynamic pressure generation groove 741 can include a first spiral groove 7411 and a second spiral groove 7412, the first spiral groove 7411 surrounds the second spiral groove 7412, the spiral directions of the first spiral groove 7411 and the second spiral groove 7412 are opposite, and one end of the first spiral groove 7411 close to the second spiral groove 7412 is connected or disconnected with one end of the second spiral groove 7412 close to the first spiral groove 7411.

[0061] In the embodiment of the present application, by adopting the above-mentioned arrangement mode of the dynamic pressure generation groove, the thrust disc can be non-contactly retained in the desired manner in the case of forward rotation or reverse rotation of the rotating shaft, thereby making the rotating shaft have the advantages of high load capacity and good stability.

[0062] When the gas bearing of the thrust bearing 700 is a mixed gas bearing with dynamic and static pressure, the thrust bearing 700 is provided with both a dynamic pressure generating groove and a static pressure inlet throttling orifice. Since the dynamic pressure generating groove and the static pressure inlet throttling orifice have already been described separately above, they will not be repeated here to avoid repetition.

[0063] The thrust bearing 700 in this embodiment of the invention can also be a thrust bearing 700 capable of actively correcting bearing clearance.

[0064] like Figure 5 As shown, in the first stator 720 and the second stator 730, each stator includes a stator body, a pressure plate 760 and a bearing damper 750. The bearing damper 750 is disposed between the stator body and the pressure plate 760, and the pressure plate 760 is disposed on the side of the stator body near the thrust plate 710.

[0065] The bearing damper 750 is made of shape memory material and can undergo plastic deformation under the action of the pressure plate 760 to adjust the bearing clearance, which includes a first clearance and a second clearance.

[0066] The bearing damper 750 can be made of shape memory metal or shape memory polymer, wherein the shape memory metal can be any one of titanium-nickel alloy, copper-zinc alloy, copper-aluminum-nickel alloy, copper-molybdenum-nickel alloy, and copper-gold-zinc alloy. If the bearing operates in a high-temperature environment, the bearing damper 750 can be made of a high-temperature resistant (e.g., above 300°C) shape memory metal.

[0067] Due to machining or assembly errors, before the thrust bearing 700 operates, there is a non-parallelism between the first stator 720 or the second stator 730 and the thrust disk 710, resulting in uneven clearance between them. During the operation of the thrust bearing 700, the pressure plate 760 adjusts its position and orientation under the combined action of air film pressure and the load of the shaft 100. The pressure plate 760 compresses the bearing damper 750 on the side with the smaller clearance, causing corresponding plastic deformation. This supports the pressure plate 760 in a position parallel to the thrust disk 710, correcting the uniformity of the bearing clearance and thus meeting the requirement for smooth bearing operation.

[0068] In the embodiment of the present application, the bearing damper can include at least two adjustment units, and the bearing damper can be an integral device formed by continuously arranging the at least two adjustment units, or can include at least two independently arranged adjustment members, which can include at least one adjustment unit. For example, one adjustment unit is one adjustment member, two adjustment units form one adjustment member, three adjustment units form one adjustment member, and so on. It can be understood that when one adjustment unit forms one adjustment member, the adjustment unit is equivalent to the adjustment member. When the bearing damper is an integral device formed by continuously arranging the at least two adjustment units, on the one hand, the installation can be faster; on the other hand, bearings of different sizes or types can need to be configured with different types of bearing dampers, and the application range is relatively limited. When the bearing damper includes at least two independently arranged adjustment members, the independently arranged adjustment members can be applicable to any bearing, and only a proper number of adjustment members need to be configured according to the size or type of the bearing, or the multiple adjustment members can be arranged in a shape suitable for the bearing.

[0069] In the embodiment of the present application, as shown in Figures 6-7 The adjustment unit can be a half-shell structure including a protruding part 751 and a supporting part 752, and the protruding part 751 and the supporting part 752 are integrally formed. The outer surface of the protruding part 751 is a smooth arc-shaped curved surface, and the supporting part 752 smoothly extends from the protruding part 751 to the periphery. The entire adjustment unit can take the protruding part 751 as a part that generates plastic deformation of the adjustment unit, and the supporting part 752 can serve as a part that supports the entire adjustment unit. The adjustment unit is arranged in the above-mentioned half-shell structure, so that the adjustment unit is in a relatively stable state before and after being stressed. When arranged, the protruding part 751 faces the pressing plate 760, and the supporting part 752 is arranged in close contact with the stator body 722. The protruding part 751 can be plastically deformed under the action of the pressing plate 760 to adjust the bearing gap.

[0070] In addition to the above-mentioned half-shell structure, the adjustment unit can also be a wave-shaped structure, a sawtooth-shaped structure, a spherical shell structure, a half-spherical shell structure, and the like.

[0071] In the embodiment of the present application, in order to make the adjustment unit have better plastic deformation performance, the thickness of the adjustment unit should not be too large; in order to make the adjustment unit have relatively stable mechanical properties, the height of the adjustment unit should not be too large. The height H of the adjustment unit can be between 1 mm and 3 mm, and the thickness L of the adjustment unit can be between 0.1 mm and 0.3 mm.

[0072] In the embodiment of the application, the adjusting members can be uniformly distributed along the end surfaces of the first stator body and the second stator body in the circumferential direction to form the bearing dampers 750 arranged in a ring shape; the adjusting members can also be uniformly distributed along the end surfaces of the first stator body and the second stator body in the radial direction to form the bearing dampers 750 arranged in a linear shape; or the adjusting members can be uniformly distributed along the end surfaces of the first stator body and the second stator body in the circumferential direction and in the axial direction, respectively, so that the adjusting members are distributed in multiple circles along the end surfaces of the first stator body and the second stator body, respectively, to form the bearing dampers arranged in a multi-ring shape. The above-mentioned arrangement modes of the adjusting members can make the adjustment process of the bearing gap more stable and make the bearing gap more uniform.

[0073] In the thrust bearing 700 with the above-mentioned structure, the dynamic pressure generating groove can be arranged on the end surface of the pressure plate 760 facing the thrust disc 710.

[0074] In the thrust bearing 700 with the above-mentioned structure, the first static pressure air inlet throttle hole 721 can pass through the first stator body, the bearing damper 750 and the pressure plate 760 in sequence to communicate the bearing gap with the external air source; and the second static pressure air inlet throttle hole 731 can pass through the second stator body, the bearing damper 750 and the pressure plate 760 in sequence to communicate the bearing gap with the external air source.

[0075] For the thrust bearing provided with the static pressure gas bearing, the working process of the thrust bearing can include the following steps:

[0076] S1: The static pressure gas bearing is started, and the thrust disc reaches a predetermined position between the first stator and the second stator under the action of the static pressure gas bearing. There is a gap between the thrust disc and the end surfaces of the first stator and the second stator. Under the driving of the rotating shaft, the thrust disc starts to rotate relative to the first stator and the second stator under lubrication to prevent wear.

[0077] S2: In the acceleration stage, the thrust disc accelerates with the acceleration of the rotating shaft, and the axial load also increases accordingly. When a predetermined rotating speed is reached, the controller controls the magnetic bearing to be started, and the magnetic bearing and the static pressure gas bearing jointly support the axial load.

[0078] S3: In the shutdown stage, the thrust disc decelerates with the deceleration of the rotating shaft, and the axial load also decreases accordingly. When the rotating speed is lower than the predetermined rotating speed, the controller controls the magnetic bearing to be turned off, and the static pressure gas bearing is turned off until the thrust disc is completely stopped.

[0079] The predetermined rotating speed is 5% to 30% of the rated rotating speed.

[0080] During the starting of the magnetic bearing, the controller adjusts the size of the current in the coil according to a preset operation program, so that the magnetic bearing adapts to the change of the axial force borne by the thrust bearing.

[0081] It should be noted that for the thrust bearing without the static pressure gas bearing, in step S1, the magnetic bearing can be controlled to be turned on by the controller so that the thrust disc reaches the predetermined position between the first stator and the second stator under the action of the magnetic bearing. In step S3, the magnetic bearing is controlled to be turned off by the controller until the thrust disc is completely stopped.

[0082] For the gas thrust bearing, the gap between the thrust disc and the stator directly affects the stability of the gas bearing, and therefore, the gas bearing has high requirements for the flatness of the end surface of the thrust disc, the flatness of the end surface of the stator, and the parallelism between the end surfaces of the thrust disc and the stator. The manufacturing method of the conventional thrust bearing is to assemble the thrust disc and the rotating shaft after they are machined in place. Since the thrust disc and the rotating shaft can be slightly deformed during the assembly process, and the gap between the thrust disc and the stator is uneven due to the limitation of the assembly precision, the overall running stability of the gas bearing is not high.

[0083] To solve the above problems, the manufacturing method of the thrust bearing provided by the embodiments of the present application includes the following steps:

[0084] S1: manufacturing a thrust disc, a stator and a rotating shaft, wherein the stator includes a first stator and a second stator.

[0085] S2: fixedly mounting the thrust disc and the rotating shaft to form a thrust disc-rotating shaft assembly.

[0086] S3: machining the thrust disc-rotating shaft assembly so that the perpendicularity between the end surface of the thrust disc and the circumferential surface of the rotating shaft is within 0.1 microns.

[0087] S4: assembling the first stator to a bearing housing, and loading the thrust disc-rotating shaft assembly into the bearing housing, and then sleeving the second stator on the rotating shaft.

[0088] The method for manufacturing the thrust disc includes the following steps:

[0089] S111: providing a thrust disc blank, and rough machining the thrust disc blank;

[0090] S112: quenching the thrust disc blank so that the hardness of the thrust disc blank is higher than or equal to 55HRC (Rockwell hardness);

[0091] S113: finish machining the thrust disc blank so that the parallelism between the two end surfaces of the thrust disc is within 0.1 microns, the maximum unevenness of any end surface of the thrust disc is less than or equal to 0.5 microns, and the flatness is within 1 micron.

[0092] The method for manufacturing the stator comprises the following steps:

[0093] S121: providing a stator blank, and rough machining the stator blank;

[0094] S122: quenching the stator blank, so that the hardness of the stator blank is higher than or equal to 55HRC;

[0095] S123: finish machining the stator blank, so that the parallelism between the two end faces of the stator is within 0.1 microns, the maximum unevenness of at least the end face of the stator facing the thrust disc is less than or equal to 0.5 microns, and the flatness is within 1 micron.

[0096] The method for manufacturing the rotating shaft comprises the following steps:

[0097] S131: providing a rotating shaft blank, and rough machining the rotating shaft blank;

[0098] S132: quenching the rotating shaft blank, so that the hardness of the rotating shaft blank is higher than or equal to 55HRC.

[0099] When the thrust bearing is a static pressure gas bearing, a static pressure air inlet throttle hole is further arranged on the stator, and the method for manufacturing the stator further comprises the following step:

[0100] S124: machining at least one static pressure air inlet throttle hole on the stator.

[0101] When the thrust bearing is a dynamic pressure gas bearing, a dynamic pressure generation groove is further arranged on the stator or the thrust disc. For the case of arranging the dynamic pressure generation groove on the stator, the method for manufacturing the stator further comprises the following step:

[0102] S125: machining a dynamic pressure generation groove on the end face of the stator facing the thrust disc.

[0103] For the case of arranging the dynamic pressure generation groove on the thrust disc, the method for manufacturing the thrust disc further comprises the following step:

[0104] S114: machining a dynamic pressure generation groove on the two end faces of the thrust disc.

[0105] Optionally, the machining of the dynamic pressure generation groove in steps S125 and S114 can be performed by etching, which comprises the following steps:

[0106] S1141: sequentially cleaning the to-be-machined part with carbon tetrachloride or trichloroethylene, acetone, and alcohol;

[0107] S1142: coating a photosensitive resist on the to-be-machined end face of the to-be-machined part;

[0108] S1143: The part to be processed is dried at a temperature of 70°C to 90°C for 20 to 40 minutes, for example, the part to be processed is dried at a temperature of 80°C for 30 minutes;

[0109] S1144: Place a mask plate with a dynamic pressure generating groove above a high-pressure mercury lamp, and place the end face of the part to be processed with the groove on the mask plate for exposure. For example, use a high-pressure mercury lamp with a voltage of 1kV and a current of 1A for 20 minutes.

[0110] S1145: Develop using developer;

[0111] S1146: The part to be processed is dried at a temperature of 70°C to 90°C for 20 to 40 minutes, for example, the part to be processed is dried at a temperature of 80°C for 30 minutes;

[0112] The component to be processed is the stator or the thrust disk; the dynamic pressure generating groove on the mask plate is a mirror image of the dynamic pressure generating groove formed on the component to be processed.

[0113] The thrust bearings manufactured using the above process have high rotational accuracy, meeting the requirements for high-speed and stable operation of bearings.

[0114] Embodiments of the present invention also provide a rotor system using the aforementioned thrust bearing.

[0115] like Figure 8 As shown, the rotor system includes:

[0116] Shaft 100;

[0117] The thrust bearing 700 has one end face of its thrust disk connected to one end of the rotating shaft 100. A magnetic bearing is provided on the side of the thrust disk away from the rotating shaft 100. One stator of the thrust bearing 700 is sleeved on the rotating shaft 100, and the other stator of the thrust bearing 700 is sleeved on the magnetic bearing.

[0118] The first radial bearing 500, motor 400, compressor 300, second radial bearing 610 and turbine 200 are sequentially arranged on the rotating shaft 100. The first radial bearing 500 is located on the rotating shaft 100 near the thrust bearing 700. Both the first radial bearing 500 and the second radial bearing 610 are non-contact radial bearings.

[0119] like Figure 9 As shown, the rotor system includes:

[0120] First rotating shaft 100;

[0121] A thrust bearing 700 has one end face of its thrust disc connected to one end of the first rotating shaft 100. A coupling is provided on the end face of the thrust disc away from the rotating shaft 100. A magnetic bearing is sleeved on the coupling. One stator of the thrust bearing 700 is sleeved on the first rotating shaft 100, and the other stator of the thrust bearing 700 is sleeved on the magnetic bearing.

[0122] A compressor 300, a first radial bearing 500, and a turbine 200 are sequentially arranged on a first rotating shaft 100. The compressor 300 is located on the first rotating shaft 100 near the thrust bearing 700. The thrust bearing 700 and the compressor 300 are spaced at a predetermined distance so that the thrust bearing 700 does not block the air inlet of the compressor 300.

[0123] The second rotating shaft 101 has one end connected to the coupling connector via a coupling 102.

[0124] A second radial bearing 610, a motor 400, and a third radial bearing 620 are sequentially mounted on the second rotating shaft 101.

[0125] The first radial bearing 500, the second radial bearing 610, and the third radial bearing 620 are all non-contact radial bearings.

[0126] The predetermined distance between the thrust bearing 700 and the compressor 300 can be 0.5 to 2 times the height of the blades at the air inlet of the compressor 300 impeller, but is not limited to this. Its specific dimensions can be designed according to the specific parameters of the compressor 300 and the thrust bearing 700.

[0127] Figure 8 The rotor system shown is compared to Figure 9 The rotor system shown eliminates the coupling, with the generator 400 and turbine 200 mounted coaxially, resulting in a simple structure and high transmission efficiency.

[0128] Since the thrust bearing 700 is a gas-magnetic hybrid thrust bearing, placing the thrust bearing 700 at the cold end and spacing it at a predetermined distance from the compressor 300 can prevent the thrust bearing 700 from blocking the air inlet of the compressor 300.

[0129] In this embodiment of the invention, the compressor 300 can be a centrifugal compressor 300, the turbine 200 can be a centrifugal turbine, the motor 400 can be a hydrodynamic bearing motor, and the part of the rotating shaft corresponding to the bearing of the motor 400 can be provided with a first hydrodynamic generating groove.

[0130] Furthermore, the motor 400 can also be an integrated starter motor.

[0131] In this way, at the initial starting moment of the rotor system, the motor 400 can be started in the starting mode to drive the rotor system, and when the rotating speed of the rotor system reaches the preset rotating speed, the working mode of the motor 400 can be switched to the power generation mode.

[0132] The rotor system shown in Figure 8 is taken as an example to further illustrate other embodiments of the rotor system.

[0133] As shown in Figure 10 , a third radial bearing 620 can be further arranged between the motor 400 and the compressor 300 to improve the stability of the rotor system. The third radial bearing 620 is a non-contact radial bearing.

[0134] Optionally, the first radial bearing 500 is a dynamic-static pressure hybrid radial bearing combining a gas static pressure radial bearing and a gas dynamic pressure radial bearing.

[0135] Optionally, the second radial bearing 610 and the third radial bearing 620 are gas-magnetic hybrid radial bearings.

[0136] The rotor system shown in Figure 9 is taken as an example to further illustrate other embodiments of the rotor system.

[0137] As shown in Figure 11 , a fourth radial bearing 630 can be further arranged between the thrust bearing 700 and the compressor 300 to improve the stability of the rotor system. The fourth radial bearing 630 is a non-contact radial bearing.

[0138] For a light turbine, such as a turbine made of ceramic material, ceramic fiber composite material, etc., when the diameter of the thrust disc of the thrust bearing 700 is small, and the situation of blocking the gas turbine inlet is not serious, the rotor system shown in Figures 12-13 can be used. The diameter of the thrust disc of the thrust bearing 700 of the rotor system is small, and the thrust bearing 700 does not block the gas turbine inlet. The predetermined distance between the thrust bearing 700 and the compressor 300 can be reduced, that is, the axial length of the entire rotor system is shortened, and the stability of the rotor system is improved.

[0139] Optionally, on the basis that the first radial bearing 500 is a dynamic-static pressure hybrid radial bearing combining a gas static pressure radial bearing and a gas dynamic pressure radial bearing, a magnetic element is added to form a gas-magnetic hybrid radial bearing. The structure of the gas-magnetic hybrid radial bearing is basically the same as that of the second radial bearing 610 and the third radial bearing 620, and the only difference is that the magnetic element is not arranged at the position close to the turbine 200 of the first radial bearing 500 because the magnetic element is not resistant to high temperature. Figures 14-19 The rotor systems corresponding to Figures 8-13 are respectively shown one by one.

[0140] To protect the magnetic elements on the first radial bearing 500, the heat energy radiated from the turbine 200 to the first radial bearing 500 can be reduced. Specifically, a heat insulation layer is arranged on the side of the turbine 200 close to the first radial bearing 500. Here, the heat insulation layer can be aerogel or other materials.

[0141] When the rotor system is applied to a gas turbine generator set whose fuel is hydrogen, methanol, ethanol, glycol or other alcohol gases, the first radial bearing 500 is preferably a gas dynamic and static pressure hybrid radial bearing. Since the above-mentioned fuel combustion process will not produce oil stains or impurities, etc., the selection of the gas dynamic and static pressure hybrid radial bearing can not only avoid the dry friction of the pure dynamic pressure bearing in the opening and closing stages, but also avoid the wear of the rotating shaft and the bearing. At the same time, the static pressure throttle hole of the static pressure bearing will not be blocked by oil stains.

[0142] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto, and any person skilled in the art can easily think of changes or replacements within the technical range disclosed by the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A thrust bearing for mounting on a rotating shaft, characterized by The thrust bearing comprises: A thrust disc, one end surface of the thrust disc is used for connecting with one end of the rotating shaft, and a magnetic bearing is arranged on the side of the thrust disc away from the rotating shaft; A first stator and a second stator are respectively arranged on the two sides of the thrust disc, the first stator has a first gap with the thrust disc, the second stator has a second gap with the thrust disc, the first stator is sleeved on the magnetic bearing, and the second stator is sleeved on the rotating shaft; The thrust disc can move in the axial direction of the rotating shaft under the magnetic force of the magnetic bearing; An end surface of the thrust disc close to the magnetic bearing is provided with a coupling connector, the magnetic bearing is sleeved on the coupling connector, and the coupling connector is used for connecting a coupling; An end surface of the thrust disc is provided with a protruding rotating shaft connecting part, an end of the rotating shaft is provided with a connecting hole, and the rotating shaft connecting part is inserted into the connecting hole to realize the connection between the thrust disc and the rotating shaft; The magnetic bearing comprises a coil electrically connected with a controller, and the controller is used for controlling the on-off and size of the current in the coil; The controller is used for controlling the on-off and size of the current in the coil according to a preset operation program; A first static pressure air inlet throttling hole for connecting an external air source with the first gap is arranged on the first stator, and a second static pressure air inlet throttling hole for connecting an external air source with the second gap is arranged on the second stator; And / or, an end surface of the thrust disc facing the first stator and the second stator, or an end surface of the first stator and the second stator facing the thrust disc is provided with a dynamic pressure generating groove; Each of the first stator and the second stator comprises a stator body, a pressing plate and a bearing damper, the bearing damper is arranged between the stator body and the pressing plate, and the pressing plate is arranged on the side of the stator body close to the thrust disc; The bearing damper is made of a shape memory material, and can be plastically deformed under the action of the pressing plate to adjust a bearing gap, the bearing gap comprises the first gap and the second gap; A magnetic part is arranged on the end surface of the thrust disc facing the magnetic bearing, or the thrust disc is made of a magnetic conductive material, so that the thrust disc can move in the axial direction of the rotating shaft under the magnetic force of the magnetic bearing; The gap between the thrust disc and the first stator and the second stator forms a gas bearing, and the gas bearing cooperates with the magnetic bearing to form a gas-magnetic hybrid bearing.

2. A method of manufacturing a thrust bearing, characterized by Comprise: Manufacture a thrust disc, a rotating shaft and a stator, the stator comprises a first stator and a second stator; Fix and install the thrust disc and the rotating shaft to form a thrust disc rotating shaft assembly; Process the thrust disc rotating shaft assembly so that the perpendicularity between the end surface of the thrust disc and the circumferential surface of the rotating shaft is within 0.1 microns; Assemble the first stator to a bearing housing, and assemble the second stator to the thrust disc rotating shaft assembly; The method for manufacturing the thrust disc comprises the following steps: Provide a thrust disc blank, and coarsely process the thrust disc blank; quenching the thrust disc blank so that the hardness of the thrust disc blank is greater than or equal to 55 Rockwell Hardness HRC; finishing the thrust disc blank so that the parallelism between the two end faces of the thrust disc is within 0.1 microns, the maximum unevenness of any end face of the thrust disc is less than or equal to 0.5 microns, and the flatness is within 1 micron; the method for manufacturing the stator comprises the following steps: providing a stator blank, and rough machining the stator blank; quenching the stator blank so that the hardness of the stator blank is greater than or equal to 55 HRC; finishing the stator blank so that the parallelism between the two end faces of the stator is within 0.1 microns, the maximum unevenness of at least the end face of the stator facing the thrust disc is less than or equal to 0.5 microns, and the flatness is within 1 micron; the method for manufacturing the rotating shaft comprises the following steps: providing a rotating shaft blank, and rough machining the rotating shaft blank; quenching the rotating shaft blank so that the hardness of the rotating shaft blank is greater than or equal to 55 HRC; machining at least one static pressure intake throttle hole on the stator; and / or, machining dynamic pressure generating grooves on the end face of the stator facing the thrust disc, or machining dynamic pressure generating grooves on the two end faces of the thrust disc; the dynamic pressure generating grooves are machined by etching, comprising the following steps: sequentially cleaning the part to be machined with carbon tetrachloride or trichloroethylene, acetone, and alcohol; coating the end face of the part to be machined to be etched with a photosensitive resist; drying the part to be machined in a temperature of 70-90°C for 20-40 minutes; placing a mask plate with dynamic pressure generating grooves above a high-pressure mercury lamp, and exposing the end face of the part to be machined to the mask plate; developing with a developing solution; drying the part to be machined in a temperature of 70-90°C for 20-40 minutes; wherein the part to be machined is the stator or the thrust disc; the dynamic pressure generating grooves on the mask plate and the dynamic pressure generating grooves formed on the part to be machined are in a mirror image relationship.

3. A rotor system, characterized by comprise: a rotating shaft; the thrust bearing of claim 1, one end face of the thrust disc of the thrust bearing is connected with one end portion of the rotating shaft; a first radial bearing, a motor, a compressor, a second radial bearing, and a turbine are sequentially arranged on the rotating shaft, the first radial bearing is located on the rotating shaft close to the thrust bearing, and the first radial bearing and the second radial bearing are both non-contact radial bearings; a third radial bearing is further arranged between the motor and the compressor, and the third radial bearing is a non-contact radial bearing.

4. A rotor system characterized by, comprise: a first rotating shaft; the thrust bearing of claim 1, one end face of the thrust disc of the thrust bearing is connected with one end portion of the first rotating shaft, and a magnetic bearing is sleeved on the shaft coupling connector; A compressor, a first radial bearing and a turbine are sequentially arranged on the first rotating shaft, the compressor is located on the first rotating shaft close to the thrust bearing, and the thrust bearing is spaced apart from the compressor by a predetermined distance so that the thrust bearing does not block the air inlet of the compressor; A second rotating shaft, one end of the second rotating shaft is connected with the coupling connector through a coupling; A second radial bearing, a motor and a third radial bearing are sequentially arranged on the second rotating shaft; The first radial bearing, the second radial bearing and the third radial bearing are all non-contact radial bearings; A fourth radial bearing is further arranged between the thrust bearing and the compressor, and the fourth radial bearing is a non-contact radial bearing.

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