High-speed heavy-load energy-saving dynamic-static pressure damping sliding bearing

Abstract

A high-speed heavy-load energy-saving dynamic-static pressure damping sliding bearing, comprising a sliding bearing body, the sliding bearing body is composed of a bearing shell, an oil control frame, a tilting pad group, an adjusting pad group and a nozzle, wherein the bearing shell is installed on one side of the oil control frame, and the tilting pad group is arranged on the other side of the bearing shell on the oil control frame, the adjusting pad group is arranged on the side of the tilting pad group between the bearing shell and the tilting pad group, the tilting pad group and the adjusting pad group are connected together through a limiting screw pin, and are installed on a curved groove arranged on the oil control frame through a suspension pin, and the nozzle is also installed on the tilting pad group, respectively, and the bearing shell, the oil control frame, the tilting pad group, the adjusting pad group and the nozzle constitute an integral sliding bearing. The self-balancing ability of the bearing bush is enhanced, and the bearing carrying capacity and stability during rapid start and stop of the compressor rotor are improved.

Description

Technical Field

[0001] This invention belongs to the field of bearing technology, specifically relating to a high-speed, heavy-duty, energy-saving dynamic and static pressure damping sliding bearing, suitable for supporting the main shaft of a high-speed, heavy-duty centrifugal compressor. Background Technology

[0002] Centrifugal compressor units are developing towards larger sizes, higher speeds, and higher pressures. This requires compressor rotor supports with greater load-bearing capacity and higher linear speeds, and the rotor dynamics place higher demands on the stability provided by the bearings. As the aerodynamic performance of large compressors approaches its peak, the power consumption of the compressor rotor support bearings will account for an increasingly larger proportion of total power consumption. Therefore, achieving energy-efficient bearing design for centrifugal compressors is a key factor in improving the overall efficiency of the compressor.

[0003] Hydrostatic bearings are high-performance, long-life bearings characterized by excellent rigidity, extremely low coefficient of friction, ideal precision, and damping properties. The hydrostatic oil film they form provides strong support to the shaft, ensuring smooth rotation and effectively absorbing potential vibration energy. They are used in rotating machinery operating under extreme conditions such as high speed, precision, and heavy loads. The performance of the bearing plays a decisive role to a certain extent, directly affecting the dynamic characteristics of the compressor rotor. However, with the development of centrifugal compressors, the commonly used five-piece evenly distributed tilting pad bearings in existing technologies are insufficient to meet the rotor support requirements of centrifugal compressors under high-speed, heavy-load conditions due to their structural limitations, even with a width-to-diameter ratio of 1 or higher. Simultaneously, as the bearing width increases, the bearing temperature rise and power consumption also increase dramatically. During high-speed spindle operation, the bearing temperature rises with the increase in oil film temperature. When the temperature reaches a critical point, internal deformation occurs in the bearing, affecting its performance, such as stiffness, rotational accuracy, and lifespan. To control temperature rise, methods such as increasing bearing clearance are used in the bearing design, but this also reduces bearing stability to some extent, which is detrimental to the stable operation of the centrifugal compressor rotor. Therefore, a high-speed, heavy-load, energy-saving hydrostatic damping sliding bearing was designed to overcome the above problems. Summary of the Invention

[0004] In order to overcome the shortcomings of the existing technology, the purpose of this invention is to provide a high-speed, heavy-duty, energy-saving dynamic and static pressure damping sliding bearing, which can provide good stability and rigidity, ideal precision and damping performance for centrifugal compressor rotors under high-speed and heavy-duty working conditions, while having the characteristics of reasonable structure, high efficiency and energy saving.

[0005] This invention proposes the following technical solution: a high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing, comprising a sliding bearing body, the sliding bearing body being composed of a bearing housing, an oil control frame, a tilting pad assembly, an adjusting shim assembly, and nozzles. The bearing housing is mounted on one side of the oil control frame, and a tilting pad assembly is mounted on the oil control frame on the other side of the bearing housing. An adjusting shim assembly is mounted on the side of the tilting pad assembly between the tilting pad assembly and the bearing housing. The tilting pad assembly and the adjusting shim assembly are connected together by limiting screws and pins, and then mounted on curved grooves in the oil control frame by suspension pins. Nozzles are also mounted on the tilting pad assembly. The bearing housing, oil control frame, tilting pad assembly, adjusting shim assembly, and nozzles constitute an integral sliding bearing.

[0006] Preferably, the tilting bearing assembly consists of a main bearing and a secondary bearing. An adjustable lifting oil hole is provided on the oil outlet side of the main bearing, and a damping adjustment groove and an adjustment oil groove containing a cooling circuit are provided on its oil inlet side. A nozzle is provided on each side of the secondary bearing, and a damping spring with self-balancing capability is provided on the bearing housing between the secondary bearing and the bearing housing. The damping spring is connected to the inner diameter of the bearing housing by an adjustable thread, and a gap of 1~1.5mm is provided between the damping spring and the secondary bearing.

[0007] Preferably, the number of the main bearing bush and the secondary bearing bush is at least two, and the main bearing bush and the secondary bearing bush are arranged in pairs, with an uneven circumferential distribution.

[0008] Preferably, the nozzles on both sides of the secondary bearing bush are throttling jet atomizing nozzles. After the lubricating oil is throttled and accelerated through the throttling orifice in the nozzle, it is diffused and atomized at the nozzle outlet and sprayed onto the shaft diameter.

[0009] As a preferred embodiment, the main load-bearing bearing has a ship-shaped structure with a bow and stern, which enhances the bearing's self-balancing ability under harsh working conditions and improves the bearing's resistance to oil pressure fluctuations.

[0010] Preferably, the oil control frame is made of carbon steel cast from a Bausch alloy, and the oil groove is dug deep to ensure the oil content, thereby providing suitable static pressure for the bearing.

[0011] The beneficial effects of the invention are as follows: The high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing designed in this invention has the advantages of high precision, good rigidity, strong load-bearing capacity, high stability, and low power consumption. By unevenly distributing the tilting pads, the bearing's load-bearing capacity is greatly improved, and it exhibits excellent reliability and stability when used in high-speed centrifugal compressors. By creating damping oil grooves on the main load-bearing bearing, the instability under harsh operating conditions such as high-speed, heavy-load centrifugal compressors can be effectively overcome. Attached Figure Description

[0012] Figure 1 This is a diagram of the internal structure of the bearing of the present invention.

[0013] Figure 2 This is a longitudinal sectional view of the bearing of the present invention.

[0014] Figure 3 This is a cross-sectional view of the main load-bearing bearing of the present invention.

[0015] Figure 4 This is a longitudinal sectional view of the main load-bearing bearing of the present invention.

[0016] Figure 5 This is a longitudinal view of the secondary bearing bush of the present invention. Detailed Implementation

[0017] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the following embodiments are provided to illustrate the present invention. However, the present invention may also be implemented in other ways different from those described herein, and therefore the present invention is not limited to the specific embodiments disclosed below.

[0018] In the description of this invention, unless otherwise stated, "a plurality of" means two or more; the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0019] like Figure 1 As shown, a high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing includes a sliding bearing body. The sliding bearing body consists of a bearing housing 1, an oil control frame 2, a tilting pad assembly 3, an adjusting shim assembly 4, and a nozzle 5. The bearing housing 1 is installed on one side of the oil control frame 2. On the other side of the bearing housing 1, a tilting pad assembly 3 is provided on the oil control frame 2. An adjusting shim assembly 4 is provided on the side of the tilting pad assembly 3 between the tilting pad assembly 3 and the bearing housing 1. The tilting pad assembly 3 and the adjusting shim assembly 4 are connected together by a limiting screw pin 404 and then installed in a curved groove provided on the oil control frame 2 by a suspension pin 401. Nozzles 5 are also installed on the tilting pad assembly 3. The bearing housing 1, oil control frame 2, tilting pad assembly 3, adjusting shim assembly 4, and nozzle 5 constitute an integral sliding bearing.

[0020] Figure 2As shown, the tilting bearing assembly 3 consists of a main bearing bush 310 and a secondary bearing bush 320. An adjustable lifting oil hole 312 is provided on the oil outlet side of the main bearing bush 310, and a damping adjustment groove 314 and an adjustment oil groove 313 containing a cooling circuit are provided on its oil inlet side. The damping adjustment groove is used to increase the damping coefficient of the bearing, thereby improving the bearing's stability and anti-excitation capability. A nozzle 5 is provided on each side of the secondary bearing bush 320, and a self-balancing damping spring 321 is provided on the bearing housing 1 between the secondary bearing bush 320 and the bearing housing 1. The damping spring 321 is threadedly adjustable to the inner diameter of the bearing housing 1, and a gap of 1~1.5mm is provided between the damping spring 321 and the secondary bearing bush 320. (See also...) Figure 3 As shown, numbers 331 and 332 are the oil inlets of the two regulating oil tanks.

[0021] The number of primary load-bearing bearing shells 310 and secondary load-bearing bearing shells 320 is at least two, and the primary load-bearing bearing shells 310 and secondary load-bearing bearing shells 320 are arranged in pairs, in a non-uniform circumferential distribution. The geometric dimensions of the primary and secondary load-bearing bearing shells are arranged according to the magnitude and direction of the bearing load.

[0022] The nozzles 5 on both sides of the secondary bearing bush 320 are throttling jet atomizing nozzles. After the lubricating oil is throttled and accelerated through the throttling orifice in the nozzle, it is diffused and atomized at the nozzle outlet and sprayed onto the shaft diameter.

[0023] Figure 4 As shown, the main load-bearing bearing 310 has a ship-shaped structure and is equipped with a bow and a stern.

[0024] The oil control frame 2 is made of carbon steel cast from a alloy, and a deep oil groove is used to ensure the oil content, thereby providing suitable static pressure for the bearing. For ease of understanding, it is also provided... Figure 5 This is a longitudinal view of the secondary load-bearing bearing in this invention. Specific Implementation

[0025] A high-speed, heavy-duty, energy-saving dynamic and static pressure damping sliding bearing includes a bearing housing 1, an oil control frame 2, a tilting pad assembly 3, an adjusting shim assembly 4, and a nozzle 5. The bearing housing 1, oil control frame 2, tilting pad assembly 3, adjusting shim assembly 4, and nozzle 5 together form an integral sliding bearing body.

[0026] In a preferred embodiment, the tilting bearing block group 3 can be divided into four blocks, unevenly distributed around the circumference, with the main bearing bearing 310 and the secondary bearing bearing 320 each forming a pair. Specifically, in this embodiment, the two main bearing bearings 310 are provided with adjustable lifting oil holes 312 on the oil outlet side, a damping adjustment groove 314 on the oil inlet side, and two adjustment oil grooves 313 containing cooling circuits. The main bearing bearings 310 are designed with a ship-like structure, featuring a bow and stern. The wrap angle of the main bearing bearing block is 78°, the angle between the fulcrum and the oil outlet side is 34°, the oil inlet side is raised like a bow, the oil outlet side has a stern like a stern, and the center of gravity is near the oil outlet side. Specifically, in this embodiment, each of the two secondary bearing bushes 320 is provided with a throttling jet atomizing nozzle on both sides. The lubricating oil is throttled and accelerated in the nozzle through the throttling orifice, and then diffused and atomized at the nozzle outlet to the shaft diameter. Each bush is also provided with a self-balancing damping spring 321. The damping spring 321 is connected to the inner diameter of the bearing housing 1 by an adjustable thread. The distance between the damping spring 321 and the back of the secondary bearing bush 320 is 1~1.5mm.

[0027] In a preferred embodiment, the back of the tilting pad assembly 3 is provided with an adjusting pad assembly 4 and a sliding adjusting block, which can adjust the bearing installation clearance by grinding and adjusting the thickness of the shims. Specifically, in this embodiment, the tilting pad assembly 3 and the adjusting pad assembly 4 are connected as a whole by a limiting screw pin 404, and then radially limited by a suspension pin 401 through the curved groove of the left and right oil control brackets 2. The bearing shell is then combined and limited by a movable screw pin on the back, ensuring that the bearing shell can move flexibly in a localized manner without falling off.

[0028] In a preferred embodiment, the oil control frame 2 is made of carbon steel cast from a busbar alloy. A deep oil groove method is used to ensure the oil content of the bearing, providing a suitable hydrostatic oil chamber. This creates a hydrostatic system between the inner ring of the bearing and the main shaft, while also ensuring smooth flow of lubricating oil. Specifically, in this embodiment, lubricating oil is supplied to the bearing bush through the oil supply hole in the bearing housing 1, and the high-speed rotation of the rotor forms a dynamic oil film on the surface of the bearing bush.

[0029] Compared with the prior art, the beneficial effects of this invention are: 1. By setting up lifting oil holes, this invention enables the rapid establishment of a stable dynamic pressure oil film in the bearing bush, thereby improving the bearing capacity of the bearing bush when the rotor passes the critical speed.

[0030] 2. By setting a damping adjustment groove, the present invention increases the damping coefficient of the bearing, thereby improving the bearing's stability and anti-excitation capability.

[0031] 3. By setting up an adjusting oil groove in the cooling circuit, this invention reduces the instability of the bearing bush and the lubricating oil during operation, achieves the application of a smaller bearing clearance, ensures the optimal value of the minimum oil film thickness, reduces bearing power consumption, and improves bearing support force.

[0032] 4. By setting a throttling jet atomizing nozzle, this invention achieves precise control of the lubricating oil volume, controls the oil film thickness and bearing temperature rise of the bearing bush, and reduces bearing power consumption; 5. By incorporating damping springs, this invention enhances the self-balancing ability of the bearing bushes, thereby improving the bearing load capacity and overcritical stability of the compressor rotor during rapid start-up and shutdown.

[0033] 6. This invention enhances the self-balancing ability of the bearing under harsh working conditions and improves the bearing's resistance to oil pressure fluctuations by designing the bearing bush in a ship-like structure with a bow and stern.

[0034] 7. This invention improves the safety and stability of high-speed rotating mechanical rotor systems.

[0035] 8. The present invention has a simple structure and is easy to install and maintain.

[0036] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing, comprising a sliding bearing body, characterized in that: The sliding bearing body consists of a bearing housing (1), an oil control frame (2), a tilting pad assembly (3), an adjusting shim assembly (4), and a nozzle (5). The bearing housing (1) is mounted on one side of the oil control frame (2). A tilting pad assembly (3) is provided on the inner side of the bearing housing (1) on the oil control frame (2). An adjusting shim assembly (4) is provided on the side of the tilting pad assembly (3) between the tilting pad assembly (3) and the bearing housing (1). The tilting pad assembly (3) The bearing housing (1), the oil control frame (2), the tilting pad assembly (3), the adjusting pad assembly (4), and the nozzle (5) are connected together by a limiting screw pin (404) and then installed in the curved groove of the oil control frame (2) by a suspension pin (401). The bearing housing (1), the oil control frame (2), the tilting pad assembly (3), the adjusting pad assembly (4), and the nozzle (5) form an integral sliding bearing. The tilting pad assembly (3) consists of a main bearing bush (310) and a secondary bearing bush (320). The main bearing bush (310) is located at the outlet of the main bearing bush (310). An adjustable lifting oil hole (312) is provided on the oil edge, and a damping adjustment groove (314) and an adjustment oil groove (313) with a cooling circuit are provided on the oil inlet side; the main bearing bush (310) has a ship-shaped structure with a bow and a stern, the main bearing bush has a 78° wrap angle, the radial line passing through the fulcrum and the inner angle formed by the oil outlet side are 34°, the oil inlet side is raised to form the bow, the oil outlet side with a tail forms the stern, the center of gravity is close to the oil outlet side, and a damping adjustment groove (314) and an oil outlet side (313) are provided on both sides of the secondary bearing bush (320). There is a nozzle (5), and a damping spring (321) with self-balancing capability is provided on the bearing housing (1) between the secondary bearing bush (320) and the bearing housing (1). The damping spring (321) is threadedly adjustable to the inner diameter of the bearing housing (1), and there is a gap between the damping spring (321) and the secondary bearing bush (320). The number of the main bearing bush (310) and the secondary bearing bush (320) is at least two.

2. The high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing according to claim 1, characterized in that: The nozzles (5) provided on both sides of the secondary bearing bush (320) are throttling jet atomizing nozzles. After the lubricating oil is throttled and accelerated through the throttling orifice in the nozzle, it is diffused and atomized at the nozzle outlet and sprayed onto the shaft diameter.

3. The high-speed, heavy-duty, energy-saving hydrostatic damping sliding bearing according to claim 1, characterized in that: The oil control frame (2) is made of carbon steel matrix cast from Babbitt alloy to ensure oil content and thus provide suitable static pressure for the sliding bearing.

Images