Method and device for throttling control of hydrostatic bearings

Abstract

This invention discloses a throttling control method and apparatus for hydrostatic bearings. The method includes: Step S1: setting control parameters for a solenoid valve controller, the control parameters including a preset pressure value and a preset speed value; Step S2: reading the actual speed and actual oil chamber pressure of the hydrostatic bearing through a sensor, and calculating the external load of the hydrostatic bearing based on the actual oil chamber pressure; Step S3: determining the control mode of the solenoid valve controller based on the relationship between the actual speed and the preset speed value, and the relationship between the external load and the preset pressure value; Step S4: controlling the solenoid valve to connect the throttle corresponding to the control mode through the solenoid valve controller to adjust the load range of the hydrostatic bearing. The throttling control method and apparatus for hydrostatic bearings disclosed in this application solves the problem of limited load-bearing capacity and low load-bearing capacity of hydrostatic bearings.

Description

Technical Field

[0001] This invention relates to the field of ultra-precision machine tool technology, and more specifically, to a hydrostatic bearing throttling control method and device. Background Technology

[0002] Currently, hydrostatic bearings primarily utilize throttles to regulate oil pressure and flow rate to enhance their load-carrying capacity. Existing throttles mainly include fixed and variable throttles. Fixed throttles maintain a constant hydraulic resistance during operation, making them inflexible under varying loads, resulting in lower load-carrying capacity for hydrostatic bearings. Variable throttles, such as diaphragm feedback throttles, adjust hydraulic resistance through the deformation of a metal diaphragm. However, limited by the material properties of the diaphragm, their deformation under pressure is limited, thus restricting the load-carrying capacity range of hydrostatic bearings and consequently reducing their overall load-carrying capacity. Summary of the Invention

[0003] The main objective of this invention is to provide a throttling control method and device for hydrostatic bearings, so as to at least solve the problem that hydrostatic bearings have a limited range of load-bearing capacity and low load-bearing capacity.

[0004] According to one aspect of the present invention, a method for throttling control of a hydrostatic bearing is provided, comprising:

[0005] Step S1: Set the control parameters of the solenoid valve controller, including a preset pressure value and a preset speed value;

[0006] Step S2: Read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing through the sensor, and calculate the external load of the hydrostatic bearing based on the actual oil chamber pressure;

[0007] Step S3: Determine the control mode of the solenoid valve controller based on the relationship between the actual rotational speed and the preset rotational speed value, and the relationship between the external load and the preset pressure value;

[0008] Step S4: Control the solenoid valve to connect the throttle corresponding to the control mode through the solenoid valve controller to adjust the load range of the hydrostatic bearing.

[0009] Furthermore, the control mode includes a first control mode and a second control mode. The first control mode is configured to control the solenoid valve to conduct with the first throttle via the solenoid valve controller, and the second control mode is configured to control the solenoid valve to conduct with the second throttle via the solenoid valve controller.

[0010] Further, step S3 includes:

[0011] Step S31: Determine the relationship between the actual rotational speed and the preset rotational speed value, and the relationship between the external load and the preset pressure value;

[0012] Step S32: If the actual rotational speed is not greater than the preset rotational speed value and the external load is not greater than the preset pressure value, then switch the control mode of the solenoid valve controller to the first control mode;

[0013] Step S33: If the actual rotational speed is greater than the preset rotational speed value or the external load is greater than the preset pressure value, then switch the control mode of the solenoid valve controller to the second control mode.

[0014] Further, the load range includes a first load range and a second load range, the first load range is configured as [a, b], and the second load range is configured as (b, c], where a < b < c. Step S4 includes:

[0015] Step S41: When the solenoid valve controller is in the first control mode, the solenoid valve is controlled to be connected to the first throttle via the solenoid valve controller, so as to adjust the load range of the hydrostatic bearing to the first load range.

[0016] Step S42: When the solenoid valve controller is in the second control mode, the solenoid valve is controlled to be connected to the second throttle via the solenoid valve controller, so as to adjust the load range of the hydrostatic bearing to the second load range.

[0017] Furthermore, the external load is calculated by multiplying the actual oil chamber pressure read by the sensor by the effective area of ​​the oil chamber. The formula for calculating the external load is as follows:

[0018] F = P1 × Ae1 - P2 × Ae2, where: F represents the external load of the hydrostatic bearing, P1 represents the pressure on the high-pressure side of the oil chamber, P2 represents the pressure on the low-pressure side of the oil chamber, Ae1 represents the effective area on the high-pressure side of the oil chamber, and Ae2 represents the effective area on the low-pressure side of the oil chamber.

[0019] According to another aspect of the present invention, a hydrostatic bearing throttling control device is also provided, the hydrostatic bearing throttling control device being used at least to perform the aforementioned hydrostatic bearing throttling control method, the hydrostatic bearing throttling control device comprising:

[0020] A turntable assembly, wherein the turntable assembly is provided with a hydrostatic bearing and a sensor, the sensor being used to read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing;

[0021] A control component, comprising a solenoid valve controller and a solenoid valve, wherein the solenoid valve controller is electrically connected to the sensor, and the solenoid valve is electrically connected to the solenoid valve controller;

[0022] A throttling assembly, comprising a first throttler and a second throttler, wherein the first throttler is connected to the solenoid valve and the oil inlet of the turntable assembly, respectively, and the second throttler is connected to the solenoid valve and the oil inlet of the turntable assembly, respectively.

[0023] Furthermore, both the first throttle and the second throttle include a variable throttle, the fluid resistance of which varies with the external load of the hydrostatic bearing.

[0024] Furthermore, the variable throttle includes a diaphragm feedback throttle, which comprises a throttle upper cover plate, a metal diaphragm sheet, and a throttle body. The throttle body has a groove, the throttle upper cover plate covers the groove, and the metal diaphragm sheet is disposed within the groove to form a non-communicating regulating chamber and a pressure stabilizing chamber. The regulating chamber is located between the bottom of the groove and the metal diaphragm sheet, and the pressure stabilizing chamber is located between the metal diaphragm sheet and the throttle upper cover plate. The throttle body is provided with a throttling platform, an oil inlet, a first flow channel inlet, and a second flow channel inlet. The system comprises a first flow channel, a second flow channel, a main oil port, and an oil outlet. The throttling platform is located within the pressure stabilizing chamber. The throttling platform is equipped with a throttling platform oil port. The oil inlet is connected to both the first flow channel port and the second flow channel port. The second flow channel port is connected to the regulating chamber. The first flow channel port is connected to the first flow channel. The first flow channel is connected to both the pressure stabilizing chamber and the second flow channel. The pressure stabilizing chamber is connected to the throttling platform oil port. The throttling platform oil port is connected to the oil outlet. The second flow channel is connected to the main oil port. The main oil port is connected to the oil outlet.

[0025] The thin-film feedback throttle is configured as follows:

[0026] When the oil outlet is not connected to a load, the metal diaphragm is deformed by the pressure of the regulating chamber, thereby reducing the volume of the pressure stabilizing chamber and controlling the flow rate of the oil outlet to decrease.

[0027] When the oil outlet is connected to a load, the metal diaphragm is deformed by the pressure of the pressure stabilizing chamber, thereby increasing the volume of the pressure stabilizing chamber and controlling the increase of the flow rate at the oil outlet.

[0028] Furthermore, the solenoid valve includes a two-position three-way solenoid valve, which is provided with a first oil inlet, a first oil outlet, and a second oil outlet. The first oil inlet is connected to the oil tank, the first oil outlet is connected to the first throttle, and the second oil outlet is connected to the second throttle. When the solenoid valve controller is in a first control mode, the first oil inlet is connected to the first oil outlet, and when the solenoid valve controller is in a second control mode, the first oil inlet is connected to the second oil outlet.

[0029] Furthermore, the sensor includes a speed sensor and a pressure sensor, which are respectively disposed on the hydrostatic bearing. The speed sensor is used to read the actual speed of the hydrostatic bearing, and the pressure sensor is used to read the actual oil chamber pressure of the hydrostatic bearing.

[0030] In this invention, by integrating speed and pressure sensors, the actual speed and oil chamber pressure information of the hydrostatic bearing can be obtained in real time and accurately as a control reference for the solenoid valve controller. This allows the system to respond quickly to changes in the bearing's operating state, ensuring that the bearing always remains in optimal working condition. Based on the actual speed and oil chamber pressure read by the sensors, the external load on the hydrostatic bearing is calculated based on the oil chamber pressure. The control mode of the solenoid valve controller is automatically switched based on the comparison between the external load, the actual speed, and a preset value. This adaptive control method allows the system to automatically adjust the selection of the throttle according to changes in operating conditions, thereby optimizing the bearing's lubrication and load-bearing capacity. By defining different load ranges and adjusting the bearing's load range according to actual operating conditions, this application achieves precise control of bearing performance. Optimization of the load range not only improves the bearing's load-bearing capacity and stability but also extends its service life and reduces the failure rate. Precise control of the oil flow direction and flow rate avoids unnecessary energy waste. When the bearing does not require excessive lubrication or load-bearing capacity, the oil supply can be automatically reduced, thereby reducing energy consumption and operating costs. Attached Figure Description

[0031] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0032] Figure 1 This is a schematic diagram of the hydrostatic bearing throttling control device disclosed in an embodiment of the present invention;

[0033] Figure 2 This is an exploded view of the thin-film feedback throttling device disclosed in an embodiment of the present invention;

[0034] Figure 3 The diagram shown is a schematic diagram of the internal structure of the thin-film feedback throttling device disclosed in an embodiment of the present invention;

[0035] Figure 4 The diagram shown is a schematic diagram of the oil circuit structure of the thin-film feedback throttle disclosed in an embodiment of the present invention;

[0036] Figure 5 The diagram shown is a schematic flowchart of the hydrostatic bearing throttling control method disclosed in an embodiment of the present invention.

[0037] The above figures include the following reference numerals:

[0038] 10. Turntable assembly; 20. Control assembly; 21. Solenoid valve; 211. First oil inlet; 212. First oil outlet; 213. Second oil outlet; 30. Throttling assembly; 31. First throttle; 32. Second throttle; 33. Diaphragm feedback throttle; 34. Throttling cover plate; 341. Arc-shaped boss; 35. Metal diaphragm sheet; 36. Throttling body; 361. Groove; 362. Oil inlet; 363. First flow channel inlet; 364. Second flow channel inlet; 365. First flow channel; 366. Second flow channel; 367. Main oil port; 37. Sealing element; 40. Oil tank. Detailed Implementation

[0039] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0040] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0041] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0042] like Figure 1As shown in the embodiment of this application, a hydrostatic bearing throttling control device is provided, including a turntable assembly 10, a control assembly 20, and a throttling assembly 30. The turntable assembly 10 is equipped with a hydrostatic bearing and a sensor, the sensor being used to read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing; the control assembly 20 includes a solenoid valve controller and a solenoid valve 21, the solenoid valve controller being electrically connected to the sensor, and the solenoid valve 21 being electrically connected to the solenoid valve controller; the throttling assembly 30 includes a first throttle 31 and a second throttle 32, the first throttle 31 being connected to both the solenoid valve 21 and the oil inlet of the turntable assembly 10, and the second throttle 32 being connected to both the solenoid valve 21 and the oil inlet of the turntable assembly 10.

[0043] In this embodiment, the actual rotational speed and oil chamber pressure information of the hydrostatic bearing are acquired in real time and accurately by sensors, enabling precise control based on the actual operating state of the bearing. The solenoid valve controller adjusts the state of the solenoid valve 21 based on sensor data, selectively injecting oil into the bearing through the first throttle 31 or the second throttle 32, achieving accurate adjustment of bearing lubrication and support force, and enhancing the system's adaptability and response speed. By precisely controlling the oil flow direction and flow rate, the lubrication effect and load-bearing capacity of the hydrostatic bearing can be optimized, ensuring that the hydrostatic bearing maintains a stable working state under different operating conditions. This helps improve machining accuracy, extend the service life of the hydrostatic bearing, and reduce failures caused by poor lubrication or insufficient load-bearing capacity. Precise control of oil flow rate and pressure avoids unnecessary energy waste. When the hydrostatic bearing does not require excessive lubrication or support force, the oil supply can be automatically reduced, thereby reducing energy consumption and operating costs.

[0044] Optionally, both the first throttle 31 and the second throttle 32 include a variable throttle, the hydraulic resistance of which varies with the external load on the hydrostatic bearing. The variable throttle includes a thin-film feedback throttle 33, such as... Figure 2 and Figure 3As shown, the diaphragm feedback throttle 33 includes a throttle upper cover plate 34, a metal diaphragm sheet 35, and a throttle body 36. The throttle body 36 is provided with a groove 361, and the throttle upper cover plate 34 covers the groove 361. The metal diaphragm sheet 35 is disposed in the groove 361 to form an independent regulating chamber and a pressure stabilizing chamber. The regulating chamber is located between the bottom of the groove 361 and the metal diaphragm sheet 35, and the pressure stabilizing chamber is located between the metal diaphragm sheet 35 and the throttle upper cover plate 34. The throttle body 36 is provided with a throttle platform, an oil inlet 362, a first flow channel 363, and a second flow channel 364. The system comprises a first flow channel 365, a second flow channel 366, a main oil port 367, and an oil outlet. A throttling platform is located within the pressure stabilizing chamber. The throttling platform is equipped with a throttling platform oil port. The oil inlet 363 is connected to both the first flow channel port 363 and the second flow channel port 364. The second flow channel port 364 is connected to the regulating chamber. The first flow channel port 363 is connected to the first flow channel 365. The first flow channel 365 is connected to both the pressure stabilizing chamber and the second flow channel 366. The pressure stabilizing chamber is connected to the throttling platform oil port. The throttling platform oil port is connected to the oil outlet. The second flow channel 366 is connected to the main oil port 367. The main oil port 367 is connected to the oil outlet.

[0045] like Figure 4 As shown, the thin-film feedback throttling device relies on an annular area formed by frustums of radius (r2-r1) and a thickness of... The slits h between the elastic thin films achieve throttling. In this embodiment, the thin-film feedback throttling device is configured as follows:

[0046] When the oil outlet is not connected to a load, the metal diaphragm 35 is deformed by the pressure of the regulating chamber, so that the volume of the pressure regulating chamber decreases, thereby controlling the flow rate of the oil outlet to decrease; when the oil outlet is connected to a load, the metal diaphragm 35 is deformed by the pressure of the pressure regulating chamber, so that the volume of the pressure regulating chamber increases, thereby controlling the flow rate of the oil outlet to increase.

[0047] In this embodiment, the throttle body 36 and the throttle upper cover plate 34 are fitted together and connected by bolts or other connecting parts, forming a sealed first flow channel and a second flow channel at the joint end face. The metal diaphragm sheet 35 is pre-deformed under the pressure of the arc-shaped boss 341 of the throttle body 36 and the throttle upper cover plate 34, thereby forming different regulating chambers and stabilizing chambers. Hydraulic oil enters the throttle from the oil inlet 362 at pump pressure Ps. The hydraulic oil entering the throttle 362 is divided into two streams. One stream flows through the first flow channel 365 and the first flow channel opening 363 into the stabilizing chamber, and through the second flow channel 366 directly into the main oil port. The other stream is divided into two streams and enters the second flow channel opening 264 through the groove into the regulating chamber. Specifically, when the oil outlet is not connected to a load, the oil outlet pressure Pr is 0, the oil pressure in the pressure stabilizing chamber is less than the oil pressure in the regulating chamber, and the metal diaphragm 35 deforms under pressure, bending towards the throttle platform to make the gap between the throttle platform and the metal diaphragm 35 zero. At this time, only hydraulic oil flows out of the oil outlet through the main oil port 367, and the oil outlet flow rate is minimal. When the oil outlet is connected to a load, the pressure in the pressure stabilizing chamber increases, the original balance is broken, and the metal diaphragm 35 bends towards the upper cover plate 34 of the throttle, increasing the gap between the throttle platform and the diaphragm. The hydraulic oil in the pressure stabilizing chamber can then flow out through the throttle platform port, merging with the hydraulic oil in the main oil port and flowing out of the oil outlet together. When the load pressure changes, the metal diaphragm 35 will deform accordingly under the action of force. The volume of the pressure stabilizing chamber changes with the deformation of the metal diaphragm 35, which plays a role in controlling the flow rate of the oil outlet. The greater the load pressure, the greater the flow rate, so that the oil film thickness changes very little and has higher oil film rigidity, thereby ensuring that the hydrostatic functional components connected to it have high motion accuracy requirements.

[0048] Specifically, the thin-film feedback throttle in this embodiment also includes a sealing element 37, which includes a sealing ring. The sealing ring is disposed in the gap between the upper cover plate 34 of the throttle and the main body 36 of the throttle, so that the upper cover plate 34 of the throttle can better seal the groove 361 of the main body 36 of the throttle. Because an adjustment cavity is provided in the groove 361 near the upper cover plate 34 of the throttle, oil will flow through the adjustment cavity when the hydrostatic turntable is working. Therefore, the sealing treatment can prevent the oil in the adjustment cavity from overflowing and improve the reliability of the hydrostatic turntable.

[0049] like Figure 1As shown, the solenoid valve 21 includes a two-position three-way solenoid valve. The two-position three-way solenoid valve is provided with a first oil inlet 211, a first oil outlet 212 and a second oil outlet 213. The first oil inlet 211 is connected to the oil tank 40, the first oil outlet 212 is connected to the first throttle 31, and the second oil outlet 213 is connected to the second throttle 32. When the solenoid valve controller is in the first control mode, the first oil inlet 211 is connected to the first oil outlet 212. When the solenoid valve controller is in the second control mode, the first oil inlet 211 is connected to the second oil outlet 213.

[0050] By switching between the first and second control modes using the solenoid valve controller, the two-position three-way solenoid valve can selectively connect the first oil outlet 212 to the first throttle 31 or the second oil outlet 213 to the second throttle 32. This allows for flexible adjustment of the oil flow path according to actual needs, thereby achieving precise control over the bearing's load-bearing capacity. When the solenoid valve controller is in different control modes, the oil flows into the hydrostatic bearing through different throttles, each with different pressure regulation characteristics. Therefore, by changing the oil flow direction, different configurations of bearing lubrication and support force can be achieved, significantly expanding the load-bearing capacity range of the hydrostatic bearing. Because the load-bearing capacity of the hydrostatic bearing can be flexibly adjusted, this embodiment allows the hydrostatic bearing to better adapt to different processing requirements, thereby improving overall processing efficiency. By employing a two-position three-way solenoid valve and corresponding throttle configuration, bearing performance can be optimized by adjusting the oil path under high load, low speed, or high speed processing conditions, ensuring smooth processing.

[0051] Furthermore, the sensor includes a speed sensor and a pressure sensor, which are respectively installed on the hydrostatic bearing. The speed sensor is used to read the actual speed of the hydrostatic bearing, and the pressure sensor is used to read the actual oil chamber pressure of the hydrostatic bearing.

[0052] like Figure 5 As shown, according to an embodiment of this application, a hydrostatic bearing throttling control method is also provided. This method is executed at least by the aforementioned hydrostatic bearing throttling control device, and includes:

[0053] Step S1: Set the control parameters of the solenoid valve controller, including preset pressure value and preset speed value;

[0054] Specifically, the control parameters of the solenoid valve controller are determined according to the normal operating conditions of the specific industrial equipment in which the hydrostatic bearing is applied. In this embodiment, the preset pressure value of the solenoid valve controller is set to 5000N and the preset speed value is 1000RPM.

[0055] Step S2: Read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing through the sensor, and calculate the external load of the hydrostatic bearing based on the actual oil chamber pressure;

[0056] Furthermore, the external load is calculated by multiplying the actual oil chamber pressure read by the sensor by the effective area of ​​the oil chamber. The formula for calculating the external load is as follows:

[0057] F = P1 × Ae1 - P2 × Ae2, where: F represents the external load of the hydrostatic bearing, P1 represents the pressure on the high-pressure side of the oil chamber, P2 represents the pressure on the low-pressure side of the oil chamber, Ae1 represents the effective area on the high-pressure side of the oil chamber, and Ae2 represents the effective area on the low-pressure side of the oil chamber.

[0058] Specifically, the hydrostatic bearing throttling control device is activated to control the hydrostatic bearing to start operating. The speed sensor and pressure sensor operate in real time; the speed sensor reads the actual rotational speed of the hydrostatic bearing, and the pressure sensor reads the actual oil chamber pressure. The external load on the hydrostatic bearing is calculated based on the actual oil chamber pressure. For example, at a certain moment, the sensor reads the high-pressure side pressure P1 of the oil chamber as 60 N / cm². 2 The low-pressure side pressure P2 of the oil chamber is 40 N / cm. 2 Based on the external load calculation formula F=P1×Ae1-P2×Ae2, the effective area of ​​the high-pressure side oil cavity is set to 100cm². 2 The effective area of ​​the low-pressure side oil chamber is 80 cm². 2 The external load F can be obtained as 60×100-40×80=2800N, and the actual speed measured by the speed sensor is 800RPM.

[0059] Step S3: Determine the control mode of the solenoid valve controller based on the relationship between the actual rotational speed and the preset rotational speed value, as well as the relationship between the external load and the preset pressure value;

[0060] Furthermore, the control modes include a first control mode and a second control mode. The first control mode is configured to control the solenoid valve to conduct with the first throttle via the solenoid valve controller, and the second control mode is configured to control the solenoid valve to conduct with the second throttle via the solenoid valve controller.

[0061] Further, step S3 includes:

[0062] Step S31: Determine the relationship between the actual rotational speed and the preset rotational speed value, as well as the relationship between the external load and the preset pressure value;

[0063] Step S32: If the actual rotational speed is not greater than the preset rotational speed value and the external load is not greater than the preset pressure value, then switch the control mode of the solenoid valve controller to the first control mode.

[0064] Step S33: If the actual rotational speed is greater than the preset rotational speed value or the external load is greater than the preset pressure value, switch the control mode of the solenoid valve controller to the second control mode.

[0065] Step S4: Control the solenoid valve to connect the throttle corresponding to the control mode through the solenoid valve controller to adjust the load range of the hydrostatic bearing.

[0066] Further, the load interval includes a first load interval and a second load interval, the first load interval is configured as [a, b], and the second load interval is configured as (b, c], where a < b < c. Step S4 includes:

[0067] Step S41: When the solenoid valve controller is in the first control mode, the solenoid valve is controlled to be connected to the first throttle via the solenoid valve controller, so as to adjust the load range of the hydrostatic bearing to the first load range.

[0068] Step S42: When the solenoid valve controller is in the second control mode, the solenoid valve is controlled to connect with the second throttle to adjust the load range of the hydrostatic bearing to the second load range.

[0069] Specifically, the device automatically determines the control mode of the solenoid valve controller based on the relationship between the actual rotational speed and the preset rotational speed value, and the relationship between the external load and the preset pressure value. Since the actual rotational speed of 800 RPM is not greater than the preset rotational speed value of 1000 RPM, and the external load of 2800 N is not greater than the preset pressure value of 5000 N, the control mode of the solenoid valve controller is switched to the first control mode. After receiving the command, the solenoid valve controller quickly controls the solenoid valve 21 to conduct with the first throttle 31. At this time, the load range of the hydrostatic bearing is adjusted to the first load range [a, b]. Assuming that a = 2000 N and b = 4000 N are set in this embodiment, the hydrostatic bearing can work under suitable conditions, ensuring good lubrication and load-bearing performance. As the operating conditions change, the actual rotational speed is monitored again to increase to 1200 RPM, and the oil chamber pressure also changes. The external load is recalculated to be 3500 N. At this point, since the actual rotational speed of 1200 RPM is greater than the preset rotational speed of 1000 RPM, according to the control logic, even if the external load is still less than the preset pressure value, the control mode of the solenoid valve controller is switched to the second control mode. The solenoid valve controller controls the solenoid valve 21 to conduct with the second throttle 32, adjusting the load range of the hydrostatic bearing to the second load range (b, c], assuming c = 6000 N, to adapt to the new working state, maintain the stable operation of the hydrostatic bearing, and avoid problems such as wear and overheating caused by changes in working conditions.

[0070] In the above embodiments, by integrating sensors to acquire the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing in real time, and calculating the external load based on the actual oil chamber pressure, precise monitoring of the hydrostatic bearing's operating state is achieved. Based on the monitoring results, the solenoid valve controller can intelligently switch control modes and select the most suitable throttle for oil supply, thereby ensuring that the hydrostatic bearing maintains optimal operating conditions under different operating conditions. This adaptive control method significantly improves the system's stability and reliability. By defining different load ranges and adjusting the bearing's load range according to actual operating conditions, fine control of bearing lubrication and load-bearing capacity is achieved. In the first control mode, the bearing operates in a lower load range, suitable for light load or low-speed conditions; in the second control mode, the bearing can handle heavy load or high-speed conditions. This optimization of the load range allows the bearing to exhibit good lubrication and load-bearing performance under various operating conditions, extending its service life. By precisely controlling the oil flow direction and flow rate, this embodiment avoids unnecessary energy waste. When the hydrostatic bearing does not require excessive lubrication or load-bearing capacity, the oil supply can be automatically reduced, thereby reducing energy consumption and operating costs.

[0071] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0072] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0073] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A throttling control method for hydrostatic bearings, characterized in that, include: Step S1: Set the control parameters of the solenoid valve controller, including a preset pressure value and a preset speed value; Step S2: Read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing through the sensor, and calculate the external load of the hydrostatic bearing based on the actual oil chamber pressure; Step S3: Determine the control mode of the solenoid valve controller based on the relationship between the actual rotational speed and the preset rotational speed value, and the relationship between the external load and the preset pressure value. The control mode includes a first control mode and a second control mode. The first control mode is configured to control the solenoid valve to connect with the first throttle via the solenoid valve controller. The second control mode is configured to control the solenoid valve to connect with the second throttle via the solenoid valve controller. Step S3 includes: Step S31: Determine the relationship between the actual rotational speed and the preset rotational speed value, and the relationship between the external load and the preset pressure value; Step S32: If the actual rotational speed is not greater than the preset rotational speed value and the external load is not greater than the preset pressure value, then switch the control mode of the solenoid valve controller to the first control mode; Step S33: If the actual rotational speed is greater than the preset rotational speed value or the external load is greater than the preset pressure value, then switch the control mode of the solenoid valve controller to the second control mode; Step S4: The solenoid valve controller activates the throttle corresponding to the control mode to adjust the load range of the hydrostatic bearing. The load range includes a first load range and a second load range. The first load range is configured as [a, b], and the second load range is configured as (b, c], where a < b < c. Step S4 includes: Step S41: When the solenoid valve controller is in the first control mode, the solenoid valve is controlled to be connected to the first throttle via the solenoid valve controller, so as to adjust the load range of the hydrostatic bearing to the first load range. Step S42: When the solenoid valve controller is in the second control mode, the solenoid valve is controlled to be connected to the second throttle via the solenoid valve controller, so as to adjust the load range of the hydrostatic bearing to the second load range.

2. The hydrostatic bearing throttling control method according to claim 1, characterized in that, The external load is calculated by multiplying the actual oil chamber pressure read by the sensor by the effective area of ​​the oil chamber. The formula for calculating the external load is as follows: Where: F represents the external load of the hydrostatic bearing, P1 represents the high-pressure side pressure of the oil chamber, P2 represents the low-pressure side pressure of the oil chamber, Ae1 represents the effective area of ​​the high-pressure side of the oil chamber, and Ae2 represents the effective area of ​​the low-pressure side of the oil chamber.

3. A hydrostatic bearing throttling control device, characterized in that, The hydrostatic bearing throttling control device is used at least to perform the hydrostatic bearing throttling control method as described in claim 1 or 2, characterized in that the hydrostatic bearing throttling control device comprises: A turntable assembly, wherein the turntable assembly is provided with a hydrostatic bearing and a sensor, the sensor being used to read the actual rotational speed and actual oil chamber pressure of the hydrostatic bearing; A control component, comprising a solenoid valve controller and a solenoid valve, wherein the solenoid valve controller is electrically connected to the sensor, and the solenoid valve is electrically connected to the solenoid valve controller; A throttling assembly, comprising a first throttler and a second throttler, wherein the first throttler is connected to the solenoid valve and the oil inlet of the turntable assembly, respectively, and the second throttler is connected to the solenoid valve and the oil inlet of the turntable assembly, respectively.

4. The hydrostatic bearing throttling control device according to claim 3, characterized in that, Both the first throttle and the second throttle include a variable throttle, the fluid resistance of which varies with the external load of the hydrostatic bearing.

5. The hydrostatic bearing throttling control device according to claim 4, characterized in that, The variable throttle includes a diaphragm feedback throttle, which comprises a throttle upper cover, a metal diaphragm sheet, and a throttle body. The throttle body has a groove, and the throttle upper cover covers the groove. The metal diaphragm sheet is disposed within the groove to form a non-communicating regulating chamber and a pressure-stabilizing chamber. The regulating chamber is located between the bottom of the groove and the metal diaphragm sheet, and the pressure-stabilizing chamber is located between the metal diaphragm sheet and the throttle upper cover. The throttle body includes a throttle platform, an oil inlet, a first flow channel inlet, a second flow channel inlet, and a third flow channel inlet. The system comprises a first flow channel, a second flow channel, a main oil port, and an oil outlet. The throttling platform is located within the pressure stabilizing chamber. The throttling platform is equipped with a throttling platform oil port. The oil inlet is connected to both the first flow channel port and the second flow channel port. The second flow channel port is connected to the regulating chamber. The first flow channel port is connected to the first flow channel. The first flow channel is connected to both the pressure stabilizing chamber and the second flow channel. The pressure stabilizing chamber is connected to the throttling platform oil port. The throttling platform oil port is connected to the oil outlet. The second flow channel is connected to the main oil port. The main oil port is connected to the oil outlet. The thin-film feedback throttle is configured as follows: When the oil outlet is not connected to a load, the metal diaphragm is deformed by the pressure of the regulating chamber, thereby reducing the volume of the pressure stabilizing chamber and controlling the flow rate of the oil outlet to decrease. When the oil outlet is connected to a load, the metal diaphragm is deformed by the pressure of the pressure stabilizing chamber, thereby increasing the volume of the pressure stabilizing chamber and controlling the increase of the flow rate at the oil outlet.

6. The hydrostatic bearing throttling control device according to claim 3, characterized in that, The solenoid valve includes a two-position three-way solenoid valve, which is provided with a first oil inlet, a first oil outlet, and a second oil outlet. The first oil inlet is connected to the oil tank, the first oil outlet is connected to the first throttle, and the second oil outlet is connected to the second throttle. When the solenoid valve controller is in a first control mode, the first oil inlet is connected to the first oil outlet, and when the solenoid valve controller is in a second control mode, the first oil inlet is connected to the second oil outlet.

7. The hydrostatic bearing throttling control device according to claim 3, characterized in that, The sensor includes a speed sensor and a pressure sensor, which are respectively disposed on the hydrostatic bearing. The speed sensor is used to read the actual speed of the hydrostatic bearing, and the pressure sensor is used to read the actual oil chamber pressure of the hydrostatic bearing.

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