An adjuster for a self-feedback and self-adjusting hydrostatic spindle

Abstract

The present invention discloses an adjuster for a hydrostatic spindle with self-feedback and self-adjustment, specifically relating to the technical field of machining spindles. It includes a hydrostatic spindle system, a monitoring system, and a temperature adjustment system. The temperature adjustment system is configured with a cooling and temperature regulation system. The monitoring system includes temperature monitoring components, and two groups of temperature monitoring components are provided. The two groups of temperature monitoring components are respectively used to detect the temperature of the surface of the clearance surface and the temperature of the surface of the oil cavity. The temperature adjustment system includes a first cooling control component and a second cooling control component. The present invention separately adjusts the actual temperature of the cooling fluid input into the first cooling flow channel and the second cooling flow channel, and by means of the temperature difference between the two groups of cooling fluids, compensates for the temperature difference of the working temperature rise between the clearance surface and the oil cavity, ensuring that the working temperature at the corresponding positions within the bearing bush is more uniform, enabling stable rotation to be maintained for a long time, reducing the working vibration of the spindle, and improving the machining accuracy.

Description

Technical Field

[0001] The present invention relates to the technical field of machining spindles, and more specifically, to an adjuster for a hydrostatic spindle with self-feedback and self-adjustment. Background Art

[0002] The machine tool spindle is a core functional component of modern machine tools, and its function is to drive the tool (grinding wheel) or workpiece to rotate to achieve high-speed precision machining. A hydrostatic bearing is a sliding bearing that uses a pressure pump to forcibly pump a pressure lubricant into the tiny gap between the bearing and the shaft. The hydrostatic spindle is the product of the combination of the two. The spindle is supported by a liquid hydrostatic bearing, integrating the functions of the machine tool spindle and the motor structurally.

[0003] Among them, the hydrostatic spindle mainly includes a bearing body and a spindle. The bearing body is composed of a shaft housing and a bearing bush. The bearing bush is arranged outside the spindle, and the shaft housing is arranged outside the bearing bush to form a system support. A corresponding flow channel is arranged in the shaft housing to provide oil for the gap between the bearing bush and the spindle. The bearing bush is usually made of high-strength steel or cast iron, and its inner surface is precision machined to ensure smoothness and flatness, which helps the formation of an oil film. At the same time, the hydrostatic spindle also includes a restrictor, which can be in the form of a fixed-size small hole, a capillary tube, or an adjustable valve body, etc. By adjusting the opening degree of the restrictor to adapt to different working conditions (the throttle surface controls the flow rate and pressure of the fluid by restricting the flow area of the fluid, thereby precisely controlling the speed and pressure of the system. This control is very important for maintaining the stability and efficiency of the system, including flow control, pressure regulation, temperature management, and prevention of blockage, etc.).

[0004] An oil cavity is also arranged between the bearing bush and the spindle, so as to store lubricating oil and provide necessary space for the formation of the oil film (located on the inner wall of the bearing bush and distributed around the journal. The number and layout of the oil cavities need to be considered in the design to optimize the pressure distribution of the oil film).

[0005] In addition, the hydrostatic spindle is also correspondingly provided with an oil supply system to supply clean and pressure-stable lubricating oil to the bearing. It mainly includes components such as an oil pump, a filter, a cooling device, a pressure regulating valve, etc. and a sealing device (using mechanical seals, labyrinth seals or other forms of seals. Good sealing performance is very important for maintaining the cleanliness of the system), etc. Ensuring the quality of the lubricating oil is crucial for maintaining the stability of the oil film.

[0006] Although the hydrostatic spindle achieves non-contact support through the oil film, theoretically reducing direct metal-to-metal contact friction, in practical applications, under the high-speed rotation of the spindle, the flow of lubricating oil in the bearing clearance will generate shear force. This shear action will cause relative movement between lubricating oil molecules, which is then converted into heat. Especially for the oil film formed under high-pressure conditions, the internal shear will result in energy loss and be released in the form of heat. Regarding the oil supply system, during the circulation of lubricating oil, the lubricating oil can be cooled by an external cooling device to avoid excessive lubricating oil temperature. However, during use, the temperatures of the bearing and the spindle will still change. Especially when the spindle is used for long-term machining and runs at a high speed, the temperatures of the bearing and the spindle will also increase. At this time, since the overall texture of the spindle is uniform, the resulting thermal deformation is also relatively uniform. For the bearing, multiple oil cavities are provided inside it. In the circumferential direction, the inner wall structure of the bearing is slightly uneven. However, for a hydrostatic spindle with relatively small oil cavities, the thickness of the lubricating oil in the oil cavity is relatively low. Therefore, the heat transfer difference between the lubricating oil in the oil cavity and that in the remaining clearances is not significant, and the overall thermal deformation of the bearing is also within a controllable range.

[0007] However, for some heavy-duty machining and processing equipment that needs to face sudden loads or impacts, such as large grinding machines, oil cavities with larger spaces need to be used. Thus, when the spindle bears a large radial or axial load, the larger oil cavities can store more lubricating oil, provide stronger load-bearing capacity, and help disperse pressure to ensure the stability of the oil film and prevent failure caused by local overload.

[0008] For such equipment, due to the increased space of the oil cavity, the thickness of the lubricating oil in the oil cavity is relatively high during use. At this time, the thickness difference between the lubricating oil in the oil cavity and that in the clearance is relatively large, and the temperature conduction difference is also relatively large. Especially during the grinding of large workpieces, the machining cycle is long, the machining load is large, and the temperature change of the spindle is large. At this time, the uneven heat conduction leads to uneven temperature distribution on the inner wall of the bearing, resulting in relatively uneven thermal deformation of the bearing. At this time, it is easy to cause a large radial error in the rotation of the spindle, forming radial runout, which further increases the vibration intensity of the spindle and affects the machining accuracy of the equipment. Summary of the Invention

[0009] An adjuster for a self-feedback and self-adjusting hydrostatic spindle provided by the present invention aims to solve the following problem: For existing heavy-duty machining and processing equipment that needs to face sudden loads or impacts, the space of the oil cavity increases, and the thickness of the lubricating oil in the oil cavity is relatively high during use. At this time, the thickness difference between the lubricating oil in the oil cavity and that in the clearance is relatively large, and the temperature conduction difference is also relatively large, resulting in uneven thermal deformation of the bearing and affecting the machining accuracy of the equipment.

[0010] To achieve the above object, the present invention provides the following technical solution: An adjuster for a self-feedback and self-adjusting hydrostatic spindle, comprising a hydrostatic spindle system, a monitoring system, and a temperature adjustment system. The temperature adjustment system is configured with a cooling and temperature adjustment system. The hydrostatic spindle system includes a spindle housing, a main shaft, and a bearing bush. The main shaft is rotatably installed inside the bearing bush. The mating surface between the bearing bush and the main shaft is set as a clearance surface, and a plurality of oil cavities are arranged along the circumferential direction on the clearance surface.

[0011] The monitoring system includes temperature monitoring components, and there are two sets of temperature monitoring components. The two sets of temperature monitoring components are respectively used to detect the temperature of the surface of the clearance surface and the temperature of the surface of the oil cavity.

[0012] The temperature adjustment system includes a first cooling control component and a second cooling control component. The first cooling control component includes a first cooling flow channel, and the second cooling control component includes a second cooling flow channel. The first cooling flow channel is arranged in the area of the bearing bush corresponding to the oil cavity, and the second cooling flow channel is arranged in the area of the bearing bush corresponding to the clearance surface. The first cooling flow channel is connected with a first cooling fluid supply unit, and the second cooling flow channel is connected with a second cooling fluid supply unit. The cooling and temperature adjustment system is used to control the temperature of the cooling fluid provided by the first cooling fluid supply unit and the second cooling fluid supply unit.

[0013] In a preferred embodiment, the bearing bush is installed in the spindle housing. A dynamic sealing structure is arranged between the two ends of the main shaft and the bearing bush. The hydrostatic spindle system further includes an oil supply system and a lubricating oil channel. The lubricating oil channel includes an oil inlet channel and an oil outlet channel arranged on the spindle housing, and radial throttle holes and axial throttle holes arranged on the bearing bush. The radial throttle holes and the axial throttle holes are both arranged corresponding to the oil inlet channel and are in communication. The radial throttle holes extend inwards to the oil cavity, and the axial throttle holes extend towards the dynamic sealing structure. A return groove is further arranged in the bearing bush. The return groove is used to communicate the space between the dynamic sealing structure and the main shaft with the clearance surface and finally communicate with the oil outlet channel.

[0014] In a preferred embodiment, oil inlet throttle guiding grooves are arranged at the positions of the radial throttle holes and the axial throttle holes on the outer wall of the bearing bush. The oil inlet throttle guiding grooves surround the bearing bush and are arranged corresponding to the oil inlet channel.

[0015] In a preferred embodiment, the first cooling flow channel is connected with a first input pipe and a first output pipe. The first cooling fluid supply unit supplies flowing cooling fluid into the first cooling flow channel through the first input pipe. The second cooling flow channel is connected with a second input pipe and a second output pipe. The second cooling fluid supply unit supplies flowing cooling fluid into the second cooling flow channel through the second input pipe.

[0016] In a preferred embodiment, a first input guiding groove, a first output guiding groove, a second input guiding groove, and a second output guiding groove are provided on the outer wall of the bearing shell. Each first cooling channel is respectively communicated with the first input guiding groove and the first output guiding groove. Each second cooling channel is respectively communicated with the second input guiding groove and the second output guiding groove. The first input pipe, the first output pipe, the second input pipe, and the second output pipe are all installed on the shaft housing. The first input guiding groove is communicated with the first input pipe. The first output guiding groove is communicated with the first output pipe. The second input guiding groove is communicated with the second input pipe. The second output guiding groove is communicated with the second output pipe.

[0017] In a preferred embodiment, each first cooling channel is a movable pipe. The two ends of the movable pipe are connected with the first input pipe and the first output pipe through hoses. Adjusting distance movable cavities are provided at positions corresponding to the movable pipes in the bearing shell. The movable pipes are slidably installed in the adjusting distance movable cavities. The adjusting distance movable cavities are filled with heat-conducting liquid. A control structure is further provided on the hydrostatic main shaft system for controlling the sliding of the movable pipes in the adjusting distance movable cavities to adjust the distance between the movable pipes and the inner wall of the oil cavity.

[0018] In a preferred embodiment, the cooling and temperature adjusting system is a distributor. The distributor is fixedly installed on the shaft housing. Corresponding distribution chambers are respectively provided for the second cooling channels of each region clearance surface and the first cooling channels of each region oil cavity in the distributor. The second cooling channels of each region clearance surface are respectively communicated with the corresponding distribution chambers through the second input pipes, while the first cooling channels of each region oil cavity are respectively communicated with the corresponding distribution chambers through the first input pipes.

[0019] In a preferred embodiment, a partition plate is slidably arranged in the distribution chamber. A high-temperature flow channel and a low-temperature flow channel are formed in the distribution chamber with the partition plate as the boundary and are distributed up and down. The high-temperature flow channel is connected to a high-temperature liquid source through a pipeline. The low-temperature flow channel is connected to a low-temperature liquid source through a pipeline. Distribution grooves are provided at positions corresponding to the second input pipe or the first input pipe in the distribution chamber. A moving driver is installed outside the distribution chamber. The moving driver is used to drive the partition plate to lift.

[0020] In a preferred embodiment, two groups of pushing blocks are further provided in the distribution chamber corresponding to the first cooling channel. The two groups of pushing blocks are respectively located at both ends of the partition plate and cause the partition plate to generate a bending deformation by squeezing the partition plate. A pressure piston chamber is further provided at the position corresponding to the pushing block in the distribution chamber. The pushing block is slidably arranged in the pressure piston chamber. The pressure piston chamber is connected with an air inflation pump structure through a pipeline.

[0021] In a preferred embodiment, a plurality of temperature sensors corresponding to the temperature sensors in each oil chamber are provided, and the plurality of temperature sensors are arranged along the circumferential direction of the bearing bush. The monitoring system further includes a vibration monitoring component, and the vibration monitoring component is embedded and installed in the bearing bush. The vibration monitoring component is used to detect the vibration when the main shaft rotates and operates.

[0022] The beneficial effects of the present invention are as follows: By detecting the temperature of the surface of the clearance surface and the temperature of the surface of the oil chamber, and respectively adjusting the actual temperature of the cooling fluid input into the first cooling flow channel and the second cooling flow channel through the cooling and temperature adjustment system, with the temperature difference between the two groups of cooling fluids, the temperature difference of the working temperature rise between the clearance surface and the oil chamber is compensated. Furthermore, it can ensure that the temperature at the corresponding position inside the bearing bush is more uniform, and the generated thermal deformation within the specified range is also relatively uniform in temperature. Therefore, when the hydrostatic main shaft system is in a long-term and heavy-load working state, it can maintain stable rotation for a long time, reduce the working vibration of the main shaft, and improve the machining accuracy of the grinding machine. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a schematic diagram of the overall structure of the present invention.

[0024] Figure 2 It is a schematic diagram of the internal structure of the bearing bush of the present invention.

[0025] Figure 3 It is a longitudinal sectional view of the hydrostatic main shaft system of the present invention.

[0026] Figure 4 It is a schematic diagram of the connection between the first cooling flow channel and the first input guiding groove of the present invention.

[0027] Figure 5 Based on the present invention Figure 3 The enlarged view of the structure of part A.

[0028] Figure 6 It is a schematic diagram of the input-output connection of the first cooling flow channel of the present invention.

[0029] Figure 7 It is a schematic diagram of the external structure of the hydrostatic main shaft system of the present invention.

[0030] Figure 8 It is a schematic diagram of the structure of each guiding groove on the bearing bush of the present invention.

[0031] Figure 9 It is a transverse sectional view of the hydrostatic main shaft system of the present invention.

[0032] Figure 10 It is a schematic diagram of the structure of one of the cooling fluid temperature control systems provided by the present invention.

[0033] Figure 11This is a schematic structural diagram of the distribution chamber corresponding to the first cooling control component of the present invention.

[0034] Figure 12 This is a schematic structural diagram of the distribution groove of the present invention.

[0035] Figure 13 This is a schematic structural diagram of the distribution chamber corresponding to the second cooling control component of the present invention.

[0036] Figure 14 This is a schematic structural diagram of the present invention when the movable pipe is used as the first cooling flow channel.

[0037] Reference numerals are: 1, static pressure main shaft system; 11, shaft housing; 111, oil inlet channel; 112, oil outlet channel; 12, main shaft; 13, bearing bush; 131, clearance surface; 132, oil cavity; 133, radial throttle hole; 134, axial throttle hole; 135, oil inlet throttle guiding groove; 136, return groove; 137, pitch adjustment movable cavity; 14, dynamic sealing structure; 2, monitoring system; 21, temperature monitoring component; 22, vibration monitoring component; 3, temperature adjustment system; 31, first cooling control component; 311, first cooling flow channel; 3101, movable pipe; 312, first input pipe; 3121, first input guiding groove; 313, first output pipe; 3131, first output guiding groove; 32, second cooling control component; 321, second cooling flow channel; 322, second input pipe; 3221, second input guiding groove; 323, second output pipe; 3231, second output guiding groove; 4, cooling and temperature adjustment system; 41, high-temperature flow channel; 42, low-temperature flow channel; 43, distribution chamber; 44, distribution groove; 45, partition plate; 46, moving driver; 47, pushing block; 48, pressure piston chamber. Detailed implementation manners

[0038] The following further describes the present application in detail with reference to the accompanying drawings. It is necessary to point out here that the following specific implementation manners are only used to further illustrate the present application and cannot be understood as limiting the protection scope of the present application. Those skilled in the art can make some non-essential improvements and adjustments to the present application based on the above application content.

[0039] Refer to the attached drawings of the specification Figures 1 to 14, An adjuster for a self-feedback and self-adjusting hydrostatic spindle, including a hydrostatic spindle system 1, a monitoring system 2, and a temperature adjustment system 3. The temperature adjustment system 3 is configured with a cooling and temperature adjustment system 4. Among them, the hydrostatic spindle system 1 includes a shaft housing 11, a main shaft 12, and a bearing bush 13. The main shaft 12 is rotatably installed inside the bearing bush 13, and the bearing bush 13 is installed in the shaft housing 11 (usually fixedly installed). The mating surface between the bearing bush 13 and the main shaft 12 is set as a clearance surface 131. A plurality of oil cavities 132 are arranged along the circumferential direction on the clearance surface 131. The oil cavities 132 are recessed. A dynamic sealing structure 14 (common structures for rotating seals such as hydrostatic bearings, such as mechanical seal structures, packing seal structures, and labyrinth seal structures, etc.) is provided between the two ends of the main shaft 12 and the bearing bush 13. The hydrostatic spindle system 1 also includes an oil supply system and a lubricating oil passage. The oil supply system fills the clearance surface 131 and the oil cavities 132 with lubricating oil through the lubricating oil passage, and forms a pressure oil film between the main shaft 12 and the clearance surface 131, thereby forming a support for the main shaft 12.

[0040] Specifically, the oil supply system is a hydraulic oil pump and its associated hydraulic oil, hydraulic oil cooling equipment, etc. The lubricating oil passage includes an oil inlet passage 111 and an oil outlet passage 112 provided on the shaft housing 11, a radial throttle hole 133 and an axial throttle hole 134 provided on the bearing bush 13. Among them, the radial throttle hole 133 and the axial throttle hole 134 are both correspondingly arranged with the oil inlet passage 111 and are connected. The radial throttle hole 133 extends inward to the oil cavity 132 to directly supply oil to the oil cavity 132. The axial throttle hole 134 extends toward the dynamic sealing structure 14 to supply oil to the inside of the dynamic sealing structure 14. A return groove 136 is also provided inside the bearing bush 13. The return groove 136 is used to connect the space between the dynamic sealing structure 14 and the main shaft 12 with the clearance surface 131, and finally form a connection with the oil outlet passage 112, thereby forming an oil supply path and filling the space between the main shaft 12 and the bearing bush 13 with lubricating oil.

[0041] Among them, oil inlet throttle guiding grooves 135 are provided at the positions corresponding to the radial throttle hole 133 and the axial throttle hole 134 on the outer wall of the bearing bush 13. The oil inlet throttle guiding grooves 135 surround the bearing bush 13, and the oil inlet throttle guiding grooves 135 are correspondingly arranged with the oil inlet passage 111, so as to be able to form an oil supply guide to ensure that the lubricating oil can be quickly and evenly distributed when entering. At the same time, a throttling structure can also be formed by means of the radial throttle hole 133 and the oil inlet throttle guiding grooves 135.

[0042] In the above-mentioned hydrostatic spindle system 1, the lubricating oil in the oil cavity 132 not only plays a load-bearing role, but also provides a good lubrication effect, reducing the direct contact between the spindle 12 and the bearing bush 13, thereby extending the service life. When the spindle 12 rotates, the oil cavity 132 can also generate hydrodynamic pressure, further enhancing the load-bearing capacity and oil film stiffness, which is particularly significant during high-speed operation. By using the unique structure of the oil cavity 132, it is in a pure hydrostatic state when the spindle 12 does not rotate, and a hydrodynamic load-bearing oil film is naturally formed during rotation, improving the stiffness of the system. It should be noted that the above-mentioned solution of the hydrostatic spindle system 1 is a mature solution for existing hydrostatic spindles and hydrostatic bearings, and its detailed structure will not be elaborated in this embodiment.

[0043] In the above-mentioned embodiment, although the lubricating oil itself is equipped with a cooling device to cool the lubricating oil during circulation to avoid the accumulation of lubricating oil heat, due to the relatively large viscosity and slow flow of the lubricating oil during actual use, it can only ensure that the lubricating oil is in a normal working state. However, during actual use, heat is continuously generated in the hydrostatic spindle system 1, especially the bearing bush 13 will be heated and deformed. When the oil cavity 132 is too large, the thickness of the lubricating oil in the oil cavity 132 is relatively large. Therefore, the heat absorption conditions of the solid structure of the bearing bush 13 at the oil cavity 132 and the clearance surface 131 are different, which is likely to cause temperature differences, and then lead to uneven thermal deformation, resulting in the rotational error and vibration superposition of the spindle 12. Therefore, on the basis of the above, this embodiment is equipped with a monitoring system 2, a temperature adjustment system 3, and a cooling and temperature adjustment system 4 for the hydrostatic spindle system 1. Among them, the monitoring system 2 includes a temperature monitoring component 21 and a vibration monitoring component 22. The temperature monitoring component 21 is set in two groups, and the two groups of temperature monitoring components 21 are respectively arranged corresponding to the clearance surface 131 and the oil cavity 132, that is, the two groups of temperature monitoring components 21 are respectively used to detect the temperature of the surface of the clearance surface 131 and the temperature of the surface of the oil cavity 132. Specifically, corresponding temperature sensors can be embedded and installed on the inner sides of their surfaces to detect the temperature of the corresponding area materials, and the detected information is transmitted to the control system of the grinding machine, so as to form the temperature monitoring of different areas in the inner wall of the temperature monitoring component 21. The vibration monitoring component 22 is embedded and installed in the bearing bush 13. The vibration monitoring component 22 is used to detect the vibration when the spindle 12 rotates and operates. For example, an eddy current sensor is used for non-contact detection. At the same time, the vibration monitoring component 22 also transmits the detected information to the control system of the processing grinding machine to form the vibration monitoring of the spindle 12.

[0044] Due to the different thicknesses of the lubricating oil in the clearance surface 131 and the oil cavity 132, resulting in different heat conduction and thermal deformation, therefore, this embodiment respectively sets corresponding cooling structures for the clearance surface 131 and the oil cavity 132. Specifically, refer to the attached Figures 2 to 6, the temperature adjustment system 3 includes a first cooling control component 31 and a second cooling control component 32. The first cooling control component 31 includes a first cooling flow channel 311, and the second cooling control component 32 includes a second cooling flow channel 321. The first cooling flow channel 311 is arranged in the area of the bearing bush 13 corresponding to the oil cavity 132, and the second cooling flow channel 321 is arranged in the area of the bearing bush 13 corresponding to the clearance surface 131. The first cooling flow channel 311 is connected to a first cooling fluid supply unit. The first cooling flow channel 311 is connected to a first input pipe 312 and a first output pipe 313. The first cooling fluid supply unit supplies flowing cooling fluid into the first cooling flow channel 311 through the first input pipe 312. The second cooling flow channel 321 is connected to a second cooling fluid supply unit. The second cooling flow channel 321 is connected to a second input pipe 322 and a second output pipe 323. The second cooling fluid supply unit supplies flowing cooling fluid into the second cooling flow channel 321 through the second input pipe 322. Both the first cooling fluid supply unit and the second cooling fluid supply unit are connected to the cooling and temperature adjustment system 4, that is, the cooling and temperature adjustment system 4 is used to control the temperature of the cooling fluid supplied by the first cooling fluid supply unit and the second cooling fluid supply unit.

[0045] Specifically, both the first cooling fluid supply unit and the second cooling fluid supply unit are composed of a cooling fluid and a corresponding fluid pump. The fluid pump pumps the cooling fluid into the corresponding first cooling flow channel 311 or second cooling flow channel 321. The cooling and temperature adjustment system 4 independently controls the temperature of the cooling fluid in the first cooling flow channel 311 and the second cooling flow channel 321 respectively. That is, the grinding machine control system processes the corresponding temperature signals of the clearance surface 131 and the oil cavity 132 obtained in real time by the temperature sensors correspondingly arranged by the temperature monitoring component 21, and then the system gives an information feedback. After the cooling and temperature adjustment system 4 obtains the corresponding feedback signal, it makes corresponding adjustments in time, that is, adjusts the actual temperature of the cooling fluid input into the first cooling flow channel 311 and the second cooling flow channel 321. By means of the temperature difference between the two groups of cooling fluids, the temperature difference of the working temperature rise between the clearance surface 131 and the oil cavity 132 is compensated. Furthermore, it can ensure that the working temperature rise at the corresponding position in the bearing bush 13 is more uniform, and the resulting thermal deformation within the specified range is also relatively uniform in temperature. Furthermore, in the working state of the hydrostatic spindle system 1 with long time and large load, it can maintain stable rotation for a long time, reduce the working vibration of the spindle 12, and improve the machining accuracy of the grinding machine. In addition, when the vibration monitoring component 22 detects a sudden vibration of the spindle 12, after the grinding machine control system obtains this signal, it gives a feedback signal to the grinding machine in time and adjusts the processing parameters, and stops the machine in time when necessary to reduce losses.

[0046] It should be noted that in the above embodiments, the cooling and temperature control system 4 is used to control the temperature change of the cooling fluid, and the change range is preferably in the range from above zero to the normal room temperature. Under the condition of ensuring effective heat dissipation of the hydrostatic spindle system 1, through reasonable adjustment, the hydrostatic spindle system 1 can be cooled more evenly.

[0047] Furthermore, with regard to the cooling uniformity of the regions of each clearance surface 131 and oil cavity 132, multiple groups of second cooling channels 321 and first cooling channels 311 can be provided in the regions corresponding to each clearance surface 131 and oil cavity 132 to improve the cooling effect. Among them, the groups of second cooling channels 321 in the regions corresponding to all clearance surfaces 131 can be controlled uniformly or independently in each region. Similarly, the groups of first cooling channels 311 in the regions corresponding to all oil cavities 132 can be controlled uniformly or independently in each region. Based on the above unified control scheme, referring to the attached drawings of the specification Figure 2 、 Figure 4 、 Figure 6 and Figure 8 , the oil inlet throttling guide groove 135 can be referred to. A first input guide groove 3121, a first output guide groove 3131, a second input guide groove 3221, and a second output guide groove 3231 are provided on the outer wall of the bearing bush 13. The respective guide grooves are used for unified guidance. Specifically, each first cooling channel 311 is respectively communicated with the first input guide groove 3121 and the first output guide groove 3131, and each second cooling channel 321 is respectively communicated with the second input guide groove 3221 and the second output guide groove 3231. A first input pipe 312, a first output pipe 313, a second input pipe 322, and a second output pipe 323 are provided on the shaft housing 11. The first input guide groove 3121 is communicated with the first input pipe 312, the first output guide groove 3131 is communicated with the first output pipe 313, the second input guide groove 3221 is communicated with the second input pipe 322, and the second output guide groove 3231 is communicated with the second output pipe 323. Thus, the supply of the cooling fluid to the first cooling channels 311 and the second cooling channels 321 can be realized by means of a small number of the first input pipe 312 and the second input pipe 322. In the above scheme, only one group can be provided for each of the first input pipe 312 and the second input pipe 322.

[0048] Based on the above embodiments, during the actual machining process of the grinding machine, if the machining feed direction is single and a long-term single force needs to be maintained (for example, the circumferential side wall of the grinding device needs to be in contact with the workpiece for a long time and feed. At this time, the workpiece will form a reverse thrust on the grinding structure, and then the main shaft 12 will be subjected to a radial thrust in a fixed direction). Therefore, a radial force in a single direction will be formed on the main shaft 12. At this time, the pressure on the fixed area of the bearing bush 13 by the main shaft 12 will relatively increase, and the temperature rise during operation here is relatively high. Therefore, uneven temperature rise in some areas will also be caused. At this time, it is not appropriate to uniformly control each group of first cooling channels 311 and second cooling channels 321. Therefore, at this time, each first cooling channel 311 is grouped according to the number of corresponding oil cavities 132. The first cooling channels 311 in each oil cavity 132 in each area are uniformly controlled as a group, while the first cooling channels 311 between the oil cavities 132 in each area are relatively independently controlled. Similarly, each second cooling channel 321 is grouped according to the number of corresponding clearance surfaces 131. The second cooling channels 321 in each clearance surface 131 in each area are uniformly controlled as a group, while the second cooling channels 321 between the clearance surfaces 131 in each area are relatively independently controlled. Furthermore, multiple independent control areas can be formed around the main shaft 12, and more precise adjustment can be made according to the monitoring feedback signal.

[0049] In addition, in the case of higher precision requirements and when cost permits, each first cooling channel 311 and each second cooling channel 321, based on the above principle, can also be individually controlled to further improve the control effect, but relatively speaking, the cost is higher.

[0050] The existing shapes in the oil cavity 132 mainly include a rectangular groove and an arc-shaped groove structure. Among them, the rectangular groove is a groove structure with a constant distance between the inner wall and the main shaft 12, while the distance between the inner wall of the arc-shaped groove and the main shaft 12 gradually decreases towards both sides. That is, the transition between the two side positions of the arc-shaped groove and the clearance surface 131 is relatively smooth, which can reduce the impact on the lubricating oil. However, since the thickness of the lubricating oil stored inside the oil cavity 132 will also change when the arc-shaped groove is adopted, specifically refer to the attached drawings of the specification. Figure 5, therefore, the first cooling channels 311 of the oil chambers 132 in each region also need to be controlled more precisely. That is, the temperature monitoring components 21 corresponding to the temperature sensors in each oil chamber 132 are set to be multiple, and the multiple temperature sensors are arranged along the circumferential direction of the bearing bush 13, so as to be able to detect and feedback the temperature distribution in the oil chamber 132 more precisely. At the same time, after obtaining more precise monitoring signals, it is also necessary to improve the control accuracy of each first cooling channel 311 at the oil chamber 132. Among them, the simplest is as described above, that is, each first cooling channel 311 is independently controlled, but the cost is relatively high. Therefore, this embodiment also provides the following solution to adapt to the temperature difference problem in each oil chamber 132 interval. For example, referring to the attached Figure 5 , among the first cooling channels 311 corresponding to each oil chamber 132 region, from the center of the oil chamber 132 to both sides, the distance from each first cooling channel 311 to the inner wall of the oil chamber 132 gradually increases, so that the first cooling channel 311 in the region with the largest thickness of the lubricating oil in the center area is closer, and the heat dissipation effect is better. On the contrary, the heat dissipation effect of the first cooling channels 311 in the two side directions is relatively poor, so as to compensate for the problem of temperature adjustment difference caused by uneven thickness of the lubricating oil in the oil chamber 132.

[0051] The above solution is relatively simple, but has great limitations, that is, although the distance of the first cooling channel 311 changes, its position is fixed, and it is difficult to cope with sudden situations of parameter mutations. Therefore, this embodiment also provides the following technical solution. Specifically, referring to the attached Figure 14 , each first cooling channel 311 is a movable pipe 3101. Both ends of the movable pipe 3101 are connected to the first input pipe 312 and the first output pipe 313 through hoses. A distance adjustment cavity 137 is provided at the position corresponding to each movable pipe 3101 in the bearing bush 13. The movable pipe 3101 is slidably installed in the distance adjustment cavity 137. The distance adjustment cavity 137 is filled with a heat-conducting liquid (such as mercury or water or other objects). A control structure for controlling the sliding of the movable pipe 3101 in the distance adjustment cavity 137 to adjust the distance between the movable pipe 3101 and the inner wall of the oil chamber 132 is also provided on the hydrostatic spindle system 1. This control structure can directly select a driving structure such as a micro cylinder.

[0052] In the above embodiments, the temperature reduction and regulation system 4 can directly adopt the combination of heating and cooling devices (such as the combination of an electric heater and a liquid nitrogen cooling device, etc.) to pre-control the temperature of the cooling fluid. Then, after obtaining the feedback signal, it is pumped to the corresponding area by the corresponding fluid pump. However, since the above cooling fluid is transported to the hydrostatic spindle system 1 after the temperature is pre-controlled, the actual temperature of the cooling fluid will be affected by the ambient temperature during the transportation process. Moreover, if temperature control devices are independently set for each group of the first cooling channels 311 and the second cooling channels 321, the cost will be higher. Therefore, this embodiment also provides another temperature reduction and regulation system 4. Specifically, refer to the attached drawings of the specification Figures 10 to 13 , the temperature reduction and regulation system 4 is a distributor, which is fixedly installed on the shaft housing 11. Corresponding to the second cooling channels 321 of each area clearance surface 131 and the first cooling channels 311 of each area oil chamber 132 in the distributor, corresponding distribution chambers 43 are respectively provided. The second cooling channels 321 of each area clearance surface 131 are respectively communicated with the corresponding distribution chambers 43 through the second input pipes 322, and the first cooling channels 311 of each area oil chamber 132 are respectively communicated with the corresponding distribution chambers 43 through the first input pipes 312. A partition plate 45 is slidably arranged in the distribution chamber 43. The distribution chamber 43 is divided into a high-temperature flow channel 41 and a low-temperature flow channel 42 distributed up and down with the partition plate 45 as the boundary. The high-temperature flow channel 41 is connected to a high-temperature liquid source through a pipeline, and the low-temperature flow channel 42 is connected to a low-temperature liquid source through a pipeline. Among them, the temperature of the high-temperature liquid source is higher than that of the low-temperature liquid source, but the height of the high-temperature liquid source generally does not exceed room temperature. Each liquid source is pumped into the distribution chamber 43 through the corresponding pump. And distribution grooves 44 are arranged at the positions corresponding to the second input pipes 322 or the first input pipes 312 in the distribution chamber 43. The side wall of the partition plate 45 corresponds to the distribution grooves 44. A moving driver 46 (such as a micro air pump) is installed outside the distribution chamber 43. The moving driver 46 is used to drive the partition plate 45 to lift and lower. Specifically, refer to the attached drawings of the specification Figure 12 , the partition plate 45 is attached to the distribution groove 44 to form a demarcation point. By controlling the lifting and lowering of the partition plate 45, the proportion of the high-temperature fluid and the low-temperature fluid flowing into the distribution groove 44 and finally flowing into the second input pipe 322 can be controlled, and then the temperature of the flowing liquid in the final second input pipe 322 can be controlled (a temperature sensor can be equipped on the pipeline for direct detection and feedback). Since the distributor of the temperature reduction and regulation system 4 can be directly arranged on the shaft housing 11, the transportation distance is short after the corresponding fluid temperature is regulated, and the influence of the outside world is small, thereby shortening the feedback time and improving the control accuracy.

[0053] In addition, based on the above solution, since the internal oil film thickness of each regional gap surface 131 is uniform, therefore, the second cooling channels 321 of each regional gap surface 131 form a group, and each group of second cooling channels 321 is connected to a distribution chamber 43 and is subject to relative regional unified control. For the oil chamber 132, the above method can also be adopted. The first cooling channels 311 of the oil chambers 132 in each region form a group, and each group of first cooling channels 311 is connected to a distribution chamber 43. However, as mentioned in the previous text, the thickness of the lubricating oil in the oil chamber 132 itself varies. Therefore, in order to adapt to this variation and difference, the present embodiment also provides the following solution. Specifically, referring to the appended Figure 13 , there are also two sets of push blocks 47 provided in the distribution chamber 43 corresponding to the first cooling channels 311. The two sets of push blocks 47 are respectively located at both ends of the partition plate 45, and the partition plate 45 is caused to generate a bending deformation by extruding the partition plate 45. Among them, a pressure piston chamber 48 is also provided at the position of the push block 47 in the distribution chamber 43. The push block 47 is slidably arranged in the pressure piston chamber 48. The pressure piston chamber 48 is connected to an air inflation pump structure through a pipeline, so that the push block 47 forms a piston. By controlling the inflation air pressure, the extrusion effect of the push block 47 on the partition plate 45 can be controlled. Since the distribution grooves 44 corresponding to the first input pipes 312 in each group of first cooling channels 311 are arranged along the length direction of the partition plate 45, and when the partition plate 45 is bent, the distribution effects on the respective distribution grooves 44 are also different, which can just adapt to the situation where the lubricating oil thickness corresponding to each group of first cooling channels 311 in the oil chamber 132 is different. Thus, a balance is achieved between equipment cost and technical effect, and more precise control of the first cooling channels 311 can be realized while ensuring that the first cooling channels 311 can be controlled by group.

[0054] The above-described embodiments merely represent several implementation manners of the present invention. The description thereof is relatively specific and detailed, but it should not be construed as a limitation to the scope of the patent of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several modifications and improvements can still be made, and these all belong to the protection scope of the present invention.

Claims

1. An adjuster for a self-feedback and self-adjusting hydrostatic spindle, characterized in that: It includes a hydrostatic spindle system (1), a monitoring system (2) and a temperature adjustment system (3). The temperature adjustment system (3) is configured with a cooling and temperature adjustment system (4). The hydrostatic spindle system (1) includes a housing (11), a main shaft (12) and a bearing bush (13). The main shaft (12) is rotatably installed inside the bearing bush (13). The mating surface of the bearing bush (13) and the main shaft (12) is set as a clearance surface (131). A plurality of oil cavities (132) are arranged on the clearance surface (131) along the circumferential direction. The monitoring system (2) includes temperature monitoring components (21). There are two sets of the temperature monitoring components (21). The two sets of temperature monitoring components (21) are respectively used to detect the temperature of the surface of the clearance surface (131) and the temperature of the surface of the oil cavity (132). The temperature adjustment system (3) includes a first cooling control component (31) and a second cooling control component (32). The first cooling control component (31) includes a first cooling flow channel (311). The second cooling control component (32) includes a second cooling flow channel (321). The first cooling flow channel (311) is arranged in the area of the bearing bush (13) corresponding to the oil cavity (132). The second cooling flow channel (321) is arranged in the area of the bearing bush (13) corresponding to the clearance surface (131). The first cooling flow channel (311) is connected with a first cooling fluid supply unit. The second cooling flow channel (321) is connected with a second cooling fluid supply unit. The cooling and temperature adjustment system (4) is used to control the temperature of the cooling fluid provided by the first cooling fluid supply unit and the second cooling fluid supply unit. The first cooling flow channel (311) is connected with a first input pipe (312) and a first output pipe (313). The first cooling fluid supply unit supplies flowing cooling fluid to the first cooling flow channel (311) through the first input pipe (312). The second cooling flow channel (321) is connected with a second input pipe (322) and a second output pipe (323). The second cooling fluid supply unit supplies flowing cooling fluid to the second cooling flow channel (321) through the second input pipe (322). Each of the first cooling flow channels (311) is a movable pipe (3101). Both ends of the movable pipe (3101) are connected with the first input pipe (312) and the first output pipe (313) through hoses. At the position of the bearing bush (13) corresponding to each movable pipe (3101), a distance adjustment movable cavity (137) is arranged. The movable pipe (3101) is slidably installed in the distance adjustment movable cavity (137). The distance adjustment movable cavity (137) is filled with a heat-conducting liquid. A control structure is also arranged on the hydrostatic spindle system (1) for controlling the sliding of the movable pipe (3101) in the distance adjustment movable cavity (137) to adjust the distance between the movable pipe (3101) and the inner wall of the oil cavity (132).

2. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to claim 1, wherein: The bearing shell (13) is installed in the shaft housing (11). A dynamic sealing structure (14) is provided between the two ends of the main shaft (12) and the bearing shell (13). The hydrostatic main shaft system (1) further includes an oil supply system and a lubricating oil passage. The lubricating oil passage includes an oil inlet passage (111) and an oil outlet passage (112) provided on the shaft housing (11), and a radial throttle hole (133) and an axial throttle hole (134) provided on the bearing shell (13). The radial throttle hole (133) and the axial throttle hole (134) are both arranged corresponding to the oil inlet passage (111) and are in communication. The radial throttle hole (133) extends inward into the oil cavity (132), and the axial throttle hole (134) extends toward the dynamic sealing structure (14). A return groove (136) is further provided in the bearing shell (13). The return groove (136) is used to communicate the space between the dynamic sealing structure (14) and the main shaft (12) with the clearance surface (131), and finally communicate with the oil outlet passage (112).

3. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to claim 2, characterized in that: Oil inlet throttle guiding grooves (135) are arranged at positions corresponding to the radial throttle hole (133) and the axial throttle hole (134) on the outer wall of the bearing shell (13). The oil inlet throttle guiding grooves (135) are arranged around the bearing shell (13), and the oil inlet throttle guiding grooves (135) are arranged corresponding to the oil inlet passage (111).

4. The regulator of a self-feedback and self-adjusting hydrostatic spindle according to claim 3, characterized in that: A first input guiding groove (3121), a first output guiding groove (3131), a second input guiding groove (3221) and a second output guiding groove (3231) are arranged on the outer wall of the bearing shell (13). Each of the first cooling channels (311) is communicated with the first input guiding groove (3121) and the first output guiding groove (3131) respectively. Each of the second cooling channels (321) is communicated with the second input guiding groove (3221) and the second output guiding groove (3231) respectively. The first input pipe (312), the first output pipe (313), the second input pipe (322) and the second output pipe (323) are all installed on the shaft housing (11). The first input guiding groove (3121) is communicated with the first input pipe (312), the first output guiding groove (3131) is communicated with the first output pipe (313), the second input guiding groove (3221) is communicated with the second input pipe (322), and the second output guiding groove (3231) is communicated with the second output pipe (323).

5. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to claim 3, characterized in that: The cooling and temperature regulating system (4) is a distributor. The distributor is fixedly installed on the shaft housing (11). Corresponding distribution chambers (43) are respectively provided for the second cooling channels (321) corresponding to the clearance surfaces (131) of each region and the first cooling channels (311) of each region of the oil cavity (132). The second cooling channels (321) of the clearance surfaces (131) of each region are respectively communicated with the corresponding distribution chambers (43) through the second input pipes (322), and the first cooling channels (311) of each region of the oil cavity (132) are respectively communicated with the corresponding distribution chambers (43) through the first input pipes (312).

6. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to claim 5, characterized in that: A partition plate (45) is slidably arranged in the distribution chamber (43). The distribution chamber (43) is divided by the partition plate (45) into a high-temperature flow channel (41) and a low-temperature flow channel (42) which are distributed vertically. The high-temperature flow channel (41) is connected to a high-temperature liquid source through a pipeline, and the low-temperature flow channel (42) is connected to a low-temperature liquid source through a pipeline. Distribution grooves (44) are arranged in the distribution chamber (43) corresponding to the positions of the second input pipe (322) or the first input pipe (312). A moving driver (46) is installed outside the distribution chamber (43), and the moving driver (46) is used to drive the partition plate (45) to move up and down.

7. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to claim 6, characterized in that: Two groups of pushing blocks (47) are further arranged in the distribution chamber (43) corresponding to the first cooling flow channel (311). The two groups of pushing blocks (47) are respectively located at both ends of the partition plate (45), and the partition plate (45) is bent and deformed by squeezing the partition plate (45). A pressure piston chamber (48) is also arranged at the position corresponding to the pushing block (47) in the distribution chamber (43). The pushing block (47) is slidably arranged in the pressure piston chamber (48), and the pressure piston chamber (48) is connected to an air inflation pump structure through a pipeline.

8. The adjuster of a self-feedback and self-adjusting hydrostatic spindle according to any one of claims 2 to 7, characterized in that: The temperature monitoring component (21) is provided with a plurality of temperature sensors corresponding to the temperature sensors in each oil chamber (132), and the plurality of temperature sensors are arranged along the circumferential direction of the bearing bush (13). The monitoring system (2) further includes a vibration monitoring component (22), and the vibration monitoring component (22) is embedded in the bearing bush (13). The vibration monitoring component (22) is used to detect the vibration when the main shaft (12) rotates and operates.

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