An ultra-thin double-sided spindle

Abstract

This invention discloses an ultra-thin double-sided turning spindle, belonging to the technical field of lathe machining equipment. The application includes a base with a through hole in the center; a spindle box rotatably disposed within the through hole of the base, with a tapered clamping member in the center for holding workpieces; an oil chamber end cap connected to the end of the spindle box where a pressure cylinder is located; a piston member including an outer ring and an inner ring, the outer ring being slidably disposed within the pressure cylinder; and a drive disc disposed at the opening end of the pressure cylinder and connected to the spindle box for driving the spindle box to rotate; wherein the outer ring divides the pressure cylinder into a buffer chamber and an oil chamber. Through this invention, by simultaneously embedding the spindle box, piston member, and drive disc within the base for integrated assembly, multiple functions such as clamping drive, rotational support, and motion buffering are highly integrated within a limited axial space, thereby significantly reducing the overall axial thickness of the spindle and facilitating the clamping and machining of shorter workpieces.

Description

Technical Field

[0001] This invention relates to an ultra-thin double-sided turning spindle, belonging to the technical field of lathe machining equipment. Background Technology

[0002] A double-sided turning spindle is a lathe clamping mechanism used to hold workpieces for double-sided machining. Its principle is to clamp the workpiece synchronously by double-end chucks, drive the spindle to rotate with the spindle motor, and rotate the workpiece. The two turrets feed according to the program, and turn both ends or both sides of the workpiece at the same time. There is no need to flip the workpiece during the entire machining process, and no secondary clamping is required. This can effectively improve machining efficiency and avoid errors caused by secondary clamping.

[0003] Most existing double-sided machining spindles use hydraulic or pneumatic / hydraulic clamps to hold workpieces. The overall thickness of the machining spindle is relatively thick, which makes it difficult to clamp and process some short workpieces. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to provide an ultra-thin double-sided machining spindle, which solves the problem that the existing double-sided machining spindle is difficult to process parts with short shaft lengths due to its thickness.

[0005] The technical problem to be solved by the present invention is achieved by the following technical solution: an ultra-thin double-sided machining spindle, including a base with a through hole in the middle; The spindle box is rotatably mounted in the through hole of the base, with a tapered clamping member in the middle for clamping the workpiece, and a groove on the outer ring as a pressure cylinder. The oil chamber end cap is disposed on the spindle box facing the opening end of the pressure cylinder; A piston component includes an outer ring portion and an inner ring portion, wherein the outer ring portion is slidably disposed within the pressure cylinder; A drive disc is disposed at the open end of the pressure cylinder and connected to the spindle box, and is used to drive the spindle box to rotate; The outer ring portion divides the pressure cylinder into a buffer chamber and an oil chamber.

[0006] By adopting the above technical solution, and simultaneously embedding the spindle box, piston components, and drive disc into the base for integrated assembly, multiple functions such as clamping drive, rotary support, and motion buffering are highly integrated within a limited axial space. This significantly reduces the overall axial thickness of the spindle, facilitating the clamping and processing of shorter workpieces and effectively expanding its applicability. Compared to the traditional method of using a separate hydraulic cylinder for pressure supply, this application achieves a more stable pressure supply by directly installing a corresponding pressure cylinder on the spindle box as the pressure supply source. Furthermore, the entire supply process does not require a separate external pressure cylinder, maximizing the reduction of the overall thickness of the double-sided machining spindle.

[0007] The present invention is further configured such that: the oil chamber is provided with a self-sealing hydraulic joint for pressurizing or depressurizing it, and a pressure-holding valve for maintaining pressure thereon.

[0008] By adopting the above technical solution, hydraulic oil can be quickly injected into the oil chamber through the self-sealing hydraulic joint, quickly clamping and fixing the workpiece arranged in the through hole in the middle of the clamping component. Simultaneously, with the addition of a pressure-holding valve, minor hydraulic oil leakage in the oil chamber can be compensated for by the pressure-holding valve, ensuring the stability of the clamping force. Traditional double-sided machining spindles do not have a pressure-holding function within their pressure cylinders; their pressure-holding time and maximum pressure are generally around 4 MPa. However, this application, through multiple symmetrically arranged pressure-holding valves, can continuously maintain the pressure inside the pressure cylinders when clamping the workpiece, with a maximum pressure supply of up to 8 MPa, effectively improving the stability of workpiece clamping and extending the pressure-holding time.

[0009] The present invention is further configured such that: a sinking groove is provided on the oil cavity end cap, and the outer ring portion abuts against the opening of the sinking groove to close it and form the oil cavity.

[0010] By adopting the above technical solution, the oil chamber end cover can be directly integrated into the oil chamber structure, eliminating the need for an additional independent oil cylinder body, further compressing the axial dimension of the main shaft, and further reducing the thickness of the entire vehicle main shaft.

[0011] The invention is further configured to include a flow guide channel, which is provided on the spindle box. The flow guide channel includes a first flow channel, a second flow channel, and a third flow channel that are interconnected after batch drilling.

[0012] By adopting the above technical solution, the internal flow channel is formed by drilling in batches and then connecting them, which eliminates the need for a complex casting process to embed the flow channel, thus effectively reducing the processing difficulty.

[0013] The invention is further configured to include a transition channel, which is provided on the end cap of the oil chamber. The transition channel includes a fourth flow channel, a fifth flow channel, and a sixth flow channel that are interconnected after being drilled in batches. The first flow channel, the second flow channel, the third flow channel, the fourth flow channel, the fifth flow channel, and the sixth flow channel are connected in sequence to connect the self-sealing hydraulic joint or pressure holding valve to the oil chamber.

[0014] By adopting the above technical solution, oil passages are directly opened on the spindle box and oil chamber end cover, eliminating the need for external hydraulic pipelines. This not only avoids pipeline interference when the spindle rotates, but also further reduces the radial space occupied, adapting to the compact layout of the spindle.

[0015] The present invention is further configured such that: at least one return spring is provided in the buffer cavity, one end of the return spring abuts against the piston and the other end abuts against the spindle box.

[0016] By adopting the above technical solution, the internal space of the buffer chamber can be fully utilized to install the return spring, eliminating the need for additional spring installation positions and further reducing axial dimensions. The return spring allows the piston to automatically slide back and reset after oil chamber depressurization, causing the clamping component to release the workpiece, thus simplifying the power system. Furthermore, the reverse buffering force provided by the return spring during clamping counteracts the impact of piston movement, resulting in smoother clamping action and reduced collision damage between the workpiece and the clamping component.

[0017] The present invention is further configured such that: the pressure holding valve includes a valve body and a pressure holding plug disposed in the valve body, and an elastic element is disposed between the pressure holding plug and the valve body.

[0018] By adopting the above technical solution and through the elastic force setting of the elastic element, when a slight leak occurs in the oil cavity, the volume in the oil cavity can be compressed by the pushing of the elastic element, so that the pressure in the oil cavity remains relatively constant, ensuring that the clamping force can be maintained continuously and stably.

[0019] The invention is further configured such that: a groove is provided at the end of the clamping member away from the cone angle, and a spiral engaging part is provided on the piston member to engage with the groove.

[0020] By adopting the above technical solution, the clamping components can be quickly installed and disassembled, facilitating subsequent maintenance.

[0021] The present invention is further configured such that: the spiral snap-fit ​​portion is transitionally connected to an inner chamfered surface, and the end of the clamping member is provided with an abutting chamfer that abuts against the inner chamfered surface.

[0022] By adopting the above technical solution, the inner chamfered surface can play a guiding and centering role during assembly, reducing the assembly difficulty of the screw clamp and improving assembly efficiency and coaxiality. When the clamping component pushes the clamped workpiece through the piston component, the inner chamfered surface and the abutment chamfer can disperse the contact stress, avoid the wear and deformation of parts caused by local stress concentration, and extend the service life of the parts.

[0023] The present invention is further configured such that: a transmission gap is reserved between the outer ring of the drive disk and the inner ring of the base, and a transmission component that can extend into the transmission gap is provided at the bottom of the base, the transmission component being used to drive the drive disk to rotate.

[0024] By adopting the above technical solution, a transmission pair is set up by utilizing the radial assembly gap between the outer ring of the drive disc and the inner ring of the base. The transmission component extends radially from the bottom of the base for driving, without occupying the axial space of the main shaft, and further reducing the overall axial thickness.

[0025] The beneficial effects of this invention are: The entire main shaft is designed with ultra-thin integration as its core feature. By directly opening oil circuits and oil chambers on the main shaft box and oil chamber end cover, a highly integrated hydraulic power source is formed, which solves the technical pain point of traditional double-sided vehicle main shafts having a large axial volume and difficulty in clamping short-length components.

[0026] By nesting and integrating the rotating support, clamping drive, motion buffer, hydraulic flow channel, and transmission mechanism into the internal space of the base and spindle box, the axial dimension is reduced from the source. By adopting a nested structure in which the base is embedded in the spindle box, the axial thickness is reduced, and the outer ring of the piston is used as a separator for the pressure cylinder, thereby simultaneously achieving the dual functions of pressure drive and buffer damping within the pressure cylinder. Attached Figure Description

[0027] Figure 1 This is an exploded view of the present invention; Figure 2 This is a schematic diagram of the internal three-dimensional structure of the spindle box of the present invention; Figure 3 This is a schematic diagram of the internal three-dimensional structure of the spindle box of the present invention; Figure 4 This is a schematic diagram of the internal three-dimensional structure of the piston component of the present invention; Figure 5 This is a three-dimensional structural diagram of the clamping component of the present invention; Figure 6 This is a three-dimensional structural diagram of the oil cavity end cap of the present invention; Figure 7 This is a schematic diagram of the internal three-dimensional structure of the pressure-holding valve of the present invention; Figure 8 This is a schematic diagram showing the installation relationship between the drive disk and the base of the present invention.

[0028] In the diagram: 100, base; 200, spindle box; 210, pressure cylinder; 220, guide channel; 221, first flow channel; 222, second flow channel; 223, third flow channel; 300, clamping component; 310, slot; 320, chamfered abutment; 400, piston component; 410, inner ring; 420, outer ring; 430, spiral snap-fit ​​part; 440, inner chamfered surface; 500, oil chamber end cover; 510, sinker; 520, transition channel; 52 1. Fourth flow channel; 522. Fifth flow channel; 523. Sixth flow channel; 600. Drive disc; 700. Oil chamber; 800. Buffer chamber; 900. Self-sealing hydraulic joint; 10. Pressure holding valve; 101. Valve body; 102. Pressure holding plug; 103. Elastic element; 11. Return spring; 12. Water-spinning tray; 13. Sealing plate; 14. Workpiece; 15. Transmission clearance; 16. Double-sided hinged main bearing; 17. Lubrication hole; 18. Lubrication channel; 19. Sealing groove. Detailed Implementation

[0029] To facilitate a clear understanding of the technical means, creative features, objectives, and effects of this invention, the invention will be further described below in conjunction with specific illustrations.

[0030] like Figure 1 As shown, an ultra-thin double-sided lathe spindle includes a base 100 for supporting and fixing on a lathe. A through hole is opened in the middle of the base 100, and a double-sided hinged main bearing 16 is fixedly installed in the through hole. A spindle box 200 is provided on the inner ring of the double-sided hinged main bearing 16. A tapered through hole is opened in the middle of the spindle box 200, and a tapered clamping member 300 is provided in the tapered through hole. The outer surface of the entire clamping member 300 is in contact with the inner surface of the tapered through hole, and a retractable clamping through hole is reserved in the middle. One side of the clamping member 300... The end is connected to a piston 400 for pushing it to slide along the axial direction of the spindle box 200. The piston 400 includes an inner ring portion 410 connected to the clamping member 300 and an outer ring portion 420 connected to the spindle box 200. Under the push of the piston 400, the clamping member 300 slides along the central axis of the spindle box 200. When sliding towards the cone angle, the cone-shaped inner surface contracts inward, so that after the clamping member 300 contracts, the clamping through hole in its middle contracts synchronously, thereby realizing the rapid clamping of the workpiece 14.

[0031] like Figure 2 and Figure 3 As shown, in the above embodiment, a pressure cylinder 210 is provided on the spindle box 200, and the outer ring 420 is slidably disposed in the pressure cylinder 210, dividing the pressure cylinder 210 into two parts: a buffer chamber 800 and an oil chamber 700. The oil chamber 700 is close to the opening end of the pressure cylinder 210, and an oil chamber end cap 500 is installed at the opening end of the pressure cylinder 210 for sealing.

[0032] like Figure 1 As shown, a drive disc 600 is also concentrically arranged on the outer ring of the oil chamber end cover 500. The drive disc 600 is fixedly connected to the spindle box 200 by bolts. The spindle box 200 can be driven to rotate by the drive disc 600, thereby controlling the clamping member 300 to drive the workpiece 14 to rotate.

[0033] During the clamping process of workpiece 14, workpiece 14 is first inserted into the middle through hole of clamping member 300. Then, by continuously injecting hydraulic oil into oil chamber 700, the outer ring 420 on piston member 400 is pushed to slide towards the depth of pressure cylinder 210, which drives the clamping member 300 connected to it to slide towards its cone angle direction. Finally, under the guidance and contraction of the tapered through hole of spindle box 200, clamping member 300 retracts inward, and workpiece 14 is clamped and fixed.

[0034] like Figure 3 As shown, on the spindle box 200, on the outer wall of the pressure cylinder 210 with a larger diameter, a flow channel 220 is provided, including a first flow channel 221, a second flow channel 222 and a third flow channel 223 that are perpendicularly connected to each other. The three flow channels are formed by drilling in batches and then connected to each other to finally form the flow channel 220.

[0035] Similarly, using the same drilling method, such as Figure 6 As shown, a fourth flow channel 521, a fifth flow channel 522, and a sixth flow channel 523 are opened in batches on the end cover of the fuel tank. The three flow channels are interconnected to form a transition channel 520.

[0036] In this embodiment, the third flow channel 223 and the fourth flow channel 521 are interconnected, and a self-sealing hydraulic connector 900 or a pressure holding valve 10 is provided at the inlet of the first flow channel 221. Both are threaded connections. There are two self-sealing hydraulic connectors 900 and two pressure holding valves 10, symmetrically arranged on the spindle box 200 with the central axis of the clamping member 300 as the center of symmetry. Specifically, the self-sealing hydraulic connector 900 is a one-way valve; one serves as an outlet to supply hydraulic oil to the pressure chamber, and the other as an inlet to extract hydraulic oil from the pressure chamber. The symmetrical arrangement of the two self-sealing hydraulic connectors 900 ensures a relatively stable dynamic balance during the rotation of the entire spindle, preventing unnecessary wear on the shaft-related components due to local center of gravity shift. Similarly, the symmetrical arrangement of the two pressure holding valves 10 also prevents the spindle center of the entire spindle box 200 from shifting, ensuring drive stability.

[0037] In other embodiments, for operating conditions where the weight of the valve itself has little or no impact on the overall weight, the number of pressure-holding valves 10 can also be set to one. Similarly, to increase the maximum adjustable volume during overall pressure holding, the number of pressure-holding valves 10 can also be three or more.

[0038] like Figure 7 As shown, the pressure holding valve 10 specifically includes a valve body 101 threadedly connected to the spindle box 200. The valve body 101 has an internal cavity, and a pressure holding plug 102 is slidably disposed in the cavity. An elastic element 103 is also disposed between the pressure holding plug 102 and the bottom surface of the internal cavity of the valve body 101. The pressure holding plug 102 is directly connected to the oil chamber 700. The pressure generated by the hydraulic oil in the oil chamber 700 can directly act on the pressure holding plug 102. If hydraulic oil leakage occurs, a partial gap will appear in the oil chamber 700 due to the hydraulic oil leakage, resulting in a decrease in the pressure difference generated by the hydraulic oil. This allows the elastic element 103 located in the inner cavity of the valve body 101 to push the pressure holding plug 102 towards the oil chamber 700 through elasticity, compressing the volume of the oil chamber 700, thereby reducing the pressure difference change in the oil chamber 700 caused by the hydraulic oil leakage, and ensuring that the workpiece 14 can be stably clamped.

[0039] It should be noted that in the above embodiment, the pressure holding valve 10 is fixed to the spindle box 200 by a threaded connection, and the end of the pressure holding plug 102 abuts against the opening of the first flow channel 221. After hydraulic oil is injected into the oil chamber 700, it can be pushed by the pressure of the hydraulic oil to slide a certain distance away from the opening of the first flow channel 221, so that a certain gap is reserved between the pressure holding plug 102 and the opening of the first flow channel 221. This allows the elastic element 103 to push the pressure holding plug 102 to slide towards the opening of the first flow channel 221 if pressure leakage occurs in the oil chamber 700, thereby compressing the volume in the oil chamber 700 and avoiding large pressure fluctuations that could affect the stability of the workpiece 14 clamping.

[0040] like Figure 6As shown, the oil chamber end cover 500 is provided with a recessed groove 510. When the oil chamber end cover 500 is installed, the opening of the recessed groove 510 faces the pressure cylinder 210. The outer ring 420 of the piston 400 is clamped between the recessed groove 510 and the pressure cylinder 210 and can slide within the pressure cylinder 210. The inner ring 410 of the piston 400 is slidably engaged with the central through hole of the oil chamber end cover 500. Its outer surface is in contact with the inner surface of the central through hole of the oil chamber end cover 500 and can slide relative to each other. The recessed groove 510 on the oil chamber end cover 500 and the pressure cylinder 210 separated by the outer ring 420 together form the oil chamber 700. At the same time, when the oil chamber end cover 500 is installed, the third flow channel 223 and the fourth flow channel 521 are aligned and connected, so that the oil chamber 700 is connected to the external self-sealing hydraulic joint 900 or pressure holding valve 10 through the guide channel 220 and the transition channel 520.

[0041] like Figure 8 As shown, the drive disc 600 is located at one end near the opening of the pressure cylinder 210, and the drive disc 600 is fixedly connected to the other end face of the spindle box 200 by bolts. In this embodiment, the drive disc 600 is specifically a synchronous pulley, and its outer ring can be connected to the motor to realize power transmission after being fitted with a synchronous belt, so as to drive the workpiece 14 to rotate.

[0042] In other embodiments, the drive disk 600 may also be a transmission component such as a gear, and its rotation is controlled by a gear that meshes with the drive disk 600 at the bottom of the base 100, thereby controlling the rotation of the clamped workpiece 14.

[0043] It should be noted that in the above embodiments, the drive components used to rotate the drive disk 600 are all located below the base 100. Specifically, a transmission gap 15 is reserved between the outer ring of the drive disk 600 and the inner ring of the base 100. Simultaneously, a transmission component extending into the transmission gap 15 is provided at the bottom of the base 100. This component can be a synchronous belt or a gear, depending on the specific drive method used. The bottom of the transmission gap 15 is a connecting port on the base 100. The transmission component can extend into the transmission gap 15 through the connecting port at the bottom of the base 100 to transmit power to the drive disk 600. In this embodiment, by directly reserving the transmission gap 15 on the base 100 itself, and using the transmission component at the bottom of the base 100 as a power source, the overall structural compactness can be greatly improved, further reducing the thickness of the entire double-sided machining spindle and increasing the clamping applicability range of the workpiece 14 axis length.

[0044] like Figure 1As shown, at least one return spring 11 is installed in the buffer cavity 800. One end of the return spring 11 abuts against the piston 400, and the other end abuts against the spindle box 200. A single return spring 11 can be arranged around the entire inner surface of the pressure cylinder 210, with both ends abutting against the piston 400 and the bottom surface of the pressure cylinder 210 respectively, thus ensuring uniform force on the piston 400 during subsequent reset. Alternatively, multiple return springs can be arranged circumferentially around the inner surface of the pressure cylinder 210. In this embodiment, multiple return springs 11 are installed in a multiple arrangement, with two springs per group, equidistantly arranged circumferentially within the pressure cylinder 210, for a total of five groups. It should be noted that the specific number of return springs 11 arranged in this embodiment is not limited; the above embodiment only provides a preferred solution applicable to specific working conditions.

[0045] By setting a return spring 11, the piston 400 can quickly reset after pressure relief in the oil chamber 700. This allows the piston 400 to slide along the clamping member 300 even when not hydraulically pushed, keeping the central through hole open and preventing parts from jamming. Furthermore, the return spring 11 provides constant thrust to the piston 400 when it is pushed, improving the stability of the clamping action and making it smoother. Based on the above embodiment, several abutment holes are provided circumferentially on the outer ring 420 end face of the piston 400 to abut the return spring 11. These holes constrain the return spring 11, preventing it from shifting and ensuring uniform force distribution during subsequent piston 400 reset.

[0046] like Figure 4 and Figure 5 As shown, a slot 310 is provided at the end of the clamping member 300 away from the cone angle, and an abutment chamfer 320 is provided at this end. At the same time, a spiral engaging part 430 is provided in the middle of the piston member 400, and an inner chamfer surface 440 with the same inclination angle as the abutment chamfer 320 is provided in the middle opening. When installing the clamping member 300, the end with the abutment chamfer 320 and the slot 310 is aligned with the spiral engaging part 430. By rotating the clamping member 300, the slot 310 gradually engages with the spiral engaging part 430. The clamping member 300 is continuously controlled to rotate relative to the piston member 400 until the abutment chamfer 320 and the inner chamfer surface 440 abut against each other, and the installation of the clamping member 300 is completed. In the above embodiment, the mutual contact between the inner chamfered surface 440 and the abutting chamfer 320 allows the clamping member 300 to be guided during installation. At the same time, the engagement between the slot 310 and the spiral engagement part 430 allows the clamping member 300 to be quickly installed onto the piston member 400, improving the overall assembly efficiency.

[0047] like Figure 1As shown, a sealing plate 13 and a water-throwing plate 12 are respectively provided at both ends of the spindle box 200. The water-throwing plate 12 can improve the efficiency of the coolant being thrown out when the workpiece 14 is being cut, and prevent the coolant from entering the interior of the spindle and causing corrosion of the cutting fluid.

[0048] Specifically, the outer ring of the water-spinning plate 12 and the outer ring of the base 100 are provided with U-shaped sealing grooves 19. After the water-spinning plate 12 is fixed to the end face of the outer ring of the base 100 by bolts, the openings of the two sealing grooves 19 face each other and interlock to form a labyrinth sealing structure. In this embodiment, water-spinning plates 12 are installed on both the left and right end faces of the base 100. After each water-spinning plate 12 is installed on the end face of the base 100, the labyrinth sealing structure formed by its splicing with the sealing grooves 19 on the base 100 can effectively prevent external coolant from entering the interior of the base 100, and has a high degree of sealing performance. Moreover, during rotation, its own tilt angle can cause the coolant to generate centrifugal force that diffuses outward, further throwing the coolant out.

[0049] Furthermore, an annular lubrication channel 18 is provided on the outer ring of the double-sided hinged main bearing 16, and a lubrication hole 17 is provided on the side of the base 100. After the double-sided hinged main bearing 16 is installed inside the base 100, it forms a sealing ring with the inner surface of the base 100. The lubrication hole 17 on the side of the base 100 can communicate with the lubrication channel 18. When the double-sided hinged main bearing 16 rotates, oil mist is sprayed into the annular lubrication channel 18 through the lubrication hole 17. After the oil mist enters the lubrication channel through the lubrication hole 17, it can flow under the drive of the double-sided hinged main bearing 16, thereby lubricating the double-sided hinged main bearing 16. To a certain extent, it can also cool it down and prevent the double-sided hinged main bearing 16 from accumulating heat during long-term rotation, which would affect the stability of the workpiece 14 rotation.

[0050] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments, and various changes and modifications can be made without departing from the spirit and scope of the invention, all of which fall within the scope of protection claimed by the present invention. The scope of protection of the present invention is defined by the appended claims and their equivalents.

Claims

1. An ultra-thin double-sided machining spindle, characterized in that, include: The base (100) has a through hole in the middle; The spindle box (200) is rotatably disposed in the through hole of the base (100), and a tapered clamping member (300) for clamping the workpiece (14) is provided in the middle, and a groove is opened on the outer ring as a pressure cylinder (210). The oil chamber end cap (500) is disposed on the spindle box (200) with its open end facing the pressure cylinder (210); The piston component (400) includes an outer ring portion (420) and an inner ring portion (410), wherein the outer ring portion (420) is slidably disposed within the pressure cylinder (210); A drive disc (600) is disposed at the open end of the pressure cylinder (210) and connected to the spindle box (200) for driving the spindle box (200) to rotate; The outer ring (420) divides the pressure cylinder (210) into a buffer chamber (800) and an oil chamber (700).

2. The ultra-thin double-sided machining spindle according to claim 1, characterized in that: The oil chamber (700) is equipped with a self-sealing hydraulic joint (900) for pressurizing or depressurizing it, and a pressure-holding valve (10) for maintaining its pressure.

3. The ultra-thin double-sided machining spindle according to claim 2, characterized in that: The oil chamber end cap (500) is provided with a sinking groove (510), and the outer ring (420) abuts against the opening of the sinking groove (510) to close it and form the oil chamber (700).

4. The ultra-thin double-sided machining spindle according to claim 3, characterized in that: It also includes a flow channel (220) on the spindle box (200), the flow channel (220) including a first flow channel (221), a second flow channel (222) and a third flow channel (223) that are interconnected after batch drilling.

5. The ultra-thin double-sided machining spindle according to claim 4, characterized in that: It also includes a transition channel (520) on the oil chamber end cap (500). The transition channel (520) includes a fourth flow channel (521), a fifth flow channel (522), and a sixth flow channel (523) that are interconnected after batch drilling. The first flow channel (221), the second flow channel (222), the third flow channel (223), the fourth flow channel (521), the fifth flow channel (522), and the sixth flow channel (523) are connected in sequence to connect the self-sealing hydraulic joint (900) or the pressure holding valve (10) to the oil chamber (700).

6. The ultra-thin double-sided machining spindle according to claim 1, characterized in that: At least one return spring (11) is provided in the buffer cavity (800). One end of the return spring (11) abuts against the piston (400), and the other end abuts against the spindle box (200).

7. The ultra-thin double-sided machining spindle according to claim 2, characterized in that: The pressure holding valve (10) includes a valve body (101) and a pressure holding plug (102) disposed in the valve body (101), and an elastic element (103) is disposed between the pressure holding plug (102) and the valve body (101).

8. The ultra-thin double-sided machining spindle according to claim 1, characterized in that: The clamping member (300) has a slot (310) at the end away from the cone angle, and the piston member (400) has a spiral engaging part (430) that engages with the slot (310).

9. The ultra-thin double-sided machining spindle according to claim 8, characterized in that: The spiral snap-fit ​​part (430) is transitionally connected to an inner chamfered surface (440), and the end of the clamping member (300) is provided with an abutting chamfer (320) that abuts against the inner chamfered surface (440).

10. The ultra-thin double-sided machining spindle according to claim 1, characterized in that: A transmission gap (15) is reserved between the outer ring of the drive disk (600) and the inner ring of the base (100). The bottom of the base (100) is provided with a transmission member that can extend into the transmission gap (15). The transmission member is used to drive the drive disk (600) to rotate.

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