A rotary type device provides a general means of supplying three hydraulic pressures in the shaft

Abstract

The utility model relates to the technical field of rotary equipment tooling, especially to a kind of universal device of rotary equipment provides three-way hydraulic pressure in shaft;Including connecting sleeve, rotary mandrel, shell, back cover, front bearing, rear bearing, sealing system;Three independent hydraulic passages are formed in rotary mandrel, and hydraulic communication is established with oil supply connector C, oil supply connector AB respectively;Single-tooth framework sealing combination A and mountain type framework sealing combination constitute first sealing pair;Mountain type framework sealing combination and single-tooth framework sealing combination B constitute the structure of second sealing pair, reach the technical contradiction of current technology cannot take into account high speed, high pressure and multi-pass, so that the device can be in the stable operation under the condition that speed is not less than 1500 revolutions per minute, hydraulic pressure is not less than 7.0 megapascal, and leakage is controlled at low level, thereby the reliability, efficiency and life effect of rotary equipment shaft hydraulic power provision are significantly improved.

Description

Technical Field

[0001] This utility model relates to the technical field of tooling for rotary equipment, and in particular to a universal device for providing three-way hydraulic pressure within the shaft of rotary equipment. Background Technology

[0002] In the field of mechanical manufacturing, rotary equipment (such as the spindle of a CNC machine tool) often requires multiple hydraulic pressures within its rotating shaft to drive tooling fixtures. With the increasing demands for equipment speed and machining accuracy, higher requirements are placed on the speed, pressure, and number of hydraulic passages within the shaft. Currently, there are two main types of existing technical solutions in this field. The first type is a low-speed rotary head using O-ring seals. Its disadvantage is that when the number of hydraulic passages reaches three or more, its maximum permissible speed is usually no more than 100 rpm, making it difficult to meet the needs of high-speed machining. The second type is a high-speed rotary head using a hard-seal structure. While it can adapt to higher speeds, its maximum pressure resistance is usually no more than 3.5 MPa, and it suffers from significant leakage, while also having higher manufacturing costs. It is evident that existing technical solutions present a technical contradiction in terms of the three key performance parameters of speed, pressure, and number of passages. There is a lack of a device that can simultaneously meet the requirements of high speed (e.g., not less than 1500 rpm), high pressure (e.g., not less than 7.0 MPa), and stable hydraulic power supply through multiple passages (three or more). This has become a technical bottleneck restricting the performance improvement of related equipment. Utility Model Content

[0003] The purpose of this invention is to provide a universal device for providing three-way hydraulic pressure within the shaft of rotating equipment, addressing the shortcomings of existing technologies. This solves the technical contradiction that existing technologies cannot simultaneously handle high speed, high pressure, and multiple pathways, enabling the device to operate stably under conditions of a speed of not less than 1500 rpm and a hydraulic pressure of not less than 7.0 MPa, while keeping leakage at a low level. This significantly improves the reliability, efficiency, and lifespan of the hydraulic power provided within the shaft of rotating equipment.

[0004] To achieve the above objectives, the technical solution adopted by this utility model is as follows: including a connecting sleeve, a rotating spindle, a housing, a rear cover, a front bearing, a rear bearing, and a sealing system; The connecting sleeve is fixedly connected to the shaft of the rotary equipment and drives the rotary spindle to rotate synchronously; The housing includes a front housing and a rear housing that are fixedly connected to each other. The housing and the rear cover constitute a stationary part and the rotating spindle is rotatably supported by the front bearing and the rear bearing. The housing is provided with an oil supply connector C, an oil supply connector AB, and an oil return connector; The rotary spindle has three independent hydraulic channels that are hydraulically connected to oil supply connector C and oil supply connector AB respectively. The sealing system is disposed in the annular gap between the rotary mandrel and the housing, and includes a single-tooth skeleton seal assembly A, a mountain-shaped skeleton seal assembly and a single-tooth skeleton seal assembly B arranged sequentially along the axial direction of the rotary mandrel; The single-tooth skeleton seal assembly A and the mountain-shaped skeleton seal assembly form a first seal pair, which are used to seal the area between the oil supply joint AB corresponding to the oil passage and the oil supply joint C corresponding to the oil passage. The mountain-shaped skeleton seal assembly and the single-tooth skeleton seal assembly B constitute a second seal pair, used to seal the area between the oil supply joint C corresponding to the oil passage and the return oil joint located in the return oil zone.

[0005] Furthermore, both the front and rear housings are made of aluminum alloy.

[0006] Furthermore, the sealing lips of the single-tooth skeleton seal assembly A, the mountain-shaped skeleton seal assembly, and the single-tooth skeleton seal assembly B are all oriented towards the oil passage corresponding to the oil supply connector C.

[0007] Furthermore, the sealing system also includes O-rings for achieving a static seal, including O-ring A disposed between the front housing and the rear housing, and O-ring B disposed between the rear housing and the rear cover.

[0008] Furthermore, the device is configured to operate continuously under conditions where the rotational speed is higher than rpm and the hydraulic pressure is higher than MPa, and the leakage rate of the device is less than ml / min when operating continuously under these conditions.

[0009] Furthermore, the front housing and the rear housing are fixedly connected by a plurality of circumferentially evenly arranged hexagonal screws.

[0010] Furthermore, the oil return connector is disposed on the rear cover and located on the side of the single-tooth skeleton seal assembly B facing away from the mountain-shaped skeleton seal assembly.

[0011] The device comprises a connecting sleeve, a rotating spindle, a housing, a rear cover, a front bearing, a rear bearing, and a sealing system. The connecting sleeve is fixedly connected to the rotating shaft and drives the rotating spindle to rotate synchronously. The housing includes a front housing and a rear housing fixedly connected to each other. The housing and the rear cover form a stationary part, and the rotating spindle is rotatably supported by the front and rear bearings. The housing is provided with an oil supply connector C, an oil supply connector AB, and an oil return connector. Three independent hydraulic channels are formed inside the rotating spindle, which are hydraulically connected to the oil supply connector C and the oil supply connector AB, respectively. The sealing system is located in the annular gap between the rotating spindle and the housing, and includes a single-tooth skeleton seal assembly A, a mountain-shaped skeleton seal assembly, and a single-tooth skeleton seal assembly arranged sequentially along the axial direction of the rotating spindle. The frame sealing assembly B; the single-tooth frame sealing assembly A and the mountain-shaped frame sealing assembly form a first sealing pair, used to seal the area between the oil supply joint AB and the corresponding oil supply joint C; the mountain-shaped frame sealing assembly and the single-tooth frame sealing assembly B form a second sealing pair, used to seal the area between the oil supply joint C and the return oil area where the return oil joint is located. This structure solves the technical contradiction of existing technologies being unable to simultaneously handle high speed, high pressure, and multiple passages, enabling the device to operate stably under conditions of a speed of not less than 1500 rpm and a hydraulic pressure of not less than 7.0 MPa, while controlling leakage at a low level, thereby significantly improving the reliability, efficiency, and lifespan of the hydraulic power provided within the shaft of rotating equipment. Attached Figure Description

[0012] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0013] Figure 1 A cross-sectional view of a general device for providing three-way hydraulic pressure within the shaft for rotating equipment according to embodiments of this utility model; Figure 2 This is a schematic diagram of the input port of an embodiment of the present utility model; Figure 3 This is a schematic diagram of the output port of an embodiment of the present utility model; Figure 4 This is an exploded view of the structure of an embodiment of the present invention.

[0014] Figure label: 1. Connecting sleeve; 2. Rotary spindle; 3. Front housing; 4. Rear housing; 5. Rear cover; 6. Front bearing; 7. Rear bearing; 8. Single tooth skeleton seal assembly A; 9. Mountain-shaped skeleton seal assembly B; 10. Oil return connector; 11. Oil supply connector C; 12. Oil supply connector AB; 13. O-ring A; 14. O-ring B; 15. O-ring C; 16. Socket head screw AB; 17. Detailed Implementation

[0015] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments.

[0016] In the description of this utility model, it should be noted that the orientation or positional relationship indicated by terms such as "center", "up", "down", "left", "right", "vertical", "horizontal", "inner", and "outer" are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0017] A general-purpose device for providing three hydraulic pressures within the shaft of rotating equipment, such as... Figures 1-4 As shown, it includes a connecting sleeve 1, a rotating spindle 2, a housing, a rear cover 5, a front bearing 6, a rear bearing 7, and a sealing system; The connecting sleeve 1 is fixedly connected to the shaft of the rotary equipment and drives the rotary spindle 2 to rotate synchronously; The housing includes a front housing 3 and a rear housing 4 that are fixedly connected to each other. The housing and the rear cover 5 constitute a stationary part, and the rotating spindle 2 is rotatably supported by the front bearing 6 and the rear bearing 7. The housing is provided with an oil supply connector C12, an oil supply connector AB13, and an oil return connector 11; The rotary spindle 2 has three independent hydraulic channels that are hydraulically connected to the oil supply connector C12 and the oil supply connector AB13 respectively. The sealing system is disposed in the annular gap between the rotary mandrel 2 and the housing, and includes a single-tooth skeleton seal assembly A8, a mountain-shaped skeleton seal assembly 9 and a single-tooth skeleton seal assembly B10 arranged sequentially along the axial direction of the rotary mandrel 2; The single-tooth skeleton sealing assembly A8 and the mountain-shaped skeleton sealing assembly 9 form a first sealing pair, which are used to seal the area between the oil supply joint AB13 corresponding oil passage and the oil supply joint C12 corresponding oil passage. The mountain-shaped skeleton sealing assembly 9 and the single-tooth skeleton sealing assembly B10 form a second sealing pair, which are used to seal the area between the oil supply joint C12 corresponding to the oil passage and the return oil joint 11 located in the return oil zone.

[0018] Specifically, the rotating spindle 2 is provided with output ports A, B, and C. The oil supply connector C12 on the housing serves as input port C, and the oil supply connectors AB13 are two identical oil supply joints, serving as input ports A and B respectively. The three oil ports at the end of the rotating spindle 2 serve as output ports A, B, and C respectively, with output ports A, B, and C corresponding one-to-one with input ports A, B, and C. This device achieves reliable sealing under high-speed and high-pressure conditions by employing a specific combined sealing system composed of a single-tooth skeleton seal assembly A8, a mountain-shaped skeleton seal assembly 9, and a single-tooth skeleton seal assembly B10, and precisely defining their axial arrangement and functional division. Compared with the hard seal structure commonly used in existing high-speed rotary devices, this combined sealing method can operate stably at speeds up to 1500 rpm and hydraulic pressures up to 7.0 MPa. Its maximum pressure resistance is significantly higher than the existing high-speed solution of 3.5 MPa mentioned in the background art, while also solving the problem of large leakage in the latter. Furthermore, this device successfully integrates three independent hydraulic channels within the compact rotating spindle 2, and utilizes the aforementioned specific sealing combination to achieve effective isolation and transmission of the three hydraulic channels. This overcomes the technical bottleneck in the prior art where low-speed rotary machines using O-ring seals cannot exceed 100 rpm in the case of three or more channels, achieving a breakthrough in both the number of channels and speed performance. Moreover, this device combines a specific sealing combination with a multi-channel oil passage structure, producing a synergistic technical effect. Specifically, the mountain-shaped skeleton seal combination 9, due to its structural characteristics, can better withstand working conditions with double-sided or pressure fluctuations. It is positioned at a critical location between the two pressure oil channels and the return oil zone, and works in conjunction with the single-tooth skeleton seal combinations A8 and B10 on both sides to construct a highly efficient dynamic sealing system. This system not only ensures the sealing reliability of the device at pressures up to 7.0 MPa, controlling leakage to a low level, for example, less than 100 ml / min under the working conditions described in the embodiment, but also ensures that the surface temperature rise of the device is controlled during long-term operation. This technical solution creates a new structural solution through specific design of the sealing element type, arrangement position and functional coordination relationship. It comprehensively solves the technical contradictions in the existing technology that cannot take into account high speed, high pressure, multiple passages and low leakage, and achieves unexpected technical results, filling a market gap.

[0019] As a preferred embodiment of the above, such as Figures 1-4 As shown, both the front housing 3 and the rear housing 4 are made of aluminum alloy.

[0020] Specifically, during the assembly process, both the front housing 3 and the rear housing 4 are made of aluminum alloy and formed by casting and machining. The front housing 3 is used to accommodate and position the front bearing 6, and it has threaded holes machined on it for installing oil supply connectors AB13 and C12. The rear housing 4 is fixedly connected to the front housing 3 by hexagon socket head cap screws 17, together forming the main structure supporting the rotating spindle 2. The rear cover 5 is fixed to the rear end of the rear housing 4 to seal the cavity and support the rear bearing 7. The rotating spindle 2 is supported within the housing formed by the front housing 3 and the rear housing 4 through the front bearing 6 and the rear bearing 7. The connecting sleeve 1 is connected to the front end of the rotating spindle 2 to transmit torque. Using aluminum alloy to manufacture the front housing 3 and the rear housing 4 can significantly reduce the overall weight of the device compared to traditional materials such as cast iron or carbon steel. This characteristic helps to reduce the inertial load on the connecting sleeve 1 and the rotating spindle 2 assembly during high-speed rotation, and has a positive impact on maintaining the operational stability of the front bearing 6 and the rear bearing 7 under high-speed conditions. At the same time, aluminum alloy has good thermal conductivity. During device operation, the sealing system, including the single-tooth skeleton seal assembly A8, the mountain-shaped skeleton seal assembly 9, and the single-tooth skeleton seal assembly B10, generates frictional heat due to high-speed relative motion with the rotating spindle 2. The aluminum alloy housing can more effectively conduct the heat generated here to the external environment, helping to control the temperature rise of the device during continuous operation. This is beneficial for maintaining stable hydraulic oil viscosity, protecting the performance of sealing materials, and thus ensuring the reliability of the sealing system during long-term operation.

[0021] As a preferred embodiment of the above, such as Figures 1-4 As shown, the sealing lips of the single-tooth skeleton seal assembly A8, the mountain-shaped skeleton seal assembly 9, and the single-tooth skeleton seal assembly B10 are all oriented toward the oil passage corresponding to the oil supply connector C12.

[0022] Specifically, during the assembly of the sealing system, the single-tooth skeleton seal assembly A8 is pressed into the inner hole of the front housing 3, with its sealing lip facing inwards, i.e., aligned with the oil passage direction corresponding to the oil supply connector C12. Next, the mountain-shaped skeleton seal assembly 9 is pressed into the inner hole of the rear housing 4, with its sealing lip also facing the oil passage direction corresponding to the oil supply connector C12. Finally, the single-tooth skeleton seal assembly B10 is pressed into the inner hole of the rear housing 4 or the rear cover 5, with its sealing lip also facing the oil passage direction corresponding to the oil supply connector C12. Thus, the lip directions of the three sets of seals are unified. Firstly, this unified lip orientation design allows the sealing system to more effectively cope with the pressure conditions of specific oil passages. When the oil pressure corresponding to the oil supply connector C12 is considered the main or highest pressure source in the system, all sealing lips face the pressure source. This allows the fluid pressure to make the lips fit more tightly against the sealing surface of the rotating spindle 2, thus forming a more reliable dynamic seal under high-speed rotation. This directly contributes to achieving the low leakage requirement under 7.0 MPa high pressure described in the background art. Secondly, this directional arrangement optimizes the pressure distribution and leakage path. The uniform orientation of the sealing lips, in conjunction with the structure of the first and second sealing pairs, constructs a clear pressure gradient barrier. This helps guide possible minor leaks to a controllable area and ensures directional sealing resistance between the oil supply lines corresponding to the oil supply connector AB13 and C12, and between the oil supply line corresponding to C12 and the return oil area, thereby synergistically ensuring the stable output of the three hydraulic pressures. Finally, this preferred scheme, through specific and unified planning of the installation direction of key sealing elements, enhances the synergistic sealing efficiency and reliability of the entire sealing system under complex high-speed and high-pressure conditions, providing key support for the device to achieve excellent overall performance.

[0023] As a preferred embodiment of the above, such as Figures 1-4 As shown, the sealing system also includes O-rings for achieving static sealing, including O-ring A14 disposed between the front housing 3 and the rear housing 4, and O-ring B15 disposed between the rear housing 4 and the rear cover 5.

[0024] Specifically, O-rings for static sealing are provided at the mating surfaces of stationary components of the device. Specifically, a mounting groove is machined at the mating end face of the front housing 3 and the rear housing 4, and an O-ring A14 is placed within this groove. When the front housing 3 and the rear housing 4 are fastened together using hex socket screws 17, the O-ring A14 is compressed and undergoes elastic deformation, filling the microscopic gaps between the mating surfaces to form an effective seal. Similarly, a mounting groove is also machined at the mating end face of the rear housing 4 and the rear cover 5, and an O-ring B15 is placed within this groove. When the rear cover 5 is fixed to the rear housing 4, the O-ring B15 is compressed to achieve a reliable seal at that mating surface. Firstly, the introduction of O-rings A14 and B15 effectively solves the problem of static leakage paths that may occur when assembling multiple components such as the front housing 3, the rear housing 4, and the rear cover 5. These features ensure that all independent oil circuits within the device, particularly the pressure oil circuits corresponding to supply connectors AB13 and C12, and the return oil area connected by return connector 11, are reliably isolated at the external mating surfaces of the housing, preventing hydraulic oil leakage and the intrusion of external contaminants into the device. Secondly, reliable static seals provide a stable working environment for the internal dynamic sealing system, namely the single-tooth skeleton seal assembly A8, the mountain-shaped skeleton seal assembly 9, and the single-tooth skeleton seal assembly B10. By eliminating leakage at the static mating surfaces, the pressure field in the chamber where the dynamic seal is located can be kept stable, preventing premature failure or performance degradation of the dynamic seal due to abnormal pressure fluctuations or leakage. This indirectly supports and guarantees the long-term sealing reliability and stability of the entire device under high-speed and high-pressure operation. Finally, this preferred solution, by setting designated O-ring static seals at the mating surfaces of key static components, forms a complete sealing system with the dynamic sealing system, ensuring the reliability of internal and external sealing of the device under high-pressure conditions.

[0025] As a preferred embodiment of the above, such as Figures 1-4 As shown, the device is configured to operate continuously under conditions of a rotational speed higher than 1500 rpm and a hydraulic pressure higher than 7.0 MPa, and under these conditions, the leakage rate of the device is less than 100 ml / min.

[0026] Specifically, the performance of the device was verified as follows: Connecting sleeve 1 was reliably connected to the rotary drive shaft of the test platform; oil supply connectors AB13 and C12 were connected to the hydraulic station via high-pressure oil pipes; and return connector 11 was connected to the oil tank and then to the flow metering device via an oil pipe. The hydraulic station was started, and the system pressure was stabilized at 7.0 MPa. The test platform was then started, driving connecting sleeve 1 and the synchronously rotating rotary spindle 2 to smoothly accelerate to 1500 rpm and continue operation. During this process, the front bearing 6 and rear bearing 7 ensured stable support and rotational accuracy of the rotary spindle 2. The sealing system, including single-tooth skeleton seal assembly A8, mountain-shaped skeleton seal assembly 9, and single-tooth skeleton seal assembly B10, performed dynamic sealing under this high-speed, high-pressure condition. After continuous operation for a specified time, the volume of leaked oil flowing from return connector 11 per unit time was measured using the flow metering device, confirming that its value did not exceed 100 ml / min. Simultaneously, the temperature of the device casing, especially the front casing 3 and rear casing 4 areas, was monitored to ensure that the temperature rise was within a reasonable range.

[0027] As a preferred embodiment of the above, such as Figures 1-4 As shown, the front housing 3 and the rear housing 4 are fixedly connected by a plurality of circumferentially evenly arranged hexagonal screws 17.

[0028] As a preferred embodiment of the above, such as Figures 1-4 As shown, the oil return connector 11 is disposed on the rear cover 5 and is located on the side of the single tooth skeleton seal assembly B10 facing away from the mountain-shaped skeleton seal assembly 9.

[0029] Specifically, during the assembly of the housing, the mating surfaces of the front housing 3 and the rear housing 4 are aligned, and then multiple hexagon socket screws 17 are evenly screwed in and tightened along the circumference of the mating surfaces, thus forming an integral rigid support structure. For the oil return passage, a threaded hole is machined on the rear cover 5, where the oil return connector 11 is installed. The inlet of this oil return connector 11 leads to a chamber enclosed by the rear cover 5, the rear housing 4, and the single-tooth skeleton seal assembly B10, located on the side of the single-tooth skeleton seal assembly B10 facing away from the mountain-shaped skeleton seal assembly 9. The rotating spindle 2 is supported within the assembled housing by the front bearing 6 and the rear bearing 7, and is driven to rotate by the connecting sleeve 1. First, the use of multiple circumferentially evenly arranged hexagon socket screws 17 to connect the front housing 3 and the rear housing 4 ensures uniform stress distribution at all points on the mating surfaces. This connection method effectively ensures that the O-ring A14 located between the front housing 3 and the rear housing 4 is uniformly compressed, forming a reliable static seal and preventing oil leakage at this critical mating surface. Meanwhile, uniform connection stiffness helps maintain the coaxiality of the support holes of the front bearing 6 and the rear bearing 7, which plays a positive role in ensuring the high-speed rotational stability of the rotating spindle 2. Secondly, the return oil connector 11 is placed on the rear cover 5 and directly leads to the chamber on the side of the single-tooth skeleton seal assembly B10 facing away from the mountain-shaped skeleton seal assembly 9, forming a clear and efficient leakage oil recovery path. This design can promptly collect any trace leakage oil that may cross the second sealing pair formed by the mountain-shaped skeleton seal assembly 9 and the single-tooth skeleton seal assembly B10, and guide it directly back to the oil tank through the return oil connector 11. This prevents the accumulation of leakage oil in the sealing cavity, avoiding the additional resistance, temperature rise, or adverse effects on the performance of the seals that may result, ensuring that the entire sealing system can operate stably for a long time under design conditions. Finally, the above-mentioned preferred solution, through a specific mechanical connection structure and return oil cavity layout, improves the sealing reliability, structural stability, and operability and maintainability of the device.

[0030] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed utility model. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A universal device for providing three-way hydraulic pressure within a shaft in rotary equipment, characterized in that: Includes connecting sleeve (1), rotating spindle (2), housing, rear cover (5), front bearing (6), rear bearing (7), and sealing system; The connecting sleeve (1) is fixedly connected to the shaft of the rotary equipment and drives the rotary spindle (2) to rotate synchronously; The housing includes a front housing (3) and a rear housing (4) fixedly connected to each other. The housing and the rear cover (5) constitute a stationary part and the rotating spindle (2) is rotatably supported by the front bearing (6) and the rear bearing (7). The housing is provided with an oil supply connector C (12), an oil supply connector AB (13) and an oil return connector (11). The rotating spindle (2) has three independent hydraulic channels that are hydraulically connected to the oil supply connector C (12) and the oil supply connector AB (13) respectively. The sealing system is disposed in the annular gap between the rotary mandrel (2) and the housing, and includes a single-tooth skeleton seal assembly A (8), a mountain-shaped skeleton seal assembly (9) and a single-tooth skeleton seal assembly B (10) arranged sequentially along the axial direction of the rotary mandrel (2). The single-tooth skeleton sealing assembly A (8) and the mountain-shaped skeleton sealing assembly (9) constitute the first sealing pair, which are used to seal the area between the oil supply joint AB (13) corresponding oil passage and the oil supply joint C (12) corresponding oil passage. The mountain-shaped skeleton sealing assembly (9) and the single-tooth skeleton sealing assembly B (10) constitute a second sealing pair, which is used to seal the area between the oil supply joint C (12) corresponding to the oil circuit and the return oil joint (11) located in the return oil zone.

2. The universal device for providing three-way hydraulic pressure within the shaft of a rotating device according to claim 1, characterized in that, Both the front housing (3) and the rear housing (4) are made of aluminum alloy.

3. A universal device for providing three-way hydraulic pressure within the shaft of a rotating device according to claim 1, characterized in that, The sealing lips of the single-tooth skeleton sealing assembly A (8), the mountain-shaped skeleton sealing assembly (9), and the single-tooth skeleton sealing assembly B (10) are all set towards the oil circuit corresponding to the oil supply connector C (12).

4. A universal device for providing three-way hydraulic pressure within the shaft of a rotating device according to claim 1, characterized in that, The sealing system also includes O-rings for achieving static sealing, including O-ring A (14) disposed between the front housing (3) and the rear housing (4), and O-ring B (15) disposed between the rear housing (4) and the rear cover (5).

5. A universal device for providing three-way hydraulic pressure within the shaft of a rotating device according to claim 1, characterized in that, The device is configured to operate continuously under conditions of a rotational speed higher than 1500 rpm and a hydraulic pressure higher than 7.0 MPa, and under these conditions, the leakage rate of the device is less than 100 ml / min.

6. A universal device for providing three-way hydraulic pressure within the shaft of a rotating device according to claim 1, characterized in that, The front housing (3) and the rear housing (4) are fixedly connected by a plurality of hexagonal socket screws (17) arranged evenly in the circumference.

7. A universal device for providing three-way hydraulic pressure within a shaft in rotary equipment according to claim 1, characterized in that, The return oil connector (11) is mounted on the rear cover (5) and is located on the side of the single tooth skeleton seal assembly B (10) facing away from the mountain-shaped skeleton seal assembly (9).

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