Hydrostatic bearing isolation seal

Abstract

The application discloses a static pressure type bearing isolation seal, characterized in that comprising a dynamic component and a static component arranged oppositely, the static component comprises a static ring and a static ring seat, the static ring is installed on the static ring seat, a gas inlet groove is formed in the static ring seat, a gas inlet channel is arranged between the static ring and the static ring seat, a plurality of gas inlet through holes are formed in the static ring, one end of the gas inlet channel is communicated with the gas inlet groove, and the other end of the gas inlet channel is communicated with the gas inlet through holes; the gas outlet end of the gas inlet through holes is arranged on the end surface of the static ring facing the dynamic component. The sealed gas with pressure is introduced into the gas inlet channel through the gas inlet groove, the double-end surface sealing function is achieved, and the leakage of two media can be prevented. The sealed gas with pressure enters the end surface to form a gas film, the end surface is operated in a non-contact mode, and the formation of the gas film is not limited by rotating speed and rotating direction, and the seal can normally work in a static state of the equipment.

Description

Technical Field

[0001] This invention relates to the field of mechanical seal technology, and more specifically to a hydrostatic bearing isolation seal. Background Technology

[0002] Equipment like screw vacuum pumps, in order to reduce the overall size of the equipment, does not have a separate bearing housing. The bearings and bearing lubricating oil do not have an independent cooling and sealing system, and the bearing lubricating oil and the material medium are not structurally isolated. Therefore, a sealing device is needed between the bearing lubricating oil and the material medium to ensure that the material medium does not enter the lubricating oil and damage the bearing, or that the bearing lubricating oil enters the material medium, leading to a reduction in lubricating oil and ultimately bearing damage.

[0003] In equipment such as screw vacuum pumps, the axial space between the bearing and rotor assembly for installing seals is usually quite small, making it impossible to install conventional double-end face seals properly (conventional double-end face seals require relatively large axial installation dimensions). On the other hand, conventional single-end face seals always allow media to enter between the end faces. Rotation speed, centrifugal force, and media pressure difference all cause the media entering between the end faces to be in a flowing state, and then enter the other side of the seal, resulting in media leakage. Therefore, due to functional limitations, conventional single-end face seals cannot meet the requirements.

[0004] Conventional seals function to prevent material media from leaking into the atmosphere. These seals are typically designed as integrated cartridge seals using locating blocks, with only one axial locating surface during installation. Seals in equipment like screw pumps, however, are usually modular. The moving and stationary components typically have two locating surfaces: the moving component connects the rotor to the bearing, and the stationary component connects the bearing housing to the bushing. This requires high precision in component machining to prevent leakage of critical static seals due to accumulated errors. Summary of the Invention

[0005] The purpose of this invention is to provide a hydrostatic bearing isolation seal to solve the problem that existing single-end-face seals used in equipment such as screw vacuum pumps always allow media to enter between the end faces, thus failing to meet usage requirements.

[0006] This invention provides a hydrostatic bearing isolation seal, comprising a moving component and a stationary component arranged opposite to each other. The stationary component includes a stationary ring and a stationary ring seat. The stationary ring is mounted on the stationary ring seat, and an air inlet groove is provided on the stationary ring seat. An air inlet channel is provided between the stationary ring and the stationary ring seat. The stationary ring has a plurality of air inlet holes. One end of the air inlet channel communicates with the air inlet groove, and the other end communicates with the air inlet holes. The air outlet end of the air inlet hole is located on the end face of the stationary ring facing the moving component.

[0007] With the above technical solution, pressurized sealing gas is introduced into the air intake channel through the air intake groove, providing a double-end-face sealing function that can prevent leakage of both media. The pressurized sealing gas forms an air film between the end faces, enabling non-contact operation of the end faces. Furthermore, the formation of the air film is not limited by rotational speed or direction of rotation, and the seal can function normally even when the equipment is stationary.

[0008] As a possible preferred design, each of the air inlets is provided with at least one orifice plate. By providing orifice plates and controlling the number of air inlets with orifice plates, the flow rate of sealing gas entering the stationary ring can be controlled, thereby ensuring the formation of an air film.

[0009] As a possible preferred design, the stationary ring has a plurality of uniformly distributed end face grooves on its end face facing the moving component; preferably, the end face grooves are uniformly distributed in a ring; more preferably, the end face grooves are uniformly distributed in a ring along the edge of the stationary ring, and their centers coincide with the center of the stationary ring.

[0010] With the above technical solution, the evenly distributed end face grooves can ensure that the formed gas film is evenly distributed. Affected by the pressure difference, the gas film creeps between the end faces and opens the stationary ring end face. While it can operate without contact, part of the sealing gas enters the medium and the other part enters the lubricating oil, so that the lubricating oil and the medium are separated. This ensures that the medium will not enter the lubricating oil and cause the bearing to be damaged due to poor lubrication. It also ensures that neither the medium nor the lubricating oil will enter between the end faces of the moving and stationary components, thus ensuring the integrity of the sealing components.

[0011] Since the formation of the gas film does not depend on the dynamic pressure groove and is determined by the pressure of the sealing gas, a stable sealing gas entering the seal can form a gas film, making the gas film unaffected by the rotational speed. Unlike traditional static pressure seals where the sealing gas only provides the opening force, in this invention, the sealing gas provides both the opening force and the closing force of the floating ring.

[0012] As a possible preferred design, the stationary assembly further includes an anti-rotation component, with its two ends respectively disposed on the stationary ring seat and the stationary ring. This prevents the stationary ring from rotating.

[0013] As a possible preferred design, the stationary component further includes a push ring disposed between the stationary ring and the stationary ring seat. A second elastic element is disposed between the push ring and the stationary ring seat, with its two ends respectively disposed on the push ring and the stationary ring seat. This ensures that the stationary ring is always in contact with the moving component and provides a floating force. Furthermore, during use, when the stationary ring experiences some wear, it can still maintain contact with the moving component, thus achieving compensation.

[0014] As a possible preferred design, the stationary ring is provided with a first elastic retaining ring and a second elastic retaining ring to limit the axial movement of the stationary ring. The dimensions of the first and second elastic retaining rings intersect, and the central axes of the first and second elastic retaining rings coincide with the central axis of the stationary ring. This effectively limits the axial displacement of the stationary ring.

[0015] As a possible preferred design, a floating ring is also provided on the outer side of the stationary ring seat; a first elastic element is provided between the floating ring and the stationary ring seat, with its two ends respectively disposed on the floating ring and the stationary ring seat. This ensures that the stationary ring is always in contact with the rotating ring and provides a floating force, so that the floating ring is always in close contact with the bushing, thus avoiding the impact of machining errors, installation errors, etc. on the relative sealing between the bushing and the bearing seat.

[0016] As a possible preferred design, a first floating ring and a second floating ring are disposed between the stationary ring and the stationary ring seat; a first sealing ring is disposed on the outer side of the stationary ring seat; a second sealing ring is disposed on the end face of the floating ring away from the stationary ring seat; a third sealing ring is disposed on the inner side of the floating ring, and the inner side of the third sealing ring is the stationary ring seat; the stationary ring seat, the stationary ring, the first floating ring, the second floating ring, the first sealing ring, the second sealing ring, and the third sealing ring form the air intake channel. By forming a channel between the stationary ring seat and the stationary ring, which serves as an air intake channel, and through the sealing effect of the first floating ring, the second floating ring, the first sealing ring, the second sealing ring, and the third sealing ring, leakage of sealing gas is prevented when the sealing gas passes through the air intake channel.

[0017] As a possible preferred design, the stationary assembly further includes a retainer for securing the floating ring, the retainer being disposed between the stationary ring seat and the floating ring to prevent rotation of the floating ring.

[0018] As a possible preferred design, the moving assembly includes a moving ring, with a clamping sleeve and a bushing respectively disposed at both ends of the moving ring; the stationary assembly is disposed outside the bushing; a fourth sealing ring is disposed between the clamping sleeve and the moving ring. The rotor assembly and bearing axially press the clamping sleeve, the fourth sealing ring, the moving ring, and the bushing together, allowing the moving ring to rotate with the shaft, and the fifth sealing ring ensures the sealing between the moving ring and the rotating shaft.

[0019] The beneficial effects of this invention are:

[0020] 1. The use of a first elastic element enables a floating seal, which avoids the relative sealing between the bushing and the bearing housing being affected by machining errors or installation errors of parts; the use of a second elastic element not only provides floating force, but also enables timely contact between the stationary ring and the rotating ring when the stationary ring wears during operation, thus achieving a compensation function.

[0021] 2. Static pressure seal, which achieves sealing through an air film. The pressurized sealing air provides both opening and closing force.

[0022] 3. The sealing method disclosed in this invention differs from existing dispersion methods, reducing the requirements for component processing precision.

[0023] 4. This invention forms an air film between the stationary and rotating rings, with a portion of the sealing air entering the medium and the other portion entering the lubricating oil (i.e., the air film flows bidirectionally between the end faces, giving a single-end-face seal the function of a double-end-face seal). This isolates the lubricating oil from the medium, ensuring that the medium does not enter the lubricating oil and cause damage to the bearing due to inadequate lubrication. It also ensures that neither the medium nor the lubricating oil enters the sealing end faces, preventing seal damage. Since the formation of the air film does not depend on the dynamic pressure groove, a stable supply of sealing air is sufficient to form the air film, making the sealing air film unaffected by rotational speed. Even at zero rotational speed, it can still provide a normal seal.

[0024] 5. The seal disclosed in this invention remains in a state of pressure balance throughout the entire sealing process. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the hydrostatic bearing isolation seal in an embodiment of the present invention;

[0026] Figure 2 for Figure 1 A schematic diagram of the K-direction;

[0027] Figure 3 This is a schematic diagram of the pressurized sealing gas intake at the stationary ring in an embodiment of the present invention;

[0028] Figure 4 for Figure 3 A schematic diagram of the M-direction;

[0029] Figure 5 This is a schematic diagram of the installation of the hydrostatic bearing isolation seal in a sealing configuration according to an embodiment of the present invention.

[0030] Wherein: 1-Compression sleeve; 2-Second sealing ring; 3-Floating ring; 4-Moving ring; 5-Fourth sealing ring; 6-First elastic retaining ring; 7-Stationary ring; 8-First floating ring; 9-First elastic element; 10-Second floating ring; 11-Anti-rotation component; 12-Stationary ring seat; 13-First sealing ring; 14-Second elastic element; 15-Push ring; 16-Fixing component; 17-Third sealing ring; 18-Second elastic retaining ring; 19-Shaft sleeve; 20-Rotor assembly; 21-Rotating shaft; 22-Bearing; 23-Shaft sleeve; 24-End cover; 25-Bearing seat; 26-Bearing cover; 27-Air inlet; 28-Medium side; 29-Lubricating oil side; 30-Air inlet groove; 31-Air inlet hole; 32-End face groove; 33-Sealing gas. Detailed Implementation

[0031] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention will be further described in detail below. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and are not intended to limit the present invention.

[0032] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.

[0033] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified. "Several" means one or more, unless otherwise explicitly specified.

[0034] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention 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 invention.

[0035] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0036] The inventors of this invention discovered that there are no readily available and suitable double-end face seals for devices such as screw vacuum pumps. Furthermore, existing conventional seals are typically loosely assembled, with both moving and stationary components having two locating surfaces: the moving component connects the rotor to the bearing, and the stationary component connects the bearing housing to the bushing. This requires high precision in component machining to prevent leakage of critical static seals due to accumulated errors. Therefore, given the lack of suitable double-end face seals and the high precision requirements of conventional seals, there is an urgent need to design a seal that possesses the functionality of a double-end face seal, requires only a small axial installation dimension, and whose static seal does not require excessively high machining precision to ensure sealing effectiveness.

[0037] like Figure 1 As shown, an embodiment of the present invention provides a hydrostatic bearing isolation seal. Figure 1 As shown, the hydrostatic bearing isolation seal includes a moving component and a stationary component arranged in opposite directions. It should be noted that "arranged in opposite directions" here means that after the moving component and the stationary component are both fitted onto the rotating shaft 21, their central axes coincide with the central axis of the rotating shaft 21. The rotating part of the moving component (such as the moving ring 4) and the stationary part of the stationary component (such as the stationary ring 7) are fitted onto the outside of the rotating shaft 21 and are arranged one in front of the other along the central axis of the rotating shaft 21, and the two are in contact.

[0038] like Figure 1 and 2 As shown, the stationary component includes a stationary ring 7 and a stationary ring seat 12. The stationary ring 7 is mounted on the stationary ring seat 12. An air inlet groove 30 is provided on the stationary ring seat 12. An air inlet channel is provided between the stationary ring 7 and the stationary ring seat 12. A plurality of air inlet holes are provided on the stationary ring 7. One end of the air inlet channel is connected to the air inlet groove 30, and the other end is connected to the air inlet holes. The air outlet end of the air inlet holes is located on the end face of the stationary ring 7 facing the moving component.

[0039] like Figure 5As shown, after pressurized sealing gas 33 is introduced into the air inlet groove 30, the pressurized sealing gas 33 passes through the air inlet channel and air inlet hole in sequence to reach the end face of the stationary ring 7. Since the sealing gas 33 itself is pressurized, it can form an air film on the end face of the stationary ring 7. Affected by the pressure difference, the air film peristalsizes between the end faces and opens the sealing end faces, allowing the seal to operate without contact (the air film creates a small gap between the stationary ring 7 and the moving ring assembly). At the same time, part of the sealing gas 33 enters the medium, and another part enters the lubricating oil, thus isolating the lubricating oil and the medium. This ensures that the medium will not enter the lubricating oil and cause the bearing 22 to be damaged due to poor lubrication, and also ensures that neither the medium nor the lubricating oil will enter between the sealing end faces and damage the seal.

[0040] Since the formation of the gas film does not depend on the dynamic pressure groove, a stable sealing gas 33 can form a gas film simply by entering the seal, making the sealing gas 33 film unaffected by the rotational speed. Unlike traditional static pressure seals where the sealing gas 33 only provides opening force, in this invention, the sealing gas 33 provides both opening force and sealing closing force.

[0041] In this invention, the number of the aforementioned air inlet holes can be determined appropriately according to the actual sealing requirements. In order to ensure that the thickness of the formed air film is uniform, the air inlet holes can be evenly arranged on the end face of the stationary ring 7.

[0042] In this invention, the stationary ring 7 is mounted on the stationary ring seat 12, specifically by adopting... Figure 1 As shown in the diagram, the stationary ring seat 12 is fitted outside the stationary ring 7, and an air intake passage is provided between the two.

[0043] As one possible implementation, in order to control the flow rate of pressurized sealing gas 33 into the end face of stationary ring 7, at least one orifice plate is provided in each of the air inlet holes, and the number and specifications of the orifice plates are set according to the actual required flow rate of sealing gas 33.

[0044] As one possible implementation method, such as Figure 4 As shown, the stationary ring 7 has a plurality of uniformly distributed end face grooves 32 on its end face facing the moving component. The uniformly distributed plurality of end face grooves 32 can ensure uniform distribution of the air film. The shape of the end face grooves 32 can be arbitrary, such as square, arc, triangle, etc.; arc shape is preferred.

[0045] As one possible implementation method, such as Figure 4 As shown, the multiple end face grooves 32 are arranged in a ring, which further facilitates the formation of a uniform gas film by the pressurized sealing gas 33. As a more preferred embodiment, such as... Figure 4 As shown, the plurality of end face grooves 32 are arranged in a ring along the edge of the stationary ring 7, and their centers coincide with the center of the stationary ring 7. Figure 4 As shown, the outlet end of the air inlet is close to or partially on the end face groove 32. In this embodiment of the invention, the number of end face grooves 32 is rationally arranged according to the outer diameter of the stationary ring 7, such as... Figure 4 As shown, there are 6 end face grooves 32, which are evenly distributed along the edge of the end face of the stationary ring 7.

[0046] As one possible implementation method, such as Figure 1 As shown, the stationary component also includes an anti-rotation member 11, with its two ends respectively disposed on the stationary ring seat and the stationary ring.

[0047] The anti-rotation component 11 is mainly provided to prevent the stationary ring 7 from rotating along with the rotating shaft 21 during rotation. The anti-rotation component 11 can be a common anti-rotation component in the art, such as a cylindrical pin. The specific connection method between the anti-rotation component 11, the stationary ring seat 12, and the stationary ring 7 is selected appropriately based on the type of anti-rotation component 11 used. For example, when the anti-rotation component 11 is a cylindrical pin, one end of the cylindrical pin 11 is fixedly connected to the stationary ring seat 12, i.e., the two are interference-fitted; the other end of the cylindrical pin 11 extends into a corresponding slot on the stationary ring 7, thereby achieving the installation of the anti-rotation component 11 and preventing the stationary ring 7 from rotating.

[0048] As one possible implementation method, such as Figure 1 As shown, the stationary component also includes a push ring 15 disposed between the stationary ring 7 and the stationary ring seat 12. A second elastic element 14 is disposed between the push ring 15 and the stationary ring seat 12, with the two ends of the second elastic element 14 respectively disposed on the push ring 15 and the stationary ring seat 12.

[0049] like Figure 5 As shown, during use, the stationary ring 7 and the push ring 15 are in close contact. During long-term use, the end of the stationary ring 7 facing the moving component will inevitably wear. With the presence of the second elastic element 14, the second elastic element 14 can push the stationary ring 7 closer to the moving ring component to ensure that the stationary ring 7 and the moving ring 4 always maintain a relatively small gap during use, so as to facilitate the formation of the air film. The second elastic element 14 can also provide a floating force.

[0050] In this embodiment, the specific connection method between the second elastic element 14, the push ring 15, and the stationary ring seat 12 can be set according to the specific structure of the second elastic element 14. For example, when the second elastic element 14 is a spring assembly composed of multiple springs, the specific installation method is as follows: the stationary ring seat 12 has a plurality of evenly distributed spring holes on the end face facing the push ring 15, and a spring is provided in each spring hole of the stationary ring seat 12 and the two are connected. The end of the spring extending out of the spring hole is connected to the push ring. This connection can be a detachable connection or welding, etc.

[0051] As one possible implementation method, such as Figure 1 As shown, the stationary ring 7 is externally provided with a first elastic retaining ring 6 and a second elastic retaining ring 18 to restrict the axial movement of the stationary ring 7. The dimensions of the first elastic retaining ring 6 and the second elastic retaining ring 18 intersect, and the central axes of the first elastic retaining ring 6 and the second elastic retaining ring 18 coincide with the central axis of the stationary ring 7. Because the dimensions of the first elastic retaining ring 6 and the second elastic retaining ring 18 intersect, when the stationary ring 7 drives the second elastic retaining ring 18 to float, the first elastic retaining ring 6 can limit the maximum displacement of the stationary ring 7. Therefore, the first elastic retaining ring 6 and the second elastic retaining ring 18 play a limiting role.

[0052] In this embodiment, the first elastic retaining ring 6 and the second elastic retaining ring 18 can be configured as follows: Figure 1 As shown, the first elastic retaining ring 6 is installed on the inner side of the stationary ring seat 12 facing the stationary ring 7, and the second elastic retaining ring 18 is installed on the outer side of the stationary ring 7 facing the stationary ring seat 12.

[0053] In this embodiment, the specific installation method of the first elastic retaining ring 6 and the second elastic retaining ring 18 can be as follows: Figure 1 As shown, an installation groove is set at the corresponding installation position, and the first elastic retaining ring 6 and the second elastic retaining ring 18 are respectively inserted into the installation groove.

[0054] In order to store the sealing gas that overflows between the moving component and the stationary ring and thus achieve a sealing effect, a certain gap is provided between the inner side of the stationary ring seat 12 where the first elastic retaining ring 6 is provided and the outer side of the stationary ring 7 where the second elastic retaining ring 18 is provided.

[0055] As one possible implementation method, such as Figure 1 As shown, a floating ring 3 is also provided on the outer side of the stationary ring seat 12; a first elastic element 9 is provided between the floating ring 3 and the stationary ring seat 12, and the two ends of the first elastic element 9 are respectively provided on the floating ring 3 and the stationary ring seat 12.

[0056] like Figure 5 As shown, the first elastic element 9 can ensure that the floating ring 3 is always in contact with the bushing, providing a sealing environment and preventing leakage of sealing gas. It can also prevent the relative sealing between the bushing and the bearing housing 25 from being affected by part processing errors, installation errors, etc.

[0057] The specific structure and installation method of the first elastic element 9 are the same as those of the second elastic element 14, and will not be described in detail here.

[0058] As one possible implementation method, such as Figure 1As shown, a first floating ring 8 and a second floating ring 10 are provided between the stationary ring 7 and the stationary ring seat 12; a first sealing ring 13 is provided on the outer side of the stationary ring seat 12; a second sealing ring 2 is provided on the end face of the floating ring 3 away from the stationary ring seat 12, and a third sealing ring 17 is provided on the inner side of the floating ring 3, with the stationary ring seat 12 being the inner side of the third sealing ring 17; the air intake channel is formed between the stationary ring seat 12, the stationary ring 7, the first floating ring 8, the second floating ring 10, the first sealing ring 13, the second sealing ring 2, and the third sealing ring 17.

[0059] In this embodiment, the specific formation of the intake channel, and the installation methods of the stationary ring seat 12, stationary ring 7, first floating ring 8, second floating ring 10, first sealing ring 13, second sealing ring 2, and third sealing ring 17 can be as follows: Figure 1 and Figure 5 As shown, the details are as follows:

[0060] Three outer steps are provided on the outer side of the stationary ring 7, namely: Figure 1 From left to right, the stationary ring has a first outer step, a second outer step, and a third outer step; four inner steps are provided inside the stationary ring seat 12, namely... Figure 1 From left to right, the stationary ring seat consists of the first inner step, the second inner step, the third inner step, and the fourth inner step.

[0061] like Figure 1 and Figure 5 As shown, a first groove is provided at the second inner step of the stationary ring, and a first floating ring 8 is provided in the first groove. The outer diameter of the first floating ring 8 mates with the second outer step of the stationary ring seat. A second groove is provided at the third outer step of the stationary ring seat, and a second floating ring 10 is provided in the second groove. The outer diameter of the second floating ring 10 mates with the third inner step of the stationary ring.

[0062] The first floating ring 8 and the second floating ring 10 are dynamic during use, therefore the first floating ring 8 and the second floating ring 10 are required to have good elasticity to achieve a good seal and prevent the sealing gas from leaking when passing through the air intake channel.

[0063] Three outer steps are provided on the outer side of the stationary ring seat, namely... Figure 1 The stationary ring seat has a first outer step, a second outer step, and a third outer step from left to right. A third groove is provided on the third outer step of the stationary ring seat, and a first sealing ring 13 is provided in the third groove. The outer diameter of the first sealing ring 13 mates with the bearing seat to achieve a seal.

[0064] like Figure 1 and 5 As shown, the installation of the second sealing ring 2 is detailed below:

[0065] A fourth groove is provided on the end face of the floating ring 3 away from the stationary ring seat 12, and the second sealing ring 2 is provided in the fourth groove. The left end face of the second sealing ring 2 is engaged with the bushing.

[0066] like Figure 1 and 5 As shown, the installation of the third sealing ring 17 is detailed below:

[0067] A fourth groove is provided on the inner side of the floating ring 3, and the third sealing ring 17 is provided in the fourth groove. The third sealing ring 17 and the first outer step of the stationary ring seat are engaged.

[0068] In this embodiment, the first floating ring 8, the second floating ring 10, the first sealing ring 13, the second sealing ring 2, and the third sealing ring 17 can be common sealing ring types in the art, such as C-rings, O-rings, etc., which will not be described in detail here.

[0069] As one possible implementation method, such as Figure 1 As shown, a first elastic retaining ring 6 and a second elastic retaining ring 18 are provided outside the stationary ring 7 to restrict the axial movement of the stationary ring 7. The dimensions of the first elastic retaining ring 6 and the second elastic retaining ring 18 intersect, and the central axes of the first elastic retaining ring 6 and the second elastic retaining ring 18 coincide with the central axis of the stationary ring 7. With the aforementioned intake channel formed, the specific installation method of the first elastic retaining ring 6 and the second elastic retaining ring 18 can be as follows:

[0070] like Figure 1 and Figure 5 As shown, a second retaining ring groove is provided at the first inner step of the stationary ring seat, and the second elastic retaining ring 18 is tightened and fixed in the second retaining ring groove; a first retaining ring groove is provided at the second outer step of the stationary ring, and the first elastic retaining ring 6 is tightened and fixed in the first retaining ring groove.

[0071] As one possible implementation method, such as Figure 1 and 5 As shown, the static component also includes a fixing member 16 for fixing the floating ring 3, and the fixing member 16 is disposed between the static ring seat 12 and the floating ring 3.

[0072] In this embodiment, the fastener 16 can be a common fastening component in the art, such as an external hexagonal bolt. The connection method between the fastener 16, the stationary ring seat 12, and the floating ring 3 can be a conventional connection method in the art, depending on the specific structure of the fastener 16. For example, when the fastener 16 is an external hexagonal bolt, a pin groove is formed on one end face of the floating ring 3 facing the stationary ring seat 12, and the threaded part of the external hexagonal bolt extends into the pin groove; the threaded end of the external hexagonal bolt passes through the stationary ring seat 12 and connects to the bearing seat 25.

[0073] As one possible implementation method, such as Figure 1 and 5 As shown, the moving component includes a moving ring 4, with a clamping sleeve 1 and a bushing 23 respectively disposed at both ends of the moving ring 4; the stationary component is disposed on the outside of the bushing 23; a fourth sealing ring 5 is disposed between the clamping sleeve 1 and the moving ring 4. Figure 5 As shown, the rotor assembly 20 and bearing 22 axially press the clamping sleeve 1, the fourth sealing ring 5, the moving ring 4 and the bushing 19 together, so that the moving ring 4 can rotate with the rotating shaft 21, and the fourth sealing ring 5 can ensure the sealing between the moving ring 4 and the rotating shaft 21.

[0074] In this embodiment, the fourth sealing ring 5 can be a sealing component commonly used in the art, such as an O-ring, a C-ring, etc.

[0075] like Figure 5 As shown in the figure, this is a schematic diagram of the installation of a hydrostatic bearing isolation seal. The entire hydrostatic bearing 22 isolation seal is fitted outside the rotating shaft 21, and the rotor assembly 20 is fitted outside the rotating shaft 21. One end of the rotor assembly 20 abuts against the clamping sleeve 1, and the lower end of the bushing presses against the clamping sleeve 1, while its right side abuts against the floating ring 3. A second sealing ring 2 is provided between the floating ring 3 and the bushing. A bearing seat 25 is provided on the outer side of the right side of the stationary ring seat 12. The two ends of the end cover 24 are respectively provided on the bushing and the bearing seat 25. The end cover 24 has an air inlet 27. The bearing 22 is installed inside the bearing seat 25 and is fitted outside the rotating shaft 21. A bearing cover 26 is also provided on the outer side of the bearing 22 to cover the bearing 22. One side of the rotor assembly 20 is the medium side 28, and one side of the bearing cover 26 is the lubricating oil side 29. After installation, an air inlet 31 is opened on the end cover 24. Pressurized sealing gas 33 first enters the air inlet groove 30 through the air inlet 31, and then passes through the air inlet channel and air inlet through hole to reach the end face of the stationary ring 12 facing the moving ring 2. An air film is formed on the end face, so that the moving ring 4 and the stationary ring 7 are separated and do not contact each other. Then the sealing gas enters the gap on both sides of the stationary ring 7 to achieve the purpose of isolating the medium.

[0076] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A hydrostatic bearing isolation seal, characterized in that, The device includes a moving component and a stationary component arranged opposite to each other. The stationary component includes a stationary ring and a stationary ring seat. The stationary ring is mounted on the stationary ring seat, and an air inlet groove is provided on the stationary ring seat. An air inlet channel is provided between the stationary ring and the stationary ring seat. The stationary ring has several air inlet holes. One end of the air inlet channel is connected to the air inlet groove, and the other end is connected to the air inlet holes. The air outlet of the air inlet holes is located on the end face of the stationary ring facing the moving component. Each of the aforementioned air intake holes is provided with at least one perforated plate; The stationary ring has a plurality of evenly distributed end face grooves on its end face facing the moving component. A step is provided on the stationary ring, and a first floating ring and a second floating ring are provided between the stationary ring and the stationary ring seat. A cavity is formed between the stationary ring (7) and the stationary ring seat (12). A floating ring is also provided on the outer side of the stationary ring seat; a first elastic element is provided between the floating ring and the stationary ring seat, with the two ends of the first elastic element respectively provided on the floating ring and the stationary ring seat; The sealed air entering the intake passage is pressurized.

2. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The end face grooves are arranged in a ring shape.

3. The hydrostatic bearing isolation seal according to claim 2, characterized in that, The end face grooves are distributed in a ring along the edge of the stationary ring, and their center coincides with the center of the stationary ring.

4. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The stationary component also includes an anti-rotation component, with its two ends respectively disposed on the stationary ring seat and the stationary ring.

5. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The stationary component further includes a push ring disposed between the stationary ring and the stationary ring seat, and a second elastic element is disposed between the push ring and the stationary ring seat, with the two ends of the second elastic element respectively disposed on the push ring and the stationary ring seat.

6. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The stationary ring is provided with a first elastic retaining ring and a second elastic retaining ring to restrict the axial movement of the stationary ring. The dimensions of the first elastic retaining ring and the second elastic retaining ring are intersecting, and the central axis of the first elastic retaining ring and the second elastic retaining ring coincides with the central axis of the stationary ring.

7. The hydrostatic bearing isolation seal according to claim 1, characterized in that, A first sealing ring is provided on the outer side of the stationary ring seat; a second sealing ring is provided on the end face of the floating ring away from the stationary ring seat; a third sealing ring is provided on the inner side of the floating ring, and the inner side of the third sealing ring is the stationary ring seat; the air intake channel is formed between the stationary ring seat, the stationary ring, the first floating ring, the second floating ring, the first sealing ring, the second sealing ring, and the third sealing ring.

8. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The stationary component further includes a fixing member for fixing the floating ring, the fixing member being disposed between the stationary ring seat and the floating ring.

9. The hydrostatic bearing isolation seal according to claim 1, characterized in that, The moving component includes a moving ring, with a clamping sleeve and a bushing respectively provided at both ends of the moving ring; the stationary component is provided on the outside of the bushing; and a fourth sealing ring is provided between the clamping sleeve and the moving ring.

Images