CN116181910A - Static pressure type bearing isolation seal - Google Patents

Abstract

The invention discloses a static pressure bearing isolation seal which is characterized by comprising a movable component and a static component which are arranged in opposite directions, wherein the static component comprises a static ring and a static ring seat, the static ring is arranged on the static ring seat, an air inlet groove is formed in the static ring seat, an air inlet channel is arranged between the static ring and the static ring seat, a plurality of air inlet through holes are formed in the static ring, one end of the air inlet channel is communicated with the air inlet groove, and the other end of the air inlet channel is communicated with the air inlet through holes; the air outlet end of the air inlet through hole is arranged on the end face of the static ring, which faces the movable assembly. The pressurized sealing gas is introduced into the air inlet channel through the air inlet groove, so that the double-end-face sealing function is realized, and leakage of two mediums can be prevented. The pressurized sealing gas enters the end surfaces to form a gas film, so that the end surfaces can operate in a non-contact mode, the formation of the gas film is not limited by rotating speed and steering, and the sealing can work normally in a static state of the equipment.

Description

Static pressure type bearing isolation seal

Technical Field

The invention relates to the technical field of mechanical sealing, in particular to a static pressure type bearing isolation seal.

Background

For example, in order to reduce the overall size of the device, a separate bearing box is not arranged, a separate cooling and sealing system is not arranged between a bearing and bearing lubricating oil, and the bearing lubricating oil and a material medium are not isolated from each other structurally. A sealing device is needed to be arranged between the bearing lubricating oil and the material medium, so that the material medium can not enter the lubricating oil to damage the bearing, or the bearing lubricating oil enters the material medium, so that the lubricating oil is reduced to damage the bearing.

In devices such as screw vacuum pumps, the axial space between the bearing and the rotor assembly for mounting the seal is typically relatively small, such that conventional double-ended seals cannot be mounted properly (conventional double-ended seals require relatively large axial mounting dimensions); the conventional single-end face seal always has medium entering end faces, so that the medium entering the end faces is in a flowing state due to rotation speed, centrifugal force, medium pressure difference and the like, and then enters the other side of the seal to form medium leakage, and therefore the conventional single-end face seal is limited by functions and cannot meet the requirement of use.

Conventional seals, which function to prevent leakage of material media to the atmosphere, are typically designed as cartridge seals using a set block assembly, with only one axial locating surface during installation. The seal in the equipment such as screw pump is usually bulk type, the dynamic and static components are usually provided with two positioning surfaces, the dynamic component is connected with the rotor and the bearing, and the static component is connected with the bearing seat and the bushing, which requires higher part machining precision to ensure that some critical static seal leakage can not occur due to accumulated errors.

Disclosure of Invention

The invention aims to provide a static pressure bearing isolation seal, which solves the problem that the existing single-end face seal always has a medium entering between end faces when used for sealing equipment such as a screw vacuum pump and cannot meet the use requirement.

The invention provides a static pressure bearing isolation seal, which comprises a movable component and a static component which are arranged in opposite directions, wherein the static component comprises a static ring and a static ring seat, the static ring is arranged on the static ring seat, an air inlet groove is formed in the static ring seat, an air inlet channel is arranged between the static ring and the static ring seat, a plurality of air inlet through holes are formed in the static ring, one end of the air inlet channel is communicated with the air inlet groove, and the other end of the air inlet channel is communicated with the air inlet through holes; the air outlet end of the air inlet through hole is arranged on the end face of the static ring, which faces the movable assembly.

Under the condition of adopting the technical scheme, the pressurized sealing gas is introduced into the air inlet channel through the air inlet groove, so that the double-end-face sealing function is realized, and leakage of two mediums can be prevented. The pressurized sealing gas enters the end surfaces to form a gas film, so that the end surfaces can operate in a non-contact mode, the formation of the gas film is not limited by rotating speed and steering, and the sealing can work normally in a static state of the equipment.

As a possible preferred design, at least one perforated plate is provided in each of the inlet openings. The quantity of the air inlet through holes arranged on the orifice plate can be controlled to control the flow of sealing air entering the static ring through arranging the orifice plate and controlling the quantity of the air inlet through holes arranged on the orifice plate, so that the formation of an air film is ensured.

As a possible preferred design, the end face of the static ring facing the moving assembly is provided with a plurality of end face grooves which are uniformly distributed; preferably, the end face grooves are uniformly distributed in a ring shape; more preferably, the end face grooves are uniformly distributed in a ring shape along the edge of the static ring, and the circle center of the end face grooves coincides with the circle center of the static ring.

Under the condition of adopting the technical scheme, the end face grooves which are uniformly distributed can ensure that the formed air film is uniformly distributed; under the influence of pressure difference, the air film creeps between the end surfaces and opens the end surface of the static ring, so that one part of sealing gas enters the medium while non-contact operation is realized, and the other part of sealing gas enters the lubricating oil, so that the lubricating oil and the medium are separated, the bearing cannot be well lubricated and damaged due to the fact that the medium cannot enter the lubricating oil, and the condition that the medium or the lubricating oil cannot enter between the end surfaces of the dynamic component and the static component is ensured, and the integrity of the sealing component is ensured.

Because the formation of the air film does not depend on dynamic pressure grooves and is determined by the pressure of the sealing gas, the stable sealing gas enters the seal to form the air film, so that the air film is not influenced by the rotating speed. Unlike conventional static pressure seals in which the seal gas provides only an opening force, in the present invention, the seal gas provides both an opening force and a closing force of the floating ring.

As a possible preferred design, the static assembly further comprises an anti-rotation member, and two ends of the anti-rotation member are respectively arranged on the static ring seat and the static ring. Preventing the stationary ring from rotating.

As a possible preferred design, the static assembly further comprises a push ring arranged between the static ring and the static ring seat, a second elastic element is arranged between the push ring and the static ring seat, and two ends of the second elastic element are respectively arranged on the push ring and the static ring seat. Can guarantee that quiet ring is laminated with moving the subassembly all the time to provide the power that floats, and in the use, when certain wearing and tearing appear in quiet ring, also can make quiet ring and moving the subassembly laminating, realize the compensation.

As a possible preferred design, a first elastic clamping ring and a second elastic clamping ring for limiting the axial movement of the static ring are arranged outside the static ring, the sizes of the first elastic clamping ring and the second elastic clamping ring are crossed, and the central axes of the first elastic clamping ring and the second elastic clamping ring are coincident with the central axis of the static ring. The axial displacement of the stationary ring can be limited.

As a possible preferred design, a floating ring is further arranged outside the static ring seat; a first elastic element is arranged between the floating ring and the static ring seat, and two ends of the first elastic element are respectively arranged on the floating ring and the static ring seat. The static ring can be guaranteed to be always attached to the movable ring, floating force is provided, the floating ring is enabled to be always attached to the bushing, and relative tightness between the bushing and the bearing seat due to part machining errors, installation errors and the like can be avoided.

As a possible preferred design, a first floating ring and a second floating ring are arranged between the static ring and the static ring seat; a first sealing ring is arranged on the outer side of the static ring seat; the end face of the floating ring, which is far away from one side of the static ring seat, is provided with a second sealing ring, the inner side of the floating ring is provided with a third sealing ring, and the inner side of the third sealing ring is the static ring seat; and the air inlet channel is formed among the static ring seat, the static ring, the first floating ring, the second floating ring, the first sealing ring, the second sealing ring and the third sealing ring. Through forming a passageway between quiet ring seat and quiet ring, this passageway is as the air inlet channel to through the sealed effect of first floating ring, second floating ring, first sealing washer, second sealing washer and third sealing washer, realize when sealed gas passes through the air inlet channel, the condition that sealed gas leakage does not appear.

As a possible preferred design, the stationary assembly further comprises a fixing member for fixing the floating ring, the fixing member being disposed between the stationary ring seat and the floating ring. Preventing the floating ring from rotating.

As a possible preferred design, the moving assembly comprises a moving ring, wherein two ends of the moving ring are respectively provided with a pressing sleeve and a shaft sleeve; the static component is arranged on the outer side of the shaft sleeve; a fourth sealing ring is arranged between the pressing sleeve and the movable ring. The rotor assembly and the bearing axially compress the compression sleeve, the fourth sealing ring, the movable ring and the shaft sleeve, so that the movable ring can rotate along with the shaft, and the fifth sealing ring can ensure the tightness between the movable ring and the rotating shaft.

The invention has the beneficial effects that:

1. the first elastic element is adopted, so that the sealing mode of the seal with floatability can avoid the influence of part processing errors, installation errors and the like on the relative tightness between the bushing and the bearing seat; by adopting the second elastic element, not only can the floating force be provided, but also the static ring can be pushed to contact with the moving ring in time when the static ring is worn in operation, and the compensation function is realized.

2. The static pressure type seal is realized through an air film, and the sealing gas with pressure provides opening force and closing force at the same time.

3. The sealing disclosed by the invention is different from the existing dispersibility, and the requirement on the machining precision of parts is reduced.

4. According to the invention, the air film is formed between the stationary ring and the movable ring, one part of sealing air enters the medium, and the other part of sealing air enters the lubricating oil (namely, the air film flows bidirectionally between the end faces, so that the single-end face seal has a double-end-face sealing function), so that the lubricating oil and the medium are isolated, the bearing cannot be well lubricated and damaged due to the fact that the medium cannot enter the lubricating oil, and the sealing is damaged due to the fact that the medium or the lubricating oil cannot enter the sealing end face. Because the formation of the air film does not depend on dynamic pressure grooves, stable sealing air can enter the seal to form the air film, so that the sealing air film is not influenced by the rotating speed, and the sealing air film can be normally sealed even if the rotating speed is 0.

5. The seal disclosed by the invention is always in a pressure balance state in the whole sealing process.

Drawings

FIG. 1 is a schematic diagram of a hydrostatic bearing isolation seal in an embodiment of the present invention;

FIG. 2 is a schematic view of the K direction in FIG. 1;

FIG. 3 is a schematic view of the inlet of pressurized seal gas at the stationary ring in an embodiment of the invention;

FIG. 4 is a schematic view of the M direction in FIG. 3;

FIG. 5 is a schematic illustration of the installation of a hydrostatic bearing isolation seal in a seal type embodiment of the present invention.

Wherein: 1-compacting the sleeve; 2-a second sealing ring; 3-floating ring; 4-moving ring; 5-a fourth sealing ring; 6-a first elastic collar; 7-stationary ring; 8-a first floating ring; 9-a first elastic element; 10-a second floating ring; 11-an anti-rotation member; 12-a stationary ring seat; 13-a first sealing ring; 14-a second elastic element; 15-push ring; 16-a fixing piece; 17-a third sealing ring; 18-a second elastic collar; 19-shaft sleeve; a 20-rotor assembly; 21-a rotation axis; 22-bearings; 23-shaft sleeve; 24-end caps; 25-bearing seats; 26-a bearing cap; 27-an air inlet; 28-media side; 29-lubricating oil side; 30-an air inlet groove; 31-an air inlet; 32-end face grooves; 33-sealing gas.

Detailed Description

In order to make the technical problems, technical schemes and beneficial effects to be solved more clear, the invention is further described in detail below. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.

It will be understood that when an element is referred to as being "mounted" or "disposed" on another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, the meaning of "a plurality" is two or more, unless explicitly defined otherwise. The meaning of "a number" is one or more than one unless specifically defined otherwise.

In the description of the present invention, it should be understood that the directions or positional relationships indicated by the terms "upper", "lower", "front", "rear", "left", "right", "inside", "outside", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.

In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

The inventor of the present invention has found that there is no ready and suitable use of double-ended seals for such devices as screw vacuum pumps, and that existing conventional seals are typically bulk dynamic and static components, which typically have two locating surfaces, connecting the rotor to the bearing, and the static component to the bearing housing to the bushing, which requires higher part machining accuracy to ensure that some critical static seals do not leak due to accumulated errors. Therefore, aiming at the conventional sealing without proper double-end-face sealing and with higher requirements on the processing precision of parts, the design of the sealing is needed, the function of double-end-face sealing can be possessed, only a small axial installation size is needed, and the sealing effect can be ensured without excessively high processing precision of static sealing.

As shown in fig. 1, an embodiment of the present invention provides a hydrostatic bearing isolation seal. As shown in fig. 1, the hydrostatic bearing isolation seal includes a moving assembly and a stationary assembly disposed in opposition. The term "disposed opposite to each other" as used herein means that both the movable unit and the stationary unit are disposed around the rotation shaft 21, and the central axes of both the movable unit and the stationary unit are coincident with the central axis of the rotation shaft 21, and the rotary member (e.g., the movable ring 4) of the movable unit and the stationary member (e.g., the stationary ring 7) of the stationary unit are disposed outside the rotation shaft 21 and disposed in tandem along the central axis direction of the rotation shaft 21, and are in contact with each other.

As shown in fig. 1 and 2, the static assembly comprises a static ring 7 and a static ring seat 12, the static ring 7 is mounted on the static ring seat 12, an air inlet groove 30 is formed in the static ring seat 12, an air inlet channel is formed between the static ring 7 and the static ring seat 12, a plurality of air inlet through holes are formed in the static ring 7, one end of the air inlet channel is communicated with the air inlet groove 30, and the other end of the air inlet channel is communicated with the air inlet through holes; the air outlet end of the air inlet through hole is arranged on the end face of the static ring 7 facing the movable assembly.

As shown in fig. 5, after the pressurized sealing gas 33 is introduced into the air inlet groove 30, the pressurized sealing gas 33 sequentially passes through the air inlet channel and the air inlet through hole to reach the end face of the stationary ring 7; since the seal gas 33 itself has pressure, the seal gas 33 can form a gas film on the end face of the stationary ring 7; under the influence of pressure difference, the air film creeps between the end surfaces and opens the sealing end surfaces, so that when the seal can run in a non-contact mode (the air film enables a tiny gap to be formed between the stationary ring 7 and the movable ring assembly), one part of sealing air 33 enters the medium, the other part of sealing air enters the lubricating oil, the lubricating oil and the medium are separated, the bearing 22 cannot be well lubricated to damage the bearing due to the fact that the medium cannot enter the lubricating oil, and the sealing end surfaces cannot be damaged due to the fact that the medium or the lubricating oil cannot enter the sealing end surfaces.

Because the formation of the air film does not depend on dynamic pressure grooves, the stable sealing air 33 can enter the seal to form the air film, so that the sealing air 33 film is not influenced by the rotating speed. Unlike conventional static pressure seals, in which the seal gas 33 provides only an opening force, in the present invention, the seal gas 33 provides an opening force as well as a closing force of the seal.

In the invention, the number of the air inlet through holes can be determined in a proper amount according to the actual sealing requirement. In order to make the thickness of the formed air film uniform, the air intake through holes may be uniformly arranged on the end face of the stationary ring 7.

In the invention, the stationary ring 7 is mounted on the stationary ring seat 12, specifically, the stationary ring seat 12 is sleeved outside the stationary ring 7, and an air inlet channel is arranged between the stationary ring seat and the stationary ring seat.

As a possible implementation manner, in order to control the flow rate of the pressurized sealing gas 33 entering the end face of the static ring 7, at least one orifice plate is arranged in each air inlet through hole, and the number and the specification of the orifice plates are set according to the actual requirement of the flow rate of the sealing gas 33.

As a possible embodiment, as shown in fig. 4, the end surface of the stationary ring 7 facing the moving assembly is provided with a plurality of end surface grooves 32 which are uniformly distributed. The plurality of end surface grooves 32 which are uniformly distributed can ensure uniform distribution of the air film. Wherein: the shape of the end face groove 32 may be any shape, such as square, circular arc, triangle, etc.; preferably circular arc shape.

As a possible embodiment, as shown in fig. 4, the plurality of end face grooves 32 are distributed in a ring shape, which is further advantageous in that the pressurized seal gas 33 can form a uniform gas film. As a more preferable embodiment, as shown in fig. 4, a plurality of the end face grooves 32 are distributed in a ring shape along the edge of the stationary ring 7, and the center of the end face grooves coincides with the center of the stationary ring 7. As shown in fig. 4, the outlet end of the inlet through hole is near or partially on the end face groove 32. In the embodiment of the invention, the number of the end face grooves 32 is reasonably distributed according to the outer diameter of the stationary ring 7, and as shown in fig. 4, the number of the end face grooves 32 is 6 and is uniformly distributed on the edge of the end face of the stationary ring 7.

As a possible implementation manner, as shown in fig. 1, the static assembly further includes an anti-rotation member 11, and two ends of the anti-rotation member are respectively disposed on the static ring seat and the static ring.

The anti-rotation member 11 is provided mainly for preventing the stationary ring 7 from following rotation during rotation of the rotation shaft 21. The anti-rotation member 11 may be an anti-rotation member commonly known in the art, for example: cylindrical pins, etc. The specific connection mode of the anti-rotation piece 11, the static ring seat 12 and the static ring 7 is properly selected according to the type of the specific anti-rotation piece 11; for example: when the anti-rotation piece 11 is a cylindrical pin, one end of the cylindrical pin 11 is fixedly connected with the static ring seat 12, namely, the cylindrical pin 11 and the static ring seat are in interference fit; the other end of the cylindrical pin 11 extends into a pin groove formed in the corresponding position of the stationary ring 7, so that the anti-rotation piece 11 is mounted and the purpose of preventing the stationary ring 7 from rotating is achieved.

As a possible implementation manner, as shown in fig. 1, the static assembly further includes a push ring 15 disposed between the static ring 7 and the static ring seat 12, a second elastic element 14 is disposed between the push ring 15 and the static ring seat 12, and two ends of the second elastic element 14 are disposed on the push ring 15 and the static ring seat 12 respectively.

As shown in fig. 5, the stationary ring 7 and the push ring 15 are tightly attached in the use process, in the long-term use process, abrasion is inevitably generated at one end of the stationary ring 7 facing the moving assembly, and in the presence of the second elastic element 14, the second elastic element 14 can push the stationary ring 7 to approach the moving assembly, so that a relatively small gap is always kept between the stationary ring 7 and the moving ring 4 in the use process, so that an air film is formed, and the second elastic element 14 can also provide a floating force.

In this embodiment, the specific connection manner of the second elastic element 14 and the push ring 15 and the stationary ring seat 12 may 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 a plurality of springs, the following specific installation method is as follows: the end face of the static ring seat 12, which faces the push ring 15, is provided with a plurality of uniformly distributed spring holes, each spring hole of the static ring seat 12 is provided with a spring, the spring and the spring are connected, one end of the spring extending out of the spring hole is connected with the push ring, and the connection can be in a detachable connection or a welding mode.

As a possible embodiment, as shown in fig. 1, a first elastic collar 6 and a second elastic collar 18 for limiting the axial movement of the static ring 7 are arranged outside the static ring 7, the dimensions of the first elastic collar 6 and the second elastic collar 18 are crossed, and the central axes of the first elastic collar 6 and the second elastic collar 18 and the central axis of the static ring 7 are coincident. Because the dimensions of the first elastic clamping ring 6 and the second elastic clamping ring 18 are crossed, when the static ring 7 drives the second elastic clamping ring 18 to float, the first elastic clamping ring 6 can limit the maximum displacement of the static ring 7, and therefore the first elastic clamping ring 6 and the second elastic clamping ring 18 play a limiting role.

In this embodiment, as shown in fig. 1, the first elastic collar 6 and the second elastic collar 18 may be disposed, the first elastic collar 6 is mounted on an inner side surface of the stationary ring seat 12 facing the stationary ring 7, and the second elastic collar 18 is mounted on an outer side surface of the stationary ring 7 facing the stationary ring seat 12.

In this embodiment, as shown in fig. 1, the specific installation manner of the first elastic collar 6 and the second elastic collar 18 may be that an installation groove is provided at the corresponding installation position, and the first elastic collar 6 and the second elastic collar 18 may be respectively engaged in the installation groove.

In order to enable the sealing gas between the moving assembly and the stationary ring to be stored when overflowed, the sealing function is achieved, and therefore a certain gap is arranged between the inner side surface part of the stationary ring seat 12 provided with the first elastic clamping ring 6 and the outer side surface part of the stationary ring 7 provided with the second elastic clamping ring 18.

As a possible implementation manner, as shown in fig. 1, a floating ring 3 is further arranged outside the static ring seat 12; a first elastic element 9 is arranged between the floating ring 3 and the static ring seat 12, and two ends of the first elastic element 9 are respectively arranged on the floating ring 3 and the static ring seat 12.

As shown in fig. 5, the first elastic element 9 can ensure that the floating ring 3 is always attached to the bush, provide a sealing environment, avoid leakage of sealing gas, and also avoid influence on the relative tightness between the bush and the bearing housing 25 due to part processing errors, installation errors, and the like.

The specific structure and mounting manner of the first elastic element 9 may be the same as the second elastic element 14, and will not be described again here.

As a possible implementation manner, as shown in fig. 1, a first floating ring 8 and a second floating ring 10 are arranged between the static ring 7 and the static ring seat 12; a first sealing ring 13 is arranged on the outer side of the static ring seat 12; the end face of the floating ring 3, which is far away from one side of the static ring seat 12, is provided with a second sealing ring 2, the inner side of the floating ring 3 is provided with a third sealing ring 17, and the inner side of the third sealing ring 17 is provided with the static ring seat 12; the air inlet channel is formed among the static ring seat 12, the static 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.

In this embodiment, regarding the specific formation of the air intake passage, the mounting manners of the stationary ring seat 12, the stationary ring 7, the first floating ring 8, the second floating ring 10, the first seal ring 13, the second seal ring 2, and the third seal ring 17 may be as shown in fig. 1 and 5, and specifically as follows:

three outer steps are arranged on the outer side of the stationary ring 7, namely a stationary ring first outer step, a stationary ring second outer step and a stationary ring third outer step from left to right in FIG. 1; four inner steps are arranged on the inner side of the static ring seat 12, namely a first inner step of the static ring seat, a second inner step of the static ring seat, a third inner step of the static ring seat and a fourth inner step of the static ring seat from left to right in fig. 1.

As shown in fig. 1 and 5, a first ring groove is formed in the second inner step of the stationary ring, the first floating ring 8 is arranged in the first ring groove, and the outer diameter of the first floating ring 8 is matched with the second outer step of the stationary ring seat; the third outer step of the stationary ring seat is provided with a second ring groove, the second floating ring 10 is arranged in the second ring groove, and the outer diameter of the second floating ring 10 is matched with the third inner step of the stationary ring.

The first and second floating rings 8 and 10 are dynamic during use, so that good elasticity of the first and second floating rings 8 and 10 is required to achieve good sealing, avoiding leakage of sealing gas when passing through the air intake passage.

Three outer steps are arranged on the outer side of the static ring seat, namely a first outer step of the static ring seat, a second outer step of the static ring seat and a third outer step of the static ring seat from left to right in the figure 1. The third outer step of the static ring seat is provided with a third ring groove, the third ring groove is provided with a first sealing ring 13, and the outer diameter of the first sealing ring 13 is matched with the bearing seat to realize sealing.

As shown in fig. 1 and 5, regarding the installation of the second seal ring 2, it is specifically as follows:

a fourth ring groove is formed in the end face, far away from one side of the static ring seat 12, of the floating ring 3, the second sealing ring 2 is arranged in the fourth ring groove, and the left end face of the second sealing ring 2 is matched with the bushing.

As shown in fig. 1 and 5, regarding the installation of the third seal ring 17, it is specifically as follows:

a fourth ring groove is formed in the inner side of the floating ring 3, the third sealing ring 17 is arranged in the fourth ring groove, and the third sealing ring 17 is matched with the first outer step of the static ring seat.

In this embodiment, the specific types of 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 may be types of sealing rings commonly used in the art, for example: c-rings, O-rings, etc., are not described in detail herein.

As a possible embodiment, as shown in fig. 1, a first elastic collar 6 and a second elastic collar 18 for limiting the axial movement of the static ring 7 are arranged outside the static ring 7, the dimensions of the first elastic collar 6 and the second elastic collar 18 are crossed, and the central axes of the first elastic collar 6 and the second elastic collar 18 and the central axis of the static ring 7 are coincident. In the case of the aforementioned intake passage formation, the specific mounting manner of the first elastic collar 6 and the second elastic collar 18 may be as follows:

as shown in fig. 1 and 5, a second collar groove is formed at the first inner step of the stationary ring seat, and a second elastic collar 18 is fastened and fixed in the second collar groove; a first collar groove is formed in the second outer step of the stationary ring, and a first elastic collar 6 is tightened inwards and fixed in the first collar groove.

As a possible embodiment, as shown in fig. 1 and 5, the static assembly further 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.

In this embodiment, the fixing member 16 may be a part commonly used in the art, for example: outer hex bolts, etc. The connection between the fixing member 16 and the stationary ring seat 12 and the floating ring 3 may be selected according to the specific structure of the fixing member 16. For example: when the fixing piece 16 is an outer hexagon bolt, a pin groove is formed in one end face of the floating ring 3 facing the static ring seat 12, and the screw head part of the outer hexagon bolt extends into the pin groove; the screw end of the outer hexagon bolt penetrates through the stationary ring seat 12 and is connected with the bearing seat 25.

As a possible embodiment, as shown in fig. 1 and 5, the moving assembly comprises a moving ring 4, and two ends of the moving ring 4 are respectively provided with a compression sleeve 1 and a shaft sleeve 23; the static component is arranged outside the shaft sleeve 23; a fourth sealing ring 5 is arranged between the compression sleeve 1 and the movable ring 4. As shown in fig. 5, the rotor assembly 20 and the bearing 22 axially compress the compression sleeve 1, the fourth seal ring 5, the moving ring 4 and the shaft sleeve 19, so that the moving ring 4 can rotate along with the rotating shaft 21, and the fourth seal ring 5 can ensure tightness between the moving ring 4 and the rotating shaft 21.

In this embodiment, the fourth sealing ring 5 may be a sealing member commonly used in the art, for example: o-rings, C-rings, etc.

As shown in fig. 5, the installation schematic diagram of the hydrostatic bearing isolation seal is shown, the whole hydrostatic bearing 22 isolation seal is sleeved outside the rotating shaft 21, the rotor assembly 20 is sleeved outside the rotating shaft 21, one end of the rotor assembly 20 is abutted against the compression sleeve 1, the lower end of the bushing is pressed against the compression sleeve 1, the right side of the bushing is abutted against the floating ring 3, and a second sealing ring 2 is arranged between the floating ring 3 and the bushing. The outside on the right side of quiet ring seat 12 is provided with bearing frame 25, and the both ends of end cover 24 set up respectively on bush and bearing frame 25, and an air inlet 27 has been seted up to end cover 24, and the inside of bearing frame 25 sets up bearing 22, and bearing 22 cover is located outside rotation axis 21, and the outside of bearing 22 still is provided with the bearing cap 26 that is used for covering bearing 22, and one side of rotor subassembly 20 is medium side 28, and one side of bearing cap 26 is lubricating oil side 29. After the installation is completed, the end cover 24 is provided with the air inlet hole 31, pressurized sealing air 33 firstly enters the air inlet groove 30 through the air inlet hole 31, then sequentially passes through the air inlet channel and the air inlet through hole to reach the end surface of the stationary ring 12 facing the moving ring 2, and an air film is formed on the end surface, so that the moving ring 4 and the stationary ring 7 are separated and do not contact, and the sealing air enters the gaps at two sides of the stationary ring 7, thereby achieving the purpose of isolating media.

The foregoing description of the embodiments has been provided for the purpose of illustrating the general principles of the invention, and is not meant to limit the scope of the invention, but to limit the invention to the particular embodiments, and any modifications, equivalents, improvements, etc. that fall within the spirit and principles of the invention are intended to be included within the scope of the invention.

Claims (10)

1. The static pressure type bearing isolation seal is characterized by comprising a movable component and a static component which are arranged in opposite directions, wherein the static component comprises a static ring and a static ring seat, the static ring is arranged on the static ring seat, an air inlet groove is formed in the static ring seat, an air inlet channel is arranged between the static ring and the static ring seat, a plurality of air inlet through holes are formed in the static ring, one end of the air inlet channel is communicated with the air inlet groove, and the other end of the air inlet channel is communicated with the air inlet through holes; the air outlet end of the air inlet through hole is arranged on the end face of the static ring, which faces the movable assembly.

2. The hydrostatic bearing isolation seal of claim 1, wherein at least one orifice plate is disposed in each of the intake through holes.

3. The hydrostatic bearing isolation seal of claim 1, wherein the end face of the stationary ring facing the moving assembly is provided with a plurality of evenly distributed end face grooves; preferably, the end face grooves are distributed in an annular shape; more preferably, the end face grooves are distributed in a ring shape along the edge of the static ring, and the circle center of the end face grooves coincides with the circle center of the static ring.

4. The hydrostatic bearing isolation seal of claim 1, wherein the stationary assembly further comprises an anti-rotation member having two ends disposed on the stationary ring seat and the stationary ring, respectively.

5. The hydrostatic bearing isolation seal of claim 1, wherein the stationary assembly further comprises 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, and two ends of the second elastic element are disposed on the push ring and the stationary ring seat, respectively.

6. The hydrostatic bearing isolation seal of claim 1, wherein the stationary ring is externally provided with a first elastic collar and a second elastic collar for limiting axial movement of the stationary ring, the first elastic collar and the second elastic collar being of intersecting dimensions, a central axis of the first elastic collar and the second elastic collar coinciding with a central axis of the stationary ring.

7. The hydrostatic bearing isolation seal of claim 1, wherein a floating ring is further provided outside the stationary ring seat; a first elastic element is arranged between the floating ring and the static ring seat, and two ends of the first elastic element are respectively arranged on the floating ring and the static ring seat.

8. The hydrostatic bearing isolation seal of claim 7, wherein 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 arranged on the outer side of the static ring seat; the end face of the floating ring, which is far away from one side of the static ring seat, is provided with a second sealing ring, the inner side of the floating ring is provided with a third sealing ring, and the inner side of the third sealing ring is the static ring seat; and the air inlet channel is formed among the static ring seat, the static ring, the first floating ring, the second floating ring, the first sealing ring, the second sealing ring and the third sealing ring.

9. The hydrostatic bearing isolation seal of claim 7, wherein the stationary assembly further comprises a fixture for securing the floating ring, the fixture disposed between the stationary ring seat and the floating ring.

10. The hydrostatic bearing isolation seal of claim 1, wherein the moving assembly comprises a moving ring, and both ends of the moving ring are respectively provided with a compression sleeve and a shaft sleeve; the static component is arranged on the outer side of the shaft sleeve; a fourth sealing ring is arranged between the pressing sleeve and the movable ring.

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