CN211715183U - Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander - Google Patents
Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander Download PDFInfo
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- CN211715183U CN211715183U CN202020266744.9U CN202020266744U CN211715183U CN 211715183 U CN211715183 U CN 211715183U CN 202020266744 U CN202020266744 U CN 202020266744U CN 211715183 U CN211715183 U CN 211715183U
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Abstract
The utility model relates to a miniature high-speed turboexpander is with gas lubrication dynamic pressure sealing device, this miniature high-speed turboexpander include the casing, inside main shaft and the impeller subassembly of being equipped with of casing, impeller subassembly fixes on the main shaft, impeller subassembly's outside is equipped with bearing assembly, the bearing assembly cover is established on the main shaft, sealing device is between impeller subassembly and bearing assembly, including rotating ring and static subassembly, the rotating ring overlaps to be established on the main shaft, just the both ends centre gripping of rotating ring is in impeller subassembly with between the bearing assembly, static subassembly is fixed on the casing, just a terminal surface of static subassembly with the rotating ring laminating forms sealed face, be equipped with fluid dynamic pressure groove on the rotating ring with the terminal surface of static subassembly laminating. Compared with the prior art, the sealing device of the application is applied to the micro high-speed turboexpander, can realize zero leakage of bearing side lubricating oil to the outlet side of the expander, and has extremely low internal gas loss of the expander.
Description
Technical Field
The application relates to the technical field of mechanical sealing, in particular to a gas lubrication dynamic pressure sealing device for a miniature high-speed turboexpander.
Background
At present, the exhaust emission of diesel engines for heavy trucks has become a source of pollution to the atmosphere which must be considered and respected. With the annual improvement of government exhaust emission standards of automobiles including heavy trucks, a miniature turboexpander which takes the exhaust emission of the heavy trucks as a working medium and generates power by applying work to the outside is produced. Because the main shaft of the micro turboexpander is extremely small, the shaft diameter is generally less than 10mm, but the rotating speed is extremely high, and can often reach more than 100,000rpm, and some are even higher. For such high rotational speed micro turboexpanders, sealing between the exhaust side and the bearings is critical. In view of the high spindle speeds, a common form of seal is a non-contact labyrinth seal with air as the barrier gas to purge expander exhaust gas that leaks out of the labyrinth seal. The working clearance between the adopted non-contact labyrinth seal and the main shaft is relatively large, so that three problems are caused: firstly, the flow rate of air purging is large; secondly, the loss of bearing lubricating oil is caused; thirdly, the lubricant oil containing the additive may enter the working chamber of the micro-expander to adversely affect the operation of the micro-expander. Therefore, the current shaft end sealing mode is difficult to meet the working requirement of the miniature high-speed turboexpander.
Disclosure of Invention
The purpose of the present application is to provide a gas lubrication dynamic pressure sealing device for a micro high-speed turboexpander, which has small gas consumption and good sealing performance, in order to overcome the defects of the prior art.
In order to achieve the object of the present application, the present application provides the following technical solutions.
In a first aspect, the application provides a miniature high-speed turboexpander is with gas lubrication dynamic pressure sealing device, miniature high-speed turboexpander includes the casing, be equipped with main shaft and impeller subassembly in the casing, impeller subassembly fixes on the main shaft, impeller subassembly's outside is equipped with bearing assembly, the bearing assembly cover is established on the main shaft, sealing device is between impeller subassembly and bearing assembly, including rotating ring and static subassembly, the rotating ring overlaps to be established on the main shaft, just the both ends centre gripping of rotating ring is in impeller subassembly with between the bearing assembly, static subassembly is fixed on the casing, just a terminal surface of static subassembly with the rotating ring laminating forms sealed face, be equipped with fluid dynamic pressure groove on the terminal surface with the laminating of static subassembly on the rotating ring. In the present application, the impeller assembly and the bearing assembly are prior art, and the impeller assembly and the bearing assembly may be a body of the impeller or a shaft sleeve at one end of the impeller, which is abutted against the moving ring, and are determined according to the specific structure of the expander; similarly, the bearing assembly abutting against the moving ring may be a sleeve of the bearing assembly.
When the micro high-speed turboexpander works, the moving ring is clamped by the impeller assembly and the bearing assembly, so that the moving ring rotates at a high speed along with the impeller assembly, a pumping effect can be generated in the fluid dynamic pressure groove, a very small amount of gas is sucked from the micro high-speed turboexpander and filled between the moving ring and the static assembly (namely a sealing surface), a layer of micron-order gas film is formed between the sealing surfaces by utilizing the fluid dynamic pressure effect, the lubricating and isolating effects are realized on the sealing surfaces, and the sealed non-contact operation is realized. Because the rotating speed of the expansion machine is extremely high, the rigidity of the extremely thin air film on the sealing surface is very high, and the long-period stable operation of sealing can be ensured; meanwhile, the lubricating oil on the bearing side can be effectively isolated, namely the pressure of a medium in the shell of the expander is lower than the pressure of gas outside the shell, and zero leakage of the lubricating oil on the bearing side (namely outside the shell) to the outlet side of the expander can be ensured; in addition, since the seal surface clearance is extremely small, the consumption of the process medium on the outlet side of the expander is also extremely small, that is, with the gas-lubricated dynamic pressure seal device, zero leakage of the bearing-side lubricating oil to the expander side can be ensured only by extremely low consumption of the expander outlet gas.
In a preferred embodiment of the first aspect, the rotating ring is T-shaped, and includes a rotating ring and a shaft sleeve, the center of a fourth end surface of one end of the rotating ring is integrally and fixedly connected to one end of the shaft sleeve, the rotating ring and the shaft sleeve are both sleeved outside the spindle, a third end surface of the other end of the rotating ring abuts against the bearing assembly, a sixth end surface of the other end of the shaft sleeve abuts against the impeller assembly, the fourth end surface is provided with the hydrodynamic groove, and the fourth end surface and the stationary assembly are attached to each other to form a sealing surface. In the present application, the sealing surface is annular, that is, the portion of the fourth end surface that is integrally connected to the sleeve is removed, that is, the sealing end surface.
In a preferable mode of the first aspect, the hydrodynamic grooves are of a unidirectional rotation groove type or a bidirectional rotation groove type, a common unidirectional rotation groove type includes an arc groove or a spiral groove, and a common bidirectional rotation groove type includes a U-shaped groove, a T-shaped groove, and the like, and the hydrodynamic grooves have a groove depth of 3-20 μm. Preferably, a high-hardness wear-resistant coating or surfacing layer is formed on the fourth end face in a spraying or surfacing mode, micrometer-level hydrodynamic grooves evenly distributed along the circumferential direction are machined on the coating or surfacing layer in a special machining mode, the hydrodynamic grooves are located at the inner diameter of the sealing face and communicated with the inside of the micro-expander, and the outer diameter of the sealing face is a non-groove dam area. The base material of the moving ring is preferably high-strength precipitation hardening stainless steel, and martensite stainless steel or dual-phase steel can be selected for the working condition that the rotating speed is not very high. For the high-hardness wear-resistant coating, the material used is the hard alloy sprayed by supersonic flame, and for the high-hardness surfacing layer, the material used is the hard alloy.
In a preferable scheme of the first aspect, the periphery of the fourth end face is a dam region not provided with a hydrodynamic groove, and the width of the dam region accounts for 0.2 to 0.7 of the width of the entire sealing surface. When the width of the dam area is too small, the gas film formed in the hydrodynamic groove is too thick, and the medium gas easily passes through the dam area and leaks outwards, so that the sealing performance is reduced; when the width of the dam area is too large, the width of the hydrodynamic groove is small, an air film is not easy to form, and the service life performance of the seal is also influenced.
In a preferred scheme of the first aspect, the stationary assembly comprises a spring seat, a spring and a stationary ring, wherein the spring seat is fixed on the housing, the spring seat is arranged on the periphery of the main shaft, the stationary ring is arranged in the spring seat, a first end face at one end of the stationary ring is attached to the movable ring to form a sealing face, a second end face at the other end of the stationary ring is axially supported by a group of circumferentially uniformly distributed springs and is used for axially supporting the stationary ring, the springs are perpendicular to the sealing face, and the other end of each spring is arranged in a spring hole in the spring seat. The group of springs of the application comprises a plurality of springs and are evenly distributed along the circumferential direction. When the expander operates, the static ring is jointed with the end face of the movable ring by means of the axial pressing force of the spring and the gas pressure of the isolation gas at the bearing side or the medium gas at the outlet of the expander. The static ring material is high-quality resin-impregnated carbon graphite or antimony-impregnated carbon graphite.
In a preferred scheme of the first aspect, the fixed ring and the spring seat realize the anti-rotation between the fixed ring and the spring seat through a lug and groove structure; and a sealing ring is arranged between the matching surfaces of the static ring and the inner wall of the spring seat. The sealing ring is used for preventing gas in the expansion machine from leaking from a gap between the spring seat and the static ring.
In a preferred scheme of the first aspect, the sealing ring is an X-shaped sealing ring, and due to the existence of the spring and the high-speed rotation of the main shaft, the sealing ring between the spring seat and the stationary ring has axial micro-motion and deformation, and the X-shaped sealing ring can well follow and compensate the micro-motion and deformation, has better anti-back pressure capability, and particularly can be provided with an anti-back pressure limiting structure at the position of the X-shaped sealing ring.
In a preferred aspect of the first aspect, a snap ring is disposed on an inner wall of the spring seat, and the snap ring is used for limiting the static ring from disengaging from the spring seat. When the static component is not assembled, the static ring can be separated from the spring seat under the action of the spring because the first end face of the static ring cannot be axially limited. Therefore, the clamping ring is arranged in the spring seat, when the sealing assembly is carried out, the static ring keeps static under the action of the clamping ring and the spring, and the sealing device is convenient to assemble. After the equipment is installed, the first end face of the static ring is pressed by the dynamic ring and separated from the clamping ring, and the clamping ring cannot influence the operation of the sealing device.
In a preferred aspect of the first aspect, an O-ring seal is disposed between the spring seat and the housing.
Compared with the prior art, the beneficial effect of this application lies in:
(1) because the rotating speed of the expansion machine is extremely high, the rigidity of the extremely thin air film on the sealing surface is very high, and the long-period stable operation of sealing can be ensured; meanwhile, the lubricating oil on the bearing side can be effectively isolated, namely the pressure of a medium in the shell of the expander is lower than the pressure of gas outside the shell, and zero leakage of the lubricating oil on the bearing side (namely outside the shell) to the outlet side of the expander can be ensured;
(2) the minimum sealing surface gap ensures that the consumption of the process medium on the outlet side of the expander is very small, namely, the zero leakage of the lubricating oil on the bearing side to the expander side can be ensured only by the extremely low consumption of the outlet gas of the expander by the gas-lubricated dynamic pressure sealing device.
Drawings
Fig. 1 is a schematic structural view of a sealing device in the present invention;
FIG. 2 is a surface structure view of a fourth end face in example 1;
fig. 3 is a schematic structural view of the hydrodynamic groove of the present application as a bidirectional groove.
The device comprises a movable ring 1, a rotating ring 11, a shaft sleeve 12, a third end face 13, a fourth end face 14, a sixth end face 16, a hydrodynamic groove 17, a dam region 18, a stationary ring 2, a first end face 21, a second end face 22, a spring seat 3, an X-shaped sealing ring 4, a spring 5, a snap ring 6, an O-shaped ring 7, a main shaft 8, a housing 9, a bearing 91, an impeller 92 and an integrated connecting area A, wherein the movable ring is a movable ring, the rotating ring 11 is a rotating ring, the shaft sleeve 12 is a shaft sleeve, the third end face 13 is a third end face, the fourth end.
Detailed Description
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
A gas lubrication dynamic pressure sealing device for a miniature high-speed turboexpander is structurally shown in figure 1 and comprises a movable ring 1 and a static component. The rotating ring 1 is formed by integrating a rotating ring 11 and a shaft sleeve 12 into a whole and is T-shaped, wherein the two ends of the rotating ring 11 are respectively a third end surface 13 and a fourth end surface 14, and the fourth end surface 14 and one end of the shaft sleeve 12 are coaxially and integrally connected to form an integrated connection area a, as shown in fig. 2. The moving ring 1 is made of precipitation hardening stainless steel, a high-hardness wear-resistant coating is sprayed or surfacing-welded on the fourth end face 14 except the integrated connection area A, micrometer-scale hydrodynamic grooves 17 evenly distributed along the circumferential direction are machined on the coating or surfacing layer in a special machining mode, the hydrodynamic grooves 17 are spiral grooves, the direction of the spiral grooves is opposite to the rotating direction of the moving ring 1, for example, in the figure 2, the spiral grooves are clockwise, the rotating direction of the moving ring 1 is anticlockwise, and the groove depth of the hydrodynamic grooves 17 is 3-20 micrometers. The hydrodynamic groove 17 has a groove region at the inner diameter of the sealing surface which is in gas communication with the outlet of the micro-expander and an outer diameter which is a slotless dam region 18, i.e. in this embodiment, the sealing surface is the region of the fourth end face 14 excluding the integral joint region a. The third end surface 13 abuts against the bearing assembly 91, and the other end of the sleeve (i.e., the sixth end surface 16) abuts against the impeller assembly 92, so that the rotating ring 1 transmits torque by pressing the expander impeller assembly 92 and the bearing assembly 91, and the rotating ring 1 rotates at a high speed together with the main shaft 8. The hydrodynamic grooves used in this embodiment may also be bidirectional grooves, such as T-shaped grooves, the structure of which is shown in fig. 3.
The static assembly is composed of a carbon graphite static ring 2, a spring 5, an X-shaped sealing ring 4 and a spring seat 3, and the end face of the static ring 2 is attached to the end face of the movable ring 1 by means of axial pressing force of the spring 5 and gas pressure of isolation gas on the side of a bearing assembly 91 or medium gas at the outlet of an expander. The two ends of the static ring 2 are respectively a first end surface 21 and a second end surface 22, wherein the first end surface 21 and the fourth end surface 14 form a sealing surface, a group of springs 5 annularly distributed along the axis are arranged between the second end surface 22 and the spring seat 3, and the static ring 2 is attached to the moving ring 1 by means of axial pressing force of the springs 5 and gas pressure of isolation gas at the bearing side or medium gas at the outlet of the expansion machine. The static ring 2 and the spring seat 3 realize the rotation prevention of the static ring 2 through a lug and groove structure, and the structure is more compact than that of a common anti-rotation pin; set up the snap ring groove on the spring holder 3 to set up snap ring 6 wherein, through the axial limiting displacement of snap ring 6, can make quiet ring 2, spring 5, dynamic seal circle, spring holder 3 integrated as a whole in the static subassembly, the seal assembly of being convenient for. An O-ring 7 is provided between the spring seat 3 and the housing 9.
When the micro expander works, the movable ring 1 rotates at a high speed, the outlet gas of the expander is sucked between the sealing surfaces between the movable ring 1 and the static ring 2 by utilizing the pumping action of the micron-order hydrodynamic groove 17 etched at the inner diameter of the end surface of the movable ring 1, a micron-order gas film is formed between the sealing surfaces by utilizing the hydrodynamic effect, the lubricating and isolating action is played on the sealing surfaces, and the sealed non-contact operation is realized. Because the rotating speed of the expansion machine is extremely high, the rigidity of the extremely thin air film on the sealing surface is very high, and the long-period stable operation of sealing can be ensured; meanwhile, the lubricating oil on the bearing 91 side can be effectively isolated, and even if the medium pressure on the outlet side of the expander is lower than the gas pressure on the bearing 91 side, zero leakage of the lubricating oil on the bearing 91 side to the outlet side of the expander can be ensured; in addition, since the end surface clearance is extremely small, the consumption of the process medium on the outlet side of the expander is also extremely small, and that is, with the gas-lubricated dynamic pressure seal device, zero leakage of the lubricating oil on the bearing 91 side to the expander side can be ensured only by extremely low consumption of the expander outlet gas.
The embodiments described above are intended to facilitate the understanding and appreciation of the application by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present application is not limited to the embodiments herein, and those skilled in the art who have the benefit of this disclosure will appreciate that many modifications and variations are possible within the scope of the present application without departing from the scope and spirit of the present application.
Claims (9)
1. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander comprises a shell, wherein a main shaft and an impeller assembly are arranged in the shell, the impeller assembly is fixed on the main shaft, a bearing assembly is arranged outside the impeller assembly and sleeved on the main shaft, and the gas lubrication dynamic pressure sealing device is characterized in that the sealing device is arranged between the impeller assembly and the bearing assembly and comprises a moving ring and a static assembly, the moving ring is sleeved on the main shaft, two ends of the moving ring are clamped between the impeller assembly and the bearing, the static assembly is fixed on the shell, an end face of the static assembly and the moving ring are attached to form a sealing face, and a fluid dynamic pressure groove is formed in the end face of the moving ring, which is attached to the static assembly.
2. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander according to claim 1, wherein the dynamic ring is T-shaped and includes a rotating ring and a shaft sleeve, and a center of a fourth end surface of one end of the rotating ring is fixedly connected to one end of the shaft sleeve, the rotating ring and the shaft sleeve are both sleeved outside the main shaft, a third end surface of the other end of the rotating ring abuts against the bearing assembly, a sixth end surface of the other end of the shaft sleeve abuts against the impeller assembly, the fourth end surface is provided with the hydrodynamic grooves, and the fourth end surface and the stationary assembly are fitted to form a sealing surface.
3. The gas lubrication dynamic pressure seal device for a micro high-speed turboexpander according to claim 2, wherein the hydrodynamic groove is a groove type rotating in a unidirectional direction or a groove type rotating in a bidirectional direction, and the groove depth of the hydrodynamic groove is 3 to 20 μm.
4. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander according to claim 2, wherein the periphery of the fourth end surface is a dam region where no hydrodynamic groove is formed, and the width of the dam region occupies 0.2 to 0.7 of the width of the entire sealing surface.
5. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander according to claim 1, wherein the stationary component comprises a spring seat, a spring and a stationary ring, wherein the spring seat is fixed on the housing, the spring seat is arranged on the periphery of the main shaft, the stationary ring is arranged in the spring seat, a first end surface at one end of the stationary ring is attached to the movable ring to form a sealing surface, a second end surface at the other end of the stationary ring is axially supported by a set of circumferentially uniformly distributed springs for axial support of the stationary ring, the springs are perpendicular to the sealing surface, and the other end of the springs are arranged in a spring hole in the spring seat.
6. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander according to claim 5, wherein the static ring and the spring seat realize the rotation prevention between the static ring and the spring seat through a lug and groove structure, and a sealing ring is arranged between the matching surfaces of the static ring and the inner wall of the spring seat.
7. The gas lubrication dynamic pressure seal device for a miniature high-speed turboexpander of claim 6, wherein said seal ring is an X-shaped seal ring.
8. The gas lubrication dynamic pressure sealing device for the micro high-speed turboexpander according to claim 5, wherein a snap ring is provided on an inner wall of the spring seat, and the snap ring is used for limiting the static ring from being separated from the spring seat.
9. A gas lubrication dynamic pressure sealing device for a micro high-speed turboexpander according to claim 5, wherein an O-ring is provided between the spring seat and the housing.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020266744.9U CN211715183U (en) | 2020-03-06 | 2020-03-06 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
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| CN202020266744.9U CN211715183U (en) | 2020-03-06 | 2020-03-06 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
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| CN211715183U true CN211715183U (en) | 2020-10-20 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111188653A (en) * | 2020-03-06 | 2020-05-22 | 上海好米密封科技有限公司 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
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2020
- 2020-03-06 CN CN202020266744.9U patent/CN211715183U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111188653A (en) * | 2020-03-06 | 2020-05-22 | 上海好米密封科技有限公司 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
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Address after: 201111 Room 102, building 3, no.508 Zixu Road, Minhang District, Shanghai Patentee after: Shanghai Yousai Sealing Technology Co.,Ltd. Address before: 201111 Room 102, building 3, no.508 Zixu Road, Minhang District, Shanghai Patentee before: Shanghai haomi Sealing Technology Co.,Ltd. |
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