CN205618672U - Two -way rotation is from pump sending fluid dynamic pressure type mechanical seal - Google Patents
Two -way rotation is from pump sending fluid dynamic pressure type mechanical seal Download PDFInfo
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- CN205618672U CN205618672U CN201521134635.7U CN201521134635U CN205618672U CN 205618672 U CN205618672 U CN 205618672U CN 201521134635 U CN201521134635 U CN 201521134635U CN 205618672 U CN205618672 U CN 205618672U
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- 239000012530 fluid Substances 0.000 title claims abstract description 118
- 239000011148 porous material Substances 0.000 claims abstract description 12
- 238000007789 sealing Methods 0.000 claims description 112
- 230000003068 static effect Effects 0.000 claims description 87
- 238000005086 pumping Methods 0.000 claims description 55
- 230000002457 bidirectional effect Effects 0.000 claims description 23
- 238000000034 method Methods 0.000 abstract description 11
- 230000000694 effects Effects 0.000 abstract description 4
- 230000007547 defect Effects 0.000 abstract description 3
- 230000009699 differential effect Effects 0.000 abstract 1
- 239000008187 granular material Substances 0.000 abstract 1
- 239000002245 particle Substances 0.000 description 9
- 238000005299 abrasion Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000011010 flushing procedure Methods 0.000 description 4
- 239000007787 solid Substances 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 238000010008 shearing Methods 0.000 description 3
- 238000001914 filtration Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000009545 invasion Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
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Abstract
This technique is a two -way rotation is from pump sending fluid dynamic pressure type mechanical seal, need assist circulation system to assist work in order to overcome present two -way rotatory fluid dynamic pressure mechanical seal, lack the defect that anti granule disturbed the ability, it is by the rotating ring, O shape circle for the rotating ring, quiet ring, quiet O shape circle for the ring, a spring, the stationary seat is constituteed, the rotating ring terminal surface includes the helicla flute, sealed weir and sealed dam, quiet ring terminal surface external diameter side is processed into the conical surface, adopt the fluid pump the mode of going into with the fluid pump produce bu tong soon to the time the fluid dynamic pressure, rotating ring forward rotation comes from sealed chamber, is covered with the medium of helicla flute through the drainage pore, is added quick fast fluid by the convex surface of helicla flute, the centrifugal force effect down, the edge concave surface moves and pumps to sealed chamber to rotating ring external diameter side flow, rotating ring reverse rotation, the medium of sealed intracavity wedge along the concave surface of helicla flute, and the pump goes into to the helicla flute root to become high -pressure fluid to rotating ring internal diameter side flow moves, under the pressure differential effect, flow again through the drainage pore and into seal the chamber.
Description
Technical Field
The technology belongs to the technical field of sealing, and particularly relates to a self-pumping mechanical seal capable of rotating in two directions and having a fluid dynamic pressure effect, which is suitable for sealing rotating shafts of rotating machines such as various compressors, centrifugal pumps, reaction kettle stirrers and the like.
Background
The existing single-rotation-direction mechanical seals, such as a fluid dynamic and static pressure combined non-contact mechanical seal with a single-row spiral groove disclosed in US4212475, a fluid dynamic pressure type double-row spiral groove end face seal device disclosed in US5201521, a double-ring spiral groove end face seal disclosed in chinese patent ZL96108614.9, a centrifuge dry gas seal disclosed in ZL201020106087.8, and the like, are only suitable for unidirectional rotation, and the media forming fluid dynamic pressure are all pumped into the grooves, and higher pressure is generated at the root of the grooves, so that an end face opening force is formed, friction of the seal end face is reduced, but leakage between the end faces of the moving ring and the stationary ring is increased; although the double-row spiral groove mechanical sealing device utilizes the balance between the pump-suction pressure difference generated by two rows of spiral grooves and the fluid pressure difference between the inner side and the outer side of the sealing end surface, and overcomes the defect of large leakage rate of the single-row spiral groove mechanical sealing to a certain extent, the double-row spiral groove mechanical sealing device has a more complex structure and large installation space requirement, is only suitable for the working condition that the fluid pressure difference between the two sides of the sealing end surface is not large, and greatly limits the application range of the double-row spiral groove mechanical sealing device due to the performance characteristic. The existing double-rotation-direction mechanical seal, such as Chinese patent 201210041042.5 'mushroom-shaped groove bidirectional rotation fluid dynamic pressure type mechanical seal structure', 201010211454.5 'gas lubrication non-contact mechanical seal device capable of bidirectional rotation', US patent 5090712 and the like, better solves the sealing difficulty during the forward and reverse rotation of the rotary machine, and the mechanical seal is characterized in that a certain number of grooves with axial symmetry geometric shapes are arranged on the end faces of a moving ring and a static ring, and half of the grooves generate fluid dynamic pressure effect by using fluid sucked during rotation no matter the rotating shaft rotates forwards or reversely, so as to form opening force for separating the sealing end faces of the moving ring and the static ring which are mutually jointed, so that the end faces of the moving ring and the static ring are separated from contact to reduce abrasion, and a continuous and stable layer of fluid film with certain rigidity is formed between the two end faces to prevent the leakage of the fluid. The double-rotation-direction mechanical seal belongs to a fluid pumping type mechanical seal like the single-rotation-direction mechanical seal, clean pumping fluid needs to be provided when fluid dynamic pressure is established, an auxiliary filtering system needs to be added, otherwise, the end face of a sealing dam can be damaged by invasion of any tiny particles in the pumping fluid, and failure of the fluid dynamic pressure mechanical seal is accelerated. The proposal of ZL201310201473.3 "self-pumping hydrodynamic mechanical seal" solved this problem well. However, it still has a problem of insufficient handedness selectivity.
Disclosure of Invention
The technical purpose of the present invention is to provide a bidirectional rotary self-pumping mechanical seal, so as to overcome the defects that the existing bidirectional rotary fluid dynamic pressure mechanical seal needs an auxiliary circulation system to assist the work, has small fluid dynamic pressure effect and lacks the capability of resisting particle interference.
The technical scheme is as follows:
a bidirectional rotation self-pumping fluid dynamic pressure type mechanical seal is arranged between a shell 2 and a rotating shaft 10 of mechanical equipment and consists of a moving ring 3, an O-shaped ring 11 for the moving ring, a static ring 4, an O-shaped ring 5 for the static ring, a spring 7 and a static ring seat 13, wherein the end surface of the moving ring comprises three parts, namely a spiral groove, a sealing weir and a sealing dam, the number of the spiral grooves 31 is not less than 3, the spiral grooves are uniformly distributed on the outer diameter side of the end surface of the moving ring, the inner diameter side of the end surface of the moving ring is provided with the sealing dam 33, and the sealing surface between the spiral grooves 31; the outer diameter side of the end surface of the static ring is processed into a conical surface 41, and meanwhile, a collecting ring groove 34 communicated with the root part of each spiral groove is processed on the end surface of the dynamic ring or the static ring; the movable ring 3 or the static ring 4 is provided with a drainage pore passage 35 for communicating the collecting ring groove 34 with the sealing cavity 1, and the device is characterized in that:
fluid dynamic pressure in different rotating directions is generated by adopting a fluid pumping-out and fluid pumping-in mode;
the fluid is pumped out, that is, when the rotating ring rotates in the forward direction, the medium from the seal cavity 1 and fully distributed in the spiral groove 31 through the drainage hole channel 35 is accelerated to be high-speed fluid by the convex surface 36 of the spiral groove 31, and under the action of centrifugal force, the high-speed fluid flows to the outer diameter side of the rotating ring 3 along the concave surface 37 and is pumped out to the seal cavity 1, at this time, a low-pressure area is formed at the root of the spiral groove 31, and the medium in the seal cavity 1 flows into the root of the spiral groove 31 through the drainage hole channel 35 again under the action of pressure difference, so that a forward self-pumping cycle is formed;
The fluid is pumped, that is, when the rotating ring rotates reversely, the medium in the sealing cavity 1 is wedged along the concave surface 37 of the spiral groove 31 and flows to the inner diameter side of the rotating ring 3 to be pumped to the root of the spiral groove 31, because of the reduction of the rotating radius, the linear velocity of the fluid at the root of the spiral groove 31 is reduced, at this time, part of kinetic energy of the fluid is converted into pressure energy and becomes high-pressure fluid, and the high-pressure fluid flows into the sealing cavity 1 again through the drainage hole channel 35 under the action of pressure difference, so that one-time reverse self-pumping circulation is formed.
The beneficial effect of this technique:
1. the technology can prevent particles in the fluid from entering the sealing dam, reduce the abrasion of the end face of the sealing dam and has the capability of resisting particle interference. Specifically, the method comprises the following steps:
when the rotating ring rotates in the positive direction, the bidirectional-rotation self-pumping hydrodynamic mechanical seal works in a fluid pumping mode, and in the rotating process of the rotating ring, fluid media passing through the spiral groove 25 are subjected to the action of centrifugal force to generate flow far away from the sealing dam, so that solid particles in self-pumping fluid cannot enter the area of the sealing dam 24, and abrasive wear of the end face of the sealing dam is avoided.
When the rotating ring rotates reversely, the bidirectional rotating self-pumping fluid dynamic pressure type mechanical seal works in a fluid pumping mode, in the rotating process of the rotating ring, a medium in the seal cavity 1 is wedged into a spiral groove along the concave surface 23 of the spiral groove 25 on one hand, flows to the root part of the spiral groove in the direction parallel to the bottom surface of the spiral groove and the seal dam in the spiral groove, and on the other hand, the fluid in the spiral groove is wedged into the concave surface 23 of the spiral groove 25 on the other hand, when flowing in the spiral groove, the medium between the plane of the rotating ring seal weir and the conical surface of the stationary ring is driven to flow through the small end of the conical surface of the stationary ring in the flow velocity direction forming a certain angle with the seal dam by the action of the radial component of viscous shearing force, enters a flow collecting ring groove on the rotating ring or the stationary ring, flows to a flow guide pore passage 20 on the rotating ring 3 or the stationary ring 11 and communicated with the seal cavity 1, effectively preventing particles in the fluid from entering the end face of the sealing dam and reducing the abrasion of the end face of the sealing dam.
2. Has stable operation characteristics. Specifically, the method comprises the following steps:
when the moving ring rotates in the positive direction, the bidirectional-rotation self-pumping hydrodynamic mechanical seal works in a fluid pumping mode, the convex surface 22 of the spiral groove 25 accelerates to form high-speed fluid, and in the process of pumping the fluid out of the spiral groove 25, along with the gradual increase of the flow cross section area of the spiral groove 25, the flow speed is reduced, the pressure is increased, and the opening force for separating the moving ring 3 from the static ring 11 is formed; when the opening force for separating the moving ring 3 and the static ring 11 is increased, the spring 7 arranged on the static ring seat 14 is compressed, when the increased opening force is balanced with the sum of the spring force when the spring 7 is compressed and the effective acting force of the sealing fluid pressure, a certain gap is maintained between the moving ring and the static ring, no abrasion exists between the sealing end surfaces, the leakage rate is low, and when the resistance of the leakage fluid flowing through the sealing dam is high, the leakage rate is even reduced to zero; at the moment, the gap between the dynamic ring and the static ring is called as a balance gap; the effective acting force of the sealing fluid pressure is the product of the sealing fluid pressure and the effective acting area of the sealing fluid pressure acting on the compensating ring to close the non-compensating ring; the compensating ring is a static ring or a moving ring which is directly contacted with the spring, and the non-compensating ring is a moving ring or a static ring which is not directly contacted with the spring; when the working parameters are fluctuated to lead the actuating and the end face spacing of the static ring to be increased, the leakage rate is increased, the pressure between the end faces of the dynamic ring and the static ring is reduced, the spring 7 is further compressed, at the moment, the sum of the effective acting force of the compression spring force and the sealing fluid pressure is greater than the opening force between the end faces of the dynamic ring and the static ring, and the end face spacing of the dynamic ring and the static ring is reduced; when the distance between the end faces of the movable ring and the static ring is reduced to be smaller than the balance gap, the leakage rate is reduced, the pressure between the end faces of the movable ring and the static ring is increased, the compressed spring 7 is released, at the moment, the sum of the effective acting force of the compression spring force and the effective acting force of the sealing fluid pressure is smaller than the opening force between the end faces of the movable ring and the static ring, the distance between the end faces of the movable ring and the static ring is increased, and when the pressure difference value of the two sides of the sealing dam is larger than the resistance of the leakage fluid flowing through the. The leakage rate and the opening force are in a stable new working state by continuous automatic adjustment.
When the moving ring rotates reversely, the bidirectional rotating self-pumping fluid dynamic pressure type mechanical seal works in a fluid pumping mode, the fluid which flows to the root of the spiral groove 25 along the concave surface 23 of the spiral groove 25 is wedged and flows to the inner diameter side of the moving ring 3, the linear velocity of the fluid which flows to the root of the spiral groove 25 is reduced due to the reduction of the rotating radius, and at the moment, partial kinetic energy of the fluid is converted into pressure energy and is converted into high-pressure fluid to form opening force for separating the moving ring 3 and the static ring 11; along with the increase of the opening force for separating the moving ring 3 and the static ring 11, the spring 7 arranged on the static ring seat 14 is compressed, when the sum of the increased opening force, the spring force when the spring 7 is compressed and the effective acting force of the pressure of the sealing fluid is balanced, a certain gap is maintained between the moving ring and the static ring, no abrasion exists between the sealing end surfaces, the leakage rate is small, and when the resistance of the leakage fluid flowing through the sealing dam is large, the leakage rate is even reduced to zero; at the moment, the gap between the dynamic ring and the static ring is called as a balance gap; when the working parameters are fluctuated to lead the actuating and the end face spacing of the static ring to be increased, the leakage rate is increased, the pressure between the end faces of the dynamic ring and the static ring is reduced, the spring 7 is further compressed, at the moment, the sum of the effective acting force of the compression spring force and the sealing fluid pressure is greater than the opening force between the end faces of the dynamic ring and the static ring, and the end face spacing of the dynamic ring and the static ring is reduced; when the distance between the end faces of the movable ring and the static ring is reduced to be smaller than the balance gap, the leakage rate is reduced, the pressure between the end faces of the movable ring and the static ring is increased, the compressed spring 7 is released, at the moment, the sum of the effective acting force of the compression spring force and the effective acting force of the sealing fluid pressure is smaller than the opening force between the end faces of the movable ring and the static ring, the distance between the end faces of the movable ring and the static ring is increased, and when the pressure difference value of the two sides of the sealing dam is larger than the resistance of the leakage fluid flowing through the. The leakage rate and the opening force are in a stable new working state by continuous automatic adjustment.
3. Has the functions of self-lubricating, self-cooling flushing and self-cleaning. The fluid groove is utilized to pump out or pump in fluid automatically, so that on one hand, fluid dynamic pressure is generated on the end faces of the movable ring and the static ring, and on the other hand, the fluid continuously flows through the fluid groove, thereby not only lubricating the end faces of the movable ring and the static ring, but also taking away heat of the end faces of the movable ring and the static ring; meanwhile, the self-flushing of the sealing end face is realized, solid particles can be automatically removed, and abrasive wear of the sealing dam can be avoided; not only saves a complex washing auxiliary system and a filtering device, but also can ensure the reliability of the mechanical seal work and prolong the service life.
4. The device is suitable for forward and reverse equipment and equipment with forward and reverse rotation requirements.
5. The application range is wide. The sealing device has the functions of upstream pumping mechanical sealing and dry gas sealing, and is suitable for sealing liquid or gas.
In the bidirectional rotating self-pumping hydrodynamic mechanical seal, the diameter of the small end of the conical surface 26 positioned outside the end surface of the stationary ring 11 is larger than the outer diameter of the collecting ring groove 34 on the end surface of the moving ring or the stationary ring.
In the bidirectional rotary self-pumping fluid dynamic pressure type mechanical seal, the collecting ring groove is positioned on the end face of the movable ring, the outer diameter of the collecting ring groove is larger than the diameter of the root circle of the spiral groove, and the inner diameter of the collecting ring groove is equal to the diameter of the root circle of the spiral groove. When the collecting ring groove is arranged on the end face of the moving ring, the drainage hole channel 35 is preferably arranged on the moving ring, although the drainage hole channel 35 can also be arranged on the stationary ring.
In the bidirectional rotary self-pumping fluid dynamic pressure type mechanical seal, the collecting ring groove 34 is positioned on the end face of the stationary ring, the outer diameter of the collecting ring groove is larger than the diameter of the root circle of the spiral groove, and the inner diameter of the collecting ring groove is smaller than or equal to the diameter of the root circle of the spiral groove. When the collecting ring groove is arranged on the end face of the static ring, the drainage hole channel 35 is preferably arranged on the static ring, although the drainage hole channel 35 can also be arranged on the dynamic ring.
The position of the collector ring groove, the inner diameter and the outer diameter of the collector ring groove are required to be capable of communicating the root of the spiral groove with the drainage channel smoothly, so that the medium flows smoothly.
Drawings
Fig. 1 is a schematic axial sectional structure diagram of a bidirectional rotary self-pumping hydrodynamic mechanical seal with a collecting ring groove and a drainage channel on a rotating ring.
FIG. 2 is a schematic view of the end face of the rotating ring with spiral grooves, collecting ring grooves and drainage channels.
FIG. 3 is a schematic view of the end face of a stationary ring with a conical surface formed on the outer diameter side of the end face of the stationary ring paired with a rotating ring provided with a spiral groove, a collecting ring groove and a drainage channel.
Fig. 4 is a schematic axial sectional structure view of a bidirectional rotary self-pumping hydrodynamic mechanical seal with a collecting ring groove and a drainage channel on a stationary ring.
FIG. 5 is a schematic view of an end surface of a rotating ring with a spiral groove.
FIG. 6 is a schematic end view of a stationary ring having a tapered surface formed on the outer diameter side of the end surface paired with a rotating ring having a spiral groove and a collecting ring groove and a drainage channel formed on the end surface.
Fig. 7 shows the fluid flow conditions when the bidirectional rotary self-pumping hydrodynamic mechanical seal with collecting ring grooves and drainage channels on the rotating ring works in a pumping mode.
Fig. 8 shows the fluid flow state of the bidirectional rotary self-pumping hydrodynamic mechanical seal with collecting ring grooves and drainage channels on the rotating ring when the seal is operated in a pumping mode.
Fig. 9 shows the fluid flow conditions when the bidirectional rotary self-pumping hydrodynamic mechanical seal with collecting ring grooves and drainage channels on the stationary ring is operated in a pump-out mode.
Fig. 10 shows the fluid flow conditions of a bidirectional rotary self-pumping hydrodynamic mechanical seal with collecting ring grooves and drainage channels on the stationary ring operating in a pumping mode.
Wherein,
r1-inner radius of sealing end face between the dynamic ring and the static ring;
r2-the outer radius of the sealing end face where the moving ring and the static ring are mutually attached;
r3-inner radius of collecting ring groove;
r4 — collector ring groove outer radius;
rg-root radius of spiral groove
Rt — radius of the small end of the cone;
ro is the radius of the end face of the drainage channel;
rk is radius of the drainage channel;
h, the groove depth of the spiral groove;
t is the included angle between the conical surface and the end surface;
w 1-positive rotation of the rotating ring;w 2-reverse rotation of the rotating ring;
1-sealing the cavity; 2, a shell; 3, a movable ring; 31-a helical groove; 32, sealing the weir; 33-sealing the dam; 34-collecting ring groove; 35-drainage channel; 36-convex; 37-concave surface; 4-stationary ring; 41-a conical surface; 5, O-shaped rings for the stationary rings; 6, an anti-rotation pin; 7-a spring; 8, shaft sleeve; 9, 12-set screw; 10-axis; 11-O-shaped ring for moving ring; 13-stationary ring seat.
Detailed Description
Embodiments of the present technology are described in detail below with reference to the drawings and examples.
Example 1
Fig. 1-3 illustrate a bidirectional rotary self-pumping hydrodynamic mechanical seal with a collecting ring groove and a drainage channel on a moving ring, which is arranged between a housing 2 of mechanical equipment and a rotating shaft 10 or a shaft sleeve 8 and consists of the moving ring 3, an O-ring 11 for the moving ring, a stationary ring 4, an O-ring 5 for the stationary ring, a spring 7 and a stationary ring seat 13; the sleeve 8 is fixed to the rotary shaft 10 by a set screw 9. The movable ring 3 is fixed on the shaft sleeve 8 through a set screw 12, and an O-shaped ring 11 for the movable ring is arranged between the movable ring 3 and the shaft sleeve 8. The static ring 4 is arranged on the static ring seat 13, and the static ring and the inner hole of the static ring seat are sealed by adopting an O-shaped ring 5 for the static ring. One end of the anti-rotation pin 6 is arranged on the static ring seat, the other end of the anti-rotation pin extends into a guide groove formed in the static ring along the axial direction, and the anti-rotation pin 6 can prevent the static ring from rotating and can guide the static ring to move axially at the same time. The spring 7 is arranged between the static ring and the static ring seat, and pushes the static ring to move along the axial direction in a normal state so as to enable the static ring to be in close contact with the dynamic ring. And an O-shaped ring is adopted for sealing between the shell 2 and the static ring seat 13.
The end face of the moving ring comprises three parts, namely a spiral groove, a sealing weir and a sealing dam, 12 spiral grooves 31 are uniformly distributed on the outer diameter side of the end face of the moving ring, the inner diameter side of the end face of the moving ring is provided with the sealing dam 33, and the sealing surface between the spiral grooves 31 is provided with the sealing weir 32; meanwhile, a collecting ring groove 34 is processed on the end face of the movable ring and connected to the root of each spiral groove; the movable ring is internally provided with 6 drainage pore channels 35 which are uniformly distributed along the circumferential direction to communicate the collecting ring groove with the sealing cavity. The outer diameter side of the end surface of the stationary ring is processed into a tapered surface 41. The inner radius R3 of the collecting ring groove is equal to the root radius Rg of the spiral groove, the radius Rt of the small end of the conical surface is slightly larger than the outer radius R4= R3+2Rk of the collecting ring groove, and Rk is the radius of the drainage duct 35. The root of the spiral groove 31 is communicated with the sealing cavity 1 through a collecting ring groove 34 on the end surface of the movable ring 3 and a drainage hole passage 35 in the movable ring.
In the forward rotation, such a self-pumping hydrodynamic mechanical seal generates hydrodynamic pressure in a fluid pumping manner, and the fluid flow state thereof is as shown in fig. 7. The moving ring rotates in the positive direction, so that media from the sealing cavity 1, a drainage hole channel 35 communicated with the sealing cavity 1 through the moving ring 3 and a collecting ring groove are fully distributed with the spiral groove 31, the media are accelerated by a convex surface 36 of the spiral groove 31 to form high-speed fluid, the high-speed fluid flows to the outer diameter side of the moving ring 3 along a concave surface 37 under the action of centrifugal force and is pumped out to the sealing cavity 1, a low-pressure area is formed at the root of the spiral groove 31 at the moment, the media in the sealing cavity 1 flow into the root of the spiral groove 31 through the drainage hole channel 35 communicated with the sealing cavity 1 and the collecting ring groove on the moving ring 3 again under the action of pressure difference, and the primary positive self. In the running process of the rotating ring, the medium passing through the spiral groove 31 is acted by centrifugal force to generate flow far away from the sealing dam, so that solid particles existing in self-pumping fluid cannot enter the area of the sealing dam 33, and abrasive wear of the end face of the sealing dam is avoided.
When rotating in the reverse direction, such a self-pumping hydrodynamic type mechanical seal generates hydrodynamic pressure in a fluid pumping manner, and the fluid flow state thereof is as shown in fig. 8. The rotating ring rotates reversely, so that the medium in the sealing cavity 1 is wedged along the concave surface 37 of the spiral groove 31 and flows to the inner diameter side of the rotating ring 3 to be pumped into the root part of the spiral groove 31; due to the reduction of the rotating radius, the linear velocity of the fluid at the root of the spiral groove 31 is reduced, part of the kinetic energy is converted into pressure energy and is changed into high-pressure fluid, and the high-pressure fluid flows into the sealing cavity 1 again through the flow collecting ring groove on the movable ring 3 and the drainage pore channel 35 communicated with the sealing cavity 1 under the action of pressure difference, so that the one-time reverse self-pumping circulation is formed.
In the process of the reverse rotation of the moving ring, on one hand, a medium in the sealing cavity 1 is wedged into the spiral groove along the concave surface 37 of the spiral groove 31, and flows to the root of the spiral groove in a direction parallel to the bottom surface of the spiral groove and the sealing dam, on the other hand, fluid in the spiral groove is wedged into the concave surface 37 of the spiral groove 31, when the fluid flows in the spiral groove, the medium between the plane of the moving ring sealing weir and the conical surface of the stationary ring is driven to flow through the small end of the conical surface of the stationary ring in a flow velocity direction forming a certain angle with the sealing dam and enters the flow collecting ring groove on the moving ring through the action of the radial component force of viscous shearing force, and flows to the flow guide pore passage 35 on the moving ring 3 and communicated with the sealing cavity 1 to flow into the sealing cavity 1 again without directly.
The self-pumping circulation realizes self-lubrication of mechanical seal on one hand; on the other hand, the fluid is continuously circulated between the sealing surfaces, so that the frictional heat between the sealing surfaces is taken away in time, and the self-flushing of the sealing is realized.
Example 2
The bidirectional rotary self-pumping hydrodynamic mechanical seal with the collecting ring groove and the drainage hole on the static ring shown in fig. 4-6 is arranged between a shell 2 of a machine and a rotating shaft 10 or a shaft sleeve 8, and comprises a dynamic ring 3, an O-shaped ring 11 for the dynamic ring, a static ring 4, an O-shaped ring 5 for the static ring, a spring 7, a static ring seat 13 and the like. The sleeve 8 is fixed to the rotary shaft 10 by a set screw 9. The movable ring 3 is fixed on the shaft sleeve 8 through a set screw 12, and an O-shaped ring 11 for the movable ring is arranged between the movable ring 3 and the shaft sleeve 8. The stationary ring 4 is arranged on the stationary ring seat 13, and an O-shaped ring 5 for the stationary ring is arranged between the stationary ring and an inner hole of the stationary ring seat. One end of the anti-rotation pin 6 is arranged on the static ring seat, the other end of the anti-rotation pin extends into a guide groove formed in the static ring along the axial direction, and the anti-rotation pin 6 can prevent the static ring from rotating and can guide the static ring to move axially at the same time. The spring 7 is arranged between the static ring and the static ring seat, and pushes the static ring to move along the axial direction in a normal state so as to enable the static ring to be in close contact with the dynamic ring. And an O-shaped ring is adopted for sealing between the shell 2 and the static ring seat 13.
12 groups of spiral grooves 31 are formed in the outer side of the end face of the movable ring 3, the inner side of the end face of the movable ring 3 is provided with a sealing dam 33, and a sealing surface between the spiral grooves 31 is a sealing weir;
a collecting ring groove 34 and a conical surface 41 are machined on the end face of the stationary ring, the conical surface 41 is located on the outer diameter side of the end face of the stationary ring, and the collecting ring groove 34 is located on the inner diameter side of the end face of the stationary ring. The inner edge of the static ring is evenly distributed with 6 drainage pore channels 35 which connect the collecting ring groove and the sealing cavity. The root of the spiral groove 31 is communicated with the sealing cavity 1 through a collecting ring groove on the end surface of the static ring 4 and a drainage pore passage 35 in the static ring. The inner radius R3 of the collecting ring groove is slightly smaller than the root radius Rg of the spiral groove, the outer radius R4= R3+2Rk of the collecting ring groove, the radius Rt of the small end of the conical surface is slightly larger than the outer radius R4 of the collecting ring groove, and Rk is the radius of the drainage channel 35.
In the forward rotation, such a self-pumping hydrodynamic mechanical seal generates hydrodynamic pressure in a fluid pumping manner, and the fluid flow state thereof is as shown in fig. 9. The moving ring rotates in the positive direction, so that a medium which comes from the sealing cavity 1 and passes through the drainage hole channel 35 and the flow collecting ring groove and is fully distributed in the spiral groove 31 is accelerated to be high-speed fluid by the convex surface 36 of the spiral groove 31, the high-speed fluid flows to the outer diameter side of the moving ring 3 along the concave surface 37 under the action of centrifugal force and is pumped out to the sealing cavity 1, at the moment, a low-pressure area is formed at the root of the spiral groove 31, the medium in the sealing cavity 1 flows into the root of the spiral groove 31 through the drainage hole channel 35 and the flow collecting ring groove again under the action of pressure difference, and the. In the running process of the rotating ring, the medium passing through the spiral groove 31 is acted by centrifugal force to generate flow far away from the sealing dam, so that solid particles existing in self-pumping fluid cannot enter the area of the sealing dam 33, and abrasive wear of the end face of the sealing dam is avoided.
When rotating in the reverse direction, such a self-pumping hydrodynamic type mechanical seal generates hydrodynamic pressure in a fluid pumping manner, and the fluid flow state thereof is as shown in fig. 10. The rotating ring rotates reversely, so that the medium in the sealing cavity 1 is wedged along the concave surface 37 of the spiral groove 31 and flows to the inner diameter side of the rotating ring 3 to be pumped into the root part of the spiral groove 31; due to the reduction of the rotating radius, the linear velocity of the fluid at the root of the spiral groove 31 is reduced, part of the kinetic energy is converted into pressure energy and is changed into high-pressure fluid, and the high-pressure fluid flows into the sealing cavity 1 again through the flow collecting ring groove on the static ring 4 and the drainage pore passage 35 communicated with the sealing cavity 1 under the action of pressure difference, so that the one-time reverse self-pumping circulation is formed.
In the process of the reverse rotation of the moving ring, a medium in the sealing cavity 1 is wedged into a spiral groove along the concave surface 37 of the spiral groove 31 on one hand, and flows to the root of the spiral groove in a direction parallel to the bottom surface of the spiral groove and the sealing dam, on the other hand, a fluid in the spiral groove is wedged into the concave surface 37 of the spiral groove 31, when the fluid flows in the spiral groove, the medium between the plane of the moving ring sealing weir and the conical surface of the static ring is driven to flow through the small end of the conical surface of the static ring in a flow velocity direction forming a certain angle with the sealing dam and enter a flow collecting ring groove on the static ring through the action of the radial component of viscous shearing force, and flows to the drainage pore passage 35 on the static ring 3 and communicated with the sealing cavity 1 to flow into the sealing cavity 1 again without directly flowing to.
The self-pumping circulation realizes self-lubrication of mechanical seal on one hand; on the other hand, the fluid is continuously circulated between the sealing surfaces, so that the frictional heat between the sealing surfaces is taken away in time, and the self-flushing of the sealing is realized.
Claims (4)
1. A bidirectional rotation automatic pumping fluid dynamic pressure type mechanical seal is arranged between a shell (2) and a rotating shaft (10) of mechanical equipment and consists of a moving ring (3), O-shaped rings (11) for the moving ring, a static ring (4), O-shaped rings (5) for the static ring, a spring (7) and a static ring seat (13), wherein the end surface of the moving ring comprises three parts, namely spiral grooves, sealing weirs and sealing dams, the number of the spiral grooves (31) is not less than 3, the spiral grooves are uniformly distributed on the outer diameter side of the end surface of the moving ring, the inner diameter side of the end surface of the moving ring is provided with the sealing dams 33, and sealing surfaces among the spiral grooves (31) are provided; the outer diameter side of the end surface of the static ring is processed into a conical surface (41), and simultaneously a collecting ring groove (34) communicated with the root of each spiral groove is processed on the end surface of the dynamic ring or the static ring; set up drainage pore (35) that connect collecting ring groove (34) and sealed chamber (1) on rotating ring (3) or stationary ring (4), characterized by:
fluid dynamic pressure in different rotating directions is generated by adopting a fluid pumping-out and fluid pumping-in mode;
the fluid is pumped out, namely when the moving ring rotates in the forward direction, the medium which comes from the sealing cavity (1) and is fully distributed in the spiral groove (31) through the drainage hole channel (35) is accelerated to be high-speed fluid by the convex surface (36) of the spiral groove (31), the high-speed fluid flows to the outer diameter side of the moving ring (3) along the concave surface (37) under the action of centrifugal force and is pumped out to the sealing cavity (1), at the moment, the root of the spiral groove (31) forms a low-pressure area, and the medium in the sealing cavity (1) flows into the root of the spiral groove (31) through the drainage hole channel (35) again under the action of differential pressure to form primary forward self-pumping circulation;
The fluid is pumped, namely when the rotating ring rotates reversely, a medium in the sealing cavity (1) is wedged along the concave surface (37) of the spiral groove (31) and flows to the inner diameter side of the rotating ring (3) to be pumped to the root of the spiral groove (31), the linear velocity of the fluid at the root of the spiral groove (31) is reduced due to the reduction of the rotating radius, part of kinetic energy of the fluid is converted into pressure energy and becomes high-pressure fluid, and the high-pressure fluid flows into the sealing cavity (1) again through the drainage hole channel (35) under the action of pressure difference to form primary and secondary reverse self-pumping circulation.
2. The bidirectional rotary self-pumping hydrodynamic mechanical seal of claim 1, wherein: the diameter of the small end of the conical surface (41) positioned on the outer side of the end surface of the static ring (4) is larger than the outer diameter of the collecting ring groove (34).
3. The bidirectional rotary self-pumping hydrodynamic mechanical seal of claim 1, wherein: the collecting ring groove is positioned on the end face of the movable ring, the outer diameter of the collecting ring groove is larger than the diameter of the root circle of the spiral groove, and the inner diameter of the collecting ring groove is equal to the diameter of the root circle of the spiral groove.
4. The bidirectional rotary self-pumping hydrodynamic mechanical seal of claim 1, wherein: the collecting ring groove (34) is positioned on the end face of the static ring, the outer diameter of the collecting ring groove is larger than the diameter of the root circle of the spiral groove, and the inner diameter of the collecting ring groove is smaller than or equal to the diameter of the root circle of the spiral groove.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521134635.7U CN205618672U (en) | 2015-12-30 | 2015-12-30 | Two -way rotation is from pump sending fluid dynamic pressure type mechanical seal |
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| CN201521134635.7U CN205618672U (en) | 2015-12-30 | 2015-12-30 | Two -way rotation is from pump sending fluid dynamic pressure type mechanical seal |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465371A (en) * | 2015-12-30 | 2016-04-06 | 南京林业大学 | Bidirectional-rotation self-pumping fluid dynamic pressure type mechanical seal |
| CN110685954A (en) * | 2019-11-19 | 2020-01-14 | 潍柴动力股份有限公司 | Sealing structure and water pump |
-
2015
- 2015-12-30 CN CN201521134635.7U patent/CN205618672U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465371A (en) * | 2015-12-30 | 2016-04-06 | 南京林业大学 | Bidirectional-rotation self-pumping fluid dynamic pressure type mechanical seal |
| CN110685954A (en) * | 2019-11-19 | 2020-01-14 | 潍柴动力股份有限公司 | Sealing structure and water pump |
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