WO2016155221A1 - 封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统 - Google Patents

封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统 Download PDF

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Publication number
WO2016155221A1
WO2016155221A1 PCT/CN2015/088360 CN2015088360W WO2016155221A1 WO 2016155221 A1 WO2016155221 A1 WO 2016155221A1 CN 2015088360 W CN2015088360 W CN 2015088360W WO 2016155221 A1 WO2016155221 A1 WO 2016155221A1
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WO
WIPO (PCT)
Prior art keywords
ring
sleeve
pumping
passage
side plate
Prior art date
Application number
PCT/CN2015/088360
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English (en)
French (fr)
Inventor
邢宇
邢天宜
Original Assignee
邢宇
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Publication date
Application filed by 邢宇 filed Critical 邢宇
Publication of WO2016155221A1 publication Critical patent/WO2016155221A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid pumps

Definitions

  • the invention relates to a shaft seal flushing system for a centrifugal pump.
  • a shaft seal flushing system for a centrifugal pump.
  • it relates to a closed mechanical seal pumping ring and a shaft seal flushing system having the pumping ring.
  • FIG. 1 The circulating power of the internal liquid in the standard seal flushing schedules 52, 53A, 53B, 53C of the API 682 standard appendix D of the centrifugal pump and rotor pump shaft seal system is provided by a pumping effect ring, as in the prior art shown in FIG. 1, 2, and 3 show a prior art 2CW-CW buffered double-contact wet seal with buffer and 3CW-FB flushing system with a double-contact wet seal in a back-facing configuration with a barrier liquid And internal structure diagram.
  • Figure 4 is a schematic view showing the flushing system and internal structure of a conventional double-contact wet seal (1.2 in API 682) in a back-to-back configuration of a prior art 3CW-BB with a barrier fluid.
  • the pumping effect ring always moves together with the pump shaft for uniform speed.
  • the short teeth are made on the largest outer surface of the pumping ring. Because the tooth shape is short, all the liquid contained in the short teeth is almost in the same equipotential surface.
  • the uniform speed of the circular motion that is to say, once the liquid enters the short tooth, no matter how long the liquid stays in the short tooth, there is no increase in the speed: the liquid velocity of the position a and the position b
  • the size is the same, in other words, the pumping effect ring at this time does not accelerate.
  • This small stream of liquid needs to overcome the effects of various resistances such as liquid viscosity, static components, friction, along the path, corners, throttling, backflow, eddy currents, etc., so that the head is reduced or even stopped.
  • the maximum outer diameter of the rotating pumping ring should be as close as possible to the inner wall of the stationary cavity, and the result is that the liquid between the moving part and the stationary part. Withstands great shear forces, not only consumes power, generates excess heat, but even destroys the molecular structure of the liquid and affects the physical and chemical stability of the liquid.
  • the fluid passage is open so that the direction of the flow is random and causes turbulence, so that most of the liquid flows slowly or even stationary.
  • the technical problem to be solved by the present invention is to provide a closed mechanical seal pumping ring having a closed passage and capable of providing a reliable and stable head and flow fluid, and a shaft seal flushing system having the pumping ring.
  • a closed mechanical seal pump effect ring comprising a left side plate of the annular pumping ring arranged in parallel with each other and a right side plate of the pumping ring, the left side plate of the pumping effect ring and the right side plate of the pumping ring
  • the inner ring is sleeved on the outer circumferential surface of the sleeve of the centrifugal pump, and the outer periphery of the left side plate of the pumping effect ring and the right side plate of the pumping effect ring are connected with the sealing gland of the centrifugal pump and there is a gap
  • the left side of the pumping ring a plurality of blades disposed in a rotating radiation state between the plate and the right side plate of the pumping effect ring, and wherein the plurality of blades are disposed perpendicular to the left side plate and the right side plate, the radiating state
  • the port formed by the closing end of the plurality of blades corresponds to the liquid outlet of the
  • the outer side surface of the right side plate of the pumping ring is outwardly protruded from the sleeve, and a guide sleeve coaxial with the sleeve is integrally formed on the right side plate of the pumping ring and located at the outer side of the pumping ring An auxiliary liquid inlet is opened between the guide sleeve and the sleeve.
  • the left side plate of the pumping effect ring and the outer side surface of the right side plate of the pumping ring are integrally formed with a guide sleeve coaxial with the sleeve.
  • a shaft seal flushing system with a closed mechanical seal pumping effect ring includes a bushing sleeved on a pump shaft, and a pump casing sleeved on the outside of the pump shaft and the sleeve from the medium end to the atmospheric end a sealing gland and a second sealing gland, wherein the medium end sealing moving ring between the pump casing and the sleeve disposed from the media end to the atmospheric end is located at the first sealing gland and the bushing a medium end seal static ring between and in contact with the medium end seal moving ring, an atmospheric end seal moving ring between the second seal gland and the sleeve, and the second seal pressure An atmospheric end sealing static ring between the cover and the sleeve, a pumping ring between the second sealing gland and the sleeve, and at the end of the atmospheric end sealing ring away from the atmospheric end sealing static ring, Forming a heat between the first sealing gland, the medium end sealing ring, the medium end sealing ring, the bushing,
  • the cooling liquid circulation passage includes a first passage formed in the first sealing gland and an upper port connected to the heat outlet port of the heat exchanger through an external pipe, formed in the First sealing gland and media end a second passage between the stationary ring and the sleeve, formed in the sleeve and corresponding to the medium end sealing the moving ring and the third passage of the pump shaft, formed on the outer circumference of the pump shaft a fourth passage between the face and the inner circumferential surface of the sleeve, a fifth passage formed in the sleeve, a sixth passage formed in the pumping ring, formed in the second
  • the gland is sealed and the upper port is connected to the seventh passage of the heat exchanger inlet through an external line.
  • the cooling liquid circulation passage includes a first passage formed in the first sealing gland and an upper port connected to the heat outlet port of the heat exchanger through an external pipe, formed in the a first passage between the first sealing gland and the medium end seal static ring and the sleeve, forming a third passage in the sleeve and corresponding to the medium end sealing the moving ring and the pump shaft Forming a fourth passage between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve, forming a fifth passage in the sleeve, forming a sixth in the pumping ring a passage formed in the second sealing gland and the upper port is connected to the seventh passage of the heat exchanger inlet through an external pipe, and is further provided in sequence to be connected: formed in the pump effect ring Forming an eighth passage between the second sealing glands and the liquid inlet communicating with the liquid outlet end of the sixth passage in the pumping ring, formed between the pumping ring and the second sealing gland and The ninth channel perpendicular to the eighth channel is
  • the fourth passage formed between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve is a medium end seal formed between an outer circumferential surface of the pump shaft and an inner circumferential surface of the sleeve And a groove on the inner side wall of the sleeve between the atmospheric end seal, the medium end seal and the atmospheric end seal are respectively embedded on the inner circumferential surface of the sleeve.
  • the pumping effect ring comprises an annular pumping ring left side plate and a pumping effect ring right side plate which are arranged in parallel with each other, and the inner ring of the left side plate of the pumping effect ring and the right side plate of the pumping effect ring is sleeved on the outer circumferential surface of the sleeve of the centrifugal pump
  • the left outer plate of the pumping effect ring and the outer periphery of the right side plate of the pumping ring are connected with the second sealing gland of the centrifugal pump and have a gap, and there is a gap between the left side plate of the pumping effect ring and the right side plate of the pumping ring a plurality of blades disposed in a rotating radiation state, and wherein the plurality of blades are disposed perpendicular to the left side plate and the right side plate, and the plurality of blades in the radiating state are adjacent to the closing end of the shaft center
  • the port corresponds to a liquid outlet of a
  • the pumping effect ring comprises an annular pumping ring left side plate and a pumping effect ring right side plate which are arranged in parallel with each other, and the inner ring of the left side plate of the pumping effect ring and the right side plate of the pumping effect ring is sleeved on the outer circumferential surface of the sleeve of the centrifugal pump
  • the left outer plate of the pumping effect ring and the outer periphery of the right side plate of the pumping ring are connected with the second sealing gland of the centrifugal pump and have a gap, and there is a gap between the left side plate of the pumping effect ring and the right side plate of the pumping ring a plurality of blades disposed in a rotating radiation state, and wherein the plurality of blades are disposed perpendicular to the left side plate and the right side plate, and the plurality of blades in the radiating state are adjacent to the closing end of the shaft center
  • the port corresponds to a liquid outlet of a
  • a shaft seal flushing system with a closed mechanical seal pumping effect ring includes a bushing sleeved on a pump shaft, and a pump casing sleeved on the outside of the pump shaft and the sleeve from the medium end to the atmospheric end a sealing gland and a second sealing gland, the medium end sealing static ring between the first sealing gland and the sleeve disposed from the media end to the atmospheric end, located at the first sealing gland and the a media end sealing moving ring between the bushings and in contact with the medium end sealing static ring, an atmospheric end sealing moving ring between the second sealing gland and the bushing, and a second sealing gland An atmospheric end seal static ring connected to the bushing and in contact with the atmospheric end seal moving ring, further provided with a pump effect ring, wherein the pump effect ring is respectively located at the first seal gland and the media end seal Between the moving rings, between the second sealing gland and the sleeve, and between the second sealing gland and the atmospheric end sealing ring, sealing at the
  • the cooling liquid circulation passage includes a first passage formed in the first sealing gland and an upper port connected to the heat outlet port of the heat exchanger through a first external pipe, formed in the first passage a second passage between the first sealing gland and the pumping ring, forming a third passage between the first sealing gland, the medium end sealing static ring and the pumping ring, formed in the a fourth passage between the pumping effect ring and the medium end sealing moving ring, formed between the pumping effect ring and the medium end sealing moving ring and a fifth passage in the sleeve, formed in the bushing and a sixth passage between the pump shafts, a seventh passage formed in the sleeve, an eighth passage formed in the pump effect ring, and a ninth passage formed in the second seal gland,
  • the liquid outlet of the ninth passage is connected to the liquid inlet of the heat exchanger through a second external pipeline, and is further connected to be connected in sequence: the fluid outlet of the heat exchanger is connected through a third external pipeline Forming a tenth passage in the second
  • the sixth passage formed between the outer peripheral surface of the pump shaft and the inner circumferential surface of the sleeve is a medium end seal formed between an outer circumferential surface of the pump shaft and an inner circumferential surface of the sleeve And a groove on the inner side wall of the sleeve between the atmospheric end seal, the medium end seal and the atmospheric end seal are respectively embedded on the inner circumferential surface of the sleeve.
  • the pumping effect ring comprises an annular pumping ring left side plate and a pumping effect ring right side plate which are arranged in parallel with each other, and the inner ring of the left side plate of the pumping effect ring and the right side plate of the pumping effect ring is sleeved on the outer circumferential surface of the sleeve of the centrifugal pump
  • the left outer plate of the pumping effect ring and the outer periphery of the right side plate of the pumping ring are connected with the second sealing gland and have a gap, and the left side plate of the pumping effect ring and the right side plate of the pumping ring are rotated.
  • the ports formed by the closing ends of the plurality of blades in the radiating state correspond to the shaft a liquid outlet of the sleeve
  • the port formed by the radiation end edge of the plurality of blades in the radial state corresponds to the liquid inlet of the ninth passage formed on the second sealing gland
  • the left side plate of the pumping effect ring and the pumping effect An outer end surface of the right side plate of the ring adjacent to the sleeve is integrally formed with a medium end guide sleeve and an atmospheric end guide sleeve coaxial with the sleeve, and the second passage is formed in the outer side.
  • the fourth channel is formed in the dielectric sleeve and said end flow medium end
  • the eleventh passage is formed between the second sealing gland and the atmospheric end diversion sleeve
  • the thirteenth passage is formed at the atmospheric end diversion The sleeve is sealed between the moving end ring and the atmospheric end.
  • the closed mechanical seal pumping ring of the invention and the shaft seal flushing system with the pumping effect ring, the pumping effect ring can not only provide stable acceleration to the fluid, but also increase the distance of the liquid acceleration, and make the fluid flow speed directional to reduce the useless work. . It not only allows most of the liquid in the sealed chamber to participate in the flow, but also lengthens the fluid flow path and increases the flow area.
  • the pump effect ring rotates synchronously with the pump shaft, and the fluid moves from the axial center of the pump shaft to the edge of the pump efficiency ring. During this process, the linear velocity of the fluid micelle becomes larger and larger, and the edge speed of the pump effect ring is the largest. During this time, the fluid micelles are always in an accelerated state, and the maximum lift is obtained when the pumping ring is released.
  • the pumping effect ring has a plurality of closed passages from the axial center to the outer edge, and the fluid carried in a unit time is large, so the flow rate is increased.
  • the path through which the fluid micelles travel is long from the moment the fluid micelles enter the sealed chamber until the moment they leave the sealed chamber. Most of the liquid in the sealed chamber is in the vicinity of the path through which the fluid micelles travel, especially in the vicinity of the heat source of the mechanical seal friction pair.
  • the gap between the rotating component and the stationary component in the sealed cavity is large due to the small possibility of reflow, and the surface of the pumping ring contacting the fluid is smooth, so the liquid in the gap is affected by The shear force is relatively small, so that the useless work is reduced, and thus less heat is generated. It is not destructive to the structure of liquid molecules and is therefore beneficial to both physical and chemical stability of liquids.
  • Changing the diameter of the pumping effect ring can change the linear velocity at the outer edge of the pumping effect ring, which means that the pressure difference of the fluid flow can be changed.
  • Changing the thickness of the pumping effect ring can change the cross-sectional area of the flow passage in the pumping effect ring and the volume of the liquid contained in the pumping effect ring, that is, the fluid flow rate can be changed, so that the heat balance can be effectively and actively controlled.
  • the precision of the gap between the rotating and stationary components is low, so that the manufacturing and assembly costs can be tolerated and the wear caused by the larger operation can be tolerated and the service life can be prolonged.
  • a new auxiliary bypass flow path can be opened in the sealed chamber by adding an auxiliary suction hole to the pump effect ring.
  • a diversion sleeve can be added to the pumping effect ring to adjust the path of the flow path in the sealed chamber according to the set requirements.
  • Direction and path length directly flush the coolant to the atmospheric mechanical seal friction pair, as shown in Figure 10, Figure 11, Figure 12, Figure 13, and Figure 14.
  • the 3CW-BB can be improved in the back-to-back configuration with the barrier fluid.
  • the double-contact wet seal is assembled, as shown in Figure 15, Figure 16, Figure 17, and Figure 18.
  • FIG. 1 is a schematic structural view of a shaft seal flushing system of a prior art centrifugal pump
  • Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
  • Figure 3 is a cross-sectional view taken along line B-B of Figure 1;
  • FIG. 4 is a schematic structural view of another example of a shaft seal flushing system of a prior art centrifugal pump
  • Figure 5 is a schematic structural view of a first embodiment of a shaft seal flushing system of a centrifugal pump of the present invention
  • Figure 6 is a cross-sectional view taken along line A-A of Figure 5;
  • Figure 7 is a cross-sectional view taken along line B-B of Figure 5;
  • Figure 8 is a cross-sectional view taken along line C-C of Figure 5;
  • Figure 9 is a cross-sectional view taken along line A-A of Figure 8.
  • Figure 10 is a schematic view showing the structure of a second embodiment of the shaft seal flushing system of the centrifugal pump of the present invention.
  • Figure 11 is a cross-sectional view taken along line A-A of Figure 10;
  • Figure 12 is a cross-sectional view taken along line B-B of Figure 10;
  • Figure 13 is a cross-sectional view taken along line C-C of Figure 10;
  • Figure 14 is a cross-sectional view taken along line A-A of Figure 13;
  • Figure 15 is a schematic view showing the structure of a third embodiment of the shaft seal flushing system of the centrifugal pump of the present invention.
  • Figure 16 is a cross-sectional view taken along line B-B of Figure 15;
  • Figure 17 is a cross-sectional view taken along line C-C of Figure 15;
  • Fig. 18 is a cross-sectional view taken along line A-A of Fig. 17;
  • pump shaft 2 media end seal
  • pump effect ring 701 pump effect ring left side plate
  • Atmospheric end seal moving ring 11 Atmospheric end seal static ring
  • Blade 1704 Media end diversion sleeve
  • Atmospheric end diversion sleeve 18 First external conduit
  • the enclosed mechanical seal pumping ring of the present invention and the shaft seal flushing system having the pumping effect ring firstly have a pumping ring having a closed passage and capable of providing a reliable and stable head and flow fluid, the pumping ring not only providing stable acceleration to the fluid Moreover, the distance for accelerating the liquid is increased, and the directionality of the fluid flow velocity is made strong to reduce the useless work. It not only allows most of the liquid in the sealed chamber to participate in the flow, but also lengthens the fluid flow path and increases the flow area.
  • the closed mechanical seal pumping ring of the present invention comprises an annular pumping effect ring left side plate 701 and a pumping effect ring right side plate 702 arranged in parallel with each other.
  • the inner ring of the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring are sleeved on the outer circumferential surface of the sleeve 12 of the centrifugal pump, and the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring
  • the outer periphery is engaged with the sealing gland of the centrifugal pump and has a gap.
  • the plurality of blades 703 are arranged in a rotating radiation state between the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring, and The plurality of blades 703 are disposed perpendicular to the left side plate 701 and the right side plate 702, and the ports formed by the plurality of blades 703 in the radial state close to the closing end of the shaft center correspond to the outlet of the sleeve 12.
  • the liquid port, the edge radial end of the plurality of blades 703 in the radial state constitutes a port axial position corresponding to the liquid outlet of the liquid outlet passage formed on the sealing gland, and is also a liquid inlet of the heat exchanger 16.
  • the outer side surface of the right side plate 702 of the pumping ring is integrally formed with the sleeve 12 and is coaxial with the sleeve 12.
  • the guide sleeve 704 has an auxiliary liquid inlet 705 between the guide sleeve 704 and the sleeve 12 on the right side plate 702 of the pumping ring.
  • the outer side surface of the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring are formed integrally with each other adjacent to the sleeve 12 .
  • the closed mechanical seal pumping ring of the present invention as described above, the fluid moves from the position near the axial center of the pump shaft to the edge of the pumping ring driven by the high speed rotation of the pumping ring, and the line of the fluid micelles in the process The speed is getting bigger and bigger, and the edge speed of the pumping ring is the largest. During this period, the fluid micelles are always in an accelerated state, and the maximum lift is obtained when the pumping ring is released.
  • the pumping effect ring has a plurality of closed passages from the axial center to the outer edge, and the fluid carried in a unit time is large, so the flow rate is increased.
  • the shaft seal flushing system with the closed mechanical seal pump effect ring of the present invention comprises a sleeve 12 sleeved on the pump shaft 1, and the medium end a pump casing 3, a first sealing gland 5 and a second sealing gland 8 which are respectively connected to the outside of the pump shaft 1 and the sleeve 12 to the atmospheric end, and are disposed in sequence from the medium end to the atmospheric end.
  • a medium end sealing ring 4 between the shell 3 and the sleeve 12 a medium end seal located between the first sealing gland 5 and the sleeve 12 and in contact with the medium end sealing ring 4 a static ring 6, an atmospheric end sealing ring 10 between the second sealing gland 8 and the sleeve 12, and an atmospheric end seal between the second sealing gland 8 and the sleeve 12 a static ring 11, a pumping ring 7 between the second sealing gland 8 and the sleeve 12 and at the end of the atmospheric end sealing ring 10 away from the atmospheric end sealing static ring 11, at the first
  • a sealing gland 5, a medium end sealing static ring 6, a medium end sealing moving ring 4, a bushing 12, a pump shaft 1, a pumping ring 7 and a second sealing gland 8 are formed through an external portion.
  • the line 13 is connected to the heat exchanger 16 located outside and is capable of causing the heat exchange liquid to flow in the axial direction of the rotating member while flowing in the axial direction of the rotating member to form a cooling liquid circulation passage for heat exchange of the respective rotating members.
  • the cooling liquid circulation passage on the pumping effect ring 7 corresponds to a cooling liquid circulation passage formed on the second sealing gland 8.
  • the cooling liquid circulation passage includes a first passage 201 formed in the first sealing gland 5 and the upper port is connected to the liquid outlet of the heat exchanger 16 through the external conduit 13, a second passage 202 formed between the first sealing gland 5 and the medium end seal static ring 6 and the sleeve 12 is formed in the sleeve 12 and is sealed corresponding to the medium end
  • the moving ring 4 and the third passage 203 of the pump shaft 1 form a fourth passage 204 between the outer peripheral surface of the pump shaft 1 and the inner circumferential surface of the sleeve 12, and is formed in the sleeve 12 a fifth passage 205, a sixth passage 206 formed in the pumping ring 7, formed in the second sealing gland 8 and an upper port connected to the heat exchanger 16 through the external line 12
  • the seventh channel 207 is formed in the first sealing gland 5 and the upper port is connected to the liquid outlet of the heat exchanger 16 through the external conduit 13
  • the cooling liquid circulation passages are connected in sequence: formed on the first sealing gland 5 and the upper ports are connected through the external piping 13.
  • a first passage 201 of the liquid outlet of the heat exchanger 16 is formed at a second pass between the first sealing gland 5 and the medium end seal static ring 6 and the sleeve 12 a passage 202, a third passage 203 formed in the sleeve 12 and corresponding to the medium end sealing ring 4 and the pump shaft 1, formed on the outer peripheral surface of the pump shaft 1 and the sleeve 12 a fourth passage 204 between the inner peripheral faces, a fifth passage 205 formed in the sleeve 12, a sixth passage 206 formed in the pumping ring 7, formed in the second sealing pressure a cover 8 and an upper port connected to the seventh passage 207 of the inlet port of the heat exchanger 16 through an external line 12, and also provided in sequence to communicate with each other: the pumping effect ring 7 and the second seal are formed
  • the fourth passage 204 formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 12 is formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 12.
  • a groove on the inner side wall of the sleeve 12 between the medium end seal 2 and the atmospheric end seal 9, the medium end seal 14 and the atmospheric end seal 15 are respectively embedded in the inner circumference of the sleeve 12 On the surface.
  • the pumping effect ring 7 includes an annular pumping ring left side plate 701 and a pumping effect ring right side plate 702 which are disposed in parallel with each other, and the pumping effect ring left
  • the inner ring of the side plate 701 and the pumping ring right side plate 702 is sleeved on the outer circumferential surface of the sleeve 12 of the centrifugal pump, and the outer periphery of the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring and the second seal of the centrifugal pump
  • the gland 8 is engaged with a gap, and between the pumping ring left side plate 701 and the pumping ring right side plate 702, there are a plurality of blades 703 arranged in a rotating radiation state, and the plurality of blades 703 are Arranged perpendicularly to the left side plate 701 and the right side plate 702, the port formed by the pluralit
  • the pumping effect ring 7 includes an annular pumping ring left side plate 701 and a pumping effect ring right side plate 702 disposed in parallel with each other, and the pumping effect ring left side plate 701.
  • the inner ring of the right side plate 702 of the pumping ring is sleeved on the outer circumferential surface of the sleeve 12 of the centrifugal pump, and the outer periphery of the left side plate 701 of the pumping ring and the right side plate 702 of the pumping ring and the second sealing gland 8 of the centrifugal pump
  • There is a gap between the pumping ring left side plate 701 and the pumping ring right side plate 702 and there are a plurality of blades 703 arranged in a rotating radiation state, and the plurality of blades 703 and the
  • the left side plate 701 and the right side plate 702 are disposed perpendicularly, and the port formed by the plurality of blades 703 in the radiating state adjacent to the closing end of the shaft center corresponds to the discharge of the fifth passage 205 formed in the sleeve 12.
  • the port axial position of the radiation end edge of the plurality of blades 703 in the radial state corresponds to the liquid inlet of the seventh passage 207 formed in the second sealing gland 8, and is also the liquid inlet of the heat exchanger 16.
  • the outer side surface of the right side plate 702 of the pumping ring protrudes outward from the sleeve 12 Integrated with a sleeve 704 coaxial with the sleeve 12, on the right side plate 702 of the pumping ring and between the guiding sleeve 704 and the sleeve 12, an auxiliary liquid inlet 705 is opened.
  • a ten-channel 210 is formed between the second sealing gland 8 and an outer surface of the guiding sleeve 704, and a twelfth passage 212 is formed between the inner surface of the guiding sleeve 704 and the sleeve 12, and Tenth
  • the liquid outlet of the two passages 212 communicates through the auxiliary liquid inlet 705 to form a sixth passage 206 formed in the pumping effect ring 7.
  • the shaft seal flushing system of the present invention has the closed mechanical seal pumping ring according to claim 1 or 3, including a bushing sleeved on the pump shaft 1. 12.
  • the ring 6 is in contact with the connected medium end sealing ring 4
  • the atmospheric end sealing ring 10 between the second sealing gland 8 and the sleeve 12 is located between the second sealing gland 8 and the sleeve 12 .
  • the atmospheric end sealing static ring 11 which is in contact with the atmospheric end sealing ring 10 is further provided with a pumping ring 17, and the pumping ring 17 is respectively located at the first sealing gland 5 and the medium end sealing ring Between 4, between the second sealing gland 8 and the sleeve 12, and between the second sealing gland 8 and the atmospheric end sealing ring 10,
  • the first sealing gland 5, the medium end sealing ring 4, the sleeve 12, the pump shaft 1, the atmospheric end sealing ring 10, the second sealing gland 8 and the pumping ring 17 are respectively formed by external pipeline connection.
  • the heat exchanger 21 located outside and capable of causing the heat exchange liquid to flow in the axial direction of the rotating member while flowing in the axial direction of the rotating member, and a cooling liquid circulation passage capable of heat exchange of the respective rotating members, formed in the pumping effect ring
  • the cooling liquid circulation passages on the 17 respectively communicate with the cooling liquid circulation passages formed in the second sealing gland 8 and in the sleeve 12.
  • the cooling liquid circulation passage includes a first passage formed in the first sealing gland 5 and the upper port is connected to the liquid outlet of the heat exchanger 21 through the first external pipe 18 301, a second passage 302 formed between the first sealing gland 5 and the outer surface of the pumping ring 17, formed on the first sealing gland 5, the medium end sealing static ring 6 and the pumping effect
  • a third passage 303 between the end faces of the ring 17 is formed in a fourth passage 304 between the inner surface of the pumping ring 17 and the medium end sealing ring 4, and is formed in the pumping ring 17
  • a fifth passage 305 between the surface and the medium end sealing ring 4 and in the sleeve 12 forms a sixth passage 306 between the inner circumferential surface of the sleeve 12 and the outer circumferential surface of the pump shaft 1, a seventh passage 307 formed in the sleeve 12, an eighth passage 308 formed in the pumping ring 17, and a ninth passage 309 formed in the second sealing gland 8, the ninth passage
  • the sixth passage 306 formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 12 is formed between the outer circumferential surface of the pump shaft 1 and the inner circumferential surface of the sleeve 12.
  • a groove on the inner side wall of the sleeve 12 between the medium end seal 2 and the atmospheric end seal 9, the medium end seal 14 and the atmospheric end seal 15 are respectively embedded in the inner circumference of the sleeve 12 On the surface.
  • the pumping effect ring 17 includes an annular pumping effect ring left side plate 1701 and a pumping effect ring right side plate 1702 arranged in parallel with each other, and the pumping ring left side plate 1701 and the pumping ring right side plate 1702 are sleeved near the inner ring of the shaft center.
  • the outer circumference of the sleeve 12 of the centrifugal pump The outer circumference of the pumping ring left side plate 1701 and the pumping effect ring right side plate 1702 are engaged with the second sealing gland 8 and there is a gap, and the pumping ring left side plate 1701 and the pumping ring right side plate 1702 are There are a plurality of blades 1703 disposed in a rotating radiation state, and the plurality of blades 1703 are disposed perpendicular to the left side plate 1701 and the right side plate 1702, and the plurality of blades 1703 in the radial state are disposed.
  • a port formed near the closing end of the shaft corresponds to the liquid outlet of the sleeve 12, and a port formed by the radiating end edge of the plurality of blades 1703 in the radiating state corresponds to the axial position formed on the sealing gland Eight channels 308 inlet.
  • the pump effect ring left side plate 1701 and the pump effect ring right side plate 1702 are integrally formed on the outer side surface adjacent to the sleeve 12, and a media end diversion sleeve 1704 coaxial with the sleeve 12 and an atmosphere are integrally formed.
  • the end channel sleeve 1705 is formed between the first sealing gland 5 and the medium end guiding sleeve 1704, and the fourth channel 304 is formed at the medium end guide Between the flow sleeve 1704 and the medium end sealing ring 4, the eleventh passage 311 is formed between the second sealing gland 8 and the atmospheric end guiding sleeve 1705, the tenth A three-channel 313 is formed between the atmospheric end guide sleeve 1705 and the atmospheric end seal moving ring 10.
  • the closed mechanical seal pump effect ring and the shaft seal flushing system with the pump effect ring of the invention can be mentioned from the drawings: the pump shaft, the bush sleeve, the medium end mechanical seal moving ring, the atmospheric end mechanical seal movement Rings and pumping rings are all static components.
  • the rotating parts are all rotated synchronously with the pump shaft, in other words, the angular velocities of the rotating parts are equal every moment, so that the absolute value of the linear velocity near the axis is smaller, and vice versa.
  • the farther the line the greater the absolute value of the line speed.
  • the fluid micelles enter the pumping effect ring from the axial center and then are displaced in the direction of the edge of the pumping ring in the closed channel of the pumping ring. This moving process is the acceleration process.
  • the fluid micelles are The position of point a moves to the position of point b, which is the process of obtaining the head.
  • the pumping effect ring of the present invention has a plurality of closed passages working at the same time, so that the cross-sectional area of the channels they are superposed is large, and the large cross-sectional area is passed in unit time.
  • the fluid volume must be large, that is, the flow rate is large.
  • power is proportional to the product of flow and head. This is sufficient to demonstrate that the pump effect ring performance of the present invention is superior to prior art pump effect rings.

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Abstract

公开了一种封闭式机械密封泵效环，泵效环有相互平行设置的环形泵效环左侧板（701）和泵效环右侧板（702），泵效环左侧板（701）和泵效环右侧板（702）的内环套在离心泵的轴套（12）外周面上，泵效环左侧板（701）和泵效环右侧板（702）的外周边与离心泵的密封压盖相衔接并存在间隙，泵效环左侧板（701）和泵效环右侧板（702）之间有呈旋转式的放射状态设置的多个叶片（703），多个叶片（703）与泵效环左侧板（701）和泵效环右侧板（702）相垂直设置，放射状态的多个叶片（703）的收口端构成的端口对应于轴套（12）的出液口，放射状态的多个叶片（703）的放射端边缘构成的端口对应于形成在密封压盖上的出液通道的进液口。还公开了一种具有该泵效环的轴封冲洗系统。泵效环使密封腔里绝大部分液体都参与流动，增加液体加速的距离，加长流体流动路径而加大过流面积。

Description

封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统 技术领域
本发明涉及一种离心泵的轴封冲洗系统。特别是涉及一种封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统。
背景技术
在离心泵和转子泵轴封系统的API682标准附录D中标准密封冲洗计划52、53A、53B、53C内部液体的循环动力是靠泵效环提供，如图1所示的现有技术。图1、图2、图3表示现有技术2CW-CW带有缓冲液的集装双接触式湿密封和3CW-FB带有阻隔液的面向背配置中集装双接触式湿密封的冲洗系统和内部结构示意图。图4表示现有技术3CW-BB带有阻隔液的背靠背配置中集装双接触式湿密封(API682中1.2)的冲洗系统和内部结构示意图。冷却液从BI口进到密封腔以后由于泵效环与泵轴同步旋转而产生离心力或轴向力使得这部分液体获得动力从位置a移动到位置b，然后从BO口出去，并且经过外部冷却器14以后又从BI口进到密封腔，如此重复就使得冷却液循环液体流动起来达到冷却两套机械密封摩擦副的目的；由此可见，如果把上述冷却液的循环流动系统比喻成人体的血液循环系统，那么泵效环在这个系统中就相当于人的心脏，它和人体的心脏一样为整个冷却液的循环流动系统提供动力，因此泵效环性能的好坏就决定整个冷却液的循环流动系统工作效果的优劣。
现有技术中泵效环在整个冷却液的循环流动系统中的结构和工作原理。有很多缺点难以克服：
1、泵效环始终跟泵轴一起作匀速园周运动，短齿制作在泵效环的最大外圆表面，由于齿形很短所以含在短齿里的所有液体几乎处在同一等势面内作匀速园周运动，也就是说液体一旦进到短齿内，无论这部分液体在短齿内停留多长时间它的速度的大小都不会有任何增加即：位置a和位置b两点液体流速的大小相同，换句话说此时的泵效环不起加速作用。
2、因为齿短所以两齿之间液体体积小，致使流量小。
3、由于流体在密封腔内所经过的距离短，也就是说路径短，所以只有流体经过部位很小一部分液体参与流动，大部分液体始终处于静止状态，两套机械密封摩擦副是最需要得到冷却的地方，可是附近的冷却液体总是处于相对静止状态，这种状态对机械密封而言相当不利。
4、这一小股流动的液体需要克服来自于液体粘度、静止部件、摩擦、沿程、拐角、节流、回流、涡流等多种阻力的影响使得扬程变小，甚至停止不前。
5、为了产生有效的扬程、减小回流、提高驱动效率，就要将旋转着的泵效环最大外径尽可能接近静止腔体内壁，其结果就使得运动部件与静止部件之间的那部分液体承受极大的剪切力，不但消耗功率、产生多余热量，甚至破坏液体的分子结构而影响液体物理稳定性和化学稳定性。
6、由于旋转着的泵效环静止腔体内壁之间的间隙小，所以常常发生干涉而造成机械密封失效。
7、由于旋转着的泵效环静止腔体内壁之间的间隙小，所以提高了加工精度和装配精度的 要求，同时也缩短了运转磨损周期，降低了使用寿命，加大了成本。
8、因为流体在密封腔里的流动路径短、过流面积小，所以冷却效果差。
9、流体通道是开放的使得流动的方向随机而造成紊流，使得大部分液体流动缓慢甚至静止不动。
10、设计泵效环时没有成熟的流量、压力计算式，只能凭经验估计数据。
11、无法有效地通过改变泵效环的几何参数的方法来调整循环流体的流量和压力差。所以就不能主动调整热平衡。
12、转速较低的泵(n<1000rad/min时)很难达到效果。
上面所述都是离心泵的轴封冲洗系统有待解决的问题。
发明内容
本发明所要解决的技术问题是，提供一种具有封闭通道并且能提供可靠而稳定扬程和流量流体的封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统。
本发明所采用的技术方案是：一种封闭式机械密封泵效环，包括有相互平行设置的环形泵效环左侧板和泵效环右侧板，所述泵效环左侧板和泵效环右侧板的内环套在离心泵的轴套外周面上，所述泵效环左侧板和泵效环右侧板的外周边与离心泵的密封压盖相衔接并存在间隙，所述的泵效环左侧板和泵效环右侧板之间有呈旋转式的放射状态设置的多数个叶片，并且，所述的多数个叶片与所述的左侧板和右侧板相垂直设置，所述放射状态的多数个叶片的收口端构成的端口对应于所述轴套的出液口，所述放射状态的多数个叶片的放射端边缘构成的端口对应于形成在密封压盖上的出液通道的进液口。
所述的泵效环右侧板的外侧面上临近所述轴套处向外凸出的一体形成有与轴套同轴的导流套，在所述的泵效环右侧板上并位于所述导流套和轴套之间开有辅助进液孔。
所述的泵效环左侧板和泵效环右侧板的外侧面上临近所述轴套处相对称的各一体形成有一个与轴套同轴的导流套。
一种具有封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴上的轴套，由介质端至大气端依次连接的套在所述泵轴和轴套外侧的泵壳、第一密封压盖和第二密封压盖，由介质端至大气端依次设置的位于所述泵壳与所述轴套之间的介质端密封动环、位于第一密封压盖与所述轴套之间并与所述的介质端密封动环接触连接的介质端密封静环、位于所述第二密封压盖与所述轴套之间的大气端密封动环以及位于所述第二密封压盖与所述轴套之间的大气端密封静环，在所述的第二密封压盖与所述轴套之间且位于大气端密封动环远离大气端密封静环这一端的泵效环，在所述的第一密封压盖、介质端密封静环、介质端密封动环、轴套、泵轴、泵效环和第二密封压盖之间形成有一条通过外部管路连接位于外部的热交换器且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环上的冷却液体循环通道对应于形成在所述的第二密封压盖上的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖上且上端口通过外部管路连接所述热交换器出液口的第一通道，形成在所述的第一密封压盖和介质端密 封静环与所述的轴套之间的第二通道，形成在所述的轴套内且对应于所述介质端密封动环和泵轴的第三通道，形成在所述的泵轴外周面和所述的轴套内周面之间的第四通道，形成在所述的轴套内的第五通道，形成在所述的泵效环内的第六通道，形成在所述的第二密封压盖且上端口通过外部管路连接所述热交换器进液口的第七通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖上且上端口通过外部管路连接所述热交换器出液口的第一通道，形成在所述的第一密封压盖和介质端密封静环与所述的轴套之间的第二通道，形成在所述的轴套内且对应于所述介质端密封动环和泵轴的第三通道，形成在所述的泵轴外周面和所述的轴套内周面之间的第四通道，形成在所述的轴套内的第五通道，形成在所述的泵效环内的第六通道，形成在所述的第二密封压盖且上端口通过外部管路连接所述热交换器进液口的第七通道，以及，还设置有依次相连通的：形成在所述泵效环与所述的第二密封压盖之间且进液口连通泵效环内的第六通道的出液口端的第八通道，形成在所述泵效环与所述的第二密封压盖之间且与所述的第八通道相垂直的第九通道，形成在所述泵效环与所述的第二密封压盖之间且与所述的第九通道相垂直的第十通道，形成在所述泵效环与所述的第二密封压盖以及大气端密封动环和大气端密封静环之间的第十一通道，形成在所述泵效环与所述的大气端密封动环之间的第十二通道，所述的第十二通道贯穿所述的泵效环与形成在所述泵效环内的第六通道相连通。
所述的形成在所述的泵轴外周面和所述的轴套内周面之间的第四通道是形成在位于所述泵轴外周面与轴套内周面之间的介质端密封圈和大气端密封圈之间的轴套内侧壁上的凹槽，所述的介质端密封圈和大气端密封圈分别嵌入在所述轴套的内周面上。
所述的泵效环包括有相互平行设置的环形泵效环左侧板和泵效环右侧板，所述泵效环左侧板和泵效环右侧板的内环套在离心泵的轴套外周面上，所述泵效环左侧板和泵效环右侧板的外周边与离心泵的第二密封压盖相衔接并存在间隙，所述的泵效环左侧板和泵效环右侧板之间有呈旋转式的放射状态设置的多数个叶片，并且，所述的多数个叶片与所述的左侧板和右侧板相垂直设置，所述放射状态的多数个叶片临近轴心的收口端构成的端口对应于形成在所述轴套内的第五通道的出液口，所述放射状态的多数个叶片的放射端边缘构成的端口对应于形成在第二密封压盖内的第七通道的进液口。
所述的泵效环包括有相互平行设置的环形泵效环左侧板和泵效环右侧板，所述泵效环左侧板和泵效环右侧板的内环套在离心泵的轴套外周面上，所述泵效环左侧板和泵效环右侧板的外周边与离心泵的第二密封压盖相衔接并存在间隙，所述的泵效环左侧板和泵效环右侧板之间有呈旋转式的放射状态设置的多数个叶片，并且，所述的多数个叶片与所述的左侧板和右侧板相垂直设置，所述放射状态的多数个叶片临近轴心的收口端构成的端口对应于形成在所述轴套内的第五通道的出液口，所述放射状态的多数个叶片的放射端边缘构成的端口对应于形成在第二密封压盖内的第七通道的进液口，所述的泵效环右侧板的外侧面上临近所述轴套处向外凸出的一体形成有与轴套同轴的导流套，在所述的泵效环右侧板上并位于所述导流套和轴套之间开有辅助进液孔，第十通道形成在所述第二密封压盖与所述导流套之间，第十二通道形成在所述导流套与所述轴套之间，且第十二通道的出液口通过所述辅助进液孔连通形成在所述泵效环内的第六通道。
一种具有封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴上的轴套，由介质端至大气端依次连接的套在所述泵轴和轴套外侧的泵壳、第一密封压盖和第二密封压盖，由介质端至大气端依次设置的位于所述第一密封压盖与所述轴套之间的介质端密封静环、位于第一密封压盖与所述轴套之间并与所述的介质端密封静环接触连接的介质端密封动环、位于第二密封压盖与所述轴套之间的大气端密封动环、位于第二密封压盖与所述轴套之间且与所述的大气端密封动环接触连接的大气端密封静环，还设置有泵效环，所述的泵效环分别位于所述第一密封压盖与介质端密封动环之间、第二密封压盖与所述的轴套之间以及第二密封压盖与所述的大气端密封动环之间，在所述的第一密封压盖、介质端密封动环、轴套、泵轴、大气端密封动环、第二密封压盖以及泵效环之间形成有分别通过外部管路连接位于外部的热交换器且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环上的冷却液体循环通道分别连通形成在所述的第二密封压盖内和轴套内的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖上且上端口通过第一外部管路连接所述热交换器出液口的第一通道，形成在所述的第一密封压盖和所述泵效环之间的第二通道，形成在所述的第一密封压盖、介质端密封静环和泵效环之间的第三通道，形成在所述的泵效环与所述介质端密封动环之间的第四通道，形成在所述的泵效环与介质端密封动环之间以及轴套内的第五通道，形成在所述的轴套与所述泵轴之间的第六通道，形成在所述轴套内的第七通道，形成在所述泵效环内的第八通道，形成在所述第二密封压盖内的第九通道，所述第九通道的出液口通过第二外部管路连接所述热交换器的进液口，还设置有依次相连通的：通过第三外部管路连接所述热交换器出液口的形成在所述第二密封压盖内第十通道，形成在所述的第二密封压盖与所述的泵效环之间的第十一通道，形成在所述的第二密封压盖、泵效环以及大气端密封静环之间的第十二通道，形成在所述的泵效环与大气端密封动环之间的第十三通道，形成在所述的泵效环与大气端密封动环之间以及轴套内的第十四通道，所述第十四通道的出液口与所述的形成在所述的轴套与所述泵轴之间的第六通道相连通。
所述的形成在所述的泵轴外周面和所述的轴套内周面之间的第六通道是形成在位于所述泵轴外周面与轴套内周面之间的介质端密封圈和大气端密封圈之间的轴套内侧壁上的凹槽，所述的介质端密封圈和大气端密封圈分别嵌入在所述轴套的内周面上。
所述的泵效环包括有相互平行设置的环形泵效环左侧板和泵效环右侧板，所述泵效环左侧板和泵效环右侧板的内环套在离心泵的轴套外周面上，所述泵效环左侧板和泵效环右侧板的外周边与第二密封压盖相衔接并存在间隙，所述的泵效环左侧板和泵效环右侧板之间有呈旋转式的放射状态设置的多数个叶片，并且，所述的多数个叶片与所述的左侧板和右侧板相垂直设置，所述放射状态的多数个叶片的收口端构成的端口对应于所述轴套的出液口，所述放射状态的多数个叶片的放射端边缘构成的端口对应于形成在第二密封压盖上的第九通道的进液口，所述的泵效环左侧板和泵效环右侧板的外侧面上临近所述轴套处相对称的分别一体形成有一个与轴套同轴的介质端导流套和大气端导流套，所述的第二通道是形成在所述第一密封压盖与介质端导流套之间，所述的第四通道是形成在所述的介质端导流套与所述介质端 密封动环之间，所述的第十一通道是形成在所述的第二密封压盖与大气端导流套之间，所述的第十三通道是形成在所述的大气端导流套与所述的大气端密封动环之间。
本发明的封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统，泵效环不但能给流体提供稳定加速度，而且将液体加速的距离增加、让流体流动速度的方向性强来减小无用功。它既能让密封腔里绝大部分液体都参与流动，又能加长流体流动路径而加大过流面积。在API682这个泵用轴封系统标准里适用2CW-CW带有缓冲液的集装双接触式湿密封和3CW-FB带有阻隔液的面向背配置中集装双接触式湿密封以及适用3CW-BB带有阻隔液的背靠背配置中集装双接触式湿密封，甚至改造热交换器和管线就能实现布置2中2CW-CS带有抑制密封的接触式、湿式内密封和2NS-CS带有抑制密封的非接触式密封摩擦副的气体冷却来改善机械密封性能。
优点：
1、泵效环与泵轴同步旋转，流体从泵轴的轴心进入后向泵效环的边缘移动，在此过程中流体微团的线速度越来越大，到了泵效环的边缘线速度最大，在此期间流体微团始终处于加速状态，即将脱离泵效环时就获得了最大的扬程。
2、该泵效环具有多个从轴心到外边缘的封闭通道，单位时间内所携带的流体体积大，所以增大了流量。
3、从流体微团刚刚进入密封腔开始一直到即将离开密封腔的那一刻，流体微团所走过的路线长。密封腔里大部分液体都处于流体微团所走过的路径附近而参与流动，尤其是机械密封摩擦副这个发热源附近也是如此。
4、不是一小股而是一大股流体被本发明泵效环的大压力差、大流量驱动的作用下流动起来动力十足。
5、使用本发明泵效环由于回流的可能性小所以在密封腔内的旋转部件与静止部件之间的间隙较大，而且泵效环接触流体的表面平滑，所以处在这个间隙里的液体所受的剪切力相对较小，使得无用功减小，由此所产生的热量也就少。对液体分子结构的破坏性不大，因而对液体物理稳定性和化学稳定性都有好处。
6、因为流体在密封腔里的流动路径长而过流面积大，所以冷却效果好。
7、流体是沿着封闭路径流动，故流动的方向一致，能量损失就小，效率高。
8、设计泵效环时可以参考离心泵的闭式叶轮的设计方法，成熟的流量、压力计算式和典型螺线模型，既方便又可靠。
9、改变泵效环的直径就能改变泵效环外圆边缘处的线速度，也就是说能改变流体流动的压力差。
10、改变泵效环的厚度就能改变泵效环内流道的截面面积和含在泵效环里液体的体积，也就是说能改变流体流量，所以能有效而主动地控制热平衡。
11、对旋转与静止部件之间的间隙精度要求低，所以既能制造和装配成本又能容忍更大的运转所造成的磨损量，延长使用寿命。
12、可以用在泵效环上增加辅助吸入孔的方法在密封腔内开辟新的辅助旁路流动路线。
13、可以在泵效环上增加导流套来调整在密封腔内按照设定的要求改变流动路线的路径 方向与路径长度，直接让冷却液对准大气端机械密封摩擦副进行冲洗，如图10、图11、图12、图13、图14所示。
14、通过增加泵效环外径的方法就可以应用于转速较低的泵的轴封系统。
15、有利于提供内循环装置的扬程和流量特性曲线，使一批多套同等规格和型号机械密封试验所得到的循环装置的扬程和流量数据所绘制的特性曲线基本一致(API682中8.6.2.1)。
16、有利于采用缓冲液切向出口(API682中7.2.4.2.1)。
17、可以改善3CW-BB带有阻隔液的背靠背配置中集装双接触式湿密封，如图15、图16、图17、图18所示的机械密封摩擦副。
附图说明
图1是现有技术离心泵的轴封冲洗系统结构示意图；
图2是图1的A-A剖视图；
图3是图1的B-B剖视图；
图4是现有技术离心泵的轴封冲洗系统另一实例的结构示意图；
图5是本发明离心泵的轴封冲洗系统第一实施例的结构示意图；
图6是图5的A-A剖视图；
图7是图5的B-B剖视图；
图8是图5的C-C剖视图；
图9是图8的A-A剖视图；
图10是本发明离心泵的轴封冲洗系统第二实施例的结构示意图；
图11是图10的A-A剖视图；
图12是图10的B-B剖视图；
图13是图10的C-C剖视图；
图14是图13的A-A剖视图；
图15是本发明离心泵的轴封冲洗系统第三实施例的结构示意图；
图16是图15的B-B剖视图；
图17是图15的C-C剖视图；
图18是图17的A-A剖视图。
图中
1：泵轴                            2：介质端密封圈
3：泵壳                            4：介质端密封动环
5：第一密封压盖                    6：介质端密封静环
7：泵效环                          701：泵效环左侧板
702：泵效环右侧板                  703：叶片
704：导流套                        705：辅助进液孔
8：第二密封压盖                    9：大气端密封圈
10：大气端密封动环                 11：大气端密封静环
12：轴套                           13：外部管路
14：介质端密封圈                   15：大气端密封圈
16：热交换器                       17：泵效环
1701：泵效环左侧板                 1702：泵效环右侧板
1703：叶片                         1704：介质端导流套
1705：大气端导流套                 18：第一外部管路
19：第二外部管路                   20：第三外部管路
21：热交换器                       22：进液孔
23：出液孔                         201：第一通道
202：第二通道                      203：第三通道
204：第四通道                      205：第五通道
206：第六通道                      207：第七通道
208：第八通道                      209：第九通道
210：第十通道                      211：第十一通道
212：第十二通道                    301：第一通道
302：第二通道                      303：第三通道
304：第四通道                      305：第五通道
306：第六通道                      307：第七通道
308：第八通道                      309：第九通道
310：第十通道                      311：第十一通道
312：第十二通道                    313：第十三通道
314：第十四通道                    G：冲洗液流向
具体实施方式
下面结合实施例和附图对本发明的封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统做出详细说明。
本发明的封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统，首先一种具有封闭通道并且能提供可靠而稳定扬程和流量流体的泵效环，该泵效环不但能给流体提供稳定加速度，而且将液体加速的距离增加、让流体流动速度的方向性强来减小无用功。它既能让密封腔里绝大部分液体都参与流动，又能加长流体流动路径而加大过流面积。在API682这个泵用轴封系统标准里适用2CW-CW带有缓冲液的集装双接触式湿密封和3CW-FB带有阻隔液的面向背配置中集装双接触式湿密封以及适用3CW-BB带有阻隔液的背靠背配置中集装双接触式湿密封，甚至改造热交换器和管线就能实现布置2CW-CS带有抑制密封的接触式、湿式内密封和2NS-CS带有抑制密封的非接触式内密封摩擦副的气体冷却来改善机械密封性能。
如图5、图6、图7、图8、图9所示，本发明的封闭式机械密封泵效环，包括有相互平行设置的环形泵效环左侧板701和泵效环右侧板702，所述泵效环左侧板701和泵效环右侧板702的内环套在离心泵的轴套12外周面上，所述泵效环左侧板701和泵效环右侧板702的 外周边与离心泵的密封压盖相衔接并存在间隙，所述的泵效环左侧板701和泵效环右侧板702之间有呈旋转式的放射状态设置的多数个叶片703，并且，所述的多数个叶片703与所述的左侧板701和右侧板702相垂直设置，所述放射状态的多数个叶片703靠近轴心的收口端构成的端口对应于所述轴套12的出液口，所述放射状态的多数个叶片703的边缘放射端构成的端口轴向位置对应于形成在密封压盖上的出液通道的出液口，也是热交换器16的进液口。
如图10、图12、图13、图14所示，所述的泵效环右侧板702的外侧面上临近所述轴套12处向外凸出的一体形成有与轴套12同轴的导流套704，在所述的泵效环右侧板702上并位于所述导流套704和轴套12之间开有辅助液进孔705。
如图15、图16、图17、图18所示，所述的泵效环左侧板701和泵效环右侧板702的外侧面上临近所述轴套12处相对称的各一体形成有一个与轴套12同轴的导流套704。
如上所述的本发明的封闭式机械密封泵效环，流体从泵轴的轴心附近的位置进入后在泵效环高速旋转的驱动下向泵效环的边缘移动，在此过程中流体微团的线速度越来越大，到了泵效环的边缘线速度最大，在此期间流体微团始终处于加速状态，即将脱离泵效环时就获得了最大的扬程。泵效环具有多个从轴心到外边缘的封闭通道，单位时间内所携带的流体体积大，所以增大了流量。
如图5、图6、图7、图8、图9所示，本发明的具有封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴1上的轴套12，由介质端至大气端依次连接的套在所述泵轴1和轴套12外侧的泵壳3、第一密封压盖5和第二密封压盖8，由介质端至大气端依次设置的位于所述泵壳3与所述轴套12之间的介质端密封动环4、位于第一密封压盖5与所述轴套12之间并与所述的介质端密封动环4接触连接的介质端密封静环6、位于所述第二密封压盖8与所述轴套12之间的大气端密封动环10以及位于所述第二密封压盖8与所述轴套12之间的大气端密封静环11，在所述的第二密封压盖8与所述轴套12之间且位于大气端密封动环10远离大气端密封静环11这一端的泵效环7，在所述的第一密封压盖5、介质端密封静环6、介质端密封动环4、轴套12、泵轴1、泵效环7和第二密封压盖8之间形成有一条通过外部管路13连接位于外部的热交换器16且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环7上的冷却液体循环通道对应于形成在所述的第二密封压盖8上的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖5上且上端口通过外部管路13连接所述热交换器16出液口的第一通道201，形成在所述的第一密封压盖5和介质端密封静环6与所述的轴套12之间的第二通道202，形成在所述的轴套12内且对应于所述介质端密封动环4和泵轴1的第三通道203，形成在所述的泵轴1外周面和所述的轴套12内周面之间的第四通道204，形成在所述的轴套12内的第五通道205，形成在所述的泵效环7内的第六通道206，形成在所述的第二密封压盖8且上端口通过外部管路12连接所述热交换器16进液口的第七通道207。
如图10、图12、图13、图14所示，所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖5上且上端口通过外部管路13连接所述热交换器16出液口的第一通道201，形成在所述的第一密封压盖5和介质端密封静环6与所述的轴套12之间的第二通 道202，形成在所述的轴套12内且对应于所述介质端密封动环4和泵轴1的第三通道203，形成在所述的泵轴1外周面和所述的轴套12内周面之间的第四通道204，形成在所述的轴套12内的第五通道205，形成在所述的泵效环7内的第六通道206，形成在所述的第二密封压盖8且上端口通过外部管路12连接所述热交换器16进液口的第七通道207，以及，还设置有依次相连通的：形成在所述泵效环7与所述的第二密封压盖8之间且进液口连通泵效环7内的第六通道206的出液口端的第八通道208，形成在所述泵效环7的右侧板702外侧表面与所述的第二密封压盖8之间且与所述的第八通道208相垂直的第九通道209，形成在所述泵效环7的导流套704外表面与所述的第二密封压盖8之间且与所述的第九通道209相垂直的第十通道210，形成在所述泵效环7的导流套704端面与所述的第二密封压盖8及大气端密封动环10气端密封静环11的第十一通道211，所述第十一通道211与所述的第十通道210相垂直，形成在所述泵效环7的导流套704内表面与所述的大气端密封动环10之间的第十二通道212，所述的第十二通道212贯穿所述的泵效环7的辅助进液孔705与形成在所述泵效环7内的第六通道206相连通。
所述的形成在所述的泵轴1外周面和所述的轴套12内周面之间的第四通道204是形成在位于所述泵轴1外周面与轴套12内周面之间的介质端密封圈2和大气端密封圈9之间的轴套12内侧壁上的凹槽，所述的介质端密封圈14和大气端密封圈15分别嵌入在所述轴套12的内周面上。
如图5、图6、图7、图8、图9所示，所述的泵效环7包括有相互平行设置的环形泵效环左侧板701和泵效环右侧板702，所述泵效环左侧板701和泵效环右侧板702的内环套在离心泵的轴套12外周面上，所述泵效环左侧板701和泵效环右侧板702的外周边与离心泵的第二密封压盖8相衔接并存在间隙，所述的泵效环左侧板701和泵效环右侧板702之间有呈旋转式的放射状态设置的多数个叶片703，并且，所述的多数个叶片703与所述的左侧板701和右侧板702相垂直设置，所述放射状态的多数个叶片703临近轴心的收口端构成的端口对应于形成在所述轴套12内的第五通道205的出液口，所述放射状态的多数个叶片703的放射端边缘构成的端口轴向位置对应于形成在第二密封压盖8内的第七通道207的进液口。
如图10、图12、图13、图14所示，所述的泵效环7包括有相互平行设置的环形泵效环左侧板701和泵效环右侧板702，所述泵效环左侧板701和泵效环右侧板702的内环套在离心泵的轴套12外周面上，所述泵效环左侧板701和泵效环右侧板702的外周边与离心泵的第二密封压盖8相衔接并存在间隙，所述的泵效环左侧板701和泵效环右侧板702之间有呈旋转式的放射状态设置的多数个叶片703，并且，所述的多数个叶片703与所述的左侧板701和右侧板702相垂直设置，所述放射状态的多数个叶片703临近轴心的收口端构成的端口对应于形成在所述轴套12内的第五通道205的出液口，所述放射状态的多数个叶片703的放射端边缘构成的端口轴向位置对应于形成在第二密封压盖8内的第七通道207的进液口，也是热交换器16的进液口，所述的泵效环右侧板702的外侧面上临近所述轴套12处向外凸出的一体形成有与轴套12同轴的导流套704，在所述的泵效环右侧板702上并位于所述导流套704和轴套12之间开有辅助进液孔705，第十通道210形成在所述第二密封压盖8与所述导流套704外表面之间，第十二通道212形成在所述导流套704内表面与所述轴套12之间，且第十 二通道212的出液口通过所述辅助进液孔705连通形成在所述泵效环7内的第六通道206。
如图15、图16、图17、图18所示，本发明的具有权利要求1或3所述的封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴1上的轴套12，由介质端至大气端依次连接的套在所述泵轴1和轴套12外侧的泵壳3、第一密封压盖5和第二密封压盖8，由介质端至大气端依次设置的位于所述第一密封压盖5与所述轴套12之间的介质端密封静环6、位于第一密封压盖5与所述轴套12之间并与所述的介质端密封静环6接触连接的介质端密封动环4、位于第二密封压盖8与所述轴套12之间的大气端密封动环10、位于第二密封压盖8与所述轴套12之间且与所述的大气端密封动环10接触连接的大气端密封静环11，还设置有泵效环17，所述的泵效环17分别位于所述第一密封压盖5与介质端密封动环4之间、第二密封压盖8与所述的轴套12之间以及第二密封压盖8与所述的大气端密封动环10之间，在所述的第一密封压盖5、介质端密封动环4、轴套12、泵轴1、大气端密封动环10、第二密封压盖8以及泵效环17之间形成有分别通过外部管路连接位于外部的热交换器21且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环17上的冷却液体循环通道分别连通形成在所述的第二密封压盖8内和轴套12内的冷却液体循环通道。
所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖5上且上端口通过第一外部管路18连接所述热交换器21出液口的第一通道301，形成在所述的第一密封压盖5和所述泵效环17的外表面之间的第二通道302，形成在所述的第一密封压盖5、介质端密封静环6和泵效环17的端面之间的第三通道303，形成在所述的泵效环17的内表面与所述介质端密封动环4之间的第四通道304，形成在所述的泵效环17的内表面与介质端密封动环4之间以及轴套12内的第五通道305，形成在所述的轴套12的内周面与所述泵轴1的外周面之间的第六通道306，形成在所述轴套12内的第七通道307，形成在所述泵效环17内的第八通道308，形成在所述第二密封压盖8内的第九通道309，所述第九通道309的出液口通过第二外部管路19连接所述热交换器21的进液口，还设置有依次相连通的：通过第三外部管路20连接所述热交换器21出液口的形成在所述第二密封压盖8内第十通道310，形成在所述的第二密封压盖8与所述的泵效环17的外表面之间的第十一通道311，形成在所述的第二密封压盖8、泵效环17的端面以及大气端密封静环11之间的第十二通道312，形成在所述的泵效环17的外表面与大气端密封动环10之间的第十三通道313，形成在所述的泵效环17的内表面与大气端密封动环10之间以及轴套12内的第十四通道314，所述第十四通道314的进液口与所述的形成在所述的轴套12的内周面与所述泵轴1的外周面之间的第六通道306相连通。
所述的形成在所述的泵轴1外周面和所述的轴套12内周面之间的第六通道306是形成在位于所述泵轴1外周面与轴套12内周面之间的介质端密封圈2和大气端密封圈9之间的轴套12内侧壁上的凹槽，所述的介质端密封圈14和大气端密封圈15分别嵌入在所述轴套12的内周面上。
所述的泵效环17包括有相互平行设置的环形泵效环左侧板1701和泵效环右侧板1702，所述泵效环左侧板1701和泵效环右侧板1702靠近轴心的内环套在离心泵的轴套12外周面 上，所述泵效环左侧板1701和泵效环右侧板1702的外周边与第二密封压盖8相衔接并存在间隙，所述的泵效环左侧板1701和泵效环右侧板1702之间有呈旋转式的放射状态设置的多数个叶片1703，并且，所述的多数个叶片1703与所述的左侧板1701和右侧板1702相垂直设置，所述放射状态的多数个叶片1703靠近轴心的收口端构成的端口对应于所述轴套12的出液口，所述放射状态的多数个叶片1703的放射端边缘构成的端口对应于形成在密封压盖上轴向位置的第八通道308的进液口。所述的泵效环左侧板1701和泵效环右侧板1702的外侧面上临近所述轴套12处相对称的分别一体形成有一个与轴套12同轴的介质端导流套1704和大气端导流套1705，所述的第二通道302是形成在所述第一密封压盖5与介质端导流套1704之间，所述的第四通道304是形成在所述的介质端导流套1704与所述介质端密封动环4之间，所述的第十一通道311是形成在所述的第二密封压盖8与大气端导流套1705之间，所述的第十三通道313是形成在所述的大气端导流套1705与所述的大气端密封动环10之间。
本发明的封闭式机械密封泵效环和具有该泵效环的轴封冲洗系统，从各附图中可以提到旋转部件有：泵轴、轴套、介质端机械密封动环、大气端机械密封动环、泵效环，除此之外都是静止部件。
所述的这些旋转部件都与泵轴同步旋转，换句话说就是这些旋转部件每时每刻的角速度相等，由此越靠近轴心的部位线速度的绝对值就越小，反之，距离轴心越远的部位线速度的绝对值就越大。在本发明中流体微团是从轴心地带进入泵效环，然后在泵效环的封闭通道里向该泵效环的边缘的方向位移，这个移动的过程就是加速过程，在附图中流体微团从a点的位置移动到b点的位置，这也就是获得扬程的过程。除此之外从附图中还可以看出本发明的泵效环具有多个封闭通道同时工作，所以它们叠加起来的通道的横截面积就大，在单位时间里通过这个大的横截面积的流体体积必然也就大，即：流量大。我们都知道：功率与流量和扬程的乘积成正比。这就足以说明本发明的泵效环性能优于现有技术的泵效环。

Claims (13)

  1. 一种封闭式机械密封泵效环，其特征在于，包括有相互平行设置的环形泵效环左侧板(701)和泵效环右侧板(702)，所述泵效环左侧板(701)和泵效环右侧板(702)的内环套在离心泵的轴套(12)外周面上，所述泵效环左侧板(701)和泵效环右侧板(702)的外周边与离心泵的密封压盖相衔接并存在间隙，所述的泵效环左侧板(701)和泵效环右侧板(702)之间有呈旋转式的放射状态设置的多数个叶片(703)，并且，所述的多数个叶片(703)与所述的左侧板(701)和右侧板(702)相垂直设置，所述放射状态的多数个叶片(703)的收口端构成的端口对应于所述轴套(12)的出液口，所述放射状态的多数个叶片(703)的放射端边缘构成的端口对应于形成在密封压盖上的出液通道的进液口。
  2. 根据权利要求1所述的封闭式机械密封泵效环，其特征在于，所述的泵效环右侧板(702)的外侧面上临近所述轴套(12)处向外凸出的一体形成有与轴套(12)同轴的导流套(704)，在所述的泵效环右侧板(702)上并位于所述导流套(704)和轴套(12)之间开有辅助进液孔(705)。
  3. 根据权利要求1所述的封闭式机械密封泵效环，其特征在于，所述的泵效环左侧板(701)和泵效环右侧板(702)的外侧面上临近所述轴套(12)处相对称的各一体形成有一个与轴套(12)同轴的导流套(704)。
  4. 一种具有权利要求1或2所述的封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴(1)上的轴套(12)，由介质端至大气端依次连接的套在所述泵轴(1)和轴套(12)外侧的泵壳(3)、第一密封压盖(5)和第二密封压盖(8)，由介质端至大气端依次设置的位于所述泵壳(3)与所述轴套(12)之间的介质端密封动环(4)、位于第一密封压盖(5)与所述轴套(12)之间并与所述的介质端密封动环(4)接触连接的介质端密封静环(6)、位于所述第二密封压盖(8)与所述轴套(12)之间的大气端密封动环(10)以及位于所述第二密封压盖(8)与所述轴套(12)之间的大气端密封静环(11)，其特征在于，在所述的第二密封压盖(8)与所述轴套(12)之间且位于大气端密封动环(10)远离大气端密封静环(11)这一端的泵效环(7)，在所述的第一密封压盖(5)、介质端密封静环(6)、介质端密封动环(4)、轴套(12)、泵轴(1)、泵效环(7)和第二密封压盖(8)之间形成有一条通过外部管路(13)连接位于外部的热交换器(16)且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环(7)上的冷却液体循环通道对应于形成在所述的第二密封压盖(8)上的冷却液体循环通道。
  5. 根据权利要求4所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖(5)上且上端口通过外部管路(13)连接所述热交换器(16)出液口的第一通道(201)，形成在所述的第一密封压盖(5)和介质端密封静环(6)与所述的轴套(12)之间的第二通道(202)，形成在所述的轴套(12)内且对应于所述介质端密封动环(4)和泵轴(1)的第三通道(203)，形成在所述的泵轴(1)外周面和所述的轴套(12)内周面之间的第四通道(204)，形成在所述 的轴套(12)内的第五通道(205)，形成在所述的泵效环(7)内的第六通道(206)，形成在所述的第二密封压盖(8)且上端口通过外部管路(12)连接所述热交换器(13)进液口的第七通道(207)。
  6. 根据权利要求4所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖(5)上且上端口通过外部管路(13)连接所述热交换器(16)出液口的第一通道(201)，形成在所述的第一密封压盖(5)和介质端密封静环(6)与所述的轴套(12)之间的第二通道(202)，形成在所述的轴套(12)内且对应于所述介质端密封动环(4)和泵轴(1)的第三通道(203)，形成在所述的泵轴(1)外周面和所述的轴套(12)内周面之间的第四通道(204)，形成在所述的轴套(12)内的第五通道(205)，形成在所述的泵效环(7)内的第六通道(206)，形成在所述的第二密封压盖(8)且上端口通过外部管路(12)连接所述热交换器(13)进液口的第七通道(207)，以及，还设置有依次相连通的：形成在所述泵效环(7)与所述的第二密封压盖(8)之间且进液口连通泵效环(7)内的第六通道(206)的出液口端的第八通道(208)，形成在所述泵效环(7)与所述的第二密封压盖(8)之间且与所述的第八通道(208)相垂直的第九通道(209)，形成在所述泵效环(7)与所述的第二密封压盖(8)之间且与所述的第九通道(209)相垂直的第十通道(210)，形成在所述泵效环(7)与所述的第二密封压盖(8)以及大气端密封动环(10)和大气端密封静环(11)之间的第十一通道(211)，形成在所述泵效环(7)与所述的大气端密封动环(10)之间的第十二通道(212)，所述的第十二通道(212)贯穿所述的泵效环(7)与形成在所述泵效环(7)内的第六通道(206)相连通。
  7. 根据权利要求5或6所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的形成在所述的泵轴(1)外周面和所述的轴套(12)内周面之间的第四通道(204)是形成在位于所述泵轴(1)外周面与轴套(12)内周面之间的介质端密封圈(2)和大气端密封圈(9)之间的轴套(12)内侧壁上的凹槽，所述的介质端密封圈(14)和大气端密封圈(15)分别嵌入在所述轴套(12)的内周面上。
  8. 根据权利要求4或5所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的泵效环(7)包括有相互平行设置的环形泵效环左侧板(701)和泵效环右侧板(702)，所述泵效环左侧板(701)和泵效环右侧板(702)的内环套在离心泵的轴套(12)外周面上，所述泵效环左侧板(701)和泵效环右侧板(702)的外周边与离心泵的第二密封压盖(8)相衔接并存在间隙，所述的泵效环左侧板(701)和泵效环右侧板(702)之间有呈旋转式的放射状态设置的多数个叶片(703)，并且，所述的多数个叶片(703)与所述的左侧板(701)和右侧板(702)相垂直设置，所述放射状态的多数个叶片(703)临近轴心的收口端构成的端口对应于形成在所述轴套(12)内的第五通道(205)的出液口，所述放射状态的多数个叶片(703)的放射端边缘构成的端口对应于形成在第二密封压盖(8)内的第七通道(207)的进液口。
  9. 根据权利要求4或6所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的泵效环(7)包括有相互平行设置的环形泵效环左侧板(701)和泵效环右侧板(702)，所述泵效环左侧板(701)和泵效环右侧板(702)的内环套在离心泵的轴套(12)外周面上， 所述泵效环左侧板(701)和泵效环右侧板(702)的外周边与离心泵的第二密封压盖(8)相衔接并存在间隙，所述的泵效环左侧板(701)和泵效环右侧板(702)之间有呈旋转式的放射状态设置的多数个叶片(703)，并且，所述的多数个叶片(703)与所述的左侧板(701)和右侧板(702)相垂直设置，所述放射状态的多数个叶片(703)临近轴心的收口端构成的端口对应于形成在所述轴套(12)内的第五通道(205)的出液口，所述放射状态的多数个叶片(703)的放射端边缘构成的端口对应于形成在第二密封压盖(8)内的第七通道(207)的进液口，所述的泵效环右侧板(702)的外侧面上临近所述轴套(12)处向外凸出的一体形成有与轴套(12)同轴的导流套(704)，在所述的泵效环右侧板(702)上并位于所述导流套(704)和轴套(12)之间开有辅助进液孔(705)，第十通道(210)形成在所述第二密封压盖(8)与所述导流套(704)之间，第十二通道(212)形成在所述导流套(704)与所述轴套(12)之间，且第十二通道(212)的出液口通过所述辅助进液孔(705)连通形成在所述泵效环(7)内的第六通道(206)。
  10. 一种具有权利要求1或3所述的封闭式机械密封泵效环的轴封冲洗系统，包括有套在泵轴(1)上的轴套(12)，由介质端至大气端依次连接的套在所述泵轴(1)和轴套(12)外侧的泵壳(3)、第一密封压盖(5)和第二密封压盖(8)，由介质端至大气端依次设置的位于所述第一密封压盖(5)与所述轴套(12)之间的介质端密封静环(6)、位于第一密封压盖(5)与所述轴套(12)之间并与所述的介质端密封静环(6)接触连接的介质端密封动环(4)、位于第二密封压盖(8)与所述轴套(12)之间的大气端密封动环(10)、位于第二密封压盖(8)与所述轴套(12)之间且与所述的大气端密封动环(10)接触连接的大气端密封静环(11)，其特征在于，还设置有泵效环(17)，所述的泵效环(17)分别位于所述第一密封压盖(5)与介质端密封动环(4)之间、第二密封压盖(8)与所述的轴套(12)之间以及第二密封压盖(8)与所述的大气端密封动环(10)之间，在所述的第一密封压盖(5)、介质端密封动环(4)、轴套(12)、泵轴(1)、大气端密封动环(10)、第二密封压盖(8)以及泵效环(17)之间形成有分别通过外部管路连接位于外部的热交换器(21)且能够使热交换液体在随旋转部件同步旋转的同时，又沿旋转部件的轴向流动能够对各旋转部件进行热交换的冷却液体循环通道，形成在所述泵效环(17)上的冷却液体循环通道分别连通形成在所述的第二密封压盖(8)内和轴套(12)内的冷却液体循环通道。
  11. 根据权利要求10所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的冷却液体循环通道包括有依次相连通的：形成在所述的第一密封压盖(5)上且上端口通过第一外部管路(18)连接所述热交换器(21)出液口的第一通道(301)，形成在所述的第一密封压盖(5)和所述泵效环(17)之间的第二通道(302)，形成在所述的第一密封压盖(5)、介质端密封静环(6)和泵效环(17)之间的第三通道(303)，形成在所述的泵效环(17)与所述介质端密封动环(4)之间的第四通道(304)，形成在所述的泵效环(17)与介质端密封动环(4)之间以及轴套(12)内的第五通道(305)，形成在所述的轴套(12)与所述泵轴(1)之间的第六通道(306)，形成在所述轴套(12)内的第七通道(307)，形成在所述泵效环(17)内的第八通道(308)，形成在所述第二密封压盖(8)内的第九通道(309)，所述第九通道(309)的出液口通过第二外部管路(19)连接所述热交换器(21)的进液口，还设置 有依次相连通的：通过第三外部管路(20)连接所述热交换器(21)出液口的形成在所述第二密封压盖(8)内第十通道(310)，形成在所述的第二密封压盖(8)与所述的泵效环(17)之间的第十一通道(311)，形成在所述的第二密封压盖(8)、泵效环(17)以及大气端密封静环(11)之间的第十二通道(312)，形成在所述的泵效环(17)与大气端密封动环(10)之间的第十三通道(313)，形成在所述的泵效环(17)与大气端密封动环(10)之间以及轴套(12)内的第十四通道(314)，所述第十四通道(314)的出液口与所述的形成在所述的轴套(12)与所述泵轴(1)之间的第六通道(306)相连通。
  12. 根据权利要求11所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的形成在所述的泵轴(1)外周面和所述的轴套(12)内周面之间的第六通道(306)是形成在位于所述泵轴(1)外周面与轴套(12)内周面之间的介质端密封圈(2)和大气端密封圈(9)之间的轴套(12)内侧壁上的凹槽，所述的介质端密封圈(14)和大气端密封圈(15)分别嵌入在所述轴套(12)的内周面上。
  13. 根据权利要求10所述的具有封闭式机械密封泵效环的轴封冲洗系统，其特征在于，所述的泵效环(17)包括有相互平行设置的环形泵效环左侧板(1701)和泵效环右侧板(1702)，所述泵效环左侧板(1701)和泵效环右侧板(1702)的内环套在离心泵的轴套(12)外周面上，所述泵效环左侧板(1701)和泵效环右侧板(1702)的外周边与第二密封压盖(8)相衔接并存在间隙，所述的泵效环左侧板(1701)和泵效环右侧板(1702)之间有呈旋转式的放射状态设置的多数个叶片(1703)，并且，所述的多数个叶片(1703)与所述的左侧板(1701)和右侧板(1702)相垂直设置，所述放射状态的多数个叶片(1703)的收口端构成的端口对应于所述轴套(12)的出液口，所述放射状态的多数个叶片(1703)的放射端边缘构成的端口对应于形成在第二密封压盖(8)上的第九通道(309)的进液口，所述的泵效环左侧板(1701)和泵效环右侧板(1702)的外侧面上临近所述轴套(12)处相对称的分别一体形成有一个与轴套(12)同轴的介质端导流套(1704)和大气端导流套(1705)，所述的第二通道(302)是形成在所述第一密封压盖(5)与介质端导流套(1704)之间，所述的第四通道(304)是形成在所述的介质端导流套(1704)与所述介质端密封动环(4)之间，所述的第十一通道(311)是形成在所述的第二密封压盖(8)与大气端导流套(1705)之间，所述的第十三通道(313)是形成在所述的大气端导流套(1705)与所述的大气端密封动环(10)之间。
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