CN2471985Y - Assembled suspended sealer - Google Patents
Assembled suspended sealer Download PDFInfo
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- CN2471985Y CN2471985Y CN 00262138 CN00262138U CN2471985Y CN 2471985 Y CN2471985 Y CN 2471985Y CN 00262138 CN00262138 CN 00262138 CN 00262138 U CN00262138 U CN 00262138U CN 2471985 Y CN2471985 Y CN 2471985Y
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Abstract
The utility model relates to a combined floating-ring sealing device, which comprises a seal chamber, an end cover, an inner floating ring, an outer floating ring and a shaft sleeve. The utility model is characterized in that a supercharging segment, a buoyancy lift segment and a leakproof segment are arranged in the sealing device. The supercharging segment is fixed on the inlet side of the sealing oil near the inner floating ring; the leakproof segment is arranged at the side of sealed gas in the inner hole of the inner floating ring; the buoyancy lift segment is positioned between the supercharging segment and the leakproof segment. The utility model can improve the adaptability of the floating-ring sealing device for the pressure difference, expand the scope of safe operation, and decrease internal leakage of the seal oil. The utility model can be applied to shaft seal for the centrifugal compressors and other rotating machines, which use the toxic, explosive, or other dangerous gases as working gases.
Description
The invention belongs to the rotation shaft seal, particularly a kind of combined floating ring sealing device is used for the shaft end seal device of rotating machineries such as centrifugal compressor.
Float-ring sealing device is a kind of conventional seals device of rotating machineries such as centrifugal compressor." chemical industry sealing technique " book has detailed description (chief editor such as Hu Guozhen, Chemical Industry Press, 1990.9) to float-ring sealing device.Rotating machinery is inner if than high poisonous of atmospheric pressure, inflammable, dangerous gas such as explosive grade, for preventing that this sealed gas from leaking in the atmosphere along running shaft, between the casing of rotating machinery and running shaft, float-ring sealing device is housed, this device comprises the seal chamber that the center is with holes, seal chamber places in the casing, running shaft passes the hole of seal chamber, be fixed with axle sleeve on the running shaft, be equipped with on the axle sleeve ring-type in, outer floating ring, and leave the gap, interior floating ring is positioned near sealed gas one side, and outer floating ring is positioned near atmosphere one side, feeds the sealing oil that is higher than sealed gas pressure in the seal chamber.When running shaft rotated, sealing oil formed oil film in the gap between axle sleeve and floating ring, and this oil film floats floating ring, avoided contacting with axle sleeve, satisfied and did not have wearing and tearing.Long-life requirement: the inner hole wall of interior floating ring is one section smooth wall, and the radius clearance between the axle sleeve is generally 0.03-0.10mm, the pressure of the oil film in this gap is higher than the pressure of sealed gas, thus can stop sealed gas to spill along the gap, thus reach the purpose of sealing.Meanwhile, the oil in the oil film flows into sealed gas one side along the gap, and the internal leakage of sealing oil that Here it is should reduce the internal leakage of sealing oil as far as possible.And the radius clearance between outer floating ring and the axle sleeve is generally 0.10-0.30mm, and most sealing oil turn back to leakproof fuel cell through this gap, and the heat that friction in the oil film is generated is taken away simultaneously.Float-ring sealing device can proper functioning precondition be the pressure that the sealing oil pressure that enters this device is higher than sealed gas.Difference between the two, the sealing oil pressure of floating ring and the difference of sealed gas pressure are called oil gas pressure reduction in promptly entering, and its value is generally 0.03-0.06MPa.But oil gas pressure reduction has fluctuation in actual motion, in case oil gas pressure reduction is reduced to 0 or negative value, when the sealing oil pressure of floating ring is equal to or less than the pressure of sealed gas in promptly entering, then sealed gas will enter seal chamber along the gap between interior floating ring and the axle sleeve, destroy oil film, and then floating ring loses floatability, contact with the axle sleeve of rotation, form violent friction, the heat of generation destroys floating ring, causes sealed gas leak to leak, seal failure jeopardizes production safety.
The object of the present invention is to provide a kind of combined floating ring sealing device, overcome the deficiency of above-mentioned float-ring sealing device, when oil gas pressure reduction is reduced to 0 or during negative value, this combined floating ring sealing device still can normally move, simultaneously, can reduce the internal leakage of sealing oil again.
This bright purpose is achieved in that a kind of combined floating ring sealing device comprises seal chamber, end cap, interior floating ring, outer floating ring, axle sleeve; The porose plate-like end cap in tubbiness seal chamber that bottom centre is porose and center is connected as a single entity, place in the casing of rotating machinery, the running shaft of rotating machinery passes the hole of seal chamber and end cap, be fixed with axle sleeve on the running shaft, the interior floating ring and the outer floating ring of ring-type are housed on the axle sleeve, all gapped between interior floating ring hole and outer floating ring hole and the axle sleeve, interior floating ring is positioned at the side near sealed gas, the interior edge face of an one end face and end cap is fitted with one heart mutually, outer floating ring is positioned at the side near atmosphere, the interior edge face of an one end face and seal chamber is fitted with one heart mutually, it is characterized in that: have the supercharging section in the sealing device, buoyance lift section and leakproof section, the supercharging section is positioned at the sealing oil inlet side near floating ring, and the leakproof section is positioned at the close sealed gas side of floating ring endoporus, and the buoyance lift section is positioned between supercharging section and the leakproof section.
Advantage of the present invention is: when oil gas pressure reduction descended, the sealing oil of floating ring was boosted in the supercharging section will enter, make buoyance lift section oil gas pressure reduction remain on the occasion of, the buoyance lift section produces stable uplift, prevents that oil film is destroyed, enlarges the safe operation scope; In addition, the leakproof section stops sealing oil to be leaked to sealed gas side, thereby reduces the sealing oil internal leakage.
For ease of narrating and understanding the present invention, make such regulation:
1. the pressure of the sealing oil of floating ring is higher than the pressure of sealed gas in entering under the normal condition, and sealing oil will be along the clearance leakage between interior floating ring hole and the axle sleeve to sealed gas one side.On the internal surface in floating ring hole spiral chute is arranged in of the present invention, when the spiral fluted function is to stop sealing oil when sealed gas side leaks, this spiral chute is called the transport screw groove; When the spiral fluted function is that this spiral chute was called the reverse acting spiral groove when oil gas pressure reduction was raise.
2. mutually rotation in face-off and gapped two toroidal surfaces with one heart, one are static, constitute centrifugal gap, sealing oil is arranged in the gap, and the function when centrifugal gap is to stop sealing oil when sealed gas side leaks, and this centrifugal gap is called the centrifugal gap of forward; Function when centrifugal gap is that this centrifugal gap was called reverse centrifugal gap when oil gas pressure reduction was raise.
3. the negative value scope dictates in " oil gas pressure reduction be reduced to 0 or negative value " of the present invention is [0-(0.03)] MPa.
Description of drawings:
Fig. 1 is a kind of longitudinal sectional view of combined floating ring sealing device.
Fig. 2 is the pressure distribution schematic representation of combined floating ring sealing device shown in Figure 1.
Fig. 3 is the longitudinal sectional view of another kind of combined floating ring sealing device.
Fig. 4 is the pressure distribution schematic representation of combined floating ring sealing device shown in Figure 3.
Fig. 5 is the longitudinal sectional view of another combined floating ring sealing device.
Fig. 6 is the pressure distribution schematic representation of combined floating ring sealing device shown in Figure 5.
Now represented in conjunction with the accompanying drawings embodiment is elaborated.
A kind of combined floating ring sealing device comprises seal chamber, end cap, interior floating ring, outer floating ring, axle sleeve; The porose plate-like end cap in tubbiness seal chamber that bottom centre is porose and center is connected as a single entity, place in the casing of rotating machinery, the running shaft of rotating machinery passes the hole of seal chamber and end cap, be fixed with axle sleeve on the running shaft, the interior floating ring and the outer floating ring of ring-type are housed on the axle sleeve, all gapped between interior floating ring hole and outer floating ring hole and the axle sleeve, interior floating ring is positioned at the side near sealed gas, the interior edge face of an one end face and end cap is fitted with one heart mutually, outer floating ring is positioned at the side near atmosphere, the interior edge face of an one end face and seal chamber is fitted with one heart mutually, it is characterized in that: have the supercharging section in the sealing device, buoyance lift section and leakproof section, the supercharging section is positioned at the sealing oil inlet side near floating ring, and the leakproof section is positioned at the close sealed gas side of floating ring endoporus, and the buoyance lift section is positioned between supercharging section and the leakproof section.
Fig. 1 is a kind of longitudinal sectional view of combined floating ring sealing device.It is characterized in that: the internal surface in interior floating ring hole is made up of reverse acting spiral groove, smooth section and transport screw groove successively, and three's internal diameter is identical, and is relative with the outer surface of the axle sleeve that waits external diameter, and gapped; Wherein, the reverse acting spiral groove is the supercharging section, and the transport screw groove is the leakproof section, and smooth section is the buoyance lift section.
In this combined floating ring sealing device, the porose plate-like end cap 2 in tubbiness seal chamber 1 that bottom centre is porose and center is connected as a single entity, place in the casing 6 of rotating machinery, the running shaft 7 of rotating machinery passes the hole of seal chamber 1 and end cap 2, be fixed with axle sleeve 5 on the running shaft 7, the interior floating ring 3 and the outer floating ring 4 of ring-type are housed on the axle sleeve 5, all gapped between the endoporus of the endoporus of interior floating ring 3 and outer floating ring 4 and the axle sleeve 5, interior floating ring 3 is positioned at the side near sealed gas 8, an end face 9 of interior floating ring 3 is fitted with one heart mutually with the interior edge face 10 of end cap 2, outer floating ring 4 is positioned at the side near atmosphere 11, and an end face 12 of outer floating ring 4 is fitted with one heart mutually with the interior edge face 13 of seal chamber 1.It is characterized in that: the internal surface of the endoporus of interior floating ring 3 is made up of reverse acting spiral groove 14, smooth section 15 and transport screw groove 16 successively, the diameter of these three sections internal surfaces is identical, relative and gapped with the periphery of the axle sleeve 5 that waits external diameter, wherein, reverse acting spiral groove 14 is the supercharging section, is positioned at the sealing oil inlet side near floating ring 3; Transport screw groove 16 is the leakproof section, is positioned at the side near sealed gas 8.Smooth section 15 is the buoyance lift section, between above-mentioned supercharging section and leakproof section.
Forward and reverse spiral chute is exactly two sections spiral chutes on the internal surface of interior floating ring 3 endoporus, and the rotation direction of the two is opposite, because sealing oil has viscosity, when axle sleeve rotated with running shaft, spiral chute had pump to the sealing oil in its groove and draws effect.Feed the sealing oil that pressure is higher than sealed gas pressure from the filler opening 17 of seal chamber 1, when running shaft 7 drives axle sleeve 5 rotations, forward and reverse spiral chute all is that the direction pump towards smooth section 15 draws sealing oil, if the pressure of the sealing oil of floating ring is Pa in entering, the pressure of sealed gas is Pe, referring to Fig. 2, this figure is the pressure distribution schematic representation of combined floating ring sealing device shown in Figure 1.The coordinate of the endoporus of floating ring 3 in horizontal ordinate is represented, it is formed by three sections, is followed successively by reverse acting spiral groove 14, smooth section 15 and transport screw groove 16, and ordinate is represented the sealing oil pressure at above-mentioned three sections internal surface places.
The oil gas pressure differential deltap Pa=Pa-Pe=0.05MPa of floating ring 3 in normal condition lower seal oil enters, wherein: Pa is the pressure of floating ring 3 in sealing oil enters, and Pe is the pressure of sealed gas, (referring to Fig. 2).Floating ring 3 was sentenced the expression of a point in sealing oil entered, reverse acting spiral groove 14 is the supercharging section, make in design reverse acting spiral groove 14 will enter in the sealing oil of the floating ring 0.05MPa that boosts, reach the b point among Fig. 2, this b represents the intersection of reverse acting spiral groove 14 and smooth section 15, then the oil gas pressure reduction of smooth section is Δ Pb=Pb-Pe=0.05+0.05=0.10MPa, and wherein Pb is the sealing oil pressure of smooth section; Because gapped between smooth section 15 and the axle sleeve 5, sealing oil forms oil film wedge in the gap, interior floating ring 3 is floated, floating ring 3 and axle sleeve 5 automatic centerings in making, remain gappedly, avoid contacting with the axle sleeve 5 that rotates, this is identical with the effect of interior floating ring in the existing float-ring sealing device; Simultaneously,, prevent that sealed gas from entering this gap, guarantee the seal arrangement safe operation because the pressure of sealing oil is higher than the pressure of sealed gas in the gap.The sealing oil that leakproof section-transport screw groove 16 then will flow out smooth section 15 is drawn to the direction pump of smooth section 15, prevent the sealing oil leakage, and the length of transport screw groove 16 is greater than the length of reverse acting spiral groove 14, the oil gas pressure reduction of fully can balance above-mentioned Δ Pb=0.10MPa.C point among Fig. 2, the intersection of this some expression transport screw groove 16 and smooth section 15; D point among Fig. 2 is a bit of zero for oil gas pressure reduction in the transport screw groove 16, the e point then is the end points of transport screw groove 16, owing to make the physical length ce section of transport screw groove 16 greater than the needed minimum length cd section of equilibrium oil draught head Δ Pb in design, therefore, theoretically, the internal leakage of sealing oil is zero.Pressure distribution is seen the curve abcde of Fig. 2.
The sealing oil pressure decline 0.05MPa of floating ring 3 in entering, (a ' among Fig. 2 during the pressure P e of the sealed gas of pressure Pa ' equal of the sealing oil of floating ring 3 in promptly entering, the e point), the oil gas pressure differential deltap Pa '=Pa '-Pe=0MPa of floating ring 3 in sealing oil enters, because the sealing oil of the floating ring 0.05MPa (b ' point among Fig. 2) that boosts in supercharging section-reverse acting spiral groove 14 will enter, then the oil gas pressure reduction of smooth section 15 is Δ Pb '=Pb '-Pe=0+0.05=0.05MPa, because it is gapped between smooth section 15 and the axle sleeve 5, sealing oil forms oil film wedge in the gap, interior floating ring 3 is floated, the axle sleeve 5 of avoiding and rotating contacts, simultaneously, because the pressure of sealing oil is higher than the pressure of sealed gas in the gap, prevent that sealed gas from entering this gap, guarantee the seal arrangement safe operation.This shows that when the difference Δ Pa ' of the pressure of pressure and the sealed gas of sealing oil-feed reduces to when zero, the sealing device still can safe operation.The sealing oil that leakproof section-transport screw groove 16 then will flow out smooth section 15 is drawn to the direction pump of smooth section 15, prevent the sealing oil leakage, and the length of transport screw groove 16 is greater than the length of reverse acting spiral groove 14, the oil gas pressure reduction (c ' point among Fig. 2) of Δ Pb '=0.05MPa that complete energy balance is above-mentioned, therefore the internal leakage of sealing oil reduces, theoretically, the internal leakage of sealing oil is zero.Pressure distribution is seen curve a ' b ' c ' d ' e of Fig. 2.
The pressure Pa of the sealing oil of floating ring 3 in entering is " less than the pressure P e of sealed gas (a among Fig. 2 " .e point), for example, Δ Pa "=Pa "-Pe=(0.02) MPa, when negative oil gas pressure reduction having occurred, because supercharging section-reverse acting spiral groove 14 is with the sealing oil that the enters 0.05MPa (b among Fig. 2 " point) that boosts; the oil gas pressure reduction of smooth section 15 is Δ Pb "=Pb "-Pe=(0.02)+0.05=0.03MPa, still is positive oil gas pressure reduction; Because it is gapped between smooth section 15 and the axle sleeve 5, sealing oil forms oil film wedge in the gap, interior floating ring 3 is floated, the axle sleeve 5 of avoiding and rotating contacts, simultaneously, because the pressure of sealing oil is higher than the pressure of sealed gas in the gap, prevents that sealed gas from entering this gap, guarantee the seal arrangement safe operation.At this moment, the sealing device still is in the safe operation scope.The sealing oil that leakproof section-transport screw groove 16 then will flow out smooth section 15 is drawn to the direction pump of smooth section 15, prevent the sealing oil leakage, and the length of transport screw groove 16 is greater than the length of reverse acting spiral groove 14, fully can balance above-mentioned Δ Pb " the oil gas pressure reduction of=0.03MPa (c among Fig. 2 " point), therefore the internal leakage of sealing oil reduces, theoretically, the internal leakage of sealing oil is zero.Pressure distribution is seen curve a " b " c " d " e of Fig. 2.
Generally, the axial length of reverse acting spiral groove 14 is 4-20mm, and the axial length of transport screw groove 16 is two to five times of axial length of reverse acting spiral groove 14.
Forward and reverse spiral chute all is a multiple thread, 2-60 of numbers of starts.10-30 of optimum ranges.
The spiral fluted helix angle is generally 2 °-30 °, and optimum range is 5 °-20 °.
In sum, this combined floating ring sealing device is the combination of floating-ring seal and spiral seal, it has the advantage of the two concurrently: the automatic centering effect of floating-ring seal and the pump of spiral seal draw effect, improved the adaptability of seal arrangement to the oil gas pressure-difference fluctuation, enlarged range of safety operation, and the internal leakage of sealing oil is reduced.
Fig. 3 is the longitudinal sectional view of another kind of combined floating ring sealing device.It is characterized in that: columniform boss structure is arranged on the axle sleeve, and an end face of this boss is relative with an end face of a stationary components, and gapped, constitutes reverse centrifugal gap, and this reverse centrifugal gap is the supercharging section; The internal surface in interior floating ring hole is made up of smooth section and transport screw groove, the internal diameter of smooth section is greater than the internal diameter of transport screw groove, link to each other with toroidal surface between the two, form the endoporus step, this step is relative with another end face of the boss of above-mentioned axle sleeve, and gapped, constitute the centrifugal gap of forward, the centrifugal gap of this forward is the part of leakproof section; Transport screw groove on the internal surface in interior floating ring hole then is another part of leakproof section; Smooth section on the internal surface in interior floating ring hole is relative with the periphery of above-mentioned axle sleeve boss and gapped, is the buoyance lift section.
In this combined floating ring sealing device, the porose plate-like end cap 22 in tubbiness seal chamber 21 that the center is porose and center is connected as a single entity, place in the housing 26 of rotating machinery, the running shaft 27 of rotating machinery passes the hole of seal chamber 21 and end cap 22, be fixed with axle sleeve 25 on the running shaft 27, the interior floating ring 23 and the outer floating ring 24 of ring-type are housed on the axle sleeve 25, all gapped between the endoporus of the endoporus of interior floating ring 23 and outer floating ring 24 and the axle sleeve 25, interior floating ring 23 is positioned at the side near sealed gas 28, an end face 29 of interior floating ring 23 is fitted with one heart mutually with the interior edge face 30 of end cap 22, outer floating ring 24 is positioned at the side near atmosphere 31, and an end face 32 of outer floating ring 24 is fitted with one heart mutually with the interior edge face 33 of seal chamber 21.The feature of sealing is: cylindrical boss structure 36 is arranged on the axle sleeve 25, an end face 37 of this boss 36 is relative with one heart with an end face 39 of a stationary components spring seat 38, and gapped, constitute reverse centrifugal gap 40, this reverse centrifugal gap 40 is the supercharging section; The internal surface of the endoporus of interior floating ring 23 is made up of smooth section 34, transport screw groove 35 successively, and wherein transport screw groove 35 is positioned at the side near sealed gas 28; The diameter of smooth section 34 is greater than the diameter of transport screw groove 35, link to each other with toroidal surface between the two, constitute endoporus step 42, another end face 41 of boss structure 36 on this step 42 and the above-mentioned axle sleeve 25 is relative, and it is gapped, constitute the centrifugal gap 43 of forward, the centrifugal gap 43 of this forward is the part of leakproof section; Transport screw groove 35 on the internal surface of the interior floating ring 23 of close sealed gas side is another part of leakproof section; Smooth section 34 on interior floating ring 23 endoporus is relative with the periphery 44 of above-mentioned axle sleeve boss 36, and gapped, is the buoyance lift section.
Forward and reverse centrifugal gap is exactly to be made of relative arrangement and gapped two concentric circle anchor rings, one of them rotation, one are static, be filled with sealing oil in its gap, when a toroidal surface rotation, because sealing oil toughness, drive the sealing oil rotation and produce centrifugal force, and then be converted into pressure.Feed sealing oil from the filler opening 45 of seal chamber 21, when running shaft 27 drove axle sleeves 25 and rotates, forward and reverse centrifugal gap and transport screw groove all were that the direction pump towards smooth section 34 draws sealing oil.The pressure of sealing oil of floating ring 23 is Pa in entering, and the pressure of sealed gas is Pf, and referring to Fig. 4, this figure is the pressure distribution schematic representation of combined floating ring sealing device shown in Figure 3.The coordinate of the internal surface in floating ring hole in horizontal ordinate is represented, its starting point is reverse centrifugal gap 40, and coupled is smooth section 34, and the end of smooth section 34 is the centrifugal gap 43 of forward, and coupled is transport screw groove 35; The internal surface place sealing oil pressure in floating ring hole in ordinate is represented.
The oil gas pressure differential deltap Pa=Pa-Pf=0.05MPa (a among Fig. 4 of floating ring 23 in normal condition lower seal oil enters, the f point), if the supercharging section that the reverse centrifugal gap between end face 37 and 39 40 constitutes is with the sealing oil 0.05MPa (the b point among Fig. 4) that boosts, then the oil gas pressure reduction of smooth section 34 is Δ Pb=Pb-Pf=0.05+0.05=0.10MPa, because smooth section 34 is relative and gapped with the periphery 44 of axle sleeve boss 36, sealing oil forms oil film wedge in the crack during this time, floating ring is floated, floating ring 23 and axle sleeve 25 automatic centerings in making, remain gapped, the axle sleeve 25 of avoiding and rotating contacts, and this is identical with the effect of interior floating ring in the existing float-ring sealing device; Simultaneously, because sealing oil pressure is higher than sealed gas pressure in the gap, prevent that sealed gas from entering in this gap, guaranteed the safe operation of interior floating ring.The sealing oil that the leakproof section that the centrifugal gap 43 of forward and transport screw groove 35 constitutes will flow out interior floating ring smooth section 34 is together drawn towards the direction pump of smooth section 34, oil gas pressure differential deltap Pb (the b point among Fig. 4) that in design can complete equilibrium smooth section 34.(Pc-Pd) is the pressure reduction in the centrifugal gap 43 of forward among the figure, (Pd-Pe) be that pressure in the transport screw groove 35 reduces, e point among the figure is a bit of zero for oil gas pressure reduction in the transport screw groove 35, the f point is the end points of transport screw groove 35, because the physical length df section that makes transport screw groove 35 in design is greater than the needed minimum length de section of equilibrium oil draught head (Pd-Pe), therefore the internal leakage of sealing oil is zero theoretically.Pressure distribution is seen the curve abcdef of Fig. 4.
The sealing oil pressure decline 0.05MPa of floating ring 23 in entering, in promptly entering during the pressure P f of the sealed gas of pressure Pa ' equal of the sealing oil of floating ring 23 (a ' .f point among Fig. 4), the oil gas pressure differential deltap Pa '=Pa '-Pf=0MPa of floating ring 23 in sealing oil enters, but because the supercharging section that reverse centrifugal gap 40 constitutes is with the sealing oil 0.05MPa (b ' point among Fig. 4) that boosts, then the oil gas pressure reduction of smooth section 34 is Δ Pb '=Pb '-Pf=0+0.05=0.05MPa, because smooth section 34 is relative and gapped with the periphery 44 of axle sleeve boss 36, sealing oil forms oil film wedge in the crack during this time, floating ring is floated, floating ring 23 and axle sleeve 25 automatic centerings in making, remain gapped, the axle sleeve 25 of avoiding and rotating contacts, and this is identical with the effect of interior floating ring in the existing float-ring sealing device; Simultaneously, because sealing oil pressure is higher than sealed gas pressure in the gap, prevent that sealed gas from entering in this gap, guaranteed the safe operation of interior floating ring.The sealing oil that the leakproof section that the centrifugal gap 43 of forward and transport screw groove 35 constitutes will flow out interior floating ring smooth section 34 is together drawn towards smooth 34 direction pump, oil gas pressure differential deltap Pb ' (b ' point among Fig. 4) that in design can complete equilibrium smooth section 34.Therefore the internal leakage of sealing oil is zero theoretically.This moment, the sealing device was in the safe operation scope.Pressure distribution is seen curve a ' b ' c ' d ' ef of Fig. 4.
The pressure decline 0.07MPa of the sealing oil of floating ring 23 in entering, the pressure Pa of the sealing oil of floating ring 23 in promptly entering " when being lower than the pressure P f of sealed gas (a among Fig. 4 " the .f point), be Δ Pa "=Pa "-Pf=(0.02) MPa, negative oil gas pressure reduction has appearred, but since the supercharging section that reverse centrifugal gap 40 constitutes will enter in the sealing oil of floating ring 0.05 MPa that boosts, therefore, at the pressure of smooth section 34 sealing oil is Pb " (b among Fig. 4 " point), the oil gas pressure reduction of smooth section 34 is Δ Pb "=Pb "-Pf=0.05-0.02=0.03MPa, because smooth section 34 is relative and gapped with the periphery 44 of axle sleeve boss 36, sealing oil forms oil film wedge in the crack during this time, floating ring is floated, the axle sleeve 25 of avoiding and rotating contacts, simultaneously, because sealing oil pressure is higher than sealed gas pressure in the gap, prevents that sealed gas from entering in this gap, guaranteed the safe operation of interior floating ring.The sealing device still is in the safe operation scope.The sealing oil of floating ring smooth section 34 was drawn towards the direction pump of smooth section 34 in the leakproof section that centrifugal gap 43 of forward and transport screw groove 35 constitute will flow out together, oil gas pressure differential deltap Pb that in design can complete equilibrium smooth section 34 " (b among Fig. 4 " point), therefore the internal leakage of sealing oil is zero theoretically.Pressure distribution is seen curve a " b " c " d " ef of Fig. 4.
In sum, this combined floating ring sealing device is the combination of floating-ring seal and centrifugal seal and spiral seal, it has three's advantage concurrently: the automatic centering effect of floating-ring seal and the pump of centrifugal seal and spiral seal draw effect, the present invention has improved the adaptability of seal arrangement to the oil gas pressure-difference fluctuation, has enlarged range of safety operation and the internal leakage of sealing oil is reduced.
The radius length in forward and reverse centrifugal gap is 3-20mm, the axial distance 0.3-5mm between the optimum range 5-10mm, two toroidal surfaces, optimum range 0.5-3mm.
Fig. 5 is the longitudinal sectional view of another combined floating ring sealing device.It is characterized in that: the internal surface in interior floating ring hole is made up of reverse acting spiral groove, smooth section and transport screw groove; Wherein, the reverse acting spiral groove is the supercharging section; The reverse acting spiral groove is identical with the internal diameter of smooth section, and the internal diameter of smooth section links to each other with toroidal surface between the two greater than the internal diameter of transport screw groove, forms the endoporus step; Columniform boss structure is arranged on the axle sleeve, and an end face of this boss is relative with above-mentioned endoporus step, and gapped, constitutes the centrifugal gap of forward, and the centrifugal gap of this forward is the part of leakproof section; Transport screw groove on the internal surface in interior floating ring hole then is another part of leakproof section; Smooth section on the internal surface in interior floating ring hole is relative with the periphery of above-mentioned axle sleeve boss and gapped, is the buoyance lift section.
In this combined floating ring sealing device, the porose plate-like end cap 52 in tubbiness seal chamber 51 that the center is porose and center is connected as a single entity, place in the housing 56 of rotating machinery, the running shaft 57 of rotating machinery passes the hole of seal chamber 51 and end cap 52, be fixed with axle sleeve 55 on the running shaft 57, the interior floating ring 53 and the outer floating ring 54 of ring-type are housed on the axle sleeve 55, all gapped between the endoporus of the endoporus of interior floating ring 53 and outer floating ring 54 and the axle sleeve 55, interior floating ring 53 is positioned at the side near sealed gas 58, an end face 59 of interior floating ring 53 is fitted with one heart mutually with the interior edge face 60 of end cap 52, outer floating ring 54 is positioned at the side near atmosphere 61, an end face 62 of outer floating ring 54 is fitted with one heart mutually with the interior edge face 63 of seal chamber 51, it is characterized in that: the internal surface of the endoporus of interior floating ring 53 comprises reverse acting spiral groove 64, smooth section 65, with transport screw groove 66, wherein, reverse acting spiral groove 64 is the supercharging section, reverse acting spiral groove 64 is identical with the internal diameter of smooth section 65, and the internal diameter of smooth section 65 is greater than the internal diameter of transport screw groove 66, link to each other with toroidal surface between the two, form endoporus step 67; Columniform boss structure 68 is arranged on the axle sleeve 55, end face 69 of this boss is relative with above-mentioned endoporus step 67, and it is gapped, constitute the centrifugal gap 70 of forward, the centrifugal gap 70 of this forward is the part of leakproof section, and 66 of the transport screw grooves on the internal surface of the endoporus of interior floating ring 53 are another part of leakproof section; Smooth section 65 on the internal surface of the endoporus of interior floating ring 53 is relative with the periphery 71 of above-mentioned axle sleeve boss 68, and gapped, is the buoyance lift section.
Include reverse acting spiral groove 64 in the present embodiment, it can boost the sealing oil of floating ring 53 in entering, the 0.05MPa that for example boosts, smooth section 65 is relative with the periphery 71 of axle sleeve boss 68, and gapped, sealing oil forms oil film wedge in the crack during this time, floating ring is floated, and floating ring 53 and axle sleeve 55 automatic centerings remain gapped in making, the axle sleeve 55 of avoiding and rotating contacts, and this is identical with the effect of interior floating ring in the existing float-ring sealing device; Simultaneously, because sealing oil pressure is higher than sealed gas pressure in the gap, prevent that sealed gas from entering in this gap, guaranteed the safe operation of interior floating ring.The sealing oil of floating ring smooth section 65 was drawn towards the direction pump of smooth section 65 in the leakproof section that centrifugal gap 70 of forward and transport screw groove 66 constitute will flow out together, oil gas pressure differential deltap Pb (the b point among Fig. 4) that in design can complete equilibrium smooth section 65, (Pc-Pd) is the pressure reduction in the centrifugal gap 70 of forward among the figure, (Pd-Pe) be that pressure in the transport screw groove 66 reduces, e point among the figure is a bit of zero for oil gas pressure reduction in the transport screw groove 66, the f point is the end points of transport screw groove 66, because the physical length df section that makes transport screw groove 66 in design is greater than the needed minimum length de section of equilibrium oil draught head (Pd-Pe), therefore the internal leakage of sealing oil is zero theoretically.
The oil gas pressure differential deltap Pa=Pa-Pf=0.05MPa (a among Fig. 6, f point) of floating ring 53 in normal condition lower seal oil enters, the oil gas pressure differential deltap Pb=Pb-Pf=0.05+0.05=0.10Mpa of smooth section 65, everywhere pressure distribution is seen curve abcdef on the internal surface of the endoporus of interior floating ring 53.
The sealing oil pressure decline 0.05MPa of floating ring 53 in entering, in promptly entering during the pressure P f of the sealed gas of pressure Pa ' equal of the sealing oil of floating ring 53 (a ' among Fig. 6, f point), the oil gas pressure differential deltap Pa '=Pa '-Pf=0MPa of floating ring 53 in sealing oil enters, because the sealing oil of the floating ring 0.05MPa (b ' point among Fig. 2) that boosts in supercharging section-reverse acting spiral groove 64 will enter, then the oil gas pressure reduction of smooth section 65 is Δ Pb '=Pb '-Pf=0+0.05=0.05MPa, oil gas pressure reduction for positive has guaranteed the safe operation of interior floating ring.Everywhere pressure distribution is seen the curve a ' b ' c ' d ' ef among Fig. 6 on the internal surface of the endoporus of interior floating ring 53.
The pressure Pa of the sealing oil of floating ring 53 in entering " less than the pressure of sealed gas time (a among Fig. 2 " .f point), for example, Δ Pa "=Pa "-Pf=(0.02) MPa, when negative oil gas pressure reduction having occurred, because supercharging section-reverse acting spiral groove 64 is with the sealing oil that the enters 0.05MPa (b among Fig. 2 " point) that boosts; then the oil gas pressure reduction of smooth section 65 is Δ Pb "=Pb "-Pf=(0.02)+0.05=0.03MPa, still is positive oil gas pressure reduction, has guaranteed the safe operation of interior floating ring.Everywhere pressure distribution is seen curve a " b " c " d " ef among Fig. 6 on the internal surface of the endoporus of interior floating ring 53.
In sum, this combined floating ring sealing device is the combination of floating-ring seal and centrifugal seal and spiral seal, it has three's advantage concurrently: the automatic centering effect of floating-ring seal and the pump of centrifugal seal and spiral seal draw effect, the present invention has improved the adaptability of seal arrangement to the oil gas pressure-difference fluctuation, enlarged range of safety operation, and the internal leakage of sealing oil is reduced.
In the various embodiments described above, according to the needs of structure, the position of seal chamber and end cap can be exchanged, and for example: the position of 51 and 52 among 21 and 22 among 1 among Fig. 1 and 2, Fig. 3, Fig. 5 can be exchanged.
By above-mentioned all embodiments as seen, when oil gas pressure reduction is reduced to 0 or during negative value, combined floating ring sealing device of the present invention still can normally move, and has enlarged range of operation, and the internal leakage of sealing oil is reduced.The present invention is applicable to dangerous gas such as poisonous, inflammable, explosive to be the shaft end seal of the rotating machinery such as centrifugal compressor, turbine of working gas.
Claims (4)
1. a combined floating ring sealing device comprises seal chamber, end cap, interior floating ring, outer floating ring, axle sleeve; The porose plate-like end cap in tubbiness seal chamber that bottom centre is porose and center is connected as a single entity, place in the casing of rotating machinery, the running shaft of rotating machinery passes the hole of seal chamber and end cap, be fixed with axle sleeve on the running shaft, the interior floating ring and the outer floating ring of ring-type are housed on the axle sleeve, all gapped between interior floating ring hole and outer floating ring hole and the axle sleeve, interior floating ring is positioned at the side near sealed gas, the interior edge face of an one end face and end cap is fitted with one heart mutually, outer floating ring is positioned at the side near atmosphere, the interior edge face of an one end face and seal chamber is fitted with one heart mutually, it is characterized in that: have the supercharging section in the sealing device, buoyance lift section and leakproof section, the supercharging section is positioned at the sealing oil inlet side near floating ring, and the leakproof section is positioned at the close sealed gas side of floating ring endoporus, and the buoyance lift section is positioned between supercharging section and the leakproof section.
2. combined floating ring sealing device according to claim 1, it is characterized in that: the internal surface in interior floating ring hole is made up of reverse acting spiral groove, smooth section and transport screw groove successively, three's internal diameter is identical, relative with the sleeve outer surface that waits external diameter and gapped: wherein, the reverse acting spiral groove is the supercharging section, the transport screw groove is the leakproof section, and smooth section is the buoyance lift section.
3. combined floating ring sealing device according to claim 1, it is characterized in that: columniform boss structure is arranged on the axle sleeve, and an end face of this boss is relative with an end face of a stationary components, and gapped, constitute reverse centrifugal gap, this reverse centrifugal gap is the supercharging section; The internal surface in interior floating ring hole is made up of smooth section and transport screw groove, the internal diameter of smooth section is greater than the internal diameter of transport screw groove, link to each other with toroidal surface between the two, form the endoporus step, this step is relative with another end face of the boss of above-mentioned axle sleeve, and gapped, constitute the centrifugal gap of forward, the centrifugal gap of this forward is the part of leakproof section: the transport screw groove on the internal surface in interior floating ring hole then is another part of leakproof section; Smooth section on the internal surface in interior floating ring hole is relative with the periphery of above-mentioned axle sleeve boss and gapped, is the buoyance lift section.
4. combined floating ring sealing device according to claim 1 is characterized in that: the internal surface in interior floating ring hole is made up of reverse acting spiral groove, smooth section and transport screw groove successively; Wherein, the reverse acting spiral groove is the supercharging section; The reverse acting spiral groove is identical with the internal diameter of smooth section, and the internal diameter of smooth section links to each other with toroidal surface between the two greater than the internal diameter of transport screw groove, forms the endoporus step; Columniform boss structure is arranged on the axle sleeve, and an end face of this boss is relative with above-mentioned endoporus step, and gapped, constitutes the centrifugal gap of forward, and the centrifugal gap of this forward is the part of leakproof section; Transport screw groove on the internal surface in interior floating ring hole then is another part of leakproof section; Smooth section on the internal surface in interior floating ring hole is relative with the periphery of above-mentioned axle sleeve boss and gapped, is the buoyance lift section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00262138 CN2471985Y (en) | 2000-11-16 | 2000-11-16 | Assembled suspended sealer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00262138 CN2471985Y (en) | 2000-11-16 | 2000-11-16 | Assembled suspended sealer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2471985Y true CN2471985Y (en) | 2002-01-16 |
Family
ID=33617490
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 00262138 Expired - Lifetime CN2471985Y (en) | 2000-11-16 | 2000-11-16 | Assembled suspended sealer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2471985Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101324273B (en) * | 2007-06-14 | 2011-01-19 | 湖南崇德工业科技有限公司 | Rotating shaft oil seal |
| CN103939607A (en) * | 2013-01-22 | 2014-07-23 | 天华化工机械及自动化研究设计院有限公司 | Integrated shaft end sealing device |
| CN112377412A (en) * | 2020-11-12 | 2021-02-19 | 湖北同方高科泵业有限公司 | Liquid ring vacuum pump shaft seal structure |
| CN112377411A (en) * | 2020-11-12 | 2021-02-19 | 湖北同方高科泵业有限公司 | Liquid ring type corrosion-resistant plastic vacuum pump |
-
2000
- 2000-11-16 CN CN 00262138 patent/CN2471985Y/en not_active Expired - Lifetime
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101324273B (en) * | 2007-06-14 | 2011-01-19 | 湖南崇德工业科技有限公司 | Rotating shaft oil seal |
| CN103939607A (en) * | 2013-01-22 | 2014-07-23 | 天华化工机械及自动化研究设计院有限公司 | Integrated shaft end sealing device |
| CN103939607B (en) * | 2013-01-22 | 2016-06-29 | 天华化工机械及自动化研究设计院有限公司 | A kind of integration type shaft end sealing device |
| CN112377412A (en) * | 2020-11-12 | 2021-02-19 | 湖北同方高科泵业有限公司 | Liquid ring vacuum pump shaft seal structure |
| CN112377411A (en) * | 2020-11-12 | 2021-02-19 | 湖北同方高科泵业有限公司 | Liquid ring type corrosion-resistant plastic vacuum pump |
| CN112377411B (en) * | 2020-11-12 | 2022-08-05 | 湖北同方高科泵业有限公司 | Liquid ring type corrosion-resistant plastic vacuum pump |
| CN112377412B (en) * | 2020-11-12 | 2022-08-09 | 湖北同方高科泵业有限公司 | Liquid ring vacuum pump shaft seal structure |
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