CN1226641A - High speed centrifugal pump - Google Patents
High speed centrifugal pump Download PDFInfo
- Publication number
- CN1226641A CN1226641A CN 98111853 CN98111853A CN1226641A CN 1226641 A CN1226641 A CN 1226641A CN 98111853 CN98111853 CN 98111853 CN 98111853 A CN98111853 A CN 98111853A CN 1226641 A CN1226641 A CN 1226641A
- Authority
- CN
- China
- Prior art keywords
- impeller
- ring
- seal
- bearing
- sealing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Abstract
A high-speed centrifugal pump is composed of pump casing, blade wheel and its axle, bearing and its cooling and lubricating unit, bearing seal, chevron pre-seal of blade wheel between blade wheel and front end cover, post-seal of blade wheel between blade wheel and its axle, and the seal for water outlet of blade wheel. It features that said seals form a combination of non-contact seal composed of spiral blocking pump and shielded spiral pump with contact-type mechanical seal to obtain excellent seal of blade wheel.
Description
The present invention relates to centrifugal pump, particularly the seal arrangement of high speed centrifugal pump.
Existing centrifugal pump has high speed pump and conventional pump.The single suction single stage centrifugal pump is arranged, multistage centrifugal pump, centrifugal sand pump, centrifugal slurry, the high-speed eddy pump ..., usually by pump case and impeller wherein, impeller shaft that links to each other with power transmission and bearing thereof, formations such as the preposition sealing of impeller, rearmounted sealing and bearing seal.
The postposition sealing of impeller, promptly impeller and the impeller shaft impeller shaft sealing of company headquarters mutually mainly contain packing seal, mechanical seal, sub-propeller sealing.Wherein mechanical seal, as announced among the EP484305 by (1) stationary ring (stationary ring), rotating ring (rotating ring) the contact-type frictional sealing pair that partners; (2) based on the compensation damping mechanism of elastic element cylindrical screw compressing spring (or magnetic element); (3) auxiliary seal ring; (4) driving mechanism four parts that rotating ring and axle are rotated together constitute.The sub-propeller sealing, as announcing among the CN92215983.1, by back blade, sub-propeller, fixed guide vane, cavity, axle sleeve, stage clip, stop component such as sealing and form, wherein the fluid that is driven in the seal chamber by back blade and sub-propeller is made high speed rotating and produces centrifugal force to reduce or eliminate leakage pressure reduction.Be the primary component that produces sealing load, its structure has enclosed, semi-open type, combined type.The characteristics of above-mentioned rearmounted sealing are mixed sealing by mechanical seal or by what sub-propeller and mechanical seal were formed, stop the leakage of water-pumping chamber's fluid along the impeller shaft running clearance.Its sealing configuration all belongs to the sealing of contact friction formula.Above-mentioned seal operation characteristics are that lift is high more, filler in the stuffing box then, or the mechanical seal friction pair is just transferred tightly more.Its shortcoming is that the filling of gland sealed filler also can not cause seize at that time, the excessively heated axle accident, and mechanical seal is transferred tightly more, the big more then power consumption of its tight more surface friction drag of sealing is high more, the sealing that has also need be supplied with cooling water, and its sealing material consumption is big, thereby has limited the raising of pump shaft rotating speed.In addition, its complex structure, the accuracy of manufacturing height, particularly the manufacture difficulty of high-speed mechanism sealing is bigger, and maintenance difficulty is big, the manufacture cost height.The power consumption of sub-propeller sealing configuration is also higher than mechanical seal, packing seal, accounts for the 5-15% of air horsepower.
The preposition sealing of impeller, it is the sealing of impeller suction side and pump case, the impeller of existing centrifugal pump is based on double shrouded wheel, there is an evagination pipe in the inlet of impeller, constitute seal arrangement with the stationary seal ring in the front cover of pump case, the preposition sealing of high-speed eddy pump, as announcing among the EP484305, outwards two steps of outstanding section and the running clearance that the pump case front cover forms constitute by suction eye.Preposition sealing is divided into suction chamber with the pump case inner chamber, and pumping chamber.Be characterized in that the fluid that leaks to suction eye in the water-pumping chamber is the simple seal ring that constitutes by by running clearance, or stepped sealed ring reduces leakage rate.During impeller work, produce a negative pressure of vacuum in the fluid suction side, produce a malleation, increase with suction pressure reduction at the fluid of pumping chamber with the impeller rotation at the fluid exhaust end, be subjected to the effect of pull of vacuum, preposition sealing ring gap enters suction chamber and forms a return loss segment fluid flow from the suction side.When being mixed with the solid sand grains of some in the fluid, these solid sand grains pass seal clearance with reflux fluid, can quicken the wearing and tearing of preposition sealing, cause the circulation leakage flow to increase, and directly draw suction journey, lift and the flow efficient of ringing pump, shorten life cycle.This shows that the shortcoming of existing preposition sealing is that the circulation leakage is difficult to eliminate.Therefore, stoping circulation to be leaked becomes the important topic that current centrifugal pump manufacturer faces, and also is one of important means that improves pump shaft useful horsepower.
Given this, the object of the present invention is to provide the good high speed centrifugal pump of a kind of its impeller seals, and a kind of bearing of its impeller shaft further is provided and seals good high speed centrifugal pump.
The present invention is according to the volute pump theory, employing is provided with the formula sealing of being put in prison between impeller and its front cover, at impeller and adopt between the end cap thereafter by spiral retardance pump and shielding volute pump and constitute non-contact sealing, the contact seal of recombinant mechanical type, volute pump is set between impeller drain opening and pump case seals the purpose that realizes good impeller seals; Further force the theory of cooling and lubricating according to gear oil pump, employing coaxial-type volute pump is to rolling bearing or ladder sliding type bearing coercively fed cutting oil and adopt the contactless volute pump of contact-type mechanical seal combination that is made of stator and rotor to seal the purpose that realizes good bearing and sealing thereof.
High speed centrifugal pump of the present invention (referring to accompanying drawing), comprise pump case and on front cover (3), impeller in the pump case (8) and impeller shaft (21) thereof, the preposition sealing of impeller, the rearmounted sealing of impeller, the sealing of impeller drain opening, the bearing of impeller shaft and cooling and lubricating device, bearing seal, it is characterized in that the preposition anti-blocking spiral (11) that is sealed with the front end of impeller (8) of above-mentioned impeller, between impeller and front cover, have by at least one pair of seal ring that matches (13) and seal groove (12,14) constitute with the formula of being put in prison of giving the indentation runner that water channel (22) is communicated with of sealing usefulness and seal; Above-mentioned impeller postposition is sealed with the rotor mechanism that is sleeved on the impeller shaft, with the stator (40) that links with pump case, above-mentioned rotor mechanism has the rotator seat (23) of the anterior tubular that matches with impeller, the rear sleeve of rotator seat is equipped with spring adjusting part (25), with cooperating annular Sealing panoramatic head (28) is housed with spiral, ladder axial region at the Sealing panoramatic head is equipped with O type seal ring (30), with the reducing stuffing box gland (31) that matches with rotator seat, main spring (32) is arranged between spring adjusting part and Sealing panoramatic head, there is water conservancy diversion slope (34) rear end of the front portion of rotator seat, and spiral chute (35), recessed circular groove (36) is arranged on the fore ear end face, on water conservancy diversion slope and spiral chute, be fitted with the radome (37) of annular, the water conservancy diversion commutation wing (38) that in this radome match in Zhou Youyu water conservancy diversion slope, periphery has screw wing (39), said stator is the clearance type that the gap that communicates with impeller cavity is arranged with the front portion of the rotator seat of rotor mechanism and cooperates, be fitted with the constriction (41) in week in the stepped shaft in the front-end face of stator week, and the formation fluid reflux blocks pump chamber (42) between the screw wing of constriction and above-mentioned radome, the end face of the rear end of stator matches with above-mentioned O type seal ring, the clasp (43) that the above-mentioned circular groove of Zhou Youyu matches in the rear end; Above-mentioned impeller drain opening be sealed with the front side of the drain opening of impeller and rear side be symmetry and with spiral chute (15,17) and water conservancy diversion slope (16,18) of being communicated with for water channel (22,45), have that being sleeved on the impeller matches with spiral chute and water conservancy diversion slope respectively merges two radomes (9,10) that constitute reflection angle (53,54) respectively, the commutation fin (52) that pumps up water is arranged on the radome angle.
Above-mentioned bearing and cooling and lubricating device are for forcing the cooling and lubricating rolling bearing structure, cartridge housing (61) is arranged, its periphery of impeller shaft in cartridge housing (21) support has the left hand screw of suction inlet in the alternate formation (68) and the double helical wheel of middle suction (67) of right-hand screw, left and right side at the double helical wheel of middle suction respectively has rolling bearing (65,66), and there is the oil inlet hole (64) that communicates with the oil storage pool (63) of lubricant oil at the middle part of cartridge housing.
Above-mentioned bearing and cooling and lubricating device are for forcing cooling and lubricating ladder sliding bearing structure, left ladder shaft part and right ladder shaft part that impeller shaft is arranged, the conical surface that links to each other successively from inside to outside (72 that symmetry is arranged on left side ladder shaft part and the right ladder shaft part, 78), straight cylindrical surfaces (73,79), conical surface (74,80), straight cylindrical surfaces (75,81), conical surface (76,82), the left ladder axle sleeve (70) that links to each other and match with above-mentioned left and right sides ladder shaft part respectively with the left and right side of bearing spider (69) is respectively arranged, with adjustable right ladder axle sleeve (71), the left and right sides end face of above-mentioned bearing spider has recessed left annular groove (85) and right annular groove (86) respectively, thereby all within it respectively formation in the left interior ring (87) and the right side encircles (88), the middle part of the bearing spider between the ring in the ring and the right side in respect to a left side, the oil inlet hole (64) that is communicated with oil storage pool (63) is arranged, between the ladder shaft part of the left and right sides of impeller shaft, have respectively with a left side in ring and right in encircle corresponding helix structure left-handed helical wheel (90) and right hand helix take turns (91), left-handed helical wheel and right hand helix wheel form the middle suction inlet (93) that is communicated with oil inlet hole separately, between left-handed helical wheel and right hand helix wheel encircles in ring right respectively and in the left side, the left side shielding baulk ring (96) and the right baulk ring (97) that shields that respectively have its transverse section of constituting by interior ring and outer shroud to take the shape of the letter U, the interior ring (98) of above-mentioned left side shielding baulk ring cooperates with left-handed helical wheel, the periphery of its outer shroud has left-handed zigzag fashion spiral chute and matches with left annular groove, the interior ring (99) of above-mentioned right shielding baulk ring cooperates with the right hand helix wheel, and the periphery of its outer shroud has dextrorotation zigzag fashion spiral chute and matches with right annular groove.
Above-mentioned bearing seal is in the bearing outside, the sealed stator (104,113) of the tubular that having links to each other with cartridge housing is the L transverse section, canned rotor seat (105,115) with the annular that is the transverse section of falling L that links to each other with impeller shaft, and be communicated with oil drainage hole (107,117) by the two Seal cage that constitutes, cooperate annular is housed anti-to let out wheel (108), have and prevent to let out with spiral on the canned rotor seat and take turns the reducing seal ring (109) that matches, anti-letting out has the O-ring seals (110) that matches with sealed stator on the wheel, main spring (111) is arranged between sealed stator and canned rotor.
Above-mentioned pump case has housing (1), and with front cover (3) that links to each other with the front end and back end of housing respectively and rear end cover (4), having matches with the periphery of impeller respectively constitutes the pump chamber isolating ring (5,6) of isolated pumping chamber.
The outside end face of the bigger diameter end of above-mentioned rotator seat (23) has rotor seal ring (33), its miner diameter end has adjustment nut (24), above-mentioned O V-shaped ring (30) has fixed block (29), above-mentioned spring adjusting part (25) has the positioning screw (26) that links to each other with rotator seat, between the periphery of above-mentioned stator (40) outer rim and the pump case seal stator circle (48) is arranged.
The right ladder shaft part of above-mentioned impeller shaft has the fastening screw nut (77) that is the multidiameter shaft shape of scyewed joint with impeller shaft, has with scyewed joint in the said right ladder axle sleeve (71) and adjusts the fastening screw nut (84) that cover (83) matches.
High speed centrifugal pump of the present invention is a single suction single-stage high-speed centrifugal pump, can replace multistage centrifugal pump, finishes high-lift water delivery engineering, also can take out sand, inhale to become silted up and carries out operation such as high-pressure wash, and a pump is used more.
Said structure of the present invention makes it have following advantage and effect.
One, the rearmounted sealing of impeller of the present invention is adopted by spiral retardance pump, and the shielding volute pump constitutes the noncontact seal structure, recombinant mechanical type contact static seal structure.Compare with existing mechanical seal for pump and sub-propeller sealing, have in work replacing multistage centrifugal pump, its fluidic seal ability is adjusted automatically with rotation speed change, the static sealing ability can be adjusted by spring adjusting part, and its frictional loss is few, and life cycle is long, safeguard simple, material there is not specific (special) requirements, highly versatile, operating cost is low relatively.In addition, this sealing configuration also can be used for the power ship stern shaft seal gland.
Two, the preposition sealing of impeller of the present invention is adopted at suction eye anti-blocking spiral to be set, and on impeller front end and pump case front cover the seal ring of corresponding cooperation, the labyrinth seal structure that seal groove constitutes is set.Stop the fluid in the pump case pumping chamber or directly leak to suction eye for backwash is fluid-encapsulated outward, thereby improve the preposition anti-leakage seal performance of impeller.
Three, the axial shield volute pump sealing configuration of the drain opening of impeller of the present invention is compared with existing impeller of pump, has the function that leak fluid is converted to the jet fluid-tight, and the circulation leakage rate at impeller front end suction port place is effectively controlled; When the big fluid of pumping sand content; the axial shield volute pump will be outward to convert high-speed jet to fluid-encapsulated for fluid-encapsulated; not the going to pot property wearing and tearing of protection impeller periphery; in addition; the axial shield volute pump forms the reflection fluid and stops seal ring and protect the running clearance of impeller not to be subjected to the intrusion erosive wear of solid impurity in the impeller operation gap, keep the water conservancy project efficient of centrifugal pump.
Four, bearing of the present invention and cooling and lubricating device are the theories of forcing cooling and lubricating according to gear oil pump, adopt the coaxial-type volute pump that bearing is forced cooling and lubricating.When the rotating speed of impeller shaft is below 8000 rev/mins, adopts rolling bearing structure, and inhale double volute pump in adopting and impeller shaft rotates synchronously; When the rotating speed of impeller shaft more than 8000 rev/mins the time, adopt successive incremental tiers formula bearing structure, eliminating the axial float of bearing, and adopt the axial double double-layer spiral pump of middle suction by two groups of single double-layer spiral pumps combinations of single suction.Cutting oil in the oil storage pool is sucked side by side after bearings at both ends is carried out the pressure lubrication cooling,, send oil storage pool again back to, realize the pump circulation cooling and lubricating again through bearing, bearing seal.Have and carry out automatic cooling and lubricating at random, guarantee the lubricated and cooling of bearing of turning round, thereby help reducing the manufacture cost of centrifugal pump.In addition, the single double-layer spiral pump structure of above-mentioned single suction can be used as the volute pump vane rotor.
Five, the pump housing of combined type pump case of the present invention, by two pump chamber isolating rings it is divided into two isolated pumping chambers, impeller operation chamber, and constitute the radial seal of impeller, form the running chamber of impeller again with front cover and rear end cover, and communicate with isolated pumping chamber.Compare with the integrated type pump housing of the pump case of existing centrifugal pump; have after fluid that impeller pumps enters pumping chamber; under the shielding action of pump chamber spacer ring; the running clearance that is difficult for the backspace impeller; and when the big fluid of pumping sand content; fluid-encapsulated by outer confession in impeller radial seal interval, provide and stop the protected fluid cover, guarantee the advantage that the impeller appearance is not is not worn and torn.
Below, with embodiment and accompanying drawing thereof the present invention is further described again.
Brief description of drawings.
Fig. 1 is the structural representation of a kind of high speed centrifugal pump of the present invention.
Fig. 2 is the structural representation of the rearmounted sealing of impeller of Fig. 1.
Fig. 3 is the stereogram of front portion of the rotator seat of Fig. 2.
Fig. 4 is the stereogram of the radome of Fig. 2.
Fig. 5 is the structural representation of the ladder sliding type bearing means of Fig. 1.
Fig. 6 is the structural representation of the bearing seal of Fig. 1.
Fig. 7 is the structural representation of the impeller of Fig. 1.
Fig. 8 is the structural representation of radome of the impeller of Fig. 1.
Embodiment 1
A kind of high speed centrifugal pump of the present invention, as shown in drawings.Constitute by pump case, impeller, impeller shaft, front cover, the preposition sealing of impeller, the rearmounted sealing of impeller, the sealing of impeller drain opening, bearing and cooling and lubricating device, bearing seal etc.
Above-mentioned pump case, as shown in Figure 1, be fabricated structure, the housing 1 that the scroll casing shape that is common centrifugal pump formula is arranged, have a surplus liquid discharge orifice and discharge the bolt 2 of surplus liquid of lower part of frame, the front end of housing 1 is fitted with the front cover 3 that encircles dish type with screw, and its rear end is fitted with the rear end cover 4 that is tubular with screw.Front and rear in the housing has the pump chamber isolating ring 5,6 that matches with week in the housing respectively, the interior week of two pump chamber isolating rings matches with the periphery of impeller, thereby constitute two isolated pumping chambers, and formation is the current drainage seam 7 of symmetry with the impeller drain opening between two isolated pumping chambers.
Above-mentioned pump chamber isolating ring is kept apart the axial limit of pumping chamber in the pump case and impeller drain opening both sides, constitute the axial operation gap, impeller is equal to or slightly less than the width that current drainage is stitched with the thickness of the annular jet body that centrifugal force is discharged, when the impeller high speed rotating, the drain opening that distributes on circumference of impeller is discharged high speed centrifugation annular jet body, passes the current drainage seam.Have the fluid of stopping isolated pumping chamber and return the function of letting out.Promptly become working fluid after entering isolated pumping chamber, under the obstruction of continuous centrifugal annular jet stream body, the fluid that enters isolated pumping chamber is difficult for getting back to the impeller operation gap from the current drainage seam, thereby constitutes the radial seal of the impeller that is made of centrifugal annular jet.
Above-mentioned impeller 8 shown in Fig. 1,7,8, is fabricated structure, is fitted in the pump case, and by impeller 8, radome 9,10 is formed.The similar common centrifugal pump impeller structure of the main body of above-mentioned impeller 8, the front portion of impeller is a minor diameter, its periphery is shaped on anti-blocking spiral 11; The rear portion of impeller is a large-diameter portion, has in the front side at the rear portion of impeller to be stepped shaft that arrange and seal groove 12, seal ring 13, seal groove 14 that join successively to periphery from the middle part; Be shaped on the spiral chute 15 and the water conservancy diversion slope 16 that is toroidal of bull at the front end of impeller rear portion periphery, its rear end is shaped on symmetrical with it spiral chute 17 and water conservancy diversion slope 18, a plurality of uniform water conservancy diversion fins 19 are arranged in the impeller, outer end between the water conservancy diversion fin is a drain opening 20, and the sweepback angle α that drain opening is launched backward is 20～40 °.The guide vane front end is to making the convex arc transition wall between the drain opening, the current drainage channel rear wall is made the concave arc training wall.After entering the fluid that is axial flow in the pipeline and entering suction eye, under the guiding of convex arc transition wall, progressively carry out the transition to radially centrifugal flow by axial flow, the cavitation erosion harm that eliminate fluid produces because of commutation suddenly is to adapt to the requirement that impeller runs up.
Above-mentioned impeller shaft 21 is multidiameter shaft shape, and its front end relies on scyewed joint and impeller center to be connected.
Above-mentioned front cover 3, as shown in Figure 1, the middle part is a fluid inlet, there is seal groove 12, seal ring 13, seal groove 14, spiral chute 15 corresponding identical seal rings, seal groove, seal ring, the seal groove with above-mentioned impeller 8 its rear end, what the sealing usefulness that is made of radially screw that is connected in front cover and axial bore was arranged gives water channel 22, above-mentioned radially screw can be connected with the pressure water source (not shown), and axial bore communicates with the spiral chute 15 of impeller.Front cover is fitted in front cover on the housing 1 of impeller front side with the through hole on its dish edge of a plurality of uniform bolt-throughs.
The preposition sealing of above-mentioned impeller, shown in Fig. 1,7,8, anti-blocking spiral 11 by the front portion of impeller 8, constitute with match by the seal groove 12 of impeller 8, seal ring 13, seal groove 14, with corresponding seal ring, seal groove, seal ring, seal groove on the front cover labyrinth seal structure that forms the indentation runner and the water channel 22 of giving that is communicated with the indentation runner.Stop the fluid in the pump case pumping chamber and directly leak the preposition anti-leakage seal performance of raising impeller outward for backwash is fluid-encapsulated to suction eye with this.
The rearmounted sealing of above-mentioned impeller shown in Fig. 1,2,3,4, has the rotor mechanism that is sleeved on the impeller shaft 21, and is inlaid in the pump chamber isolating ring 6 of pump case and the stator between the rear end cover 4.It is that major diameter, middle part and rear portion are the rotator seat 23 of the cascade tubular of minor diameter that above-mentioned rotor mechanism has anterior, the adjustment nut 24 useful scyewed joint suit in termination, rear portion of rotator seat, that be used to adjust rotator seat, the place ahead of adjusting nut is set with spring adjusting part 25, has on the spring adjusting part and itself and rotator seat can be the positioning screw 26 that is fixedly linked.Surface at the middle part of rotator seat is shaped on spiral 27, relies on this spiral, cooperates with spiral the Sealing panoramatic head 28 that the front side is the annular that multidiameter shaft, rear side match with spring adjusting part is housed.On the middle stage of the ladder axial region of Sealing panoramatic head, be fixed with O type seal ring 30 with Bond or fixed block 29.On the inner step of the ladder axial region of Sealing panoramatic head, the bigger diameter end of suit reducing stuffing box gland 31, the miner diameter end of reducing stuffing box gland are sleeved on the rotator seat 23, constitute the anti-mechanism of letting out of guiding spiral.Between Sealing panoramatic head 28 and spring adjusting part 25, main spring 32 is housed.In the annular groove of the front-end face of the major diameter front portion of rotator seat 23 rotor seal ring 33 is housed.Periphery in the rear end of the front portion of rotator seat is made water conservancy diversion slope 34 and spiral chute 35, and the end face in this rear end is shaped on recessed circular groove 36.Be set with annular radome 37 on water conservancy diversion slope and spiral slot part, the tubaeform oral area in week has the water conservancy diversion commutation wing 38 that matches with water conservancy diversion slope 34 in the radome, and periphery has the screw wing 39 that distributes circlewise.Above-mentioned spiral chute 35, water conservancy diversion slope 34 with radome 37 combinations, constitutes the shielding volute pump.Said stator 40 matches with the above-mentioned shielding volute pump of the major diameter front portion of rotator seat 23, the constriction that is fitted with the stepped shaft inner chamber interior week 41 of the front end of stator, and between the screw wing 39 of constriction and above-mentioned radome, form fluid reflux retardance pump chamber 42, thereby constitute spiral retardance pump by the screw wing of stator and radome; The end face of stator rear end matches with above-mentioned O type seal ring 30, clasp 43 left-hand threads in week are in above-mentioned circular groove 36 in the rear end, constitute the pump case of helping of above-mentioned shielding volute pump, the front-end face of stator peripheral portion has rectangle ring cavity 44, ear end face have with rear end cover 4 on the water conservancy diversion annular groove 46 of communicating for water channel 45 of sealing usefulness, the flowing hole 47 that is communicated with rectangle ring cavity and water conservancy diversion annular groove is arranged.Between the rear end cover 4 of the periphery of stator 40 outer rims and pump case, be embedded with seal stator circle 48.
The working principle of the rearmounted sealing of impeller: place the O type seal ring 30 on the Sealing panoramatic head 28, under the tension force effect of main spring 32, move along spiral 27 rotations and forward end, O type seal ring 30 on the Sealing panoramatic head is contacted with the ear end face of stator 40, obtain the static or sealing function when slowly running of impeller shaft.When impeller shaft 21 high speed rotating, Sealing panoramatic head 28 is with the impeller shaft high speed rotating, obtain higher centrifugal inertia force, be enough to overcome the revolution tension force of main spring, the Sealing panoramatic head rotates and moves rearwards to spring adjusting part 25 along spiral 27, and the O type seal ring 30 on it disengages with the rear end of stator 40; The screw wing 39 of while radome 37 peripheries, in fluid reflux retardance pump chamber 42 with the reverse blowback of leak fluid, form helical resistive viscous flow body reduced pressure sealing circle, after letting out the blocked decompression of slip-stream body, flowing through shields volute pump suction port 49, and it is interior along spiral chute 35 reverse blowbacks that the conductively-closed volute pump sucks radome, the water conservancy diversion commutation wing 38 on the angle of radome, be the oblique angle and inject the running clearance of rotor mechanism, form reflection fluid wedge-like seal ring.The rearmounted sealing of above-mentioned impeller obtains non-contact dynamic pressure fluid-tight function by helical resistive viscous flow body reduced pressure sealing circle and reflection fluid wedge-like seal ring.
Above-mentioned impeller drain opening sealing, as Fig. 1,7, shown in 8, front-end and back-end that are set in impeller and radome 9 and the radome 10 that matches with the spiral chute 15 and the spiral chute 17 of impeller are respectively arranged, this two radome all ringwise, have in week in it symmetrical and respectively with the water conservancy diversion slope 16 and the water conservancy diversion slope 18 corresponding flaring angles of impeller, the commutation that on angle, the is evenly equipped with a plurality of bar shapeds radially fin 52 that pumps up water, thereby between radome 9 radomes 10 and water conservancy diversion slope 16 and water conservancy diversion slope 18, form fluid-encapsulated reflection angle 53 and reflection angle 54 respectively.Working fluid enters impeller 8 sweepback angle current drainage channels along flowing to shown in Fig. 7 arrow.Above-mentioned spiral chute 15,17 respectively with radome 9,10, with the commutation of the radome fluid reversing groove that fin 52 and impeller angle form that pumps up water, constitute each axial shield volute pump of the impeller front-end and back-end of impeller drain opening both sides, form the reflection fluid-tight of impeller drain opening.The running clearance of the outer ring cavity in the front cover 3, with the axial shield pump intake 57 of impeller front end, the circulation suction chamber that retardance step 59 constitutes the axial shield volute pump of front end, the running clearance of the outer ring cavity in the rear end cover 4 is with the axial shield pump intake 58 of impeller rear end, the circulation suction chamber that retardance step 60 constitutes the axial shield volute pump of rear end.
The working procedure of impeller drain opening sealing: when centrifugal pump pumping free from admixture fluid, when impeller 8 rotary works, the part working fluid flows to the axial shield spiral pump intake 57,58 of impeller along the running clearance 55,56 of impeller periphery, under the helping of retardance step 59,60, by the reverse blowback of this pump, flow to reflection angle 53,54, place commutation in the reflection angle wing 52 that pumps up water that fluid is injected running clearance 55,56 along the oblique angle of reflection angle.When pumping pasty material fluid or when containing the sand flow body; send into the fluid-encapsulated of no solid impurity for water channel 22,45, water conservancy diversion annular groove 46 by sealing; form aforesaid reflection fluid wedge-like seal ring; the working fluid that stops impeller to pump enters running clearance; and running clearance carried out backwash, not the going to pot property wearing and tearing of running clearance of protection impeller.
Above-mentioned bearing and cooling and lubricating device are installed in the rear end of impeller shaft 21, and wheel speed can adopt pressure lubrication cooling rolling bearing as shown in Figure 1 below 8000 rev/mins the time.This bearing has the cartridge housing 61 that is tubular, and the rear end of cartridge housing is connected with bolt and cartridge housing support 62, and the front end of cartridge housing is connected with the rear end cover 4 of bolt and pump case.The oil inlet hole 64 that communicates with the oil storage pool 63 of splendid attire lubricating cooling oil is arranged at the middle part of cartridge housing.Between cartridge housing two end part and impeller shaft 21, common rolling bearing 65 and rolling bearing 66 respectively are housed, the periphery of the support of the impeller shaft between above-mentioned two rolling bearings in cartridge housing has the double helical wheel 67 of the middle suction that has left hand screw and right-hand screw to constitute by side face, makes annular groove and suction inlet 68 in forming between left hand screw and right-hand screw.The double helical wheel of middle suction can be made one whole, is fixed on the impeller shaft; Also can make the separation member composite structure, constitute by the left-handed helical wheel and the right hand helix wheel that are fixed in successively on the impeller shaft.The double helical wheel 67 of middle suction on the impeller shaft 21 is inhaled double volute pump in constituting with cartridge housing 61.
The working procedure of above-mentioned pressure lubrication cooling rolling bearing and cooling and lubricating device: when the double volute pump 67 of middle suction rotates with impeller shaft 21, suck the lubricating cooling oil of oil storage pool 63 by the oil inlet hole 64 of cartridge housing 61, the rolling bearing 65 of right-hand member and rolling bearing 66 provide lubricating cooling oil left, the heat that rolling bearing is produced during with running is taken away, and reaches the purpose that prolongs bearing life.
When wheel speed more than 8000 rev/mins the time, bearing and cooling and lubricating device can adopt pressure cooling ladder sliding type bearing as shown in Figure 5.The cartridge housing of this bearing by the ring bearing spider 69 that base is arranged and about the end left ladder axle sleeve 70 and the right ladder axle sleeve 71 that connect firmly with bolt constitute.The support of the impeller shaft 21 that this two axle sleeve is supported is left ladder shaft part and right ladder shaft part, left side ladder shaft part has conical surface 72 continuous successively from inside to outside and that diameter reduces, there is spiral fluted straight cylindrical surfaces 73 on the surface, conical surface 74, there is spiral fluted straight cylindrical surfaces 75 on the surface, the conical surface 76 of throttling closed-entry, the useful scyewed joint of right multidiameter shaft is fitted in the fastening screw nut 77 that is ladder axle sleeve shape on the impeller shaft 21, forms conical surface 78 continuous successively from inside to outside and that diameter reduces, there is spiral fluted straight cylindrical surfaces 79 on the surface, conical surface 80, there is spiral fluted straight cylindrical surfaces 81 on the surface, the conical surface 82 of throttling closed-entry.Above-mentioned left ladder axle sleeve 70 is tubular, and its inner chamber matches with left ladder shaft part, and left multidiameter shaft overlaps the flange plate that the rear end cover 4 of useful bolt and pump case is connected; Above-mentioned right ladder axle sleeve 71 is also cylindrical, is fitted with the adjustment cover 83 that its inner chamber matches with right multidiameter shaft with thread joined structure in the cylinder, is fitted with and adjusts the fastening screw nut 84 that cover joins in cylinder, thereby constitute adjustable right ladder axle sleeve.At the left and right sides of above-mentioned bearing spider 69 end face, recessed left annular groove 85 and right annular groove 86 are arranged respectively, thereby form ring 87 in the left side respectively within it week, with right interior ring 88, the middle part of the bearing spider between the ring in the ring and the right side in respect to a left side, the oil inlet hole 64 that useful adapter 50 is communicated with the oil storage pool 63 of splendid attire cutting oil, useful flat key 89 is packed on the impeller shaft 21 between the ladder shaft part of the left and right sides of impeller shaft 21, and encircle left-handed helical wheel 90 and the right hand helix wheel 91 that corresponding surface is a helical groove structure respectively with in the interior ring in a left side and the right side, between left-handed helical wheel and the right hand helix wheel every the cushion block 92 that the less annular of diameter is housed, thereby form the middle suction inlet 93 is communicated with oil inlet hole 64, and take turns 91 formation shoe cream rooms 94 respectively and between the left ladder axle sleeve of cartridge housing and the right ladder axle sleeve at left-handed helical wheel 90 and right hand helix, 95.Left-handed helical wheel and right hand helix wheel respectively and in the left side ring and right in encircle between, left side shielding baulk ring 96 and right shielding baulk ring 97 that its transverse section of being made of interior ring and outer shroud takes the shape of the letter U are housed to each phase embedding, the interior ring 98 of above-mentioned left side shielding baulk ring cooperates with left-handed helical wheel 90, the periphery of its outer shroud has left-handed zigzag fashion spiral chute and matches with left annular groove 85, the interior ring 99 of above-mentioned right shielding baulk ring cooperates with right hand helix wheel 91, and the periphery of its outer shroud has dextrorotation zigzag fashion spiral chute and matches with right annular groove 86.
Above-mentioned left and right sides ladder shaft part constitutes left and right sides cascade sliding bearing with left ladder axle sleeve 70 and right ladder axle sleeve 71 respectively.The conical surface that left and right sides ladder shaft part matches with left and right sides ladder axle sleeve is used to the axial float that stops impeller shaft to be produced in the ladder axle sleeve, the conical surface of the conical surface 76,82 of multidiameter shaft outer end, the left and right sides and corresponding left and right sides ladder axle sleeve constitutes the expenditure and pressure reducing.The interior ring 98 of above-mentioned left side shielding baulk ring 96 cooperates with left-handed helical wheel 90, constitutes left internal layer shielding volute pump; The left-handed zigzag fashion spiral fluted outer shroud that has of left side shielding baulk ring 96 matches with left annular groove 85, constitutes the outer retardance in left side volute pump.Left side internal layer retardance volute pump and the combination of the outer retardance in left side volute pump constitute the single double-layer spiral pump of left single suction.The interior ring 99 of above-mentioned right shielding baulk ring 97 cooperates with right hand helix wheel 91, constitutes right internal layer shielding volute pump; The dextrorotation zigzag fashion spiral fluted outer shroud that has of right shielding baulk ring 97 matches with right annular groove 86, constitutes right outer retardance volute pump.Right internal layer retardance volute pump and the combination of right outer retardance volute pump constitute the single double-layer spiral pump of right single suction.Double double-layer spiral pump is inhaled in the single double-layer spiral pump of above-mentioned left single suction, cushion block 92, the single double-layer spiral pump combination of left single suction in the formation.
The working procedure of above-mentioned pressure cooling ladder sliding type bearing and cooling and lubricating device: the double double-layer spiral pump of middle suction rotates with impeller shaft 21, left and right sides internal layer shielding volute pump is through oil inlet hole 64, middle suction inlet 93 sucks cutting oils and enters shoe cream room 94 to two ends respectively, 95, cutting oil is along the running clearance of cascade sliding bearing, to first section conical surface 72, after 78 shaft parts carry out pressure lubrication, enter first section straight cylindrical surfaces 73, the bearing play section of 79 shaft parts, this straight cylindrical surfaces 73, the lubricant oil that the spiral chute on 79 surfaces is pressed into pressure under centrifugal action, shape is thrown to left and right sides ladder axle sleeve 70 in the shape of a spiral, 71 inwall forms the centrifugal pressure oil film wedge and impeller shaft is lifted, lubricant oil revolves under row's active force in pump pressure and spiral fluted, be pressed into second section conical surface 74, behind 80 shaft parts, enter second section straight cylindrical surfaces 75, the bearing play section of 81 shaft parts, through the 3rd section conical surface 76, the throttling reducing of 82 shaft parts is discharged, and lubrication principle is with aforementioned identical.Shoe cream room 94,95 cutting oil, because of cascade bearing operation gap after shrinking one by one, at shoe cream room 94,95 form pump pressure, make the part cutting oil along the running clearance 100 that forms respectively between left and right sides helical wheel and the left and right sides ladder axle sleeve, 101, be back to above-mentioned about the suction port separately 102 of outer shielding volute pump, 103, ring 87 in the left side of bearing spider 69, under the obstruction of right interior ring 88, respectively by about outer shielding volute pump blowback running clearance 100 again, 101 and form fluid retardance seal ring, stop cutting oil to reflux to middle suction inlet 93.
Above-mentioned bearing seal shown in Fig. 1,6, has the fore bearing sealing and the rear bearing sealing that match with the front end and back end of above-mentioned bearing and cooling and lubricating device.
Fore bearing is sealed with scyewed joint and is packed in the sealed stator 104 that links to each other in the rear end cover 4 rear end inner chambers of above-mentioned pump case and with cartridge housing and be the annular of L transverse section.The canned rotor seat 105 that is packed in the tubular that is the transverse section of falling L on the impeller shaft 21 is arranged in the sealed stator, reach the Seal cage 106 that constitutes by the two cooperation, the oil drainage hole 107 that is communicated with Seal cage is arranged on the barrel of rear end cover 4 rear ends, and oil drainage hole is communicated with oil storage pool 63 through pipeline 51.On canned rotor seat 105, cooperate the anti-wheel 108 of letting out that annular is housed, helical tooth is arranged in anti-periphery of letting out wheel with spiral.Have larger diameter end with anti-let out that wheel matches, smaller diameter end matches with the canned rotor seat reducing stuffing box gland 109, be embedded with 0 RunddichtringO 110 that is contact matching with sealed stator in the annular seal groove on the anti-front-end face of letting out wheel, main spring 111 arranged anti-letting out between wheel and the sealed stator.
The sealing of rear bearing sealing and structure and fore bearing is symmetrical, has in the inner chamber that is inlaid in tail end cover 112, and links to each other with cartridge housing and be the sealed stator 113 of the tubular of L transverse section, and annular seal ring 114 is arranged between the end plate of sealed stator ear end face and tail end cover.The rear end of tail end cover bolt and cartridge housing 61 connects firmly.The canned rotor seat 115 that is packed in the annular that is the transverse section of falling L on the impeller shaft 21 is arranged in the sealed stator, reach the Seal cage 116 that constitutes by the two cooperation, the oil drainage hole 117 that is communicated with Seal cage 116 is arranged on the barrel of tail end cover 112, and oil drainage hole is communicated with oil storage pool 63 through pipeline 51.The structure of above-mentioned sealed stator 113 and canned rotor seat 115 and anti-structure of letting out wheel, reducing stuffing box gland, O RunddichtringO, main spring that matches and fore bearing sealing is symmetrical.
The working procedure of bearing seal: when impeller shaft is static, the front and back bearings sealing is respectively under the tension force effect of main spring, promote the anti-wheel of letting out respectively, do remotely spiral motion mutually along it with the canned rotor that respectively has the spiral cooperation of one's own, O RunddichtringO is separately contacted with sealed stator respectively, the reducing stuffing box gland is let out the wheel advance and retreat with anti-separately, thereby constitutes the contact seal under static state or the fine motion condition.When the impeller shaft rotation reaches certain rotating speed, Xuan Zhuan the anti-wheel of letting out is under surface friction drag and action of centrifugal force thereupon, do closely spiral motion mutually, compress main spring respectively, the O RunddichtringO is disengaged with sealed stator respectively, the anti-simultaneously spiral tangential stress and the centrifugal force of taking turns the helical tooth generation of peripheral distribution separately of letting out, stop cutting oil to leak vertically, force the cutting oil of sending here by bearing and cooling and lubricating device, arrange to oil storage pool 63 via oil drainage hole 107,117 respectively, thereby constitute the non-contact sealing.
Claims (7)
1, high speed centrifugal pump, comprise pump case and on front cover (3), impeller in the pump case (8) and impeller shaft (21) thereof, the preposition sealing of impeller, the rearmounted sealing of impeller, the sealing of impeller drain opening, the bearing of impeller shaft and cooling and lubricating device, bearing seal, it is characterized in that the preposition anti-blocking spiral (11) that is sealed with the front end of impeller (8) of above-mentioned impeller, between impeller and front cover, have by at least one pair of seal ring that matches (13) and seal groove (12,14) to constitute labyrinth sealing with the indentation runner that is communicated with to water channel (22) of sealing usefulness; Above-mentioned impeller postposition is sealed with the rotor mechanism that is sleeved on the impeller shaft, with the stator (40) that links with pump case, above-mentioned rotor mechanism has the rotator seat (23) of the anterior tubular that matches with impeller, the rear sleeve of rotator seat is equipped with spring adjusting part (25), with cooperating annular Sealing panoramatic head (28) is housed with spiral, ladder axial region at the Sealing panoramatic head is equipped with O type seal ring (30), with the reducing stuffing box gland (31) that matches with rotator seat, main spring (32) is arranged between spring adjusting part and Sealing panoramatic head, there is water conservancy diversion slope (34) rear end of the front portion of rotator seat, and spiral chute (35), recessed circular groove (36) is arranged on the fore ear end face, on water conservancy diversion slope and spiral chute, be fitted with the radome (37) of annular, the water conservancy diversion commutation wing (38) that in this radome match in Zhou Youyu water conservancy diversion slope, periphery has screw wing (39), said stator is the clearance type that the gap that communicates with impeller cavity is arranged with the front portion of the rotator seat of rotor mechanism and cooperates, be fitted with the constriction (41) in week in the stepped shaft in the front-end face of stator week, and the formation fluid reflux blocks pump chamber (42) between the screw wing of constriction and above-mentioned radome, the end face of the rear end of stator matches with above-mentioned O type seal ring, the clasp (43) that the above-mentioned circular groove of Zhou Youyu matches in the rear end; Above-mentioned impeller drain opening be sealed with the front side of the drain opening of impeller and rear side be symmetry and with spiral chute (15,17) and water conservancy diversion slope (16,18) of being communicated with for water channel (22,45), have that being sleeved on the impeller matches with spiral chute and water conservancy diversion slope respectively merges two radomes (9,10) that constitute reflection angle (53,54) respectively, the commutation fin (52) that pumps up water is arranged on the radome angle.
2, high speed centrifugal pump according to claim 1, it is characterized in that said bearing and cooling and lubricating device are for forcing the cooling and lubricating rolling bearing structure, cartridge housing (61) is arranged, its periphery of impeller shaft in cartridge housing (21) support has the left hand screw of suction inlet in the alternate formation (68) and the double helical wheel of middle suction (67) of right-hand screw, left and right side at the double helical wheel of middle suction respectively has rolling bearing (65,66), and there is the oil inlet hole (64) that communicates with the oil storage pool (63) of lubricant oil at the middle part of cartridge housing.
3, high speed centrifugal pump according to claim 1, it is characterized in that said bearing and cooling and lubricating device are for forcing cooling and lubricating ladder sliding bearing structure, left ladder shaft part and right ladder shaft part that impeller shaft is arranged, the conical surface that links to each other successively from inside to outside (72 that symmetry is arranged on left side ladder shaft part and the right ladder shaft part, 78), straight cylindrical surfaces (73,79), conical surface (74,80), straight cylindrical surfaces (75,81), conical surface (76,82), the left ladder axle sleeve (70) that links to each other and match with above-mentioned left and right sides ladder shaft part respectively with the left and right side of bearing spider (69) is respectively arranged, with adjustable right ladder axle sleeve (71), the left and right sides end face of above-mentioned bearing spider has recessed left annular groove (85) and right annular groove (86) respectively, thereby all within it respectively formation in the left interior ring (87) and the right side encircles (88), the middle part of the bearing spider between the ring in the ring and the right side in respect to a left side, the oil inlet hole (64) that is communicated with oil storage pool (63) is arranged, between the ladder shaft part of the left and right sides of impeller shaft, have respectively with a left side in ring and right in encircle corresponding helix structure left-handed helical wheel (90) and right hand helix take turns (91), left-handed helical wheel and right hand helix wheel form the middle suction inlet (93) that is communicated with oil inlet hole separately, between left-handed helical wheel and right hand helix wheel encircles in ring right respectively and in the left side, the left side shielding baulk ring (96) and the right baulk ring (97) that shields that respectively have its transverse section of constituting by interior ring and outer shroud to take the shape of the letter U, the interior ring (98) of above-mentioned left side shielding baulk ring cooperates with left-handed helical wheel, the periphery of its outer shroud has left-handed zigzag fashion spiral chute and matches with left annular groove, the interior ring (99) of above-mentioned right shielding baulk ring cooperates with the right hand helix wheel, and the periphery of its outer shroud has dextrorotation zigzag fashion spiral chute and matches with right annular groove.
4, high speed centrifugal pump according to claim 1, it is characterized in that said bearing seal is in the bearing outside, the sealed stator (104 of the tubular that having links to each other with cartridge housing is the L transverse section, 113), canned rotor seat (105 with the annular that is the transverse section of falling L that links to each other with impeller shaft, 115), and by the two Seal cage that constitutes and oil drainage hole (107,117) be communicated with, cooperate the anti-wheel (108) of letting out that annular is housed with spiral on the canned rotor seat, have with anti-letting out and take turns the reducing seal ring (109) that matches, anti-letting out has the O-ring seals (110) that matches with sealed stator on the wheel, main spring (111) is arranged between sealed stator and canned rotor.
5, high speed centrifugal pump according to claim 1, it is characterized in that said pump case has housing (1), front cover (3) that links to each other with the front end and back end of housing respectively and rear end cover (4), having matches with the periphery of impeller respectively constitutes the pump chamber isolating ring (5,6) of isolated pumping chamber.
6, according to claim 1,2,3,4 or 5 described high speed centrifugal pumps, the outside end face that it is characterized in that the bigger diameter end of said rotator seat (23) has rotor seal ring (33), its miner diameter end has adjustment nut (24), said O V-shaped ring (30) has fixed block (29), said spring adjusting part (25) has the positioning screw (26) that links to each other with rotator seat, between the periphery of said stator (40) outer rim and the pump case seal stator circle (48) is arranged.
7, high speed centrifugal pump according to claim 5, the right ladder shaft part that it is characterized in that said impeller shaft has the fastening screw nut (77) that is the multidiameter shaft shape of scyewed joint with impeller shaft, has with scyewed joint in the said right ladder axle sleeve (71) and adjusts the fastening screw nut (84) that cover (83) matches.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98111853A CN1065325C (en) | 1998-02-17 | 1998-02-17 | High speed centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98111853A CN1065325C (en) | 1998-02-17 | 1998-02-17 | High speed centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1226641A true CN1226641A (en) | 1999-08-25 |
| CN1065325C CN1065325C (en) | 2001-05-02 |
Family
ID=5221739
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98111853A Expired - Fee Related CN1065325C (en) | 1998-02-17 | 1998-02-17 | High speed centrifugal pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1065325C (en) |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1139729C (en) * | 2000-05-12 | 2004-02-25 | 清华大学 | Shielded pipeline pump |
| CN100404876C (en) * | 2004-07-07 | 2008-07-23 | 日立产业有限公司 | Turbo-type fluid machine and a stepped seal apparatus to be used therein |
| CN102562595A (en) * | 2012-02-20 | 2012-07-11 | 赵来福 | High-efficiency screw composite oil conveying pump |
| CN102678935A (en) * | 2012-04-27 | 2012-09-19 | 大连华阳光大密封有限公司 | Pump ring used for mechanical seal |
| CN101680486B (en) * | 2007-05-31 | 2013-02-06 | Bsh博世和西门子家用器具有限公司 | Bearing shield for bearing a shaft |
| WO2013034059A1 (en) * | 2011-09-07 | 2013-03-14 | Zhang Hong | Water-borne skimming ship |
| CN102996505A (en) * | 2012-12-27 | 2013-03-27 | 武汉大学 | Abrasion-resistant centrifugal pump impeller |
| CN104265678A (en) * | 2014-09-26 | 2015-01-07 | 浙江理工大学 | Sealing mechanism for gap between impeller and volute |
| CN105240280A (en) * | 2015-10-30 | 2016-01-13 | 江苏大学 | Centrifugal pump with rectangular gear pump front cavity structure |
| CN105422502A (en) * | 2015-12-18 | 2016-03-23 | 李良荣 | Intelligent sanitary pump |
| CN105757001A (en) * | 2016-04-26 | 2016-07-13 | 浙江理工大学 | Centrifugal pump with front pump cavity provided with parallelogram tooth-shaped structures |
| CN106762790A (en) * | 2016-12-31 | 2017-05-31 | 浙江耐士伦机械有限公司 | A kind of automobile engine cooling fan transmission device |
| CN109162958A (en) * | 2018-10-31 | 2019-01-08 | 芜湖飞龙汽车电子技术研究院有限公司 | A kind of electronic water pump for automobile flow blocking mechanism |
| CN109944948A (en) * | 2019-03-12 | 2019-06-28 | 哈尔滨理工大学 | A kind of novel bidirectional helical sealing |
| CN110735808A (en) * | 2019-11-28 | 2020-01-31 | 江苏科技大学 | pulsating flow enhanced cooling bearing seat device |
| CN112177800A (en) * | 2020-09-29 | 2021-01-05 | 西安航天动力研究所 | Cooling structure for spiral wheel pair bearing of liquid rocket engine pump |
| CN113775563A (en) * | 2021-10-31 | 2021-12-10 | 浙江水泵总厂有限公司 | Impeller outlet structure and centrifugal pump with same |
| CN114302799A (en) * | 2019-09-04 | 2022-04-08 | 克劳斯马菲挤塑有限公司 | Sealing device with cooling mechanism |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87202820U (en) * | 1987-03-03 | 1987-11-04 | 湖南大学 | Corrosion-resistance sealed centrifugal pump |
| DE4126504A1 (en) * | 1991-08-07 | 1993-02-11 | Duechting Pumpen Maschf Gmbh | Centrifugal pump with sliding ring seal - has annular skirt overlapping sealing gap |
| CN2134514Y (en) * | 1992-08-12 | 1993-05-26 | 上海贵盈密封材料制造有限公司 | Anti-leak, corrosion-resisting centrifugal pump |
| DE4228042A1 (en) * | 1992-08-24 | 1994-03-03 | Klein Schanzlin & Becker Ag | Pressure cover for centrifugal pumps |
| JPH0979384A (en) * | 1995-09-19 | 1997-03-25 | Mitsubishi Heavy Ind Ltd | Sealing device for centrifugal pump |
-
1998
- 1998-02-17 CN CN98111853A patent/CN1065325C/en not_active Expired - Fee Related
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1139729C (en) * | 2000-05-12 | 2004-02-25 | 清华大学 | Shielded pipeline pump |
| CN100404876C (en) * | 2004-07-07 | 2008-07-23 | 日立产业有限公司 | Turbo-type fluid machine and a stepped seal apparatus to be used therein |
| CN101680486B (en) * | 2007-05-31 | 2013-02-06 | Bsh博世和西门子家用器具有限公司 | Bearing shield for bearing a shaft |
| WO2013034059A1 (en) * | 2011-09-07 | 2013-03-14 | Zhang Hong | Water-borne skimming ship |
| CN102562595A (en) * | 2012-02-20 | 2012-07-11 | 赵来福 | High-efficiency screw composite oil conveying pump |
| CN102678935A (en) * | 2012-04-27 | 2012-09-19 | 大连华阳光大密封有限公司 | Pump ring used for mechanical seal |
| CN102996505A (en) * | 2012-12-27 | 2013-03-27 | 武汉大学 | Abrasion-resistant centrifugal pump impeller |
| CN104265678B (en) * | 2014-09-26 | 2017-02-15 | 浙江理工大学 | Sealing mechanism for gap between impeller and volute |
| CN104265678A (en) * | 2014-09-26 | 2015-01-07 | 浙江理工大学 | Sealing mechanism for gap between impeller and volute |
| CN105240280A (en) * | 2015-10-30 | 2016-01-13 | 江苏大学 | Centrifugal pump with rectangular gear pump front cavity structure |
| CN105422502A (en) * | 2015-12-18 | 2016-03-23 | 李良荣 | Intelligent sanitary pump |
| CN105757001A (en) * | 2016-04-26 | 2016-07-13 | 浙江理工大学 | Centrifugal pump with front pump cavity provided with parallelogram tooth-shaped structures |
| CN106762790A (en) * | 2016-12-31 | 2017-05-31 | 浙江耐士伦机械有限公司 | A kind of automobile engine cooling fan transmission device |
| CN109162958A (en) * | 2018-10-31 | 2019-01-08 | 芜湖飞龙汽车电子技术研究院有限公司 | A kind of electronic water pump for automobile flow blocking mechanism |
| CN109944948A (en) * | 2019-03-12 | 2019-06-28 | 哈尔滨理工大学 | A kind of novel bidirectional helical sealing |
| CN114302799A (en) * | 2019-09-04 | 2022-04-08 | 克劳斯马菲挤塑有限公司 | Sealing device with cooling mechanism |
| CN114302799B (en) * | 2019-09-04 | 2024-01-05 | 克劳斯马菲挤塑有限公司 | Sealing device with cooling mechanism |
| CN110735808A (en) * | 2019-11-28 | 2020-01-31 | 江苏科技大学 | pulsating flow enhanced cooling bearing seat device |
| CN112177800A (en) * | 2020-09-29 | 2021-01-05 | 西安航天动力研究所 | Cooling structure for spiral wheel pair bearing of liquid rocket engine pump |
| CN112177800B (en) * | 2020-09-29 | 2021-11-16 | 西安航天动力研究所 | Cooling structure for spiral wheel pair bearing of liquid rocket engine pump |
| CN113775563A (en) * | 2021-10-31 | 2021-12-10 | 浙江水泵总厂有限公司 | Impeller outlet structure and centrifugal pump with same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1065325C (en) | 2001-05-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1065325C (en) | High speed centrifugal pump | |
| CN105927579B (en) | A kind of centrifugal fluid transporter of non-internal leakage axial force self-balancing | |
| CN101985921B (en) | External radial plunger pump of casing tongue sealing mechanism | |
| CN2355149Y (en) | High speed centrifugal pump | |
| CN108869379B (en) | Centrifugal pump sealing ring with axial guide vanes | |
| WO1998044261A1 (en) | Improved mechanical seal for shafts and axles | |
| CN202833205U (en) | Double-way spiral liquid supply device | |
| CN203867961U (en) | Efficient centrifugal pump with impeller having a non-contact sealing function | |
| CN101037998A (en) | Positive vortex highly effective high pressure pump | |
| CN1109825C (en) | High-speed centrifugal pump | |
| CN106640666B (en) | A kind of centrifugal multistage pump multiple centrifugal pump | |
| CN108869384B (en) | Radial sealing ring of centrifugal pump with cylindrical guide vanes | |
| CN100554697C (en) | Conveying equipment | |
| CN1065327C (en) | Sealer for impeller shaft | |
| CN212615557U (en) | Rotary thread matching structure of multi-stage pump sealing ring and impeller body opening ring | |
| CN205618672U (en) | Two -way rotation is from pump sending fluid dynamic pressure type mechanical seal | |
| CN111828644B (en) | Combined sealing device | |
| WO2013131351A1 (en) | Multi-stage submersible pump for mines | |
| CN209321783U (en) | A kind of chain wheel device of drag conveyor | |
| CN207961040U (en) | A kind of single-stage double-suction middle-opening formula centrifugal pump | |
| US4648794A (en) | Pump with high speed expeller | |
| CN109827059A (en) | A kind of cycloid gear pump of two-way fuel feeding | |
| CN104791253B (en) | Multistage centrifugal pump | |
| CN111102232B (en) | Differential rotary spraying pump | |
| CN209244862U (en) | Shield vortex pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |