Pump assembly of turbo-pump unit, and automatic axial rotor unloading mechanism of turbo-pump unit

FIELD: engines and pumps.

SUBSTANCE: pump housing includes pumped medium inlet and outlet housings and a projection-shaped rear annular element, which together form a flow cavity for arrangement of a screw centrifugal impeller of a closed type and an automatic rotor axial unloading mechanism. Blades of the impeller are of different length and variable height as to length, which decreases towards the impeller outlet with observance of a quasiequality condition of the cross sectional area at an interblade channel inlet. Number of blades at the outlet is divisible and exceeds at least by two times the number of blades at the impeller inlet. Active volume of dynamic filling of a set of interblade channels of impeller is provided with possibility of releasing to flow part of (4.7÷45)×10-5 m3/rpm of pumped liquid per revolution of impeller. The automatic axial unloading mechanism includes adjacent annular shoe and belt, which form an end slot seal. The seal provides a self-adjustable flow of the pumped medium from the high pressure zone to the low pressure zone through overflow openings in the main disc and creates pulsating change of axial rotor unloading force.

EFFECT: increasing service life, improving reliability, compactness and operating efficiency of a pump assembly and an automatic axial unloading mechanism at simultaneous reduction of material consumption.

12 cl, 2 dwg

 

Group of inventions relates to turboboosting, namely to the pumping node and the machine axial unloading of the rotor turbopump unit designed to supply industrial water to the steam boilers and oil products in oil, gas, chemical and petrochemical, metallurgical and other enterprises.

Known turbopump Assembly, comprising a housing, a rotor mounted on bearings attached to the housing restrictive stops and the machine axial unloading of the rotor. The machine axial discharge is located between the lugs. Between the second stop and the outer race of a bearing support, as well as between the fifth of the machine axial unloading and rotor made gaps. The rotor is spring-loaded in the direction of abutment of the machine (EN 2083881 C1, publ. 10.07.1997).

Known turbopump Assembly, comprising a housing and a rotor with screw, centrifugal impeller and the turbine is mounted on bearings with power pumped liquid resistant device - hydraulic main heel and heel pad for axial forces. Drain the hydraulic chamber heel communicated with the inlet of the centrifugal wheel. The auger has a helical array of blades on the periphery, forming together asiareview stage with great reduced cross-section at the inlet than at the outlet. In the disk Centro the panorama wheels with holes, whereby the discharge chamber of the hydraulic heel communicated with the inlet of the centrifugal wheel (EN 2341689 C2, publ. 20.12.2008).

Known turbopump Assembly including turbine site with the collector supply of the working fluid with a nozzle device, a rotor with impeller turbine housing outlet spent working fluid, the reference node, the pump Assembly with the impeller and the machine axial discharge (Waluchow YEAR, Veselov NR. Experimental testing turbopump Assembly THA 100/580 with end seals on the bearings rolling: Proceedings of the VI international scientific-technical conference "SINT"11", LLC "Voronezh international Conference, UDC 621.675(063), ISBN 978-5-904786-98-4, p.42-45).

The disadvantages of the known solutions are increased structural complexity of pumping nodes, lack of secure unloading of the rotor Assembly from axial forces and low durability of the unit as a whole.

The present invention is to develop a pump unit, endowed with enhanced life, reliability and efficiency in the turbopump Assembly when applying the pumped liquid from the cold, hot water to oil, oil products to the consumer while reducing material consumption and increasing the compactness and efficiency of the unit, as well as in the development of the machine axial unloading of the rotor from Savich forces.

The task in part a pump unit turbopump Assembly decides that the pump Assembly according to the invention, includes a pump housing of the hydraulic end of the rotor shaft and sacienaasim impeller, the pump housing is made teams, including the case of the entrance to the pipe axial inlet for the fluid, the body of the tap consists of a front annular element connected to the housing of the entrance, as well as from the rear annular element associated with the front, which together form a flow cavity with a volume sufficient to accommodate snakecharming impeller, axial machine unloading of the rotor and helical bend and back the annular case element removal performed with the ledge in cross section and combined with the inner side of a rear wall of the housing of the flow part, and snakesentence the impeller is made in the form of a structurally integrated with the auger multiple centrifugal impeller, forming the impeller, preferably of the closed type, and includes a core and covering disks with the system located between the shoulder blades, separated interscapular channels, and the blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller with respect from the conditions kathiravelu cross-sectional area at the entrance to the interscapular channel, formed by two adjacent blades of maximum length and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder of smaller length, and the number of blades and respectively interscapular of output channels in multiples of not less than two times the number of blades and channels respectively at the entrance to the impeller; active amount of dynamic filling together interscapular channels of the impeller of the pump is made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about fluid, in addition, the machine axial unloading of the rotor comprises an annular heel, the ledge is fixed or made on the back wall of the housing of the flow part, and also includes an annular band on the rear side of the main disk of the impeller and is coupled with the fifth with the formation of end gap seal made with the possibility of a self-regulating flow fluid from the zone high zone of low pressure, preferably, in the lead-in portion of the flow cavity of the impeller through executed in the main disk of the impeller, at least one bypass hole and the creation of this pulsating axial force changes razgruzki the rotor.

While the impeller blades of the pump in a variant embodiment with a single-stage interleaving length can be performed with a radial removal of lead-tops short blades from the axis of the impeller, not less than 1.3 times the radial removal of lead-tops of the long blades, preferably, with the location of the peaks of the short blades at a radial distance corresponding to the small radius r of the mid-length of long blades in the range r±15%.

The number of blades of the impeller can be made from 4 to 16, preferably 12 blades.

The auger can be performed not less than dvukhzaryadnym with spiral blades and a hollow shaft, which, at least most of the length is made covering the wound in his section of the drive shaft turbopump Assembly and provided with a smooth expansion in the transition zone of the channel of the screw in the multiple-channel centrifugal wheel with tilt angle to the axis of the shaft the greater part of the shaping of the contour of the transition, a variant of the extension shaft 18°÷30°.

The screw can be provided with spiral blades, made mainly with variables, at least part of the length of the radius and/or step spiral twist, including the possibility of increasing in the course of the flow of fluid, while the average grade the t of step increasing spiral twist G Wdefined in the range values of ΔGW=(0,25÷1,35)m/m

During the flow of fluid lead-in area of the spiral blade of the auger impeller can be performed with an angle of twist of the spiral with the increment of the radius of each of the vanes from 0 to R in the angular range comprising (85-250)°.

Spiral tap in the pump casing may be made in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels with the difference of the squares of the output and input sections, referred to the length of the channel with a gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea, which is G=0,87-0,95.

To drain the fluid from flowing part of the pump casing, the latter may be provided with a pipe outlet, made mainly diffuser, tangential type.

The belt of the machine axial unloading of the rotor on the back side of the main disk of the impeller can be made open to the duct peritonism channel having annular inner and outer side walls, and an annular heel provided with a circular table, a console in cross section with a protruding rim, edge which made the return end of the inner wall of the belt with the formation of the and output of peritoneo channel mentioned end gap seal with the possibility of an adjustable pulsating output of the last of the excess fluid.

On the main and top drives the pump impeller can be made of the slotted seal, main drive of the impeller is made slit seal radius larger than the radius of the gap seals on the top disk, and an end face of the abutment of the machine axial unloading of the rotor is constructed with a diameter smaller than or equal to the diameter of the gap seals on the top disk of the impeller.

The pump Assembly turbopump Assembly variant may be designed for pumping liquids, including, at least, hot, cold, industrial water, oil and products of petroleum cracking with the possibility of creating a working pressure of up to 750 m and the feed rate of the pumped medium from 20 to 1000 m3/h, including at rated rotor speed turbopump Assembly, preferably 9, 85·104(±20%)/min

The task in the part of the machine of the axial discharge of the turbopump rotor Assembly decides that the machine axial unloading of the rotor according to the invention, performed in pumping node turbopump Assembly, including the housing flow of the pump with entrance point of the fluid flowing in the cavity, the back wall and placed in a flow cavity sacienaasim impeller with screw, combined with the centrifugal wheel, the imp is United in the view of the impeller, preferably, the closed type with blades located between the base and covering disks in this machine axial unloading of the rotor is constructed consisting of an annular heel, the ledge is fixed or made on the back wall of the housing of the flow part, and an annular band on the back side of the main disk of the impeller associated with the meridional or bell-conical inner annular wall of the heel with the possibility of flow of the fluid from the zone of high pressure at the outlet of the impeller in a low-pressure zone at the entrance to the cavity of the impeller through at least one peritonei hole in the basal part of the main disk, and an annular heel machine axial unloading of the rotor is supplied with the console in cross section circular table with a protruding rim, and the band performed on outdoor duct peredachny channel, preferably with annular inner and outer walls, through one of which the band paired slot seal between mating surfaces mentioned annular walls of the heel and the belt, and through the other end wall of the belt and the end of the annular rim of the heel end formed slit the seal, the combined flow system with by-pass channels, thus covering the disk of the impeller is made adjacent to to the cusu entry in a flow cavity with the formation of the gap seal moreover, the radial distance of the inner wall peritoneo channel in the ring belt is made not greater than the radial distance from the axis of the shaft slotted seal, and the thickness of the gap-type input peredachny channel adopted not less than 1.5 times the minimum gap mentioned end gap seal at the exit of the channel, but less than the maximum value of the above-mentioned gap.

Technical result achieved is given by a set of signs is the development of a pump unit, endowed with enhanced life, reliability and efficiency in the turbopump Assembly.

This is achieved by a set designed in the invention, design and technology solutions for the main part of the pump node of the unit of work items and the parameters of their work, namely the impeller snakecharming type with the stated parameters are found by solving machine axial unloading of the rotor. Use located at the entrance to the impeller of the pump screw ensures high anticavitation quality pump and dvuhzavitkovym spiral tap in the pump casing provides radial uphill throughout the range of operation modes of the unit.

Thus the performance of the pumping node turbopump unit comprises the reception in the invention of the execution eliminates leakage of the pumped fluid, as well as significantly reduce the consumption of materials and to increase the compactness and efficiency of the unit as a whole. In addition, the rotor is unloaded from axial forces axial machine unloading, which runs on the medium being pumped, which eliminates the use of complex axial bearings and high-speed mechanical seal in the pump housing and the entire unit as a whole.

The invention is illustrated by drawings, where:

figure 1 shows the pump Assembly with the machine of the axial discharge of the turbopump rotor Assembly, a longitudinal section;

figure 2 - impeller pump, primary drive with the blades longitudinal section.

The pump Assembly turbopump Assembly includes a pump housing of the flow part, the rotor shaft 1 and sacienaasim impeller 2. The pump casing is made teams and includes case 3 input socket 4 axial inlet for the fluid and the housing outlet. Case drain consists of a front annular element 5 connected to the housing 3 and also from the back of the ring element 6 is associated with the front element 5, which together form a flow cavity 7 with a volume sufficient to accommodate snakecharming impeller 2, the machine of the axial discharge of the rotor and the spiral-of-way. The rear annular element 6-housing allocation is made with the ledge in erachem section and combined with the inner side of a rear wall of the housing of the flow part.

Snakesentence impeller 2 is made in the form of a structurally integrated with the auger 8 multiple centrifugal impeller, forming the impeller, preferably of the closed type. The impeller 2 includes a core and covering disks 9 and 10, respectively, with the system located between the blades 11, separated interscapular channels 12. The blade 11 is made preferably of different lengths and variable height along the length, decreasing towards the exit of the impeller 2 in compliance with the conditions of quasimomenta cross-sectional area at the entrance to the interscapular channel 12 formed by two adjacent blades 11 and maximum length, and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder of smaller length. The number of blades 11 and respectively interscapular channels 12 at the exit multiple of not less than two times the number of blades and channels respectively at the entrance to the impeller 2.

The active volume is dynamically populate the aggregate interscapular channels 12 of the impeller 2 of the pump is made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about the pumped medium.

The machine axial unloading of the rotor comprises an annular heel 13, a fixed ledge is performed on the back wall of the housing of the flow part. The machine axial discharge also includes an annular band 14 on the rear side of the main disk 9 of the impeller 2. The belt 14 is connected with the fifth 13 with the formation of the slotted end seal 15. Slit the seal 15 is made with the possibility of a self-regulating flow fluid from the zone high zone of low pressure, preferably, in the lead-in portion of the flow cavity 7 of the impeller 2 through executed in the main disk 9 of the impeller, at least one bypass hole 16 and the creation of this pulsating axial force changes unloading of the rotor.

The blades 11 of the impeller 2 of the pump in a variant embodiment with a single-stage interleaving length last performed with the radial removal of lead-tops short blades from the axis of the impeller, not less than 1.3 times the radial removal of lead-tops of the long blades, preferably, with the location of the peaks of the short blades at a radial distance corresponding to the small radius r of the mid-length of long blades in the range r±15%.

The number of blades 11 of the impeller 2 is taken from 4 to 16, preferably 12 blades.

The screw 8 is made not less than dvukhzaryadnym with spiral blades 17 and the hollow shaft, which, at least most of the length is made covering the wound the it section of the drive shaft 1 turbopump Assembly. The screw 8 is provided with a smooth expansion in area 18 of the transfer channel of the screw in the multiple-channel centrifugal wheel with tilt angle to the axis of the shaft the greater part of the shaping of the contour of the transition, a variant of the extension shaft 18°÷30°.

The screw 8 is provided with helical blades 17, made mainly with variables, at least part of the length of the radius and/or step spiral twist, including the possibility of increasing in the course of the flow of fluid. The average gradient of increase of the step spiral twist GWdefined in the range values of ΔGW=(0,25÷1,35)m/m

During the flow of fluid lead-in section 19 of the helical blades 17 of the screw 8 of the impeller is made with an angle of twist of the spiral with the increment of the radius of each of the vanes from 0 to R in the angular range comprising (85-250)°.

Spiral tap in the pump housing made in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels with the difference of the squares of the output and input sections, referred to the length of the channel with a gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea, which is G=0,87-0,95.

To drain the fluid from flowing part of the casing the pump latter is supplied by a pipe outlet, made, mostly, diffuser, tangential type (not shown).

The belt 14 of the machine axial unloading of the rotor on the back side of the primary drive 9 of the impeller 2 is made open to the duct peritonism channel 20 having annular inner and outer side walls 21 and 22 respectively. The annular abutment ring 13 is provided table 23, the cantilever cross-section with a protruding rim, edge which made the return end of the inner wall 21 of the belt 14 with the formation at the outlet of peritoneo channel 20 slotted end seal 15 with the possibility of an adjustable pulsating output of the last of the excess fluid.

On the ground and covering disks 9 and 10 respectively of the impeller 2 of the pump is made slotted seal. On the primary disk 9 of the impeller is made slit seal 24 with a radius greater than the radius of the slotted seal 25 on the top disk 10. The end of the heel 13 of the machine axial unloading of the rotor is made of diameter less than or equal to the diameter of the slotted seal 25 on the top disk 10 of the impeller 2.

The pump Assembly turbopump Assembly variant is designed for pumping liquids, including, at least, hot, cold, industrial water, oil and products of petroleum cracking with the possibility of creating a working voltage is RA up to 750 m and the feed rate of the pumped medium from 20 to 1000 m 3/h, including at rated rotor speed turbopump Assembly, preferably 9,85·104(±20%)/min

The machine of the axial discharge of the turbopump rotor Assembly made in pumping node turbopump Assembly. The pump Assembly includes the housing flow of the pump, provided with a housing 3 inputs for the fluid flowing in the cavity 7, the rear wall 26 and placed in flow-through cavity 7 sacienaasim impeller 2. The impeller includes a screw 8, combined with the centrifugal wheel, made in the form of the impeller, preferably of the closed type with blades 11 arranged between the base and covering disks 9 and 10.

The machine axial unloading of the rotor is constructed consisting of an annular heel 13, a ledge secured or made on the back wall 26 of the housing of the flow part, and an annular band 14 on the rear side of the main disk 9 of the impeller 2, is associated with the meridional or bell-conical inner annular wall of the abutment 13 with the possibility of flow of the fluid from the zone of high pressure at the outlet of the impeller in a zone of low pressure at the inlet in flow cavity 7 of the impeller 2 via at least one peritonei hole 16 in the basal part of the main disk 9.

Ring the heel 13 of the machine axial unloading the rotor is equipped with a console in the cross section of the annular table 23 with a protruding knob. The belt 14 is open to the duct peredachny channel 20, preferably with annular inner and outer walls 21 and 22 respectively. Through the outer wall 22 of the belt 14 carries a slit seal 24 between the mating surfaces mentioned annular walls of the abutments 13 and belt 14. By the end of the inner wall 21 of the belt 14 and the end of the annular rim of the table 23 of the abutment 13 is formed slit end seal 15, the combined flow system bypass channel 27.

Top disk 10 of the impeller 2 is attached to the housing 3 of the sign-in flow cavity 7 with the formation of the gap seal 25. The radial distance of the inner wall 21 peritoneo channel 20 in the belt 14 is not greater than the radial distance from the axis of the shaft slotted seal 25.

The thickness of the slotted gap 28 at the entrance to peredachny channel 20 adopted not less than 1.5 times the minimum gap mentioned slotted end seal 15 at the exit of the channel 20, but less than the maximum value of the above-mentioned gap.

Operation of pumping node turbopump Assembly with automatic axial unloading of the rotor is as follows.

In the pump turbopump Assembly the medium to be pumped through the pipe 4 inputs, getting on the entrance to snakesentence impeller 2, is moved from the price of the RA to the periphery by centrifugal force, gaining kinetic energy and getting a spin in the direction of rotation of the impeller 2.

After exiting the impeller 2, the flow moves to dvuhtochechny spiral tap, extending to the pipe outlet for the fluid in compliance with the conditions of quasimomenta of flow rates in each channel allotment. From draining the medium to be pumped enters the pipe outlet and enters the pipeline for further transportation.

At the nominal speed of the rotor on snakesentence impeller 2 pump also acts axial force Fa. When the pressure of the pumped fluid at the outlet of the impeller 2 of the latter is fed through the slit seal 24 on the main disc 9 between fifth 13 and belt 14. Slit the seal 24 is made on a radius greater than the radius of the slotted seal 25 on the top disk 10. Next, the medium to be pumped through the slit end seal 15 between the belt 14 and the fifth 13, relieving the axial load on the shaft 1, through the system peritoneo and bypass channels 20 and 27 and the hole 16 in the main disk 9 in the root zone and is returned to the zone of low pressure in the flow-through cavity 7 of the impeller 2.

When the reduction of the strain on the shaft 1, the gap 29 slotted end seal 15 is reduced or collapses, then the process fluctuation of axial load and razhrosceval 1 is repeated in a similar way by means of the machine of the axial unloading.

Unbalanced area 30 of the impeller 2 is constantly creating axial force at rated load side of the heel 13, which interacts with the axial force from the turbine creates unloading of the rotor against axial forces. Touch the butt side of the table 23 of the abutment 13 and the return end of the belt 14 does not occur, since the minimum value of 0,1...0,15 mm gap end gap seal 15 in a flow cavity 7 increases the pressure and impeller together with the rotor moves away, revealing a gap, and the pressure in the flow cavity 7 when it falls. The rotor is in quasi-equilibrium position during the entire time turbopump Assembly.

Thus, due to the developed invention constructive and technological solutions pumping node unit, the parameters of the impeller and machine axial discharge of the rotor, reach increased endurance and reliability, and efficiency of feed fluid to the consumer while reducing material consumption and increase the compactness of the pumping node.

1. The pump Assembly turbopump Assembly, characterized in that includes a pump housing of the hydraulic end of the rotor shaft and sacienaasim impeller, the pump housing is made teams, including the case of the entrance to the pipe axial supply pumped from the food, case drain consists of a front annular element connected to the housing of the entrance, as well as from the rear annular element associated with the front, which together form a flow cavity with a volume sufficient to accommodate snakecharming impeller, axial machine unloading of the rotor and helical exhaust, and the rear annular case element removal performed with the ledge in cross section and combined with the inner side of a rear wall of the housing of the flow part, and snakesentence the impeller is made in the form of a structurally integrated with the auger multiple centrifugal impeller, forming the impeller, preferably of the closed type, and includes a core and a covering disks with the system located between the shoulder blades, separated interscapular channels, and the blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller with respect to the conditions kathiravelu cross-sectional area at the entrance to the interscapular channel formed by two adjacent blades of maximum length and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder of smaller length, and the number of blades and respectively milophoto the different output channels fold, not less than two times the number of blades and channels respectively at the entrance to the impeller; active amount of dynamic filling together interscapular channels of the impeller of the pump is made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about fluid, in addition, the machine axial unloading of the rotor comprises an annular heel, the ledge is fixed or made on the back wall of the housing of the flow part, and also includes an annular band on the rear side of the main disk of the impeller and is coupled with the fifth with the formation of end gap seal made with the possibility of a self-regulating flow fluid from the zone high zone of low pressure, preferably, in the lead-in portion of the flow cavity of the impeller through executed in the main disk of the impeller, at least one bypass hole and the creation of this pulsating axial force changes unloading of the rotor.

2. The pump Assembly turbopump Assembly according to claim 1, characterized in that the impeller blades of the pump in a variant embodiment with a single-stage interleaving length last performed with the radial removal of lead-tops short blades from the axis of the impeller, no man is e than 1.3 times the radial removal of lead-tops of the long blades, preferably, the location of peaks of short blades at a radial distance corresponding to the small radius r of the mid-length of long blades in the range r±15%.

3. The pump Assembly turbopump Assembly according to claim 1, characterized in that the number of blades of the impeller taken from 4 to 16, preferably 12 blades.

4. The pump Assembly turbopump Assembly according to claim 1, characterized in that the screw is made not less than dvukhzaryadnym with spiral blades and a hollow shaft, which, at least most of the length is made covering the wound in his section of the drive shaft turbopump Assembly and provided with a smooth expansion in the transition zone of the channel of the screw in the multiple-channel centrifugal wheel with tilt angle to the axis of the shaft the greater part of the shaping of the contour of the transition, a variant of the extension shaft 18°÷30°.

5. The pump Assembly turbopump Assembly according to claim 1, characterized in that the screw is provided with spiral blades, made mainly with variables, at least part of the length of the radius and/or step spiral twist, including the possibility of increasing in the course of the flow of fluid, the average gradient of increase of the step spiral twist GWdefined in the range values AGW=(0,25÷1,35)m/m

6. Pumping node turbopump is on Assembly according to claim 5, characterized in that during the flow of fluid lead-in area of the spiral blade of the screw impeller is made with an angle of twist of the spiral with the increment of the radius of each of the vanes from 0 to R in the angular range comprising (85-250)°.

7. The pump Assembly turbopump Assembly according to claim 1, distinguish fact that the spiral tap in the pump housing made in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels with the difference of the squares of the output and input sections, referred to the length of the channel with a gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea, which is G=0,87-0,95.

8. The pump Assembly turbopump Assembly according to claim 1, characterized in that to drain the fluid from flowing part of the pump casing the latter is supplied by a pipe outlet, made mainly diffuser, tangential type.

9. The pump Assembly turbopump Assembly according to claim 1, characterized in that the belt of the machine axial unloading of the rotor on the back side of the main disk of the impeller is made open to the duct peritonism channel having annular inner and outer side walls, and an annular heel provided with a circular table, a console in the ass is enom section with a protruding rim, the end which made the return end of the inner wall of the belt with the formation at the outlet of peritoneo channel mentioned end gap seal with the possibility of an adjustable pulsating output of the last of the excess fluid.

10. The pump Assembly turbopump Assembly according to claim 1, characterized in that the primary and covering disks of the impeller of the pump is made slotted seal, main drive of the impeller is made slit seal radius larger than the radius of the gap seals on the top disk, and an end face of the abutment of the machine axial unloading of the rotor is constructed with a diameter of less than or equal to the diameter of the gap seals on the top disk of the impeller.

11. The pump Assembly turbopump Assembly according to claim 1, wherein the variant is designed for pumping liquids, including, at least, hot, cold, industrial water, oil and products of petroleum cracking with the possibility of creating a working pressure of up to 750 m and the feed rate of the pumped medium from 20 to 1000 m3/h, including at rated rotor speed turbopump Assembly, preferably 9,85·104(±20%)/min

12. The machine of the axial discharge of the turbopump rotor Assembly, characterized by the fact that performed in pumping node turbopump agreg is the including case flow of the pump with entrance point of the fluid flowing in the cavity, the back wall and placed in a flow cavity sacienaasim impeller with screw, combined with the centrifugal wheel, made in the form of the impeller, preferably of the closed type with blades located between the base and covering disks in this machine axial unloading of the rotor is constructed consisting of an annular heel, the ledge is fixed or made on the back wall of the housing of the flow part, and an annular band on the back side of the main disk of the impeller associated with the meridional or bell-conical inner annular wall of the heel with the possibility flow of the fluid from the zone of high pressure at the outlet of the impeller in a low-pressure zone at the entrance to the cavity of the impeller through at least one peritonei hole in the basal part of the main disk, and an annular abutment of the machine axial unloading of the rotor is supplied with the console in cross section circular table with a protruding rim, and the band performed on outdoor duct peredachny channel, preferably with annular inner and outer walls, through one of which the band paired slot seal between the response surface is mi-mentioned annular walls of the heel and the belt, and through the other end wall of the belt and the end of the annular rim of the heel end formed slit the seal, the combined flow system with by-pass channels, thus covering the disk of the impeller is made adjacent to the housing inlet in flow cavity with the formation of the gap seal and the radial distance of the inner wall peritoneo channel in the ring belt is made not greater than the radial distance from the axis of the shaft slotted seal, and the thickness of the gap-type input peredachny channel adopted not less than 1.5 times the minimum gap mentioned end gap seal at the exit of the channel, but less than the maximum magnitude of the said a gap.



 

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19 cl, 7 dwg

FIELD: engines and pumps.

SUBSTANCE: structural-technological model range of chemical pumps includes a set of pumps. Each pump of the row is made as follows as per a single-type system: it is centrifugal, one-stages; it includes a rotor shaft and an impeller and consists of flow and travel parts. The pump travel part housing includes bearing supports. The flow part housing is provided with a flow cavity combined with a spiral collector of pumped liquid with diffusion airfoil gradient of 1÷70 m2/m. The impeller is of a closed type and has the main and covering discs and a system of blades. The main disc is protected on the rear side with a hydraulic lock containing an impeller in the form of an independent disc. The flow part housing is equipped with an detachable annular wall geometrically coordinated with the hydraulic lock. The least of outside radii of the above wall is equal at least to the wheel flow-through radius of the wheel, and hydraulic lock impeller radius is equal at least to the wheel radius. The main wheel disc is equipped with an annular comb and a through opening.

EFFECT: increasing service life, durability, operating reliability of pump operation, pumping efficiency, protection against leakages of pumped media and noxious fumes to atmosphere.

21 cl, 7 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed method comprises making the pump composite housing of running section housing thrust plate with bearings, suspension case and flow section housing, making the pump rotor shaft, impeller, adapter case and structural assy. Pump is assembled pump assy is mounted and tested. Flow section housing and suspension case are separated by detachable circular ledged rear wall. Pump incorporates enclosed vaned impeller, vanes being made with angular twisting. Active volume of dynamic filling of diffuser vane channels allows ejection of (5.0…1500)×10-5 m3/vol of pumped fluid into flow section. Impeller disk are protected from outside by hydraulic locks composed by impeller with a set of radial vanes. Impeller vane radius is sufficient for development of hydrodynamic counter pressure to sustain pumped medium head under pump standard operating conditions at 0.25 of vane length from vane near-root point.

EFFECT: simplified manufacture and assembly, longer life, higher reliability and efficiency.

26 cl, 6 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed pump unit comprises rotary motor, adaptor with power coupling and rotary semi-submersible pump. Composite pump housing comprises running section housing arranged above thrust plate and suspension case secured to thrust plate from below and locked with flow section housing. Said shaft runs in running section housing bearings and while its lower support extends through suspension case and into flow section housing to be rigidly coupled with impeller hub. Rotor shaft top end is fitted in adapter power coupling. Impeller comprises the main and cover discs with s set of curved vanes. Active volume of intervane channel filling allows forcing out in one impeller revolution of (5.0-1500)x10-5 m3/rev of transferred medium. Impeller main disc is protected by impeller-like hydraulic lock. Flow section housing has circular ledged wall of wall outer radius smaller than that of impeller vanes.

EFFECT: simplified design, fabrication and assembly, higher reliability and efficiency.

22 cl, 4 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed pump comprises running and flow sections. Flow section housing comprises header case with circular ledged comb, rear wall consisting of connected circular comb of header case and rear wall ledged circular element as well as detachable cover. Pump running part housing is equipped with bearings and crankcase. Exposed impeller is composed of multistart impeller including vaned main disc with hub and circular comb. Aid comb features outer radius congruent with mating inner radius of circular ledged comb in header case. Said main disc is equipped with hydrodynamic protection composed by impeller. Protection is furnished with hydraulic lock with extra impeller with radius smaller than that of working impeller. Circular element of rear wall geometrically complies by inner radius of ledge with hydraulic lock radius.

EFFECT: better tightness, longer life and higher reliability.

11 cl, 2 dwg

FIELD: engines and pumps.

SUBSTANCE: every representative pump of proposed model series includes identical design system. Every rotary semi-submersible pump is equipped with thrust plate. Housing of every pump comprises running section housing and suspension case locked therewith and secured to thrust plate from below. Pump incorporates exposed or closed impeller. Mean gradient of vane axis mounting angle and identical gradient of angular configuration of vane channel median axis makes (0…7.0) rad/m over vane length. Vanes and channels feature invariable or variable curvature. Impeller discs are protected from outside and rear side by hydraulic locks composed by impellers. Impeller vane radius is sufficient for development of hydrodynamic counter pressure to sustain pumped medium head under pump standard operating conditions at 0.25 of vane length from vane near-root point 0.45R from impeller axis. Said main disc is equipped with circular ledge making an open circular channel with impeller hub wall.

EFFECT: simplified manufacture and assembly, longer life, higher reliability and efficiency.

25 cl, 5 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed pump comprises drive motor, adapter with power coupling and rotary semi-submerged pump. Composite pump housing comprises running section housing with bearings and suspension case attached to thrust plate from below and locked to flow section housing. Said shaft runs in running section housing bearings and while its lower support extends through suspension case and into flow section housing to be rigidly coupled with impeller hub. Rotor shaft top end is fitted in adapter power coupling. Impeller comprises the main and cover discs with s set of curved vanes. Means gradient of vane axis mounting angle and identical gradient of angular configuration of vane channel median axis makes (0…7.0) rad/m over vane length. The impeller main and cover discs are protected by hydraulic locks composed by impeller. Impeller features widened hub with circular channel in hub body exposed from above.

EFFECT: simplified design, fabrication and assembly, higher reliability and efficiency.

22 cl, 4 dwg

FIELD: engines and pumps.

SUBSTANCE: dispersing stage comprises distributor. The latter comprises top and bottom vaned disc, semi-exposed impeller including drive vaned disc. Impeller drive disc has a through circular groove. Groove width varies from two to ten percent of vane maximum OD. Circular groove is made in drive disc every vane. Distributor bottom disc diameter does not exceed 85 percent of vane OD. At least one circular cutout is made at distributor inlet in every vane.

EFFECT: better dispersion, higher reliability.

7 cl, 7 dwg

FIELD: engines and pumps.

SUBSTANCE: invention relates to pump engineering, particularly to vertical pulp pumps. Proposed pump comprises housing, rotor with shaft and exposed impeller. Impeller comprises main disc wit the system of curved blades separated by interblade channels. Inner surface of pump housing flow chamber and that of impeller are coated with protective layer of wearproof polymer material. Impeller disc and blades are combined and composed of shaping, primarily, plate-like structural carcass and said protective layer. Said protective layer is applied on both sides of said carcass elements to allow paired self-anchoring of opposite carcass elements and blades. Disc carcass and blades are perforated. Ratio of total areas of perforation cross section and polymer web filled therein to add to anchoring of protective layers to imperforated carcass area features definite magnitude. Disc carcass diameter is smaller than design working wheel diameter by at least two initial contour depths of protective layer. Blade carcass height is smaller than design blade height by initial contour depth of protective layer.

EFFECT: longer life, higher reliability and efficiency.

12 cl, 2 dwg

FIELD: machine building.

SUBSTANCE: hydraulic machine comprises wheel fitted on shaft, both running about axis X5. Hydrostatic or hydrodynamic bearing 100 with water lubrication is composed of shaft radial peripheral surface 52 on one side and on the opposite side by inner radial surface 102 of member 101 fixed relative to said axis. Said bearing is arranged between two edges 121 and 122 to make water film removal zones created in standard operation of bearing 100. Said fixed member 101 has cavity 130 exposed to its inner radial surface 102 nearby bearing first edge 121 of said first and second edges 121, 122. Said fixed member comprises means 131, 132, 133 to communicate said cavities with those outside the bearing 100, nearby second edge 122. Said cavity 130 and said means 131, 132, 133 can remove flow parts that form water film in case removal of water film at the level of said first edge is impossible.

EFFECT: reliable operation of the bearing.

14 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: shaping method of a rotor deviation signal in magnetic suspension systems of a rotary machine with current control by means of pulse-width modulation (PWM control) in an electromagnet consists in supply of PWM control signals to input of power amplifier 1. From amplifier 1 output the signals in the form of polygonal shaped voltages are supplied to electromagnet 3. At the same time, current signals are supplied to current converter 2 of electromagnet 3 with further extraction of a variable component of sawtooth current. Further, it is converted to a signal proportional to curvature of sawtooth current signal at the switching interval of a PWM control signal, and its further conversion to a rotor deviation signal.

EFFECT: simplifying a self control scheme and creating a simpler sensorless magnetic suspension device, which will allow simplifying the structure of supports of a rotary machine and increasing interference immunity of magnetic suspension systems.

11 cl, 6 dwg

FIELD: engines and pumps.

SUBSTANCE: compressor impeller comprises main disc and vanes bent backward relative to direction of motion. In compliance with this invention vanes feature constant inclination angle at the vane peripheral section, Note here that section with constant inclination angle is located some 0.7-0.95 D2 impeller OD.

EFFECT: decreased stepwise uniformity of rates and pressure at outlet, higher efficiency.

1 dwg

FIELD: oil and gas industry.

SUBSTANCE: submersible centrifugal unit has a modular design and includes a compensator, an electric motor, a seal section, a gas separator, a pump, an armoured electric cable and a bearing. Shafts of modular sections are installed on the support. The support is made in the form of a bush neck, a bearing sleeve and a spline coupling, which are interconnected with each other. Bearings are spherical and installed in the housing. Chambers of channels of bearings and oil supplying channels of the housing are of a split type.

EFFECT: improving reliability and durability of a submersible pump unit by reduction of occurring oscillations owing to changing the structure of support of the shaft with bearings.

2 dwg

FIELD: engines and pumps.

SUBSTANCE: pump comprises housing with inlet and outlet and rotor. The latter comprises the shaft running in radial and radial thrust ball bearings and auger wheel with helical blades and hollow taper bush fitted on said shaft. Said bush adjoins the outlet at larger diameter via radial and end grooves of slotted stepwise clearance to make release chamber with bypass channels on outer side of wheel space. Said channels communicate the chamber with auger wheel inlet cavity. Radial thrust ball bearing outer race is fitted in the housing with end clearance not smaller than end clearance of said slotted stepwise seal. Shroud is fixed at the auger wheel blades, at wheel outer line taper section, to abut on inlet via slotted seal end clearance equal thereto.

EFFECT: higher reliability, longer life.

1 dwg

FIELD: oil and gas industry.

SUBSTANCE: submersible centrifugal pump unit consists of compensator, electric motor, protector, gas separator with suction strainer, pump, armoured electric cable. Shafts of modular sections are interconnected by spline coupling protected by a flexible and sealed housing fixed at shafts by means of slots and fixing yokes.

EFFECT: improving reliability and durability of submersible pumping unit by protection of vulnerable points in process of the pumping unit operation.

2 dwg

FIELD: oil and gas industry.

SUBSTANCE: set comprises a centrifugal pump with a submerged electric motor, an additional lower pump section with a drive from the submerged motor, a motor hydraulic protection, a packer, a nozzle. The packer disconnects producing and water-absorbing reservoirs. The nozzle connects the lower pump section with the under-packer space and has a plunger at the lower end. The plunger tightly enters the cylinder installed in the packer. The intake of the additional pump section arranged in its upper part is connected with a flat pipe to a well space below the producing reservoir. Blades of impellers of the lower pump section are made for opposite direction of rotation. Impellers are installed on the shaft of the lower pump section in the tilted position. If a water sublayer of the producing reservoir is arranged above the oil one, a dead partition is installed in the lower part of the nozzle. Above the partition there is a hole for water arrival from the well into the nozzle. Below the partition there is a hole made for water arrival into the under-packer space from the upper part of the additional pump section via a flat pipe. In the receiving part of the additional pump section there is a centrifugal separator for separation of oil and its discharge via a side hole in the pump vessel into the well.

EFFECT: invention may be used for dual oil production and water injection in water wells.

1 cl, 4 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed delivery oil rotary pump comprises casing and casing cover. Rotor composed of shaft and impeller is arranged between casing and cover. Pump rotor runs in console bearing supports located outside pump casing. Said bearings represent two types of antifriction bearings: spherical two-row roller bearing to take up pump shaft axial load and floating toroidal roller bearing. Both bearings are fitted on the shaft by means of tapered coupling bushes with axial split Impeller is fitted on the shaft with the help of two-sided collet jig with conical sleeves and screws while rotor end seals are fitted on the shaft with the help one-side collet jigs with conical bushes and screws.

EFFECT: reduced noise and vibration, higher reliability and efficiency, longer life

5 cl, 3 dwg

FIELD: engines and pumps.

SUBSTANCE: unit includes the main pump and an electric motor, which are mounted on a frame. Their shafts are connected through a coupling to a detachable intermediate shaft. Attachments of the pump and the electric motor to common or separate frames are made using high-accuracy built supports adjustable as to height and self-adjusting as to an angle. Attachment surfaces of the pump legs are lifted to the level of common central axis of supply and discharge branch pipes of the pump. Shafts of the pump and the electric motor are connected by means of a compensating double coupling to flexible discs.

EFFECT: creation of the main electric pump unit with improved technical and economic characteristics, and namely with reduced noise and vibrations, improved reliability, service life and efficiency.

4 cl, 5 dwg

FIELD: machine building.

SUBSTANCE: invention refers to rotor (2) for hydraulic machine, which includes shaft (6) and axial thrust ring (8) installed on it and used as an element of an axial bearing serving for axial support of shaft (6). It is proposed that axial thrust ring (8) includes the first cylindrical contact surface (14) serving for radial support on shaft (6) and the second conical contact surface (22) serving for self-adjustment on shaft (6).

EFFECT: creation of a rotor for a hydraulic machine, which is designed both for operation with chemically corrosive gases, and for operation at high rotation frequencies.

FIELD: engines and pumps.

SUBSTANCE: turbo-pump unit includes a turbine assembly comprising steam inlet and outlet housings, a nozzle block and a turbine. The unit includes a pump assembly comprising a housing with a screw centrifugal impeller of a closed type. The pump housing includes inlet and outlet housings and a projection-shaped rear annular element, which together form a flow cavity for arrangement of the impeller and an automatic rotor axial unloading mechanism. Blades of the impeller are of different length and variable height as to length, which decreases towards the impeller outlet with observance of a quasiequality condition of the cross sectional area at an interblade channel inlet. Number of blades at the outlet is divisible and exceeds at least by two times the number of blades at the inlet. Active volume of dynamic filling of a set of interblade impeller channels is equal to (4.7÷45)×10-5 m3/vol of pumped medium. A spiral tap of the pump assembly is made in the form of a two-way volatile with difference of surface areas of outlet and inlet sections of channels, which is related to the channel length, with an expansion gradient in swirling direction, which is accepted based on a quasiequality condition of velocities of flows in each channel of the volatile.

EFFECT: increasing service life, improving compactness, efficiency and operating reliability of the unit and medium pumping effectiveness at simultaneous reduction of material consumption.

18 cl, 7 dwg

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