Turbo-pump unit, and cold, hot and industrial water pumping method

FIELD: engines and pumps.

SUBSTANCE: turbo-pump unit includes turbine, support and pump assemblies. The turbine assembly includes steam inlet and outlet housings, a nozzle block and single-stage turbine. The pump unit includes a pump housing, a screw centrifugal impeller and an automatic rotor axial unloading device. The impeller s made in the form of a screw and a multiturn centrifugal pump of a closed type, which are combined. Blades of the latter 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 and interblade channels at the outlet is divisible, and exceeds at least by two times the number of blades and channels at the inlet. The screw is multiturn and has spiral blades and a hollow shaft; besides, it is equipped with smooth expansion in a transient zone of the screw channel to the multiturn channel of the centrifugal wheel. Screw blades have variable radius and/or pitch of spiral swirling and have a certain average gradient of swirling pitch increase.

EFFECT: increasing service life, improving operating reliability of a unit and pumping effectiveness of different liquid media to a consumer at simultaneous reduction of material consumption and improving compactness and efficiency of the unit.

19 cl, 7 dwg

 

The invention relates to turboboosting, namely the turbopump units designed to supply industrial water to the steam boilers, oil products at oil, gas, chemical and petrochemical, metallurgical and other business enterprises, as well as to a method of pumping mentioned liquid media.

Known turbopump Assembly containing the pump housing, turbine housing, bearing housing of the pump and the turbine, the spring-loaded rotor, the node unloading axial forces and fixed to the housings restrictive stops. Case turbine bearing support rigidly mounted in the intermediate casing. The emphasis in the case of turbine bearings made movable in the axial direction in the form of an elastic element and sleeve with stop axial movement by a bearing (EN 2083860 C1, publ. 10.07.1997).

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).

Famous torbenson the th unit, 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.

The Assembly also includes a bearing, powered by built-labyrinth pump, bearing, driven by a differential fluid pressure between the cavity of the turbine and the centrifugal wheel. 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 drive centrifugal wheel with holes, through which 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 TNA 100/580 with end seals on the bearings rolling: Proceedings of the VI international scientific-technical conference “SINT”11”, LLC “In ronicky 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 the units, lack of protection from cavitation of the pump and the low durability of the unit.

The present invention is to develop a turbopump unit, endowed with enhanced life, reliability and efficiency of supply fluid to the consumer while reducing material consumption and increasing the compactness and efficiency of the unit by reducing electricity consumption per unit mass of fluid, including raising variant of universality turbopump Assembly, and to develop a method of pumping a variety of fluids from the cold, hot water to the oil.

The task in part turbopump Assembly decides that the turbopump Assembly according to the invention contains the turbine site, forming the drive turbopump Assembly and including a housing supply working fluid of type pair, combined with the nozzle device made in the form of a disk inclined, preferably supersonic nozzles, active, at least a single-stage turbine having a shaft with impeller, consisting of at least one disk with blades and interscapular channels; and located behind the tour is given by the vector flow of the working fluid enclosure exhaust of the working fluid; in addition, the turbopump Assembly includes a support Assembly that consists attached to the housing of the exhaust of a working body body chassis turbopump Assembly with at least two bearing assemblies and chassis of the shaft, and the pump Assembly including a pump housing of the hydraulic end of the rotor shaft and sacienaasim impeller and the turbine shaft, the shaft of the chassis Assembly and the rotor shaft of the pump are integrated into a common drive shaft turbopump unit, in this case the flow of the pump 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 ring element connected to the housing of the entrance, as well as from the ledge in the cross section of the rear annular element, which together form a flow cavity with a volume sufficient to accommodate snakecharming impeller, axial machine unloading of the rotor and the spiral tap, with 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 vanes issue is lnany, preferably, 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 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; however, the screw is made, preferably, multiple 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°; and a helical auger blades are 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 the drug is stania step spiral twist G Wdefined in the range values of ΔGW=(0,25÷1.35) with m3/m

Active dynamic volume filling together interscapular channel impeller pump can be performed with a variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about. the pumped medium.

Auger snakecharming the pump impeller can be performed not less than dvukhzaryadnym with spiral blades having in the course of the flow of fluid lead-in section 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 that makes (85-250)°.

Blade centrifugal impeller 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%.

Spiral drain pump unit can be performed, preferably in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial twist and with a diffuse Pat tern of the RNO-expanding channels and a larger outlet cross section with respect to the input with a gradient expansion in the course of twist, adopted in compliance with the conditions of quasimomenta of flow rates in each channel of the cochlea.

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 machine axial unloading of the rotor can be made containing 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 education peritoneo annular channel having annular inner and outer side walls, and an annular abutment of the machine axial unloading rotor 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 at the outlet of peritoneo channel end gap seal with the possibility of an adjustable pulsating output of the last of the excess pumped environment, and formed between the return side walls of the annular ledge of the heel and the belt side slit seal is made with the possibility of pulsating passes peredachny channel fluid from the zone of high pressure axial machine is agrusti return in a low-pressure zone, preferably, the lead-in part of the 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.

On the top disk of the impeller of the pump may be made slit the seal, while the mechanical slit the seal on the main disk of the impeller is made with a 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 housing supply working fluid turbine site can be provided with an inlet pipe and a collector comprising an axisymmetric ring sealed envelope, at least a large part of which has the form type longitudinally truncated fragment of a torus or doughnut, is sealed from the pressure side to the drive nozzle apparatus on the outer and inner annular edges.

Nozzle nozzle apparatus can be performed in the disk 8÷15, mainly 12, and the longitudinal axes radially equidistant removed from the axis of the turbine, and are separated by an imaginary circle at equal angles in the range (24÷45)°.

The impeller blades of the turbine can is to be performed convexo-concave width, and the thickness of the vanes adopted variable in the direction of flow of the working fluid maximum, mainly in the middle part of the link width of the blade, while the link width of the blades in the projection conditional on link a plane connecting the input and output side edges of the blades, adopted not greater than the radial height of the blade, and the total number of blades of the impeller of the turbine taken 2.6÷34,4 times the number of nozzles in the nozzle unit.

Case exhaust of the working fluid can be made watertight with a beveled annular wall, an opposed output edges interscapular channels of the impeller of the turbine, and is equipped with a predominantly tangential outlet nozzle exhaust steam.

The shaft of the chassis Assembly can be made console, with one of the consoles forms a turbine shaft, and the other forms the pump shaft, and the shaft of the chassis with these consoles forms a common shaft turbopump Assembly.

The rotor shaft turbopump Assembly may be supported on the body chassis through the mentioned bearings, mainly equipped with ball bearings, one of which, preferably, is fixed in the axial direction, and the other, preferably made floating, both of these bearings are made with the possibility of C the shields working cavities seals, including type of labyrinths, while the rotor shaft is made hollow and is supplied to the duct with a liquid cooling system, and at least the bearing of the turbine is made with the possibility of additional air cooling by fan.

Turbopump Assembly can be mounted on a rigid, preferably, welded frame with the possibility of installing on the Foundation with the opportunity detachable fixation through a system of anchors.

Turbopump Assembly variant may be designed for pumping hot, cold, industrial water, oil and products of petroleum cracking with pressure up to 750 m and supply (flow) from 20 to 1000 m3/h, including at rated rotor speed 9,85·104(±20%)/min

The task in terms of how pumping is solved in that in the method of pumping hot and cold industrial water according to the invention, the pumping is carried out using at least one turbopump unit, structurally described above.

When pumping cold type of tap water can produce in the water supply systems of industrial, civil and residential complexes.

Pumping hot water can conduct, including excessive pressure up to 2 MPa or more and the temperature is dependent on the 85-105°C and the heating and/or hot water supply, industrial, civil and residential complexes.

Pumping industrial water can produce for power utility boilers, and industrial enterprises.

Technical result achieved given set of features, is to develop a turbopump unit, endowed with enhanced life, reliability and efficiency to deliver the pumped liquid media, as well as in the development of the method of delivery of the mentioned environments.

This is achieved by a set designed in the invention, design and technology solutions for the main units and the parameters of their work, namely the design of the rotor shaft with thrust bearing system of bearings and seals; the design of the impeller turbines, nozzles nozzle apparatus with the stated parameters; the shape of the manifold inlet and the housing outlet of the working fluid in the turbine site, and perform a pump unit with 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.

This implement is giving turbopump unit in the proposed invention the execution eliminates leakage of the pumped fluid and steam, and also simplifies Assembly, significantly reducing consumption and increasing the compactness and efficiency of the unit. In addition, the application of the drive steam turbines significantly reduces energy consumption.

The invention is illustrated by drawings, where:

figure 1 shows turbopump Assembly, side view;

figure 2 - turbopump Assembly, a longitudinal section;

figure 3 - blade impeller turbine section;

figure 4 - location of the nozzles in the nozzle disk apparatus, a longitudinal section;

figure 5 - snakesentence impeller pump, a longitudinal section;

figure 6 - centrifugal impeller pump, primary drive with blades, longitudinal section,

7 - centrifugal impeller pump and machine axial discharge of the rotor, fragment, longitudinal section.

Turbopump Assembly includes a turbine site 1, which forms the drive of the turbopump Assembly. Turbine site includes a casing 2 for supplying the working fluid of type pair, combined with the nozzle device 3, and is also active at least single-stage turbine and located behind the turbine of the vector flow of the working fluid housing 4 exhaust of the working fluid is steam.

Nozzle apparatus 2 is made in the form of a disk with inclined, preferably supersonic nozzles 5, which are made confused-diffuser. The turbine was settled and provided with a shaft 6 impeller 7, consisting of at least one disk with vanes 8 and interscapular channels.

Turbopump Assembly includes a support unit 9 comprising fixed to the body 4 of the exhaust steam housing 10 chassis turbopump Assembly with at least two bearing assemblies 11 and chassis of the shaft 12.

Turbopump Assembly also contains the pump Assembly 13, which includes a pump housing 14 of the flow part, the rotor shaft 15 and sacienaasim impeller 16.

When the turbine shaft 6, the shaft 12 of the chassis Assembly and the shaft 15 of the pump rotor from the common shaft turbopump Assembly.

Case 14 flow of the pump is made teams. The housing 14 of the pump includes a housing 17 of the entrance to the pipe 18 axial inlet for the fluid, the housing 19 of the outlet consists of a front annular element connected with the housing 17 and also from the ledge in the cross section of the rear annular element 20 associated with the front element. Together they form a flow cavity 21 with a volume sufficient to accommodate snakecharming impeller 16, the machine axial unloading of the rotor and spiral outlet 22. Snakesentence impeller 16 in the form of structurally combined with the auger 23 multiple centrifugal impeller, forming the impeller, preferably, Zack is itogo type.

The centrifugal impeller includes a core and covering disks 24 and 25, respectively, with the system located between the blades 26, separated interscapular channels 27. The blades 26 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 27 formed by two adjacent vanes 26 maximum length and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder 26 of smaller length. The number of blades 26 and respectively interscapular channels 27 on the output speed, not less than two times the number of blades and channels respectively at the entrance to the impeller 16.

The screw 23 is made, preferably, multiple spiral blades 28 of the hollow shaft 15, which, at least most of the length is made covering the wound in his section of the drive shaft turbopump Assembly. The screw 23 provided with a smooth expansion zone 29 of the transfer channel of the screw 23 in the multiple-channel centrifugal impeller, with an angle of inclination 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°.

Spiral blades 28 of the screw 23 is ispolneny, 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

ΔGW=(0,25÷4,35) m3/m

The active volume is dynamically populate the aggregate interscapular channels 27 of the impeller 16 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.

Auger 23 of the impeller 16 of the pump is made not less than dvukhzaryadnym with spiral blades 28, having in the course of the flow of fluid lead-in area 30 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)°.

The blades 26 of the centrifugal impeller 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 of ±15%.

Spiral bend 22 in the housing 14 of the pump is made, preferably, in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore extending channels 31 and a larger outlet cross section with respect to the input with a gradient expansion in the course of twist, adopted in compliance with the conditions of quasimomenta of flow rates in each channel of the cochlea.

To drain the fluid from flowing part of the housing 14 of the pump, the latter provided with a socket 32 of the allotment made, mainly, diffuser, tangential type.

The machine axial unloading of the rotor comprises an annular heel 33, the ledge is fixed or made on the back wall of the housing 14 flow of the pump. The machine axial discharge also includes an annular band 34 on the rear side of the main disk 24 of the impeller 16 and is coupled with the fifth with 33 education peritoneo annular channel 35 having an annular inner and outer side walls. The annular heel 33 of the machine axial unloading rotor provided with a circular table 36, the cantilever cross-section with a protruding rim, edge which made the return end of the inner wall of the belt 34 with the formation at the outlet of peritoneo channel 35 end gap seal 37 with the ability to regulate the dummy pulse output from the last of the excess fluid.

Formed between the return side walls of the annular ledge of the abutments 33 and belt 34 side slit seal 38 is made to provide the opportunity pulsating passes peredachny channel 35 for the fluid from the zone of high pressure machine of the axial discharge with a return to the zone of low pressure, preferably, in the lead-in part of the cavity of the impeller 16 performed mostly through the disk 24 of the impeller, at least one bypass hole 39 and the creation of this pulsating axial force changes unloading of the rotor.

On the covering disk 25 of the impeller 16 of the pump is made slit seal 40. Mechanical slit seal 37 on the primary disk 24 of the impeller 16 is made with a radius greater than the radius of the slotted seal 40 on the covering disk 25. The end of the abutment 33 of the machine axial unloading of the rotor is made of diameter less than or equal to the diameter of the slotted seal 40 on the covering disk 25 of the impeller.

Case 2 the supply of the working fluid turbine site 1 is equipped with a supply pipe 41, the collector 42 and the cover 43. The manifold 42 includes an axisymmetric ring sealed envelope, at least a large part of which has the form type longitudinally truncated fragment of a torus or doughnut, is sealed from the pressure side to the drive nozzle apparatus 3 through vneshnei inner annular edges 44.

Nozzle 5 nozzle apparatus 3 is executed in the disk 8÷15, mainly 12, the longitudinal axes radially equidistant removed from the axis of the turbine and are separated by an imaginary circle at equal angles in the range (24÷45)°.

The blades 8 of the impeller 7 of the turbine is made convex-concave across its width. The thickness of the blades 8 is adopted for the variable in the direction of flow of the working fluid with the maximum δmaxmainly in the middle part of the link width of the blade. Link width of the blades 8 in the projection conditional on link a plane connecting the input and output side edges of the blades, adopted not greater than the radial height of the blade. The total number of blades 8 of the impeller 7 of the turbine taken 2.6÷34,4 times the number of nozzles 5 in the nozzle unit 3.

Case 4 exhaust of the working fluid is airtight with a beveled annular wall 45, an opposed output edges interscapular channels of the impeller 7 of the turbine, and is equipped with a predominantly tangential nozzle 46 exit exhaust steam.

The shaft 12 of the chassis of the unit has a console, with one of the consoles forms a turbine shaft 6 and the other forms a shaft 15 of the pump. The shaft 12 of the chassis with these consoles forms a common shaft turbopump Assembly.

The rotor shaft turbopump Assembly operta the housing 10 of the chassis through the bearings 11, mainly, equipped with ball bearings 47, one of which, preferably, is fixed in the axial direction, and the other, preferably made floating. The ball bearings 47 are designed to protect workers cavities seals, including the type of labyrinths 48. The rotor shaft is made hollow and is supplied to the duct with a liquid cooling system. At least the bearing 47 of the turbine is made with the possibility of additional air cooling by fan 49.

Turbopump Assembly is mounted on a rigid, preferably, welded to the frame 50 with the possibility of installing on the Foundation with the opportunity detachable fixation through a system of anchors.

Turbopump Assembly variant is designed for pumping hot, cold, industrial water, oil and products of petroleum cracking with pressure up to 750 m and supply (flow) from 20 to 1000 m3/h, including at rated rotor speed 9,85·104(±20%)/min

In the method of pumping hot and cold industrial water pumping is performed by using at least one turbopump unit, structurally described above.

Pumping cold type water produced in the water supply system of industrial, civil and residential is kompleksow.

Pumping hot water produce including excessive pressure up to 2 MPa or more and a temperature of 85-105°C and the heating and/or hot water supply, industrial, civil and residential complexes.

Pumping industrial water to produce power utility boilers, and industrial enterprises.

Work turbopump Assembly is as follows.

After heating the structure and drain from the housing cavity 4 exhaust of the working fluid is steam turbine site 1 - start the turbopump Assembly. When this flow cavity 21 of the housing 14 of the pump is filled with the pumped liquid to the valve in the pressure line located at the outlet of the pump.

Open adjustable valve, feeding steam under pressure into the reservoir 42 and through the twelve nozzle 5 nozzle apparatus 3 at the turbine inlet. Dispersed pairs under the differential to supersonic speeds, passing the impeller 7 of the turbine kinetic energy. When the rotor of the turbine enters the rated speed 170-1(10200 rpm).

The unbalanced area of the turbine creates on the rotor axial force in the direction of the pump, through which the shaft takes the thrust bearing 47, which after reaching the rated speed compensates for the machine axial unloading.

In pumping node 13 Perekatov who controls the environment through pipe 18 for supplying, getting on the entrance to snakesentence impeller 16 is moved from the center to the periphery by centrifugal force, while gaining kinetic energy and getting a spin in the direction of impeller rotation.

After exiting the impeller 16, the flow moves to dvuhtochechny spiral tap 22, extending to the nozzle 32 of the exhaust fluid in compliance with the conditions of quasimomenta of flow rates in each channel 31 diversion. From the outlet 22 of the medium to be pumped enters the inlet 32 to the outlet and enters the pipeline for further transportation.

At the nominal speed of the rotor on snakesentence impeller pump 16 also applies axial force. This axial force directed toward the turbine and the heel 39 of the machine axial discharge because of a difference of diameters of the slot seals 38, 40 on the impeller and the location of the gap end gap seal 37. Under the influence of a specified axial force to the rotor moves, or reducing the mechanical clearance between the impeller 16 and 39 fifth, or Vice versa, revealing a gap in the end-cap seal 37, is the equilibrium position, compensating axial force on the thrust bearing 47.

Mechanical seal 51 in the housing cavity 4 exhaust steam does not pass pumping and cooling them with liquid on one side of the cavity of the turbine for IP is your hammer when water gets into the hot cavity and exclusion of moisture vapor, leading to erosion of structural elements. On the other hand do not let water condensation in the cavity reference node 9, which is communicated with the atmosphere through the opening 52 in the bottom area of the housing 10 chassis, designed to drain the allowable leakage.

Additionally, the bearing 47 secured rotating labyrinth seal 48 that provides for the evacuation of water and steam arising from the interaction with a hot body 4 of the turbine exhaust through the opening 52 in the housing 10 of the chassis. Similarly, in a pump set single mechanical seal 53, not admitting fluid into the bearing cavity, separated rotating labyrinth seal 48. In case of minor leakage of the mechanical seal 53 they are derived from the flow cavity 21 through the opening 52 in the housing 10 of the chassis. In the process turbopump Assembly, the rotor and the ball 47 is cooled by blowing air through the fan 49.

During operation, the rotor is fixed with two sensors 54 speed and vibration sensors arranged on the housing 10 of the chassis. Fixed velocity, which must not exceed allowable values.

Stop turbopump Assembly carried out by closing the valve in the steam supply, and after the pressure drop between the pump and the rotor stops close for wieku on the discharge side of the pump. Water for cooling mechanical seals 53 are served in the cavity of the turbine site 1 to cool the turbine casing.

Thus, due to the developed invention design and technology solutions for the major units and their work achieve greater resource unit, reliability and efficiency of supply fluid to the consumer while reducing material consumption and increasing the compactness and efficiency of the turbopump Assembly.

1. Turbopump Assembly, characterized in that it includes a turbine hub, forming the drive turbopump Assembly and including a housing supply working fluid of type pair, combined with the nozzle device made in the form of a disk inclined, preferably supersonic nozzles, active, at least a single-stage turbine having a shaft with impeller, consisting of at least one disk with blades and interscapular channels; and located behind the turbine of the vector flow of the working fluid enclosure exhaust of the working fluid; in addition, the turbopump Assembly includes a support Assembly that consists attached to the housing of the exhaust a working body body chassis turbopump Assembly with at least two bearing assemblies and chassis of the shaft, and the pump Assembly, on the expectation of the pump housing of the flow part, the rotor with the shaft and sacienaasim impeller and the turbine shaft, the shaft of the chassis Assembly and the rotor shaft of the pump are integrated into a common drive shaft turbopump unit, in this case the flow of the pump 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 ledge in the cross section of the rear annular element, which together form a flow cavity with a volume sufficient to accommodate snakecharming impeller, axial machine unloading of the rotor and the spiral tap, with snakesentence impeller made in the form of structurally combined 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 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 on which ihade 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; however, the screw is made, preferably, multiple 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 area extension shaft 18°÷30°; and a helical auger blades are 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) with m3/m

2. Turbopump Assembly according to claim 1, characterized in that the 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)×10-5 m3/about. the pumped medium.

3. Turbopump Assembly according to claim 1, characterized in that the screw snakecharming impeller of the pump is made not less than dvukhzaryadnym with spiral blades having in the course of the flow of fluid lead-in section 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 that makes (85-250)°.

4. Turbopump Assembly according to claim 1, characterized in that the blades of the centrifugal impeller 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%.

5. Turbopump Assembly according to claim 1, characterized in that the spiral drain pump unit is designed preferably in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels and a larger outlet cross section with respect to the input with a gradient expansion in the course of twist, adopted in compliance with the conditions is waterwaste of flow rates in each channel of the cochlea.

6. 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.

7. Turbopump Assembly according to claim 1, characterized in that the machine axial unloading of the rotor is constructed containing 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 education peritoneo annular channel having annular inner and outer side walls, and an annular abutment of the machine axial unloading rotor 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 at the outlet of peritoneo channel end gap seal with the possibility adjustable pulsating output of the last of the excess fluid, and formed between the return side walls of the annular ledge of the heel and the belt side slit seal is made with the possibility of pulsating passes peredachny channel fluid from the zone of high pressure axial machine razgruzki the return in a low-pressure zone, preferably, the lead-in part of the 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.

8. Turbopump Assembly according to claim 7, characterized in that on the top disk of the impeller of the pump is made slit the seal, while the mechanical slit the seal on the main disk of the impeller is made with a radius greater 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.

9. Turbopump Assembly according to claim 1, characterized in that the housing supply working fluid turbine Assembly is provided with inlet pipe and a collector comprising an axisymmetric ring sealed envelope, at least a large part of which has the form type longitudinally truncated fragment of a torus or doughnut, is sealed from the pressure side to the drive nozzle apparatus on the outer and inner annular edges.

10. Turbopump Assembly according to claim 1, characterized in that the nozzles of the nozzle unit is made in the disk 8÷15, mainly 12, and the longitudinal axes radially equidistant removed from the axis of the turbine and the e are separated by an imaginary circle at equal angles, defined in the range (24÷45)°.

11. Turbopump Assembly according to claim 1, characterized in that the impeller blades of the turbine are made convex-concave width, and the thickness of the vanes adopted variable in the direction of flow of the working fluid maximum, mainly in the middle part of the link width of the blade, while the link width of the blades in the projection conditional on link a plane connecting the input and output side edges of the blades, adopted not greater than the radial height of the blade, and the total number of blades of the impeller of the turbine taken 2.6÷34,4 times the number of nozzles in the nozzle unit.

12. Turbopump Assembly according to claim 1, characterized in that the housing of the exhaust of the working fluid is airtight with a beveled annular wall, an opposed output edges interscapular channels of the impeller of the turbine, and is equipped with a predominantly tangential outlet nozzle exhaust steam.

13. Turbopump Assembly according to claim 1, characterized in that the shaft of the chassis of the unit has a console, with one of the consoles forms a turbine shaft, and the other forms the pump shaft, and the shaft of the chassis with these consoles forms a common shaft turbopump Assembly.

14. Turbopump Assembly according to claim 1, characterized in that the rotor shaft turbopump Assembly supported n the body chassis through the mentioned bearings, mainly, equipped with ball bearings, one of which, preferably, is fixed in the axial direction, and the other, preferably made floating, both of these bearings are designed to protect workers cavities seals, including the type of labyrinths, while the rotor shaft is made hollow and is supplied to the duct with a liquid cooling system, and at least the bearing of the turbine is made with the possibility of additional air cooling by fan.

15. Turbopump Assembly according to claim 1, characterized in that mounted on a rigid, preferably, welded frame with the possibility of installing on the Foundation with the opportunity detachable fixation through a system of anchors.

16. Turbopump Assembly according to claim 1, wherein the variant is designed for pumping hot, cold, industrial water, oil and products of petroleum cracking with pressure up to 750 m and supply (flow) from 20 to 1000 m3/h, including at rated rotor speed 9,85·104(±20%)/min

17. The method of pumping hot and cold industrial water, characterized in that the pumping is carried out using at least one turbopump Assembly, which is made according to any one of claims 1 to 16.

18. Way lane is kakivaya on 17, characterized in that the pumping cold type water produced in the water supply system of industrial, civil and residential complexes.

19. The method of pumping through 17, characterized in that the pumping of hot water produced including excessive pressure up to 2 MPa or more and a temperature of 85-105°C and the heating and/or hot water supply, industrial, civil and residential complexes.

20. The method of pumping through 17, characterized in that the pumping industrial water to produce power utility boilers, and industrial enterprises.



 

Same patents:

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: engines and pumps.

SUBSTANCE: invention relates to pump engineering, particularly to electrically driven pump for transfer of chemically aggressive fluids. Proposed unit comprises motor, rotary pump and coupling. Single-stage cradle-mounted pump comprises housing with running and flow housings. Flow housing comprises collector case integrated with pressure pipe and having circular stepped ledge, rear wall composed by circular stepped ledge and circular stepped ledge, and detachable lead-in cover with axial feed pipe. Running section housing has crankcase and bearings. Exposed impeller is composed of multifilar impeller with main disc with hub and set of blades and circular ledge arranged in outline. Ledge outer radius is congruent with mating inner radius of circular steeped ledge. Said disc a vaned impeller. Pump has hydraulic lock composed of said separate disc with vaned impeller fitted on the shaft. Impeller radius is smaller than that of working wheel.

EFFECT: protection against leaks, longer life, higher reliability, non-polluting design.

13 cl, 5 dwg

FIELD: engines and pumps.

SUBSTANCE: pump composite housing, rotor with shaft and impeller and power drive are produced. Pump running part housing is equipped with bearings. Pump flow section housing has flow section to accommodate impeller and involute collector. Said impeller represents encases multifilar impeller with the main and cover discs. Hydraulic lock composed of independent disc with impeller and circular removable element are arranged behind the main disc. Hydraulic lock impeller radius is smaller than that of impeller. Impeller main disc is equipped with circular ledge. Said ledge makes with impeller hub wall a circular channel communicated with hydraulic lock and, via through bore in main disc, directly with impeller inner surface. Pump is assemble and mounted at pump and drive bearing platform with the help of half-couplings. After assembly, pump unit is tested.

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

22 cl, 7 dwg

FIELD: engines and pumps.

SUBSTANCE: turbine assembly of the unit includes a working medium - steam supply housing, a nozzle block with inclined nozzles, a turbine having a shaft with a runner, and a waste steam outlet housing located downstream of the turbine in the steam flow direction. The steam supply housing is equipped with a header including an axisymmetrical annular cover having the shape of a flattened fragment of a tore or a toroid. The turbine runner us made at least of one disc with blades. Blades are convex-concave as to width and have radial height comprising (0.05÷0.25) of the disc radius. The blade thickness is variable in the direction of steam flow with maximum in the middle part of the blade chord width. The chord width of the blade in the projection to a conditional chord plane attaching inlet and outlet side edges of the blade does not exceed radial height of the blade. The nozzles are made in the disc in the amount of 8÷15, located radially at equal distance with their longitudinal axes from the turbine axis and equally spaced in a conditional circumferential direction at equal angles determined in the range of (24÷45)°. Total number of blades exceeds by 2.6÷34.4 times the number of nozzles.

EFFECT: increasing service life, improving reliability and operating efficiency of a turbine assembly at simultaneous reduction of material consumption and improving compactness of the assembly.

9 cl, 3 dwg

FIELD: engines and pumps.

SUBSTANCE: turbo-pump unit includes a turbine assembly with working medium inlet and outlet housings, a nozzle block and a single-stage turbine. The unit includes a pump assembly with a screw centrifugal impeller. The working medium supply housing is equipped with a manifold including an axisymmetrical tight annular cover. The large part of the cover has the shape of a longitudinally flattened fragment of a tore or a toroid. Turbine runner blades are convex-and-concave as to width, radial height of 0.05÷0.25 of the turbine runner disc radius. The blade thickness is accepted as variable in the direction of working medium flow vector with maximum in the middle part of the blade chord width. The chord width of the blade in the projection to a conditional chord plane attaching inlet and outlet side edges of the blade does not exceed radial height of the blade. The inter-blade channel is of a confuser-and-diffuser type in the direction of the steam flow vector with maximum constriction of flow cross sectional area determined in zone of maximum thickness of blades. Total number of turbine runner blades exceeds by 2.6÷34.4 times the number of nozzles in the nozzle block.

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

19 cl, 6 dwg

Turbo-pump unit // 2459118

FIELD: engines and pumps.

SUBSTANCE: unit contains pumps of oxidiser and fuel with spline joined shafts, turbine wheel is fastened on one of shafts. Unit contains dummy piston of automatic unloading machine, the piston is combined with the main propeller disk of one of pumps. Unloading machine is restricted by radial seal in peripheral part of the main disk and by control axial slot near propeller hub. Ball bearing of this pump is designed with outer ring installed in housing with axial gap, ball bearing of the second pump is designed with axial stop located in housing with gap along butt end of ball bearing outer ring. Shaft of one pump with backing butt-end rest on backing butt-end of shaft of the second pump. Gaps along butt-ends of axial stop of outer ring of ball bearing of pump without unloading machine are designed larger than corresponding axial gaps along butt-ends of outer ring of ball bearing of pump with unloading machine.

EFFECT: improving efficiency factor of turbo-pump unit and enhancing pump anticavitation properties.

3 cl, 3 dwg

Hydraulic pulsator // 2457367

FIELD: machine building.

SUBSTANCE: hydraulic pulsator comprises feed branch pipe 1, guide vanes 2, vaned impeller 7, pressure branch pipe 21, discharge branch pipe 22, radial and axial bearings for impeller shaft 23 to run in.Vanes and channels of guide vanes 2 are arranged in mutually shifted sectors so that vanes 5 forming pressure channels are arranged above drain channels 3 formed by vanes 3. Impeller 7 incorporates main and supplementary vanes that form drain and pressure channels 11 and 15, respectively, arranged in sectors shifted in height.

EFFECT: simplified design, higher reliability and efficiency.

2 cl, 3 dwg

FIELD: engines and pumps.

SUBSTANCE: pump includes bodies 8, 26, 28, centrifugal impeller 2 with hub 3, which is installed on shaft 1, and screw 15. Shaft 1 is installed in bearing 7 protected with seal 40. Inside hub 3 on bearings 10, 11 there is installed intermediate shaft 9 so that a gap is formed. Inner shaft 12 having axial non-through hole 34 is formed inside intermediate shaft 9 on bearings 13, 14 so that a gap is formed. On the end of shaft 12, on the pump inlet side there installed is screw 15, and impeller 16 of hydraulic turbine 17, which is installed inside shaft 1, is fixed on opposite end. On shaft 9, on the inlet side between screw 15 and impeller 2 there installed is screw 19, and on the other end - impeller 20 of hydraulic turbine 21. Rear seal 31 under which discharge cavity 32 is made is provided on impeller 2. Shaft 1 is hollow and has front, middle and rear cavities 23, 24 and 25. Hydraulic turbine 17 is installed between cavities 24, 25 and hydraulic turbine 21 is installed between cavities 24, 23. Inner thrust bearing 14 is installed inside nozzle assembly 22 of hydraulic turbine 21. Cavity 32 is connected through hole 42 made in shaft 1 to cavity 25. In hub 3 there made are through holes 33 connecting cavity 23 to cavity 6 of impeller 2.

EFFECT: improving cavitation properties of pump and providing unloading of axial forces of inner and intermediate shafts.

3 cl, 2 dwg

FIELD: engines and pumps.

SUBSTANCE: pump includes body, centrifugal impeller 2 with hub 3, which is installed on shaft 1, and screw 15. Shaft 1 is installed in the main bearing 7 protected with seal 40 so that cavity 41 is formed between them. Inside hub 3 on bearings 10, 11 there is installed intermediate shaft 9 so that a gap is formed, and inner shaft 12 having axial non-through hole 34 is formed inside intermediate shaft 9 on bearings 4, 13 so that a gap is formed. On the end of shaft 12, on the inlet side there installed is screw 15, and impeller 16 of hydraulic turbine 17, which is installed inside shaft 1, is fixed on opposite end. On shaft 9, on the inlet side between screw 15 and impeller 2 there installed is screw 19, and on the other end - impeller 20 of hydraulic turbine 21. Seal 31 under which discharge cavity 32 is made is provided on impeller 2. Shaft 1 is hollow and has front, middle and rear cavities 23-25. Hydraulic turbine 17 is installed between cavities 24, 25 and hydraulic turbine 21 is installed between cavities 23, 24. Bearing 4 is installed inside nozzle assembly 22 of hydraulic turbine 21. Discharge cavity 32 is connected through hole 45 in shaft 1 to cavity 24. Cavity 41 is connected through channel 42 to pump outlet and to cavity 25. In hub 3 there made are holes 33 connecting cavity 23 to cavity 6 of impeller 2.

EFFECT: improving cavitation properties of pump and providing unloading of axial forces of inner and intermediate shafts.

4 cl, 4 dwg

FIELD: power industry.

SUBSTANCE: blower contains cylindrical housing 1 inside which there located is evaporation, working and condensing chambers 8, 10, 15. End walls 2, 3 are connected by means of central wick 4 covered with shell 5 so that gaps 6, 7 are formed at walls 2, 3 and passing along central axis. In evaporation and condensing chambers 8, 15 the inner surface of side wall and end walls 2, 3 are covered with grid 16 made from thin layer of porous material and connected in the centre of end walls 2, 3 with central wick 4. Inside working chamber 10 there are power turbines 11,12 which are coaxially located one after another, rigidly attached to inner surface of its wall and outer surface of shell. On outer surface of working chamber 10 there is impeller 13. Outer housing 17 covering impeller 13 is helical.

EFFECT: increasing efficiency of heat-pipe centrifugal blower.

2 dwg

Turbine pump // 2423621

FIELD: engines and pumps.

SUBSTANCE: turbine pump comprises bodies 10, 23, a centrifugal pump 1, a screw 14, turbines 15, 16. The centrifugal pump comprises a centrifugal impeller 4 with a hub 5, installed on an outer hollow shaft 3, which is installed in a bearing 9, protected with a seal 47. The turbines 15, 16 comprise nozzle blocks 21, 22 and impellers 17, 18, a body 23, an input and an output nozzles 51, 52. Inside the shaft 3 on bearings 12, 13 there is an inner shaft 11. The impellers 17, 18 of the turbines 15, 16 are installed accordingly on an inner and an outer shafts 3, 11. The screw 14 is installed on the outer shaft 3, at the same time the impeller 18 of the second turbine 16 is arranged with a smaller diameter compared to the impeller 17 of the first turbine 15 and is installed in the back cavity 25, arranged inside the body 23 of the turbines 15, 16 in its central part. The channel 53 of gas supply to the second turbine 16 is arranged in the diaphragm 49, and the channel of gas bleed - in the form of one or several tubes 54, which connect the back cavity 25 with the outlet nozzle 52 of turbines.

EFFECT: improved cavitation properties of a pump included into a composition of a turbine pump and unloading of axial forces in inner and outer shafts.

3 cl, 6 dwg

Turbo-pump unit // 2418989

FIELD: engines and pumps.

SUBSTANCE: unit includes housings 10, 18-20, 22, 23, pump 1 and gas turbine 2. Pump 1 includes screw 11, centrifugal impeller 4 with hub 5 having inner cavity 27 and which is installed on shaft 3 which is installed in bearing 9 protected with seal 31. Turbine 2 includes at least one stage with guide vanes 17 and impeller 15. Screw 11 is installed on shaft 3 with possibility of sliding. Before screw 11 there installed is hydroturbine 12 rigidly attached to it, and before hydroturbine 12 there installed is additional screw 13 having bandage 14 rigidly attached to centrifugal impeller 4. Inside hub 5 there is inner cavity 27 and through holes 28 attaching inner cavity 27 of hub 5 to cavity 8 inside impeller 4. Inside through holes 28 there installed are centrifugal flow controls 35.

EFFECT: improving cavitation properties of pump included in turbine-pump unit, and providing removal of axial forces.

4 cl, 6 dwg

Turbo-pump unit // 2418988

FIELD: engines and pumps.

SUBSTANCE: unit includes housings 14, 15 34, 35, 37, 44, 45, 47, two screws 33, 43 and two centrifugal impellers 31, 41 with hubs 32, 42, which are installed on shafts in bearings 53-55 protected with seals 56-58, and three gas turbines 4-6 installed in housing 14 with suction and exhaust nozzles 16, 18. Turbines 4-6 include guide vanes 10-12 and impellers with blades 7-9. Between outer and inner shafts 28 and 30 there installed is intermediate shaft 29. Impeller of the first turbine 4 is installed on outer shaft 28, impeller of the second turbine 5 is installed on intermediate shaft 29, and impeller of the third turbine 6 is installed on inner shaft 30. The first centrifugal impeller 31 of pump 2 is installed closer to turbine 4 on outer shaft 28. The first screw 33 and the second impeller 41 of pump 3 are installed on intermediate shaft 29. The second screw 43 is installed on inner shaft 30.

EFFECT: improving cavitation properties of pumps included in turbine-pump unit, and providing removal of forces from all shafts.

4 cl, 1 dwg

FIELD: shipbuilding, rocketry, aircraft, chemical and other industries.

SUBSTANCE: invention relates to hydraulic machine building and it can be used in industries where stringent requirements to reliability, cavitation, and variable characteristics at minimum mass of construction are placed. Proposed turbopump contains sliding bearings lubricated by handled liquid, axial vortex stage with conical bushing of screw and additional channels with restrictors connecting pressure and intake parts. To reduce overall dimensions and increase reliability, hydraulic balancing device and rear bearing are combined. Pulsations are reduced owing to division of liquid and gas-phase leaks and their removal along separate pipelines. Relief holes are made in turbine disk to reduce axial force at non-standard conditions.

EFFECT: improved reliability and stability of turbopump set within wide range of changes of flow rate of handled liquid, improved cavitation characteristics, reduced weight and overall dimensions.

3 cl, 1 dwg

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