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

FIELD: engines and pumps.

SUBSTANCE: turbo-pump unit includes a turbine assembly comprising a steam inlet housing, a nozzle block with inclined convergent-divergent nozzles, a turbine having a shaft with a runner, and a waste steam outlet housing located downstream of the turbine. The steam inlet housing is equipped with a supply connection pipe and a header including an axisymmetrical annular cover, the larger part of which has the shape of a tore or toroid fragment. The header is attached to the nozzle block disc. The nozzles of the block are made in the disc in the amount of 8÷15, are located radially at equal distance with their longitudinal axes from the turbine axis and equally spaced in a circumferential direction at equal angles determined in the range of (24÷45)°. Longitudinal axis of each nozzle is located in a conditional plane parallel to the turbine shaft axis normally to the turbine shaft axis, normally to radius and inclined in the above plane at an angle to the conditional plane of the disc in the direction opposite to rotation vector of the turbine runner at an angle of (12÷25)°. The pump assembly of the unit includes a pump housing with a screw centrifugal impeller.

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

19 cl, 6 dwg

 

The invention relates to turboboosting, namely the turbopump units designed to supply industrial water to the steam boilers and oil products in 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).

Known turbocharger used in Sony 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 "Raven is Skye 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 the type of gas, combined with the nozzle device made in the form of a disk inclined, preferably supersonic nozzles, which are made confused-diffuser, as well as active, at least a single-stage turbine having a shaft with impeller, consisting of at least one disk with blades and milupa the face-to-face channels, and, in addition, 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 chassis exhaust the chassis undercarriage turbopump Assembly with at least two bearing assemblies and chassis of the shaft, and the pump Assembly including a pump housing, a rotor with a shaft and sacienaasim impeller, the turbine shaft, the shaft of the chassis Assembly and the rotor shaft of the pump are integrated into a common shaft turbopump Assembly, in addition, the housing supply working fluid turbine Assembly is provided with the inlet pipe and 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, which is tightly connected with the discharge side radially equidistant about the axis of the shaft of the turbine to the nozzle disk apparatus on the outer and inner annular edges, and nozzle nozzle of the device is made in the disk 8÷15 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)°, while the spatial removal of the axes of the nozzles are fixed at the point of intersection of the latter with conditional PLoS is awn drive nozzle apparatus, as the radial distance of each of these points from the axis of the turbine shaft made of not less than one third of the radial height of the impeller blades of the turbine radial distance transverse root sections mentioned blades to the turbine shaft, in addition, the longitudinal axis of each nozzle nozzle apparatus is located in an imaginary plane parallel to the axis of the turbine shaft, is normal to the radius and inclined at the specified plane at an angle to an imaginary plane of the disk in the direction opposite to the direction of rotation of the impeller of the turbine at an angle (12÷25)°.

In this case the 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 spent working fluid.

The annular shell collector turbine site can be hermetically attached to the drive nozzle apparatus with the gamut of the input estuaries nozzles on the outer and inner annular edges, preferably by welding.

The impeller blades of the turbine can be 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 blades, etc is this link the width of the blades in the projection conditional on the link 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.

The impeller blades of the turbine can be radially removed from the axis of the shaft of the turbine, not less than 0,8R, where R is the radius of the disc of the impeller of the turbine, and evenly spaced around the circumference of the disk with a gradient Radiani density G determined in the range

Grad. G (10÷44) [u/rad],

where the gradient G is a numerical characteristic of blades placed in the angular range of one radian.

Interscapular channel impeller turbines can be performed confused-diffuser in the direction of flow of the working fluid with the maximum narrowing of the cross-flow area S defined in the zone of maximum thickness of the blades δmaxfrom the expression

S=ΔR(2πR-Tδmax)/T,

where ΔR is the radial height interscapular channel, T is the number of interscapular channels according to the number of disk blades of the impeller of the turbine.

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 is gregate can 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 ball 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.

The pump casing can be 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 with the housing inlet, and provided with a pipe outlet, made mainly diffuser, tangential type, 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 pump housing and spiral drainage pumping node, prefer the Ino, as 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 of quasimomenta of flow rates in each channel of the cochlea.

Snakesentence the impeller may be 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 impeller blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller, with the number of blades taken from 4 to 16, preferably 12, and the screw snakecharming impeller of the pump is made not less than dvukhzaryadnym, equipped with a smooth expansion in the transition zone of the channel of the screw in multiple-channel centrifugal wheel and spiral blades, made mainly with variables, at least part of the length of the radius and pitch of the spiral twist, having in the course of the flow of fluid lead-in section with an angle of twist of the spiral increments is elicina radius of each of the blades from 0 to R in the angular range, component (85-250)°, and the gradient G of the step angle of twist of each blade within the axial length of the spiral auger is defined in the range G=(17÷70)π rad/m

The machine axial unloading of the rotor may include an annular heel, the ledge is fixed or made on the back wall of the pump housing and 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 comprising side and end gap-type seals made with the possibility of a self-regulating flow fluid from the zone high zone low pressure mentioned centrifugal wheel to regulate the axial unloading of the rotor turbopump Assembly.

The basis of the drive snakecharming impeller may be provided in the basal part of the disk, at least one peritonism the opening and covering the disk is made adjacent to the building entrance for the fluid through the slit seal.

Case exhaust of the working fluid in the turbine unit may be equipped with mechanical seals to ensure the integrity of structural connectors.

Turbopump Assembly can be mounted on a rigid, preferably, welded frame with the possibility of installing on the base with the prob is the possibility 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 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 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 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.

Thus the performance turbopump unit in the proposed invention the execution eliminates leakage of the pumped fluid and the working fluid, and also simplifies Assembly, significantly reducing consumption and increasing the compactness and efficiency of the unit. In addition, the application of the drive gas turbines significantly reduces energy consumption.

The invention is illustrated by drawings, where:

1 shows a turbopump unit, view of the side;

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 the blades 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 the type of gas, combined with the nozzle device 3, as well as active, at least a single-stage turbine and located behind the turbine of the vector flow of the working fluid housing 4 exhaust of the working fluid is a gas.

Nozzle apparatus 3 is executed in the form of a disk with inclined, preferably supersonic nozzles 5, which are made confused-diffuser. The turbine is 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 gas casing 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, including housing the pump 14, 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 2 the supply of the working fluid turbine site 1 provided with the inlet pipe 17, the collector 18 and the cover 19. The manifold 18 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, which is tightly connected with the discharge side radially equidistant about the axis of the shaft 6 of the turbine to the nozzle disk apparatus 3 through the outer and inner annular edges 20.

Nozzle 5 nozzle apparatus 3 is executed in the disk number 8-15 and 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)°. Spatial destruction of the axes of the nozzles 5 is fixed at the point of intersection of the latter with a nominal plane of the disk nozzle apparatus 3. The radial distance of each of these points from the axis of the shaft 6 of the turbine taken not less than one-third of the radial height of the blade 8 of the impeller 7 of the turbine radial distance transverse root sections mentioned blades to the shaft 6 of the turbine. The longitudinal axis of each nozzle 5 nozzle apparatus 3 is located in an imaginary plane, parallel to the axis of the shaft 6 of the turbine, is normal to the radius and inclined at the specified plane at an angle to an imaginary plane of the disk nozzle apparatus 3 in the direction opposite to the direction of rotation of the impeller 7 of the turbine at an angle (12÷25)°.

Case 4 exhaust of the working fluid is airtight with a beveled annular wall 21, the opposed output edges interscapular channels of the impeller 7 of the turbine, and is equipped with a predominantly tangential inlet 22 of the output of the spent working fluid.

The annular shell of the collector 18 of the turbine site 1 is hermetically attached to the drive nozzle apparatus 3 with the gamut of the input estuaries nozzles 5 to the outer and inner annular edges 20, preferably by welding.

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 maximum, mainly 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 vanes 8, adopted not greater than the radial height of the blade 8. 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.

The blades 8 of the impeller 7 of the turbine radially removed the t axis of the shaft 6 of the turbine, not less than 0,8R, where R is the radius of the disc of the impeller 7 of the turbine, and evenly spaced around the circumference of the disk with a gradient Radiani density G determined in the range

Grad. G=(10÷44) [u/rad],

where the gradient G is a numerical characteristic of the blades 8, placed in the angular range of one radian.

Interscapular channel impeller 7 of the turbine performed confused-diffuser in the direction of flow of the working fluid with the maximum narrowing of the cross-flow area S defined in the zone of maximum thickness of the blades δmaxfrom the expression

S=ΔR(2πR-Tδmax)/T,

where ΔR is the radial height interscapular channel;

T - the number of interscapular channels according to the number of disk blades of the impeller of the turbine.

The shaft 12 of the chassis of the unit has a console. While 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 supported on the housing 10 of the chassis through the bearings 11, mainly equipped with ball bearings 23, one of which, preferably, is fixed in the axial direction, and the other, preferably made floating. The bearings 23 are designed to protect workers cavities seals, including the type of l is of Perinton 24. The rotor shaft is made hollow and is supplied to the duct with a liquid cooling system, and at least the bearing 23 of the turbine is made with the possibility of additional air cooling by fan (not shown).

The housing 14 of the pump is made teams. The housing 14 includes a housing 25 of the entrance to the pipe 26 axial inlet for the fluid, the housing 27 of the outlet consists of a front annular element connected to the housing 25 of the inlet, and provided with a socket 28 way, made mainly diffuser, tangential type, as well as from the back of the ring element 29 that is associated with the front annular case element 27-of-way. Together they form a flow cavity 30 with a volume sufficient to accommodate snakecharming impeller 16, the machine axial unloading of the rotor and the spiral-of-way. The rear annular element 29 of the housing 27 of the allotment made the ledge in cross section and combined with the inner side of a rear wall of the housing 14 of the pump.

When this spiral allotment is made, 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 gradient expansion for x is DN twist, adopted in compliance with the conditions of quasimomenta of flow rates in each channel of the cochlea.

Snakesentence impeller 16 in the form of structurally combined with the auger 31 multiple centrifugal impeller, forming the impeller, preferably of the closed type. The centrifugal impeller includes a core and covering disks 32 and 33, respectively, with the system located between the blades 34, separated interscapular channels 35. The blades 34 of the centrifugal impeller is made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller. The number of blades 34 taken from 4 to 16, preferably 12.

Auger 31 snakecharming impeller 16 of the pump is made not less than dvukhzaryadnym, equipped with a smooth expansion in the zone 36 of the transfer channel of the screw 31 in the multiple-channel centrifugal wheel and spiral blades 37. The blades 37 are made mainly with variables, at least part of the length of the radius and pitch of the spiral twist and have in the course of the flow of fluid lead-in section 38 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)°. The gradient G of the step angle of twist of each blade 37 within the axial length of the spiral auger 37 the definition is in the range of G=(17÷70)π rad/m

The machine axial unloading of the rotor comprises an annular heel 39, the ledge is fixed or made on the back wall of the housing 14 of the pump. The machine also includes an annular band 40 on the rear side of the main disk 32 snakecharming impeller 16 and is coupled with the fifth 39 education peritoneo annular channel 41. Peredachny channel 41 includes side and end gap-type seals 42 and 43, respectively, and made with the possibility of a self-regulating flow fluid from the zone high zone low-pressure centrifugal impeller with providing regulation of the axial discharge of the turbopump rotor Assembly. The base disk 32 snakecharming impeller 16 is supplied in the basal part of the disk 32, at least one peritonism hole 44. Covering the disk 33 snakecharming impeller 16 is made adjacent to the building entrance for the fluid through the slit seal 45.

Case 4 exhaust of the working fluid in the turbine site 1 is equipped with mechanical seals 46 to ensure the integrity of structural connectors.

Turbopump Assembly is mounted on a rigid, preferably, welded frame 47 with the possibility of installing on the Foundation with the opportunity detachable fixation through a system of anchors.

The turbocharger used in the axle 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 complexes.

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 a gas turbine site 1 launch turbopump Assembly. When this flow cavity 30 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 that supplies gas under Yes the population in the manifold 18 and through the twelve nozzle 5 nozzle apparatus 3 at the turbine inlet. Dispersed gas 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 23, which after reaching the rated speed compensates for the machine axial unloading.

In pumping node 13 the medium to be pumped through the pipe 26 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, extending to the inlet 28 of the exhaust 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 28 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 42, 45 on the impeller 16 is the location of the gap end gap seal 43. Under the influence of a specified axial force to the rotor moves, or reducing the mechanical clearance between the impeller 16 and the fifth 39 or Vice versa revealing the gap in the end seal 43, is the equilibrium position, compensating axial force on the thrust bearing 23.

Mechanical seal 46 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, ensuring the tightness of the connectors in the whole range of operating temperatures and preventing erosion of structural elements. On the other hand do not allow the condensate into the cavity reference node 9, which is communicated with the atmosphere through the opening 48 in the bottom area of the housing 10 chassis, designed to drain the allowable leakage.

Additionally, the bearing 23 secured rotating labyrinth seal 24, which ensures the evacuation of the condensate arising from the interaction with a hot body 4 of the turbine exhaust through the opening 48 in the housing 10 of the chassis. Similarly, in a pump set single mechanical seal 49, not admitting fluid into the bearing cavity, separated rotating labyrinth seal 24. In case of minor leakage of the mechanical seal 49 are derived from the flow cavity 30 through the opening 48 in the housing 10 of the chassis. In processability turbopump Assembly, the rotor and the bearings 23 is cooled by blowing air through the fan.

During operation, the rotor is fixed with two sensors 50 rpm 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 and close the valve on the discharge side of the pump. Water for cooling mechanical seals 46 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 reach a higher 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 the type of gas, combined with the nozzle device made in the form of a disk inclined, preferably supersonic nozzles, which are made confused-diffuser, as well as active, at least a single-stage turbine having a shaft with impeller, consisting of not m is it than one disk with blades and interscapular channels, and, in addition, 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 chassis exhaust the chassis undercarriage turbopump Assembly with at least two bearing assemblies and chassis of the shaft, and the pump Assembly including a pump housing, a rotor with a shaft and sacienaasim impeller, the turbine shaft, the shaft of the chassis Assembly and the rotor shaft of the pump are integrated into a common shaft turbopump Assembly, in addition, the housing supply working fluid turbine Assembly is provided with the inlet pipe and 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, which is tightly connected with the discharge side radially equidistant about the axis of the shaft of the turbine to the nozzle disk apparatus on the outer and inner annular edges, and nozzle nozzle of the device is made in the disk 8÷15 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)°, while the spatial removal of the axes of the nozzles are fixed at the point of intersection of the latter with conditional PLoS is awn drive nozzle apparatus, as the radial distance of each of these points from the axis of the turbine shaft made of not less than one third of the radial height of the impeller blades of the turbine radial distance transverse root sections mentioned blades to the turbine shaft, in addition, the longitudinal axis of each nozzle nozzle apparatus is located in an imaginary plane parallel to the axis of the turbine shaft, is normal to the radius and inclined at the specified plane at an angle to an imaginary plane of the disk in the direction opposite to the direction of rotation of the impeller of the turbine at an angle (12÷25)°.

2. 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 spent working fluid.

3. Turbopump Assembly according to claim 1, characterized in that the annular shell collector turbine site is hermetically attached to the drive nozzle apparatus with the gamut of the input estuaries nozzles on the outer and inner annular edges, preferably by welding.

4. 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 a variable in which upravlenii vector 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.

5. Turbopump Assembly according to claim 1, characterized in that the impeller blades of the turbine radially removed from the axis of the shaft of the turbine, not less than 0,8R, where R is the radius of the disc of the impeller of the turbine, and evenly spaced around the circumference of the disk with a gradient Radiani density G determined in the range
Grad. G=(10÷44) [u/rad],
where the gradient G is a numerical characteristic of blades placed in the angular range of one radian.

6. Turbopump Assembly according to claim 1, characterized in that the interscapular channel impeller turbines are made confused-diffuser in the direction of flow of the working fluid with the maximum narrowing of the cross-flow area S defined in the zone of maximum thickness of the blades δmaxfrom the expression
S=ΔR(2πR-Tδmax)/T,
where ΔR is the radial height interscapular channel, T is the number of interscapular channels according to the number of disk blades of the impeller of the turbine.

7. Turbopump Assembly according to claim 1, characterized in that th tree of the chassis of the unit has a console, while 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.

8. Turbopump Assembly according to claim 1, characterized in that the rotor shaft turbopump Assembly 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 ball 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.

9. Turbopump Assembly according to claim 1, characterized in that 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 with the housing inlet, and provided with a pipe outlet, made mainly diffuser, tangential type, as well as from the rear annular element associated with the front, which together education is comfort flow cavity volume, enough 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 pump casing, and a 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 of quasimomenta of flow rates in each channel of the cochlea.

10. Turbopump Assembly according to claim 1, characterized in that 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 impeller blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller, with the number of blades taken from 4 to 16, preferably 12, and the screw snakecharming impeller on the wasp made not less than dvukhzaryadnym, equipped with smooth expansion in the transition zone of the channel of the screw in the multiple-channel centrifugal wheel and spiral blades, made mainly with variables, at least part of the length of the radius and pitch of the spiral twist, 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)°, and the gradient G of the step angle of twist of each blade within the axial length of the spiral auger is defined in the range G=(17÷70)π rad/m

11. Turbopump Assembly according to claim 9, characterized in that the machine axial unloading of the rotor comprises an annular heel, the ledge is fixed or made on the back wall of the pump housing and 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 comprising side and end gap-type seals made with the possibility of a self-regulating flow fluid from the zone high zone low pressure mentioned centrifugal wheel to regulate the axial unloading of the rotor turbopump Assembly.

12. Turbopump Assembly according to claim 9, characterized in that the base disk snakecharming impeller is nebgen in the basal part of the disk, at least one peritonism hole, and covering the disk is made adjacent to the building entrance for the fluid through the slit seal.

13. Turbopump Assembly according to claim 1, characterized in that the housing of the exhaust of the working fluid in the turbine Assembly is provided with mechanical seals to ensure the integrity of structural connectors.

14. 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.

15. 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

16. 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 15.

17. The method according to item 16, characterized in that the pumping cold type water produced in the water supply system of industrial, civil and residential complexes.

18. The way p is P16, 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.

19. The method according to item 16, characterized in that the pumping industrial water to produce power utility boilers, and industrial enterprises.



 

Same patents:

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

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: 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

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

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

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

FIELD: engines and pumps.

SUBSTANCE: turbine of gas turbine engine includes an annular inlet channel, the inner housing of which is formed with a rear cover plate and an inner conical shell telescopically installed on radial projections of flanges of nozzle vanes of the first stage. Radial projections of flanges of nozzle vanes of the first stage are rectangular in cross section and contact with their side walls to axial projections of conical shell and rear cover plate, which are trapezoidal in cross section. Axial projections of the shell are located on outer side of axial projections of the rear cover plate. Conical shell is fixed in axial direction relative to the cover plate with its front flange by means of annular radial connection of male-female type. Front flange is split and consists of sectors, and bolted connection of the front flange with the cover plate is provided with an annular groove at the joint of flange and cover plate around the bolt shank.

EFFECT: invention allows improving turbine reliability.

2 cl, 5 dwg

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