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

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

 

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 turbo is asony 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 unloading. (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 "Poronajsk the I international Conference", UDK(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, 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 outside the Bina of the vector flow of the working fluid case of output spent working fluid; in addition, the turbopump Assembly includes a support Assembly that consists attached to the base of output spent 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 Assembly, the housing of the flow part of the pumping unit is designed teams, including the case of the entrance to the pipe axial inlet for the fluid, the body of the tap consists of a front the annular element connected to the housing of the entrance, as well as from the ledge in the cross section of 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 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 mail the syrup channels, moreover, the blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller with respect to the conditions kathiravelu cross-sectional area at the entrance to the interscapular channel formed by two adjacent blades of maximum length and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder of smaller length, and the number of blades and respectively 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, and the active volume is dynamically populate the aggregate interscapular channel impeller pump made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about fluid, in addition, the spiral drain pump unit made in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels with the difference of the squares of the output and input sections, referred to the length of the channel, with the gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea and the components of G=0,87-0,95.

This blade centralino.chicago wheel 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 of g mid length long blades in the range r±15%.

The auger can be performed not less than dvukhzaryadnym with spiral blades and a hollow shaft, which, at least most of the length is made covering the wound in his section of the drive shaft turbopump Assembly and provided with a smooth expansion in the transition zone of the channel of the screw in the multiple-channel centrifugal wheel with tilt angle to the axis of the shaft the greater part of the shaping of the contour of the transition, variance components in the area 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 possible increases in the course of the flow of fluid.

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 targetlocale 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 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 zones 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 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 greater than the radius of the school is avago seals on the top disk, and an end face of the abutment of the machine axial unloading of the rotor is constructed with a diameter of less than or equal to the diameter of the gap seals on the top disk of the impeller.

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 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 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 amount the creation 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 spent working fluid.

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 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.

Turbopump Assembly can be mounted on a rigid, preferably, welded frame with the possibility of installing on the base with the possibility of the completely 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 steam, and also simplifies Assembly, significantly reducing consumption and increasing the compactness and efficiency of the unit. Also used as a drive turbines operating with a working medium gas type, significantly reduces energy consumption.

The invention is illustrated by drawings, where:

figure 1 shows a turbocharger used in Sony unit, 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 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 2 is made 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, including attached to the housing 4 exhaust of the working fluid, the housing 10 of the chassis turbopump Assembly with at least two terminal connection or lead ecovie the supports 11 and the 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 of the closed 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 the output sabotage wheel in compliance with the conditions of quasimomenta 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 active volume is dynamically populate the aggregate interscapular channels 27 of the impeller of the pump is made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about the pumped medium.

Spiral outlet 22 of the pump unit is designed in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore extending channels 28 with the difference of the squares of the output and input sections, referred to the length of the channel 28, with the gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea and the components of G=0,87-0,95.

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 is the removal of lead-tops of the long blades, preferably, the location of peaks of short blades at a radial distance corresponding to the small radius of g mid length long blades in the range r±15%.

The screw 23 is made not less than dvukhzaryadnym with spiral blades 29 and the hollow shaft. Shaft, 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 gradual expansion in the zone 30 of the transfer channel of the screw 23 in the multiple-channel centrifugal wheel. The angle of inclination to the axis of the shaft the greater part of the shaping of the contour of the transition variant is in the area of the extension shaft 18°÷30°. Spiral blades 29 of the auger is 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 flow of the pumping medium, starting with the lead-in area 31.

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 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 possibility of an adjustable pulsating output of 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 constructed with a diameter of less than or equal to the yameru 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 the outer and inner annular edges 44.

Nozzle 5 nozzle apparatus 3 is executed 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 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 the edges interscapular channels of the impeller 7 of the turbine, and provided with a mainly tangential inlet 46 of the output of the spent working fluid.

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 supported on 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 system liquid cooling. 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 m 3/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 (gas) turbine site 1 launch 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 for differential up over Vukovich 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 the medium to be pumped through the 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 mechanical selavo what about the seal 37. 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-cap seal 37, is the equilibrium position, compensating axial force on the thrust bearing 47.

Mechanical seal 51 in the housing cavity 4 exhaust of the working fluid does not pass pumping and cooling them with liquid on one side of the cavity of the turbine to prevent water hammer when water gets into the hot cavity, 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. The 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 on uma sensors 54 speed and vibration sensors, located on the body 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 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 the type of gas, 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 housing in the exhaust stroke of the working fluid; in addition, the turbopump Assembly includes a support Assembly that consists attached to the base of output spent 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 Assembly, the housing of the flow part of the pumping unit is designed teams, including the case of the entrance to the pipe axial inlet for the fluid, the body of the tap consists of a front the annular element connected to the housing of the entrance, as well as from the ledge in the cross section of 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 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 mail the syrup channels, moreover, the blades are made, preferably, of different lengths and variable height along the length, decreasing towards the exit of the impeller with respect to the conditions kathiravelu cross-sectional area at the entrance to the interscapular channel formed by two adjacent blades of maximum length and the total cross-sectional area at the outlet located between them shorter channels, separated by an intermediate shoulder of smaller length, and the number of blades and respectively 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, and the active volume is dynamically populate the aggregate interscapular channel impeller pump made with variant release on duct for one revolution of the impeller (4,7÷45)×10-5m3/about fluid, in addition, the spiral drain pump unit made in the form of dvuhaktnoy snails with the division lead estuaries, mainly on the 180° radial spin and diffusore expanding channels with the difference of the squares of the output and input sections, referred to the length of the channel, with the gradient expansion of G along the twist taken from the condition of quasimomenta of flow rates in each channel of the cochlea and the components of G=0,87-0,95.

2. Turbopump Assembly according to claim 1, trichosis fact, that blade centrifugal impeller 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%.

3. Turbopump Assembly according to claim 1, characterized in that the screw is made not less than dvukhzaryadnym with spiral blades and a hollow shaft, which, at least most of the length is made covering the wound in his section of the drive shaft turbopump Assembly and provided with a smooth expansion in the transition zone of the channel of the screw in the multiple-channel centrifugal wheel angle to the axis of the shaft the greater part of the shaping of the contour of the transition, variance components in the area 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.

4. Turbopump Assembly according to claim 1, characterized in that to drain the fluid from flowing part to the of Cusa pump latter is supplied by a pipe outlet, made, mostly, diffuser, tangential type.

5. 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 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 through executed in the main disk of the impeller, less than the least one bypass hole and the creation of this pulsating axial force changes unloading of the rotor.

6. Turbopump Assembly according to claim 5, 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 of less than or equal to the diameter of the gap seals on the top disk of the impeller.

7. 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.

8. 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 are separated by an imaginary circle at equal angles in the range (24÷45)°.

9. Turbopump Assembly according to claim 1, featuring the the action scene, 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.

10. 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.

11. 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.

12. Turbopump Assembly according to claim 1, characterized in that the rotor shaft turbopump Assembly supported on the body chassis through the mentioned bearings, pre-emption is about, 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.

13. 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.

14. 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

15. 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 14.

16. The method according to item 15, characterized the eat, the pumping cold type water produced in the water supply system of industrial, civil and residential complexes.

17. The method according to item 15, wherein the pumping of hot water produced, including excessive pressure up to 2 MPa or more and a temperature of 85-105°C or more, the heating and/or hot water supply, industrial, civil and residential complexes.

18. The method according to item 15, wherein the pumping industrial water to produce power utility boilers, and industrial enterprises.



 

Same patents:

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

Fan // 2505714

FIELD: ventilation.

SUBSTANCE: fan is designed for creation of an air jet in a room, an office or other rooms. A bladeless fan includes nozzle (14) installed on base (12), and an air flow creation device. Nozzle (14) includes internal channel (94) intended to receive an air flow, outlet section (26) designed for air flow discharge and several fixed guide vanes (120), each of which is located in internal channel (94) and intended to direct some part of the air flow to outlet section (26). Nozzle (14) determines hole (24) through which the air flow leaving outlet section (26) sucks the air outside the fan.

EFFECT: improvement of comfortable conditions and increase of fan safety.

33 cl, 14 dwg

FIELD: machine building.

SUBSTANCE: proposed invention comprises radial flow compressor diffuser blade with leading edge, trailing edge and invariable-thickness section arranged there between. Radius of curvature of leading edge and that of trailing edge vary over the blade span. Ratio between invariable-thickness section length and blade chord length makes at least 50% and does not vary over the blade span.

EFFECT: higher efficiency.

20 cl, 8 dwg

FIELD: engines and pumps.

SUBSTANCE: proposed pump comprises housing, impeller with top and bottom vaned rims, ring distributor and pipe bend with outer and inner rings to make manifold with pressure pipe. Said distributor is arranged between pipe bend and manifold. Rings in lower part arte composed elliptical concentric bottoms along pump axis. Channels extending to bottom rim are composed of branch pipes to pass through said bottoms while their axes extend through the center of said bottoms. Guide vanes are arranged from distributor to said branch pipes. The latter communicate with bottom rim via lower confuser with flat radial ribs between branch pipes located by its inner part from branch pipes and by outer part from inner ring to bottom rim. Circular baffle is arranged between housing and outer ring to separate feed line to rims. Channels to top rim are located between two circular elements connected by radial ribs and jointed thereto by flat ribs combined into top confuser within the limits of diameter of intersection of inner generating lines of branch pipe, confuser inner part and inner bottom.

EFFECT: simplified design, higher efficiency, longer life, smaller overall dimensions.

12 cl, 9 dwg

Vertical pump // 2497025

FIELD: engines and pumps.

SUBSTANCE: vertical pump comprises housing and rotor with diagonal-type impeller. Impeller shaft runs in plain bearings. Distributor with vanes that form channels is arranged downstream of said impeller. Vane cross-section, normal to vane surface and that forming said channels, features variable thickness and is shaped to trapezoid with maximum magnitude nearby base at channel smaller radius. Minimum tolerable clearance is kept between impeller vanes and distributor vanes. Maximum diameter of distributor channels relative to impeller rotational axis is calculated by the formula and depends on minimum diameter of impeller working edges and impeller width at outlet.

EFFECT: decreased overall dimensions, higher efficiency.

2 dwg

Centrifugal pump // 2493439

FIELD: engines and pumps.

SUBSTANCE: centrifugal pump comprises a body with an inlet nozzle changing into the central part of the body. The central part of the body changes into a discharge nozzle. In the central part of the body there is an impeller of tunnel type. On the front circular disc of the wheel there are circular channels. On the inner wall of the central part of the body upstream the inlet to the discharge nozzle there is a step. On the inner side of the body cover installed at the side of the inlet nozzle there are circular collars.

EFFECT: increased efficiency factor and maximum permissible speed of rotation and reduced head resistance to rotation and noise level.

3 dwg

Pump // 2491449

FIELD: engines and pumps.

SUBSTANCE: proposed pump has housing 1 with lateral suction pipe 3 connected to annular chamber 4 changing into conical pipe 5 ahead of rotor impeller 2. Inner and outer walls 6 of said conical pipe 5 are rigidly connected by shaped identical supports 7 arranged regularly over radial section of pipe 5. Annular chamber 4 and pipe 3 feature thick walls. Thick-wall section of conical pipe ensures stiffness of the stator in crosswise and lengthwise directions and invariable sizes in cold pump. Shaped supports provided for fluid flow acceleration. Thin-wall section of pump inlet allows deformation of inlet in turbo pump assy in mounting and in cooling without flexure of stator bearing seat axes and uniform fluid feed to conical pipe.

EFFECT: decreased influence of geometrical asymmetry of lateral feed on stator seat axes sharp curves.

1 cl, 1 dwg

FIELD: engines and pumps.

SUBSTANCE: gas turbine diffuser comprises two circular baffles extending inside each other and connected by, in fact, radial vanes. Lower peripheral edge of one of said baffles comprises cutouts regularly distributed along diffuser lengthwise axis. Invention covers also gas turbine engine, in particularly, aircraft turbojet or turbo-prop, comprising aforesaid diffuser and annular combustion chamber arranged downstream of diffuser and inside engine outer housing. Fuel is forced into combustion chamber by injectors arranged between diffuser and combustion chamber to extend, in fact, radially inside inner space from outer housing. Cutouts of downstream peripheral edge of said or every diffuser baffle are leveled axially with injectors to allow upstream shift of every injector in said cutout for removal of said injector.

EFFECT: decreased axial size of turbine and its weight.

14 cl, 7 dwg

FIELD: engines and pumps.

SUBSTANCE: rotary pump comprises multiple radial impellers and multiple radial diffusers with multiple vanes. Diffuser vanes have trailing edges flexing at transition section at angle making, at least, thirty degrees, into diffuser outlet channels. Note here that multiple diffuser vanes form diffuser channels extending through said transition section and into appropriate diffuser outlet channel with minimum change in cross-section area to decrease fluid separation.

EFFECT: higher pump efficiency.

24 cl, 6 dwg

FIELD: machine building.

SUBSTANCE: centrifugal compressor includes a housing and a shaft. The above shaft is installed so that it can be rotated in the compressor housing. At least one impeller is located in the compressor housing on the shaft. A medium outlet element of certain length in radial direction and axial direction of the centrifugal compressor is installed after the last impeller of the compressor on the medium way in the compressor housing. At that, the medium outlet element has a medium passage. The above passage is spread through a certain angular value in the direction of the centrifugal compressor perimetre. At that, the medium outlet element is made from material with certain structure. The passage is made in the form of an additionally made spatial interruption of substance cohesion of material structure. Centrifugal compressor manufacturing method is described as well.

EFFECT: improved operating and technical characteristics and lower costs for manufacture of a centrifugal compressor.

19 cl, 4 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: 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: 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

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