EA014075B1 - The bladed machine (versions) - Google Patents

Abstract

In the bladed machine, according to the first embodiment, comprises a body with central and peripheral channels of passing of a working medium, which is jointed with an external machine by means of arbor, on which there is fixed one hub of axial working runner, having a circular system of blades, sequentially alternating lengthwise the axis of the arbor with a circular system of guide vanes of controlling apparatus, the vanes are fixed in the body, the working runner is furnished at least one ring-type bush, which is hard by bound with the hub of the working runner and a circular system of the working runner blades and the controlling apparatus of guide vanes, which are accomplished at least in two rows with the central row and the peripheral row with the circular systems of blades and guide blades correspondingly. The blade machine, according to the second embodiment, comprises a body with central and peripheral channels of passing of a working medium, which is jointed with an external machine by means of arbor, on which there is fixed one hub of axial working runner, having a circular system of blades, sequentially alternating lengthwise the axis of the arbor with a circular system of guide vanes of controlling apparatus, the vanes are fixed in the body, is provided with the second working runner with a hub, encompassed by the first working runner and kinematically connected to an additional shaft, connected to a shaft of an outer machine, the circular systems of the working runner blades and of controlling apparatuses of the guide vanes are accomplished in three rows with a peripheral and middle circular rows of the blades and guide vanes correspondingly. In each embodiment the working runner blades and guide apparatus vanes circular systems are made as biplanes - with the periodically alternating blades and vanes of an unequal length.

Description

(57) In a vane machine according to the first embodiment, comprising a housing with a central and peripheral channels for transmitting a working medium, a shaft connected to an external machine, on which a hub of an axial impeller is mounted, having a circular system of blades alternating in series along the axis of the shaft with a circular system of guide vanes apparatus fixed in the housing, the impeller is equipped with at least one annular sleeve rigidly connected to the hub, and a circular system of impeller blades and vanes arata are made at least double-row with the central and peripheral rows of circular systems of blades and blades, respectively. The vane machine according to the second embodiment, comprising a housing with central and peripheral channels for transmitting the working medium, a shaft connected to an external machine, on which a hub of an axial impeller is fixed, having a circular system of blades alternating in series along the axis of the shaft with a circular system of vanes of the guide apparatus fixed in case, equipped with a second impeller with a sleeve covering the first impeller, kinematically connected with an additional shaft connected to an external machine, circular sys emy impeller blades and guide blades are made from three-row peripheral, intermediate and central rows of blades and vanes, respectively. In each of the options, the blades of the impeller and the blades of the guide apparatus can be made in each row of variable height along the sleeve. At the same time, the specific power (per unit mass), useful pressure, as well as durability, while maintaining high values of efficiency, are increased.

The claimed group of inventions relates to the field of engineering, in particular to reversible axial blade machines for liquid and gas, suitable both for generating mechanical energy and for supplying a working medium under pressure.

Known centrifugal vane machine, comprising a housing with channels for transmitting a working medium, a shaft connected to an external machine, on which a hub of a radial-axial impeller having a circular blade system (1) is fixed.

The disadvantages of this machine include increased hydraulic and especially disk losses, reaching in total, for example, in injection vanes of low speed (IH100) of 30-35% or more of the power of power plants. In addition, under conditions of often fixed maximum allowable radial dimensions of the flow part and close to optimal geometry of the blade systems in terms of hydrodynamic parameters, the possibility of a qualitative increase in pressure is practically exhausted.

Known axial propeller blade machine, comprising a housing with a Central and peripheral channels for transmission (exhaust and supply) of the working medium, a shaft connected to an external machine, on which a hub of an axial impeller is mounted, having a circular system of blades alternating in series along the axis of the shaft with a circular system of blades guide apparatus fixed in the housing (2).

The disadvantage of this vane machine is the reduced value of the head (bladed type pump), or useful (pusher type turbine, i.e. motor type) pressure, as well as high specific material consumption (low power per unit mass).

The technical task of the group of inventions, united by a single inventive concept, is to create an energetically more efficient reversible blade machine for working on liquids and gases and to expand the arsenal of blade machines.

The technical result, which provides a solution to the problem of the group of inventions, consists in increasing the specific power (per unit mass), useful pressure and durability, while maintaining high values of efficiency.

The essence of the invention according to the first embodiment consists in the fact that in a vane machine comprising a housing with central and peripheral channels for transmitting the working medium, a shaft connected to an external machine, on which a hub of an axial impeller having a circular blade system sequentially alternating along the shaft axis is detachably fixed with a circular system of vanes of the guide apparatus fixed in the housing, the impeller is provided with at least one annular sleeve rigidly connected to the hub, and circular systems of the blade the impeller and vanes of the guide vanes are made at least two-row with the central and peripheral rows of circular systems of vanes and vanes, respectively, which are installed on both sides of the impeller bushings, while the circular systems of vanes of the vanes and vanes of the impeller are installed in each row with the opposite the sequence of their alternation, and in the housing is made at least one annular axisymmetric recess, covering from one of the ends of the impeller bushing with rofessional knee flow inversion.

In the particular case of execution according to the first embodiment of the invention, the impeller is made with two annular bushings rigidly connected to the hub, and the circular systems of the impeller blades and vanes of the guide apparatus are made three-row with the central, intermediate and peripheral rows of circular systems of blades and blades, while the body cavity made with two axisymmetric annular recesses located on opposite sides of the impeller, each of which covers from one of the ends a corresponding the main sleeve and the impeller blades fixed on both sides of the impeller with the formation of two flow inversion bends between the rows of circular systems of blades and blades. Preferably, one of the circular systems of the vanes of the guide vane is partially located in the inversion elbow.

In the following particular case of the execution according to the first embodiment of the invention, the circular systems of the blades of the impeller and vanes of the guide apparatus are made in two rows with multistage central and peripheral rows of the circular systems of the blades and blades, the blades are rigidly mounted in sleeves fixedly mounted on the impeller bushing on both its sides, the blades the guide apparatus is rigidly mounted in the rims, the rims of the blades of the peripheral row are fixedly mounted in the housing, the impeller bushing is rigidly connected to dull, and in the casing there are two axisymmetric annular recesses in two additionally installed intermediate casing closures with the formation of two inversion bends, while the casing is equipped with a support sleeve mounted concentrically to the shaft with the rim of the central row vanes fixed to it.

In the fourth particular case of the invention according to the first embodiment, the circular systems of the blades of the impeller and vanes of the guide apparatus are made in three rows with multistage central, intermediate and peripheral rows of circular systems of the blades and blades, the blades of the intermediate and peripheral rows are rigidly mounted in sleeves fixedly mounted on the hub of the impeller on both sides, the vanes of the guide vane are fixedly mounted

- 1 014075 in the rims, the rims of the blades of the peripheral row are fixedly mounted in the housing, the impeller bushing is rigidly connected to the hub, and two annular axisymmetric recesses are made in the housing in two additionally installed intermediate housing closures with the formation of two inversion elbows, the housing is equipped with a support mounted concentrically to the shaft a sleeve with the rims of the blades of the central and intermediate rows fixedly fixed on it on both sides, the shaft is equipped with a series and fixedly mounted on it additional hubs on which the blades of the central row are rigidly fixed. Preferably, the additional hubs of the blades and rims of the blades of the central row are made of triangular longitudinal section, and the blades and blades of the central row are made in pairs tapering in length towards each other.

In the following particular case of the execution according to the first embodiment of the invention, the circular systems of the blades of the impeller and vanes of the guide apparatus are made in two rows with multistage central and peripheral rows of the circular systems of the blades and blades, the blades are rigidly mounted in sleeves fixedly mounted on the impeller bushing on both its sides, the blades the guide apparatus is rigidly mounted in the rims, the rims of the blades of the peripheral row are fixedly mounted in the housing, the impeller bushing is rigidly connected to stupid, and in the housing there are two axisymmetric annular recesses in two additionally installed intermediate housing closures with the formation of two inversion elbows, the housing is equipped with a support sleeve mounted concentrically to the shaft with rim blades of the central row fixed to it, while the impeller sleeve is made stepwise, the sleeves are made variable thickness with a trapezoidal longitudinal section, and the blades and blades are made in each row of variable height along the impeller bushing, moreover, the height of the blades and blades sequentially and uniformly decreases in the peripheral row from the peripheral transmission channel to the inversion knee, and in the next row in the opposite direction.

In particular cases of the invention according to the first embodiment, the central transmission channel is located inside the support sleeve from the side of its attachment to the housing, and the peripheral transmission channel is made on the opposite side and around the impeller sleeve, each impeller sleeve is made with a rounded end on the inverse elbow side and with sliding elements from the side opposite the inversion elbow, at least in one channel of the working medium transmission a stator lattice of radial jumpers is installed, formed composite.

In this case, the circular systems of the impeller blades and vanes of the guide apparatus can be made monoplane - with blades and blades of the same length - or biplane - with periodically alternating blades and with periodic alternating blades of unequal length.

The essence of the invention according to the second embodiment consists in that a blade machine comprising a housing with central and peripheral channels for transmitting a working medium, a shaft connected to an external machine, on which a hub of an axial impeller is mounted, having a circular system of blades alternating in series with the circular axis of the shaft the system of blades of the guide apparatus fixed in the casing, characterized in that it is equipped with a second impeller with a sleeve covering the first impeller kinematically connected with additional with a body shaft connected to an external machine, the circular systems of the blades of the impellers and vanes of the guide apparatus are made in three rows with the peripheral and intermediate rows of circular systems of blades and vanes, respectively, which are installed on both sides and around the sleeve of the second impeller, and with the central row of circular systems the blades and blades that are installed around the hub of the first impeller, the hub is made of composite ring parts, each of which is detachably connected to the shaft and rigidly fastened and with the blades of the central row, the blades of the peripheral and intermediate rows are rigidly mounted in the sleeves mounted on the sleeve of the second impeller on both sides, the blades are rigidly mounted in the rims, the rims of the blades of the peripheral row are fixedly mounted in the housing, and the latter is equipped with a support sleeve fixed to the shaft concentric with the shaft the installation of the rims of the blades of the Central and intermediate rows, while in the casing there are two axisymmetric annular recesses in two additionally installed intermediate casing 's contactors, and each of the recesses includes a corresponding one of the ends of the sleeve to form a flow inversion knee.

Preferably, the sleeve of the second impeller is made stepped, the sleeves and ring parts of the composite hub are made of variable thickness with trapezoidal longitudinal sections, and the blades of the impeller and vanes of the guide apparatus are made in each row of variable height along the respective bushings, and the height of the blades and blades decreases in the peripheral row from peripheral transmission channel to the knee inversion, in the intermediate row - in the opposite direction, and in the central row - from the knee inversion to c central channel transmission.

In this case, the impellers are connected to the external machine by gears with different diameters. At least one channel for transmitting the working medium has a stator lattice made of radial jumpers, the housing is made integral. In different cases, the performance of the circular systems of the blade

- 2014075 of the impeller and vanes of the guide vane can be made monoplane - with blades and blades of the same length, or biplane - with periodically alternating blades and with periodically alternating blades of unequal length.

In the drawing of FIG. 1 shows a structural diagram of a two-row blade machine, in FIG. 2, the section Ι-Ι in FIG. 1, in FIG. 3 is a step section ΙΙ-ΙΙ of FIG. 1, in FIG. 4 is a section ΙΙΙ-ΙΙΙ of FIG. 1, in FIG. 5 is a structural diagram of a three-row blade machine with a casing on the shaft; FIG. 6 is another structural diagram of a three-row blade machine without a casing on the shaft; FIG. 7 is a structural diagram of a multi-stage two-row blade machine, in FIG. 8 - section GU-GU of FIG. 7, in FIG. 9 is a section Y-U of FIG. 7, in FIG. 10 is a structural diagram of a multi-stage three-row blade machine, in FIG. 11 is a structural diagram of a multi-stage two-row blade machine with a variable height of the blades and blades, in FIG. 12 is a kinematic diagram of a drive of a blade machine with two impellers, in FIG. 13 shows a device for connecting a second impeller to a drive; FIG. 14 is a structural diagram of a multi-stage three-row blade machine with two impellers.

The vane machine (Fig. 1-4) according to the first embodiment of the invention comprises a housing 1 with a housing closure 13, as well as with the central and peripheral channels 2, 3 of the transmission medium, connected to an external machine (not shown) shaft 4, which is detachable, for example, with a key connection 12, a hub 5 of an axial impeller is fixed, having a circular system of blades 6 sequentially alternating along the axis of the shaft 4 with a circular system of blades 7 of the guide apparatus fixed in the housing 1. The impeller is provided with an annular sleeve 8, rigidly connected with the hub 5 of the blades 6, and the circular systems of the blades 6 of the impeller and the blades 7 of the guide apparatus are made at least two-row with the central and peripheral rows of the circular systems of the blades 6 and the blades 7, respectively, which are installed on both sides of the sleeve 8 of the impeller (see in Fig. 1 rectangles elongated along the vertical axis). At the same time, at least one axisymmetric annular recess is made in the housing 1, covering the sleeve 8 from one of the ends and the impeller blades 6 fixed on both sides thereof with the formation of a flow inversion elbow 9.

The impeller can also be made (Fig. 5, 6) with two ring bushings 8, 10, rigidly connected with the hub 5 of the blades 6, and the circular system of the blades 6 of the impeller and the blades 7 of the guide apparatus are made in three rows with a central, intermediate and peripheral rows circular systems of blades 6 and blades 7. Moreover, the cavity of the housing 1 is made with two axisymmetric annular recesses located on opposite sides of the impeller, each of which covers a corresponding sleeve 8 or 10 from one of the ends and fixed on both sides of the blade 6 of the impeller with the formation of the elbows 9, 11, respectively, the inverse of the flow between the rows of circular systems of the blades 6 and the blades 7. The bushings 8 and 10 of the impeller are interconnected and with the hub 5 of the blades 6. One of the circular systems of blades 7 of the guide apparatus is partially located in the elbow 9 and / or 11 of the inversion. The impeller hub 5 is detachably connected to the shaft 4, for example, with a key 12. The machines in FIG. 5 and FIG. 6 differ in the opposite sequence of alternating circular systems of blades 6 of the impeller and blades 7 of the guide apparatus in each row, as well as the execution of the hub 5 and the presence of a fixed casing 24.

Circular systems of blades 6 of the impeller and vanes 7 of the guide vane (Fig. 7-9) can be made double-row with multi-stage central and peripheral rows of circular systems of vanes 6 of the impeller and vanes 7 of the vane. The impeller sleeve 8 is rigidly connected to the hub 5, and in the housing 1 there are two axisymmetric annular recesses in two additionally installed intermediate case closers 13, 14 with the formation of two inversions 9, 11. The housing 1 is equipped with a support sleeve 15 mounted concentrically to the shaft 4 with the rims 16 of the blades 7 of the central row fixed on it from the outside. The blades 6 are rigidly mounted in the sleeves 17 fixedly mounted on the impeller sleeve 8 on both sides thereof, the blades 7 of the peripheral row are rigidly mounted in the rims 16 fixed in the housing 1. The central transmission channel 2 is preferably located inside the support sleeve 15 of the housing 1, and the peripheral the transmission channel 3 is made on the opposite side, around the impeller sleeve 8.

Circular systems of blades 6 of the impeller and vanes 7 of the guide apparatus (Fig. 10) can be made three-row with multistage central, intermediate and peripheral rows of circular systems of blades 6 and blades 7. The sleeve 8 of the impeller is rigidly and detachably connected to the hub 5, which is fixed on the shaft 4, for example, with a keyway 12. In the housing 1 there are two axisymmetric annular recesses in two additionally installed intermediate case closers 13, 14 with the formation of two inversions 9, 11. The blades 7 of the guide apparatus are rigidly mounted in the rims 16. The housing 1 is equipped with a support sleeve 15 mounted concentrically to the shaft 4 with the rims 16 of the blades 7 of the central and intermediate rows fixed on both sides of it. The blades 6 of the peripheral and intermediate rows are rigidly mounted in the sleeves 17, fixedly mounted on the sleeve 8 on both sides of it. The rims 16 of the blades 7 of the peripheral row are rigidly mounted in the housing 1. The shaft 4 is equipped with sequentially mounted and fixed

- 3 014075 on it, for example, keyed connections 12 additional hubs 18, on which the blades 6 of the central row are rigidly fixed. The additional hubs 18 of the blades 6 and the rim 16 of the blades 7 of the central row are preferably made of triangular longitudinal section, and the blades and blades 7 of the central row are made in pairs tapering in length towards each other.

Circular systems of the blades 6 of the impeller and vanes 7 of the guide apparatus (Fig. 11) can be double-row with multi-stage central and peripheral rows of circular systems of the blades 6 and vanes 7. The sleeve 8 of the impeller is made stepwise and is rigidly connected by a key 12 to the hub 5, as shown in FIG. 7. In the housing 1, two annular axisymmetric recesses are made in two additionally installed intermediate case closers 13, 14 with the formation of two inversions 9, 11. The blades 7 of the guide apparatus are rigidly mounted in the rims 16. The housing 1 is equipped with a support sleeve 15 mounted concentrically to the shaft 4 with the rims 16 of the central row blades 7 fixed to it. The rims 16 of the blades 7 of the peripheral row are rigidly mounted in the housing 1. The blades 6 are rigidly mounted in the sleeves 17, fixedly mounted on the sleeve 8 on both sides thereof. The sleeves 17 are made of variable thickness, and the blades 6 and blades are made in each row of variable height along the sleeve 8, and the heights 1 of ₂ blades 6 and blades 7 are sequentially and uniformly reduced in the peripheral row from the peripheral transmission channel 3 to the inversion knee 9, and in the next row - in the opposite direction. The Central channel 2 is preferably located inside the support sleeve 15 of the housing 1, and the peripheral channel 3 is made on the opposite side, around the sleeve 8 of the impeller.

In some of the previous particular cases of the implementation of the blade machine according to the first embodiment of the invention, each impeller sleeve 8, 10 is made with a rounded end from the side of the inversion knees 9, 11 and with sliding and sealing elements from the side opposite to the inversion knees 9, 11. In the channel 2 and / or 3, preferably, a stator lattice of radial bridges 19 can be installed. The housing 1, as a rule, is made integral.

Each circular system of blades 6 of the impeller and blades 7 of the guide apparatus can be made monoplane - with blades 6 and blades 7 of the same length, or biplane - with periodically alternating blades 6 and periodically alternating blades 7 of unequal length (see profiles in Fig. 3, shown by solid and dashed lines).

The blade machine according to the second embodiment of the invention (Figs. 12-14) comprises a housing 1 with central and peripheral channels 2 and 3 for transmitting the working medium connected to an external machine 25, a shaft 4, on which a hub 5 of an axial impeller (first) is fixed, having a circular a system of blades 6 sequentially alternating along the axis of the shaft 4 with a circular system of blades 7 of the guide apparatus fixed in the housing 1. The second impeller has a sleeve 8 surrounding the first impeller, kinematically connected with the additional shaft 20, is connected with an external machine 25. The circular systems of the blades 6 of both impellers and vanes 7 of the guide apparatus are made three-row with the peripheral and intermediate rows of sequentially alternating circular systems of the blades 6 and blades 7, which are installed on both sides of the sleeve 8 of the second impeller, and with a central row circular systems of blades 6 and blades 7, which are installed around the hub 5 of the first impeller. The hub 5 (see the dashed brace in Fig. 14) is made of composite ring parts 23, detachably connected, for example, by key connections 12 (Fig. 10) to the shaft 4 and rigidly attached to its circular system of blades 6 of the central row. The blades 6 of the peripheral and intermediate rows are rigidly mounted in the sleeves 17, fixedly mounted on the sleeve 8 of the second impeller on both sides. The blades 7 are rigidly mounted in the rims 16. The rims 16 of the blades 7 of the peripheral row are fixedly mounted in the housing 1. The housing 1 is equipped with a support sleeve 15 mounted concentrically to the shaft 4 with the rims 16 of the blades 7 of the central and intermediate rows fixed on both sides. In the housing 1, two axisymmetric annular recesses are made in two additionally installed intermediate case closers 13, 14, and each of these recesses covers a corresponding sleeve 8, 15 from one of the ends with the formation of two inverted flow bends 9, 11. Preferably, the sleeve 15 of the second impeller is stepped, the sleeves 17, the annular parts 23 of the composite hub 5 are made of variable thickness with trapezoidal longitudinal sections, and the blades 6 of the impeller and vanes 7 of the guide apparatus are made in each row of variable height 1 ₂ , 1t, along the bushings 8 , 15, with heights b ₁₅ 11 ₂ . 1 ₃ blades 6 and blades 7 are reduced in the peripheral row from the peripheral transmission channel 3 to the inversion knee 9, in the intermediate row - in the opposite direction, and in the central row - from the inversion knee 11 to the central transmission channel 2.

The connection of the shaft 4 of the first impeller and the additional shaft 20 of the second impeller with the external machine 25 is made by means of gears 21, 22 of different diameters.

In the channel 2 and / or 3, preferably, a stator lattice of radial bridges 19 can be installed. The housing 1, as a rule, is made integral.

Each circular system of blades 6 of the impellers and blades 7 of the guide vane can be made monoplane - with blades 6 and blades 7 of the same length, or biplane - with periodically alternating blades 6 and with periodically alternating blades 7

- 4 014075 howling length (see in Fig. 3 profiles depicted by solid and dashed lines). In each period of biplane systems, an additional shortened blade 6 and blade 7, respectively, are installed in the output (when the machine operates as a supercharger) part of the inter-blade and interscapular channels.

In each of the variants of the invention, if necessary, a fixed casing 24 is mounted on the shaft 4. As an external machine, as a rule, an electric motor or an electric generator 25 is used. All rotating parts have corresponding parts transmitting rotation, support and sealing units, as well as other connecting parts (not marked). Between rotating and stationary parts there are necessary gaps (not marked).

The blades 6 and blades 7 in all cases are performed spatial hydrodynamically appropriate form (Fig. 3).

The blade machine operates as follows.

When using the machine (Fig. 1-4) as a supercharger (see solid arrows in Fig. 1) of an incompressible (practically) working fluid (for example, liquid), the supplied power Ν 'from the shaft 4 of the machine, driven into rotation, for example, from an electric motor 25 with a torque M 'and an angular velocity ω, so that Ν' = M'sh, through the keyway 12, is transmitted to the hub 5, fixed on the shaft 4, and from it to the blades 6 of the impeller. The blades 6 of the central row with their inter-blade channels form together with the interscapular channels of the blades 7, as well as with the axisymmetric surfaces of the hub 5, sleeve 8, elbow 9 and central channel 2 adjacent to them, the flow part of the central row stage, the active section of which is highlighted in FIG. 1 dotted rectangle. Hereinafter, a step is understood to mean a sequence of two working bodies following each other in the form of one circular system of blades 6 of the impeller and one circular system of blades 7 of the guide apparatus. Due to the hydrodynamic interaction of the blades 6 of the central row with the working fluid, part Ν'2 of the supplied power Ν 'is spent on creating a useful head Н _{2 of the} stage of the central row with a useful supply О (volume flow) of the working fluid, through it and, therefore, part Ν ₂ ~ OH ₂ useful second used mechanical energy of the working fluid. Hereinafter, the symbol ~ means proportionality. The pressure Н _{2 is} proportional to the difference of the circulations (average moments of the absolute velocity of the working fluid) behind Г ₂₂ and before Г _{21 the} blades 6 of the central row. During the flow around the blades 7 of this series by the working fluid, Г ₂₂ decreases to a small (modulo) Г23 value with the majority of the kinetic energy of the stream being converted to potential energy (static pressure) and the reactive moment M _p2 arising from such a process is transferred from these blades 7 on the housing 1 through the stator grating (jumpers 19). A further decrease in the residual kinetic energy of the working fluid, as usual, is realized in channel 2, made in the form of a diffuser. Another part of the supplied power Ν'1 = Ν '- Ν'2 through the sleeve 8 enters the blades 6 of the peripheral row, forming their inter-blade channels together with the inter-blade channels of the corresponding vanes 7 of the guide apparatus, as well as with the axisymmetric surfaces of the sleeve 8, knee adjacent to them 9, the housing 1 and the peripheral channel 3, the flow part of the stage of the peripheral row.

When the working fluid flows around the blades 6 of the peripheral row, Ν ' ₁ is converted into the useful second mechanical energy of this body Ν ₁ ~ ОН, with the useful pressure of the stage of this series Н1 and the useful supply of O. entering the flowing part of the stage of the peripheral row from channel 3, usually in the form of a confuser. Head H is proportional to the difference T ₁₂ for circulation and before G11 blades 6. Like processes hydromechanical working bodies in the central row at a flow of working fluid vanes 7 peripheral circulation P number ₁₂ decreases to a small value of T ₁₃ with increasing potential energy of the stream and form the reactive moment M _p1 perceived by the housing 1. In the U-shaped elbow 9 of inversion, a smooth transfer of the working fluid from the flowing part of the stage of the peripheral row to the flowing part of the stage of the central row takes place. Moreover, in accordance with the law of conservation of angular momentum, accurate to hydraulic losses in the elbow 9, an approximate constancy of the circulations is maintained (equality between the circulations G ₁₃ and G ₂₁ ). The presence of small end gaps causes overflows (see Fig. 3, solid curved arrows) of a certain amount of the working fluid from the side of the increased pressure of the blades 6 and the blades 7 to the back side of the reduced pressure and the associated end losses, which according to the theory of blade machines belong to hydraulic to losses.

Thus, the equation of balance of supplied power and useful second mechanical energy of the working fluid under simplifying (not fundamental) conditions for the complete identity of the steps in each separately taken row (for the described case of the implementation of the first embodiment of the invention, each row contains one step of the working bodies) and the absence external leakage on the shaft 4 has the following General view:

- 5 014075

Σ ^ · «= 2;

Λ = 1

Ν '- Μ'ω, Νί - pi - тпЯе--, pi = 1,

7m7ok '? rk _rk ^ ok7 where:

* 2 ^η ° ^ί 'ΰ ^' N - (r _a -r ").

Equation (3) is equivalent to the expression

And 2 · _Λ3 ^_ / Ά: 1, ^υ ιΡ ~ ^υ ι / ^1N to ~ ------- + - Σ --->

Ryo ² yo

O) (2) (3) (4) or using the Bernoulli equation for the relative motion of the working fluid in the area where the blades 6 are located and the absolute motion in the interval of the blades 7, as well as taking into account the smallness of the potential differences of the external mass forces (gravity) on these sections and _ ^υ Ρ2 ^{+ and} к2 ~ ™ к2 'Д1 ^{+ and} к1 ~ г, ^к 2 £ 2д

’’ (5) (6)

Ek

Reactive moments are determined from the equation

In equations (3), (6) T _n circulations of the moments determined absolute speed ratio 2ir = (w ") _d, / = 1,2.3. (7)

In expressions (1) - (7), the following notations are additionally adopted: η is the number of rows; t _to - the number of steps in each row; k is the index of the row number; ρ - density of the working body, d - the acceleration of gravity, c * _rk - hydraulic efficiency of use plots of flow parts of the machine is the series of steps of its working bodies, q _m - mechanical efficiency of the machine, n _0k, p _rk - volumetric and hydraulic efficiency of each stage to the row; but

- flow of transit flows between rows, for the embodiment of FIG. $ 1 where Ap is the leakage rate through the sliding end face of sleeve 8; (th _and ) _k1 , p _k1 , o _k1 , and _k1 , those _k1 are the values of the velocity moments, pressures, absolute values of the absolute and H (u = sot, r is the radius of the point), relative And 'speeds before (index индекс = 1) and behind the blades 6, i.e. in front of the blades 7 of the guide vane (1 = 2), as well as behind the blades 7 of the guide vane (1 = 3); about _and - the peripheral component of the absolute speed And + And ',, 1-3. hydraulic losses in the step to the next row.

Bleed-through channel 2 working fluid has acquired as a result of the foregoing workflow momentary mechanical power P n = s <? 2 ^t ^ ⁿ = k ² 'k = ^t} (8)

A = 1

The directions of movement of the working fluid, rotation ω of the shaft 4 of the machine and the action of the drive torque M 'applied to it, as well as the orientation of the circulations G _k1 are shown in FIG. 1 solid arrows mi.

When using the machine as a turbine, by virtue of the principle of reversibility of the working process in vane machines, the conversion of mechanical energy occurs with an inversion of the direction of flow of the working fluid, i.e. with its movement from the intake channel 2 under full pressure H 'and, therefore, with high hydromechanical energy to the drainage channel 3 with a usually minimum possible level of this energy. At the same time, the transition processes in the energy and power fields of the machine are carried out in the reverse sequence, namely, from the triggering of part Н'2 of the total pressure Н 'at the flow rate of the working fluid О', i.e. parts Ν ' ₂ ~ O'N' _{2 of the} total second mechanical energy Ν '~ O'N' of the working fluid before transmitting the useful power Ν, for example, to the electric generator, I rotate through the shaft 4 of the machine

- 6 014075 with an angular velocity ω and a driving (torque) moment M. The directions of movement of the working fluid and the shaft 4 of the machine, as well as the orientation of the circulations Г _к1 in the turbine application of the machine are shown in FIG. 1, 2 dashed lines.

Therefore, the balance equation of the total second mechanical energy of the working fluid in the machine and the net power N for the turbine operation is

N = £ N ^ 2, k = \ (9)

Ν-Μΰ>, X / ^ r _to r & r _y b _to r * _k ^ _to r _rk H _to \ t _to = 1, where:

(YU)

Hk = ^ - (Γ _k1 - Γ _k2 ).

(I) (12)

In expressions (9) - (12), H '| ... C' and Η _(: .Ο spent and useful head pressures of the stage of the kth * r series and costs, respectively, leakage rate through the sliding end face of sleeve 8 in this operating mode machines from the central channel 2 high pressure (with a full pressure of the working fluid N ') in the drain peripheral channel 3.

Since the principle of reversibility of the working process for blade machines is also valid for the other proposed solutions to the technical problem, a further description of the functioning of the machine is limited to consideration of the processes of pumping the working fluid, but in FIG. 5-14, the dashed arrows show the directions of movement of the working fluid, rotation, and the action of the drive torque of the shaft 4 of the machine when it operates as a turbine.

For the embodiment of FIG. 5 and when using the machine as a supercharger of an incompressible working fluid, the supplied power Ν 'from the shaft 4 of the machine, isolated by the casing 24, is transmitted to the hub 5, and from it it enters the blades 6 of the impeller with the conversion of its part Ν' ₃ into a useful second mechanical energy of the working fluid, expressed in creating a useful pressure H _{3 of} the central row stage (see Fig. 5, a dashed rectangle) with a useful supply of O. In this process, the circulation of G ₃₁ in front of the blades 6 is formed by the blades 7 of the intermediate row G ₃₁ G ₂₃ , and the circulation of G ₃₂ behind the blades 6 is reduced to the minimum attainable level of G _{33 by the} blades 7 of the next row.

Part N'-N3 of the supplied power N through the sleeve 10 is transmitted to the blades 6 of the impeller of the intermediate row stage. A further sequence of conversions of the supplied power into the useful second mechanical energy of the working fluid is similar to that described for the embodiment of the machine of FIG. 1-4 when it works as a supercharger.

In the U-shaped knee 11 of inversion, the flow is rotated 180 ° smoothly with the working fluid being transferred from the flowing part of the intermediate row stage to the flowing part of the central row stage while maintaining the equality (up to hydraulic losses in the knee 11) of the circulation behind the blades 7 of the guiding apparatus Г ₂₃ and in front of the blades 6 of the impeller G ₃₁ . The flowing part of the stage of the central row behind the blades 7 is in communication with the central channel 2 of the removal of the working fluid from the machine.

Internal overflows are formed in two radial sealing and sliding belts along the ends of the bushings 8, 10 with the leakage rate AO and Δθ ₁ , respectively.

The inversion case closure 13, rigidly fixed in the housing 1, forms the boundary of the Inverted Elbow 11 and is permanently connected to the vanes 7 of the intermediate row guide apparatus and the stator lattice 19. The stator lattice 19 is designed to increase the uniformity of the velocity field of the working fluid entering the channel 3, and then to the working bodies 6, 7 of the first stage of the peripheral row and the transmission of power loads from the blades 7 through the contactor 13 to the housing 1.

The working process of such a machine is described by equations (1) - (8) with the values of the parameter n = 3 and leakage rates between the rows k = 1,2,3 (see Fig. 5, 6) ^_ ~ Δξ) ⁺ Δβμ Δζ? 3 - ΔΟρ

In the embodiment shown in FIG. 6, also a three-row design of the machine with one stage of the working bodies for each row, the supply of the working fluid in the discharge mode, in contrast to FIG. 5, is carried out through channel 3 to the working bodies 6, 7 of the central row stage, and discharge through channel 2 from the working bodies 6, 7 of the peripheral row stage. In this case, equations (1) - (8) and (9) (12) of the mathematical description of the working process of such a machine remain valid, but with the number of rows n = 3.

For the embodiment shown in FIG. 7-9, double-row multi-stage in each row of the machine

- 7 014075 when it is in the discharge mode (see arrows in Fig. 7 in solid lines), the processes of transferring the supplied power Ν 'from the shaft 4 of the machine to the working fluid (here, the liquid) and its conversion into useful second mechanical energy N are not qualitatively differ from the hydromechanical interactions occurring in the embodiment of FIG. 1-4. The differences are as follows: the drive power Ν 'from the shaft 4 of the machine through a detachable connection - the key 12 and the hub 5 - enters the rotating (with angular velocity ω) sleeve 8, and from it through the sleeves 17 to the blades 6 of the impellers of each stage of both rows. By hydrodynamic interaction of the blades 6 and blades 7 with the working fluid, the supplied powers Ν ' ₁ , Ν' ₂ to the working bodies of the steps of the central and peripheral rows, respectively (Ν ' ₁ + Ν' ₂ = Ν ') are converted into useful second mechanical energy of the flow Ν ₁ , Ν ₂ (Ν ₁ + Ν ₂ = Ν). The reactive moments M _p1 , M _p2 arising in this process, the circular systems of the blades 7 of each stage through the outer and inner ring rims 16 are perceived by the body

one.

The suction of the working fluid into the flowing part of the working bodies of the steps of the peripheral row (see Fig. 7, the upper dotted rectangle elongated along the 0-0 axis) occurs through the peripheral channel 3 with the stator grating 19 (see Fig. 9, section V - V) . After flowing around the blades 6 and the blades 7 of the working bodies t! steps of this row with the acquisition of useful second mechanical energy Ν _{1, the} working fluid through the U-shaped knee 9 of inversion, made in the closure 13 with stator gratings 19 (see Fig. 8, section IV - IV), enters the flow part of the working bodies t ₂ steps of the central row (see Fig. 7, the inner dotted rectangle extended along the 0-0 axis).

As a result of the previously mentioned hydrodynamic interaction with the blades 6 and blades 7 of each stage of the central row, the working fluid with additional useful second mechanical energy Ν2 enters the U-shaped knee 11 of the casing contactor 14 with stator gratings 19 (see Fig. 9, section V - V ) fixedly installed in the housing 1. The removal of the working fluid with a useful second mechanical energy Ν1 + Ν2 = Ν is carried out through the annular central channel 2 between the stationary support housing sleeve 15 and the casing 24. Support -uplotnitelnye rotation assemblies between rotating and stationary components provide the perception of axial-radial loads with an acceptable level of internal working fluid leakages.

The balance equation of the supplied power and the useful second mechanical energy of the working fluid, as well as the equation for the reactive moments are of the form (1) - (8) (and (9) - (12) for the turbine mode of operation) with the number of stages in each row t _to > 1, k = 1.2.

In the embodiment of FIG. 10 three-row multistage in each row of the machine with a single-shaft scheme of its operation and application as a supercharger, the power Ν 'brought to the shaft 4 of the machine is divided into two flows потока' ₃ and Ν'-Ν ' ₃ . Part Ν ' ₃ is transferred to the blades 6 of the central row with its subsequent hydrodynamic transformation in the flowing part of the working bodies of this row (see Fig. 10, the dotted rectangle extended along the axis 0-0) into useful second mechanical energy of the working fluid Ν3. The reactive moments of MP3 formed in this process through the blades 7 of the central row and the support sleeve 15 are closed on the composite housing 1.

The sequence of formation of the parts Ν ' ₂ , Ν' ₁ from the power Ν'-Ν ' ₃ and their conversion into useful second mechanical energies Ν ₂ , Ν _{1 is} similar to that described for the execution of the machine of FIG. 7, so that the total useful second mechanical energy of the working fluid is equal to Ν = Ν ₁ + Ν ₂ + Ν3.

The withdrawal of the working fluid is carried out through channel 2.

The workflow is described by equations (1) - (8) [and (9) - (12) for the turbine mode] with parameter values η = 3, t _k > 1, k = 1, 2, 3.

The embodiment of the machine of FIG. 14, characterized by the absence of a hub 5 and the output of the rotating sleeve 8 behind the machine body 1, allows for a two-shaft operation scheme (see Fig. 12, 13 — a scheme of a two-shaft drive).

When the machine of FIG. 14, as a supercharger, the supplied power Ν ', for example, from an electric motor 25, the output shaft of which rotates at an angular speed ω ₀ , is divided into two streams например' = Ν 'in a twin-shaft multiplier made, for example, in the form of gears 21, 22 0 + Ν'3. Part Ν'3 of this flow enters the shaft 4 of the machine, rotating at an angular speed ω0, and the other part Ν ' ₀ is transmitted to the sleeve 8 rotating with an angular speed ωι <ω, for example, by means of a spline connection of the sleeve 8 with an additional shaft 20 (Fig. 13), so that Ν ' ₀ = M' ₀ <A1.

Further sequences and processes of transforming the power flows Ν ' ₁ , Ν' ₂ (Ν ' ₁ + Ν'' ₂ = Ν' ₀ ) in the peripheral and intermediate rows of the working bodies, as well as the flow Ν ' ₃ in the central series of working bodies into useful ones second mechanical energies of the working fluid Ν ₁ , Ν ₂ , Ν ₃ (Ν ₁ + Ν ₂ + Ν ₃ = Ν) do not fundamentally differ from those described previously in the single-shaft operation scheme of a three-row machine (see Fig. 10).

In the equations of the working process of the machine (1) - (8) and (9) - (12) for the considered two-shaft version of its execution it is necessary to make the following changes.

In equations (1), (9), Ν '= M' ₀ <L1 + M '<l, Ν = M ₀ <L1 + M <l, respectively, where M ₀ <L1 = Ν ₀ is the useful power transmitted from the working fluid to the rotating sleeve 8 during turbine operation of the machine.

In equations (3), (12) for values of the index k = 1.2, the angular velocity ω should be replaced by ω _μ

Embodiments of the machine of FIG. 11 and 14 are suitable for use as a working fluid of a gas or other compressible fluid and are distinguished by a design that takes into account the specifics of thermodynamic processes of compression (injection mode) and expansion (turbine operation mode) of such a body. A change in the heights of the blades 6 and the blades 7 (see Fig. 11, 14 parameters b ₁ , 1ι _2. 1ι ₃ ) provides a smooth narrowing of the flow part from step to step in each row of working bodies.

Workflows for machine options of FIG. 11 and 14 satisfy equations (1) - (8) for the injection mode and (9) - (12) for the operation of the machine in the turbine mode for the corresponding values of the indices n, t _, and with the introduction of mass flows C = ρθ and, instead of the pressures ρ, the enthalpies ί (the lower indices are omitted).

The use of a biplane system of blades 6 and blades 7 does not introduce qualitative changes in the working process of the machine, which still satisfies equations (1) - (8) and (9) - (12), however, as will be shown later, it improves its hydrodynamic indicators.

The workflow of a single- or multi-stage blade machine of the axial type of the traditional (made in accordance with the prototype), i.e., single-row (index k = n = 1), execution with a simplifying, but not fundamental assumption of a constant density ρ of the working fluid, is described by the same equations (1) - (8) and (9) - (12), as the proposed machine, but with the value of the parameter n in these equations equal to n = 1. In the multi-row execution, this parameter is equal to n = 2 or n = 3 . Therefore, with the same number of steps m ₁ in the compared machines and the same development set (injection mode), or used useful (turbine mode) the pressure of the stage Н1 of the peripheral (first) row, the total useful pressure Н in the multi-row machine, with identical (for definiteness) stages in each row, will exceed the value of this performance indicator for the machine of generally accepted design on DN (n = 2) = t ₂ N ₂ - in the case of applying a two-row scheme (presented in Figs. 1-4, 7-9, 11) and on DN (n = 3) = t ₂ N ₂ + t ₃ N ₃ in a three-row case (shown in FIG. 5, 6, 10). Here, as indicated earlier, Н2, Н3 and т2, т3 are the useful pressures of each stage and their numbers in the intermediate and central rows, respectively.

We give specific estimates of the increase (increment) in the pressure of the machines according to the proposed solutions, assuming the full efficiency of all stages to be the same, which is quite acceptable in evaluative calculations. We introduce the parameters

where 0 |. _: - average diameters of the working bodies of each row (see, for example, the designations of these parameters for a two-row machine in Fig. 2), the parameter n can take one of the values 1, 2, 3, and, obviously, 11 = b1 = 1. Then, for dimensionless pressure increments of two-row and three-row machines in general, we will have, respectively

DL (u = 2) = - And ₂ , Dy (n = 3) = “Y2 + - ku No. [/ I]” /]

Further, we take into account that for axial type machines Όμ = О _к , and _к1 = and _к and equations (3), (12), which determine the useful pressure of the steps of each row, can be written in the form

where k _ik are the coefficients of the moments of speed and u _k = < _{k k} t _k ,

Here in the expressions for the transport speeds and _{k the} angular velocity

ΰ)% = О> (к = 1, ц) for single-shaft and ω _Η = ω _{(: 2} = ω ₁ , ω _{(: 3} = ω for two-shaft execution of the machine, and in the expression for the increment of the DW circulations _to the parameter ζμ the second lower index is g = 2–3 under the injection and g = 23 turbine modes of operation.

and since

- 9 014075 finally get

This implies a quadratic dependence of the parameters 11 |. _: multi-row machine from angular speeds he and diameters E _to .

Subsequent theoretical analysis and evaluative computational studies of the conditions for ensuring stable operation of the machine with changes in feeds (expenses) of O. i.e. monotonically decreasing with increasing O pressure and flow characteristics of the steps H _k = H _1: (O). as well as generally accepted degrees of expansion of the interscapular and interscapular canals for injection processes. showed. that in the range of speed coefficients of the stage 1 ^ = 50 ^ 150, on average, ά ₂ «0.72 can be taken. ά ₃ "0.43. and for the coefficients of the velocity moments in the vicinity of the optimal operating modes, establish approximately the same value for all the series of these coefficients of the velocity moment. assuming them equal to _{|| to} «0.7. Suppose now for definiteness. that in a multi-row machine, the axial (along the O-O axis) dimensions of the rows. and also the number of steps in them k = 1, n are the same and together with the diameter E |. _: = ₁ are equal to the axial size of the active section of the flowing part, respectively. the number of steps t ₁ and the average diameter Ό _{1 of the} working bodies of the axial-type propeller bladed machine with its traditional (single-row) design. Then, in the case of two-row machines for a dimensionless pressure increment, we obtain Δ1ι (π = 2) «0.52. and in three-row versions with a single-shaft operation scheme Δ1ι (π = 3) "0.7. Respectively. at η = 2, a 1.5 times increase in the total useful head of machine H is achievable. and at η = 3, 1.7 times.

The embodiment of FIG. 6 allows the use of blades 6 of the impeller and blades 7 of the guide apparatus. located in the center row. as a screw step and thereby increase the anti-cavitation qualities of the machine during the discharge mode of its operation on the liquid.

If the three-row machines are made according to the two-shaft operation scheme (according to the variant of claim 15 of the formula) as shown in FIG. 12-14. with angular speeds of rotation of the shaft 4 of the machine ω (central row k = ω

3). and the rotating sleeve 8 ω ₁ (peripheral and intermediate rows k = 1.2). then with equal relationships. eg. 2 and 2.5. their total useful head H will increase successively by 2.2 and 2.6 times.

The use of periodic circular biplane systems of blades and blades in the working bodies of the steps of different rows of k (as shown in Fig. 3 with k = 1) instead of their monoplane systems will increase the pressure of the machine by another 10-15% due to an increase in the weekend (for the discharge mode working body) parts of the interscapular and interscapular canals of density directing the flow surfaces and. Consequently. reduce the deviation of the average direction of movement of the working fluid from these surfaces. those. reducing the effect of "under-rotation" of the flow.

In general, for all variants of execution can be obtained. although in varying degrees. but a qualitative increase in the total useful pressure of the machine. Moreover, in view of the axial and radial dimensions comparable with the analogue. as well as the metal construction of the proposed machine. its specific power will be increased.

Axial hydrodynamic forces P ₀₁ and P ₀₂ "(0.6 ^ 0.7) P ₀ . formed during the flow around the blades 6 of the peripheral and central rows (shown in Fig. 1). have opposite directions. in this connection, in such machines the resulting axial force decreases by 60-70%. acting on support sealing units. This increases the durability of the proposed blade machines.

The established results are achieved with the practical maintenance of high energy performance of the machine. those. at the level of these indicators. close to those for an analog single-row axial-type propeller machine.

through the sliding ends of the bushings 8. 10 (see, respectively. losses associated with leaks *

wearing (2), (10) for) are largely compensated by the absence of end losses in the inter-blade and inter-blade channels. formed by blades 6 and blades 7. mounted on the corresponding sections of the flowing parts without end gaps (see Fig. 1-6). The components of hydraulic losses included in the determination of the parameter ^ mk (see Eqs. (1), (9)) and associated with 180 ° rotation of the working fluid flow in the U-shaped bends 9. 11 inversions for low-speed machines. insignificant due to the low levels of the meridian and circumferential components of the absolute velocity in these channels and according to estimates, are in the range of 0.25-0.5%. Mapping

- 10 014075 energy indicators of low-speed machines, made according to the variants of the present invention, with single and multistage centrifugal (blowers) and centripetal (turbines) vane machines of traditional design shows that the proposed solutions allow, in addition to a qualitative increase in the total useful head H, to increase the overall Efficiency by 7 10% due to the lack of disc losses in the working bodies of the proposed machines. In a machine with two impellers, it is possible to control the total pressure by changing the number of revolutions of each of the impellers, given that the pressure of the steps of each row is proportional to the squares of the angular velocities ω and ω _{1 of the} shaft 4 and the additional shaft 20, respectively.

As a result of the invention, variants of an energy-efficient reversible blade machine for operating on liquids and gases are created and the arsenal of blade machines is expanded.

At the same time, specific power (per unit mass), useful pressure, and durability are increased, while maintaining high values of efficiency.

Information sources:

1. Pfleiderer K. Blade machines for liquids and gases. M. Mashgiz, 1960, p. 175, 176.

2. Lomakin A.A. Centrifugal and axial pumps. M-L., Mechanical Engineering, 1966, p. 15, 346, 348 (prototype).

Claims (20)

CLAIM 1. Blade machine, comprising a housing with central and peripheral channels of transmission of the working medium, connected to an external machine shaft, on which the hub of an axial impeller having a circular system of blades alternating along the axis of the shaft with a circular system of guide vanes fixed in housing, characterized in that the impeller is equipped with at least one ring sleeve rigidly connected to the hub, and the circular system of the blades of the impeller and blades guide its apparatus is made at least double-row with central and peripheral circular systems of rows of blades and blades, respectively, which are installed on both sides of the impeller hub, while the circular systems of blades of the guide vanes and blades of the impeller are installed in each row with the opposite sequence of alternation and in the housing there is at least one annular axisymmetric recess covering the impeller sleeve at one of the ends with the formation of a flow inversion knee. 2. Blade machine according to claim 1, characterized in that the impeller is made with two annular bushings rigidly connected to the hub, and the circular systems of the blades of the impeller and the vanes of the guide vane are made in three rows with the central, intermediate and peripheral rows of the circular systems of the blades and blades , while the cavity of the housing is made with two annular axisymmetric recesses located on opposite sides of the impeller, each of which covers a corresponding sleeve from one of the ends and replennye on both sides of the impeller blades to form a flow inversion knee between rows of circular systems the blades and vanes. 3. Blade machine according to claim 2, characterized in that one of the circular systems of the blades of the guide vane is partially located in the inversion knee. 4. Blade machine according to claim 1, characterized in that the circular systems of the blades of the impeller and the blades of the guide vane are double-row with multi-stage central and peripheral rows of the circular systems of the blades and vanes, the blades are rigidly mounted in sleeves fixedly mounted on the hub of the impeller on both its sides, the blades of the guide vane are rigidly mounted in the rims, the rims of the blades of the peripheral row are fixed in the housing, the sleeve of the impeller is rigidly connected to the hub, and in the housing of Two annular axially symmetric depressions in two additionally installed intermediate case contactors with the formation of two inversion knees are made, while the case is equipped with a support sleeve mounted concentrically with the shaft with rims of the central row blades fixed on it. 5. Blade machine according to claim 1, characterized in that the circular systems of the blades of the impeller and the blades of the guide vane are made three-row with multi-stage central, intermediate and peripheral rows of the circular systems of the blades and blades, the blades of the intermediate and peripheral rows are rigidly mounted in sleeves fixedly fixed on the impeller hub on either side of it, the blades of the guide vane are rigidly mounted in the rims, the rims of the blades of the peripheral row are fixed in the housing, the hub of the worker the wheels are rigidly connected to the hub, and in the case there are two annular axisymmetric recesses in two additionally installed intermediate case contactors with the formation of two inversion knees, the case is fitted with a support sleeve mounted concentrically to the shaft with rims of central and intermediate rows of blades fixed to it on both sides it is supplied with additional hubs consistently and fixedly mounted on it, on which the blades of the central row are rigidly fixed. - 11 014075 6. Blade machine according to claim 5, characterized in that the additional hubs of the blades and the rims of the blades of the central row are made of a triangular longitudinal section, and the blades and blades of the central row are made in pairs tapering towards each other. 7. Blade machine according to claim 1, characterized in that the circular systems of the blades of the impeller and the blades of the guide vane are double-row with multi-stage central and peripheral rows of the circular systems of the blades and vanes, the blades are rigidly mounted in sleeves fixedly mounted on the hub of the impeller on both its sides, the blades of the guide vane are rigidly mounted in the rims, the rims of the blades of the peripheral row are fixed in the housing, the sleeve of the impeller is rigidly connected to the hub, and in the housing of Two annular axially symmetric depressions in two additionally installed intermediate case contactors with two inversion knees are formed, the case is equipped with a support sleeve mounted concentrically to the shaft with rims of central row blades fixedly mounted on it, while the impeller sleeve is stepped, sleeves are made of varying thickness with trapezoidal longitudinal section, and the blades and blades are made in each row of variable height along the sleeve of the impeller, and the height of the blades and blades sequentially and uniformly decreases in the peripheral row from the peripheral channel transmission to the knee inversion, and in the next row - in the opposite direction. 8. Bladed machine according to any one of claims 4 to 7, characterized in that the central transmission channel is located inside the support sleeve on the side of its attachment to the housing, and the peripheral transmission channel is made on the opposite side and around the impeller sleeve. 9. Bladed machine according to any one of claims 1 to 6, characterized in that each sleeve of the impeller is made with a rounded end on the side of the inversion knee and with sliding elements on the side opposite to the inversion knee. 10. Blade machine according to any one of claims 1 to 7, characterized in that a stator grille of radial jumpers is installed in at least one transmission channel of the working medium. 11. Blade machine according to any one of claims 1 to 7, characterized in that the body is made integral. 12. Blade machine according to any one of paragraphs.1-7, characterized in that the circular system of the blades of the impeller and the vanes of the guide vane made monoplanar - with blades and vanes of the same length. 13. Blade machine according to any one of paragraphs.1-7, characterized in that the circular system of the blades of the impeller and the vanes of the guide vane made biplane - with periodically alternating blades and with periodically alternating blades of unequal length. 14. Blade machine, comprising a housing with a central and peripheral channels of transmission of the working medium, connected to an external machine shaft, on which is fixed the hub of an axial impeller having a circular system of blades alternately alternating along the axis of the shaft with a circular system fixed in the case of guide vanes, characterized in that it is provided with a second impeller with a sleeve embracing the first impeller, kinematically connected with an additional shaft connected to an external machine, of circles e systems of blades of impellers and blades of the guide vane are made three-row with peripheral and intermediate rows of circular systems of blades and blades, respectively, which are installed on both sides and around the hub of the second impeller, and with a central row of circular systems of blades and blades that are installed around the hub the first impeller, the hub is made of a composite of annular parts, each of which is detachably connected to the shaft and rigidly fastened to the blades of the central row, the peripheral blades and intermediate rows are rigidly mounted in sleeves mounted on the sleeve of the second impeller on both sides, the blades are rigidly mounted in the rims, the rims of the blades of the peripheral row are fixedly mounted in the housing, and the latter is equipped with a shaft sleeve fixed centrally to the central and intermediate rows, at the same time in the case there are two annular axisymmetric recesses in two additionally installed intermediate case contactors, and each of these recesses covers from one of the ends of the corresponding sleeve with the formation of a knee flow inversion. 15. Blade machine according to claim 14, characterized in that the sleeve of the second impeller is made stepped, sleeves and annular parts of the composite hub are made of varying thickness with trapezoidal longitudinal sections, and the blades of the impeller and vanes of the guide vane are made in each row of variable height along the corresponding sleeves, and the height of the blades and blades decreases in the peripheral row from the peripheral transmission channel to the inversion knee, in the intermediate row - in the opposite direction, and in the central Row - an inversion from the knee to the center channel bandwidth. 16. Blade machine according to claim 14, characterized in that the impellers are connected with the external machine gears with different diameters. 17. Blade machine according to any one of paragraphs.14-16, characterized in that at least one channel of the transmission medium installed stator grille of the radial jumpers. 18. Blade machine according to any one of paragraphs.14-16, characterized in that the casing is made composite. - 12 014075 19. Blade machine according to any one of paragraphs.14-16, characterized in that the circular system of the blades of the impellers and the vanes of the guide vane made monoplane - with blades and vanes of the same length. 20. Blade machine according to any one of paragraphs.14-16, characterized in that the circular system of the blades of the impellers and blades of the guide vane made biplane - with periodically alternating blades and with periodically alternating unequal length.