The inductor pump with high suction power

 

The invention relates to inductor is connected upstream of the pump rotor great suction power. The inductor includes a crankcase having first and second cylindrical part of the inner wall and surrounding the rotor inductor with multiple blades. The first cylindrical part of the wall, beginning before the leading edge of the blades and partially overlapping blades of the rotor of the inductor, formed with a peripheral part of the blades gap above the gap formed in the peripheral part of the blades with the second cylindrical portion of the wall of the crankcase. The second cylindrical part of the inner wall of the crankcase adjacent to the first cylindrical part. The ratio of the gaps between the peripheral part of the blades and, respectively, the first and second cylindrical portions of the wall of the crankcase exceeds 10. The invention is aimed at eliminating cavitation instability while maintaining the suction. 3 C.p. f-crystals, 1 tab., 11 Il.

The present invention relates to an inductor for a pump with high suction capacity, including a crankcase surrounding the rotor inductor that includes a lot of blades that make up the gap with Carter.

There are various types of pumps with pain is x as argali, for rocket engines.

These pumps are supplied with the first input rotary element, called an inductor.

When the turbopump inducer with higher expense ratios common phenomenon Sorgenfrei cavitation.

Ifdenotes the coefficient of discharge of the machine, andodenotes the coefficient of discharge corresponding to the point adaptation of the inductor (i.e., the case when the flow is below the average inductor angle corresponding to the angle of the blades in the casing of the machine), various inductors American, European and Japanese origin operate at costs/oclose to 0,6. In this work area meets phenomenon Sorgenfrei cavitation. This phenomenon is present, in particular, in the inductor for the liquid hydrogen turbopump connected to the rocket engine VULCAIN 1, and also in the inductor for jekokilasonia turbopump United with the same rocket engine VULAIN 1.

Thus, by lowering the pressure at the inlet of the inductor observed phase torque cavitation, which causes considerable vibration and radial forces on the axle. This type of cavitation origin is tsya dominant when Sorgenfrei frequency Fs, part of the value of the order of 1.2 rotation frequency F0the car, with Versiliana frequency Fs is gradually approaching the synchronous frequency F0as continued pressure decrease power inductor.

In Fig. 6 schematically shows a curve: 1= f(), whereis the dimensionless pressure at the entrance to the inductor,- the pressure at the entrance to the inductor.

It is noted that this curve 1 consists of nearly horizontal portion 10 and, when the pressure reduction, Brokeback region 12 and the region of the trench 11, which corresponds to the phase rotating cavitation. Between the hump 10 and the cavity 11 there is a region where the slope of the curve defined d/dis negative. In this area there is a destabilization for the complete system of lines and pump. Part 13 of the curve corresponds to a drop characteristics when the overpressure of the inductor, when the value ofbecomes very weak.

Already been suggested, in particular, in published Japanese application 5-332300, change the geometry of the pump housing near the inductor to try STI 24 Carter gradually inclined portion 43 is reduced above (before) the blades 36 of the rotor 23 of the inductor and in the field 26 has a value D2 smaller than the diameter D1 of the inner wall part 27 Carter, located above the inductor, the diameter D2 remains larger than the diameter Dt of the rotor 23, forming a clearance J1 between the inner cylindrical portion of the crankcase 24 in region 26 and the rotor 23 of the inductor. Thus, the clearance J2 between the diameter Dt of the rotor 23 and part 27 Carter diameter D1 greater clearance J1 between the rotor 23 and the region 26 of the crankcase and is maintained at a small distance d1 above (before) the rotor of the inductor 23. In this known method, the clearance J2 twice the clearance J1. Anyway, the tests showed that under these conditions, the execution of the extended portion of the inner diameter of the crankcase above the rotor is not sufficient to avoid in all cases the torque cavitation and eliminate Sorgenfrei strip.

The solution proposed in Japanese patent application JP-A-5 332 300, does not allow a reliable way to eliminate vibration caused by the phenomenon of torque cavitation relative to the crankcase or relative to the rotor. The result remains the risk of damaging parts of the pump, for example, bearings, and that the fluid pressure at the inlet to the pump must remain above a minimum value, which may occur torque cavitation. Thus, it is desirable to reduce the fluid pressure at the inlet to the pump so that the pressure gekostet mechanical design of storage tank liquid connected to the pump with inducer.

Known inducer pump with high suction capacity, containing respectively having first and second cylindrical part of the inner wall and surrounding the rotor inductor having multiple blades. The first cylindrical part of the wall, beginning before the leading edge of the blades and partially overlapping blades of the rotor of the inductor, formed with a peripheral part of the blades gap above the gap formed in the peripheral part of the blades with the second cylindrical portion of the wall of the crankcase (SU 1023138 - the closest equivalent). The known device does not solve the problem of eliminating cavitation instability while maintaining the suction.

The present invention is to eliminate the above disadvantages and manufacturing of inductor pump great suction power, which will be eliminated Versiliana band in the whole range of the inductor in order to avoid the phenomenon of Sorgenfrei cavitation and reduce the risk of vibrations of large amplitude.

This task is solved through the inductor pump great suction power, having a crankcase surrounding the rotor inductor, including many who Yu blades and casing provides increased clearance, which value is greater than the normal clearance in the area, which leads simultaneously to the first cylindrical part of the inner wall of the crankcase above the rotor of the inductor and the area of the inner wall of the crankcase adjacent to the first cylindrical part and covering the above part of the rotor of the inductor by the distance starting from the leading edge of the blades of the rotor of the inductor, and the fact that the ratio between the size of the enlarged gap and the magnitude of the normal gap (gap normal values) greater than 10.

The magnitude of the normal gap is from 0.4 to 1% of the radius of the peripheral portion of the blades of the inducer.

As an example, the magnitude of the normal Sonora is from 0.4 to 0.9 mm, and the diameter of the enlarged gap from 5 to 10 mm

The distance along the axis of the rotor of the inductor, since the leading edge of the blades, is 15 to 20% of the axis length of the blades of the inducer.

Other characteristics and advantages of the invention become clear from the following description private implementation methods of the invention, given as examples, with reference to the drawings, in which: - Fig. 1 shows a schematic view showing the main feature of the invention associated with separatively geometry Carter, located on the rotor of the inductor in accordance with known methods of the invention - Fig. 3 shows a view in axial section of an example of manufacturing turbopump according to known methods, to which the invention is applicable, is shown in Fig. 4 shows the enlarged view in axial section of the inlet part of the pump according to Fig. 3, includes an inductor is shown in Fig. 5 shows a view of the end of the input part of Fig. 4, is shown in Fig. 6 shows the curve= f(), illustrating the development of overpressureinductor (without dimension) depending on pressureat the entrance to the inductor, to the classic pump - Fig. 7 on the same graph shows three curves= f(), where the two curves correspond to well-known equipment of the inductor, and the third curve corresponds to the equipment of the inductor according to the invention, - Fig. 8 shows the region of appearance Sorgenfrei frequency in the plane (/o,determined by the coefficient of discharge/oand pressureat the entrance to the inductor, for hr/964.gif">at the entrance to the famous classical inducer, in particular with the advent of sorgenfrey bands,
- Fig. 10 shows the development of the characteristic frequency bands depending on pressureat the entrance to such an inductor, which is supplied by the equipment according to the invention, with the configuration according to Fig. 1, with the complete elimination sorgenfrey bands, and
- Fig. 11 shows the development of the characteristic frequency bands depending on pressureat the entrance to such an inductor supplied with the equipment by known methods, such as shown in Fig. 2, namely with the advent sorgenfrey bands.

First, with reference to Fig. 3 and 5, for example, the inductor is known, in particular from Japanese application 5-332 330 and used in the pump 21 with great suction power, such as, for example, a turbo pump for forcing into the rocket engine of Argos, for example, liquid hydrogen.

The pump 21 with great suction power consists of the impeller 29, mounted on the shaft of rotation 28, the rear part of which has one or more of the wheels 31 of the turbine 30. The shaft 28 is installed in the crankcase housing 32 of the pump using at least one of the bearing 46. The rotor of the inductor 23 may include, for example, groups who m 34.

On the end portion of the input 39 of the crankcase 24 can be provided by the flanges 44 for fastening the tank with liquid or line supply of liquid. The stationary vanes 45, connected to the crankcase 24, may be provided between the rotor of the inductor 23 and the impeller 29.

Thus, the turbo pump 21 shown in Fig. 3, represents the inductor 23, 24, situated in the classical manner on the input directly to the pump with impeller 29 and provided with a structure designed to prevent vibrations caused by torque cavitation. For this purpose at the entrance of the crankcase separating the flow paths in the rotor, is provided by the extended portion 27 with an inner diameter D1 greater than the inner diameter D2 region 26 surrounding the blades 36 of the rotor 23.

Through various comparative studies have shown that this geometry Carter really contributes a small reduction Sorgenfrei torque cavitation, but does not completely eliminate sweringen strip and the corresponding radial vibration.

The invention has a different geometry Carter, other than those described in Fig. 2 to 5, and offers such a configuration of the crankcase, which allows you to safely and completely fix sverhsuschestvennaya in Fig. 2. It should be noted that the invention represents an improved inductor, which can be used with different types of pumps with high suction capacity and, therefore, not be limited by the design of the pump is described as an example with reference to Fig. 3 - 5.

In the configuration according to Fig. 1, the first cylindrical portion 127 of the inner wall of the crankcase 124, located in front of the rotor of the inductor 123, has a diameter greater than the diameter of the second cylindrical portion 126 of the inner wall of the crankcase 124, opposite the blades 136 of the rotor of the inductor 123. The area of the truncated-conical transition between the first and second cylindrical parts 127, 126 missing (as opposed to region 43 in Fig. 2), and the first cylindrical portion 127 of the inner wall of the crankcase 124 has continued in the form of additional cylindrical part A with diameter equal to the diameter of the cylindrical part 127, along an area d11, starting at the level of the leading edge of the blades 136, so that there is formed an enlarged gap J12, not only to the rotor of the inductor 123, but also along an area d11, covering the above part of the rotor of the inductor 123. When this ratio is maintained between the enlarged gap J12 Mei gap normal values between J11 part 126 of the inner wall of the crankcase 124 and the peripheral part of the blades 136 of the inductor is greater than 10. Clearance normal value ranges from 0.4 to 1% of the radius of the peripheral portion of the blades of the inducer.

As an example, the gap normal values J11 can be from 0.4 to 0.9 mm, and more clearance J12 to be from 5 to 10 mm

Usually the gap J11 equal to about 0.4 mm, while the gap J12 - 6 mm

Distance coverage d11, which extends along the axis of the rotor of the inductor 23, starting from the leading edge of the blades 136, may be from 15 to 20% of the axial length of the blades of the inducer.

Thus, regardless of the form of the leading edge, Versiliana band may not be available on all spending area of the inductor, if the crankcase has the above described structure with increased clearance, covering part of the rotor at a considerable distance d11 and significant value of the ratio J12/J11, i.e. above 10.

In Fig. 10 shows the change of the characteristic frequency bands depending on pressureat the entrance to the inductor for turbopump equipped with an inductor according to the invention. In normal position the rotation frequency F0the machine corresponds to the strip 61, and at low pressures - subsynchronous strip 62. It should be noted that this subsynchronous strip 62, which corresponds to sit the same drawbacks what sorgenfrey band known inducers.

As an example in Fig. 9 and 11 show the change in the characteristic frequency bands depending on pressureat the entrance to the inductor, for turbopump provided with a known inducer with normal clearance, on the one hand, and for turbopump equipped with an inductor described with reference to Fig. 2 to 5, on the other hand.

In Fig. 9 near the strips 53, 54, 56 corresponding to the rotation frequency F0machines and interference (noise) 55 arranged around the rotation frequency F0that shows a lot of other bands that correspond to the phenomena torque cavitation, causing vibration. Thus, there is a pronounced Versiliana strip 57 with the frequency Fs of the order of 1.1 to 1.2 rotation frequency F0. Versiliana strip 57 is present at relatively high and extended input pressuresthat prevents in practice. Strips 59, 60 also appear in Fig. 11 with the doubled frequency compared to the frequency of rotation F0. Other interfering strip 51, 58, corresponding to the combination of the rotation frequency F0and Sorgenfrei frequency Fs, also appear in the chart of Fig. 9. Thus, the strip 51 Clevo visible Versiliana strip 77, at relatively high and extended input pressure, next to a group of other United strips 72 to 76 and 78 to 80, the analysis of which can be done similarly to the strips 52-56 and 58-60 in Fig. 9.

Comparing Fig. 10 and Fig. 9 and 11, can be seen as reduced sources of harmful vibration when applying the configuration of the crankcase according to the invention.

However, if we consider the curve= f() in Fig. 7 and when the establishment of such a curve in the case of turbo pump equipped with an inductor according to the invention (curve 301), on the one hand, and in the case of a turbopump according to the method, with a normal gap (101), on the other hand, and in the case of a turbopump configuration Carter of which corresponds to that shown in Fig. 2 - 5 (curve 201), it can be noted that the curves 101 and 201 retain the configuration of the curve 1 in Fig. 6, after a simple part 110, 210 with the recess 111, 211, then bump 112, 212, prior to the fall 113, 213, while reducing pressureat the entrance to the inductor.

On the contrary, the curve 301 corresponding to the inductor according to the invention, shows that reducing pressureat the entrance to the inductor, the curve represents the plateau 310, which continues without convexity to a small value to reduce the dis negative, which guarantees the best stability system consisting of a pump and supply lines and discharge lines. This combination of cavity Carter, limited area A and covering the portion of the blades 136, and increased the ratio between J12/J11 eliminates sweringen cavitation on all site useful consumption.

Ifis the coefficient of discharge of the machine, it is noted that the phenomenon Sorgenfrei cavitation is limited in the plane (,) (Fig. 8).

Thus, at the higher value ofthe cavitation is absent or negligible (which corresponds to the part of the plateau of the curves in Fig. 6 and 7), and ifrepresents an amount close enough to the border, valid inductor appears asimmetrical different channels with the blades of the inducer with a strongly developed cavitation, which accompanies the inevitable fall of the characteristics overpressure inductor (which corresponds to the descending parts of the curves in Fig. 6 and 7).

However, in the event of a change in discharge coefficientmachine, you receive the point of the minimum consumption, Acutet cavitation.

In Fig. 8 shows the different areas marked REF In that match the geometry of the crankcase with the normal gap and the geometry of the crankcase of Fig. 2, with different values for the parameters J1, J2 and d1, which are listed in the table.

In Fig. 8 does not appear in the area corresponding to inductor representing the geometry of the crankcase according to the invention (Fig. 1), for example, with parameters J11= 0.4 mm, J12=6 mm and d11=12 mm from the moment of elimination Sorgenfrei strip.


Claims

1. The inductor pump with high suction capacity, containing respectively having first and second cylindrical part of the inner wall and surrounding the rotor inductor, having a set of blades, and the first cylindrical part of the wall, beginning before the leading edge of the blades and partially overlapping blades of the rotor of the inductor, formed with a peripheral part of the blades gap above the gap formed in the peripheral part of the blades with the second cylindrical portion of the wall of the crankcase, wherein the second cylindrical part of the inner wall of the crankcase adjacent to the first cylindrical part, and the ratio of the gaps between the peripheral part of the blades and, according to the present fact, the gap formed in the peripheral part of the blades with the second cylindrical portion of the wall of the crankcase is from 0.4 to 1% of the radius of the peripheral portion of the rotor blades of the inducer.

3. The inductor under item 1 or 2, characterized in that the gap formed in the peripheral part of the blades with the second cylindrical portion of the wall of the crankcase is from 0.4 to 0.9 mm, and a gap formed in the peripheral part of the blades with the first cylindrical portion of the wall of the crankcase, is from 5 to 10 mm

4. The inductor in one of the paragraphs. 1-3, characterized in that the distance along the axis of the rotor of the inductor determines the overlap portion of the blades of the rotor, since the leading edge of the blades, the first cylindrical portion of the wall is 15 to 20% of the axial length of the rotor blades of the inducer.

 

Same patents:

The invention relates to a centrifugal pump units with high suction capability mainly for pumping condensate from the condensers of steam power plants

Pump unit // 2187707
The invention relates to pumping units for supplying fuel to the propulsion unit of the aircraft

Pumps // 2187705
The invention relates to a pump engineering turn out and can be used for design of the water supply for extinguishing forest fires and water the young plants

Mixed flow pump // 2181853
The invention relates to mixed flow pumps for pumping liquids containing inclusions of gas or vapor, mainly for pumping fuel in the power plants of aircraft

The invention relates to a pumping device for relatively volatile liquid, such as motor fuel

Axial fan // 2208712
The invention relates to an axial fan to move air through the heat exchanger, designed for use in cooling and heating systems of vehicles

Axial fan // 2208711

The invention relates to the field of ventilation technology, namely the design of the impeller with backward-curved blades channel radial fan

The invention relates to mechanical engineering and can be used in high-speed turbomachines (turbopump units rocket engines, turbochargers, aircraft gas turbine engines)

The invention relates to the field of turbine construction and can be used in the input stages of axial compressors turbo machines, mainly for power plants and pumping stations

The invention relates to axial compressors, namely, their de-icing systems, and finds greatest application in gas turbine engines

The invention relates to mechanical engineering and can be used in the manufacture and balancing of rotors of such machines, such as centrifugal pumps and compressors

The invention relates to the field of engineering, namely technology rotors, and can be used for balancing of rotors, for example, centrifugal pumps, compressors

Mixed flow pump // 2181853
The invention relates to mixed flow pumps for pumping liquids containing inclusions of gas or vapor, mainly for pumping fuel in the power plants of aircraft

The invention relates to housings of pumps for pumping liquid under the conditions of heat exchange operating an internal combustion engine
The invention relates to hydrocarbon and pump engineering turn out and can be used in the construction of turbines and pumps with welded metal spiral chamber having a Meridian cross-section, close to circular

The invention relates to the design of gas turbine engines, mainly the construction site of the stator of an axial compressor

The invention relates to a water pump housing for pumping liquid under the conditions of heat exchange operating internal combustion engines

Body fluid pump // 2176751
The invention relates to a pump housings, providing a heat exchange combustion engine

The invention relates to chemical engineering, more specifically to the manufacture of turbochargers, the body of which is designed for high pressure, high performance, and can work in harsh environments, for example when pumping serviceregistered gases, in particular condensate fields
Up!