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WO1989008191A1 - Amplificateur centrifuge de pression de fluide a contrarotation biaxiale - Google Patents

Amplificateur centrifuge de pression de fluide a contrarotation biaxiale Download PDF

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Publication number
WO1989008191A1
WO1989008191A1 PCT/JP1989/000169 JP8900169W WO8908191A1 WO 1989008191 A1 WO1989008191 A1 WO 1989008191A1 JP 8900169 W JP8900169 W JP 8900169W WO 8908191 A1 WO8908191 A1 WO 8908191A1
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WO
WIPO (PCT)
Prior art keywords
impeller
shaft
bearing
fluid
hollow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP1989/000169
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English (en)
Japanese (ja)
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Individual
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Individual
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Filing date
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Publication of WO1989008191A1 publication Critical patent/WO1989008191A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/003—Having contrarotating parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/127—Multi-stage pumps with radially spaced stages, e.g. for contrarotating type

Definitions

  • the present invention relates to a two-axis inverting centrifugal type that enables the efficiency of a rapid-centre type (a mixed flow type is a kind of centrifugal type, and therefore includes a mixed flow type as well). Fluid rise E device.
  • centrifugal type is inferior in efficiency to the axial flow type, but it is widely used for applications where the comparative rotation speed Ns is small, that is, relatively high E and small capacity. .
  • Ns the comparative rotation speed
  • an object of the present invention is to provide a two-axis inverting centrifugal fluid-lifting apparatus capable of realizing near-high efficiency in an axial flow type, excluding the above-mentioned drawbacks of the conventional centrifugal turbomachine.
  • the principle of the present invention is to use a rotating winged diffuser (referred to as a second impeller) instead of a stationary diffuser, and to use this diffuser as a conventional impeller (referred to as a second impeller). -»Call it a car) and rotate at an appropriate speed in the opposite direction.
  • the present invention is based on the principle that the high-velocity fluid discharged from the outer periphery of the first impeller is directed to the second wing army rotating in the opposite direction to the first impeller: If necessary, use a winged fixed diffuser to uniformly increase the pressure, guide the person, and increase the large relative speed to the second car, With the deceleration due to the spread of the wings of the second impeller and the rotation due to its own rotation, the absolute velocity of the fluid at the exit of the second impeller will be significantly reduced. By converting the dynamics into highly efficient BE and guiding it to a drip-shaped casing at the low speed and a suitable casing having a wide space at the low speed, it is placed in the casing. The fluid is designed to reduce the friction loss of the fluid and to obtain a large increase in the power of the fluid as a whole with high efficiency. Aru in provides a two-axis reversed centrifugal fluid temperature E device.
  • the spiral casing ie, the diffuser of the focal blade
  • the fixed diffuser of the wing which has high efficiency.
  • the diffuser wings like the fixed diffuser, have the deceleration effect due to the rotation of the diffuser wing, as well as the flow deceleration effect due to the formation of the passage by the divergent divergence.
  • the flow is reversed and the flow is reversed.
  • the spiral casing around the impeller has a very wide absolute space at a significantly lower absolute speed compared to any appropriate conventional type. Introducing the casing into a universal housing with a small resistance makes it possible to use a fixed diffuser, as shown in Fig.
  • Fig. 1 is a cross-sectional view taken from the side of the simplest embodiment of the axial flow type single-sending machine according to the present invention, and Fig. 2 is viewed from the suction side of the embodiment shown in Fig. 1.
  • Fig. 3 and Fig. 4 are the velocity diagrams of the impeller and the output rotor of the embodiment of Fig. 1, and Figs. 5 and 6 are the implementation of Fig. 1.
  • Velocity diagram of the second impeller and the output rotor of the example, and Fig. 7 shows the side of the actual driving example in Fig. 1 where the bearing on the drive side is extended and provided off-axis of the second impeller.
  • FIG. 1 is a cross-sectional view taken from the side of the simplest embodiment of the axial flow type single-sending machine according to the present invention
  • Fig. 2 is viewed from the suction side of the embodiment shown in Fig. 1.
  • Fig. 3 and Fig. 4 are the velocity diagrams of the impeller and the output
  • FIG. 8 is a side sectional view of an example of a mixed flow impeller of the centrifugal type according to the present invention
  • FIG. 9 is a modification of the embodiment of FIG.
  • FIG. 10 is a side cross-sectional view schematically showing a lubrication system provided in the shaft of the impeller.
  • FIG. 11 is a cross-sectional view showing details of the system, and FIG. 11 is a cross-sectional view when the axis of the impeller is provided through the second impeller.
  • Fig. 1 The reason that the configuration in Fig. 1 is the simplest is that the first and second wing forces are directly fixed to the motor shaft. In this type, the suction pipe is open, so it is not possible to connect the S pipe to the suction pipe.However, the use as a push-in transmitter used with the suction pipe open is not rare.
  • 1 is the motor for the 1st wing
  • 2 is the shaft of the 1st wing army
  • 3 is the 1st wing
  • ..., 4 is the efficiency of the 1st wing.
  • ⁇ S is a vortex chamber provided between the first impeller 3 and the second impeller 6, and may be omitted in some cases.
  • the reversing second impeller is very effective in increasing the efficiency of the centrifugal blocker, but on the other hand, there is a seal to reduce the amount of discharge working fluid leaking to the lower side.
  • the cover of the second impeller 6 is divided into large and small diameter rings around the outer circumference of the impeller, which is larger than the circumference.
  • the small-diameter saliva 11 is attached to the large-diameter part, and is configured to be detachable. It is a good idea to provide a rubber ring where it overlaps the ring. It is important that this small-diameter part is as thin and light as possible, and that the dynamic balance does not substantially change during installation and removal.
  • the mass ring 12 of the first wing wheel and the mass ring of the cover 11 are provided.
  • the interior of the rubber ring 13 is configured as a labyrinth seal.
  • the outer surface is a labyrinth supported by the front cover 10.
  • the balance pinuton 15 is provided on the back of the No. 1 car, and a paranubiton 16 of the second wing car is provided over it, and the rabbinance 17 is sealed between them.
  • the outer periphery of the balance piston 16 is supported by the casing 9 and is sealed and sealed by the lab.
  • FIG. 2 shows an example of the shape of a preferred impeller based on the concept of the present invention.
  • Sunawachi first over Tsubasasha has Choku ⁇ radial wings and I Ndeyusa is Aru ⁇ conventional Yo Una fixed to You for antibody 3 ⁇ 4 large dynamic pressure in small outer diameter It is difficult for a diffuser to convert the large dynamic pressure into a static pressure efficiently, so that the impeller blades are usually used as retreating wings, and the ratio of dynamic EE is increased by increasing the degree of reaction as much as possible. Although it is small, I still get only the same efficiency as mentioned above.
  • the second wing vehicle will be inverted with respect to the first wing army, and the velocity diagram will be described below according to the third , fourth , fifth , and sixth diagrams.
  • the rotation speed of the second impeller is 1 / 2 Since it is only about ⁇ ⁇ ⁇ , the disc friction loss does not increase, and ultimately both the first and second wings can ensure extremely high efficiency.
  • Fig. 3 shows the velocity bran diagram of the wing rotor, where the peripheral speed at the average diameter of the R end of the suction rod of the inducer is 1 ⁇ , the flow velocity in the axial direction is Cm, And the relative velocity between the fluid and the 3 ⁇ 4 is given by Is small, so Ul is small, and C mi is originally small, so ⁇ is also small. This is the effect of Indukey
  • Figure 4 is ⁇ at a speed diagram of the first 3 ⁇ 4 wheel Delo, u 2 is ⁇ speed w s at a flow rate of peripheral speed 3 ⁇ 4 Cm 2 radius ten thousand toward Cm: the equal I.
  • the absolute velocity of the discharged fluid is C :.
  • the relative speed is small and the blade length is short, the frictional resistance inside the impeller is very small.
  • Fig. 5 shows the velocity line ⁇ of the second wing soldier B.
  • ii a is the speed of the wing of the second wing car, but this is about 1/10 of the peripheral speed of the first car.
  • C us is the circumferential velocity of the fluid flowing to the second car II, and if the partial velocity in the direction 2 of the above-mentioned speed 2 is C U2 ,
  • D sigma first 3 ⁇ 4 wheel Dero ⁇ Da is I ⁇ at Second blade ⁇ b diameter
  • B when the larger, C u 2 is rather much large dark
  • the speed is increased to C U a $, and the static EE rises corresponding to the dynamic pressure difference.
  • the main compartment 5 is made to have an appropriate size, the efficiency of converting the dynamic E into static pressure is high, and the effect of reducing the friction loss in the second vane is high, but if it is too large, I'm sorry.
  • the casing should be spiral and have a suitable wide space to allow easy flow in either direction.
  • the most important factor in improving efficiency is to adopt a pole-high rotation speed for the No. 1 impeller and to reduce the outer diameter of each of the No. II and No. II vehicles.
  • the bearing diameter of the # 1 impeller should be small, and the structure should be double-supported with the # 1 wheel interposed.
  • a vehicle front bearing is provided in the nozzle on the suction side of the impeller, and the other drive-side bearings are made to pass through by making the shaft of the second blade arm hollow, and further extended to make the second wheel of the second wheel
  • the bearing on the wheel side of the second impeller is supported by a bearing housing fixed to the casing 9, and the bearing is connected to the housing by a flange with a mark. Supported by bearing housing 23. Also, the bearing on the main side of the first impeller is bearing housing 24 connected by a flange with a sealing 23! 5 Supported.
  • the method of supporting the above bearings may be any other suitable method.
  • Driving of the No. 1 impeller is at the end of shaft 2 by direct connection to gears, belts, and smooth motors.
  • Driving of the 2nd wing arm is performed by boogies or teeth 25 fixed to shaft 8.
  • the bearings on the side of the wing of the wing are used.
  • the wing ⁇ is taken out of the suction casing, and the shaft extends through the hollow second wing army shaft 8 and is provided at a position separated from the second wing arm shaft 8. It is also practical to use such a configuration, as shown in Fig. 8 ⁇ In this case, the blade of the # 1 impeller is considerably long, and it is correspondingly thick to stabilize shaft rotation.
  • Fig. 8 shows an example of a mixed flow impeller which is a centrifugal type variant. If attention is paid to the fact that the mixed flow impeller reduces the gap between the shroud 26 and the impeller of each vehicle, not only will the effect be high, but also the configuration of the second impeller will be improved. As it becomes simple, it can be used as Is something you like. It is not universal for low flow rates. Fig.
  • the driving means as the driving means, for the first wing vehicle, the speed increasing gear, and for the second vehicle, the belt transmission is used, and the motors are separated but all belt transmissions are used.
  • the gears are all geared, the motors can be separate, and one can drive both, and the choice is appropriate. This is similar to other examples.
  • motors with SS kw or more are made to order, and the larger the size, the higher the cost. ⁇ Especially, the U starting current is small and easy. For example, it is better to use 2 units of 5.5 kW for each 110 kW unit, and the motor, starter, etc. will be much cheaper and the starting current will be small.
  • Fig. 9 shows that the bearing of the suction wheel of the impeller is installed at a distance outside the suction casing as in Fig. 8 , but the bearing of the motor is installed inside the shaft of the second wing army.
  • This is an example of the device of the present invention in which the shaft of the No. 1 wheel is prevented from becoming too long, and the bearing of the second wheel is not too large. If the bearing of the No. 1 impeller is placed on this side, the shaft of the First Wing Army will come out very short, so that the primary dangerous rotation speed can be greatly increased and the shaft seal Even if the lubricating oil leaks if it breaks down, there is no danger of it getting into the machine.
  • the lubrication system for the bearings of the first impeller provided in the second axle becomes slightly more complicated.
  • the bearing referred to as the in-shaft bearing for short, the bearing of Aru Second impeller to its periphery Tsu ⁇ - in the cane will be referred to as two heavy bearing, the Gai ⁇ of the lubricating system Figure 9 Nyori, Next, the details will be described with reference to FIG.
  • the two bearings supporting the second impeller are supported by bearing housings 23, 27 fixed to the casing 9 and fixed by flanges.
  • the lubricating oil for the bearing of the second impeller of the double-bearing is provided on the lubricating oil housing 28 fixed to the bearing housing 27 with a flange with a seal before it.
  • the inner bearing 31 is lubricated through a long hole 30 formed in the shaft core of the shaft, and the discharged oil passes through a number of pores formed in the inner periphery of a cavity ⁇ around the bearing end. It is provided to the impeller bearing of the second impeller, and is collected and discharged without being rafted outside by the oil collecting mechanism provided in the bearing housing.
  • the lubrication system for the second R-wheel bearing can be freely selected.
  • Reference numeral 32 denotes a shaft seal made of lubricating oil provided at the end of the shaft 8, and a mechanical seal, a screw seal, and the like are appropriately formed.
  • FIG. 1G is a detailed view of the double bearing portion, and details of the thrust bearing and the lubricating oil discharge gun are described below.
  • reference numeral 33 denotes a thrust ring fixed to the axle of the first R wheel by means of a threaded portion 35 which is in contact with the journal 34. 1 of the end face j Las preparative bearing 3 6 Nyo I * to stabilize the first wing ⁇ Tsu axial position receiving the scan lath bets vehicles.
  • Lubricating oil passes between the scan Las door ring 3 3 and vinegar Las door bearing 3 6, been thrown off me ⁇ Ni ⁇ o of the scan Las door-ring was finished to the parent angle, of the second impeller hub 3 7 Gather in the oil collecting grooves 3 8 provided on the inner surface! ? Then, the oil is supplied to the second vane bearing 40 of the second dextrous through a number of oil holes 39 provided in the periphery thereof.
  • the seal on the car side of the lubricating oil of the bearing 40 is specially designed to be combined with E of the airflow leaking between the parallax piston 15 and the labyrinth 17 D, special You have to pay attention to.
  • the air flow passes through a large number of ventilation holes 41 formed on the circumference of the corner of the parallax piston 16 of the second car, and is released to the outside air.
  • a few thousand mosquitoes remain in the balance piston 16.
  • the thrust ring 33 is formed into a cylindrical shape on the wheel, and the thrust bearing is located on the thrust bearing side. A constriction is provided to prevent the oil from leaking out of the cylinder, and a lapillus 42 is provided around the cylinder to prevent the leakage of lubricating oil.
  • the configuration of the space 44 is such that a thinner sleeve 46 is further extended from the balance screw 16, and a cover 47 having a labyrinth surrounding the outer periphery thereof is mounted on the bearing housing 23. Make it up.
  • the oil bearing 4 0 has lubricated the bearing Haujin Da 2 3 on the other side are gathered space 4 8 provided, is ⁇ from discharging b 4 9 provided on the lower ⁇ . Since the shaft bearing 31 rotates in the opposite direction to the journal 34, its relative speed is high, and resistance and heat generation must be increased accordingly, but in order to alleviate this, the bearing clearance must be reduced. You should make it bigger. This is because the relative speed is large and the stability of the shaft is maintained even if the clarity is increased a little. With this configuration, the length of the shaft of the first impeller is the shortest, and the central part can be made sufficiently thick, and the high-speed stability of the shaft can be increased. Suitable when required.
  • Fig. 1 1 shows that the shaft fixed to the cantilever by the first wing arm 3 penetrates the shaft of the hollow second impeller 6, and the bearing on the impeller side is inside the hollow shaft of the second impeller 6. provided 3 ⁇ 4 ⁇ , bearing the Mou ⁇ 5 I configuration Shi favored ⁇ at which the axis of the over impeller 3 fixedly provided position S which is out out through transmural the second impeller 6 Is shown.
  • Lubricating oil is supplied from an oil supply hole 29 provided in a bearing housing 24 for supporting a bearing behind the first impeller 3, and a hollow shaft 8 of the second blade 6 is provided for the in-shaft bearing 31. From the gap between the first end of the first impeller 3 and the shaft 2, move along the shaft 2, and for the bearing of the housing 24, move in the opposite direction. Lubricated and discharged respectively.
  • the end of the shaft 2 of the first impeller 3 is provided with a coupling and connected to the hooking shaft 1a, and the drive shaft 1a is increased in speed by an appropriate speed increasing device.
  • a boogie or gear may be used instead of the coupling to increase the belt speed or gear speed.
  • the belt is pulled from the left and right with an equal force and driven by two motors.
  • the second impeller is shown as driven by pulley 25, but this is also the gear.
  • the impeller shown in Fig. 11 has no side plate and only the mass ring, but this mass ring is intended to reinforce the centrifugal force of the blades of the people. And also to prevent fluid leakage.
  • the blower or the compressor of the present invention can improve the overall efficiency of the conventional machine from 65 to 75 to 85 to 9056, respectively. Is expected to save 20 to 30 * in the future, so the increase in the rating due to the dual axis reversal will be eliminated within one year due to power savings. You can do it.
  • the floor area of the blower of the present invention is reduced, a large-capacity blower can be obtained with the same floor area.
  • the present invention is not limited to a blower, and although there are some differences in terms of seals, the present invention is not limited to turbine pumps. However, similar configurations can be achieved, with similar increases in efficiency and benefits.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'amplificateur centrifuge de pression de fluide à contrarotation axiale ci-décrit constitue une amélioration dans une turbosoufflante centrifuge, un compresseur ou une turbopompe. L'amplificateur comprend deux roues à aubes de grandes et de petites dimensions. La roue à aubes de grandes dimensions (deuxième roue à aubes) couvre la roue à aubes de petites dimensions (première roue à aubes), tourne dans le sens opposé par rapport à la première roue à aubes et sert de diffuseur rotatif. Cette deuxième roue à aubes servant de diffuseur rotatif réduit de manière extrêmement efficace à une valeur proche de zéro la vitesse élevée d'un fluide déchargé par la première roue à aubes, ou dévie la trajectoire du fluide déchargé, diminue les pertes par friction du fluide à l'intérieur du carter et provoque globalement une forte augmentation de la pression du fluide avec un grand rendement.
PCT/JP1989/000169 1988-02-24 1989-02-21 Amplificateur centrifuge de pression de fluide a contrarotation biaxiale Ceased WO1989008191A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP4149088A JPH01216095A (ja) 1988-02-24 1988-02-24 二軸反転遠心型流体昇圧装置
JP63/41490 1988-02-24

Publications (1)

Publication Number Publication Date
WO1989008191A1 true WO1989008191A1 (fr) 1989-09-08

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Application Number Title Priority Date Filing Date
PCT/JP1989/000169 Ceased WO1989008191A1 (fr) 1988-02-24 1989-02-21 Amplificateur centrifuge de pression de fluide a contrarotation biaxiale

Country Status (2)

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JP (1) JPH01216095A (fr)
WO (1) WO1989008191A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2177086C2 (ru) * 1999-11-25 2001-12-20 Лесковский Михаил Михайлович Многоступенчатый насос
EP3077681A4 (fr) * 2013-12-03 2017-08-16 Flowserve Management Company Pompe à diffuseur rotatif

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4981857B2 (ja) * 2009-07-17 2012-07-25 三菱重工業株式会社 斜流圧縮機のディフューザ
WO2019103904A1 (fr) * 2017-11-22 2019-05-31 Parker-Hannifin Corporation Pompe hydraulique à axe courbé et à assistance centrifuge

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5397605A (en) * 1977-02-07 1978-08-26 Hitachi Ltd Centrifugal type fluid machinery

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5397605A (en) * 1977-02-07 1978-08-26 Hitachi Ltd Centrifugal type fluid machinery

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2177086C2 (ru) * 1999-11-25 2001-12-20 Лесковский Михаил Михайлович Многоступенчатый насос
EP3077681A4 (fr) * 2013-12-03 2017-08-16 Flowserve Management Company Pompe à diffuseur rotatif
US11396887B2 (en) 2013-12-03 2022-07-26 Flowserve Management Company Rotating diffuser pump

Also Published As

Publication number Publication date
JPH01216095A (ja) 1989-08-30

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