WO1989008191A1

WO1989008191A1 - Biaxial contrarotating centrifugal fluid pressure booster

Info

Publication number: WO1989008191A1
Application number: PCT/JP1989/000169
Authority: WO
Original assignee: Kawanami, Shunpei
Priority date: 1988-02-24
Filing date: 1989-02-21
Publication date: 1989-09-08
Also published as: JPH01216095A

Abstract

The biaxial contrarotating centrifugal fluid pressure booster of the present invention relates to an inprovement in a centrifugal turbo-blower, a compressor or a turbine pump. The booster includes two large and small vane wheels. The larger vane wheel (second vane wheel) covers the smaller one (first vane wheel), rotates in the direction opposite to the first vane wheel and functions as a rotary diffuser. The second vane wheel as the rotary diffuser decreases extremely efficiently the high speed of a fluid discharged from the first vane wheel to nearly zero, or deflects the direction of the discharged fluid, reduces the frictional loss of the fluid inside a casing and brings about as a whole a large pressure rise of the fluid with a high efficiency.

Description

Specification

Two-axis reversing fast-center type fluid pressure booster

Technology area

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.

Background art

Originally, the 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. . By the way, for the sake of explanation, we will explain the blower and EE compressor first.

The biggest cause that the efficiency of the conventional quick-core type is inferior to that of the axial flow type is that the efficiency of the diffuser for statically converting the high dynamic pressure applied to the vehicle is low. Sanyaru Rather, the present inventor has tested that the efficiency of Toshido itself is not bad at all, and it is possible to achieve 9056 or more depending on the setting. Despite, the overall efficiency翟通low N 6 5 ~ 7 5 6 Dearu with those of _s. Than those of the high-N s of large capacity overall efficiency 8 5 * to achieve Shitiru things also Aru is, however, a large-capacity axial flow type 9 ^0-9 5 * Niwaya beams reach Nai o

Accordingly, 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. You. However, 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. ) Also converts a large part of the power supplied by the short impeller to the first impeller into efficiency, and reduces the absolute velocity of the fluid from the second impeller to a moderate level. Therefore, the friction loss in the casing having the uniform space such as the spiral winding casing is reduced, and thus the friction loss is reduced. For N s, we will give near-efficiency to the axial flow type. Therefore, 髙 N s is given a high efficiency that is not inferior to the axial flow type.

Disclosure of the invention

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.

As a precautionary measure, a comparison of the conventional turbo transmitter without an EE with a fixed diffuser will be clarified.

First, the spiral casing, ie, the diffuser of the focal blade, is compared with the fixed diffuser of the wing, which has high efficiency.

Limits can efficiently consentration flashing speed fixed diffuser winged is in the Delo speed Z's B speed ratio of diffuser Za, Nai and 1 Z4 Ti Warete, Ru ₀ other and Eba, in human B 2 The 40 m / sec type can only slow down to 80 to 60 m / sec, and the dynamic pressure with that is almost taken away by the friction in the casing, and it is generated.

If the deceleration ratio is further increased, the length of the guide 大きく increases, and the diffuser and the casing also increase in size. On the other hand, when the rotating diffuser is used, 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. In addition, 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. 2 for the length of the second car, that is, the length of the rotating diffuser wing. Since the wing of the vehicle can be shortened, the friction loss within the wing is also reduced, and a high static E rise can be achieved with high efficiency by the combined effect. All of the above effects are rotated The effect is based on the user.

In addition, when the circumferential speed of the absolute speed of the robot and the rotor is reversed for the second impeller, it means that a large increase in power has been achieved there. However, in this model, the circumferential speed of the absolute speed of the rotor of the second impeller becomes opposite in the range exceeding the design flow rate. Considering the disadvantages, it is sometimes desirable to use spiral casings with casings that have a wide space so that they can easily flow in any direction.

A brief description of the screen

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. 8 is a side sectional view of an example of a mixed flow impeller of the centrifugal type according to the present invention, and 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.

The best form to apply the sound

The present invention will be described in more detail with reference to the accompanying drawings.

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. In Fig. 1, 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. _Β S is a vortex chamber provided between the first impeller 3 and the second impeller 6, and may be omitted in some cases. Has a size of 10 to 20 mm in all directions in the radius, reducing noise and equalizing the flow * In other words, to improve the efficiency of the second impeller ⁶ . However, if this swirl chamber 5 is made larger by a factor of D, it is rather disadvantageous. <7 is the motor for the sixth wheel 6, 8 is the second impeller shaft, and ⁹ is a spiral casing. In other words, when the peripheral speed of the absolute velocity of the airflow from the second vane wheel was designed to be almost zero, rather, it was made easier to flow by making it a rotationally symmetric or appropriate wide space: 5 Hey.

10 is the cover in front of the casing ¾ Opened when installing or removing the car ο

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. You need a husband. In other words, in Fig. I, 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. Also, the mass ring 12 of the first wing wheel and the mass ring of the cover 11 are provided.

1 and 3 keep the proper time and play the role of the seal. In some cases, 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.

Sealed at 14 to reduce leakage of high E fluid on the discharge side of the second impeller. 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. _{Do θ}

In addition, 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艤radial wings and I Ndeyusa is Aru _β conventional Yo Una fixed to You for antibody ¾ 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. In the present invention, 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. In addition, since a large static ε rise can be obtained and the motion of the discharge fluid can be significantly reduced, the rotation speed of the second impeller is 1 / 2 Since it is only about ι Ζι ο, 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 ¾ 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 ¾ wheel Delo, u ₂ is钼対speed w _s at a flow rate of peripheral speed _¾ Cm ₂ radius ten thousand toward Cm: the equal I. For the sake of simplicity, if the number is sufficiently large that the fluid flows exactly in the radial direction and the slip coefficient is 1, the absolute velocity of the discharged fluid is C :. However, since the relative speed is small and the blade length is short, the frictional resistance inside the impeller is very small.

In other words, it can be said that the pressure loss in the reciprocating-type impeller itself is small, and the in-vehicle efficiency is a highly variable impeller. Instead, the absolute velocity C ₂ of the fluid flowing out is large, and the efficiency of the diffuser is only a problem.

Fig. 5 shows the velocity line の 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 ,

C us = C us u ₂ and O

Here, D _sigma first ¾ wheel Dero径, Da is I § at Second blade覃人b diameter, by increasing the Moshitsu 5, 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. If 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.

However, if a very high E power rise is required, and the relative speed between the spears and the first and second wind turbines greatly exceeds the speed of sound, the room 5 It is also good to provide a diffuser with short wings on the outer circumference and to introduce it into the second vane after slowing down appropriately, but illustration is omitted.

The β view the velocity diagram of the second-wheel Delo, when compared with FIG. 5, the relative velocity of the blades sediment for about half dark from w _a to _{W 4,} which is flared Second wing interior passage It is something that slows down. In contrast, the peripheral speed Iotaiota ₄ Yotte absolute velocity of the circumference: 5 countercurrent speed C u ₄ inverts small in对to that of human B Till.

It is important to keep this inverted speed small in order to reduce the friction loss during guiding and discharging to the crown around the impeller. However, when the flow rate becomes larger than the design value, this CU ₄ approaches zπ, and when the flow rate further increases, it becomes the opposite direction.

To accommodate a wide range of changes in flow rate, the casing should be spiral and have a suitable wide space to allow easy flow in either direction. · In general, 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. In order to reduce the friction loss of the bearings, the bearing diameter of the # 1 impeller should be small, and the structure should be double-supported with the # 1 wheel interposed. For this purpose, 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 configuration shown in Fig. 7 off-axis is preferred. In some cases, of course, it is practically possible to increase the rotation speed of the 2nd wing army to about the same as that of the 1st vehicle and achieve a large increase in power. In this case, conventional two-stage Yo Ri efficiency in the Figure 7 _β can improve, sign of the intersection of the first drawing is the same over. In this case, the lubricating oil of the impeller-side bearing is sent to the bearing via the rib ¹⁹ shown in FIG. 7 and is discharged via the rib 20. Therefore, use a mechanical seal for the oil seal, or use a seal for the discharge fluid, or use both seals. In FIG. 7, 21 indicates the shaft seal portion. * 22 indicates the bearing part. Show.

In this case, 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. However, 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. This structure o Although the lubrication system and its seal are slightly more expensive, this structure is suitable for achieving high heat efficiency * and the structure of the suction roller is simplified. In Fig. ⁷ , the military personnel of the first soldier, Russia, are not separated from each other as shown in Fig. 1, but they are effective as bodies, but they are effective. Although the figure shows a sealed ball bearing as the bearing for the second impeller, the choice of bearing and lubrication is optional.

As a method of simplifying the seals of the bearings on the side of the wing of the wing, and avoiding the risk of mixing in the cabin if leaked, the bearings on the side of the wing of the wing are used. The wing 萆 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. The result is that the shaft of the second impeller is thicker D, and the impulse loss on the impeller side of the second impeller is unavoidable to increase, but the rotation speed of the second impeller is The impact on the overall efficiency is small because the loss is small and the loss itself is not large. 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. 8 shows 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.

Generally, motors with SS kw or more are made to order, and the larger the size, the higher the cost.ょ 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. Instead, 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且- in the cane will be referred to as two heavy bearing, the Gai薆of the lubricating system Figure ⁹ Nyori, Next, the details will be described with reference to FIG.

As shown in Fig. 9, 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. From the second impeller shaft 8 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 鄞 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. However, 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.

In FIG. 10, 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且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緣Niño 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. In other words, 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. However, since a part of the airflow flows into the labyrinth, the airflow does not mix with the main flow of the lubricating oil, so that the airflow passes through the air hole 41 and the space provided in the impeller wheel of the bearing housing 23. 4 Collected in 4 The ₀ This airflow in You are拚出from discharging b 4 5 kicked, a possibility that fine amount of oil is mixed because Aru places provided Yo Uniba' full completion capable separating the 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. On the other hand, the oil bearing 4 0 has lubricated the bearing Haujin Da 2 ³ on the other side are gathered space 4 8 provided, is拼出from discharging b ^{4 9} provided on the lower鄞. 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 ¾萆側, bearing the Mouｰ5 I configuration Shi favored单純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.

In the symbols written in Figure 11, all but the four goods 23a, 40a, 44a, 47a are the same as those already described. Indicates the same element. The oil that has lubricated the in-shaft bearing 31 is further guided to the bearing of the second impeller 6 in the examples of FIGS. 9 and 10, but in FIG. 11, the second impeller Stop guiding to the impeller side bearing 40a of 6, and use the space 44a formed by the bracket 23a that supports the bearing and the recess of the cover 47a. It is discharged from the upper and lower discharge rollers 45. The reason why 4'S is provided above and below is that It is used to escape a part of the gas from the rafted gas to the lubricating oil, and to drain the oil from below.

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. However, a boogie or gear may be used instead of the coupling to increase the belt speed or gear speed. In this case, 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.

Note that 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.

There is no swirl chamber around the outer periphery of the second wing blade, and it rotates in a wide casing, but the second wing blade 6 itself is an improved type of vortex chamber.ぃ. Industrial applicability

As described above, 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. In addition, since the floor area of the blower of the present invention is reduced, a large-capacity blower can be obtained with the same floor area. Further, 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.

Claims

The scope of the claims

1. The high-speed fluid discharged from the outer periphery of the first impeller is transferred to the second impeller, which rotates in the opposite direction to the first impeller, immediately or without a condensate chamber. Derived from the fixed diffuser after decelerating and raising it appropriately, the large relative speed is noticed to the second wing car, and the wing spread of the second wing the rotation of Nyoru flashing speed of the own I Yoru Slow down of the Nyo, efficiency Nyo Ri _¾ dynamic E to reduce markedly the absolute velocities of the fluid in the second-wheel Delo Yo KuShizu It is converted to E and guided at a low speed to a winding type casing around the outer periphery of the second impeller or an appropriate casing having a wide space, and the fluid friction applied to the casing is increased. A two-axis reversing centrifugal fluid rising EE characterized in that the loss is reduced and the large E rise of the fluid as a whole is obtained with high efficiency. apparatus.

2. The shaft of the first impeller extends to the suction side, and the shaft is the shaft of the prime mover itself, or is supported by the bearing while being rotated by the prime mover. The shaft of the second impeller extends in a direction opposite to the axis of the first impeller, and the shaft is driven by the shaft of the prime mover or rotated by the prime mover. 2. The twin-shaft reversing centrifugal fluid rising E device according to claim 1, wherein the device is supported by a bearing.

3. The shaft of the second impeller is formed hollow, and the end of the first impeller, which extends toward the suction side of the first impeller, is supported by the peripheral wall of the suction nozzle. A passage for supplying and discharging lubricating oil and a passage for sealing fluid are provided in the rib, and the first axle extending to the back of the first impeller is provided with the shaft described above. 2. The two-axis inverted centrifugal fluid E device according to claim 1, wherein the two-axis impeller has a hollow shaft penetrated through the hollow shaft of the second impeller and is supported by a bearing provided outside the hollow shaft. .

4. The shaft end on the impeller side of the second impeller is hollow, and the A bearing for holding the shaft end of the impeller, lubricating oil of the bearing is supplied via a long hole penetrating the center of the second impeller, and the other bearing of the first impeller is the impeller suction side. 2. The two-axis inverting centrifugal fluid elevating device according to claim 1, wherein the device is provided outside the suction casing provided in the device.

5. The shaft of the second impeller is hollow, and the cantilever shaft of the first impeller is penetrated concentrically. The bearing on the impeller side of the first impeller is set in the shaft at the end of the hollow shaft on the impeller side. The first and second bearings are fixedly provided at a position where the shaft of the first impeller comes off the hollow shaft, and the lubricating oil for the first impeller bearing is a bearing housing of the second impeller. And the first impeller are also supplied in the middle of the first bearing housing, and the inner bearing ら from the clearance between the end of the hollow shaft and the shaft of the impeller, and vice versa: 5 directions 2. The two-axis reversing centrifuge according to claim 1, wherein the two fixed bearings are arranged so as to enter along the axis of the first impeller and to be discharged as appropriate. Mold fluid riser E device.

6. The shaft of the second impeller is hollow, the shaft extending to the suction side of the first impeller is the bearing provided outside the suction casing, and the shaft extending to the other side is the same as that of the second impeller. 2. The two-axis inverted centrifugal fluid rising E device according to claim 1, wherein each of the bearings is supported by a bearing provided outside the hollow shaft through the shaft.

7. Divide the side plate of the second impeller into large and small diameter rings with the outer diameter of the first impeller being larger than the circumference of the first impeller. 2. The two-axis inverting centrifugal fluid type E device according to claim 1, wherein a mass ring is provided at a small diameter portion which is configured to be detachable.