JP4963938B2 - Vertical shaft pump - Google Patents

Description

  The present invention relates to a vertical shaft pump.

  Conventionally, various attempts to reduce the height of the vertical shaft pump have been proposed. For example, Patent Document 1 discloses a vertical shaft pump in which a speed reducer is integrally provided on the upper outer surface of a discharge elbow. Patent Document 2 discloses a vertical shaft pump in which a part of a reduction gear is built in a discharge elbow.

  However, in any of the vertical shaft pumps described in Patent Documents 1 and 2, since the speed reducer is arranged in the discharge elbow, the speed reducer is positioned at a certain distance above the installation floor to which the vertical shaft pump is fixed. To do. Therefore, there is a tendency that vibration and noise generated by the speed reducer during operation of the vertical shaft pump increase.

  Further, in the vertical pump described in Patent Document 2, since the speed reducing device exists in the discharge elbow where the water flow is changed from the vertical direction to the horizontal direction, the fluid resistance in the discharge elbow increases. As a result, the pressure loss in the discharge elbow increases and the pump efficiency decreases.

Japanese Patent No. 3306749 Japanese Patent No. 3623135

  It is an object of the present invention to reduce the vibration and noise of a reduction gear in a vertical shaft pump and to keep the height from the installation floor low without lowering the pump efficiency.

The present invention relates to a pumping pipe extending in the vertical direction and having a suction port disposed at the lower end side, a main shaft extending in the vertical direction in the pumping pipe and having an impeller fixed to the lower end side, and an upper end side of the pumping pipe A vertical shaft pump having a discharge elbow disposed on the floor includes a straight tubular suspension pipe fixed to the installation floor, connected to the discharge elbow on the upper end side, and connected to the upper end side of the pumping pipe on the lower end side. A first part built in the suspension pipe and a tube wall of the suspension pipe, one end connected to the first part and the other end arranged outside the suspension pipe A casing having a second portion and a third portion disposed outside the suspension pipe and connected to the other end of the second portion, and extending in the vertical direction, the upper end side being the first portion Placed in the front and the bottom side is located outside the casing An output shaft connected to the upper end of the main shaft, an input shaft extending in the horizontal direction, having one end disposed in the third portion, and the other end positioned outside the casing and connected to the prime mover side A vertical shaft pump comprising: a reduction gear disposed in the casing and including a power transmission mechanism that transmits rotation input to the input shaft from the prime mover side to the output shaft.

  The first part of the casing of the speed reducer is built in the suspension pipe, the second part penetrates the suspension pipe, and the third part is arranged outside the suspension pipe. Therefore, the uppermost part of the casing of the reduction gear can be set to a height equal to or lower than the uppermost part of the discharge elbow, and the height of the vertical pump from the installation floor can be kept low.

  As compared with the case where the casing of the speed reduction device is arranged on the suspension pipe fixed to the installation floor, and the casing of the speed reduction device is arranged on the discharge elbow, the speed reduction device is located closer to the installation floor. Therefore, it is possible to reduce the vibration and noise generated by the speed reducer when the vertical pump is operated. Further, since the first portion of the casing of the speed reducer is built in the suspension pipe, noise generated by the speed reducer when the vertical shaft pump is operated can be reduced.

  Furthermore, the first portion of the casing of the speed reducer is arranged not in the discharge elbow where the direction of the water flow is changed from the vertical direction to the horizontal direction, but in a straight tubular suspension pipe. Therefore, there are no obstacles such as protrusions that increase fluid resistance in the discharge elbow, and pressure loss in the discharge elbow can be reduced, so that pump efficiency can be increased. By optimally setting the cross-sectional area of the flow path between the suspension pipe and the casing of the speed reducer with respect to the cross-sectional area of the pumping pipe, specifically, by setting these cross-sectional areas equal to each other Pressure loss can be reduced.

  Lubricating oil is sealed in at least a part of the space in the casing of the speed reducer, and deforms according to a differential pressure between the pressure of the lubricating oil in the space and the static pressure of the flow path in the suspension pipe. It is preferable to further include an automatic pressure adjusting device that changes the volume of the space so that the pressure of the lubricating oil becomes equal to the static pressure in the flow path.

  By providing this automatic pressure regulator, it is possible to prevent the lubricating oil from leaking into the flow path in the suspension pipe of the casing of the speed reducer due to the pressure difference between the inside and outside of the casing of the speed reducer. In addition, it is possible to prevent moisture from entering the casing from the flow path in the suspension pipe due to the pressure difference between the inside and outside of the casing of the reduction gear.

  It is preferable to further include a drain pipe having one end communicating with the bottom side of the first portion of the casing and the other end opened to the atmosphere.

  Moisture generated by dew condensation in the casing of the speed reducer or moisture that has entered the casing from the flow path in the suspension pipe is quickly discharged from the bottom of the first portion to the outside of the casing through the drain pipe. . Therefore, by providing this drain pipe, it is possible to prevent the lubricating oil sealed in the casing of the speed reducer from being deteriorated by moisture.

  In the vertical shaft pump of the present invention, the first part of the casing of the speed reducer is built in the suspension pipe, the second part penetrates the suspension pipe, and the third part is disposed outside the suspension pipe. ing. Therefore, the uppermost part of the casing of the reduction gear can be set to a height below the uppermost part of the discharge elbow, the height of the vertical pump from the installation floor can be kept low, and the prime mover is provided separately from the installation floor. There is no need to install a floor, nor is it necessary to install a prime mover on a large, high pedestal installed on the installation floor.

  In addition, the speed reduction device is disposed closer to the installation floor than the case where the speed reduction device casing is disposed on the discharge elbow, and the first portion of the speed reduction device casing is incorporated in the suspension pipe. The vibration and noise generated by the speed reducer during operation of the vertical shaft pump can be reduced.

  Furthermore, since the first part of the casing of the speed reducer is arranged not in the discharge elbow where the water flow is changed from the vertical direction to the horizontal direction, but in the straight tubular suspension pipe, the pressure loss in the discharge elbow The pump efficiency can be increased.

  By providing the automatic pressure regulator, it is possible to prevent leakage of lubricating oil from the casing of the speed reducer to the flow path in the suspension pipe and intrusion of moisture from the flow path in the suspension pipe into the casing.

  By providing the drain pipe, moisture in the casing of the speed reducer can be quickly discharged to the outside, and the lubricating oil sealed in the casing can be prevented from being deteriorated by moisture.

  Next, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

(First embodiment)
1 to 3 show a vertical pump 1 according to a first embodiment of the present invention. A pump casing 2 of the vertical shaft pump 1 is fixed to an installation floor 4 provided above the water tank 3. The pump casing 2 has a straight tubular pumping pipe 6 extending in the vertical direction, a vane casing 7 connected to the lower end of the pumping pipe 6, and a bell connected to the lower end of the vane casing 7 so that the lower end forms a suction port 8 a. A mouse 8 is provided. Further, the pump casing 2 includes a discharge elbow 10 connected to the upper end side of the pumped water pipe 6 through a hanging pipe 9 described in detail later. The discharge elbow 10 is curved from the vertical direction to the horizontal direction toward the discharge port 10a at the upper end. The discharge port 10a is connected to a pipe (not shown) to the discharge water tank side.

  In the pump casing 2, a main shaft 11 extending in the vertical direction is rotatably supported by underwater bearings 12A and 12B. An impeller 13 is fixed to the lower end of the main shaft 11 located in the vane casing 7. On the other hand, the upper end of the main shaft 11 located in the vicinity of the upper end of the water pump 6 is connected to an output shaft 21 of a speed reducer 16 described later via a coupling 14.

  The suspension pipe 9 is a straight tube with both ends open, and includes a flange 9a to which a discharge elbow 10 is fixed at the upper end, and a flange 9b for suspending the pumped water pipe 6 to the lower end side. A base plate 9c for fixing to the installation floor 4 is integrally provided outside the lower flange 9b. A through hole 4 a for inserting the pump casing 2 is formed in the installation floor 4. The base plate 9c is fixed to the installation floor 4 in the vicinity of the hole edge of the through hole 4a. The pumping pipe 6 fixed to the flange 9 b of the hanging pipe 9 is inserted into the through hole 4 a and extends toward the bottom of the water tank 3. In FIG. 2, 9d is a bolt hole for inserting a bolt (not shown) for connection with the pumping pipe 6 provided in the flange 9b, and 9e is for fixing to the installation floor 4 provided in the base plate 9c. This is a bolt hole through which a bolt (not shown) is inserted.

  A prime mover (not shown) is disposed on the installation floor 4, and an output shaft of the prime mover extends in the horizontal direction. The vertical shaft pump 1 includes a reduction gear 16 that decelerates and transmits the rotation of the output shaft of the prime mover to the main shaft 11 and converts the direction of the rotation shaft from the horizontal direction to the vertical direction. In other words, the speed reducer 16 functions as a converter for transmitting the driving force.

  The casing 17 of the speed reducer 16 is provided integrally with the suspension pipe 9, and the inside thereof is sealed against the atmosphere and flowing water in the pump casing 2. The casing 17 includes a first part 18 built in the suspension pipe 5, a second part 19 penetrating the pipe wall of the suspension pipe 9, and a third part arranged outside the suspension pipe 5. 20.

  The first portion 18 of the casing 17 includes a cylindrical portion 18a extending in the vertical direction, and hemispherical shell portions 18b and 18c provided at the lower and upper ends of the cylindrical portion 18a. The first portion 18 is arranged so that the axis of the cylindrical portion 18 a coincides with the axis of the flow path (circular cross section) in the suspension pipe 9. Due to the shape and arrangement of the first portion 18, an increase in flow resistance due to the incorporation of the first portion 18 in the suspension pipe 9 is suppressed to a minimum. Although the upper cylindrical portion 18a slightly protrudes from the lower end of the discharge elbow 10, the discharge elbow 10 is a straight tube extending in the vertical direction in this portion. That is, the first portion 18 of the casing 17 does not enter the portion where the discharge elbow 10 is bent from the vertical direction to the horizontal direction.

  The second portion 19 of the casing 17 is a cylindrical portion extending in the horizontal direction and penetrates the vicinity of the upper end of the tube wall of the suspension tube 9. One end of the second portion 19 (the right end portion in the figure) is located in the suspension tube 9 and is connected to the cylindrical portion 18 a of the first portion 18. The other end (the left end in the figure) of the second portion 19 is located outside the suspension tube 9 and is connected to the third portion 20.

  The third portion 20 of the casing 17 has a substantially rectangular parallelepiped hollow box shape, the bottom wall of which is constituted by the lower flange 9a of the suspension pipe 9, and the lower right portion of FIG. It is constituted by the tube wall of the tube 9.

  The output shaft 21 of the speed reducer 16 extends in the vertical direction, the upper end is disposed in the first portion 18 of the casing 17, and the lower end is located outside the first portion 18 and inside the hanging tube 9. The lower end of the output shaft 21 is connected to the upper end of the main shaft 11 by the coupling 14 as described above. The output shaft 21 is rotatably supported by the hollow shaft 22 and the two ball bearings 23A and 23B while being positioned in the thrust direction. Further, shaft sealing devices 24A and 24B are attached to a portion where the output shaft 21 penetrates the lower hemispherical shell portion 18c of the first portion 18 and a portion spaced above the portion, respectively. Yes.

  The input shaft 26 of the speed reducer 16 extends in the horizontal direction and is rotatably supported by two ball bearings 23C and 23D in the third portion 20 of the casing 17. The input shaft 26 has one end (right end in the figure) disposed in the third portion 20 of the casing 17 and the other end (left end in the figure) disposed outside the casing 17. The other end of the input shaft 26 is connected to the prime mover as described above. A shaft sealing device 24C is attached to a portion of the third portion 20 through which the input shaft 26 passes.

  In the present embodiment, the power transmission mechanism that transmits the rotation input from the prime mover to the input shaft 26 to the output shaft 21 includes a pair of spur gears 27A and 27B, an intermediate shaft 28, and a pair of bevel gears 29A and 29B. ing. First, a spur gear 27 </ b> A is fixed to one end of the input shaft 26. A spur gear 27B that meshes with the spur gear 27A is fixed to one end of an intermediate shaft 28 that extends in the horizontal direction. The intermediate shaft 28 is rotatably supported by a ball bearing 23E in the third portion 20 of the casing 17 and two ball bearings 23F and 23G in the second portion 19. A bevel gear 29 </ b> A fixed to the other end of the intermediate shaft 28 meshes with a bevel gear 29 </ b> B fixed to the upper end of the output shaft 21. The rotation of the prime mover input to the input shaft 26 is transmitted to the output shaft 21 via the spur gear 27A, the spur gear 27B, the intermediate shaft 28, the bevel gear 29A, and the bevel gear 29B. During this time, the rotation speed is reduced and the direction of the rotation axis is changed from the horizontal direction to the vertical direction.

  The vertical pump 1 of the present embodiment having the above configuration has the following characteristics.

  First, the casing 17 of the speed reducer 16 has a first portion 18 built in the suspension tube 9, a second portion 19 penetrating the suspension tube, and a third portion 20 outside the suspension tube 9. Is arranged. Therefore, the uppermost part of the casing 17 of the speed reducer 16 can be set to a height below the uppermost part of the discharge elbow 10, and the height of the vertical pump 1 from the installation floor 4 can be kept low. Therefore, it is not necessary to install another floor provided with the prime mover above the installation floor 4, and it is not necessary to install the prime mover on a large and high pedestal installed on the installation floor 4.

  Next, the casing 17 of the speed reducer 16 is arranged on the suspension pipe 9 fixed to the installation floor 4. Compared with the case where the casing of the speed reducer is arranged on the discharge elbow 10, the speed reducer 16 is installed on the installation floor 4. It is arranged close to. Therefore, vibration and noise generated by the reduction gear 16 when the vertical shaft pump 1 is operated can be reduced. Further, since the first portion 18 of the casing 17 of the speed reducer 16 is built in the suspension pipe 9 (arranged in the flow of pumped water), the operation of the vertical pump 1 is also performed in this respect. Sometimes the noise generated by the speed reducer 16 is reduced.

  Furthermore, the first portion 18 of the casing 17 of the speed reducer 16 is arranged in the straight tubular suspension pipe 9 rather than in the discharge elbow 10 in which the direction of the flow of the pumped water is bent from the vertical direction to the horizontal direction. Has been. Therefore, there are no obstacles such as protrusions that increase the fluid resistance in the discharge elbow 10, and the pressure loss in the discharge elbow 10 is not reduced, so that the pump efficiency can be increased accordingly. Pressure loss can be reduced by optimally setting the flow path cross-sectional area 51 between the suspension pipe 9 and the casing 17 of the speed reducer 16 with respect to the flow path cross-sectional area 50 of the pumped-up pipe 6. Specifically, FIG. 1 and FIG. 2 schematically show the magnitude relationship between the flow path cross-sectional areas 50 and 51, but the flow path cross-sectional area between the suspension pipe 9 and the casing 17 of the speed reducer 16. The pressure loss can be reduced by setting 51 equal to the channel cross-sectional area 50 of the water pump 6.

  Referring to FIG. 1, the inside of the casing 17 of the speed reducer 16 includes a first space 31 </ b> A on the upper side by the shaft seal device 24 </ b> A and a second lower side than the shaft seal device 24 </ b> A (the bottom side of the first portion 18). Space 31B. The first and second spaces 31A and 31B are sealed with each other by a shaft seal device 24A. The power transmission mechanisms (spur gears 27A and 27B, intermediate shaft 28, and bevel gears 29A and 29B) are all disposed in the first space 31A, and lubricating oil is sealed in the first space 31A. . In other words, the entire first space 31A is filled with lubricating oil.

  An automatic pressure regulator 33A is provided for maintaining the pressure of the lubricating oil in the first space 31A equal to the static pressure of the flow path in the suspension pipe 9. The automatic pressure adjusting device 33A includes a pressure introducing pipe 34 having both ends opened and a bellows 35 (variable member) having one end opened and the other end closed. One end of the pressure introducing pipe 34 penetrates through the upper part of the cylindrical portion 18a of the first part 18 of the casing 17 to a through hole 18d that communicates the flow path in the first space 31A and the suspension pipe 9. It is attached. An open end of a bellows 35 is attached to the other end of the pressure introducing pipe 34. Even if the bellows 35 has a plurality of annular protrusions formed at intervals by applying pressure from the inside to a cylindrical body made of metal or the like, the inner edge and the outer edge are alternately formed on a plurality of thin and corrugated annular plates. It may be formed by joining.

  The pressure of the lubricating oil in the first space 31A acts on one side (left side in the figure) of the closed end of the bellows 35. Further, the static pressure of the flow path in the suspension pipe 9 acts on the other side (right side in the figure) of the closed end of the bellows 35 via the pressure introduction pipe 34. In other words, a differential pressure between the pressure of the lubricating oil and the static pressure of the flow path acts on the closed end of the bellows 35. A through hole 18 d connected to one end of the pressure introducing pipe 34 is provided in the cylindrical portion 18 a of the first portion 18 of the casing 17, and is orthogonal to the water flow direction in the flow path in the hanging pipe 9. Have an opening. Thereby, the static pressure acts on the other side of the closed end of the bellows 35, but the dynamic pressure hardly acts.

  When the pressure of the lubricating oil and the static pressure of the flow path are balanced to a state where the pressure of the lubricating oil is higher than the static pressure of the flow path, the bellows 35 contracts by an amount corresponding to the differential pressure. The volume of the space 31A increases. As a result, the pressure of the lubricating oil in the first space 31A decreases, and the state returns to a state where the pressure of the lubricating oil and the static pressure of the flow path are balanced. On the contrary, when the pressure of the lubricating oil and the static pressure of the flow path are in balance, when the static pressure of the flow path changes to a higher state than the pressure of the lubricating oil, the bellows 35 is an amount corresponding to the magnitude of the differential pressure. Since it extends, the volume of the first space 31A decreases. As a result, the pressure of the lubricating oil in the first space 31A increases, and the state returns to a state where the pressure of the lubricating oil and the static pressure of the flow path are balanced. As described above, the automatic pressure adjusting device 33A can maintain the pressure of the lubricating oil in the first space 31A and the static pressure of the flow path in a balanced state. Therefore, leakage of the lubricating oil from the first space 31A to the flow path in the suspension pipe 9 (which occurs due to the fact that the pressure of the lubricating oil is higher than the static pressure of the flow path) can be prevented. In addition, it is possible to prevent moisture from entering the first space 31A from the flow path in the suspension pipe 9 (which occurs due to the static pressure of the flow path being higher than the pressure of the lubricating oil).

  The second space 31 </ b> B of the casing 17 of the speed reduction device 16 communicates with the atmosphere by a drain pipe 36. The drain pipe 36 has one end opened to the second space 31B in the casing 17 and the other end opened to the atmosphere. However, a normally closed gate valve 37 capable of manual operation is provided in the middle of the drain pipe 36, and lubricating oil is sealed in the second space 31B.

  In order to automatically adjust the pressure in the second space 31B, an automatic pressure adjusting device 33B having the same structure as the above-described automatic pressure adjusting device 33A is provided. The automatic pressure adjusting device 33B includes a pressure introduction pipe 34 having both ends opened and a bellows 35 (variable member) having one end opened and the other end closed. One end of the pressure introducing pipe 34 penetrates the lower part of the cylindrical portion 18a of the first part 18 of the casing 17 and communicates the second space 31B with the flow path in the hanging pipe 9. Is attached. A differential pressure between the pressure of the lubricating oil in the second space 31B and the static pressure of the flow path acts on the closed end of the bellows 35, and the bellows 35 expands and contracts accordingly, thereby lubricating in the second space 31B. It can be maintained in a state where the oil pressure and the static pressure of the flow path are balanced. Thereby, the inside of the casing 17 of the speed reducer 16 can be more reliably sealed.

  Moisture generated by dew condensation in the first portion 18 of the casing 17 or moisture that has entered the first portion 18 from the flow path in the suspension pipe 9 is the second space on the bottom side of the first portion 18. Gather at 31B. When the gate valve 37 is opened, the moisture collected in the second space 31B is quickly discharged to the outside of the casing 17 of the speed reducer 16 together with the lubricating oil through the drain pipe 36. Therefore, by providing this drain pipe, it is possible to prevent the lubricating oil enclosed in the casing 17 from being deteriorated by the influence of moisture.

(Second Embodiment)
4 and 5 show a vertical shaft pump 1 according to a second embodiment of the present invention. In the present embodiment, the structure of the suspension tube 9 is different from the first embodiment. Specifically, the base plate 9 c is provided integrally with the upper flange 9 a of the suspension pipe 9. The suspension pipe 9 itself is inserted through the through hole 4 a of the installation floor 4 and extends toward the bottom of the water tank 3.

  Further, in the present embodiment, a power transmission mechanism that transmits the rotation input from the prime mover to the input shaft 26 to the output shaft 21 is different from the first embodiment. In the present embodiment, the power transmission mechanism includes three pairs of bevel gears 41A to 41F and two intermediate shafts 42A and 42B. First, a bevel gear 41 </ b> A is fixed to one end of the input shaft 26. The bevel gear 41B meshing with the bevel gear 41A is fixed to the upper end of the first intermediate shaft 42A extending in the vertical direction. 42 A of 1st intermediate shafts are accommodated in the 3rd part 20 of the casing 17, and are rotatably supported by the two ball bearings 23H and 23I. A bevel gear 41C is fixed to the lower end of the first intermediate shaft 42A. A bevel gear 41D meshing with the bevel gear 41C is fixed to one end of a second intermediate shaft 42B extending in the horizontal direction. One end of the second intermediate shaft 42 </ b> B is disposed in the third portion 20, but the other end passes through the second portion 19 and is disposed in the first portion 18. The second intermediate shaft 42B is rotatably supported by ball bearings 23J and 23K in the second portion 19. A bevel gear 41E fixed to the other end of the second intermediate shaft 42B meshes with a bevel gear 41F fixed to the upper end of the output shaft 21. The rotation from the prime mover input to the input shaft 26 includes a bevel gear 41A, a bevel gear 41B, a first intermediate shaft 42A, a bevel gear 41C, a bevel gear 41D, a second intermediate shaft 42B, a bevel gear 41E, and a bevel gear. It is transmitted to the output shaft 21 via 41F. During this time, the rotation speed is reduced and the direction of the rotation axis is changed from the horizontal direction to the vertical direction.

  In addition, the gate valve 37 (see FIG. 1) of the drain pipe 36 and the automatic adjustment device 33B are not provided, and one end of the pressure introduction pipe 34 of the automatic pressure adjustment device 33A is the upper side of the first portion 18 of the casing 17. Except for the point connected to the through hole of the hemispherical shell-shaped portion 18a, the other configurations and operations of the second embodiment are the same as those of the first embodiment. Therefore, the same elements are denoted by the same reference numerals and description thereof is omitted.

  The present invention is not limited to the above-described embodiment, and various modifications are possible. For example, a mechanism for analyzing the components of the lubricating oil sealed in the first space 31A of the casing 17 of the speed reducer 16 at any time or at regular time intervals is provided, thereby monitoring the presence or absence of wear or failure of various bearings. May be.

1 is a longitudinal sectional view showing a vertical shaft pump according to a first embodiment of the present invention. Sectional drawing in the II-II line of FIG. The elements on larger scale of FIG. The longitudinal cross-sectional view which shows the vertical shaft pump concerning 2nd Embodiment of this invention. The elements on larger scale of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vertical shaft pump 2 Pump casing 3 Water tank 4 Installation floor 4a Through-hole 6 Pumping pipe 7 Vane casing 8 Bell mouth 8a Suction port 9 Suspension tube 9a, 9b Flange 9c Base plate 9d, 9e Bolt hole 10 Discharge elbow 10a Discharge port 11 Main shaft 12A , 12B Underwater bearing 13 Impeller 14 Coupling 16 Reduction gear 17 Casing 18 1st part 18a Cylindrical part 18b, 18c Hemispherical shell-like part 18d, 18e Through-hole 19 2nd part 20 3rd part 21 Output shaft 22 Hollow shaft 23A to 23K Ball bearing 24A to 24C Shaft seal device 26 Input shaft 27A, 27B Spur gears 28, 42A, 42B Intermediate shaft 29A, 29B, 41A-41F Bevel gear 31A First space 31B Second space 33A, 33B Automatic pressure regulator 34 Pressure introduction pipe 3 5 Bellows 36 Drain pipe 37 Gate valve 50, 51 Channel cross-sectional area

Claims (3)

A pumping pipe that extends in the vertical direction and has a suction port disposed at the lower end, a main shaft that extends in the vertical direction within the pumping pipe and that has an impeller fixed at the lower end, and is disposed at the upper end of the pumping pipe. In a vertical pump with a discharge elbow,
A straight pipe hanging pipe fixed to the installation floor, connected to the discharge elbow at the upper end side, and connected to the upper end side of the pumping pipe at the lower end side;
A first part built in the suspension pipe and a pipe wall penetrating the suspension pipe, having one end connected to the first part and the other end disposed outside the suspension pipe. A casing having a second portion and a third portion disposed outside the suspension pipe and connected to the other end of the second portion;
An output shaft extending in a vertical direction, having an upper end side disposed in the first portion, a lower end side being located outside the casing and connected to the upper end of the main shaft;
An input shaft extending in the horizontal direction, having one end disposed in the third portion and the other end positioned outside the casing and connected to the prime mover side;
A vertical shaft pump comprising: a speed reducer that is disposed in the casing and includes a power transmission mechanism that transmits rotation input to the input shaft from the prime mover side to the output shaft. Lubricating oil is sealed in at least a part of the space in the casing of the reduction gear,
The space is deformed according to a differential pressure between the pressure of the lubricating oil in the space and the static pressure of the flow path in the suspension pipe, and the pressure of the lubricating oil becomes equal to the static pressure in the flow path. The vertical shaft pump according to claim 1, further comprising an automatic pressure adjusting device that changes a volume of the vertical shaft.   The vertical shaft pump according to claim 2, further comprising a drain pipe having one end communicating with the bottom side of the first portion of the casing and the other end opened to the atmosphere.

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