JP6316624B2 - Bearing device and vertical shaft pump provided with the same - Google Patents

Description

  The present invention relates to a bearing device used for a pump, and more particularly to an external bearing device for a vertical shaft pump and a vertical shaft pump including the same.

Conventionally, vertical shaft pumps have been used, for example, for pumping water in sewers or draining in rivers. When a vertical shaft pump is used in the sewer, a high head and a large flow rate are required. About 30 m may be required as the head. In the case of a large-sized vertical shaft pump, the diameter of a suspension pipe or a discharge curved cylinder reaches 1500 mm (1.5 m) or 2000 mm (2 m). If the suspension pipe has a diameter of 2 m and a lift of 30 m is realized, it is equivalent to a water column with a diameter of 2 m and a height of 30 m, and therefore the volume of the suspension pipe corresponds to 94.2 m ³ . Further, since the mass of the rotating body (impeller, main shaft, etc.) is added, it is suggested that a thrust force of 94 t or more may be applied to the thrust bearing of the pump main shaft.

  The thrust bearing on the pump main shaft of a vertical shaft pump is subjected to the large thrust force described above, so the bearing body is surrounded by a bearing case and immersed in lubricating oil for the purpose of minimizing the frictional resistance and wear of the bearing. ing. When the thrust bearing rotates with a large thrust force applied, a large amount of heat is generated due to friction between the bearing race and the roller (roller), and the lubricating oil is heated. The lubricating oil maintains the lubricating performance (viscosity) up to a predetermined temperature, but when the temperature is exceeded, the lubricating performance is significantly reduced. In order to prevent this, it is necessary to cool the lubricating oil.

  FIG. 16 is a diagram showing an air-cooled bearing device 251 according to the prior art. As illustrated, the bearing body 253 is surrounded by the bearing case 255, and the internal space of the bearing case 255 is filled with the lubricating oil L. A heat radiating fin 263 is installed around the bearing case 255, and a cooling fan 293 for supplying cooling air to the heat radiating fin 263 is mounted on the pump main shaft 213 (see Patent Document 1). Further, in order to enhance the cooling effect, an invention of a bearing device including a second radiating fin and a cooling fan has been proposed (see cited document 2). When the lubricating oil L reaches a high temperature, heat is transferred from the lubricating oil L to the bearing case 255 and then from the bearing case 255 to the heat radiation fin 263. Then, the temperature of the radiating fin 263 rises, but when room temperature air is supplied from the cooling fan 293 to the radiating fin 263, heat exchange is performed between the radiating fin 263 and the air, and the temperature of the lubricating oil L Can be kept constant.

  FIG. 17 is a diagram showing a forced circulation type bearing device 251b according to the prior art. The bearing device 251b is provided with an oil feed pipe 263 for circulating the lubricating oil L immersed in the bearing main body 253, and a circulation pump P and a heat exchanger 267 are connected to the oil feed pipe 263. Circulation pump P is driven by electric motor 264. The heated lubricating oil L is taken out to the outside by the action of the circulation pump P, and heat is released by the heat exchanger 267, and then returned to the bearing case 255.

JP 2003-293777 A JP 2012-207640 A JP 2011-226420 A

  However, the above prior art has the following problems. That is, in the case of the air-cooled bearing device 251, it has not been able to cope with a large-lift vertical pump that generates a large thrust force. This is because, in an air-cooled bearing device having a conventional structure, the cooling capacity is determined by the heat transfer coefficient of the casing that transmits the heat of the lubricating oil, the surface area of the radiating fin that dissipates the heat, and the air volume of the cooling fan. Although the heat transfer coefficient of the casing depends on the material, the heat transfer coefficient cannot be significantly improved because it becomes a general steel material (SS material) or cast iron (FC material) based on strength and price. In addition, the surface area of the radiation fin is structurally limited. The cooling capacity of the cooling fan is limited depending on the rotational speed of the pump main shaft 213. The invention of Patent Document 2 is provided with two sets of cooling fans and heat radiating fins, but this is not sufficient for cooling.

  In the case of the forced circulation type bearing device 251b, it is necessary to install a circulation pump P and an electric motor 264 for circulating the lubricating oil L. Incidentally, in the invention of the forced circulation type bearing device disclosed in Patent Document 3, a centrifugal pump is provided on the pump main shaft, and the bearing body 253 is cooled by the action of the centrifugal pump. For this reason, since there are many components and the structure becomes complicated, the maintenance and repair costs were increased. In particular, in the case of large pumps used for sewers and rivers, there are many cases where the operation of the pumps cannot be stopped because no spare machine is provided. On the other hand, there is a strong demand from the field to eliminate as much as possible auxiliary equipment that is likely to cause failure. In other words, a highly reliable cooling mechanism that does not require an auxiliary machine is desired.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a bearing device that can sufficiently cool a bearing body with a simple structure without requiring a circulation pump or the like. That is.

  The first means is a bearing device for a vertical shaft pump, and includes a bearing main body, a bearing case that surrounds the bearing main body and contains lubricating oil, and a partition wall that partitions the internal space of the bearing case into an upper space and a lower space. And an oil feed pipe that is connected to the upper space and the lower space and circulates the lubricating oil, the bearing body is disposed in either the upper space or the lower space, and the upper space and the lower space are interposed via the bearing body. And are in fluid communication with each other.

  By adopting the configuration as described above, the bearing device operates as follows. That is, when the prime mover connected to the pump main shaft rotates, the impeller attached to the lower end of the pump main shaft rotates. Thereby, water is taken in from the suction bell mouth and discharged upward from the impeller. The discharged water flow is fed further downstream through the suspension pipe and the discharge curved drum. At this time, a large thrust force corresponding to the pressure of the water flow is applied to the bearing body of the bearing device (thrust bearing) that supports the pump main shaft. When the operation of the vertical shaft pump is continued with this large thrust force applied, a large amount of heat is generated in the bearing body. This heat then heats the lubricating oil.

  At this time, along with the rotation of the pump main shaft, the upper race constituting the bearing main body arranged in the upper space also rotates. By rotating the upper race, speed energy in the rotational direction is given to the lubricating oil. Lubricating oil to which velocity energy is applied in the rotation direction is applied with a force radially outward by centrifugal force. For this reason, the flow toward the outer peripheral portion of the bearing case is generated in the lubricating oil in the upper space. Since the oil feeding pipe is connected to the outer peripheral portion of the bearing case, the lubricating oil is fed into the oil feeding pipe. An amount of lubricating oil corresponding to the lubricating oil fed into the oil feeding pipe is supplied from the lower space through the bearing body.

  In addition to the structure of the first means, the second means adopts a structure in which the oil feeding pipe is connected to a heat exchanger provided inside the outlet pipe of the vertical shaft pump.

  The lubricating oil fed into the oil feeding pipe is supplied to the heat exchanger. Since the heat exchanger is in direct contact with the water flow in the discharge curved drum, the heat held by the lubricating oil is efficiently released into the water flow through the heat exchanger. Thereby, the temperature of lubricating oil falls. The lubricating oil whose temperature has been lowered is returned to the lower space of the bearing case through the oil feeding pipe. As described above, the lubricating oil is smoothly supplied from the lower space to the upper space. Thus, the circulation of the lubricating oil is realized only by the rotational motion of the race of the bearing body. For this reason, it is not necessary to provide a separate drive means such as a circulation pump, and it becomes possible to reduce maintenance and running costs with a simple device configuration.

  In addition to the configuration of either the first means or the second means, the third means is arranged on the side of the upper space or the lower space where the bearing main body is disposed by rotating the pump main shaft of the vertical pump with respect to the bearing case. It has a configuration in which a rotating impeller is provided.

  The fourth means has a structure in which a lubricating oil valve is provided in the middle of the oil feed pipe in addition to the structure of the first means to the third means, and this lubricating oil valve opens when the lubricating oil is above a predetermined temperature. .

  In the fifth means, in addition to any one of the first to fourth means, the oil feed pipe is connected to an oil cooler provided outside the bearing case, and a cooling fan for moving the air in the vicinity of the oil cooler Is installed on the pump main shaft of the vertical shaft pump.

  The sixth means adopts a configuration in which, in addition to the configuration of the fifth means, a cooling liquid sprayer for spraying the cooling liquid to the oil cooler is provided.

  The seventh means employs a structure in which the oil cooler is water-cooled and cooled by the water flow of the branch pipe branched from the discharge pipe, in addition to the structure of either the fifth means or the sixth means.

  In the eighth means, in addition to any one of the first to seventh means, the oil feeding pipe is arranged around the bearing case, and the oil feeding pipe is cooled by the water flow of the branch pipe branched from the discharge curved cylinder. The structure is adopted.

  In addition to the configuration of the eighth means, the ninth means further includes a cooling case surrounding the oil feed pipe, and a water flow is supplied into the cooling case.

  The tenth means is a preceding standby type vertical shaft pump, wherein the bearing device having any one of the first to ninth means, the discharge valve provided in the discharge body, and the vertical pump are in the standby state. And a control unit that controls the discharge valve based on information from the standby state detection device, and the control unit closes the discharge valve when the vertical shaft pump is in the standby state. , Is adopted.

  The eleventh means is a method for controlling a stand-by standby type vertical shaft pump including a bearing device having any one of the first to ninth means, and detects whether the vertical shaft pump is in a standby state. When the vertical pump is in a standby state, the discharge valve provided in the discharge pipe is closed.

  The twelfth means is a bearing device for a vertical shaft pump, and includes a bearing body, a bearing case that surrounds the bearing body and contains lubricating oil, and further branches from the discharge body and is lubricated within the bearing case. The structure of having a branch pipe in contact with

The thirteenth means is a bearing device for a vertical shaft pump, and includes a bearing body, a bearing case that surrounds the bearing body and contains lubricating oil, and further branches off from the discharge body and is provided at the outer periphery of the bearing case. The structure of having a branch pipe for supplying the discharge water flow is adopted.

It is a partial cross section figure which shows the vertical shaft pump which concerns on one Embodiment of this invention. It is a figure which shows the bearing apparatus used for the vertical shaft pump disclosed in FIG. 1, FIG. 2 (A) is sectional drawing of the principal part of a bearing apparatus, FIG.2 (B) is sectional drawing of a heat exchanger, FIG. 2C is a front view of the heat exchanger. It is a figure which shows the modification of a heat exchanger, FIG.3 (A) is a thing with a spiral pipe, FIG.3 (B) is a thing with a square spiral, FIG.3 (C) The pipe meanders. It is a figure which shows the bearing apparatus which concerns on the 2nd Embodiment of this invention, FIG. 4 (A) is sectional drawing of the principal part of a bearing apparatus, FIG.2 (B) is sectional drawing which shows the impeller for circulation. is there. It is a figure which shows the bearing apparatus which concerns on the 3rd Embodiment of this invention. It is a figure which shows the bearing apparatus which concerns on the 4th Embodiment of this invention. It is a figure which shows the bearing apparatus which concerns on the 5th Embodiment of this invention. It is sectional drawing of the principal part of the bearing apparatus which concerns on the 6th Embodiment of this invention. It is sectional drawing of the principal part of the bearing apparatus which concerns on the 7th Embodiment of this invention. It is a figure which shows the bearing apparatus which concerns on the 8th Embodiment of this invention. It is a figure which shows the bearing apparatus which concerns on the 9th Embodiment of this invention. It is a figure which shows the bearing apparatus which concerns on the 10th Embodiment of this invention. It is a detailed view of the bearing device 51i disclosed in FIG. It is sectional drawing of the principal part of the bearing apparatus which concerns on the 11th Embodiment of this invention. It is sectional drawing of the principal part which shows the modification of the bearing apparatus disclosed in FIG. It is sectional drawing of the principal part of the bearing apparatus which concerns on a prior art. It is sectional drawing of the principal part of the bearing apparatus which concerns on another prior art.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings. Note that an invention in which individual components described below are arbitrarily combined is also included in the technical concept of the present invention.

[Overview]
FIG. 1 is a diagram illustrating an overall outline of a vertical pump 1 according to the present embodiment, and in particular, is a vertical pump 1 including a bearing device 51 having features of the present embodiment. FIG. 2 is a detailed view showing the bearing device 51 according to the present embodiment. As shown in FIG. 1, the vertical shaft pump 1 includes a flow path including a suction bell mouth 3, a guide blade body 5, a suspension pipe 7, and a discharge curved body 9 in order from below. A pump main shaft 13 connected to the electric motor 11 is disposed at the center of the suspension pipe 7, and an impeller 15 is attached to a lower end portion of the pump main shaft 13. The upper end portion of the pump main shaft 13 is rotatably supported by the bearing device 51. The bearing device 51 is a thrust bearing for receiving a thrust force applied to the pump main shaft 13. The bearing device 51 includes oil supply pipes 63 and 65, and a heat exchanger 67 is connected to the oil supply pipes 63 and 65.

As shown in FIG. 2, the bearing device 51 includes a bearing main body 53, a bearing case 55 that surrounds the bearing main body 53 and stores lubricating oil L, and an internal space of the bearing case 55 that includes an upper space 57 and a lower space 59. Partition wall 61 and oil feed pipes 63 and 65 which are connected to the upper space 57 and the lower space 59 and circulate the lubricating oil L. The bearing body 53 is disposed in either the upper space 57 or the lower space 59, and the upper space 57 and the lower space 59 communicate with the lubricating oil L through the bearing body 53. In the present embodiment, the bearing body 53 is disposed in the upper space 57.

[Bearing body]
The bearing main body 53 used in the bearing device 51 of the present embodiment is a thrust bearing as described above. For this reason, in FIG. 2, a load directed downward in the vertical direction is supported. In the bearing body 53, the lower race 53 b is supported at a predetermined position of a bearing case 55 which is a stationary member, and the upper race 53 a is supported by a rotating member including the pump main shaft 13.

[Bearing case]
The bearing body 53 is surrounded by a bearing case 55. The bearing case 55 forms a donut-shaped internal space around the bearing body 53, and the internal space is filled with the lubricating oil L. The amount of the lubricating oil L in the bearing case 55 is a sufficient amount so that the bearing body 53 is always immersed in the lubricating oil L. For this reason, the bearing main body 53 is always lubricated by the lubricating oil L and is cooled together with it.

[Bulk in the bearing case]
The bearing case 55 is provided with a partition wall 61 that partitions an internal space into an upper space 57 and a lower space 59. The partition wall 61 according to the present embodiment is provided at an intermediate portion in the height direction of the internal space and is generally formed in the horizontal direction. For this reason, the lubricating oil L in the bearing case 55 is separated into the upper space 57 and the lower space 59 by the partition wall 61. However, the partition wall 61 terminates in the middle on the side close to the pump main shaft 13, and in this portion, the upper space 57 and the lower space 59 are in fluid communication, that is, the lubricating oil L passes between the upper space 57 and the lower space 59. You can come and go. The above-described bearing body 53 is installed in the fluid communication portion between the upper space 57 and the lower space 59. In the present embodiment, the bearing body 53 is disposed in the upper space 57 above the partition wall 61. However, the bearing body 53 may be disposed on the lower space 59 side.

  The bearing body 53 includes two races 53a and 53b and a plurality of rollers 53c disposed between the races 53a and 53b. Since a predetermined gap exists between the two rollers 53c adjacent to each other (in the depth direction in the drawing), the lubricating oil L can flow through this gap. That is, the upper space 57 and the lower space 59 communicate with each other via the bearing body 53 disposed in the fluid communication portion.

[Oil feed pipe]
Oil supply pipes 63 and 65 for circulating the lubricating oil L are connected to the upper space 57 and the lower space 59 in the bearing case 55. The oil feeding pipes 63 and 65 have a function of taking out the lubricating oil L in the bearing case 55 to the outside, lowering the temperature of the lubricating oil L by the heat exchanger 67, and then returning it to the bearing case 55. The oil feeding pipes 63 and 65 of the present embodiment extend in the tangential direction from the outer peripheral wall of the bearing case 55. In particular, the oil feeding pipe 63 connected to the upper space 57 is connected in a tangential direction so that the lubricating oil L having a velocity component in the rotational direction and radially outward can easily flow as will be described later. However, it does not have to be strictly in the tangential direction, and it does not matter if it is inclined at a predetermined angle with respect to the tangential direction. On the other hand, the oil feed pipe 65 connected to the lower space 59 does not have to be in the connection direction.

[Heat exchanger]
The oil feeding pipes 63 and 65 are connected to a heat exchanger 67 (see FIG. 1). The heat exchanger 67 is for lowering the temperature of the lubricating oil L by removing heat from the lubricating oil L. For this reason, the heat exchanger 67 functions as a cooling device. In the heat exchanger 67 of the present embodiment, the cooling pipe 69 is formed in a spiral shape, so that the length of the cooling pipe 69 is sufficiently secured. As is apparent from the figure, the oil feed pipe 63 from the upper space 57 is connected to the center of the spiral of the heat exchanger 67, while the oil feed pipe 65 going to the lower space 59 is connected to the outermost periphery of the heat exchanger 67. ing. The connection positions of the oil feeding pipes 63 and 65 may be reversed.

  As shown in FIGS. 1 and 2, the heat exchanger 67 is installed in an inspection port (hand hole) 71 provided in the discharge curved cylinder 9. The inspection port 71 is a hole that can be opened and closed for inspecting the inside of the pump, and is normally provided in the vertical shaft pump 1. The inspection port 71 is a circular hole, and is normally sealed by a circular lid 73 corresponding to the hole. The heat exchanger 67 of this embodiment is fixed to a circular lid 73, and is installed so that the main part of the heat exchanger 67 is located inside the discharge drum 9. For this reason, when the vertical shaft pump 1 is operated, the water flow flowing inside the discharge curved drum 9 directly contacts the heat exchanger 67. Thus, if the heat exchanger 67 is installed in the inspection port 71, it is not necessary to newly install a special structure for installing the heat exchanger 67, which is advantageous from the viewpoint of cost and maintenance.

  Although the heat exchanger 67 of the present embodiment has a flat spiral shape, the present invention is not limited to this. For example, a spiral heat exchanger 67a as shown in FIG. 3 (see FIG. 3A), a square spiral heat exchanger 67b (see FIG. 3B), a serpentine heat exchanger 67c (see FIG. 3B). (See FIG. 3C). These are shapes for the purpose of sufficiently securing the length of the cooling pipe, and other shapes may be adopted as long as this purpose can be achieved.

[Action]
Next, the operation of the bearing device 51 of the present embodiment configured as described above will be described. When the prime mover 11 connected to the pump main shaft 13 rotates, the impeller 15 attached to the lower end of the pump main shaft 13 rotates. Thereby, water is sucked from the suction bell mouth 3 and discharged upward from the impeller 15. The discharged water flow is supplied to a discharge pipe (not shown) further downstream through the suspension pipe 7 and the discharge curved drum 9. At this time, a large thrust force due to the pressure of the water flow is applied to the bearing body 53 of the bearing device 51 (thrust bearing) that supports the pump main shaft 13. When the operation of the vertical shaft pump 1 is continued with a large thrust force applied, a large amount of heat is generated in the bearing body 53. This heat heats the lubricating oil L.

  When the pump main shaft 13 rotates, the upper race 53a of the bearing body 53 disposed in the upper space 57 also rotates. When the upper race 53a rotates, speed energy in the rotational direction is given to the lubricating oil L from the race 53a. In the lubricating oil L to which velocity energy is given in the rotational direction, a velocity component outward in the radial direction is also generated by centrifugal force. For this reason, a flow toward the outer peripheral portion of the bearing case 55 is generated in the lubricating oil L in the upper space 57. Since the oil feed pipe 63 is connected to the outer peripheral portion of the bearing case 55, the lubricating oil L is fed into the oil feed pipe 63. An amount of the lubricating oil L corresponding to the lubricating oil L fed into the oil feeding pipe 63 is supplied from the lower space 59 through the bearing body 53.

  The lubricating oil L fed into the oil feeding pipe 63 is supplied to the heat exchanger 67. Since the heat exchanger 67 is in direct contact with the water flow in the discharge curved drum 9, the heat of the lubricating oil L is efficiently released into the water flow through the heat exchanger 67. Thereby, the temperature of the lubricating oil L falls. The lubricating oil L whose temperature has decreased is returned to the lower space 59 of the bearing case 55 through the oil feeding pipe 65. Since no rotating member is installed in the lower space 59, the flow of the lubricating oil L does not occur. Further, as described above, since the lubricating oil L is replenished from the lower space 59 to the upper space 57, the lubricating oil L is smoothly returned from the oil feed pipe 65 to the lower space 59. In this way, the lubricating oil L is circulated only by the rotational movement of the race 53a of the bearing body 53. For this reason, it is not necessary to provide new drive means such as a circulation pump, and it is possible to reduce maintenance and running costs with a simple device configuration.

[Second Embodiment]
Next, a bearing device 51b according to the second embodiment will be described with reference to FIG. Since the main configuration is the same as that of the above-described embodiment, different parts will be mainly described. A feature of this embodiment is that a circulation impeller 75 is provided in the bearing case 55. The circulation impeller 75 is attached to a rotating member that rotates together with the pump main shaft 13, and thus rotates at the same rotational speed as the pump main shaft 13. The circulation impeller 75 is configured to rotate along a horizontal plane in the upper space 57. As shown in FIG. 4B, the blades of the circulation impeller 75 are convexly curved in the rotation direction, and a total of eight blades are provided. However, the number of blades is not particularly limited, and may be two, four, or more than eight, and the shape of the blade may be a simple planar shape.

  By the rotation of the circulation impeller 75, the lubricating oil L is given speed energy in the rotational direction and radially outward. This is much larger energy than the speed energy generated by the rotation of the race 53a on the upper side of the bearing body 53. For this reason, the pressure of the lubricating oil L in the vicinity of the inlet of the oil feeding pipe 63 can be increased, and a large amount of the lubricating oil L can be fed into the oil feeding pipe 63. Further, since the circulating impeller 75 rotates, the lubricating oil L in the upper space 57 is also strongly stirred, so that the efficiency of heat exchange between the bearing body 53 and the lubricating oil L can be improved.

[Third Embodiment]
Next, a bearing device 51c according to a third embodiment will be described with reference to FIG. In the embodiment, the inspection port 71 and the heat exchanger 67 are installed in the discharge pipe 77. More specifically, the heat exchanger 67 is provided on the downstream side of the discharge valve 79 or the check valve 81. That is, a discharge valve 79 and a check valve 81 that are opened and closed by the electric motor M are provided on the downstream side of the discharge curved cylinder 9. The downstream side of the discharge valve 79 and the check valve 81 is often called a discharge valve secondary side. Since the discharge valve secondary side has the discharge valve 79 and the check valve 81, even if the operation of the vertical shaft pump 1c is stopped, the water can be stored in the discharge pipe 77 without dropping. is there.

  By installing the heat exchanger 67 in the inspection port 71 on the discharge valve secondary side, the heat exchanger 67 can always come into contact with water in the discharge pipe 77. For this reason, the vertical shaft pump 1c is a pump that performs a preliminary standby operation, and water on the secondary side of the discharge valve even in a dry operation without water on the upstream side of the discharge valve 79 or an air-lock operation at the time of pumping off. With the heat exchanger 67, the lubricating oil L can be reliably cooled.

[Fourth Embodiment]
Next, a bearing device 51d according to a fourth embodiment will be described with reference to FIG. This embodiment is characterized in that the heat exchanger 67 is provided on the upper portion of the discharge short tube 83 on the downstream side of the discharge curved cylinder 9. The discharge short pipe 83 is a discharge pipe arranged in the vicinity of the bearing device 51c. Further, the length of the oil feeding pipes 63 and 65 is shortened by providing an inspection port and a heat exchanger 67 on the upper part of the discharge short pipe 83. be able to. The heat exchanger 67 is cooled by a water flow flowing inside the discharge short pipe 83, and can cool the lubricating oil efficiently. By doing in this way, the design of the heat exchanger 67 can be afforded, and the heat exchanger 67 having a large cooling capacity can be used. Note that an existing inspection port may be used as the upper inspection port of the discharge short tube 83 or a new one may be provided.

[Fifth Embodiment]
Next, a bearing device 51e according to a fifth embodiment will be described with reference to FIG. The present embodiment is characterized in that a lubricating oil valve 85 is provided in the middle of the oil feeding pipe 63. The lubricating oil valve 85 is configured to open when the lubricating oil is above a predetermined temperature. The temperature of the lubricating oil is detected by a temperature sensor 87 installed in the bearing case 55. The detected temperature of the lubricating oil is transmitted to the control device 89, and the control device 89 opens and closes the electric lubricating oil valve 85. The reason for switching the circulation / stop of the lubricating oil according to the temperature of the lubricating oil is as follows. That is, when the temperature of the lubricating oil is low, such as when the outside air temperature is low, the viscosity of the lubricating oil is high. When the lubricating oil is fed to the heat exchanger 67 in a state where the viscosity of the lubricating oil is high, the lubricating oil is hardly heated to an appropriate temperature. When the temperature of the lubricating oil is too low, there is a possibility that the lubricating performance for the bearing main body 53 may be lowered. Therefore, in order to avoid this, the lubricating oil valve 85 is opened and closed according to the temperature of the lubricating oil.

[Sixth Embodiment]
Next, a bearing device 51f according to a sixth embodiment will be described based on FIG. The present embodiment is characterized in that the oil feeding pipes 63 and 65 are connected to an oil cooler 91 provided outside the bearing case 55. Another feature is that a fan 93 for causing the air in the vicinity of the oil cooler 91 to flow is attached to the pump main shaft 13. The oil cooler 91 has meandering pipes like a radiator of an automobile, and a large number of heat radiating ribs are attached to the meandering pipes. The oil cooler 91 of this embodiment has a donut shape that surrounds the outer peripheral surface of the bearing case 55.

  A coolant sprayer 95 for spraying coolant onto the oil cooler 91 is provided in the vicinity of the oil cooler 91. The coolant sprayer 95 is for spraying water on the oil cooler 91 in the form of a mist. The coolant uses a part of the flowing water pressurized by the vertical pump. By doing so, the oil cooler 91 can be efficiently cooled without providing a special water supply mechanism. If the oil cooler 91 can be efficiently cooled, the lubricating oil L flowing inside the oil cooler 91 can also be efficiently cooled. In addition, you may make it use the water of a normal water supply other than using the flowing water pressurized with the vertical shaft pump as a cooling fluid. By making the oil cooler 91 a cooling water spray type, even a small oil cooler can release a large amount of heat.

  The fan 93 of this embodiment does not blow air to the oil cooler 91. The fan 93 is disposed above the oil cooler 91 and has a function of sucking low-temperature air from below. For this reason, the bearing case 55 and the oil cooler 91 are covered with the cooling housing 96, and low-temperature air is taken in from below the cooling housing 96, and the air that has cooled the oil cooler 91 is formed above the cooling housing 96. The air is discharged to the outside through the air hole 97. For this reason, heat exchange is efficiently performed by the oil cooler 91 and air. Of course, even a structure in which air is blown from above to the oil cooler 91 by the fan 93 can be cooled to a certain level or more, and such a configuration is also within the range assumed in the present embodiment.

  The oil cooler 91 is not limited to the cooling water spray type as described above, and may be a water cooling type as shown in FIG. This water-cooled oil cooler 91f performs heat exchange by bringing a cooling pipe 99 through which water having a temperature lower than that of the lubricating oil L flows into contact with the oil cooler 91f. As the low-temperature water, it is preferable to use, for example, a water flow pressurized by a vertical shaft pump or water from a water supply. When using a water flow pressurized by a vertical pump, it is preferable to use water from a branch pipe branched from the discharge pipe. The water-cooled oil cooler 91f has a higher cooling capacity than that of the air-cooled type, and assuming the same cooling capacity, the water-cooled oil cooler 91f can be significantly smaller and lighter than the air-cooled type. For this reason, it is possible to apply to a vertical pump having a high lift that cannot be sufficiently cooled by the air cooling method.

[Seventh Embodiment]
Next, a seventh embodiment will be described based on FIG. The embodiment is characterized in that the oil feeding pipes 63 and 65 are arranged on the outer peripheral portion of the bearing case 55, and the oil feeding pipes 63 and 65 are cooled by the water flow of the branch pipe 101 branched from the discharge curved drum. is there. Specifically, the oil feeding pipes 63 and 65 are wound along the outer peripheral portion of the bearing case 55. The number of windings may be one round, or multiple rounds may be wound in order to enhance the cooling effect. The bearing case 55 around which the oil feeding pipes 63 and 65 are wound is surrounded by the cooling case 103.

  Inside the cooling case 103, pressurized water is supplied through the branch pipe 101 branched from the discharge curved drum 9. According to this embodiment, the length of the oil feeding pipes 63 and 65 can be shortened, and the flow path resistance of the oil feeding pipes 63 and 65 can be kept small. For this reason, even if the centrifugal force generated in the lubricating oil is small only by the rotation of the race of the bearing body 53, the lubricating oil can be reliably circulated through the oil feeding pipes 63 and 65 to be cooled. Further, it is desirable that the direction in which the lubricating oil flows in the oil feeding pipes 63 and 65 and the direction in which the water supplied to the cooling case 103 flows are so-called counterflows. This is because the efficiency of heat exchange is higher than when the lubricating oil and the cooling water flow in the same direction. Further, the water introduced into the cooling case 55 is structured to return to the suction water tank 105, and there is no need to provide a special drainage mechanism.

  The branch pipe 101 may be an air vent pipe used when starting the pump. This is because the air vent pipe is not used when the vertical shaft pump 1g is normally operated, and a pressurized water flow can be taken out. By using the air vent pipe together as the branch pipe 101, it is not necessary to provide a special branch pipe, and the equipment can be simplified. The branch pipe 101 is connected to the upstream side of the discharge valve 79. In the case of the vertical pump 1g that performs the preliminary standby operation, the discharge valve 79 is closed during the standby operation, and if water or air is taken in by the impeller 15, the air staying in the vertical pump during the standby operation. This is because the cooling case 103 is supplied via the branch pipe 101. During the standby operation, the vertical pump 1g is not pumping water, so the load is light. For this reason, a large thrust force is not applied to the bearing body 53, and no large heat is generated. Therefore, the bearing main body 53 can be sufficiently cooled not only by water cooling during normal operation but also by air cooling using the transfer pipe 101 as in the present embodiment.

[Eighth Embodiment]
Next, an eighth embodiment will be described based on FIG. This embodiment is characterized in that the branch pipe 101 is connected to the downstream side of the discharge valve 79 or the check valve 81. By connecting the branch pipe 101 to the downstream side of the discharge valve 79 or the check part 81, the bearing case 55 can be efficiently cooled even during standby operation. This is because pressurized water stays on the downstream side (discharge valve secondary side) of the discharge valve 79 or the check valve 81 even during standby operation due to the action of these valves. For this reason, pressurized water flows into the branch pipe 101, and this water can be supplied to the outer peripheral portion of the bearing case 55. Oil feed pipes 63 and 65 are provided on the outer periphery of the bearing case 55, and the oil feed pipes 63 and 65 are cooled by the supplied low-temperature water. In other words, in the bearing device 51h of the present embodiment, the lubricating oil can be cooled by water cooling regardless of whether it is in standby operation or normal operation. In order to detect the standby operation state, the vertical shaft pump may be provided with a water level sensor that detects the water level of the water absorption tank, a load sensor that detects the load of the vertical shaft pump, and the like as a standby state detection device. By these sensors, the standby operation state can be reliably detected, and appropriate cooling can be performed according to the operation state.

In addition, this embodiment is characterized in that an electric water flow valve 107 is provided in the branch pipe 101, and the water flow valve 107 is opened when the lubricating oil is at a predetermined temperature or higher. As described above, when the temperature of the lubricating oil is too low, the lubricating performance may be low. For this reason, the water flow valve 107 is opened for the first time when the lubricating oil temperature exceeds a predetermined value, and low-temperature water is supplied to the outer peripheral portion of the bearing case 55. With this configuration, when the temperature of the lubricating oil is low, the lubricating oil is not cooled, so that the temperature of the lubricating oil appropriately increases with the operation of the vertical shaft pump.

  On the other hand, when the temperature of the lubricating oil exceeds a predetermined value, the water flow valve 107 is opened. Thereby, the pressurized water is supplied from the discharge pipe 77 through the branch pipe 101 to the outer peripheral part of the bearing case 55, and the oil feeding pipes 63 and 65 arranged on the outer peripheral part of the bearing case 55 can be cooled. . If the oil feeding pipes 63 and 65 are cooled, the lubricating oil flowing through the inside is also cooled.

[Ninth Embodiment]
Next, a ninth embodiment will be described based on FIG. The embodiment is a bearing device 51i for a vertical shaft pump, and includes a bearing body 53, a bearing case 55 that surrounds the bearing body 53 and accommodates lubricating oil, and further branches from the discharge drum 9. A branch pipe 101 in contact with the outer periphery of the bearing case 55 is provided. That is, the bearing device 51i according to this embodiment is different from the above embodiments in that it does not include an oil feeding pipe. As can be seen from FIG. 12, the branch pipe 101 takes in water flows from two places of the discharge curved cylinder 9 and is in contact with the outer peripheral surface of the bearing case 55. For this reason, if the temperature of the branch pipe 101 is lower than the temperature of the bearing case 55, heat exchange is performed between the branch pipe 101 and the bearing case 55. According to this embodiment, it is not necessary to install an oil feeding pipe, and the apparatus configuration can be simplified. FIG. 13 shows details of the bearing device 51i. As shown in FIG. 13, instead of providing an oil feeding pipe, an extraction pipe 66 communicates with an upper space 57 and a lower space 59, and the surface of the extraction pipe 66 comes into contact with the water flow, so that the lubricating oil L Is supposed to be cooled.

  Next, a tenth embodiment will be described with reference to FIG. The embodiment is a bearing device 51j for a vertical shaft pump, and includes a bearing body 53, a bearing case 55j that surrounds the bearing body 53 and accommodates the lubricating oil L, and further, a discharge curved body (not shown). And a branch pipe 101j that contacts the lubricating oil L inside the bearing case 55j. That is, as in the ninth embodiment, the point that the oil feeding pipe is not provided is different from the main embodiment described above.

  Specifically, the branch pipe 101j is inserted into the bearing case 55j. Since low-temperature water flows in the branch pipe 101j, heat can be efficiently taken from the high-temperature lubricating oil L in the bearing case 55j. In particular, a circulating flow is generated in the lubricating oil L in the bearing case 55j due to the rotation of the upper race 53a of the bearing body 53. When the branch pipe 101j comes into contact with this circulating flow, the lubricating oil L can be maintained in a predetermined temperature range. FIG. 15 shows a configuration in which a partition wall 61 is further added to partition the internal space of the bearing case 55j in the vertical direction.

  The present invention can be used for an external bearing device of a vertical shaft pump.

DESCRIPTION OF SYMBOLS 1 Vertical shaft pump 3 Suction bell mouth 5 Guide vane cylinder 7 Suspension pipe 9 Discharge curved cylinder 11 Electric motor 13 Pump main shaft 15 Impellers 51, 51b, 51c, 51d, 51e, 51f, 51g, 51h, 51i, 51j Bearing device 53 Bearing Main body 53a Upper race 53b Lower race 53c Roller (roller)
55 Bearing case 57 Upper space 59 Lower space 61 Bulkhead 63, 65 Oil supply pipe 67, 67a, 67b, 67c Heat exchanger 69 Cooling pipe 71 Detection port (hand hole)
73 Circular cover 75 Circulating impeller 77 Discharge pipe 79 Discharge valve 81 Check valve 83 Discharge short pipe 85 Lubricating oil valve 87 Temperature sensor 89 Control device 91, 91f Oil cooler 93 Cooling fan 95 Coolant spray machine 96 Cooling housing 97 Air hole 99 Cooling pipe 101 Branch pipe 103 Cooling case 105 Suction water tank 107 Water flow valve

Claims (11)

A bearing device for a vertical shaft pump,
A bearing body, a bearing case that surrounds the bearing body and contains lubricating oil, a partition wall that partitions the internal space of the bearing case into an upper space and a lower space, and the lubricating oil connected to the upper space and the lower space An oil feeding pipe for circulating
The bearing body is disposed in either the upper space or the lower space, and the upper space and the lower space are in fluid communication with each other through the bearing body ,
The said oil feeding pipe connected to the side by which the said bearing main body is arrange | positioned among the said upper space or the lower space is extended toward the tangential direction from the outer peripheral wall of the said bearing case . The apparatus according to claim 1, wherein the oil feeding pipe is connected to a heat exchanger provided inside an outlet pipe of the vertical shaft pump.   The apparatus according to claim 1, wherein an impeller that rotates relative to the bearing case by rotation of a pump main shaft of a vertical pump is provided on a side of the upper space or the lower space where the bearing main body is disposed. .   The apparatus according to any one of claims 1 to 3, wherein a lubricating oil valve is provided in the middle of the oil feeding pipe, and the lubricating oil valve opens when the lubricating oil is at a predetermined temperature or higher.   The oil supply pipe is connected to an oil cooler provided outside the bearing case, and a fan for moving air in the vicinity of the oil cooler is mounted on a pump main shaft of a vertical shaft pump. A device according to claim 1.   The apparatus according to claim 5, comprising a coolant sprayer for spraying coolant on the oil cooler. The apparatus according to claim 5 or 6, wherein the oil cooler is water-cooled and is cooled by a water flow in a branch pipe branched from a discharge pipe.   The apparatus according to any one of claims 1 to 7, wherein the oil feeding pipe is arranged around the bearing case, and the oil feeding pipe is cooled by a water flow of a branch pipe branched from a discharge curved drum.   The apparatus according to claim 8, further comprising a cooling case surrounding the oil feeding pipe, wherein the water flow is supplied into the cooling case. A prior standby type vertical shaft pump, wherein the bearing device according to any one of claims 1 to 9, a discharge valve provided in a discharge pipe, and whether the vertical pump is in a standby state are detected. A standby state detection device, and a control unit that controls the discharge valve based on information from the standby state detection device,
The control unit is a vertical pump that closes the discharge valve when the vertical pump is in a standby state. A control method of a stand-by type vertical shaft pump comprising the bearing device according to any one of claims 1 to 9,
A control method for a vertical pump, which detects whether or not the vertical pump is in a standby state, and closes a discharge valve provided in a discharge body when the vertical pump is in a standby state.