JP6259289B2 - Horizontal shaft pump - Google Patents

Description

  The present invention relates to a horizontal shaft pump for transferring river water or the like, and more particularly to a bearing.

  Conventionally, horizontal shaft pumps for transferring liquids such as river water have been known. Among horizontal pumps, there are external bearings (rolling bearings) installed in the atmosphere (outside of the pump casing), pump flow There are horizontal shaft diagonal flow pumps and axial flow pumps that support a rotating body (impeller) with an underwater bearing provided in a passage (inside a pump casing). Although the present invention is limited to these horizontal shaft diagonal flow pumps and axial flow pumps, in the following description, for the sake of simplicity, they are simply referred to as “horizontal shaft pumps”. The impeller accommodated in the pump casing is located above the suction water level, sucks up the liquid in the suction water tank from the suction pipe hanging from the pump casing, and transfers the liquid. The pump casing is installed on the pump mount, and the suction pipe suspended from the pump casing extends into the suction water tank through a through portion provided in the pump mount.

  The impeller is fixed to a rotating shaft that extends horizontally in the pump casing. The rotary shaft is rotatably supported by an outer bearing (rolling bearing) provided in the atmosphere (outside the pump casing) and a submerged bearing provided in the pump flow path (in the pump casing). Since this underwater bearing is in contact with the liquid to be transferred, a sliding bearing is generally employed. The lubrication of the underwater bearing is generally self-lubricated by the liquid to be transferred or by a lubricant (for example, grease) injected from the outside.

  However, in the method of supplying the lubricant from the outside, it is necessary to periodically supply the lubricant. In addition, the fact that the lubricant must be replenished regularly by workers has increased running costs. Further, when the lubricant is insufficient, the underwater bearing may be broken.

  Many horizontal pumps used for river drainage have a large capacity of over 1000 mm, and the bearings that support the rotating bodies are custom-made because they require high load performance. long. For this reason, when a submerged bearing broke down, the horizontal axis pump had to be stopped for a long time, and there was a problem that the liquid could not be transferred during that time.

  Patent Document 1 discloses an example in which a ceramic bearing is employed as an underwater bearing by water lubrication. Ceramic bearings with water lubrication do not require the use of lubricating oil such as grease. However, since the ceramic bearing has a single load due to the structure of the horizontal axis pump, there is a concern that a load is applied only to the lower side of the ceramic bearing and the ceramic, which is a brittle material, is broken. In addition, foreign matters such as mud and dust contained in the transferred liquid may enter the bearing, which may damage the ceramic bearing.

  The horizontal axis pump sucks and transfers the liquid, but operates while forming a siphon between the suction pipe including the rotating body and the discharge pipe. The siphon may be destroyed due to small water volume operation, air suction vortex, air suction due to shaft seal leakage, etc., and the liquid in the pump may be discharged. This is called falling water. When the underwater bearing is self-lubricated, the underwater bearing is overheated as a result of idling when the water falls. When the liquid is re-transferred in this state, the underwater bearing is cooled rapidly, and particularly in the case of a ceramic bearing, there is a risk of cracking due to thermal shock (heat shock).

  Patent Document 2 discloses a resin sliding bearing as an underwater bearing by water lubrication. In this underwater bearing, the shaft support surface that supports the rotating shaft is made of resin, and a sleeve made of a cemented carbide material is used for the rotating shaft portion that is supported. Resin bearings are not suitable for long-time operation of liquids containing a large amount of silt because they have a drawback in wear resistance. In addition, the sleeve of resin or cemented carbide constituting the shaft support surface is a special material, and there is a problem that it is expensive and takes time for delivery. In addition, a special structure is required in the gap between the sleeve and the bearing, and there is a problem that the configuration of the underwater bearing is complicated.

  Patent Document 3 discloses a configuration in which an underwater bearing is disposed in a bearing chamber having a liquid-tight structure, and a lubricant is stored in the bearing chamber. With such a configuration, since the underwater bearing in the bearing chamber does not come into contact with the liquid, it is possible to employ a rolling bearing as the underwater bearing. However, the rolling bearing disclosed in Patent Document 3 requires periodic lubricant replenishment, which increases running costs. Further, since the outer surface of the bearing chamber is cooled by the liquid, there is a concern that condensation occurs in the bearing chamber. When the condensed water is mixed into the lubricant, not only the lubrication performance is deteriorated, but also there is a possibility that rust is generated in the bearing chamber and the rolling bearing.

  Rolling bearings that can be used in water are available as off-the-shelf products, but do not have the ability to withstand high loads. For this reason, the present condition is that the underwater rolling bearing which can be used for the horizontal-axis pump used for transfer of river water etc. does not exist.

JP 2007-182769 A JP 2005-127226 A Japanese Patent Laid-Open No. 10-238493

  The present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide a horizontal shaft pump that can use a general-purpose rolling bearing and can prevent the occurrence of condensation in the bearing chamber. .

One aspect of the present invention for solving the above-described problems is a rotating shaft extending in the horizontal direction, an impeller fixed to the rotating shaft, a pump casing in which the impeller is accommodated, and the rotating shaft inserted. A bearing casing disposed in the pump casing, a rolling bearing disposed in the bearing casing and rotatably supporting the rotating shaft, and the rotating shaft and the inserting port. A shaft sealing device for closing a gap between them, a gas introduction pipe for introducing a gas outside the pump casing into the bearing casing, and a gas for discharging the gas inside the bearing casing to the outside of the pump casing Bei a discharge pipe, a ventilator for ventilating the interior of the bearing casing via the gas inlet tube and the gas discharge tube, a stirrer for agitating the gas in the bearing casing , The stirring device is a horizontal axis pump characterized by having a stirring blade rotating together with the rotary shaft.

In a preferred aspect of the present invention, the ventilator is an insufflator connected to the gas introduction pipe.
In a preferred aspect of the present invention, the ventilator is a suction pump connected to the gas exhaust pipe.

A preferred aspect of the present invention is characterized by further comprising a drain pipe for discharging the liquid accumulated in the bearing casing.
In a preferred aspect of the present invention, a liquid level detection sensor provided in the bearing casing is further provided.
In a preferred aspect of the present invention, the apparatus further includes an insertion tube for introducing the photographing apparatus into the bearing casing.

A preferred aspect of the present invention is characterized by further comprising a measuring element for monitoring a bearing state for measuring vibration or temperature of the rolling bearing.
In a preferred aspect of the present invention, the bearing casing includes a removable lid disposed on a side opposite to the shaft seal device.
In a preferred aspect of the present invention, a jack for lifting the rotating shaft is disposed in the bearing casing.

  According to the present invention, since the rolling bearing is arranged in a liquid-tightly sealed bearing casing, the rolling bearing does not contact the liquid flowing in the pump casing. Therefore, a general-purpose rolling bearing such as a grease sealed type can be used. As a result, it is not necessary to regularly supply a lubricant such as grease, and the running cost can be reduced. In addition, even if the siphon is destroyed due to small water volume operation due to changes in operating conditions, air suction vortex, air suction due to shaft seal leakage due to aging of equipment, etc. Because it is operated in, there is no risk of damage. In this connection, by adopting a rolling bearing that can be operated in the air, it is possible to perform “air standby operation” in which the operation starts before the water level reaches the operation start water level. It is possible to prevent accidents. Further, the rolling bearing used is not a custom-made product but a general-purpose product that is generally available on the market. Therefore, when a rolling bearing breaks down, it can be immediately replaced with a new rolling bearing, thereby improving the reliability of the horizontal shaft pump. Furthermore, according to the present invention, gas is introduced into the bearing casing through the gas introduction pipe, and the gas in the bearing casing is exhausted through the gas discharge pipe. Therefore, since the gas in the bearing casing is constantly ventilated, it is possible to prevent dew condensation from occurring in the bearing casing even when the outer surface of the bearing casing is cooled with liquid during operation of the horizontal shaft pump. Therefore, it is possible to maintain good lubrication of the rolling bearing and to prevent the occurrence of rust.

It is a schematic sectional drawing which shows the whole structure of the horizontal shaft pump which concerns on one Embodiment of this invention. It is the expanded sectional view which expanded the bearing part of FIG. It is a schematic sectional drawing which shows a part of horizontal shaft pump which concerns on another embodiment of this invention. It is the schematic sectional drawing which showed embodiment with which the stirring apparatus was provided in the bearing casing. Fig.5 (a) is a side view which shows an example of a stirring apparatus, FIG.5 (b) is a top view which shows an example of a stirring apparatus. FIG. 6A is a side view showing another example of the stirring device, and FIG. 6B is a plan view showing another example of the stirring device. It is a schematic sectional drawing which shows the structure of the horizontal shaft pump which concerns on another embodiment of this invention. It is a schematic sectional drawing which shows the structure of the horizontal shaft pump which concerns on another embodiment of this invention. It is a schematic sectional drawing which shows the structure of the horizontal axis | shaft pump which showed the modification of embodiment shown in FIG. It is a schematic sectional drawing which shows the structure of the horizontal shaft pump which concerns on another embodiment of this invention. It is a schematic sectional drawing of the structure which made it possible to lift the rotating shaft between a rolling bearing and a shaft seal apparatus with a jack. It is the conceptual diagram which showed a mode that the position of a rolling bearing was rotated.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic cross-sectional view showing an overall configuration of a horizontal shaft pump (specifically, a mixed flow pump) according to an embodiment of the present invention. FIG. 2 is an enlarged cross-sectional view illustrating an enlarged bearing portion of the horizontal shaft pump illustrated in FIG. 1. As shown in FIG. 1, the horizontal shaft pump has a rotating shaft 5 connected to a prime mover 30 such as an electric motor, a diesel engine, or a gas turbine via a speed reducer 31. The drive shaft 35 of the prime mover 30 is coupled to the first reduction shaft 32 of the speed reducer 31 via a coupling 36. The drive gear 33 fixed to the first reduction shaft 32 is engaged with the driven gear 34. The driven gear 34 is fixed to a second reduction shaft 38, and the second reduction shaft 38 is connected to the rotary shaft 5 via a coupling 37. With such a configuration, the power from the prime mover 30 is transmitted to the rotating shaft 5 at a predetermined reduction ratio, and the rotating shaft 5 can be rotated at a desired rotation speed.

  The impeller 6 is fixed to a rotating shaft 5 that extends in the horizontal direction, and the impeller 6 rotates as the rotating shaft 5 rotates. The horizontal axis pump has an impeller casing 2 in which the impeller 6 is accommodated, and a suction bent pipe 3 connected to the impeller casing 2. A pump casing 1 is formed by the impeller casing 2 and the suction bent pipe 3. A suction pipe 4 is connected to the lower side of the suction bent pipe 3, and the tip of the suction pipe 4 is submerged in a liquid in a suction water tank (not shown).

  Operation of the horizontal axis pump is performed as follows. First, the pump casing 1 is evacuated by a vacuum pump (not shown), and the liquid in the suction water tank is sucked up by the vacuum pressure until the pump casing 1 is filled with the liquid. The rotary shaft 5 and the impeller 6 are rotated by the prime mover 30 while the pump casing 1 is filled with liquid. As the impeller 6 rotates, the liquid is sucked up through the suction pipe 4 and transferred to the outside through the suction bent pipe 3 and the impeller casing 2.

  The rotating shaft 5 extends outside the pump casing 1 through the suction bend tube 3. Further, the rotating shaft 5 is rotatably supported by an external bearing 7 disposed outside the pump casing 1 and an internal bearing 8 disposed in the pump casing 1. As shown in FIG. 2, a rolling bearing is used as the internal bearing 8 and is accommodated in a bearing casing 10 disposed in the pump casing 1. The bearing casing 10 is supported by a plurality of guide vanes 9 fixed to the inner surface of the impeller casing 2.

  The rotating shaft 5 extends into the bearing casing 10 through an insertion port 10 a provided in the bearing casing 10. The rolling bearing used for the internal bearing 8 is fixed to a bearing stand 11 installed on the inner surface of the bearing casing 10. A shaft seal device 12 that closes the gap between the insertion port 10 a and the rotary shaft 5 is disposed in the bearing casing 10. The shaft sealing device 12 allows the rotation of the rotating shaft 5 while sealing the inner space of the bearing casing 10 in a liquid-tight manner. That is, the shaft seal device 12 prevents the liquid flowing in the pump casing 1 from entering the bearing casing 10.

  Since the internal space of the bearing casing 10 is isolated from the internal space of the pump casing 1 by the shaft seal device 12, the rolling bearing as the internal bearing 8 disposed in the bearing casing 10 is a liquid flowing in the pump casing 1. Never touch. Therefore, a general-purpose rolling bearing such as a grease sealed type can be used as the rolling bearing. As a result, it is not necessary to constantly supply a lubricant such as grease, and the running cost can be reduced. Moreover, the rolling bearing used is not a custom-made product but a general-purpose rolling bearing that is generally available on the market. Therefore, when a rolling bearing fails, it can be immediately replaced with a new rolling bearing, so that the reliability of the horizontal shaft pump is improved. In addition, since a rolling bearing can be used, the life of the bearing can be greatly extended as compared with a conventional sliding bearing (for example, a ceramic bearing or a resin bearing).

  The bearing casing 10 includes a gas introduction pipe 14 for introducing gas into the bearing casing 10 from the outside of the pump casing 1, and a gas discharge pipe 15 for discharging the gas inside the bearing casing 10 to the outside of the pump casing 1. And are provided. The gas introduction pipe 14 and the gas discharge pipe 15 extend outward from the bearing casing 10, penetrate the impeller casing 2, and extend to the outside of the pump casing 1.

  As shown in FIG. 1, the gas introduction pipe 14 is connected to an insufflator (for example, a fan or a compressor) 29 that compresses and feeds gas (usually air). A dehumidifier (for example, a dry air generator, an adsorption method (passes through silica gel, etc.) that dehumidifies and drys the gas by applying heat to the gas is provided in the air supply tube 22 extending from the air supply 29 to the gas introduction tube 14. A compressor system, a membrane dryer system, etc.) 20 and a flow meter (for example, a mass flow sensor) 21 for measuring a gas flow rate are arranged. Instead of the flow meter, a pressure sensor that can measure the pressure of the gas may be provided. Alternatively, the flow meter and the pressure sensor may be arranged in series with the air supply pipe 22. In this specification, a flow meter and a pressure sensor are generically called a gas sensor. By disposing the gas sensor 21, it is possible to monitor the flow rate of the gas introduced into the bearing casing 10 and the gas leakage in the air supply pipe 22.

  The drive shaft 39 of the air supply device 29 is connected to the drive gear 33 of the speed reducer 31, and the rotational force of the drive gear 33 is used as power for the air supply device 29. Although different from the illustrated example, the air supply device 29 may be connected to an external power source or the like and driven by electric power supplied from the outside.

  In the present embodiment, the air supply device 29 is operated, and the dried gas is sent into the bearing casing 10 through the gas introduction pipe 14 and discharged through the gas discharge pipe 15. In this case, since the pressurized gas is sent into the bearing casing 10, it is preferable to provide a safety valve (relief valve) 23 in the gas conduction path. In the illustrated example, a safety valve 23 is arranged in a branch pipe branched from a discharge pipe 24 connected to the gas discharge pipe 15. Note that the exhaust pipe 17 is provided with an exhaust valve 17, and the exhaust pipe 17 is opened and closed so that the exhaust pipe 24 communicates with the outside and the communication is cut off.

  Along with the rotation of the rotary shaft 5 and the impeller 6, the dried gas is introduced into the bearing casing 10 through the gas introduction pipe 14 to fill the internal space of the bearing casing 10, and further exhausted from the bearing casing 10 through the gas discharge pipe 15. Is done. As described above, since the inside of the bearing casing 10 is always filled with the dry gas, even if the outer surface of the bearing casing 10 is cooled with a liquid during the operation of the horizontal shaft pump, it is prevented that condensation occurs in the bearing casing 10. The Further measures against condensation can be taken by arranging a heat insulating material having a high heat insulating effect such as glass wool, foamed polyethylene or phenol foam on the inner surface of the bearing casing 10.

  However, there is a possibility that condensation will occur in the bearing casing 10 when the horizontal axis pump is operated particularly when the temperature of the liquid is low, such as in winter. As a countermeasure against the occurrence of condensation, the bearing casing 10 is provided with a drain pipe 16 provided with a drain valve 18. The drain pipe 16 is preferably disposed at the lowest position of the bearing casing 10 so that the condensed water flows toward the drain pipe 16.

  In the illustrated example, the gas introduction pipe 14 is connected to the upper part of the bearing casing 10, and the gas discharge pipe 15 is connected to the lower part of the bearing casing 10. With such an arrangement, a downward gas flow is formed in the bearing casing 10, and the condensed water generated in the bearing casing 10 is easily discharged from the drain pipe 16.

  A water repellent coating may be applied to the inner surface of the bearing casing 10 so that water condensed on the inner surface of the bearing casing 10 can easily flow into the drain pipe 16. An electric valve may be adopted as the drain valve 18 so that the drain valve 18 is periodically opened.

Further, a “space heater” may be installed in the bearing casing 10 as a countermeasure against condensation during suspension such as a non-water discharge period. A dehumidifying agent such as silica gel may be installed instead of this heater. In this case, the dehumidifying agent can be attached and exchanged using a gas inlet pipe 14 or a vent pipe such as the gas outlet pipe 15.
Further, as an operation method when the pump drainage operation is stopped, a timer may be set after breaking the vacuum to supply dehumidified dry air for a certain period to prevent the occurrence of dew condensation after the operation.

  FIG. 3 is a schematic cross-sectional view showing a configuration of a horizontal axis pump according to another embodiment of the present invention. Since the configuration and operation of the present embodiment that are not particularly described are the same as those of the embodiment shown in FIG. 1 described above, redundant description thereof is omitted. In the embodiment shown in FIG. 3, a pulley 40 is attached to the rotary shaft 5, and a pulley 41 is connected to the drive shaft 39 of the air supply device 29. When the pulley 40 is rotated together with the rotating shaft 5, the pulley 41 is rotated via the belt 42. Thus, in this embodiment, the rotational force of the rotating shaft 5 is used as the power of the air feeder 29. Although not shown in the embodiment shown in FIG. 3, as in the embodiment shown in FIG. 1, a dehumidifier, a gas sensor, and an air supply pipe 22 extending from the air supply machine 29 to the gas introduction pipe 14 are provided. Can be arranged.

  Although not shown, a pulley 40 is attached to the drive shaft 35 of the prime mover 30, the first reduction shaft 32 of the reduction gear 31, or the second reduction shaft 38 of the reduction gear 31, and the pulley 40 and the air supply device 29 are attached. The belt 42 may be stretched over a pulley 41 connected to the drive shaft 39 so that the power of the air feeder 29 can be obtained as described above.

  In the embodiment described above, the air supply device 29 is connected to the gas introduction pipe 14, and the compressed gas from the air supply device 29 is introduced into the bearing casing 10. Although not shown, in another embodiment, a suction pump may be connected to the gas discharge pipe 15, and the gas in the bearing casing 10 may be discharged to the outside by the suction pump. In this case, the gas introduction pipe 14 communicates with the external space, and the external air is introduced into the bearing casing 10 through the gas introduction pipe 14 as an introduction gas.

  As described above, the ventilator that ventilates the internal space of the bearing casing 10 through the gas introduction pipe 14 and the gas discharge pipe 15 may be an air supply device 29 that introduces compressed air into the bearing casing 10 through the gas introduction pipe 14. Alternatively, a suction pump that exhausts gas from the bearing casing 10 via the gas discharge pipe 15 may be used.

  As shown in FIG. 4, a stirring device 45 for stirring the gas in the bearing casing 10 may be fixed to the rotating shaft 5. FIG. 4 is a schematic cross-sectional view showing an embodiment in which the stirring device 45 is provided in the bearing casing 10. As shown in FIG. 4, the stirring device 45 is disposed between the shaft seal device 12 and the rolling bearing used for the internal bearing 8 and has a plurality of stirring blades 46. The stirrer 45 is provided in order to effectively prevent condensation in the bearing casing 10 by generating an air flow by stirring the gas in the bearing casing 10. Since the configuration and operation of the present embodiment that are not particularly described are the same as those of the embodiment shown in FIG. 1 described above, redundant description thereof is omitted.

  FIG. 5A to FIG. 6B are diagrams showing an example of the stirring device 45. Specifically, FIG. 5A is a side view showing an example of the stirring device 45, and FIG. 5B is a plan view showing an example of the stirring device 45. FIG. 6A is a side view of another example of the stirring device 45, and FIG. 6B is a plan view of another example of the stirring device 45.

  In the example shown in FIG. 5A and FIG. 5B, a disk-shaped blade holding member 48 having a through hole 47 into which the rotating shaft 5 is fitted is used as a center. A plurality of stirring blades 46 (eight in the illustrated example) are fixed. The stirring blade 46 is attached to the blade holding member 48 in an inclined manner. In the example shown in FIG. 6A and FIG. 6B, a disk-like blade holding base 49 having a through hole 47 into which the rotating shaft 5 is inserted is used, and a plurality of sheets are perpendicular to the blade holding base 49. (In the example shown, eight sheets) of stirring blades 46 are erected. The stirring blade 46 is held by the blade holder 49 over the entire length in the longitudinal direction.

  The stirring device 45 rotates together with the rotating shaft 5 and forms an air flow in the bearing casing 10. As a result, condensation in the bearing casing 10 is effectively prevented. Therefore, corrosion of the rolling bearing, which is a main part of the horizontal shaft pump, is prevented, and the reliability of the horizontal shaft pump is improved. Further, the gas introduced through the gas introduction pipe 14 does not stagnate in the bearing casing 10, and the gas in the bearing casing 10 is uniformly discharged from the gas discharge pipe 15. The blade holding member 48 of the stirrer 45 has a function of draining water, so that even if water leaks from the shaft seal device 12, the bearing is not directly affected.

  FIG. 7 is a schematic cross-sectional view showing a configuration of a horizontal shaft pump according to still another embodiment of the present invention. Since the configuration and operation of the present embodiment that are not particularly described are the same as those of the embodiment shown in FIG. 1 described above, redundant description thereof is omitted. In the embodiment shown in FIG. 7, a liquid level detection sensor 50 for detecting liquid intrusion into the bearing casing 10 is arranged. The liquid level detection sensor 50 is provided to detect the liquid when the shaft seal device 12 fails and the liquid in the pump casing 1 has entered the bearing casing 10.

  In the embodiment shown in FIG. 7, the drain valve 18 provided in the drain pipe 16 is configured as an electric valve. When the liquid level detection sensor 50 detects a liquid, the liquid level detection sensor 50 transmits a liquid level detection signal to the drain valve 18, and the drain valve 18 receives the liquid level detection signal and opens. This prevents the liquid that has entered the bearing casing 10 from coming into contact with the rolling bearing.

  The liquid level detection sensor 50 may be installed in the drain pipe 16. In this case, the liquid level detection sensor 50 can detect the occurrence of condensation in the bearing casing 10. Also in this case, the drain valve 16 that is an electric valve can be controlled to be automatically opened.

  FIG. 8 is a schematic cross-sectional view showing a configuration of a horizontal shaft pump according to still another embodiment of the present invention. Since the configuration and operation of the present embodiment that are not particularly described are the same as those of the embodiment shown in FIG. 1 described above, redundant description thereof is omitted. As shown in FIG. 8, in the present embodiment, the bearing casing 10 is further provided with an insertion tube 55 for introducing an imaging device 53 for observing the inside of the bearing casing 10 into the bearing casing 10. The insertion pipe 55 extends from the bearing casing 10 to the outside of the pump casing 1.

  The photographing device 53 is preferably an endoscope that can photograph a state in the bearing casing 10 with a color moving image. Furthermore, it is preferable that the photographing device 53 includes a sound collecting microphone and can collect the operation sound of the rolling bearing used for the internal bearing 8 in the bearing casing 10. In this way, by photographing the inside of the bearing casing 10 with the photographing device 53, it is possible to easily observe the state of the rolling bearing. Therefore, it is only necessary to disassemble the bearing casing 10 only when an abnormality is found, and there is no need to disassemble the bearing casing 10 for every inspection.

  FIG. 9 is a schematic cross-sectional view showing the configuration of a horizontal axis pump showing a modification of the embodiment shown in FIG. In the embodiment shown in FIG. 9, a vibration sensor 54 is inserted into an insertion pipe 55 extending from the bearing casing 10 to the outside of the pump casing 1, and the vibration sensor 54 is brought into contact with the rolling bearing used for the internal bearing 8. The vibration can be measured. Since the photographing device 53 (see FIG. 8) for photographing the inside of the bearing casing 10 is used only during the inspection of the rolling bearing, the vibration sensor 54 is inserted from the insertion tube 55 except during the inspection. It is used to measure the amplitude and frequency of vibration of a rolling bearing.

  Conventionally, a vibration sensor is attached to the external bearing 7 to observe the state of the impeller 6 that vibrates due to foreign matters such as dust. However, since the external bearing 7 is separated from the impeller 6, The minute vibration of the car 6 could not be detected. In the present embodiment, the vibration sensor 54 is installed on the rolling bearing close to the impeller 6 so that the vibration of the rolling bearing can be measured. Therefore, an abnormality occurring in the impeller 6 can be immediately detected, and the reliability of the horizontal shaft pump can be determined. Can be improved.

  Although not shown, the temperature sensor can be inserted from the insertion tube 55 in place of the vibration sensor 54 or in combination with the vibration sensor 54. The temperature sensor is attached to the rolling bearing and measures the temperature of the rolling bearing. As described above, providing a temperature sensor for measuring the temperature of the rolling bearing is useful for diagnosing the abnormality of the rolling bearing. The vibration sensor 54 and the temperature sensor are used as measurement elements for monitoring the bearing state of the rolling bearing.

  FIG. 10 is a schematic cross-sectional view showing a configuration of a horizontal shaft pump according to still another embodiment of the present invention. Since the configuration and operation of the present embodiment that are not particularly described are the same as those of the embodiment shown in FIG. 1 described above, redundant description thereof is omitted. In the present embodiment, the bearing casing 10 includes a detachable lid 61 disposed on the side opposite to the shaft seal device 12.

  As shown in FIG. 10, the bearing casing 10 is provided with an inspection flange 60 so that the lid 61 can be removed. The inspection flange 60 includes a main body side flange 60 a of the bearing casing 10 and a separation side flange 60 b of the lid 61.

  With such a configuration, an operator can touch the rolling bearing used for the internal bearing 8 simply by disassembling the inspection flange 60 and removing the lid 61, and the pump can be used to replace the rolling bearing. There is no need to disassemble the casing 1. As a result, it is possible to reduce the work time and cost required to replace the rolling bearing. In particular, in a large-diameter horizontal shaft pump with an inner diameter of the pump casing 1 of 1500 mm or more, an operator can enter the pump casing 1, so that the rolling bearing can be easily replaced.

  When the inspection flange 60 is provided, as shown in FIG. 11, it is preferable to arrange a jack 63 for lifting the rotary shaft 5 at a position between the rolling bearing used for the internal bearing 8 and the shaft seal device 12. Thus, by lifting the rotating shaft 5 with the jack 63, the load applied to the rolling bearing can be reduced. For this reason, it becomes possible to take out the rolling bearing easily, and the labor of the operator who replaces the rolling bearing can be reduced.

  Moreover, by making it possible to lift the rotating shaft 5 between the rolling bearing and the shaft seal device 12 with the jack 63, the rolling bearing can be easily rotated. Since the rolling bearing of the horizontal shaft pump supports the rotating shaft 5 extending horizontally, the radial load of the rotating shaft 5 is concentrated on the lowermost end portion of the rolling bearing. That is, since the rolling bearing has a single load, a load is applied only to the lowermost end portion of the rolling bearing, and deterioration of the lowermost end portion easily proceeds. In order to prevent such local deterioration of the rolling bearing, it is preferable to periodically rotate the entire rolling bearing at the time of periodic inspection. The rolling bearing can be easily rotated by lifting the rotating shaft 5 with the jack 63.

  FIG. 12 is a conceptual diagram showing how the position of the rolling bearing used for the internal bearing 8 is rotated. As shown on the left side of FIG. 12, the radial load of the rotating shaft 5 is concentrated on the rolling element 70 at the lowermost end portion indicated by hatching among the plurality of rolling elements 70 of the rolling bearing. Therefore, as shown on the right side of FIG. 12, the entire rolling bearing is rotated (90 ° counterclockwise in FIG. 12) during periodic inspections, and the position of the rolling element 70 where the radial load is concentrated is changed. . By periodically rotating the entire rolling bearing in this way, it becomes possible to extend the life of the rolling bearing. The rolling element 70 can be a spherical ball or a cylindrical roller.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible.

DESCRIPTION OF SYMBOLS 1 Pump casing 2 Impeller casing 3 Suction curved pipe 5 Rotating shaft 6 Impeller 7 External bearing 8 Internal bearing 9 Guide vane 10 Bearing casing 10a Insertion port 11 Bearing stand 12 Shaft seal device 14 Gas introduction pipe 15 Gas discharge pipe 16 Drain pipe 17 Exhaust valve 18 Drain valve 20 Dehumidifier 21 Gas sensor (flow meter and / or pressure sensor)
22 Air Supply Pipe 23 Safety Valve 24 Discharge Piping 29 Air Supply Machine (Ventilation Device)
30 prime mover 31 reduction gear 32 first reduction shaft 33 drive gear 34 driven gear 35 drive shaft 36 coupling 37 coupling 38 second reduction shaft 39 drive shaft 40 pulley 41 pulley 42 belt 45 stirring device 46 stirring blade 47 through hole 48 Blade holding member 49 Blade holding base 50 Liquid level detection sensor 53 Imaging device 54 Vibration sensor 55 Insertion pipe 60 Inspection flange 60a Body side flange 60b Separation side flange 61 Lid 63 Jack 70 Rolling element

Claims (9)

A rotating shaft extending in the horizontal direction;
An impeller fixed to the rotating shaft;
A pump casing in which the impeller is accommodated;
A bearing casing having an insertion port into which the rotating shaft is inserted, and disposed in the pump casing;
A rolling bearing disposed in the bearing casing and rotatably supporting the rotating shaft;
A shaft sealing device for closing a gap between the rotating shaft and the insertion port;
A gas introduction pipe for introducing gas outside the pump casing into the bearing casing;
A gas discharge pipe for discharging the gas in the bearing casing to the outside of the pump casing;
A ventilator for ventilating the interior of the bearing casing via the gas inlet pipe and the gas outlet pipe;
A stirring device for stirring the gas in the bearing casing;
The horizontal shaft pump , wherein the stirring device has a stirring blade that rotates together with the rotating shaft.   The horizontal axis pump according to claim 1, wherein the ventilation device is an air supply device connected to the gas introduction pipe.   The horizontal axis pump according to claim 1, wherein the ventilation device is a suction pump connected to the gas discharge pipe. The horizontal shaft pump according to any one of claims 1 to 3 , further comprising a drain pipe for discharging the liquid accumulated in the bearing casing. The horizontal axis pump according to any one of claims 1 to 4 , further comprising a liquid level detection sensor provided in the bearing casing. The horizontal shaft pump according to any one of claims 1 to 5 , further comprising an insertion pipe for introducing a photographing device into the bearing casing. The horizontal shaft pump according to any one of claims 1 to 6 , further comprising a bearing state monitoring measuring element for measuring vibration or temperature of the rolling bearing. The horizontal shaft pump according to any one of claims 1 to 7 , wherein the bearing casing includes a removable lid disposed on a side opposite to the shaft seal device. The horizontal shaft pump according to claim 8 , wherein a jack for lifting the rotating shaft is disposed in the bearing casing.

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