JP2012207550A - Oil lifter device for lubricating sliding surface in shaft sealing device in oil chamber of submerged pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil lifter device for lubricating a sliding surface in a shaft sealing device in an oil chamber of a submerged pump, solving problems produced by opalization of lubrication oil including air bubbles.SOLUTION: The outside of a double type shaft sealing device 32 vertically located in an oil chamber 24 is surrounded by an annular cylinder 39, the inside of the annular cylinder 39 is constituted with three chambers of a suction chamber 40 provided with a suction port 43 of the lower end side, a discharge chamber 41 provided with a discharge port 44 of the upper end side and an acceleration chamber 42 being a middle portion located between the suction chamber 40 and the discharge chamber 41, the suction chamber 40 and the discharge chamber 41 are set to have a larger diameter than that of the acceleration chamber 42, a groove part 45 for guiding the lubrication oil (a) to the discharge chamber 41 is disposed on the inner circumferential surface of the acceleration chamber 42 along the swirling direction in the upgrade arrangement and widths of the suction port 43 and the discharge port 44 are set to be equal to or less than the width of the groove part 45.

Description

  The present invention relates to an oil lifter device for supplying lubricating oil to a sliding surface in an oil chamber shaft seal device of a submersible pump for lubrication.

  As shown in FIG. 4, a mechanical seal is used as the double-type shaft seal device 2 of the submersible pump 1, and such a mechanical seal needs to lubricate the sliding surface. As the supply means, an oil bath type in which an oil chamber 5 is provided between the pump chamber 3 and the motor chamber 4 and the lubricating oil a is enclosed in the oil chamber 5 is adopted.

  The amount of lubricating oil sealed in the oil chamber 5 is generally about 80% of the volume of the oil chamber in consideration of the expansion rate due to heat generation, and an air reservoir is formed in the upper portion of the oil chamber 5.

  The lubricating oil a enclosed in the oil chamber 5 is also supplied to the upper shaft sealing device 2a on the motor side located at the upper part by rising by the centrifugal force generated by the rotation of the rotating member of the double type shaft sealing device 2. However, it is consumed by lubricating the sliding surface of the double type shaft seal device 2, and therefore the oil level decreases in proportion to the operating time of the submersible pump 1, and the upper shaft seal on the motor side is reduced. When the sliding surface of the device 2a can no longer be lubricated, the oil chamber must be replenished with lubricating oil.

  In order to make the above-described lubricating oil replenishment cycle as long as possible, the double shaft seal device 2 is rotated inside the oil chamber 5 interposed between the pump chamber 3 and the motor chamber 4 as shown in FIG. An oil lifter device is provided so that the lubricating oil a in the oil chamber 5 is fed upward, and the lubricating oil limit a2 with respect to the upper shaft seal device 2a is set lower in the oil chamber 5 than in the initial sealed oil surface a1. It can be set.

  4 and 5 show a first example of an oil lifter device for a sliding surface in a conventional double shaft seal device, in which a stirring blade 6 is attached to a rotating member of the lower shaft seal device 2b, and stirring is performed by starting a motor. The lubricating oil a in the oil chamber 5 is scraped up by the rotation of the blades 6, and the lubricating oil a is supplied to the sliding surface of the upper shaft seal device 2a.

  FIGS. 6A to 6C show a second example of the oil lifter device for the sliding surface in the conventional double shaft seal device, and shows the double shaft seal device 2 provided above and below in the oil chamber 5. An outer side is surrounded by an annular cylinder 7 whose inner diameter is straight up and down, and a suction port 8 through which the lubricating oil a in the oil chamber 5 flows into the annular cylinder 7 is provided at the lower portion of the annular cylinder 7. The upper end of the body 7 is used as a discharge port 9 for discharging the lubricating oil a in the annular cylinder 7 to the outside. Further, the double-type shaft sealing device 2 extends from the inner peripheral surface to the inner peripheral surface of the annular cylinder 7. The guide vane 10 projecting toward the center of the double-type shaft seal device 2 is provided in an upwardly inclined arrangement in the rotation direction of the rotating member, and the lubricating oil a turning by the rotation of the rotating member is raised by the guide vane 10. The lubricating oil a is supplied to the sliding surface of the upper shaft seal device 2a. That (for example, see Patent Documents 1 to 3).

  The specific structure of the oil lifter device of the second example is as follows. The annular cylinder 7 is formed in a straight cylindrical shape up and down, its lower end is fixed to the pump-side housing 11, and the suction port 8 is formed around the lower end. The upper end of the annular cylinder 7 is an opening, and the discharge port 9 is formed by providing a gap between the upper end surface of the annular cylinder 7 and the peripheral wall of the upper mating ring 12.

  When the rotary member in the double shaft seal device 2 rotates to rotate the lubricating oil a in the annular cylinder 7, the lubricating oil a is raised from the suction port 8 by raising the rotating lubricating oil a by the guide vane 10. The suctioned and raised lubricating oil a flows out from the opening at the upper end to the discharge port 9, and the rising lubricating oil a lubricates the sliding surface of the upper shaft seal device 2a.

JP 2001-207995 A JP 2001-208214 A Japanese Patent Laid-Open No. 2001-227652

  By the way, the oil lifter device of the first example is a system in which the lubricating oil is scooped up by the stirring blade rotating together with the rotating member of the shaft seal device, and the scrubbed lubricating oil scatters outward due to the centrifugal force due to the rotation. As the oil level is lowered, the amount and height of the lubricating oil scraped are reduced, so that there is a problem that the lubricating oil cannot be efficiently supplied to the upper shaft seal device.

  Further, in the oil lifter device of the second example, the annular cylindrical body 7 is formed in a vertical cylindrical shape up and down, and the raised lubricating oil a flows out from the upper discharge port 9 while turning as it is, When the discharge port 9 is open to the entire periphery, and the guide vane 10 is positioned on the inner periphery of the annular cylinder 7, the portion where the lubricating oil a comes out is the discharge port as shown in FIG. Is not uniform in the circumferential direction, and a portion for sucking air in the oil chamber 5 is generated at a position downstream of the swirling flow of the portion where the lubricating oil a comes out, so that air is caught in the upper portion of the raised lubricating oil a. As a result, the lubricating oil a around the upper shaft seal device 2a changes to cloudy oil containing bubbles.

  When the operation is further continued, the entire lubricating oil a in the oil chamber 5 is changed to white turbid oil containing bubbles, and this white turbid oil contains bubbles, so the lubricity and cooling properties are deteriorated. In addition to hindering the lubrication and cooling of the sliding surface 2, it also inhibits the cooling of the lubricating oil by the external liquid (pumped liquid), so that the vigorous cycle is repeated for the sliding surface as the oil temperature increases. .

  Further, the structure in which the guide vanes 10 project from the inner peripheral surface of the annular cylindrical body 7 inevitably increases the spatial distance between the inner peripheral surface of the annular cylindrical body 7 and the rotating member of the double-type shaft seal device 2. The generation of the swirling flow of the lubricating oil a by the rotating member of the shaft seal device 2 is weak, and the reverse flow of the lubricating oil a may occur from the discharge port 9 to the suction port 8, and therefore the lubricating oil a along the guide vane 10 There is also a problem that it is difficult to sufficiently supply the lubricating oil a toward the upper shaft seal device 2a.

  Therefore, in order to solve the above-described problems, the object of the present invention is to eliminate the occurrence of air entrainment at the discharge port portion and to solve all the problems caused by white turbidity including bubbles of lubricating oil. Another object of the present invention is to provide an oil lifter device that lubricates a sliding surface in an oil chamber shaft seal device of a submersible pump.

  In order to solve the above-described problems, the present invention provides a double-type shaft sealing member above and below an oil chamber interposed between a pump chamber and a motor chamber, and the outside of the double-type shaft sealing member is formed into an annular cylindrical body. The inside of the annular cylinder is composed of three chambers, the lower end side is a suction chamber, the upper end side is a discharge chamber, and the middle part is an acceleration chamber having a swirling lubricating oil lifter function. An oil chamber shaft seal device for a submersible pump provided with a suction port for allowing indoor lubricating oil to flow into the annular cylinder, and provided with a discharge port for discharging the lubricating oil in the annular cylinder to the outside in the discharge chamber In the oil lifter device that lubricates the sliding surface, the inner diameter of the suction chamber and the inner diameter of the discharge chamber are made larger than the inner diameter of the acceleration chamber.

  The lift function of the swirl lubricating oil provided in the intermediate part is formed by a groove part recessed in the inner peripheral surface of the annular cylindrical body in an ascending arrangement along the rotation direction of the rotary member in the double type shaft seal device, The suction port provided in the suction chamber and the width of the discharge port provided in the discharge chamber may be set to be equal to or less than the width of the groove.

  It is good also as a structure which provided the rib for stopping a swirling flow in the position of the upstream of swirling lubricating oil with respect to a suction inlet in the said suction chamber.

  Further, the upper end of the annular cylinder is fitted to the outer periphery of the housing of the upper mating ring so as to absorb the axial dimension variation of the annular cylinder, and at the same time, the clearance between the upper and lower ends of the annular cylinder and the end face of the housing is eliminated. Can be.

  Here, the double-type shaft seal device comprises an upper shaft seal device and a lower shaft seal device using a mechanical seal, and the annular cylinder surrounding the outside of the double-type shaft seal device is coaxial with the pump shaft. It is provided between the pump-side housing and the motor-side housing that form the oil chamber so that it is arranged, and the intermediate acceleration chamber is rotated in the double shaft seal device by recessing a groove on its inner peripheral surface. The inner diameter is set so that the spatial distance to the member becomes as small as possible, and the swirling flow of the lubricating oil generated by the rotation of the rotating member in the double shaft seal device is strengthened.

  According to this invention, since the inner diameters of the suction chamber and the discharge chamber provided above and below the annular cylinder are made larger than the inner diameter of the acceleration chamber, the swirling flow of the lubricating oil is made as weak as possible in the suction chamber and is sucked from the suction port. The lubricating oil is prevented from returning to the original through a part of the suction port, and the air in the oil chamber is also prevented from flowing in the discharge chamber by weakening the swirling flow of the acceleration chamber. It is possible to prevent the oil from becoming white turbid due to including bubbles, and to solve the problems caused by the white turbidity including bubbles of the lubricating oil.

  In addition, since the width of the suction port provided in the suction chamber and the width of the discharge port provided in the discharge chamber is set to be equal to or less than the width of the groove, the lubricating oil sucked from the suction port passes through a part of the suction port. It can be reliably prevented from returning to its original state, and the air in the oil chamber can be reliably prevented from entraining at the discharge port, thereby preventing the occurrence of white turbidity due to bubbles in the lubricating oil, and sliding. The lubrication and cooling effect on the surface is improved.

Vertical front view of submersible pump using lubricating oil retaining device according to the present invention (A) is a longitudinal cross-sectional view in which a portion where the lubricating oil retaining device is incorporated is enlarged, and (b) is a longitudinal cross-sectional view in which the portion of the lubricating oil retaining device is further enlarged. (A) is a perspective view showing an annular cylinder of a lubricating oil retaining device, (b) is a plan view of the annular cylinder, (c) is a longitudinal front view of the annular cylinder, and (d) is a longitudinal sectional view of the annular cylinder. (E) is a bottom view showing another example of the wall provided in the suction chamber Longitudinal front view of a submersible pump using a lubricating oil retaining device as a first conventional example Fig. 4 is an enlarged longitudinal sectional view of the portion where the lubricating oil holding device shown in Fig. 4 is incorporated. (A) is a longitudinal sectional view showing a conventional oil lifter device in a submersible pump, (b) is a cross-sectional plan view taken along arrow bb in (a) showing the flow of lubricating oil in the discharge port portion, and (c). Is a perspective view showing an annular cylindrical body used in a conventional oil lifter device

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  As shown in FIG. 1, the submersible pump 21 has an oil chamber 24 interposed between a lower pump chamber 22 and an upper motor chamber 23, which are housed in a pump casing 25, and blades 26 are placed in the pump chamber 22. By rotating, the water sucked from the suction port 27 is pumped toward the discharge port 28 provided in the upper part of the pump casing 25.

  A pump shaft 29 vertically penetrates the oil chamber 24, and in the oil chamber 24, the penetrating portion is watertight in a portion where the pump shaft 29 of the pump-side housing 30 and the motor-side housing 31 forming the oil chamber 24 penetrates. A double type shaft seal device 32 is provided, and lubricating oil a for the sliding surface of the double type shaft seal device 32 is enclosed in the oil chamber 24.

  The double shaft seal device 32 includes an upper shaft seal device 32 a and a lower shaft seal device 32 b using a mechanical seal. The lower shaft seal device 32 b is placed in an annular groove 30 b of an annular wall 30 a formed in the pump-side housing 30. A lower mating ring 33 that is stored in a watertight state and is loosely engaged with the pump shaft 29, and a lower seal ring 34 that is fixed in a watertight manner so as to rotate integrally with the pump shaft 29 and is in sliding contact with the lower mating ring 33. The upper surface of the lower mating ring 33 and the lower surface of the lower seal ring 34 form a lower sliding surface 35 that maintains watertightness. The lower sliding surface 35 is always in the lubricating oil a enclosed in the oil chamber 24. It will be lubricated by immersion.

  The upper shaft sealing device 32 a is housed in an annular groove 31 b of the annular wall 31 a formed in the motor side housing 31 in a watertight state, and is integrated with the pump shaft 29 and an upper mating ring 36 that is loosely engaged with the pump shaft 29. An upper seal ring 37 that is fixed in a watertight manner so as to rotate and is in sliding contact with the upper mating ring 36, and an upper sliding surface 38 that keeps the lower surface of the upper mating ring 36 and the upper surface of the upper seal ring 37 watertight. Become.

  In the double type shaft seal device 32, a spring 39a for constantly pressing the sliding surfaces 35, 38 is provided between the upper shaft seal device 32a and the lower shaft seal device 32b. The ring 34 and the spring 39a serve as a rotating member in the double shaft seal device 32.

  In the oil chamber 24, an oil lifter device A surrounding the outside of the double shaft seal device 32 is incorporated between the pump side housing 30 and the motor side housing 31.

  As shown in FIG. 2, the annular cylinder 39 forming the oil lifter device has a cylindrical shape coaxial with the pump shaft 29, and the inside of the annular cylinder 39 discharges the suction chamber 40 on the lower end side and discharges the upper end side. The chamber 41 is composed of three chambers in which the intermediate portion is an acceleration chamber 42 having a smaller diameter than the suction chamber 40 and the discharge chamber 41, and the lubricating oil a in the oil chamber 24 is annularly formed on the peripheral wall 41 a that forms the suction chamber 40. A suction port 43 through which the cylindrical body 39 flows is provided, and a discharge port 44 for discharging the lubricating oil a in the annular cylindrical body 39 to the outside is provided in the peripheral wall 41 a forming the discharge chamber 41.

  As shown in FIG. 2 (b), the suction chamber 40 of the annular cylinder 39 is formed in a thin circular space in the vertical axis direction with an outer diameter substantially equal to the annular wall 30a provided in the pump side housing 30. The lower end is in contact with the upper surface of the annular wall 30a, and the discharge chamber 41 is formed in a thin circular space in the vertical axis direction with an outer diameter substantially equal to the annular wall 31a provided in the motor-side housing 31, By fitting an annular wall 41 b continuous with the upper end of the peripheral wall 41 a forming the discharge chamber 41 into an annular wall 31 a provided in the motor-side housing 31, it is arranged in a detent shape.

  As described above, when the upper end of the annular cylinder 39 is fitted to the annular wall 31 a provided in the motor-side housing 31, not only the axial dimension variation of the annular cylinder 39 can be absorbed, but also the annular cylinder By eliminating the gap between the upper and lower end surfaces of the body 39 and the end surface of the housing, it is possible to prevent backflow of lubricating oil and air entrainment.

  The discharge chamber 41 of the annular cylindrical body 39 is arranged so that the upper end of the discharge chamber 41 approaches directly below the upper sliding surface 38 of the upper shaft seal device 32a, and the swirling flow of the lubricating oil a flowing into the discharge chamber 41 is generated. The upper sliding surface 38 can be lubricated.

  As shown in FIG. 2B, the acceleration chamber 42 having the cylindrical shape of the annular cylinder 39 is set so that the inner diameter thereof approaches the outer diameter of the upper shaft sealing device and the lower shaft sealing device. A suction chamber 40 provided at the lower end of 42 and a discharge chamber 41 provided at the upper end are respectively formed larger in diameter than the inner diameter of the acceleration chamber 42, and the suction chamber 40 and the discharge chamber 41 have the same inner diameter.

  The annular wall forming the suction chamber 40 is provided with suction ports 43 at two positions sandwiching the shaft center, and the annular wall forming the discharge chamber 41 is disposed at two positions sandwiching the shaft center. A discharge port 44 is provided in the nozzle.

  On the inner peripheral surface of the accelerating chamber 42 in the annular cylinder 39, a groove portion whose upper and lower ends reach the suction chamber 40 and the discharge chamber 41 in order to guide the lubricating oil a flowing into the suction chamber 40 from the suction port 43 to the discharge chamber 41. 45 is provided in an ascending arrangement along the rotational direction of the rotary member in the double shaft seal device 32.

  The accelerating chamber 42 strengthens the swirling flow of the lubricating oil a generated by the rotation of the rotating member by making the inner diameter of the double shaft seal device 32 as small as possible from the rotating member.

  The reason why the inner diameter of the accelerating chamber 42 can be as small as possible with respect to the rotating member in the double shaft seal device 32 is to provide a groove 45 in the cylindrical inner circumferential surface of the accelerating chamber 42. This is because the generation of protrusions from the inner peripheral surface of the acceleration chamber 42 can be eliminated.

  3A to 3E show the shape of the annular cylinder 39 and the relationship between the suction port 43, the discharge port 44, and the groove 45 provided in the annular cylinder 39, and the suction port 43, the discharge port 44, and the groove part. 45 is provided at two positions facing each other across the axis, and the discharge port 44 is slightly displaced rearward with respect to the rotation direction of the rotary member in the double shaft seal device 32 with respect to the upper end of the groove 45, The suction port 43 and the discharge port 44 are provided so as to have a positional relationship that is substantially perpendicular to the plane.

  An annular wall 41b continuous with the upper end of the peripheral wall 41a forming the discharge chamber 41 is provided with a rotation-preventing groove 46, which is fitted to an outer peripheral projection (not shown) of the annular wall 31a provided in the motor side housing 31. By combining, the periphery of the annular cylinder 39 can be obtained.

  Generated by the rotary member of the double-type shaft seal device 32 at the inner circumference of the peripheral wall 40a forming the suction chamber 40, at a position on the near side in the rotational direction of the rotary member in the double-type shaft seal device 32 with respect to the suction port 43 The rib 47 for stopping the swirling flow of the lubricating oil can be provided to improve the suction efficiency of the lubricating oil a from the suction port 43. FIG. 3 (e) shows that the lower end of the groove 45 and the suction port 43 are double type. 3D is provided so that the lower end of the groove 45 and the suction port 43 are separated along the rotational direction of the rotating member in the double-type shaft sealing device 32. The example of arrangement | positioning of the said rib 47 at the time of providing in the position which showed is shown.

  The groove 45 provided so as to be recessed with respect to the inner peripheral surface of the acceleration chamber 42 guides the swirling lubricating oil a upward, and the width of the suction port 43 provided in the suction chamber 40 and The width of the discharge port 44 provided in the discharge chamber 41 is set to be equal to or less than the width along the circumferential direction of the groove 45.

  More specifically, the opening area of the suction port 43 and the discharge port 44 is set to be equal to or less than the cross-sectional area in the width direction of the groove 45, and the lubricating oil a equivalent to the amount pushed up by the groove 45 is obtained. The lubricating oil a sucked from the suction port 43 is prevented from flowing back from the suction port 43 and returning to the oil chamber 24, and the lubricating oil equivalent to the pushed-up amount is provided at the discharge port 44. By flowing out a, it is prevented from flowing backward into the discharge chamber 41.

  The oil lifter device A for lubricating the sliding surface in the oil chamber shaft seal device of the submersible pump according to the present invention has the above-described configuration, and as shown in FIG. The lubricating oil a is sealed up to the height of the surface a1, and the lower shaft sealing device 32b is immersed in the lubricating oil a inside the annular cylindrical body 39, and the lower half portion of the upper shaft sealing device 32a is also the lubricating oil a. Soaked in.

  When pumping up the submersible pump 21, the upper and lower shaft sealing devices 32 a and 32 b rotate with the pump shaft 29 together with the lower seal ring 34, the upper seal ring 37, and the spring 39 a, and swivel to the lubricating oil a in the annular cylinder 39. A flow is given.

  The lubricating oil a that has turned into the swirling flow in the annular cylinder 39 is pressed against the inner peripheral surface of the annular cylinder 39 by the action of centrifugal force, and rises along the rotation direction of the rotating member on the inner peripheral surface of the acceleration chamber 42. The groove 45 provided in the gradient arrangement raises the lubricating oil a.

  For this reason, the lubricating oil a in the oil chamber 24 flows into the suction chamber 40 from the suction port 43, rises in the acceleration chamber 42 along the groove 45, reaches the discharge chamber 41, and then is discharged from the discharge port 44. The lubricating oil a that reaches the discharge chamber 41 is lubricated by immersing the upper sliding surface 38 of the upper shaft seal device 32a.

  In the acceleration chamber 42, the gap between the inner peripheral surface and the lower seal ring 34, which is a rotating member of the double-type shaft sealing device 32, the upper seal ring 37, and the spring 39a is set as narrow as possible. The swirling flow of the lubricating oil a generated by the above can be made stronger, and the lubricating oil a can be reliably raised from the suction chamber 40 to the discharge chamber 41 by the groove 45.

  By making the suction chamber 40 larger in diameter than the acceleration chamber 42 in a plane, the swirling flow of the lubricating oil a flowing into the suction chamber 40 from the suction port 43 is made as weak as possible, and the suction chamber 40 is sucked into the suction chamber 40. The lubricating oil a is prevented from returning through a part of the suction port 43.

  Further, by providing the rib 47 at a position upstream of the swirl flow in the suction chamber 40 near the suction port 43, the swirl flow of the lubricating oil a is caused at the suction port 43 on the inner peripheral side of the suction chamber 40. By stopping, the lubricating oil a can be reliably introduced from the suction port 43, and the swirling flow into the groove 45 is more reliably performed.

  Furthermore, by making the discharge chamber 41 larger than the inner diameter of the acceleration chamber 42, the flow velocity of the swirling flow in the discharge chamber 41 is weakened, and at the same time, the opening width of the discharge port 44 is made equal to or smaller than the width of the groove 45. Thus, when the lubricating oil a is discharged, the air in the oil chamber 24 is prevented from being entrained, and the lubricating oil a is prevented from becoming clouded by containing bubbles, so that the upper shaft seal device 32a slides upward. The effect of lubricating and cooling the surface 38 can be enhanced.

  The annular cylinder 39 forms a groove 45 by recessing the cylindrical inner peripheral surface of the acceleration chamber 42, and the groove 45 is arranged in an upward gradient along the rotation direction of the rotating member in the double shaft seal device 32. Therefore, the gap between the inner peripheral surface of the acceleration chamber 42 and the rotary member of the double shaft seal device 32 can be set as narrow as possible, and a strong swirling flow of the lubricating oil a is generated in the acceleration chamber 42. Therefore, the lubrication limit oil surface a2 in the oil chamber 24 is lowered to the height position of the suction port 43 as shown in FIG. Thus, the lubricating oil replenishment cycle in the oil chamber 24 can be lengthened.

  Further, by setting the gap between the inner peripheral surface of the acceleration chamber 42 and the rotating member as narrow as possible, the backflow of the lubricating oil a from the discharge chamber 41 to the suction chamber 40 can be prevented.

Here, Table 1 shows the results of measuring the temperature rise of the sliding surface using the submersible pump incorporating the conventional oil lifter device shown in Patent Document 1 and the submersible pump incorporating the oil lifter device A of the present invention. Show.

  From the above measurement results, it was confirmed that the sliding surface temperature of the submersible pump incorporating the oil lifter device of the present invention was 5.6K lower than that of the submersible pump incorporating the conventional oil lifter device.

  In the oil lifter device A of the present invention, since no air is entrained in the discharge chamber 41, the entire oil chamber 24 including the discharge chamber 41 does not show the white turbidity of the lubricating oil due to the inclusion of air. This proved to be an effective means for enhancing the cooling and lubrication effect of the upper sliding surface of the mechanical seal.

  In a submersible pump incorporating a conventional oil lifter device, it was confirmed that the state of the cloudiness of the lubricating oil extends not only to the discharge chamber of the annular cylinder but also to the entire oil chamber.

A Oil lifter device 21 Submersible pump 22 Pump chamber 23 Motor chamber 24 Oil chamber 25 Pump casing 26 Blade 27 Suction port 28 Discharge port 29 Pump shaft 30 Pump side housing 30a Ring wall 30b Ring groove 31 Motor side housing 31a Ring wall 31b Ring groove 32 Double type shaft seal device 32a Upper shaft seal device 32b Lower shaft seal device 33 Lower mating ring 34 Lower seal ring 35 Lower sliding surface 36 Upper mating ring 37 Upper seal ring 38 Upper sliding surface 39 Annular cylindrical body 39a Spring 40 suction chamber 41 discharge chamber 41a peripheral wall 41b annular wall 42 acceleration chamber 43 suction port 44 discharge port 45 groove 46 groove 47 for preventing rotation rib a lubricating oil

As shown in FIG. 2, the annular cylinder 39 forming the oil lifter device has a cylindrical shape coaxial with the pump shaft 29, and the inside of the annular cylinder 39 discharges the suction chamber 40 on the lower end side and discharges the upper end side. chamber 41, than the suction chamber 40 and discharge chamber 41 and an intermediate portion is constituted by three chambers was accelerated chamber 42 of small diameter, annular lubricant a in the oil chamber 24 to the peripheral wall 40a forming the suction chamber 40 A suction port 43 through which the cylindrical body 39 flows is provided, and a discharge port 44 for discharging the lubricating oil a in the annular cylindrical body 39 to the outside is provided in the peripheral wall 41 a forming the discharge chamber 41.

As shown in FIG. 2B, the peripheral wall 40a forming the suction chamber 40 of the annular cylinder 39 has an outer diameter substantially equal to the annular wall 30a provided in the pump-side housing 30, and the inside is thin in the vertical axis direction. Formed in a circular space, the lower end is in contact with the upper surface of the annular wall 30a, and the peripheral wall 41a forming the discharge chamber 41 has an outer diameter substantially equal to the annular wall 31a provided in the motor side housing 31 and a vertical axis By forming an annular wall 41b formed in a thin circular space in the direction and connected to the upper end of the peripheral wall 41a forming the discharge chamber 41 to the annular wall 31a provided in the motor side housing 31, Arranged in a shape.

As described above, when the annular wall 41b coupled to the upper end of the annular cylinder 39 is fitted to the annular wall 31a provided in the motor-side housing 31, the degree of fitting is changed to change the axis of the annular cylinder 39. Dimensional variation in the direction can be absorbed , thereby eliminating the gap between the upper and lower end surfaces of the annular cylinder 39 and the end surfaces of the pump-side housing 30 and the motor-side housing 31, thereby preventing backflow of lubricating oil and air entrainment. Can be prevented.

Claims (4)

A double-type shaft sealing member is provided above and below an oil chamber interposed between the pump chamber and the motor chamber, and the outside of the double-type shaft sealing member is surrounded by an annular cylinder, and the inside of the annular cylinder has a lower end side. The suction chamber is composed of three chambers, the upper end of which is a discharge chamber and the middle portion is an acceleration chamber having a swivel lubricant lifter function. The suction chamber allows the lubricant in the oil chamber to flow into the annular cylinder. In the oil lifter device that lubricates the sliding surface in the oil chamber shaft seal device of the submersible pump provided with a discharge port and provided with a discharge port for discharging the lubricating oil in the annular cylinder to the outside in the discharge chamber,
An oil lifter device for lubricating a sliding surface in an oil chamber shaft seal device of a submersible pump, wherein the inner diameter of the suction chamber and the inner diameter of the discharge chamber are made larger than the inner diameter of the acceleration chamber.   The lift function of the swirl lubricating oil provided in the intermediate part is formed by a groove part recessed in the inner peripheral surface of the annular cylindrical body in an ascending arrangement along the rotation direction of the rotary member in the double type shaft seal device, 2. The shaft seal in the oil chamber of the submersible pump according to claim 1, wherein the width of the suction port provided in the suction chamber and the width of the discharge port provided in the discharge chamber are set to be equal to or less than the width of the groove. Oil lifter device that lubricates the sliding surface of the device.   The sliding surface in the oil chamber shaft seal device of the submersible pump according to claim 1 or 2, wherein a rib for stopping the swirling flow is provided at a position upstream of the swirl lubricant in the suction chamber. Oil lifter device to lubricate.   The upper end of the annular cylindrical body is fitted to the outer periphery of the housing of the upper mating ring to absorb the axial dimension variation of the annular cylindrical body and at the same time, the clearance between the upper and lower ends of the annular cylindrical body and the end surface of the housing is eliminated. An oil lifter device for lubricating a sliding surface in an oil chamber shaft seal device for a submersible pump according to any one of 1 to 3.

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