JP2007170324A - Pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a seal failure and lead to the improvement of durability by suppressing the thrust load of a coolant circulating vane and reducing the microvibration of a mechanical seal and a motor shaft. <P>SOLUTION: This pump device is provided with a seal chamber 3 storing the mechanical seal 8 interposed between a motor 1 and a pump casing 4, coolant 7 sealed in the seal chamber 3, and the coolant circulating vane 10 attached to a pump main shaft 6 in the seal chamber 3 and circulating the coolant 7. The coolant 7 is cooled by heat exchanging with fluid W to be pumped through a radiation bulkhead 31c being a bulkhead between the seal chamber 3 and the pump casing 4. The coolant circulating vane 10 is designed that the coolant 7 is sucked from both the upper and lower sides of a motor side coolant suction space 61 formed on a motor side and a pump casing side coolant suction space 62 formed on a pump casing side, and delivered in the radial direction of the pump main shaft 6. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a pump device having a coolant circulation blade that circulates coolant for cooling a motor that drives a pump main shaft.

  In the conventional pump device, for example, the pump device disclosed in Patent Document 1, as shown in FIG. 9 (corresponding to FIG. 1 of Patent Document 1), in order to prevent overheating of the motor 72 that drives the pump main shaft 71, The coolant is circulated by the circulation blade 73, and cooling water is passed through the cooling cylinder 75 provided on the outer periphery of the motor frame 74 that seals the motor 72, thereby cooling the motor 72. The cooling water that has passed through the cooling cylinder portion 75 flows into a seal chamber 78 that is interposed between a pump casing 77 and a motor 72 that surrounds an impeller 76 that is provided at the lower end of the pump main shaft 71, and the seal chamber. The coolant is sent to the cooling cylinder 75 by the coolant circulation blade 73 accommodated in 78.

Japanese Utility Model Publication No.59-43695

  The cooling liquid circulation blade 73 of this conventional pump device sucks the cooling liquid present in the cooling liquid suction / intake space 79 formed below from the cooling liquid suction port 65 and discharges it in the radial direction to discharge the cooling liquid. Since the pump is a single-suction type centrifugal blade that is fed to 68, a thrust load is generated on the pump main shaft 71. As a result, the pump main shaft 71 is susceptible to slight vibration. When this slight vibration is transmitted to the mechanical seal 100, there may be a problem that adversely affects the sealing performance of the seal portion.

  The present invention solves the above problems and suppresses the thrust load acting on the pump main shaft due to the rotation of the coolant circulation blades, thereby reducing the slight vibration of the pump main shaft and mechanical seal that adversely affects the sealing performance of the mechanical seal. An object of the present invention is to provide a pump device that can lead to improved durability.

  A pump device according to claim 1 is a motor frame in which a motor is sealed, a cooling cylinder portion surrounding the outer periphery of the motor frame, a pump main shaft driven by the motor, and a pump casing attached to the pump main shaft. An impeller that rotates inside, a seal chamber that houses a mechanical seal interposed between the motor and the pump casing, a coolant sealed in the seal chamber, and a pump main shaft that is mounted in the seal chamber And a cooling liquid circulation blade for circulating the cooling liquid, comprising a heat exchange means for cooling the heat of the cooling liquid by exchanging heat with the pumping target fluid, the cooling liquid circulation blade being a motor Coolant is sucked from the coolant suction space formed on both sides of the pump casing and the pump casing, and discharged in the radial direction of the pump main shaft. And butterflies.

  In the pump device according to the first aspect, a double suction centrifugal blade that sucks the coolant from both the motor side and the pump casing side of the coolant circulation blade and discharges it in the radial direction is used as the coolant circulation blade. Therefore, it is possible to suppress the thrust load applied to the pump main shaft due to the suction of the coolant, and to improve the durability by reducing the slight vibration of the pump main shaft and mechanical seal that adversely affects the sealing performance of the mechanical seal. Become.

  The pump device according to a second aspect is characterized in that the coolant circulation blade is provided on an outer peripheral portion of a rotating member of a mechanical seal.

  According to the present invention, it can be arranged without increasing the axial dimension of the pump with the installation of the coolant circulation blades, and the pump device can be made compact. Further, when the single suction type cooling liquid circulation blade is provided on the outer peripheral portion of the rotating member of the mechanical seal, the thrust load is directly transmitted to the rotating shaft, and the fine vibration caused by the thrust load adversely affects the sealing performance. Although there is a possibility, since the cooling circulation blade is a double suction type, the thrust load is reduced and the influence on the sealing performance can be reduced.

  A pump device according to a third aspect is the pump device according to the first or second aspect, wherein the coolant circulation blade connects two face plates having a plurality of suction holes and outer peripheral ends of the face plates to form a plurality of discharge holes. A cylindrical side peripheral wall, a face plate passage communicating the suction hole of one face plate and a suction hole of the other face plate, a discharge passage branching from the face plate passage and communicating with the discharge hole; It is characterized by having.

  In the pump device according to the third aspect, since the coolant circulation blade can be created by using a plate member such as a rolled steel plate, for example, compared with a case where the coolant circulation blade is integrally created by casting or the like. In addition to being easy to cope with shape changes (design changes), there is an advantageous effect in that it can be configured at low cost because it is not necessary to produce a mold when the production quantity is small.

  The pump device according to claim 4 is the pump device according to any one of claims 1 to 3, wherein the pump main shaft has a vertical axis, and the temperature rise after passing through the cooling cylinder portion in the seal chamber. A partition wall is provided for partitioning the high-temperature flow path section through which the coolant flows and the low-temperature flow path section through which the coolant after heat exchange flows, and the high-temperature flow path section and the low-temperature flow path section at the top of the seal chamber And a vent hole communicating with each other.

  Since the pump device according to the present invention is used in a standing state (see FIG. 1) in which the pump main shaft is directed in the vertical direction, the cooling liquid suction spaces are formed respectively above and below the cooling liquid circulation blades. However, inconvenience may occur due to this configuration. That is, the pump spindle on the upper side of the coolant circulation blade is usually equipped with a mechanical seal for preventing the coolant from entering the motor frame. Of course, the pump spindle on the lower side of the coolant circulation blade is provided. Is also equipped with a mechanical seal for the pump casing [this is also why the cooling casing is referred to as a “seal chamber (or mechanical seal chamber)”]. Therefore, when air mixed in the cooling liquid accumulates in the upper cooling liquid suction space, the liquid level in the upper cooling liquid suction space decreases, and the sliding surface (seal surface) between the stationary ring and the rotating ring in the mechanical seal. May be exposed to the accumulated air, causing the sliding surface to be poorly lubricated or cooled by the cooling liquid, and may cause seizure on the sliding surface to make it impossible to seal.

  Therefore, in the pump device according to the fourth aspect, the pump device has a vertical axis, and the uppermost portion of the high-temperature flow path portion is disposed at the uppermost portion of the seal chamber (specifically, the uppermost portion of the upper coolant suction space). Since air vents communicating with the upper part are formed, even if a situation occurs where air collects in the seal chamber (upper coolant suction space), the air is It moves to the high-temperature channel through the vent formed in the uppermost part of the seal chamber (upper coolant suction space), and it is avoided that the seal chamber (upper coolant suction space) accumulates. Become so. Accordingly, the above-described disadvantage caused by the accumulation of air in the seal chamber (upper coolant suction space), that is, the possibility of disabling the sealing function of the mechanical seal, is solved while being a simple modification by simply adding a vent hole. A good pump device in which the mechanical seal functions as expected can be economically realized.

  The pump device according to claim 5 is the pump device according to claim 4, wherein the pump main shaft has a vertical axis, and the high temperature flow in which the coolant whose temperature has increased after passing through the cooling cylinder portion flows in the seal chamber. A partition wall is provided for partitioning the passage portion and the low-temperature flow path portion through which the cooling liquid after heat exchange flows, and a vent hole communicating the high-temperature flow path portion and the low-temperature flow path portion at the top of the seal chamber It is formed.

  As in the pump device according to the fifth aspect, in the case where it is configured as a vertical shaft type provided with a discharge pipe in the lateral direction, it will be described in detail in the section of the embodiment, but for example, it is placed at the bottom of a manhole. In order to force discharge to a transfer pipe for pumping (see transfer pipe 43 in FIG. 3), the pump device is driven by being locked while the discharge pipe is disposed opposite to the inlet side opening of the transfer pipe. Usage is heavily used. In such a case, the normal horizontal posture is set when the discharge pipe is in contact with the transfer pipe, but there are various factors such as the manhole placement location and the dimensional error of the transfer pipe. Accordingly, there is a case where it is operated in an inclined posture inclined in the axial direction of the discharge pipe. The inclination can be considered both when the discharge pipe is lower and when the discharge pipe is higher.

  Thus, as in claim 5 of the present invention, at least two vent holes formed in the seal chamber are provided on the ceiling surface of the seal chamber, and the installation locations are on both sides of the pump main shaft in the axial direction of the discharge pipe. As a result, in any inclined state where the discharge pipe is in the lower and higher positions, air can be moved from one of the vent holes to the high-temperature flow path section, and air can be transferred to the seal chamber (upper coolant suction space). Accumulation is avoided. As a result, even in a vertical shaft type pump device having a discharge pipe facing sideways, there is an advantage that the above-described effect (the mechanical seal does not seize and functions well as expected) can be obtained. is there.

  A pump device according to a sixth aspect is the pump device according to the fourth or fifth aspect, wherein a fixed ring of at least one mechanical seal is attached to a ceiling surface of the seal chamber using a pressing member, The sliding surface between the fixed ring and the rotating ring of the seal is disposed at a lower position than the ceiling surface of the seal chamber, and the holding member communicates from the inner end to the outer end of the air escape groove or notch. Is formed.

  As described above, the pump main shaft on the upper side of the coolant circulation blade is equipped with a mechanical seal for the motor frame. Usually, the stationary ring is on the upper side on the motor side, and the lower side on the coolant circulation blade side. Each of the rotary rings is provided with a ring-shaped pressing member for preventing the stationary ring from being detached from the cooling casing. The inner diameter of the holding member is set so that a gap (a radial gap with the stationary ring) is provided on the inner diameter side in order to avoid interference with the sliding surface of the stationary ring and the rotating ring and the vicinity thereof. However, there is a risk of inconvenience due to the configuration. If the air in the coolant accumulates in the gap, that is, a slight annular space between the pressing member and the fixed ring in the radial direction, the thickness of the pressing member and the height positional relationship with the sliding surface Is that the cooling liquid does not reach the sealing surface, and there is a risk of developing the above-mentioned disadvantage (sliding surface seizure).

  Therefore, in the pump device according to the sixth aspect, the presser member is formed with an air escaping groove or notch communicating from the inner end to the outer end thereof, so that the presser member is formed on the inner diameter side of the presser member. Air that reaches the annular space (see the space 87 in FIG. 4) can be moved to the space on the outer diameter side of the pressing member through the groove or notch, and air is collected in the annular space. Can be prevented. Incidentally, the air that has moved to the outer diameter side of the pressing member moves to the high-temperature flow path portion through the vent formed in the uppermost portion of the seal chamber. Accordingly, it is possible to provide a pump device that can economically eliminate a sealing failure caused by providing a pressing member for locking the stationary ring by a simple device such as forming a groove or a notch in the pressing member. .

  In the pump device according to the present invention, the cooling water that has exchanged heat with the pumping target fluid is formed on the cooling liquid suction space formed on the pump casing side of the cooling liquid circulation blade and on the motor side of the cooling liquid circulation blade. By sucking in from both cooling liquid suction spaces, the thrust load caused by the cooling liquid circulation blades is suppressed, and the pump spindle and mechanical seal micro-vibration that adversely affects the sealing performance of the mechanical seal is reduced, resulting in increased durability. It becomes possible to improve.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an example of a pump device according to an embodiment of the present invention, FIG. 2 is an enlarged sectional view of a seal chamber of the pump device according to this embodiment and its surroundings, and FIG. It is a figure which shows the condition which has arrange | positioned the pump apparatus which is a form in a manhole, FIG. 3 (a) is a top view of the pump apparatus arrange | positioned in a manhole, FIG.3 (b) was arrange | positioned in the manhole. 4 is a front view of the pump device, FIG. 4 is an enlarged cross-sectional view illustrating a mechanical seal of the pump device according to the present embodiment, and FIG. 5 is a pressing member used in the seal chamber of the pump device according to the present embodiment. 6 is a diagram illustrating an example of a coolant circulation blade of the pump device according to the present embodiment, and FIG. 7 is a plan view of the coolant circulation blade illustrated in FIG. FIG. 8 shows a pump according to the present invention. It is a diagram illustrating another embodiment of a coolant circulation vanes of location.

  As shown in FIGS. 1 and 2, the pump device of the present embodiment is driven by a motor frame 2 in which the motor 1 is sealed, a cooling cylinder portion 14 provided so as to surround the outer periphery of the motor frame 2, and the motor 1. A pump main shaft 6 having an upright vertical axis P, an impeller 5 attached to the lower end of the pump main shaft 6 and rotating in the pump casing 4, and a mechanical device interposed between the motor 1 and the pump casing 4. A seal chamber (mechanical seal chamber) 3 for storing the seal 8, a coolant 7 such as a biodegradable antifreeze liquid made of lubricating oil or fresh water, distilled water, or an organic acid enclosed in the seal chamber 3, and the seal chamber 3 And a coolant circulation blade 10 attached to the pump main shaft 6 for circulating the coolant 7, wherein the coolant 7 is a partition wall between the seal chamber 3 and the pump casing 4. An example of heat exchange means) Cooling is performed by exchanging heat with the pumping target fluid W via 31c, and the coolant circulation blade 10 is formed on the motor side coolant suction space 61 formed on the motor side and on the pump casing side. The coolant 7 is sucked from the pump casing side coolant suction space 62 and discharged in the radial direction of the pump main shaft 6. The pumping target fluid is discharged from the provided discharge pipe 41.

  As shown in FIG. 2, the outer peripheral portion of the seal chamber 3 includes an upper body portion 30 and a lower body portion 31, and an annular upper chamber 30 a that opens downward is formed in the upper body portion 30. The seal chamber 3 is formed on the motor side coolant suction space 61 defined by the upper chamber 30a and the partition wall 32 on the motor side of the coolant circulation blade 10 from the upper chamber 30a and on the pump casing side of the coolant circulation blade 10. The pump casing side suction space 62 is formed, and the ceiling wall 3 b of the motor side coolant suction space 61 is formed to be the uppermost part of the seal chamber 3. At two locations on both sides of the vertical axis P of the pump main shaft 6 in the axial direction of the discharge pipe 41 at the uppermost portion of the seal chamber 3, the motor side coolant suction space 61, which is a low temperature flow path section, is connected to the high temperature flow path section. A vertically-facing vent hole 94 communicating with a certain upper chamber 30a is formed (the high-temperature channel portion and the low-temperature channel portion will be described later). The diameter of the air hole 94 may be a value that is sufficient to allow air to move by its buoyancy. If the diameter of the vent hole is too large, the cooling characteristic is deteriorated by mixing the coolant having a high temperature before heat exchange flowing through the upper chamber 30a into the coolant having a low temperature after heat exchange. Is selected considering the air exhaust and cooling characteristics. As shown in FIG. 2, it is desirable to provide the motor side cooling / intake space 61 at a position that is the outer diameter side end of the ceiling wall 3b. The cross section of the air hole is not limited to a circle.

  The lower opening of the annular upper chamber 30a is closed by the annular partition member 9, and the annular partition member 9 allows the annular upper chamber 30a and the lower chamber 31a provided in the lower body portion 31 to open upward and downward. It is partitioned by direction. In addition, an annular groove 90 is formed on the inner peripheral surface of the annular partition member 9, and a first communication passage 91 that communicates between the annular upper chamber 30a and the lower chamber 31a is provided so as to penetrate in the axial direction. A second communication path 92 is provided on the inner peripheral side of the first communication path 91 so as to communicate with the motor-side coolant suction space 61 in the axial direction. In addition, a coolant discharge passage 93 that penetrates the annular partition member 9 in the radial direction and communicates with the annular groove 90 is formed.

  The lower body portion 31 of the outer peripheral portion of the seal chamber 3 is provided with a center hole 31A, extends downward in the axial direction in a stepwise manner, and extends in the radial direction, and is connected to a lower end portion of the boss portion 31B. The heat dissipating partition wall 31C that extends to the outer peripheral portion of the impeller 5 toward the radially outer side, the peripheral wall portion 31D that rises from the outer peripheral edge portion of the heat dissipating partition wall 31C, and the upper end portion of the peripheral wall portion 31D projects outward in the radial direction. The flange 31E has a flange 31E and a flange 30A projecting radially outward provided at the lower end of the upper body 30 is coupled to the lower part 31E. The upper peripheral edge of the pump casing 4 is coupled to the above. In addition, a heat transfer promoting portion 31F made of an annular ridge is formed on the upper surface of the heat dissipation partition 31C.

  The mechanical seal 8 is called a double type as shown in FIGS. 2, 4, and 6, and is installed in a mounting circular recess 3 c that is recessed upward in the ceiling surface 3 a of the seal chamber 3. An annular support ring 85 to be fitted, an upper fixed ring 80 that is loosely fitted to the pump main shaft 6 in the seal chamber 3 and slidably fitted to the support ring 85, and the pump main shaft 6 in the seal chamber 3. And the lower fixed ring 81 fixed to the upper side of the annular receiving seat 33, the pump main shaft 6 in the seal chamber 3 is externally fitted in an integral rotation state, and is in sliding contact with the lower surface of the upper fixed ring 80. An upper rotary ring 82 that is pressed and urged upward by a coil spring 84 so as to form a seal portion, a lower rotary ring 83 that rotates simultaneously with the pump main shaft 6 and is arranged above the lower fixed ring 81, and the like are provided. .

  The annular seat 33 is attached to a central hole 31 </ b> A provided in the boss portion 31 </ b> B of the lower body portion 31 in the seal chamber 3. The support ring 85 is supported by a ring-shaped pressing member 86 that is fixed to the lower peripheral surface 3 d of the mounting circular recess 3 c on the ceiling surface 3 a of the seal chamber 3. Further, the height position of the peripheral lower surface 3d of the mounting circular dent 3c on the ceiling surface 3a of the seal chamber 3 is the same as that of the motor side coolant suction space 61 formed adjacent to the outer diameter side of the peripheral lower surface 3d. It is set lower than the height position of the ceiling wall 3b.

  As shown in FIGS. 4 and 5, the pressing member 86 is composed of three equal pressing plates 86b having a circular arc shape having a width in the radial direction. 86b is disposed in the circumferential direction for the time being so as to have equal intervals. Each presser plate 86b is formed with two bolt holes 86c for bolting it to the lower peripheral surface 3d. As a result, a total of three space portions 86a are formed between the pressing plates 86b, 86b adjacent in the circumferential direction, and these three space portions function as notches 86a for air escape. By moving the air through the motor-side coolant suction space 61 and the vent hole 94, it is possible to prevent the sliding surface from being seized due to the accumulation of air. This effect will become apparent from the following explanation.

  For example, when the presser member 86 is a component (conventional technology) made of a single annular presser plate (not shown), it is between the annular seal portion 80a whose outer diameter is narrow at the lower end of the fixed ring 80. Since an annular space (see the space 87 in FIG. 4) is formed, when the air in the coolant 7 accumulates in the space, the coolant 7 is sufficiently supplied to the sliding surface with the rotating ring 82. This may cause a seal failure. Therefore, in the pump device of the present invention, a total of three internal and external through notches (see the notches 86a in FIG. 5) are provided at an equal angle in the circumferential direction on an annular retainer plate (not shown) that is a single component. The idea is to eliminate the inconvenience described above by providing an air passage.

  From such a technical background, the space portion 86a in the pressing member 86 which is actually composed of the three pressing plates 86a is expressed as “notch” in the present specification. However, although not shown in the drawings, the air in the space 87 is supplied to the motor side coolant suction space by providing one or more inner and outer through grooves or recesses recessed upward on the lower surface of the single annular holding member. It is also possible to adopt a configuration that makes it possible to escape to 61. Further, the number of spaces and the number of bolt holes are not limited to the above-described embodiment.

  As shown in FIG. 4, FIG. 6 and FIG. 7, the coolant circulation blade 10 has a plurality of suction holes 21, two annular face plates 10a and 10b, and two face plates 10a and 10b. A cylindrical side peripheral wall 10c having a plurality of discharge holes 22 connected between the outer peripheral ends in a liquid-tight manner, and a T-shaped cooling liquid flow path 10d having a transversely laid cross section that connects the suction holes 21 and the discharge holes 22 to each other. Have. The coolant circulation blade 10 is arranged so that the coolant 7 discharged from the discharge hole 22 through the coolant flow passage 10d flows into the annular groove 90 on the inner peripheral surface of the annular partition member 9. The coolant flow path is not limited to a sideways T-shape, and may be a sideways Y-shape, and a flow path between face plates that connects the suction holes of one face plate and the suction holes of the other face plate. It is only necessary to have a discharge flow path that branches off from the flow path between the face plates and communicates with the discharge holes. In addition, it is desirable to be vertically symmetric in order to suppress the thrust load.

  Annular disks 23 and 24 are attached to the inner peripheral edges of the upper and lower face plates 10a and 10b. A plurality of insertion holes 25 are provided in the upper and lower disks 23 and 24 so as to face each other in the vertical direction, and the upper rotation ring 82 and the lower rotation ring 83 are vertically arranged in the plurality of insertion holes 25. A coil spring 84 that presses and urges in a separating direction is inserted. A spring retainer 26 is connected to the inner peripheral surfaces of the upper and lower disks 23, 24, and the spring retainer 26 is fitted and installed to rotate integrally with the pump main shaft 6. The side peripheral wall 10c is formed to have a wider width than the upper and lower face plates 10a and 10b so as to improve the sealing performance with respect to the annular groove 90. The coolant circulation blade is not limited to being joined to the spring retainer, and may be joined to another rotating member of the mechanical seal, for example, the lower retainer 88. Moreover, you may attach directly to the main axis | shaft 6. FIG.

  On the other hand, as shown in FIG. 2, a partition member 11 is provided in the lower chamber 31 a in the lower body 31 at the outer peripheral portion of the seal chamber 3. The partition member 11 is connected to a stepped cylindrical portion 11a surrounding the stepped boss portion 31B of the lower chamber 31a with a predetermined interval, and a lower end portion of the stepped cylindrical portion 11a so as to be radially outward. And a flange portion 11b facing the upper side of the heat radiation partition wall 31C with a small space therebetween, and an upper end portion of the flange portion 11b is attached to the lower surface of the annular partition member 9. As a result, a coolant channel 12 having a small passage cross-sectional area along the heat dissipation partition 31C is formed between the lower surface of the flange portion 11b and the upper surface (surface) of the heat dissipation partition 31C (an example of heat exchange means). The liquid flow path 12 is connected to the pump casing side coolant of the coolant circulation blade 10 via the step-shaped coolant flow path 15 surrounded by the surface of the step-shaped boss portion 31B and the inner surface of the step-shaped cylinder portion 11a. The suction space 62 and the second communication passage 92 of the annular partition member 9 communicate with each other. The heat exchanging means is not limited to the partition wall (radiant partition wall 31C) between the seal chamber and the pump casing, but if the heat exchange means is configured to exchange heat with the pumping target fluid, the periphery of the discharge pipe portion is a double pipe. It may be a heat exchange means formed by, for example.

  The seal chamber 3 and its outer peripheral portion are constituted by an upper chamber 30a through which the coolant 7 whose temperature has risen after passing through the cooling cylinder portion 14 flows, and a lower chamber 31a from the first communication passage 91 to the cooling passage 12. The high-temperature flow path section, the coolant flow path 15 through which the coolant 7 after heat exchange flows, the second communication path 92, the motor-side coolant suction space 61 and the pump casing-side coolant suction space 62 of the coolant circulation blade 10. And a low-temperature channel portion constituted by the annular groove 90 and the coolant discharge passage 93. The high-temperature channel portion and the low-temperature channel portion are the upper chamber 30a and the motor-side coolant in the upper body portion 30. A partition wall 32 that partitions the suction space 61 and a partition wall 34 that partitions the first communication path 91 and the second communication path 92 in the partition member 9 are partitioned by the partition member 11. Has been.

  The coolant 7 sealed in the seal chamber 3 circulates in the coolant circulation system 13 by the rotation of the coolant circulation blade 10 to cool the motor 1. That is, the lubricating liquid circulation system 13 causes the cooling liquid discharge passage 93 provided in the annular partition member 9 and the cooling cylinder portion 14 provided surrounding the outer periphery of the motor frame 2 to communicate with each other. The first path 13 </ b> A and the second path 13 </ b> B that communicates the cooling cylinder portion 14 and the annular upper chamber 30 a in the upper body portion 30 with each other via an introduction passage 30 b provided in the upper body portion 30 are provided. In addition, 16 in FIG. 1 shows a drain pipe.

  The flow of the coolant 7 in the coolant circulation blade 10 will be described in detail. Due to the rotation of the pump main shaft 6, the upper rotary ring 82, the lower rotary ring 83 and the coolant circulation blade 10 of the mechanical seal 8 rotate in conjunction with each other. When the coolant circulation blade 10 rotates, the coolant 7 is sucked from the suction holes 21 of the upper and lower face plates 10a and 10b, passes through the coolant flow path 10d, and is discharged from the discharge hole 22 of the side peripheral wall 10c to the annular partition member 9. It is discharged into the annular groove 90. That is, in this pump apparatus, the coolant 7 is sucked from both the motor side coolant suction space 61 located above the coolant circulation blade 10 and the pump casing side coolant suction space 62 located below, The centrifugal pump is configured to be discharged in the radial direction.

  The coolant 7 discharged into the annular groove 90 of the annular partition portion 9 is the annular groove 90 of the annular partition member 9 → the coolant discharge passage 93 provided in the annular partition member 9 → the first path 13A → cooling. Tube portion 14 → second path 13B → introduction passage 30b → annular upper chamber 30a of upper body portion 30 → first communication passage 91 of annular partition member 9 → lower chamber 31a of lower body portion 31 → coolant flow path 12 → Step-like coolant flow path 15 → pump casing side coolant suction space 62 → face plate 10b of coolant circulation blade 10 or step-like passage 15 → second communication passage 92 → motor side coolant suction space 61 → coolant circulation. The motor frame 2 is cooled in the process of passing through the cooling cylinder portion 14 surrounding the motor frame 2 by circulating along the normal path of the face plate 10 a of the blade 10, and the motor 1 is cooled via the cooled motor frame 2.

  The coolant flowing through the cooling cylinder portion 14 is disposed so as to cool the periphery of the upper bearing of the motor 1, and the coolant 7 passes through the cooling cylinder portion 14 so that the periphery of the bearing on the upper side of the motor 1 is cooled. It is desirable to configure. In addition, an air accommodating space (not shown) can accommodate air generated from the cooling liquid 7 on the upper side of the cooling cylinder portion 14 surrounding the upper portion of the motor frame 2, and the volume of the cooling liquid 7 expands as the temperature rises. In this case, the coolant 7 can be accommodated. Furthermore, it is desirable to provide the coolant inlet 102 and the air vent 103 below the ceiling surface of the cooling cylinder so that an air accommodating space is always formed when the coolant is filled into the pump device.

  As described above, the coolant 7 in the seal chamber 3 that circulates in the coolant channel 12 by the coolant circulation blade 10 that rotates in conjunction with the pump main shaft 6 is pumped through the heat dissipation partition 31C in the course of the circulation. Heat is exchanged with the pumping target fluid W in the casing 4 to be cooled. Moreover, since the passage cross-sectional area of the coolant channel 12 is set small, the flow rate of the coolant 7 passing through the coolant channel 12 is increased. That is, the flow rate of the cooling liquid 7 in the vicinity of the heat radiating partition 31C circulating in the cooling liquid flow path 12 is increased, the heat transfer coefficient between the cooling liquid 7 and the heat radiating partition 31C is increased, and the cooling liquid 7 and the pumping target fluid. The efficiency of heat exchange with W is improved, and the motor 1 can be effectively cooled.

  Further, since the coolant circulation blade 10 is arranged on the motor frame 2 side with respect to the coolant flow channel 12, it is affected by physical limitations (that is, the vertical width dimension) of the coolant circulation blade 10. In addition, the flow path cross-sectional area of the coolant flow path 12 can be set to be even smaller by bringing the flange portion 11b of the partition member 11 closer to the heat dissipation partition 31C. For this reason, the flow rate of the coolant 7 in the vicinity of the heat radiating partition 31C is greatly increased, the heat transfer coefficient between the coolant 7 and the heat radiating partition 31C is increased, and heat exchange between the coolant 7 and the pumping target fluid water W is performed. The efficiency can be further increased and the motor 1 can be effectively cooled.

  Furthermore, since the coolant circulation blade 10 has a structure configured on the outer peripheral portion of the mechanical seal 8, compared to a configuration in which the mechanical seal 8 and the coolant circulation blade 10 are arranged in the axial direction, It can arrange | position, without increasing the dimension of the pump axial direction by installation of the cooling fluid circulation blade | wing 10. FIG.

  On the other hand, since the heat transfer promotion part 31F made of an annular ridge is formed on the surface of the heat radiation partition 31C on the coolant flow path 12 side, the coolant 7 circulating in the coolant flow path 12 by the heat transfer promotion part 31F. The heat transfer efficiency between the coolant 7 and the heat radiating partition wall 31C is further increased, the heat exchange efficiency between the coolant 7 and the pumping target fluid W is increased, and the motor 1 is effectively cooled. Can contribute.

  Further, by surrounding the stepped boss portion 31B of the lower chamber 31a in the lower body portion 31 with the stepped cylindrical portion 11a of the partitioning member 11, the stepped coolant channel 15 is formed continuously to the coolant channel 12. By forming, the flow of the coolant 7 circulating through the step-like coolant flow path 15 is disturbed, and between the coolant 7 and the step-like boss portion 31B in which heat flows toward the heat dissipation partition 31C. The heat transfer coefficient can be increased, heat exchange between the coolant 7 and the stepped boss portion 31B can be promoted, and the motor 1 can be effectively cooled.

  The pump device configured as described above can be used in a manhole. For example, as shown in FIGS. 3 (a) and 3 (b), a transfer pipe for pumping water that has an opening flange 43a on the inlet side that opens laterally at the bottom of the manhole 44 and extends upward. 43 is fixedly arranged (an example of a stationary type transfer pipe), and a pair of guide pipes 43b are installed on the upper part of the transfer pipe 43 near the opening flange 43a so as to span the opening peripheral wall 44a of the manhole 44. 43b are erected. The discharge pipe 41 of the pump is equipped with a substantially hook-like hooking portion 42. As shown in FIG. 3A, the above-described hook portion 42 has a slide portion (showing a C shape in plan view) 42a that is fitted to the pair of guide pipes 43b and 43b so as to be relatively movable up and down. Is formed.

  Therefore, by putting the slide portion 42a into the guide pipes 43b and 43b and then lowering the suspended pump device, as shown in FIG. Is caught on the opening flange 43b from above in a normal positional relationship, so that a state in which the pump device is supported is automatically obtained. In the support state, the discharge port portion 41a of the discharge tube 41 and the opening flange 43b of the transfer tube 43 are set so that their axial centers coincide with each other, and the sewage collected at the bottom of the manhole 44, It is easy and convenient to use the method of sucking rainwater and smoothly discharging it to the transfer pipe 43. The air escape holes (vent holes) 94 are formed on both sides of the shaft center P on the center line of the pump discharge port portion 41a and at positions that are the outer diameter side ends of the ceiling wall 3b. In addition, the joining method with a transfer pipe is not limited to the said embodiment, A bolt part may be used for a flange part.

[Another embodiment]
(1) The vent holes 94 provided in the seal chamber 3 are provided as the vent holes 94 in the uppermost two portions of the ceiling wall 3b of the seal chamber in the pump device of the present embodiment. It is not limited and it is sufficient that one or more places are formed on the ceiling surface 3 b of the seal chamber 3. Therefore, a configuration formed at one position on either side across the pump main shaft 6 in the axial direction of the discharge pipe 41 and at a position that becomes the outer diameter side end of the ceiling wall 3b of the motor side coolant suction space 61, Alternatively, a configuration in which three or more vent holes 94 are provided at equal angles in the circumferential direction with respect to the axis of the pump main shaft 6 is also possible.

(2) The coolant circulation blade 10 has a shape that allows the coolant to be sucked from both sides of the coolant circulation blade and discharged in the outer diameter direction so that the thrust load is offset. Well, it is not limited to the shape of this embodiment shown in FIG. For example, a configuration as shown in FIG. Further, as shown in FIG. 8, the position where the coolant circulation blade is attached may be directly attached to the pump main shaft instead of the rotating member of the mechanical seal. In addition, the white arrow of FIG. 8 has shown the flow direction of the cooling fluid.

It is a longitudinal cross-sectional view which shows an example of the pump apparatus which is embodiment of this invention. It is an expanded sectional view of the seal chamber of the pump device which is this embodiment, and its circumference. It is a figure which shows the condition which has arrange | positioned the pump apparatus which is this embodiment in a manhole, (a) is a top view of the pump apparatus arrange | positioned in a manhole, (b) is the pump apparatus arrange | positioned in a manhole. FIG. It is an expanded sectional view explaining the mechanical seal of the pump apparatus which is this embodiment. It is a top view which shows an example of the pressing member used in the seal chamber of the pump apparatus which is this embodiment. It is a figure which shows an example of the cooling fluid circulation blade | wing of the pump apparatus which is this embodiment. It is a top view of the cooling fluid circulation blade | wing shown by FIG. It is a figure which shows another Example of the cooling fluid circulation blade | wing of the pump apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows the conventional pump apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Motor 2 Motor frame 3 Seal chamber 3a Ceiling surface 3a
DESCRIPTION OF SYMBOLS 4 Pump casing 5 Impeller 6 Pump spindle 61 Coolant suction space 7 Coolant 8 Mechanical seal 10 Coolant circulation blade 11 Partition wall 12 Coolant flow path 14 Cooling cylinder part 31C Radiation partition 41 Discharge pipe 80 Upper fixed ring 81 Lower side Fixed ring 82 Upper rotary ring 83 Lower rotary ring 85 Support ring 86 Presser member 86a Notch 94 Ventilation hole

Claims (6)

A motor frame in which a motor is sealed, a cooling cylinder portion surrounding the outer periphery of the motor frame, a pump main shaft driven by the motor, an impeller attached to the pump main shaft and rotating in a pump casing, A seal chamber that houses a mechanical seal interposed between a motor and the pump casing, a coolant sealed in the seal chamber, and a cooling unit that is attached to the pump main shaft in the seal chamber and circulates the coolant. A pump device comprising a liquid circulation blade,
Heat exchange means for cooling the cooling liquid by exchanging heat with the fluid to be pumped, the cooling liquid circulation blade sucks the cooling liquid from cooling liquid suction spaces formed on both sides of the motor side and the pump casing side, A pump device that discharges in a radial direction of a pump main shaft.   The pump device according to claim 1, wherein the coolant circulation blade is provided on an outer peripheral portion of a rotating member of a mechanical seal.   The cooling liquid circulation blade includes two face plates having a plurality of suction holes, a cylindrical side peripheral wall having a plurality of discharge holes connected to outer peripheral ends of the face plate, a suction hole of one face plate, and the other face plate. 3. An inter-face plate flow path communicating with the suction holes of the gas and a discharge flow path branched from the inter-face plate flow path and communicating with the discharge holes. The pump device described.   The pump main shaft has a vertical axis, and a high-temperature channel portion through which the coolant whose temperature has increased after passing through the cooling cylinder portion flows in the seal chamber, and a low-temperature channel portion through which the coolant after heat exchange flows 4. A partition wall for partitioning is provided, and a vent hole communicating the high-temperature channel portion and the low-temperature channel portion is formed at an uppermost portion of the seal chamber. The pump apparatus in any one.   The pump casing includes a horizontal discharge pipe for discharging a pumping target fluid in a radial direction of the pump main shaft, and the vent holes are provided at least in two places on the ceiling surface of the seal chamber, and the installation locations thereof are the discharge pipes. The pump device according to claim 4, wherein the pump device is located on both sides of the pump main shaft in the axial direction. At least one fixed ring of the mechanical seal is attached to the ceiling surface of the seal chamber using a pressing member, and the fixed ring of the mechanical seal and the sliding surface of the rotary ring are positioned lower than the ceiling surface of the seal chamber. The pump device according to claim 4 or 5, wherein the pressing member is formed with an air escaping groove or notch communicating from the inner end to the outer end thereof.

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