WO2006035724A1 - Pompe centrifuge a arbre vertical, rotor pour la pompe et climatiseur - Google Patents

Pompe centrifuge a arbre vertical, rotor pour la pompe et climatiseur Download PDF

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Publication number
WO2006035724A1
WO2006035724A1 PCT/JP2005/017641 JP2005017641W WO2006035724A1 WO 2006035724 A1 WO2006035724 A1 WO 2006035724A1 JP 2005017641 W JP2005017641 W JP 2005017641W WO 2006035724 A1 WO2006035724 A1 WO 2006035724A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
main plate
pump
casing
rotor shaft
Prior art date
Application number
PCT/JP2005/017641
Other languages
English (en)
Japanese (ja)
Inventor
Akinori Furukori
Masahiko Yoshida
Michiaki Ohno
Original Assignee
Kabushiki Kaisha Saginomiya Seisakusho
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kabushiki Kaisha Saginomiya Seisakusho filed Critical Kabushiki Kaisha Saginomiya Seisakusho
Priority to JP2006537728A priority Critical patent/JP4680922B2/ja
Publication of WO2006035724A1 publication Critical patent/WO2006035724A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/14—Pumps raising fluids by centrifugal force within a conical rotary bowl with vertical axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/20—Mounting rotors on shafts

Definitions

  • the present invention relates to a vertical shaft centrifugal pump and a pump port used for the vertical shaft centrifugal pump, and is particularly suitable for application to a drain pump incorporated in an air conditioner requiring quietness.
  • a vertical shaft centrifugal pump In a vertical shaft centrifugal pump, a liquid body intervening in a casing is rotated by the rotation of an impeller, and the liquid is discharged out of the casing by utilizing a centrifugal force generated thereby. Further, a new liquid is sucked into the casing along with the liquid discharging operation.
  • This vertical shaft centrifugal pump is used, for example, as a drainage pump of an air conditioner.
  • An impeller that constitutes a main part of a drainage pump together with a casing includes an impeller shaft connected to a motor, the impeller shaft, and a plurality of impeller plates that project radially around the impeller shaft. It has.
  • This conventional vane plate is used to rotate the liquid in the pump chamber. It is common to have a wide surface that is almost perpendicular to the direction of rotation of the slats!
  • Patent Document 3 The blades disclosed in Patent Document 3 are basically the same as Patent Document 1 and Patent Document 2.
  • Patent Document 3 a through hole is provided in a disk portion between an impeller shaft and a blade outer peripheral wall portion to prevent noise caused by axial vibration. Even if such a through hole is applied to Patent Document 1 and Patent Document 2, it cannot be said that the noise generated when the blades drain water is not sufficiently reduced.
  • the difference in pressure generated between the surface facing the rotational direction of the impeller blade rotating around the axis of the impeller shaft and the surface positioned on the opposite side is the circumference of the impeller. It increases in proportion to the square of speed. For this reason, in particular, at the outer peripheral edge of the impeller blade plate that rotates about the axis of the impeller shaft, it is easy for vibration to occur on the surface opposite to the rotation direction of the impeller blade. This is one of the major causes. In addition, when the impeller rotates, the liquid level force of the liquid that the upper end of the impeller rotates around in the pump chamber begins to be exposed. When getting over the edge, noise is generated by entraining the air in the pump chamber.
  • the impeller blade plate in the conventional drainage pump has a wide surface that is substantially orthogonal to the rotation direction of the impeller in order to promote the circulation of the liquid intervening in the pump chamber. This contributes to the generation of noise as described above.
  • the drainage pump incorporated in the air conditioner has the characteristic that its deadline is lower than other pumps and its load is essentially small. Considering these characteristics, it can be said that the conventional vane plate having a wide and substantially perpendicular surface to the direction of rotation of the impeller is unsuitable for a drainage pump incorporated in an air conditioner. Like.
  • Patent Document 1 Utility Model Registration No. 2593986
  • Patent Document 2 Japanese Patent No. 3282772
  • Patent Document 3 Japanese Patent Laid-Open No. 2002-242885
  • An object of the present invention has been made in view of the problem to be solved, and is a vertical shaft centrifugal pump excellent in quietness, a rotor incorporated in the vertical shaft centrifugal pump, and the vertical shaft centrifugal pump as a drainage pump. It is in providing the air conditioning apparatus incorporated as.
  • a first aspect of the present invention includes a rotor, a casing, a cover that is attached to the casing and forms a pump chamber in which the rotor is accommodated, and is protruded from the casing.
  • a vertical-shaft centrifugal pump having a suction pipe that forms a suction passage that communicates with a lower central portion of the pump chamber, and a discharge port that is formed in the casing and communicates with the pump chamber
  • the rotor includes the cover A rotor shaft whose upper end is connected to the drive motor from outside, a main plate concentrically and integrally connected to the rotor shaft, and a plurality of protrusions protruding substantially parallel to the axis of the rotor shaft from the main plate It comprises a book pin and a pressure equalizing section communicating with the front surface side and the back surface side of the main plate.
  • the liquid As the liquid is discharged, the liquid is sucked into the pump from the suction passage communicating with the central portion of the pump chamber.
  • the pin that rotates in the pump chamber around the axis of the rotor moves so as to wrap around the liquid in the surroundings in a laminar flow state.
  • the pin rotating in the pump chamber around the rotor shaft center is arranged in a laminar flow state with respect to the liquid intervening around the pin. Move to wrap around backwards. This creates a pressure difference between the top and bottom of the main plate, and the water flow rises from the pressure equalization section. Noise due to entrainment is suppressed.
  • a stirring member whose one end force projects along the axis of the rotor shaft can be disposed in the suction passage of the suction pipe.
  • the axial force of the rotor shaft may be a plurality of blade members protruding radially.
  • a partition wall can be formed on the cover so as to protrude downward from here to surround the rotor and to form an annular gap with the inner wall of the casing.
  • the partition wall is preferably positioned so as to face and block the discharge port formed in the casing.
  • the pump chamber can always be maintained at atmospheric pressure, the liquid can be efficiently discharged from the discharge port to the outside of the pump chamber by effectively using the centrifugal force.
  • the main plate may have an annular shape, and an annular space formed between the inner peripheral surface of the main plate and the outer peripheral surface of the rotor shaft may function as a pressure equalizing unit.
  • the main plate and the rotor shaft can be integrally connected via a plurality of stays crossing the gap. As a result, the surface of the liquid sucked up into the pump chamber can be rapidly formed into a parabolic shape.
  • a first array group in which pins and communication holes are arrayed in a first direction substantially along the circumferential direction of the main plate and a direction orthogonal thereto, and inclined by 45 degrees with respect to the first direction
  • the second array group in which the pins and the communication holes are arrayed in the direction and the direction orthogonal thereto can be alternately arrayed along the circumferential direction. This allows the first and second The direction and flow velocity of the swirl flow of the liquid obtained by each array group can be slightly changed, and bubbles generated between individual pins and the liquid can be efficiently removed.
  • each pin projected onto a plane perpendicular to the rotation direction of the main plate can be set so that the pin located on the radially inner side of the rotor shaft becomes smaller.
  • noise can be suppressed by suppressing air entrainment around the pin located on the inner side in the radial direction.
  • the kinetic energy of the pin located radially outside can be effectively applied to the liquid to improve the deadline lifting height.
  • a similar effect can be obtained by setting the protruding length of each pin to be shorter toward the inner side in the radial direction of the rotor shaft.
  • the same effect can be obtained by setting the width dimension of the distal end portion along the radial direction of the rotor shaft of the pin located radially inside the rotor shaft to be smaller than that of the proximal end portion. .
  • the same effect can be obtained by increasing the distance between the pins located on the radially inner side of the rotor shaft to the same force or wider than the distance on the outer side.
  • each pin in a plane perpendicular to the axis of the rotor shaft a circular shape, an elliptical shape, a polygonal shape such as a rectangle, or an asymmetrical shape such as an airfoil shape can be appropriately employed.
  • the maximum length of the pin along the rotation direction of the main plate can be set to the same force as or more than the maximum width dimension of the pin along the radial direction of the rotor shaft.
  • a drive motor a DC brushless motor that has less vibration than an AC motor, is small and light, and is easy to control can be employed.
  • a second aspect of the present invention is a rotor shaft, a main plate concentrically and integrally connected to the rotor shaft, and a plurality of main plate forces projecting substantially parallel to the axis of the rotor shaft. And a pressure equalizing portion that communicates the front side and the back side of the main plate.
  • This pump rotor is suitable as a rotor in the vertical shaft centrifugal pump according to the first embodiment of the present invention.
  • a third aspect of the present invention resides in an air conditioner characterized by incorporating the vertical shaft centrifugal pump according to the first aspect of the present invention as a drain pump.
  • Fig. 1 shows a vertical centrifugal pump according to the present invention as a drainage pump unit for an air conditioner. It is a conceptual diagram showing the attachment condition of one Embodiment applied to.
  • FIG. 2 is an extracted enlarged cross-sectional view of section II in FIG.
  • FIG. 3 is a longitudinal sectional view showing a schematic structure of the drainage pump unit in the embodiment shown in FIG. 1.
  • FIG. 4 is a plan view of the drainage pump unit shown in FIG.
  • FIG. 5 is a bottom view of the drainage pump unit shown in FIG.
  • FIG. 6 is a bottom view of the cover portion of the drainage pump unit shown in FIG.
  • FIG. 7 is a sectional view taken along arrow VII-VII in FIG.
  • FIG. 8 is a cross-sectional view taken along arrow VIII-VIII in FIG.
  • Fig. 9 is a three-dimensional projection view showing the appearance of the rotor in the drainage pump unit shown in Fig. 3.
  • FIG. 10 is a rear view of the rotor shown in FIG. 9.
  • FIG. 11 is a conceptual diagram schematically showing the flow direction of the fluid by the first arrangement group in the rotor shown in FIG. 9 together with FIG.
  • FIG. 12 is a conceptual diagram schematically showing the flow direction of the fluid by the second arrangement group in the rotor shown in FIG. 9 together with FIG.
  • FIG. 13 is a plan view of another embodiment in which the rotor according to the present invention is applied to the rotor of the drainage pump unit shown in FIG.
  • FIG. 14 is a bottom view of the rotor shown in FIG.
  • FIG. 15 is a longitudinal sectional view of another embodiment in which the rotor according to the present invention is applied to the rotor of the drainage pump unit shown in FIG.
  • FIG. 16 is a longitudinal sectional view of still another embodiment in which the rotor according to the present invention is applied to the rotor of the drainage pump unit shown in FIG.
  • FIG. 17 is a longitudinal sectional view of still another embodiment in which the rotor according to the present invention is applied to the rotor of the drainage pump unit shown in FIG.
  • FIG. 18 is a longitudinal sectional view showing a schematic structure of another embodiment in which the vertical shaft centrifugal pump according to the present invention is applied to the drainage pump unit shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 shows the state of attachment of the drainage pump unit in the present embodiment, and FIG. That is, the drainage pump unit 10 in the present embodiment is attached to the fixing portion 13 formed on the housing partition wall 12 of the air conditioner via the bracket 11.
  • a gasket 14 having both an anti-vibration function and a sealing function is sandwiched between the fixed portion 13 and the bracket 11 having a rectangular plate shape.
  • the mounting portion 11 a of the bracket 11 is screwed to the fixing portion 13 of the housing partition wall 12 by the mounting screw 15 screwed into the fixing portion 13.
  • the drive motor 16 is mounted on the connecting portion l ib of the bracket 11 so that the drive motor 16 for driving the rotor, which will be described later, is located outside the housing partition wall 12.
  • a control panel 17 for controlling the operation of the drive motor 16 is installed outside the housing partition wall 12, and the control panel 17 and a connector 18 attached to the drive motor 16 are connected via a cable 19.
  • the connector 18 of the drive motor 16 in the present embodiment can be disposed at a position as shown by a two-dot chain line in FIG. It can be appropriately selected in consideration of interference with the parts.
  • the bracket 11 in the present embodiment is formed of a nonmagnetic material such as austenitic stainless steel or aluminum that does not adversely affect the operation of the drive motor 16 described later.
  • FIG. 3 The internal structure of the main part of the drainage pump unit 10 is shown in FIG. 3, its planar shape and bottom face shape are shown in FIGS. 4 and 5, respectively, and the bottom face shape of the cover part is shown in FIG.
  • the cross-sectional structures taken along arrows VII-VII and VIII-VIII in Fig. 3 are shown in Figs. 7 and 8, respectively, and the appearance of the rotor is shown in Fig. 9, and the bottom shape is shown in Fig. 10. That is, the drainage pump unit 10 in the present embodiment has a cylindrical side wall portion 20a and a conical bottom wall portion 20b.
  • a casing 20 and a cover 22 connected to the upper end of the side wall 20a of the casing 20 and forming a pump chamber 21 with the casing 20 are provided.
  • the drainage pump unit 10 is also assembled between a rotor 23 housed in the pump chamber 21, a drive motor 16 connected to the rotor 23 and rotating the rotor 23, and a cover 22 and the drive motor 16. It further comprises the aforementioned bracket 11 for partitioning these.
  • the bracket 11 is arranged to separate the drive motor 16 disposed outside the housing partition wall 12 of the air conditioner, the cover 22 and the casing 20 disposed inside the housing partition wall 12. It is attached to 12 fixed parts 13. For this reason, it is not necessary to provide a drain plate for protecting the bearing portion of the drive motor 16 between the cover 22 and the drive motor 16. However, even if a drive motor with different capacities is used, the drainage pump unit 10 may simply replace the drive motor 16. As a result, there is an advantage that the bracket 11 and the like need not be replaced at all.
  • a DC brushless motor is employed as the drive motor 16, which can be much smaller and lighter than an AC motor with large vibrations, and its drive control is easy.
  • High-frequency vibration which is a drawback of the DC motor, can be reliably cut off by interposing the gasket 14 described above between the housing partition wall 12 of the air conditioner and the mounting part 11a of the bracket 11.
  • the bottom wall portion 20b of the casing 20 is set in a conical shape with the central portion recessed downward, but the bottom wall portion 20b is set in a slightly flat bottom shape parallel to the horizontal plane.
  • the casing 20 is formed with a suction pipe 25 that protrudes downward from the center of the bottom wall portion 20b and forms a suction passage 24 communicating with the pump chamber 21.
  • the casing 20 is also integrally formed with a discharge pipe 27 that protrudes radially outward of the rotor 23 from the side wall portion 20a and opens a discharge port 26 that faces the pump chamber 21.
  • the suction pipe 25 is positioned in the drain pan 28 of the air conditioner indicated by a two-dot chain line in FIG. 3, and is almost immersed in the condensed water accumulated in the drain pan 28.
  • the discharge pipe 27 is connected to the base end of a drain pipe 29 whose leading end is led out of the casing partition wall 12 of the air conditioner.
  • the inner diameter of the discharge pipe 27 is increased toward the downstream side so as to face the pump chamber 21. Force that keeps the discharge port 26 constricted Consideration is given to ensure the workability when fitting the drain pipe 29 with a constant outer diameter of the discharge pipe 27 and the sealing performance between them. For this reason, the thickness of the discharge pipe 27 becomes thicker toward the base end side.
  • the outer peripheral portion of the discharge pipe 27 is subjected to a thinning process, thereby reducing the rigidity and weight of the discharge pipe 27. Is also achieved at the same time.
  • the shape and shape of the lightening formed on the outer periphery of the discharge pipe 27 is not limited. Moyo.
  • a plurality (four in the illustrated example) of locking claws 30 projecting outward in the radial direction upward are equidistantly spaced along the circumferential direction on the outer periphery of the lower part of the cover 22 which is a molded resin product. Formed.
  • a claw holder 31 having a frame shape that can be elastically deformed in the radial direction and capable of locking the locking claws 30 is provided on the outer periphery of the side wall portion 20a of the casing 20. Therefore, the locking claw 30 can be snapped to the claw holder 31 by pushing the cover 22 into the casing 20 with an upward force.
  • the casing 20 and the cover 22 can be integrated extremely easily, and the relative rotational position of the casing 20 relative to the cover 22 can be selected. That is, as shown by a two-dot chain line in FIG. 5, the direction of the discharge pipe 27 can be changed to any one of the four directions in accordance with the arrangement of other members.
  • the rotation of the cover 22 relative to the casing 20 can be restricted in a state where the locking claw 30 is locked to the claw holder 31. Therefore, as long as the claw holder 31 is slightly elastically deformed in the radial direction, the casing 20 and the claw holder 31 can be formed from a hard composite grease material mixed with glass fiber or inorganic whisker. 20 can be designed with high strength.
  • a plurality of (four in the illustrated example) connecting pins 32 projecting through the connecting portion l ib of the bracket 11 and the mounting flange 16a formed on the drive motor 16 are provided. It has been.
  • the forceps 32a formed at the upper end of the connecting pin 32 can utilize a technique such as ultrasonic welding, and the shape of the drive motor 16 and the bracket 11 is sufficient. It only has to be a shape that does not come off easily.
  • a boss portion 34 having a cylindrical cross section with its upper surface closed is formed upward, and a pair of spacers 35 having a semicircular arc shape surrounding the boss portion 34 are formed. Projected.
  • the boss 34 is located at the center of the hole 34a through which the spindle 16b of the drive motor 16 passes, and a plurality of bosses 34 are provided on the outer periphery of the boss 34 to maintain the inside of the pump chamber 21 at atmospheric pressure (four in the illustrated example). ) Slit 34b.
  • the upper end of the spacer 35 comes into contact with the connecting part l ib of the bracket 11.
  • a gap 35a between adjacent spacers 35 forms an air communication path together with a gap 22a having a pair of labyrinth structures formed on the outer peripheral edge of the cover 22.
  • the rotational phase between the gap 35a between the adjacent spacers 35 and the pair of gaps 22a formed at the outer peripheral edge of the cover 22 is shifted by approximately 90 degrees.
  • the air communication path that leads from the pump chamber 21 to the outside of the drainage pump unit 10 through the slit 34b and the gaps 35a and 22a can be greatly bent.
  • the slit 34b is formed in the boss portion 34 in the direction opposite to the rotation direction of the rotor 23 (left rotation direction in FIG. 7), that is, in the clockwise tangential direction in FIG. The amount of drainage overflowing from the slit 34b can be reduced.
  • a cylindrical partition wall 37 that forms an annular gap 36 with the side wall 20a of the casing 20 is a bottom wall of the casing 20. Projecting downwards toward part 20b. Therefore, the condensed water located at the upper peripheral edge of the pump chamber 21 flows downward due to the presence of the partition wall 37 and passes through the gap 38 between the lower end of the partition wall 37 and the bottom wall portion 20b of the casing 20 to form an annular shape. It is guided from the gap 36 into the discharge port 26. As a result, it is possible to prevent bubbles present on the upper peripheral edge of the pump chamber 21 from flowing into the discharge port 26 side.
  • the partition wall 37 in the present embodiment is for suppressing air bubbles present on the upper peripheral edge of the pump chamber 21 from flowing into the discharge port 26 side. It is necessary to form around the entire circumference Absent. However, when the partition wall 37 is formed only at a position facing the discharge port 26, the upstream side of the partition wall 37 from the discharge port 26 needs to be close to the inner peripheral surface of the side wall portion 20a of the casing 20. There is. Thereby, it is possible to prevent the condensed water containing bubbles flowing in the pump chamber 21 from directly flowing into the annular gap 36. Further, it is preferable that the lower end portion of the partition wall 37 is formed in a curved surface such as a semicircular shape so that the smooth flow of the condensed water is not hindered.
  • An O-ring 39 is mounted between the casing 20 and the partition wall 37 of the cover 22, and the fitting part force of the casing 20 and the cover 22 is also considered so that the condensed water does not leak outside. Yes.
  • the rotor 23 in the present embodiment includes a rotor shaft 40 having a cylindrical connection portion 40a to which the spindle 16b of the drive motor 16 is coupled at the upper end, and a plurality of radially extending projections (see FIG. In the example shown, there are four stays 41).
  • the rotor 23 includes an annular main plate 42 that is integrally connected to the rotor shaft 40 via a stage 41, and a surface of the main plate 42, that is, substantially parallel to the axis of the rotor shaft 40 from the upper surface side. And a number of pins 43 projecting from each other.
  • the rotor 23 is formed from the bottom end of the rotor shaft 40 and a large number of communication holes 44 that are formed on the front surface side and the back surface, that is, the lower surface side.
  • a stirring member 45 protruding along the axis of the rotor shaft 40 and located in the suction passage 24 is further provided.
  • the main plate 42 is concentric with the rotor shaft 40, and functions as a pressure equalizing portion of the present invention together with the communication hole 44 described above between the inner peripheral surface of the main plate 42 and the outer peripheral surface of the rotor shaft 40.
  • a void 46 is formed.
  • the stay 41 described above crosses the gap 46 and connects the rotor shaft 40 and the main plate 42.
  • four sets of the first array group A and the second array group B are alternately formed along the circumferential direction of the main plate 42.
  • the pins 43 and the communication holes 44 are alternately arranged in a first direction (in the left-right direction in FIG. 8) substantially along the circumferential direction of the main plate 42 and in a direction perpendicular thereto.
  • the pins 43 and the communication holes 44 are alternately arranged in a direction inclined by 45 degrees with respect to the first direction and in a direction perpendicular thereto.
  • Each pin 43 has a substantially square cross-section cut by a plane perpendicular to the axis of the rotor shaft 40. In order to minimize the watering noise, the square corners of the corners are rounded.
  • the stirring member 45 has four blades 45a whose cross-sectional shape perpendicular to the axis of the rotor shaft 40 has a cross shape.
  • the condensed water entering the pump chamber 21 is swirled at a higher speed by the main plate 42 and the pin 43 of the rotating rotor 23.
  • a part of the condensed water is discharged from the annular gap 36 to the discharge port 26 through the gap between the bottom wall portion 20b of the casing 20 and the lower end of the partition wall 37 of the cover 22.
  • new condensed water in the drain pan 28 is sucked into the suction passage 24, and the condensed water in the drain pan 28 is continuously discharged from the discharge port 26 to the outside through the drain pipe 29. .
  • the drainage height of the drainage pump unit 10 is also It is decided by itself.
  • the amount of drainage depends on the area of the pin 43 projected on a plane perpendicular to the rotation direction of the main plate 42.
  • the pin 43 of the rotor 23 rotates at a speed higher than the swirling speed of the condensed water. For this reason, the condensed water present in the surroundings is compared by rolling the outer periphery of the pin 43 when it is considered that the condensed water is swirling in the pump chamber 21 with respect to the stationary pin 43. It will be in a state where it flows smoothly backward.
  • a highly resistive vane plate having a wide surface substantially perpendicular to the rotation direction of the vane wheel is not used, so even the pin 43 located on the outermost peripheral side of the rotor 23 However, there is almost no cavitation behind the turning direction.
  • the flow direction of the condensed water formed by the first array group A of the pins 43 and the communication holes 44 is in the radial direction as shown in FIG. 11 schematically showing the flow state. Tilted almost 45 degrees Direction. This flow direction gives relatively large kinetic energy to the condensed water.
  • the flow direction of the condensed water formed by the second arrangement group B is substantially the circumferential direction of the main plate 42 as shown in FIG. 12, which schematically shows the flow state. On the other hand, it gives a relatively small kinetic energy. As a result, the defoaming effect can be further enhanced by the flow of these two types of condensed water.
  • the swirling circumferential speed of the condensed water in the suction pipe 25 is considerably slower than the swirling circumferential speed of the condensed water in the pump chamber 21, even if the stirring member 45 is the blade 45a having a large resistance, There is no such problem that a cavity is generated here.
  • the presence of the partition wall 37 formed on the cover 22 can prevent bubbles from being mixed into the condensed water discharged to the discharge port 26 side. it can. It is also possible to eliminate noise when bubbles are discharged to the discharge port 26 side.
  • FIGS. 13 and 14 show the planar shape and bottom shape of another embodiment of the rotor 23 according to the present invention, respectively. As shown in FIGS. 13 and 14, the outer peripheral surface of the main plate 42 can be formed into an irregular gear.
  • a pin 43 having an elliptical cross-sectional shape cut by a plane perpendicular to the axis of the rotor shaft 40 is adopted, and the major axis direction thereof is arranged along the circumferential direction of the main plate 42. It is also possible. In this case, the concave and convex portions formed on the outer peripheral surface of the main plate 42 enhance the stirring action on the condensed water and improve the capacity as a drainage pump.
  • elements having the same functions as those in the previous embodiment are denoted by the same reference numerals.
  • FIG. 15 shows a cross-sectional structure of the main part of another embodiment of the rotor 23 according to the present invention. As can be seen from FIG. 15, depending on the height of the swirling water surface of the condensate formed in the pump chamber 21 (indicated by a two-dot chain line in the figure).
  • the pin 43 closer to the rotor shaft 4027 can be formed in a tapered shape such that its taper angle ⁇ increases.
  • FIG. 18 shows a schematic structure of another embodiment of the drainage pump unit 10 according to the present invention in which the pin 43 protrudes downward from the back surface of the main plate 42.
  • the same reference numeral is used for this, and duplicate explanations are omitted.
  • the rotor 23 in the present embodiment is formed with a main plate 42 so as to be close to the bottom plate 33 of the cover 22, and the back surface force of the main plate 42 also has a large number of pins 43 protruding toward the bottom wall portion 20 b of the casing 20. .
  • the lower end of each pin 43 is closer to the bottom wall portion 20b of the casing 20 at approximately the same distance so that the pin 43 located on the radially inner side of the rotor 23 has a longer protruding length from the main plate 42. It is set.
  • a larger rectifying effect can be obtained for the condensed water sucked into the pump chamber 21 by the main plate 42 disposed in the vicinity of the bottom plate 33 of the cover 22.
  • a cylindrical portion 11 c surrounding the drive motor 16 is formed between the mounting portion 11 a of the bracket 11 and the connecting portion l ib, thereby transmitting the noise generated by the drive motor 16.
  • the direction can be regulated.
  • the pins 43 and the communication holes 44 can be randomly formed on the main plate 42 without being aligned as in the arrangement groups A and B as in the above-described embodiment. Alternatively, it is possible to cause the pin 43 to protrude on both sides of the main plate 42. In any case, it is desirable to appropriately adjust the quantity, layout, etc., in order to secure the required amount of drainage for the drainage pump unit 10 and reduce vibration and noise.
  • the main plate 42 may be formed in a conical shape so as to be parallel to the conical bottom wall portion 20b of the casing 20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Abstract

Dans une pompe conventionnelle d’évacuation d’eau assemblée dans un climatiseur, la rotation d’une roue de pales produit une cavitation qui entraîne un problème de bruit. Dans le cadre de l’invention, une pompe d’évacuation d’eau à arbre vertical possède un rotor (23), un carter (20), un couvercle (22) qui forme avec le carter (20) une chambre de pompe (21) hébergeant le rotor (23), un tuyau d’aspiration (25) formant un circuit d’aspiration (24) mis en communication avec une partie centrale d’extrémité basse de la chambre de pompe (21), et un orifice de refoulement (26) communiquant avec la chambre de pompe (21). Le rotor (23) possède un arbre rotor (40) connecté à sa section d’extrémité haute à un moteur (16), une plaque principale circulaire (42) reliée concentriquement et intégralement à l’arbre rotor (40), des goupilles (43) faisant saillie de la plaque principale (42) sensiblement en parallèle à l’axe de l’arbre rotor (40), et des sections exerçant une pression uniforme (44, 46) formées dans la plaque principale (42) et communiquant entre le côté de la surface avant et le côté de la surface arrière de la plaque principale (42).
PCT/JP2005/017641 2004-09-30 2005-09-26 Pompe centrifuge a arbre vertical, rotor pour la pompe et climatiseur WO2006035724A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006537728A JP4680922B2 (ja) 2004-09-30 2005-09-26 立軸形遠心ポンプおよびそのロータならびに空気調和装置

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Application Number Priority Date Filing Date Title
JP2004288850 2004-09-30
JP2004-288850 2004-09-30

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WO2006035724A1 true WO2006035724A1 (fr) 2006-04-06

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015055164A (ja) * 2013-09-10 2015-03-23 株式会社鷺宮製作所 ドレンポンプ
JP2018025188A (ja) * 2016-08-09 2018-02-15 合利美股▲分▼有限公司 空調装置の排水ポンプ

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5686827B2 (ja) * 2013-01-23 2015-03-18 株式会社鷺宮製作所 遠心ポンプ
WO2015000153A1 (fr) * 2013-07-03 2015-01-08 Li Lin Pompe à rotor conique
JP6381451B2 (ja) * 2015-01-17 2018-08-29 株式会社鷺宮製作所 遠心ポンプ
JP2017106388A (ja) * 2015-12-10 2017-06-15 株式会社鷺宮製作所 ポンプロータ、および、それを備える排水ポンプ
JP6882959B2 (ja) * 2017-08-30 2021-06-02 株式会社鷺宮製作所 排水ポンプ及び空気調和機
KR102405913B1 (ko) * 2021-10-15 2022-06-07 권진형 더미돌출부에 의해 케비테이션을 방지한 임펠러, 및 이를 구비한 펌프

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5110445B1 (fr) * 1970-03-03 1976-04-03
JPH08210289A (ja) * 1995-02-06 1996-08-20 Fuji Koki Seisakusho:Kk 排水ポンプ
JP2925076B2 (ja) * 1997-01-17 1999-07-26 太産工業株式会社 排水ポンプ
JP2004353492A (ja) * 2003-05-27 2004-12-16 Saginomiya Seisakusho Inc 立軸形遠心ポンプおよびポンプ用羽根車
JP2005188497A (ja) * 2003-12-05 2005-07-14 Daikin Ind Ltd ドレンポンプ及びそれを備えた空気調和装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4012667B2 (ja) * 2000-06-13 2007-11-21 日本電産サンキョー株式会社 ポンプ装置
JP3511044B2 (ja) * 2000-06-21 2004-03-29 株式会社鷺宮製作所 ドレン排水ポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5110445B1 (fr) * 1970-03-03 1976-04-03
JPH08210289A (ja) * 1995-02-06 1996-08-20 Fuji Koki Seisakusho:Kk 排水ポンプ
JP2925076B2 (ja) * 1997-01-17 1999-07-26 太産工業株式会社 排水ポンプ
JP2004353492A (ja) * 2003-05-27 2004-12-16 Saginomiya Seisakusho Inc 立軸形遠心ポンプおよびポンプ用羽根車
JP2005188497A (ja) * 2003-12-05 2005-07-14 Daikin Ind Ltd ドレンポンプ及びそれを備えた空気調和装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015055164A (ja) * 2013-09-10 2015-03-23 株式会社鷺宮製作所 ドレンポンプ
JP2018025188A (ja) * 2016-08-09 2018-02-15 合利美股▲分▼有限公司 空調装置の排水ポンプ

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CN100451342C (zh) 2009-01-14
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KR20070058489A (ko) 2007-06-08
KR100970822B1 (ko) 2010-07-16
CN101031723A (zh) 2007-09-05

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