WO2006035724A1

WO2006035724A1 - Vertical shaft centrifugal pump, rotor for the pump, and air conditioner

Info

Publication number: WO2006035724A1
Application number: PCT/JP2005/017641
Authority: WO
Inventors: Akinori Furukori; Masahiko Yoshida; Michiaki Ohno
Original assignee: Kabushiki Kaisha Saginomiya Seisakusho
Priority date: 2004-09-30
Filing date: 2005-09-26
Publication date: 2006-04-06
Also published as: JP4680922B2; KR20070058489A; JPWO2006035724A1; CN101031723A; CN100451342C; KR100970822B1

Abstract

In a conventional water discharge pump assembled in an air conditioner, the rotation of a blade wheel produces cavitation to cause a problem with quietness. A vertical shaft water discharge pump of the invention has a rotor (23), a casing (20), a cover (22) that forms, together with the casing (20), a pump chamber (21) in which the rotor (23) is received, a suction pipe (25) forming a suction path (24) communicating with a lower end central portion of the pump chamber (21), and a discharge port (26) communicating with the pump chamber (21). The rotor (23) has a rotor shaft (40) connected at its upper end section to a drive motor (16), a circular main plate (42) cocentrically integrally connected to the rotor shaft (40), pins (43) projecting from the main plate (42) substantially in parallel to the axis of the rotor shaft (40), and uniformly pressing sections (44, 46) formed in the main plate (42) and communicating between the front surface side and the back surface side of the main plate (42).

Description

Specification

Vertical shaft centrifugal pump and its rotor and air conditioner

Technical field

[0001] 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.

Background art

[0002] 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.

[0003] In an air conditioner, in-air condensed water generated during cooling operation is discharged to the outside of the room. Therefore, the condensed water is temporarily stored in a drain pan, and this force can also be discharged to the outside using a drain pump. Generally done.

[0004] As such drainage pumps, those disclosed in Patent Document 1 and Patent Document 2 are known. In the drainage pumps disclosed therein, an impeller is accommodated in a pump chamber surrounded by a cover and a casing, and a motor is connected to the impeller shaft of the impeller. By driving this motor, the impeller can be rotated in the pump chamber, and a liquid such as water intervening in the pump chamber can be rotated together with the impeller. That is, by rotating the liquid in the pump chamber together with the impeller, the liquid is discharged out of the pump chamber from the discharge pipe communicating with the outer peripheral portion of the pump chamber using the centrifugal force generated in the liquid. As the liquid is discharged from the pump chamber, the suction pipe force communicating with the center of the lower end of the pump chamber also draws new liquid into the pump chamber.

[0005] 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!

[0006] The blades disclosed in Patent Document 3 are basically the same as Patent Document 1 and Patent Document 2. In 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.

[0007] In recent years, there has been a demand for a reduction in operating noise in an air conditioner, and it is also possible to reduce the operating noise of a drainage pump incorporated in the air conditioner apparatus and various types of noise generated thereby. It is demanded. For example, even a slight hydraulic noise generated by the operation of a drain pump is problematic.

[0008] As is well known, 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.

[0009] 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. However, 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.

[0010] 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

Disclosure of the invention

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.

[0012] 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, wherein 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.

[0013] In the present invention, when the drive motor connected to the upper end of the rotor shaft is operated, the rotor rotates in the pump chamber in which liquid such as water is interposed. For this reason, as the pin that also projects the main plate force of the rotor rotates in the liquid, the liquid in the pump chamber gradually starts to rotate with the rotor due to its viscosity. In this way, a centrifugal force is generated accompanying the rotation of the liquid intervening in the pump chamber, and this centrifugal force deforms the surface of the liquid intervening in the pump chamber into a parabolic surface, so that the liquid can It is discharged to the discharge port communicating with the outer periphery. 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.

[0014] According to the vertical shaft centrifugal pump of the first aspect of the present invention, 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.

[0015] In the vertical shaft centrifugal pump according to the first aspect of the present invention, 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. When a stirring member protruding from one end of the rotor shaft along the axis of the rotor shaft is arranged in the suction passage of the suction pipe, the suction passage force can provide a swirling flow to the liquid sucked into the pump chamber, further increasing the pump efficiency. It becomes possible to improve.

[0016] 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. As a result, the air intervening in the pump chamber is prevented from flowing to the discharge port side, and noise generated when the bubbles move from the pump chamber to the discharge port can be eliminated.

[0017] It is also possible to form in the cover an atmosphere communication path that communicates between the pump chamber and the outside.

In this case, since 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.

[0018] 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. In this case, 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.

[0019] It is also effective to form a plurality of communication holes that connect the front surface side and the back surface side of the main plate, and to function these communication holes as a pressure equalizing portion, and to communicate bubbles that are interposed directly under the outer peripheral side of the back surface of the main plate. The hole can be prevented from escaping to the surface side and flowing into the discharge port side. In this case, 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.

[0020] The area of 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. As a result, noise can be suppressed by suppressing air entrainment around the pin located on the inner side in the radial direction. Also, 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. Further, 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. . Alternatively, 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.

[0021] As a cross-sectional shape of 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. In this case, 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.

[0022] As 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.

[0023] 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.

[0024] 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.

Brief Description of Drawings

[0025] [Fig. 1] 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] 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] 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

[0026] An embodiment in which a vertical shaft centrifugal pump according to the present invention is applied to a drainage pump unit incorporated in an air conditioner will be described in detail with reference to Figs. The present invention is not limited to these embodiments, and can be further combined with each other or can be modified or modified within the concept of the present invention described in the claims of this specification. Therefore, the present invention can naturally be applied to any other technology belonging to the spirit.

[0027] 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.

[0028] It should be noted that 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.

[0029] 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. In the present embodiment, 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.

In the present embodiment, 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.

[0031] In the present embodiment, 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. There is no problem. 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. Further, 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.

In the present embodiment, 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. However, in this embodiment, 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. As long as the ease of fitting and sealing of the drain pipe 29 to the discharge pipe 27 can be ensured, the shape and shape of the lightening formed on the outer periphery of the discharge pipe 27 is not limited. Moyo.

[0033] 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. For this reason, 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. In the present embodiment, by forming the claw holder 31 in a frame shape, 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.

[0034] On the outer periphery of the upper end of the cover 22, 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. By melting the upper end of the connecting pin 32 to form a force-applying portion 32a, the cover 22, the connecting portion ib of the bracket 11 and the drive motor 16 are integrally joined. 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.

[0035] At the center of the bottom plate 33 of the cover 22, 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. In the present embodiment, 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. As a result, 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. As a result, it is possible to obtain a great silencing effect against high-frequency (1000 Hz or higher) noise that occurs in the pump chamber 21 and has high straightness.

[0036] When the drive motor 16 is stopped, a part of the drainage that flows backward from the drain pipe 29 to the pump chamber 21 via the discharge port 26 may overflow from the slit 34b. However, in the present embodiment, 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.

[0037] At the outer peripheral edge of the bottom plate 33 of the cover 22 facing the pump chamber 21 side, 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. That is, 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.

[0038] 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.

[0039] 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. Further, 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.

[0040] 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. In the present embodiment, 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. In the first arrangement group A, 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 In the second arrangement group B, 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. Furthermore, 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.

[0041] When the drive motor 16 of the drainage pump unit 10 having such a configuration starts to operate, the condensed water intervening in the suction passage 24 is stirred by the rotation of the stirring member 45, and gradually the stirring member due to its viscosity. Begins swirling in suction passage 24 with 45. The centrifugal force generated with the swirling of the condensed water in the suction passage 24 causes the water surface to draw a concave three-dimensional parabolic curved surface, and passes over the upper end of the suction passage 24 to the bottom wall portion 20b of the pump chamber 21. Then, the main plate 42 and the pin 43 are immersed in the condensed water. In this way, 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. As the condensed water is discharged, 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. . In this case, since the pressure difference between the radial center side of the rotor 23 and the radial outer end is determined by the rotational speed of the rotor 23 and its maximum diameter, that is, the outer diameter of the main plate 42, the drainage height of the drainage pump unit 10 is also It is decided by itself. However, 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.

[0042] During the operation of the drainage pump unit 10, 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. In other words, unlike the conventional case, 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. As a result, it is possible to greatly reduce the noise caused by the cavity. In particular, in this embodiment, 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. On the other hand, 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. Further, since 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. In addition, even when the drain pump unit 10 is started and at the low head, 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.

[0043] It is necessary to make the outer periphery of the main plate 42 into a complete circle centered on the axis of the rotor shaft 40. The cross-sectional shape of the pin 43 cut along a plane perpendicular to the axis of the rotor shaft 40 is the above-described implementation. Various shapes other than the substantially square shape can be adopted. For example, 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. Alternatively, 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. In FIGS. 13 and 14, elements having the same functions as those in the previous embodiment are denoted by the same reference numerals.

In the embodiment described above, the height of each pin 43 is set so that the upper end of each pin 43 is positioned on the same horizontal plane. For this reason, the water level of the condensed water in the pump chamber 21 is displaced in a mortar shape while the rotor 23 is rotating, and the upper surface of the pin 43 on the inner peripheral side close to the rotor shaft 40 also exposes the water surface force to stir the condensed water. become unable. Therefore, 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). Therefore, it is effective to set the height of the pin 43 farther from the rotor shaft 40 to the maximum so that the function of the pins 43 arranged in the radial direction can be maximized. Alternatively, in order to obtain the same effect, the area of the pin 43 projected onto the plane perpendicular to the rotation direction of the main plate 42 is set to be as small as the pin 43 positioned radially inward of the rotor shaft 40. Can also be dealt with. Specifically, for example, as shown in FIG. 16, the pin 43 closer to the rotor shaft 4027 can be formed in a tapered shape such that its taper angle Θ increases.

In the embodiment described above, the pin 43 protrudes upward from the front surface side of the main plate 42, but the back surface force of the main plate 42 may also protrude downward as shown in FIG. In the case of the rotor 23 shown in FIG. 17, a pin 43 closer to the rotor shaft 40 is formed with a step having a small diameter portion 43a on the lower end side so that the outer diameter becomes smaller. Thus, 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. That is, 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. In the case of the present embodiment, 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. In the present embodiment, 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.

Note that 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. Similarly, 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.

Claims

The scope of the claims

[1] A rotor, a casing, a cover that is attached to the casing and forms a pump chamber in which the rotor is accommodated, and a casing that protrudes from the casing and is provided at the center of the lower end of the pump chamber. A vertical shaft centrifugal pump having a suction pipe that forms a suction passage that communicates with a discharge port that is formed in the casing and communicates with the pump chamber, wherein the rotor is

A rotor shaft whose upper end is connected to the external force drive motor of the cover;

A main plate concentrically connected to the rotor shaft integrally;

The main plate force, a plurality of pins projecting substantially parallel to the axis of the rotor shaft, and a pressure equalizing portion communicating with the front side and the back side of the main plate

Vertical shaft centrifugal pump characterized by

[2] The rotor is further provided with a stirring member that protrudes from one end of the rotor shaft along the axis of the rotor shaft and is located in the suction passage of the suction pipe. The vertical shaft centrifugal pump according to 1.

[3] The cover according to claim 1 or 2, wherein the cover has a partition wall that protrudes downward so as to surround the rotor and forms an annular gap with the inner wall of the casing. Vertical shaft centrifugal pump described in 1.

4. The vertical shaft centrifugal pump according to claim 3, wherein the partition wall is arranged to face and block a discharge port formed in the casing.

[5] The vertical shaft centrifugal pump according to any one of claims 1 to 4, wherein the cover is formed with an air communication path communicating the pump chamber with the outside.

[6] The apparatus according to any one of claims 1 to 5, wherein the main plate includes a plurality of communication holes that communicate between the front surface side and the back surface side, and the communication holes function as the pressure equalizing portion. Vertical shaft centrifugal pump as described.

7. The vertical shaft centrifugal pump according to claim 6, wherein in the pin and the communication hole, the first array group and the second array group are alternately arranged along the circumferential direction. .

[8] In the first arrangement group, the pins and the communication holes are arranged in a first direction substantially along a circumferential direction of the main plate and in a direction perpendicular thereto, and the second arrangement group is 8. The vertical shaft centrifugal pump according to claim 7, wherein the pin and the communication hole are arranged in a direction inclined by 45 degrees with respect to the first direction and in a direction perpendicular thereto.

[9] The area of each of the pins projected on a plane perpendicular to the turning direction of the main plate is set to be smaller as the pins located on the radially inner side of the rotor shaft. The vertical shaft centrifugal pump according to claim 8.

[10] rotor shaft,

A main plate concentrically connected to the rotor shaft integrally;

A pump rotor characterized by comprising:

11. The pump rotor according to claim 10, further comprising a stirring member protruding along the axis of the rotor shaft.

[12] The pump according to claim 10 or 11, comprising a plurality of communication holes communicating the front surface side and the back surface side of the main plate, and these communication holes function as the pressure equalizing section. Rotor.

13. The pump rotor according to claim 12, wherein in the pin and the communication hole, the first array group and the second array group are alternately arranged along the circumferential direction.

[14] In the first arrangement group, the pins and the communication holes are arranged in a first direction substantially along a circumferential direction of the main plate and in a direction orthogonal thereto, and the second arrangement group includes the second arrangement group, 14. The pump rotor according to claim 13, wherein the pin and the communication hole are arranged in a direction inclined by 45 degrees with respect to the first direction and in a direction perpendicular thereto.

[15] The area of each of the pins projected on a plane perpendicular to the rotation direction of the rotor shaft is set to be smaller as the pin located on the radially inner side of the rotor shaft. Item 15. The pump rotor according to any one of Items 10 to 14.

[16] An air conditioner characterized in that the vertical shaft centrifugal pump according to any one of claims 1 to 9 is incorporated as a drainage pump!