US20110182734A1 - Centrifugal pump impeller - Google Patents
Centrifugal pump impeller Download PDFInfo
- Publication number
- US20110182734A1 US20110182734A1 US13/002,072 US200913002072A US2011182734A1 US 20110182734 A1 US20110182734 A1 US 20110182734A1 US 200913002072 A US200913002072 A US 200913002072A US 2011182734 A1 US2011182734 A1 US 2011182734A1
- Authority
- US
- United States
- Prior art keywords
- section
- impeller body
- lid
- balance weight
- impeller
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
- 230000002787 reinforcement Effects 0.000 claims description 22
- 210000000078 claw Anatomy 0.000 claims description 15
- 239000003921 oil Substances 0.000 description 16
- 238000000034 method Methods 0.000 description 10
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 238000013016 damping Methods 0.000 description 4
- 229920005989 resin Polymers 0.000 description 4
- 239000011347 resin Substances 0.000 description 4
- 229920003002 synthetic resin Polymers 0.000 description 4
- 239000000057 synthetic resin Substances 0.000 description 4
- 239000007769 metal material Substances 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
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
- F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
- F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
-
- 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
- F04D29/2238—Special flow patterns
- F04D29/225—Channel wheels, e.g. one blade or one flow channel
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid 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
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/662—Balancing of rotors
Definitions
- a technique disclosed herein relates to a centrifugal pump impeller.
- a centrifugal pump has been used for delivering, e.g., drainage.
- a non-clog impeller in which a flow path connecting between an inlet opening through a first end surface and an outlet opening through a circumferential surface is formed has been known as an impeller in which it is less likely to cause clogging of, e.g., drainage containing solid substances such as impurities (see, e.g., Patent Document 1).
- the non-clog impeller has a single vane, and therefore is formed in non-symmetric shape about a rotation axis.
- a part of the impeller disclosed in Patent Document 1 is removed in order to achieve static balance at rest and dynamic balance during rotation in air (hereinafter collectively referred to as “mechanical balance”).
- mechanical balance In a second end surface of the substantially cylindrical impeller, which is on an opposite side to the first end surface in which the inlet is formed, such removal allows formation of a recessed section which opens through the second end surface, and which is recessed in a cylindrical axis direction in the second end surface.
- a recessed section which opens through a second end surface, and which is recessed in a cylindrical axis direction in the second end surface may be formed in order to reduce or prevent shrinkage caused when forming the impeller due to the substantially constant thickness of the impeller.
- PATENT DOCUMENT 1 Japanese Patent Publication No. 2006-291937
- centrifugal pump impeller disclosed herein is an advantageous impeller for simplifying an attachment structure of a lid attached to an impeller body, and simplifying an assembly process.
- Inventors of the present invention have focused on an engagement structure between an impeller body and a lid; and have arrived at a configuration in which an engagement between the impeller body and the lid is facilitated through an engagement section, and a balance weight is sandwiched between the lid engaged with the impeller body and the impeller body to fix the balance weight to the impeller body.
- An example of a centrifugal pump impeller includes an impeller body having a substantially cylindrical shape with first and second end surfaces facing each other in a cylindrical axis direction, and with a circumferential surface interposed between the first and second end surfaces; and including an internal flow path which connects between an inlet opening in the first end surface and an outlet opening in the circumferential surface, and a recessed section which opens in the second end surface, and which is recessed in the cylindrical axis direction in the second end surface; a lid which is attached to the second end surface of the impeller body, and which covers the opening of the recessed section so that the second end surface of the impeller body defines a flat surface; and a balance weight arranged between the impeller body and the lid.
- the lid is attached and fixed to the impeller body through an engagement section, and holding sections of the balance weight are formed in a back-side surface.
- the balance weight is sandwiched between the holding section of the lid and the impeller body, and is fixed by the holding section of the lid and the impeller body.
- the lid is attached and fixed to the impeller body through the engagement section.
- the balance weight is sandwiched between the holding section of the lid and the impeller body, and then the balance weight is attached and fixed to the impeller body. That is, the lid and the balance weight are simultaneously attached to the impeller body, thereby simplifying an assembly process of the impeller.
- FIG. 1 is a cross-sectional view of a submersible pump including a centrifugal pump impeller which is illustrated as an example.
- FIG. 2 is a perspective view of the impeller.
- FIG. 3 is a front view of the impeller.
- FIG. 4 is a bottom view of the impeller.
- FIG. 5 is a V-V cross-sectional view of FIG. 4 .
- FIG. 6 is a plan view of an impeller body in a state in which a lid is removed.
- FIG. 7 is a view illustrating a back-side surface of the lid.
- FIG. 8 is a VIII-VIII cross-sectional view of FIG. 7 .
- FIG. 9 is an enlarged plan view around a boss section of the impeller body.
- FIG. 10 is an enlarged cross-sectional view around the boss section of the impeller body.
- FIG. 11 is a perspective view of an upper balance weight.
- FIG. 12 is a perspective view of a lower balance weight.
- An example of a centrifugal pump impeller includes an impeller body having a substantially cylindrical shape with first and second end surfaces facing each other in a cylindrical axis direction, and with a circumferential surface interposed between the first and second end surfaces; and including an internal flow path which connects between an inlet opening in the first end surface and an outlet opening in the circumferential surface, and a recessed section which opens in the second end surface, and which is recessed in the cylindrical axis direction in the second end surface; a lid which is attached to the second end surface of the impeller body, and which covers the opening of the recessed section so that the second end surface of the impeller body defines a flat surface; and a balance weight arranged between the impeller body and the lid.
- the lid is attached and fixed to the impeller body through an engagement section, and holding sections of the balance weight are formed in a back-side surface.
- the balance weight is sandwiched between the holding section of the lid and the impeller body, and is fixed by the holding section of the lid and the impeller body.
- the lid is attached and fixed to the impeller body through the engagement section, thereby sandwiching the balance weight between the holding section of the lid and the impeller body. Consequently, the balance weight is attached and fixed to the impeller body. As described above, the lid and the balance weight are simultaneously attached to the impeller body, thereby facilitating an assembly process of the impeller.
- the engagement section may include engagement grooves formed in the impeller body or the lid; and engagement claws which are formed in the lid or the impeller body, and which are engaged with the engagement grooves by elastically deforming when attaching the lid to the impeller body.
- the engagement groove and the engagement claw can be engaged with each other without using, e.g., tools.
- the tools etc. are not required when attaching the lid to the impeller body, thereby further simplifying the assembly process of the impeller.
- a plurality of pins may be formed so as to protrude from the back-side surface of the lid; and a plurality of pinholes into which the pins are fitted may be formed so as to open through the second end surface of the impeller body.
- Positions of the pin and the pinhole are adjusted to each other, and the position of the lid is determined on the impeller body.
- the fitting of the pin into the pinhole allows the lid to be more firmly fixed to the impeller body.
- Each of the pinholes may be formed in a boss section provided in the second end surface of the impeller body.
- a plurality of protrusions may be formed with spacing in a circumferential direction in a circumferential surface of the boss section.
- Fitting holes which have a larger diameter than that of the boss section, and which have a smaller diameter than that of a circle defined by connecting tip ends of the plurality of protrusions may be formed in the balance weight; and, in order to fix the balance weight to the impeller body, the fitting holes of the balance weight may be fitted onto the boss sections with the protrusions being pressed against the boss sections.
- the holding section of the lid is formed in circular shape so as to surround the pin, and holds the balance weight in a section around the fitting hole.
- the fitting hole of the balance weight is fitted onto the boss section of the impeller body, and therefore the balance weight can be correctly positioned on a predetermined section of the impeller body.
- the fitting hole of the balance weight is fitted onto the boss section of the impeller body, and the holding section of the lid presses against the section around the fitting hole. This reduces or prevents occurrence of rattling of the balance weight, and firmly fixes the balance weight to the impeller body.
- a plurality of reinforcement ribs extending in a radial direction may be formed inside the recessed section of the impeller body, and an end surface of the reinforcement rib in the cylindrical axis direction may be a mounting surface on which the balance weight is mounted.
- the boss section may be integrally formed with the reinforcement rib in the mounting surface of the reinforcement rib.
- the reinforcement rib improves a strength of the impeller body.
- the boss section is integrally formed with the reinforcement rib, thereby improving stiffness of the boss section.
- the balance weight is more stably fixed to the impeller body.
- FIG. 1 illustrates a submersible pump 1 including an impeller which is illustrated as an example.
- the submersible pump 1 includes a pump section 21 with an impeller 6 , and a motor section 22 with a motor 3 for driving the impeller 6 .
- the pump section 21 is arranged below an oil casing 23
- the motor section 22 is arranged above the oil casing 23 . That is, the pump section 21 and the motor section 22 are arranged one above the other.
- the submersible pump 1 is a lightweight pump in which a head cover 34 and a pump casing 4 which will be described later are made of predetermined resin material.
- the motor section 22 includes the motor 3 with a stator 31 and a rotor 32 ; a stator casing 33 covering the stator 31 of the motor 3 ; and the head cover 34 attached to an upper end of the stator casing 33 .
- a rotating shaft 35 of the motor 3 vertically extends.
- the stator casing 33 is formed in substantially cylindrical shape with upper and lower openings.
- the upper opening of the stator casing 33 is closed with a motor cover 36 , and a bearing 35 a rotatably supporting an upper end section of the rotating shaft 35 is provided on a lower surface of the motor cover 36 .
- the head cover 34 is attached to the upper end of the stator casing 33 .
- the head cover 34 has an upper wall and a circumferential wall which downwardly extends from a circumferential section of the upper wall, and which is fixed to an upper end section of the stator casing 33 .
- the head cover 34 has an inverted U-shaped cross section.
- the head cover 34 and the motor cover 36 defines a housing space 34 a in which various electric components are housed.
- a cable boot into which a power feeding cable for feeding power to the motor 3 is inserted is attached so as to pass through the upper wall of the head cover 34 , and a handle 34 b is attached to a center section of an upper surface of the upper wall.
- the head cover 34 is fixed to the oil casing 23 with a plurality of bolts 37 (only one bolt is illustrated in the figure) arranged at predetermined interval in the circumferential direction. That is, the bolt 37 inserted into a through-hole formed in a circumferential section of the head cover 34 passes through the motor cover 36 . Then, the bolt 37 downwardly extends along an inner circumferential surface of the stator casing 33 , and is screwed into a circumferential section of the oil casing 23 . In such a manner, in the submersible pump 1 , the long vertically-extending bolt 37 fixes the head cover 34 , the stator casing 33 , and the motor cover 36 to the oil casing 23 at one time. Such a configuration allows reduction in the number of components and the number of assembly steps of the submersible pump 1 .
- the oil casing 23 is attached to a lower end of the stator casing 33 , and the lower opening of the stator casing 33 is closed with the oil casing 23 .
- the pump casing 4 is attached to a lower side of the oil casing 23 , and therefore the oil casing 23 and the pump casing 4 define an oil chamber 53 filled with lubricating oil.
- a through-hole into which the rotating shaft 35 of the motor 3 is inserted is formed in the oil casing 23 , and a bearing 35 b rotatably supporting a middle section of the rotating shaft 35 is attached to an upper surface of the oil casing 23 .
- the rotating shaft 35 is sealed by a mechanical seal 51 , and a circular wall 52 is provided, which surround a substantially entire outer circumferential section of the mechanical seal 51 .
- the pump section 21 includes the impeller 6 attached to a lower end of the rotating shaft 35 of the motor 3 , and the pump casing 4 .
- the submersible pump 1 is a centrifugal pump.
- a first pump casing 41 on an upper side, which defines the oil chamber 53 together with the oil casing 23 , and a second pump casing 42 on a lower side are integrated by welding, thereby forming the pump casing 4 .
- the first pump casing 41 and the second pump casing 42 are integrated by welding as described above, and therefore a flange is not required, which is required, e.g., when integrating two pump casings with a bolt-nut fastening means. Consequently, the size of the submersible pump 1 is reduced.
- a through-hole into which the rotating shaft 35 is inserted is formed in an upper section of the pump casing 4 , and a volute chamber 43 in which the impeller 6 is housed is formed inside the pump casing 4 .
- the pump casing 4 has a lower opening, and a liner ring 44 with an opening 44 a, which supports a wear ring section 692 which is a lower end section of the impeller 6 is attached to such an opening.
- a discharge section 45 which laterally protrudes, and which is upwardly curved is integrally formed with a side section of the pump casing 4 .
- the discharge section 45 communicates with the volute chamber 43 , and has a discharge port 45 a with an upper opening.
- the discharge port 45 a is connected to an outlet pipe which is not shown in the figure.
- the seat 7 includes a body section 71 made of synthetic resin; and a cover 72 which covers a lower side of the body section 71 , and which is made of rubber. Inserting sections 73 into which the lower ends of the legs 46 are inserted, and in which the lower ends of the legs 46 are fastened with screws are integrally formed with the body section 71 so as to upwardly protrude.
- a damping rubber member or damping steel plate 74 is interposed between a lower surface of the leg 46 and the inserting section 73 .
- the seat 7 functions to reduce or prevent displacement of a position where the submersible pump 1 is arranged due to the cover 72 , and to control vibration by the damping rubber member or damping steel plate 74 when driving the submersible pump 1 .
- the impeller 6 is a non-clog impeller having a substantially cylindrical shape, and is fixed to the lower end of the rotating shaft 35 so that a cylindrical axis of the impeller 6 is coaxial to the rotating shaft 35 (see FIG. 1 ).
- the impeller 6 includes an impeller body 61 , and a lid 62 attached to an upper end surface of the impeller body 61 .
- the impeller 6 also includes an upper balance weight 63 and a lower balance weight 64 .
- the upper balance weight 63 is arranged and fixed between the impeller body 61 and the lid 62
- the lower balance weight 64 is embedded in the wear ring section 692 of the impeller body 61 as illustrated in FIG. 5 .
- the impeller body 61 has a substantially cylindrical shape.
- An inlet 601 opening at the bottom of the impeller body 61 is formed in a lower end surface of the impeller body 61 , and an outlet 602 opening through a side of the impeller body 61 is formed in a predetermined section of a circumferential surface of the impeller body 61 .
- An internal flow path 603 extending in the cylindrical axis direction is formed inside the impeller 6 , and the internal flow path 603 connects between the inlet 601 and the outlet 602 .
- An external flow path 604 inwardly recessed in the radial direction is formed in an outer circumferential surface of the impeller body 61 .
- the external flow path 604 is not a flow path extending in the cylindrical axis direction, and the center of the flow path is positioned on a plane perpendicular to the cylindrical axis of the impeller body 61 .
- the external flow path 604 reaches a downstream side of the internal flow path 603 at the outlet 602 , and extends across a substantially entire perimeter of the impeller 6 .
- the external flow path 604 is defined by a vane 605 .
- the vane 605 is a so-called “single radial-flow vane (centrifugal vane), and the centrifugal vane 605 increases the pressure of water in the external flow path 604 , and then discharges such water to an outer circumferential side (outer side in the radial direction).
- a first flange section 681 outwardly protruding in the radial direction around an entire circumference is formed above the external flow path 604 of the impeller body 61 .
- a second flange section 682 outwardly protruding in the radial direction around the entire circumference is also formed below the external flow path 604 .
- the second flange section 682 horizontally divides the impeller 6 into a lower section where the inlet 601 is formed, and an upper section where the outlet 602 is formed. That is, the impeller 6 is a closed-type impeller in which the second flange section 682 divides between the inlet 601 and the outlet 602 .
- a shaft support section 691 is formed so as to upwardly protrude in the center of the upper end surface of the impeller body 61 , which is above the first flange section 681 .
- the shaft support section 691 is made of predetermined metal material, and is provided with an attachment hole into which the rotating shaft 35 of the motor 3 is inserted to be fixed.
- the downwardly-protruding wear ring section 692 inserted into the opening 44 a of the pump casing 4 is formed below the second flange section 682 of the impeller body 61 .
- the first and second flange sections 681 and 682 are set to a smaller diameter so that the diameter of the impeller body 61 becomes as small as possible.
- the impeller body 61 is designed with almost no step between the second flange section 682 and the wear ring section 692 .
- the diameters of the first and second flange sections 681 and 682 may be further reduced in order to, e.g., eliminate such a step.
- the diameter of the wear ring section 692 is increased so that the diameter of the inlet 601 is increased, thereby eliminating the step between the second flange section 682 and the wear ring section 692 .
- the impeller body 61 is made of synthetic resin. As illustrated in FIGS. 5 and 6 , a recessed section 611 recessed in the cylindrical axis direction in the upper end surface of the impeller body 61 is formed in order to reduce or prevent shrinkage caused when forming the impeller due to the substantially constant thickness of the impeller. As illustrated in FIG. 6 , the recessed section 611 extends substantially three-fourths of the entire perimeter from an opening side of the outlet 602 (upper side as viewed in FIG. 6 ), in the counterclockwise and circumferential directions. In addition, as illustrated in FIG. 5 , the recessed section 611 is formed so that the depth is relatively shallow on the opening side of the outlet 602 (right side as viewed in FIG. 5 ), and the depth is relatively deep on a side opposite to the opening side of the outlet 602 (left side as viewed in FIG. 5 ).
- Reinforcement ribs 612 extending in the radial direction, and connecting between the shaft support section 691 and a circumferential section of the impeller body 61 are formed in an upper end section of the impeller body 61 .
- three reinforcement ribs 612 are formed at predetermined angles in an upper half region corresponding to the opening side of the outlet 602 , and a single reinforcement rib 612 is formed in a lower half region corresponding to the side opposite to the opening side of the outlet 602 .
- Three of the four reinforcement ribs 612 are arranged inside the recessed section 611 . As illustrated in, e.g., FIG.
- the three reinforcement ribs 612 arranged on the opening side of the outlet 602 are also used as a mounting section on which the upper balance weight 63 is mounted. That is, an upper end surface of each of the reinforcement ribs 612 serves as a mounting surface 614 on which the upper balance weight 63 is mounted. Further, a boss section 613 for fixing the upper balance weight 63 is formed in the substantially center of the reinforcement rib 612 in the radial direction.
- the boss section 613 is formed in circular shape as viewed in plan, which has a diameter larger than the width of the reinforcement rib 612 .
- An upwardly-opening pinhole 615 which extends in the cylindrical axis direction is formed in the center of the boss section 613 .
- three protrusions 616 outwardly protruding in the radial direction are integrally formed with the boss section 613 at equal interval in the circumferential direction.
- the upper balance weight 63 made of predetermined metal material is formed in substantially fan-like shape by cutting a section corresponding to a predetermined angular range from an annular disk-like member having a predetermined thickness.
- the upper balance weight 63 has a flattened shape in which the width of the upper balance weight 63 in the radial direction is larger than the thickness of the upper balance weight 63 in the cylindrical axis direction (vertical direction).
- the upper balance weight 63 is arranged between the shaft support section 691 and the circumferential section of the impeller body 61 .
- the inner diameter of the upper balance weight 63 is set so as to be larger than the diameter of the shaft support section 691
- the outer diameter of the upper balance weight 63 is set so as to be smaller than the diameter of the circumferential section of the impeller body 61 .
- the shape of the upper balance weight 63 is not limited, and may be suitably set so that a required weight can be ensured under a condition where the upper balance weight 63 is arranged between the impeller body 61 and the lid 62 .
- three holes 631 passing through the upper balance weight 63 in a thickness direction are formed corresponding to the three boss sections 613 . Each of such holes is a fitting hole 631 fitted onto the boss section 613 .
- the diameter of such a hole is set so as to be larger than that of the boss section 613 , and to be smaller than that of a circle defined by connecting tip ends of the protrusions 616 .
- the upper balance weight 63 is mounted on the mounting surface 614 of the reinforcement rib 612 so that each of the fitting holes 631 is fitted onto the boss section 613 .
- the upper balance weight 63 is positioned in a predetermined section of the upper end surface of the impeller body 61 on the opening side of the outlet 602 .
- the fitting hole 631 of the upper balance weight 63 is set so as to have the diameter larger than that of the boss section 613 , and smaller than that of the circle defined by connecting the tip ends of the protrusions 616 .
- a part of the protrusions 616 is pressed against the boss section 613 , thereby fitting the fitting hole onto the boss section 613 . This reduces the rattling of the upper balance weight 63 .
- the lid 62 has a circular disk-like shape, and a through-hole 621 into which the shaft support section 691 of the impeller body 61 is inserted is formed in the center of the lid 62 .
- the lid 62 is made of synthetic rein.
- a front-side surface of the lid 62 is flat.
- two engagement claws 622 are integrally formed with the lid 62 at predetermined interval in the circumferential direction.
- the engagement claw 622 is a claw to be engaged with an engagement groove 683 formed at a circumference of the upper end section of the impeller body 61 , and the engagement claw 622 and the engagement groove 683 serve as an engagement means for attaching and fixing the lid 62 to the impeller body 61 .
- each of the pins 623 is fitted into the pinhole 615 formed in the boss section 613 .
- the fitting of the pin 623 into the pinhole 615 allows the lid 62 to be more stably attached and fixed to the impeller body 61 .
- Holding sections 624 for holding the upper balance weight 63 are further formed so as to protrude from the back-side surface of the lid 62 .
- the holding section 624 is formed in circular shape so as to surround the pin 623 . As illustrated in FIG. 10 , when attaching and fixing the lid 62 to the impeller body 61 , a lower surface of the holding section 624 downwardly presses against an upper surface of the upper balance weight 63 around the boss section 613 . Thus, the upper balance weight 63 is sandwiched between the lid 62 and the impeller body 61 .
- two through-holes 625 are formed on each of the opening side of the outlet 602 and its opposite side.
- Such through-holes are air vent holes 625 through which air is vented from the recessed section 611 of the impeller body 61 to fill the recessed section 611 with water.
- Air vent holes may be formed in the upper balance weight 63 . In such a case, such air vent holes are desirably formed in the same positions as those of the air vent holes 625 formed in the lid 62 .
- the air vent holes 625 are provided in the lid 62 to fill the recessed section 611 with water as described above. Thus, this reduces or prevents a loss of mechanical balance of the impeller 6 due to remaining air in the recessed section 611 , and reduces occurrence of vibration when driving the impeller 6 .
- the lower balance weight 64 is embedded in the wear ring section 692 on the opening side of the outlet 602 of the impeller body 61 .
- the lower balance weight 64 made of predetermined metal material is a plate curved in arc, and has a vertically-elongated shape in which a height in the cylindrical axis direction is larger than a thickness in the radial direction.
- the lower balance weight 64 is embedded in the wear ring section 692 so that a lower end surface of the lower balance weight 64 is exposed in the lower end surface of the impeller body 61 .
- Two through-holes 641 are formed in predetermined positions of the lower balance weight 64 , and each through-hole 641 serves as a positioning hole into which a positioning pin 8 of a mold is inserted.
- a notch 642 is formed in a center section of a lower end of the lower balance weight 64 .
- the shaft support section 691 and the lower balance weight 64 are arranged in predetermined positions inside the mold (not shown in the figure).
- a position of the lower balance weight 64 in the circumferential direction, and an inclination of the lower balance weight 64 are determined by the two positioning pins 8 as illustrated in FIG. 12 .
- the positioning pin 8 includes a small-diameter section 81 on a tip end side, and a large-diameter section 82 on a base end side.
- a position of the lower balance weight 64 in the radial direction is also determined by a position of a step defined by such sections having the different diameters. In such a manner, the lower balance weight 64 can be accurately positioned in a predetermined section inside the mold, thereby ensuring the lower balance weight 64 embedded in the thin wear ring section 692 of the impeller body 61 .
- the impeller body 61 is formed by a well-known resin molding. As illustrated in FIGS. 2 and 3 , holes 693 are formed in the wear ring section 692 of the molded impeller body 61 by the positioning pins 8 .
- the separately-prepared upper balance weight 63 is attached to the upper end surface of the molded impeller body 61 .
- the fitting hole 631 of the upper balance weight 63 is fitted onto the boss section 613 with the protrusions 616 of the boss section 613 being pressed against the fitting hole 631 .
- the separately-molded lid 62 is attached to the impeller body 61 .
- the pin 623 of the lid 62 is fitted into the pinhole 615 of the impeller body 61 , and the engagement claw 622 of the lid 62 is elastically deformed to be engaged with the engagement groove 683 of the impeller body 61 .
- the holding sections 624 of the lid 62 press against the upper balance weight 63 .
- attachment of the upper balance weight 63 to the impeller body 61 is completed.
- the fastening means such as bolts is not used to fix the lid 62 to the impeller body 61 , and the engagement claws 622 are engaged with the engagement grooves 683 to attach and fix the lid 62 to the impeller body 61 .
- tools etc. are not required for the assembly process, and the assembly of the impeller 6 is simplified.
- the upper balance weight 63 is fixed to the impeller body 61 . Consequently, the assembly process of the impeller 6 is further facilitated.
- the engagement claws 622 are provided in the lid 62 , and the engagement grooves 683 opening toward outside are provided in the circumferential section of the impeller body 61 .
- the engagement sections are not protrude from the front-side surface of the lid 62 , thereby ensuring the flat surface at the upper end of the impeller 6 . This is advantageous to reduce a power loss.
- engagement grooves may be provided in the lid 62
- engagement claws may be provided in the impeller body 61 .
- the engagement section where the lid 62 is engaged with the impeller body 61 is not limited to the combination of the engagement claw 622 and the engagement groove 683 , and any configuration may be employed.
- the circumferential section of the lid 62 is fixed to the impeller body 61 by the engagement claws 622 and the engagement grooves 683 , and the pins 623 provided in the lid 62 are fitted into the pinholes 615 of the impeller body 61 .
- an inner section of the lid 62 in the radial direction can be fixed to the impeller body 61 . Consequently, the inner section of the lid 62 in the radial direction is not apart from the impeller body 61 .
- the fitting hole 631 of the upper balance weight 63 is fitted onto the boss section 613 of the impeller body 61 .
- the upper balance weight 63 can be correctly positioned on the predetermined section of the impeller body 61 , and the occurrence of the rattling of the upper balance weight 63 can be reduced or prevented.
- the reinforcement rib 612 improves the strength of the impeller body 61 itself.
- the upper balance weight 63 and the boss section 613 used for the fixing of the lid are integrally formed with the reinforcement rib 612 , thereby improving the stiffness of the boss section 613 . This is advantageous to more stably fix the upper balance weight 63 and the lid 62 to the impeller body 61 .
- the lower balance weight 64 has the vertically-elongated shape, thereby embedding the lower balance weight 64 in the wear ring section 692 which is thin in the radial direction.
- the lower balance weight 64 is embedded in the impeller body 61 , and therefore it is not necessary to attach the balance weight to the second flange section 682 .
- This allows the diameter of the inlet 601 of the impeller 6 to be as large as possible, thereby ensuring predetermined substance passage properties.
- the diameters of the first and second flange sections 681 and 682 become as small as possible in order to reduce the diameter of the impeller 6 , thereby reducing the power of the submersible pump 1 .
- the retaining section 694 is configured by forming the notch 642 at the lower end of the lower balance weight 64 , thereby reducing or preventing the disengagement of the lower balance weight 64 .
- the retaining section 694 is configured by forming the notch 642 at the lower end of the lower balance weight 64 .
- a through-hole passing through the lower balance weight 64 in the thickness direction may be formed in, e.g., a middle section of the lower balance weight 64 in the height direction, thereby forming a resin retaining section crossing the lower balance weight 64 in the thickness direction.
- the entire lower balance weight 64 may be embedded in the impeller body 61 , and therefore the lower end of the lower balance weight 64 may not be exposed. In such a case, the retaining section is not required.
- the lower balance weight 64 is embedded in the wear ring section 692 .
- an upper end section of the lower balance weight 64 may be positioned corresponding to the second flange section 682 .
- the lower balance weight 64 is not limited to the configuration in which the lower balance weight 64 is embedded in the wear ring section 692 , and the lower balance weight 64 may be embedded in any parts of the circumferential section of the impeller body 61 .
- the impeller is not limited to the impeller made of synthetic resin.
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Abstract
An impeller includes an impeller body in which an internal flow path and a recessed section are formed; a lid covering an opening of the recessed section; and a balance weight arranged between the impeller body and the lid. The lid is attached and fixed to the impeller body through an engagement section. Holding sections for the balance weight are formed in a back-side surface of the lid. When attaching and fixing the lid to the impeller body, the balance weight is sandwiched between the holding section of the lid and the impeller body to be fixed.
Description
- A technique disclosed herein relates to a centrifugal pump impeller.
- Conventionally, a centrifugal pump has been used for delivering, e.g., drainage. Among various impellers attached to the centrifugal pump, a non-clog impeller in which a flow path connecting between an inlet opening through a first end surface and an outlet opening through a circumferential surface is formed has been known as an impeller in which it is less likely to cause clogging of, e.g., drainage containing solid substances such as impurities (see, e.g., Patent Document 1).
- The non-clog impeller has a single vane, and therefore is formed in non-symmetric shape about a rotation axis. Thus, a part of the impeller disclosed in
Patent Document 1 is removed in order to achieve static balance at rest and dynamic balance during rotation in air (hereinafter collectively referred to as “mechanical balance”). In a second end surface of the substantially cylindrical impeller, which is on an opposite side to the first end surface in which the inlet is formed, such removal allows formation of a recessed section which opens through the second end surface, and which is recessed in a cylindrical axis direction in the second end surface. As in the foregoing impeller, in an impeller made of synthetic resin, a recessed section which opens through a second end surface, and which is recessed in a cylindrical axis direction in the second end surface may be formed in order to reduce or prevent shrinkage caused when forming the impeller due to the substantially constant thickness of the impeller. - However, the opening of the recessed section is exposed, resulting in a power loss due to fluid turbulence. Thus, in the impeller disclosed in
Patent Document 1, a lid is attached to the second end surface, and the opening of the recessed section is covered by the lid. Consequently, the flat second end surface of the impeller is defined. - PATENT DOCUMENT 1: Japanese Patent Publication No. 2006-291937
- In the conventional impeller disclosed in
Patent Document 1, the lid is fixed to an impeller body with bolts. Thus, its assembly process is complicated. In addition, in the impeller disclosed inPatent Document 1, a balance weight is attached to a back-side surface of the lid with the bolts in order to achieve the mechanical balance and balance during rotating the impeller in water (hydraulic balance). Thus, there is a disadvantage that not only a lid attachment process but also a balance weight attachment process are separately required. - The centrifugal pump impeller disclosed herein is an advantageous impeller for simplifying an attachment structure of a lid attached to an impeller body, and simplifying an assembly process.
- Inventors of the present invention have focused on an engagement structure between an impeller body and a lid; and have arrived at a configuration in which an engagement between the impeller body and the lid is facilitated through an engagement section, and a balance weight is sandwiched between the lid engaged with the impeller body and the impeller body to fix the balance weight to the impeller body.
- An example of a centrifugal pump impeller includes an impeller body having a substantially cylindrical shape with first and second end surfaces facing each other in a cylindrical axis direction, and with a circumferential surface interposed between the first and second end surfaces; and including an internal flow path which connects between an inlet opening in the first end surface and an outlet opening in the circumferential surface, and a recessed section which opens in the second end surface, and which is recessed in the cylindrical axis direction in the second end surface; a lid which is attached to the second end surface of the impeller body, and which covers the opening of the recessed section so that the second end surface of the impeller body defines a flat surface; and a balance weight arranged between the impeller body and the lid. The lid is attached and fixed to the impeller body through an engagement section, and holding sections of the balance weight are formed in a back-side surface. When the lid is attached and fixed to the impeller body, the balance weight is sandwiched between the holding section of the lid and the impeller body, and is fixed by the holding section of the lid and the impeller body.
- According to the foregoing configuration, the lid is attached and fixed to the impeller body through the engagement section. By attaching and fixing the lid to the impeller body, the balance weight is sandwiched between the holding section of the lid and the impeller body, and then the balance weight is attached and fixed to the impeller body. That is, the lid and the balance weight are simultaneously attached to the impeller body, thereby simplifying an assembly process of the impeller.
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FIG. 1 is a cross-sectional view of a submersible pump including a centrifugal pump impeller which is illustrated as an example. -
FIG. 2 is a perspective view of the impeller. -
FIG. 3 is a front view of the impeller. -
FIG. 4 is a bottom view of the impeller. -
FIG. 5 is a V-V cross-sectional view ofFIG. 4 . -
FIG. 6 is a plan view of an impeller body in a state in which a lid is removed. -
FIG. 7 is a view illustrating a back-side surface of the lid. -
FIG. 8 is a VIII-VIII cross-sectional view ofFIG. 7 . -
FIG. 9 is an enlarged plan view around a boss section of the impeller body. -
FIG. 10 is an enlarged cross-sectional view around the boss section of the impeller body. -
FIG. 11 is a perspective view of an upper balance weight. -
FIG. 12 is a perspective view of a lower balance weight. - An example of a centrifugal pump impeller includes an impeller body having a substantially cylindrical shape with first and second end surfaces facing each other in a cylindrical axis direction, and with a circumferential surface interposed between the first and second end surfaces; and including an internal flow path which connects between an inlet opening in the first end surface and an outlet opening in the circumferential surface, and a recessed section which opens in the second end surface, and which is recessed in the cylindrical axis direction in the second end surface; a lid which is attached to the second end surface of the impeller body, and which covers the opening of the recessed section so that the second end surface of the impeller body defines a flat surface; and a balance weight arranged between the impeller body and the lid. The lid is attached and fixed to the impeller body through an engagement section, and holding sections of the balance weight are formed in a back-side surface. When the lid is attached and fixed to the impeller body, the balance weight is sandwiched between the holding section of the lid and the impeller body, and is fixed by the holding section of the lid and the impeller body.
- The lid is attached and fixed to the impeller body through the engagement section, thereby sandwiching the balance weight between the holding section of the lid and the impeller body. Consequently, the balance weight is attached and fixed to the impeller body. As described above, the lid and the balance weight are simultaneously attached to the impeller body, thereby facilitating an assembly process of the impeller.
- The engagement section may include engagement grooves formed in the impeller body or the lid; and engagement claws which are formed in the lid or the impeller body, and which are engaged with the engagement grooves by elastically deforming when attaching the lid to the impeller body.
- The engagement groove and the engagement claw can be engaged with each other without using, e.g., tools. Thus, the tools etc. are not required when attaching the lid to the impeller body, thereby further simplifying the assembly process of the impeller.
- A plurality of pins may be formed so as to protrude from the back-side surface of the lid; and a plurality of pinholes into which the pins are fitted may be formed so as to open through the second end surface of the impeller body.
- Positions of the pin and the pinhole are adjusted to each other, and the position of the lid is determined on the impeller body. In combination with the engagement in the engagement section, the fitting of the pin into the pinhole allows the lid to be more firmly fixed to the impeller body.
- Each of the pinholes may be formed in a boss section provided in the second end surface of the impeller body. A plurality of protrusions may be formed with spacing in a circumferential direction in a circumferential surface of the boss section. Fitting holes which have a larger diameter than that of the boss section, and which have a smaller diameter than that of a circle defined by connecting tip ends of the plurality of protrusions may be formed in the balance weight; and, in order to fix the balance weight to the impeller body, the fitting holes of the balance weight may be fitted onto the boss sections with the protrusions being pressed against the boss sections. The holding section of the lid is formed in circular shape so as to surround the pin, and holds the balance weight in a section around the fitting hole.
- The fitting hole of the balance weight is fitted onto the boss section of the impeller body, and therefore the balance weight can be correctly positioned on a predetermined section of the impeller body. In addition, the fitting hole of the balance weight is fitted onto the boss section of the impeller body, and the holding section of the lid presses against the section around the fitting hole. This reduces or prevents occurrence of rattling of the balance weight, and firmly fixes the balance weight to the impeller body.
- A plurality of reinforcement ribs extending in a radial direction may be formed inside the recessed section of the impeller body, and an end surface of the reinforcement rib in the cylindrical axis direction may be a mounting surface on which the balance weight is mounted. The boss section may be integrally formed with the reinforcement rib in the mounting surface of the reinforcement rib.
- The reinforcement rib improves a strength of the impeller body. In addition, the boss section is integrally formed with the reinforcement rib, thereby improving stiffness of the boss section. The balance weight is more stably fixed to the impeller body.
- An embodiment of the impeller will be described below with reference to the drawings. Note that the embodiment below has been set forth merely for purposes of a preferred example in nature.
FIG. 1 illustrates asubmersible pump 1 including an impeller which is illustrated as an example. Thesubmersible pump 1 includes a pump section 21 with animpeller 6, and amotor section 22 with amotor 3 for driving theimpeller 6. In thesubmersible pump 1, the pump section 21 is arranged below anoil casing 23, and themotor section 22 is arranged above theoil casing 23. That is, the pump section 21 and themotor section 22 are arranged one above the other. Thesubmersible pump 1 is a lightweight pump in which ahead cover 34 and apump casing 4 which will be described later are made of predetermined resin material. - The
motor section 22 includes themotor 3 with astator 31 and arotor 32; astator casing 33 covering thestator 31 of themotor 3; and thehead cover 34 attached to an upper end of thestator casing 33. A rotatingshaft 35 of themotor 3 vertically extends. - The
stator casing 33 is formed in substantially cylindrical shape with upper and lower openings. The upper opening of thestator casing 33 is closed with amotor cover 36, and a bearing 35 a rotatably supporting an upper end section of therotating shaft 35 is provided on a lower surface of themotor cover 36. - The
head cover 34 is attached to the upper end of thestator casing 33. Thehead cover 34 has an upper wall and a circumferential wall which downwardly extends from a circumferential section of the upper wall, and which is fixed to an upper end section of thestator casing 33. In addition, thehead cover 34 has an inverted U-shaped cross section. Thus, thehead cover 34 and themotor cover 36 defines ahousing space 34 a in which various electric components are housed. A cable boot into which a power feeding cable for feeding power to themotor 3 is inserted is attached so as to pass through the upper wall of thehead cover 34, and ahandle 34 b is attached to a center section of an upper surface of the upper wall. Thehead cover 34 is fixed to theoil casing 23 with a plurality of bolts 37 (only one bolt is illustrated in the figure) arranged at predetermined interval in the circumferential direction. That is, thebolt 37 inserted into a through-hole formed in a circumferential section of the head cover 34 passes through themotor cover 36. Then, thebolt 37 downwardly extends along an inner circumferential surface of thestator casing 33, and is screwed into a circumferential section of theoil casing 23. In such a manner, in thesubmersible pump 1, the long vertically-extendingbolt 37 fixes thehead cover 34, thestator casing 33, and themotor cover 36 to theoil casing 23 at one time. Such a configuration allows reduction in the number of components and the number of assembly steps of thesubmersible pump 1. - The
oil casing 23 is attached to a lower end of thestator casing 33, and the lower opening of thestator casing 33 is closed with theoil casing 23. Thepump casing 4 is attached to a lower side of theoil casing 23, and therefore theoil casing 23 and thepump casing 4 define anoil chamber 53 filled with lubricating oil. A through-hole into which therotating shaft 35 of themotor 3 is inserted is formed in theoil casing 23, and abearing 35 b rotatably supporting a middle section of therotating shaft 35 is attached to an upper surface of theoil casing 23. In theoil chamber 53 defined by theoil casing 23 and thepump casing 4, the rotatingshaft 35 is sealed by amechanical seal 51, and acircular wall 52 is provided, which surround a substantially entire outer circumferential section of themechanical seal 51. - The pump section 21 includes the
impeller 6 attached to a lower end of therotating shaft 35 of themotor 3, and thepump casing 4. Thesubmersible pump 1 is a centrifugal pump. A first pump casing 41 on an upper side, which defines theoil chamber 53 together with theoil casing 23, and a second pump casing 42 on a lower side are integrated by welding, thereby forming thepump casing 4. The first pump casing 41 and thesecond pump casing 42 are integrated by welding as described above, and therefore a flange is not required, which is required, e.g., when integrating two pump casings with a bolt-nut fastening means. Consequently, the size of thesubmersible pump 1 is reduced. - A through-hole into which the
rotating shaft 35 is inserted is formed in an upper section of thepump casing 4, and avolute chamber 43 in which theimpeller 6 is housed is formed inside thepump casing 4. Thepump casing 4 has a lower opening, and aliner ring 44 with anopening 44 a, which supports awear ring section 692 which is a lower end section of theimpeller 6 is attached to such an opening. Adischarge section 45 which laterally protrudes, and which is upwardly curved is integrally formed with a side section of thepump casing 4. Thedischarge section 45 communicates with thevolute chamber 43, and has adischarge port 45 a with an upper opening. Thedischarge port 45 a is connected to an outlet pipe which is not shown in the figure. Four downwardly-extending legs 46 (only threelegs 46 are illustrated inFIG. 1 ) are arranged in a lower section of thepump casing 4 in a predetermined pattern, and lower ends of thelegs 46 are attached and fixed to aseat 7. Theseat 7 includes abody section 71 made of synthetic resin; and a cover 72 which covers a lower side of thebody section 71, and which is made of rubber. Insertingsections 73 into which the lower ends of thelegs 46 are inserted, and in which the lower ends of thelegs 46 are fastened with screws are integrally formed with thebody section 71 so as to upwardly protrude. A damping rubber member or dampingsteel plate 74 is interposed between a lower surface of theleg 46 and the insertingsection 73. Theseat 7 functions to reduce or prevent displacement of a position where thesubmersible pump 1 is arranged due to the cover 72, and to control vibration by the damping rubber member or dampingsteel plate 74 when driving thesubmersible pump 1. - As illustrated in
FIGS. 2-5 , theimpeller 6 is a non-clog impeller having a substantially cylindrical shape, and is fixed to the lower end of therotating shaft 35 so that a cylindrical axis of theimpeller 6 is coaxial to the rotating shaft 35 (seeFIG. 1 ). Theimpeller 6 includes animpeller body 61, and alid 62 attached to an upper end surface of theimpeller body 61. In addition, in order to achieve mechanical and hydraulic balance, theimpeller 6 also includes anupper balance weight 63 and alower balance weight 64. Although details will be described later, theupper balance weight 63 is arranged and fixed between theimpeller body 61 and thelid 62, and thelower balance weight 64 is embedded in thewear ring section 692 of theimpeller body 61 as illustrated inFIG. 5 . - The
impeller body 61 has a substantially cylindrical shape. Aninlet 601 opening at the bottom of theimpeller body 61 is formed in a lower end surface of theimpeller body 61, and anoutlet 602 opening through a side of theimpeller body 61 is formed in a predetermined section of a circumferential surface of theimpeller body 61. Aninternal flow path 603 extending in the cylindrical axis direction is formed inside theimpeller 6, and theinternal flow path 603 connects between theinlet 601 and theoutlet 602. Anexternal flow path 604 inwardly recessed in the radial direction is formed in an outer circumferential surface of theimpeller body 61. Theexternal flow path 604 is not a flow path extending in the cylindrical axis direction, and the center of the flow path is positioned on a plane perpendicular to the cylindrical axis of theimpeller body 61. Theexternal flow path 604 reaches a downstream side of theinternal flow path 603 at theoutlet 602, and extends across a substantially entire perimeter of theimpeller 6. Theexternal flow path 604 is defined by avane 605. Thevane 605 is a so-called “single radial-flow vane (centrifugal vane), and thecentrifugal vane 605 increases the pressure of water in theexternal flow path 604, and then discharges such water to an outer circumferential side (outer side in the radial direction). Afirst flange section 681 outwardly protruding in the radial direction around an entire circumference is formed above theexternal flow path 604 of theimpeller body 61. In addition, asecond flange section 682 outwardly protruding in the radial direction around the entire circumference is also formed below theexternal flow path 604. Thesecond flange section 682 horizontally divides theimpeller 6 into a lower section where theinlet 601 is formed, and an upper section where theoutlet 602 is formed. That is, theimpeller 6 is a closed-type impeller in which thesecond flange section 682 divides between theinlet 601 and theoutlet 602. - A
shaft support section 691 is formed so as to upwardly protrude in the center of the upper end surface of theimpeller body 61, which is above thefirst flange section 681. Theshaft support section 691 is made of predetermined metal material, and is provided with an attachment hole into which therotating shaft 35 of themotor 3 is inserted to be fixed. In addition, the downwardly-protrudingwear ring section 692 inserted into the opening 44 a of thepump casing 4 is formed below thesecond flange section 682 of theimpeller body 61. - In order to reduce power of the
submersible pump 1, the first andsecond flange sections impeller body 61 becomes as small as possible. Thus, as illustrated inFIGS. 3 and 5 , theimpeller body 61 is designed with almost no step between thesecond flange section 682 and thewear ring section 692. The diameters of the first andsecond flange sections wear ring section 692 is increased so that the diameter of theinlet 601 is increased, thereby eliminating the step between thesecond flange section 682 and thewear ring section 692. - The
impeller body 61 is made of synthetic resin. As illustrated inFIGS. 5 and 6 , a recessedsection 611 recessed in the cylindrical axis direction in the upper end surface of theimpeller body 61 is formed in order to reduce or prevent shrinkage caused when forming the impeller due to the substantially constant thickness of the impeller. As illustrated inFIG. 6 , the recessedsection 611 extends substantially three-fourths of the entire perimeter from an opening side of the outlet 602 (upper side as viewed inFIG. 6 ), in the counterclockwise and circumferential directions. In addition, as illustrated inFIG. 5 , the recessedsection 611 is formed so that the depth is relatively shallow on the opening side of the outlet 602 (right side as viewed inFIG. 5 ), and the depth is relatively deep on a side opposite to the opening side of the outlet 602 (left side as viewed inFIG. 5 ). -
Reinforcement ribs 612 extending in the radial direction, and connecting between theshaft support section 691 and a circumferential section of theimpeller body 61 are formed in an upper end section of theimpeller body 61. In the present embodiment, in theimpeller body 61 illustrated inFIG. 6 , threereinforcement ribs 612 are formed at predetermined angles in an upper half region corresponding to the opening side of theoutlet 602, and asingle reinforcement rib 612 is formed in a lower half region corresponding to the side opposite to the opening side of theoutlet 602. Three of the fourreinforcement ribs 612 are arranged inside the recessedsection 611. As illustrated in, e.g.,FIG. 10 , the threereinforcement ribs 612 arranged on the opening side of theoutlet 602 are also used as a mounting section on which theupper balance weight 63 is mounted. That is, an upper end surface of each of thereinforcement ribs 612 serves as a mountingsurface 614 on which theupper balance weight 63 is mounted. Further, aboss section 613 for fixing theupper balance weight 63 is formed in the substantially center of thereinforcement rib 612 in the radial direction. - As illustrated in
FIGS. 9 and 10 , theboss section 613 is formed in circular shape as viewed in plan, which has a diameter larger than the width of thereinforcement rib 612. An upwardly-opening pinhole 615 which extends in the cylindrical axis direction is formed in the center of theboss section 613. In an outer circumferential surface of theboss section 613, threeprotrusions 616 outwardly protruding in the radial direction are integrally formed with theboss section 613 at equal interval in the circumferential direction. - As illustrated in
FIG. 11 , theupper balance weight 63 made of predetermined metal material is formed in substantially fan-like shape by cutting a section corresponding to a predetermined angular range from an annular disk-like member having a predetermined thickness. Theupper balance weight 63 has a flattened shape in which the width of theupper balance weight 63 in the radial direction is larger than the thickness of theupper balance weight 63 in the cylindrical axis direction (vertical direction). As illustrated inFIG. 6 , theupper balance weight 63 is arranged between theshaft support section 691 and the circumferential section of theimpeller body 61. Thus, the inner diameter of theupper balance weight 63 is set so as to be larger than the diameter of theshaft support section 691, and the outer diameter of theupper balance weight 63 is set so as to be smaller than the diameter of the circumferential section of theimpeller body 61. The shape of theupper balance weight 63 is not limited, and may be suitably set so that a required weight can be ensured under a condition where theupper balance weight 63 is arranged between theimpeller body 61 and thelid 62. In theupper balance weight 63, threeholes 631 passing through theupper balance weight 63 in a thickness direction are formed corresponding to the threeboss sections 613. Each of such holes is afitting hole 631 fitted onto theboss section 613. As hypothetically illustrated inFIG. 9 , the diameter of such a hole is set so as to be larger than that of theboss section 613, and to be smaller than that of a circle defined by connecting tip ends of theprotrusions 616. - As illustrated in enlarged views of
FIGS. 9 and 10 , theupper balance weight 63 is mounted on the mountingsurface 614 of thereinforcement rib 612 so that each of thefitting holes 631 is fitted onto theboss section 613. Thus, theupper balance weight 63 is positioned in a predetermined section of the upper end surface of theimpeller body 61 on the opening side of theoutlet 602. Thefitting hole 631 of theupper balance weight 63 is set so as to have the diameter larger than that of theboss section 613, and smaller than that of the circle defined by connecting the tip ends of theprotrusions 616. Thus, a part of theprotrusions 616 is pressed against theboss section 613, thereby fitting the fitting hole onto theboss section 613. This reduces the rattling of theupper balance weight 63. - As illustrated in
FIGS. 7 and 8 , thelid 62 has a circular disk-like shape, and a through-hole 621 into which theshaft support section 691 of theimpeller body 61 is inserted is formed in the center of thelid 62. Thelid 62 is made of synthetic rein. A front-side surface of thelid 62 is flat. On each of a side corresponding to the opening of theoutlet 602 and its opposite side with respect to the cylindrical axis in the circumferential section of thelid 62, twoengagement claws 622 are integrally formed with thelid 62 at predetermined interval in the circumferential direction. Theengagement claw 622 is a claw to be engaged with anengagement groove 683 formed at a circumference of the upper end section of theimpeller body 61, and theengagement claw 622 and theengagement groove 683 serve as an engagement means for attaching and fixing thelid 62 to theimpeller body 61. - In positions of a back-side surface of the
lid 62 corresponding to theboss sections 613 of theimpeller body 61, threepins 623 are formed so as to protrude from the back-side surface. As illustrated inFIG. 10 , when attaching thelid 62 to theimpeller body 61, each of thepins 623 is fitted into thepinhole 615 formed in theboss section 613. In addition to the engagement of theengagement claw 622 with theengagement groove 683, the fitting of thepin 623 into thepinhole 615 allows thelid 62 to be more stably attached and fixed to theimpeller body 61. Holdingsections 624 for holding theupper balance weight 63 are further formed so as to protrude from the back-side surface of thelid 62. The holdingsection 624 is formed in circular shape so as to surround thepin 623. As illustrated inFIG. 10 , when attaching and fixing thelid 62 to theimpeller body 61, a lower surface of the holdingsection 624 downwardly presses against an upper surface of theupper balance weight 63 around theboss section 613. Thus, theupper balance weight 63 is sandwiched between thelid 62 and theimpeller body 61. - In the
lid 62, two through-holes 625 are formed on each of the opening side of theoutlet 602 and its opposite side. Such through-holes are air vent holes 625 through which air is vented from the recessedsection 611 of theimpeller body 61 to fill the recessedsection 611 with water. Air vent holes may be formed in theupper balance weight 63. In such a case, such air vent holes are desirably formed in the same positions as those of the air vent holes 625 formed in thelid 62. The air vent holes 625 are provided in thelid 62 to fill the recessedsection 611 with water as described above. Thus, this reduces or prevents a loss of mechanical balance of theimpeller 6 due to remaining air in the recessedsection 611, and reduces occurrence of vibration when driving theimpeller 6. - As illustrated in
FIGS. 3 and 4 , thelower balance weight 64 is embedded in thewear ring section 692 on the opening side of theoutlet 602 of theimpeller body 61. As illustrated in, e.g.,FIG. 12 , thelower balance weight 64 made of predetermined metal material is a plate curved in arc, and has a vertically-elongated shape in which a height in the cylindrical axis direction is larger than a thickness in the radial direction. As illustrated inFIG. 4 , thelower balance weight 64 is embedded in thewear ring section 692 so that a lower end surface of thelower balance weight 64 is exposed in the lower end surface of theimpeller body 61. Two through-holes 641 are formed in predetermined positions of thelower balance weight 64, and each through-hole 641 serves as a positioning hole into which a positioning pin 8 of a mold is inserted. Anotch 642 is formed in a center section of a lower end of thelower balance weight 64. When forming theimpeller body 61 by molding, a section corresponding to thenotch 642 is filled with resin, and therefore aretaining section 694 is formed, which crosses thelower balance weight 64 in the thickness direction as illustrated inFIG. 4 . - Next, a manufacturing process of the
impeller body 61 will be briefly described. First, theshaft support section 691 and thelower balance weight 64 are arranged in predetermined positions inside the mold (not shown in the figure). In such a state, a position of thelower balance weight 64 in the circumferential direction, and an inclination of thelower balance weight 64 are determined by the two positioning pins 8 as illustrated inFIG. 12 . The positioning pin 8 includes a small-diameter section 81 on a tip end side, and a large-diameter section 82 on a base end side. A position of thelower balance weight 64 in the radial direction is also determined by a position of a step defined by such sections having the different diameters. In such a manner, thelower balance weight 64 can be accurately positioned in a predetermined section inside the mold, thereby ensuring thelower balance weight 64 embedded in the thinwear ring section 692 of theimpeller body 61. - Then, the
impeller body 61 is formed by a well-known resin molding. As illustrated inFIGS. 2 and 3 , holes 693 are formed in thewear ring section 692 of the moldedimpeller body 61 by the positioning pins 8. - Next, the separately-prepared
upper balance weight 63 is attached to the upper end surface of the moldedimpeller body 61. As described above, in theupper balance weight 63, thefitting hole 631 of theupper balance weight 63 is fitted onto theboss section 613 with theprotrusions 616 of theboss section 613 being pressed against thefitting hole 631. - Subsequently, the separately-molded
lid 62 is attached to theimpeller body 61. In such a state, thepin 623 of thelid 62 is fitted into thepinhole 615 of theimpeller body 61, and theengagement claw 622 of thelid 62 is elastically deformed to be engaged with theengagement groove 683 of theimpeller body 61. When attaching and fixing thelid 62 to theimpeller body 61, the holdingsections 624 of thelid 62 press against theupper balance weight 63. Thus, attachment of theupper balance weight 63 to theimpeller body 61 is completed. - As described above, in the
impeller 6 having the foregoing configuration, the fastening means such as bolts is not used to fix thelid 62 to theimpeller body 61, and theengagement claws 622 are engaged with theengagement grooves 683 to attach and fix thelid 62 to theimpeller body 61. Thus, tools etc. are not required for the assembly process, and the assembly of theimpeller 6 is simplified. In addition, when attaching thelid 62 to theimpeller body 61, theupper balance weight 63 is fixed to theimpeller body 61. Consequently, the assembly process of theimpeller 6 is further facilitated. - The
engagement claws 622 are provided in thelid 62, and theengagement grooves 683 opening toward outside are provided in the circumferential section of theimpeller body 61. Thus, in a state in which thelid 62 is attached to theimpeller body 61, the engagement sections are not protrude from the front-side surface of thelid 62, thereby ensuring the flat surface at the upper end of theimpeller 6. This is advantageous to reduce a power loss. Note that engagement grooves may be provided in thelid 62, and engagement claws may be provided in theimpeller body 61. The engagement section where thelid 62 is engaged with theimpeller body 61 is not limited to the combination of theengagement claw 622 and theengagement groove 683, and any configuration may be employed. - The circumferential section of the
lid 62 is fixed to theimpeller body 61 by theengagement claws 622 and theengagement grooves 683, and thepins 623 provided in thelid 62 are fitted into thepinholes 615 of theimpeller body 61. Thus, an inner section of thelid 62 in the radial direction can be fixed to theimpeller body 61. Consequently, the inner section of thelid 62 in the radial direction is not apart from theimpeller body 61. - The
fitting hole 631 of theupper balance weight 63 is fitted onto theboss section 613 of theimpeller body 61. Thus, theupper balance weight 63 can be correctly positioned on the predetermined section of theimpeller body 61, and the occurrence of the rattling of theupper balance weight 63 can be reduced or prevented. - The
reinforcement rib 612 improves the strength of theimpeller body 61 itself. In addition, theupper balance weight 63 and theboss section 613 used for the fixing of the lid are integrally formed with thereinforcement rib 612, thereby improving the stiffness of theboss section 613. This is advantageous to more stably fix theupper balance weight 63 and thelid 62 to theimpeller body 61. - Unlike the
upper balance weight 63, thelower balance weight 64 has the vertically-elongated shape, thereby embedding thelower balance weight 64 in thewear ring section 692 which is thin in the radial direction. Thelower balance weight 64 is embedded in theimpeller body 61, and therefore it is not necessary to attach the balance weight to thesecond flange section 682. This allows the diameter of theinlet 601 of theimpeller 6 to be as large as possible, thereby ensuring predetermined substance passage properties. In addition, the diameters of the first andsecond flange sections impeller 6, thereby reducing the power of thesubmersible pump 1. - The lower end surface of the
lower balance weight 64 embedded in thewear ring section 692 is exposed in the lower end surface of theimpeller body 61, and therefore there is a possibility that thelower balance weight 64 is disengaged during use of theimpeller 6. However, the retainingsection 694 is configured by forming thenotch 642 at the lower end of thelower balance weight 64, thereby reducing or preventing the disengagement of thelower balance weight 64. In the present embodiment, the retainingsection 694 is configured by forming thenotch 642 at the lower end of thelower balance weight 64. However, a through-hole passing through thelower balance weight 64 in the thickness direction may be formed in, e.g., a middle section of thelower balance weight 64 in the height direction, thereby forming a resin retaining section crossing thelower balance weight 64 in the thickness direction. Alternatively, the entirelower balance weight 64 may be embedded in theimpeller body 61, and therefore the lower end of thelower balance weight 64 may not be exposed. In such a case, the retaining section is not required. - In the foregoing embodiment, the
lower balance weight 64 is embedded in thewear ring section 692. However, e.g., if the height of thelower balance weight 64 is increased under a condition where the required weight is ensured, an upper end section of thelower balance weight 64 may be positioned corresponding to thesecond flange section 682. - The
lower balance weight 64 is not limited to the configuration in which thelower balance weight 64 is embedded in thewear ring section 692, and thelower balance weight 64 may be embedded in any parts of the circumferential section of theimpeller body 61. - The impeller is not limited to the impeller made of synthetic resin.
-
- 1 Submersible Pump
- 6 Impeller
- 601 Inlet
- 602 Outlet
- 603 Internal Flow Path
- 61 Impeller Body
- 611 Recessed Section
- 612 Reinforcement Rib
- 613 Boss Section
- 615 Pinhole
- 616 Protrusion
- 62 Lid
- 622 Engagement Claw
- 623 Pin
- 624 Holding Section
- 63 Upper Balance Weight
- 631 Fitting Hole
- 683 Engagement Groove
Claims (5)
1. A centrifugal pump impeller, comprising:
an impeller body having a substantially cylindrical shape with first and second end surfaces facing each other in a cylindrical axis direction, and with a circumferential surface interposed between the first and second end surfaces; and including an internal flow path which connects between an inlet opening in the first end surface and an outlet opening in the circumferential surface, and a recessed section which opens in the second end surface, and which is recessed in the cylindrical axis direction in the second end surface;
a lid which is attached to the second end surface of the impeller body, and which covers the opening of the recessed section so that the second end surface of the impeller body defines a flat surface; and
a balance weight arranged between the impeller body and the lid,
wherein the lid is attached and fixed to the impeller body through an engagement section, and holding sections of the balance weight are formed in a back-side surface; and,
when the lid is attached and fixed to the impeller body, the balance weight is sandwiched between the holding section of the lid and the impeller body, and is fixed by the holding section of the lid and the impeller body.
2. The centrifugal pump impeller of claim 1 , wherein
the engagement section includes engagement grooves formed in the impeller body or the lid; and engagement claws which are formed in the lid or the impeller body, and which are engaged with the engagement grooves by elastically deforming when attaching the lid to the impeller body.
3. The centrifugal pump impeller of claim 1 , wherein
a plurality of pins are formed so as to protrude from the back-side surface of the lid; and
a plurality of pinholes into which the pins are fitted are formed so as to open in the second end surface of the impeller body.
4. The centrifugal pump impeller of claim 3 , wherein
each of the pinholes is formed in a boss section provided in the second end surface of the impeller body;
a plurality of protrusions are formed with spacing in a circumferential direction in a circumferential surface of the boss section;
fitting holes which have a larger diameter than that of the boss section, and which have a smaller diameter than that of a circle defined by connecting tip ends of the plurality of protrusions are formed in the balance weight, and, in order to fix the balance weight to the impeller body, the fitting holes of the balance weight are fitted onto the boss sections with the protrusions being pressed against the boss sections; and
the holding section of the lid is formed in circular shape so as to surround the pin, and holds the balance weight in a section around the fitting hole.
5. The centrifugal pump impeller of claim 4 , wherein
a plurality of reinforcement ribs extending in a radial direction are formed inside the recessed section of the impeller body, and an end surface of the reinforcement rib in the cylindrical axis direction is a mounting surface on which the balance weight is mounted; and
the boss section is integrally formed with the reinforcement rib in the mounting surface of the reinforcement rib.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008-175628 | 2008-07-04 | ||
JP2008175628A JP2010014047A (en) | 2008-07-04 | 2008-07-04 | Impeller for centrifugal pump |
PCT/JP2009/003126 WO2010001627A1 (en) | 2008-07-04 | 2009-07-06 | Impeller for centrifugal pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110182734A1 true US20110182734A1 (en) | 2011-07-28 |
Family
ID=41465733
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/002,072 Abandoned US20110182734A1 (en) | 2008-07-04 | 2009-07-06 | Centrifugal pump impeller |
Country Status (4)
Country | Link |
---|---|
US (1) | US20110182734A1 (en) |
JP (1) | JP2010014047A (en) |
CA (1) | CA2729815A1 (en) |
WO (1) | WO2010001627A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018219496A1 (en) | 2017-06-02 | 2018-12-06 | Wilo Se | Pump impeller |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012207645A (en) * | 2011-03-30 | 2012-10-25 | Sinfonia Technology Co Ltd | Fan device |
JP5904900B2 (en) * | 2012-08-07 | 2016-04-20 | 株式会社鶴見製作所 | Water pump impeller and submersible motor pump equipped with the impeller |
KR102219944B1 (en) * | 2020-10-29 | 2021-02-24 | 주식회사 신성터보마스터 | Single channel submersible pump without clogging by foreign substances |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1470607A (en) * | 1922-11-03 | 1923-10-16 | Unchokeable Pump Ltd | Impeller for centrifugal pumps |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6429294U (en) * | 1987-08-13 | 1989-02-21 | ||
JPH0544700A (en) * | 1991-08-13 | 1993-02-23 | Matsushita Electric Ind Co Ltd | Electric pump |
JP2005291116A (en) * | 2004-03-31 | 2005-10-20 | Yamada Seisakusho Co Ltd | Impeller for water pump |
JP5044105B2 (en) * | 2005-04-14 | 2012-10-10 | 新明和工業株式会社 | Centrifugal pump impeller and centrifugal pump equipped with the impeller |
-
2008
- 2008-07-04 JP JP2008175628A patent/JP2010014047A/en active Pending
-
2009
- 2009-07-06 WO PCT/JP2009/003126 patent/WO2010001627A1/en active Application Filing
- 2009-07-06 US US13/002,072 patent/US20110182734A1/en not_active Abandoned
- 2009-07-06 CA CA2729815A patent/CA2729815A1/en not_active Abandoned
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1470607A (en) * | 1922-11-03 | 1923-10-16 | Unchokeable Pump Ltd | Impeller for centrifugal pumps |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018219496A1 (en) | 2017-06-02 | 2018-12-06 | Wilo Se | Pump impeller |
DE102017005283A1 (en) | 2017-06-02 | 2018-12-06 | Wilo Se | pump impeller |
DE102017005283B4 (en) | 2017-06-02 | 2022-12-08 | Wilo Se | pump impeller |
Also Published As
Publication number | Publication date |
---|---|
CA2729815A1 (en) | 2010-01-07 |
WO2010001627A1 (en) | 2010-01-07 |
JP2010014047A (en) | 2010-01-21 |
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Owner name: SHINMAYWA INDUSTRIES, LTD., JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARUI, MOTONOBU;TAKEUCHI, KAZUKI;ENOMOTO, JUNYA;AND OTHERS;SIGNING DATES FROM 20101221 TO 20101224;REEL/FRAME:025592/0624 |
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