Water pump

Abstract

The water pump includes a rotating assembly and a rotating assembly housing. The rotating assembly has a plurality of in-line flow guiding portions. The center line longitudinal axis of each of the flow guiding portions extends on the same straight line as the rotation axis of the rotating assembly. The downstream end of the flow pressurizing portion engages with the upstream end of the rotating flow amplifying portion. The downstream end of the rotating flow amplifying portion engages with the upstream end of the flow outlet portion. The rotating assembly housing has an internal space extending along the center line axis of the rotating assembly housing. The rotating assembly is disposed within the internal space of the rotating assembly housing. The rotating assembly and the rotating assembly are jointly configured such that the rotation axis extends on the same straight line as the center line longitudinal axis of the rotating assembly housing.

Description

Technical Field

[0001] The disclosure made herein generally relates to pumps for fluid materials, and more particularly to submersible pumps for fluid materials such as liquids.

Background Art

[0002] An electric submersible pump (ESP) is a pump for fluid materials known in the art. An ESP is typically disposed at the end of the length of a fluid flow conduit (e.g., tubing or pipe) in a wellbore extending generally vertically through a formation. Fluid pumping is achieved through a plurality of successive fluid pressurization stages driven rotationally (i.e., powered) by an electric motor. Depending on the particular design of the ESP, the plurality of fluid pressurization stages may include one or more centrifugal disk plates, one or more impellers, etc. The basic function of the fluid pressurization stage is to pressurize the fluid to cause fluid flow along the axial length of the fluid flow conduit (which may extend vertically).

[0003] Conventional ESPs are known to exhibit various drawbacks. One such drawback is pumping losses due to changes in the direction of fluid flow as the fluid flows through the various fluid pressurization stages. For example, each change in the direction of fluid flow causes a loss of momentum in the inlet region of the ESP. As a result of this loss of momentum, additional energy is required to reduce the associated volumetric flow rate loss. The load generated by this additional energy (i.e., the additional operating power to reduce the associated volumetric flow rate loss output) can have the effect of accelerating wear of the internal pump, thereby shortening the overall life of the ESP. Another such drawback is that the fluid pressurization stage generates a turbulent fluid flow that decays into a laminar straight flow, resulting in pumping losses from increased sidewall resistance within the fluid flow conduit.

[0004] Therefore, an ESP that overcomes the drawbacks associated with conventional ESPs is advantageous, desirable, and useful. SUMMARY OF THE INVENTION

[0005] Embodiments of the disclosure made herein are directed to a submersible pump (electric or otherwise) that overcomes the drawbacks associated with conventional ESPs. For this purpose, compared to conventional ESPs, the submersible pump according to embodiments of the disclosure made herein beneficially reduces pumping pressure loss, reduces pumping energy, provides improved volumetric flow efficiency resulting from increased flow velocity, and exhibits an improved operating life. Unlike conventional ESPs that exhibit significant energy inefficiencies resulting from pumping losses caused by changes in the direction of fluid flow as the fluid flows through various fluid pressurization stages (as described above), the ESP according to embodiments of the disclosure made herein reduces, if not eliminates, harmful direction changes in the fluid flow and associated frictional flow losses as a result of the in-line flow, resulting in a significant reduction in relative energy consumption and an increase in flow capacity. In addition, the submersible pump according to embodiments of the disclosure made herein beneficially reduces, if not eliminates, the common cavitation problems exhibited in many centrifugal ESPs and other types of pump designs. These enhanced functionalities result in improved performance, reliability, and durability.

[0006] In one or more embodiments, the submersible pump includes a rotating assembly and a rotating assembly housing. The rotating assembly has a plurality of in-line flow guiding portions. The centerline longitudinal axis of each of the flow guiding portions extends collinearly with the rotational axis of the rotating assembly. The downstream end of the flow pressurizing portion engages the upstream end of the rotational flow amplifying portion. The downstream end of the rotational flow amplifying portion engages the upstream end of the flow outlet portion. The rotating assembly housing has an internal space that extends along the centerline longitudinal axis of the rotating assembly housing. The rotating assembly is disposed within the internal space of the rotating assembly housing. The rotating assembly and the rotating assembly housing are jointly configured such that the rotational axis extends collinearly with the centerline longitudinal axis of the rotating assembly housing.

[0007] In one or more embodiments of the disclosure made herein, the submersible pump includes a rotating assembly having a rotating shaft and a rotating assembly housing having an internal space extending along the central axis of the rotating assembly housing. The rotating assembly is disposed within the internal space of the rotating assembly housing with the rotating shaft extending along the same straight line as the central longitudinal axis of the rotating assembly housing. The rotating assembly includes an impeller, a rotating flow amplification body, and an outlet body. The impeller has sidewalls extending around the rotating shaft and defining an internal space of the impeller. The sidewalls are tapered such that the impeller has a first cross-sectional area adjacent to its first end and a second cross-sectional area adjacent to its second end. The second cross-sectional area is larger than the first cross-sectional area. The sidewalls include a plurality of flow guiding protrusions, each of which extends outwardly away from the internal space of the impeller and extends from a location adjacent to the first end of the impeller with an upward inclination in a direction opposite to the rotational direction of the rotating assembly. Each of the flow guiding protrusions extends from a location adjacent to the first end of the impeller to a location adjacent to the second end of the impeller. Each of the flow guiding protrusions has a leading edge and a trailing edge with respect to the rotational direction. Each of the flow guiding protrusions has a fluid flow path extending through the flow guiding protrusion along at least a portion of the leading edge. The rotating flow amplification body has a first end engaged with the second end of the impeller so as to suppress unrestricted rotational movement between the rotating flow amplification body and the second end of the impeller at least in the rotational direction. The rotating flow amplification body has a central passage extending along its entire length. The central axis of the rotating flow amplification body extends along the same straight line as the rotating shaft. A plurality of vanes extend from the inner surface of the rotating flow amplification body defining the central passage. Each of the vanes extends from a location adjacent to the first end of the rotating flow amplification body with an upward inclination in a direction opposite to the rotational direction of the rotating assembly. The outlet body has a first end engaged with the second end of the rotating flow amplification body so as to suppress unrestricted rotational movement between the outlet body and the second end of the rotating flow amplification body at least in the rotational direction. The central axis of the outlet body extends along the same straight line as the rotating shaft.

[0008] In one or more embodiments, the rotational flow amplification section includes a plurality of bearings integral with its outer surface, and each of these bearings has a circumferential outer surface that engages a mating portion of the inner surface defining the internal space of the rotational assembly housing.

[0009] In one or more embodiments, each of the bearings includes one or more grooves within its circumferential outer surface. In one or more embodiments, the internal space of the flow pressurization section extends continuously into the central passage of the rotational flow amplification section, and the central passage of the rotational flow amplification section extends continuously into the central passage of the flow outlet section.

[0010] In one or more embodiments, the closed end of the internal space of the flow pressurization section, opposite its downstream end, has a maximum inner diameter smaller than the maximum inner diameter at the downstream end of the internal space of the flow pressurization section. The internal space of the flow pressurization section has, at its downstream end, a maximum inner diameter substantially the same as the maximum inner diameter of the central passage of the rotational flow amplification section. The central passage of the rotational flow amplification section has a maximum inner diameter substantially the same as the maximum inner diameter at the upstream end of the central passage of the flow outlet section. The central passage of the flow outlet section has, along its length, a cross-sectional area that tapers from the maximum inner diameter at its upstream end to a smaller inner diameter at its downstream end.

[0011] In one or more embodiments, the flow pressurization section includes an impeller having side walls that extend around the rotation axis and define the internal space of the impeller. The side walls are tapered such that the impeller has a first cross-sectional area adjacent to its first end and a second cross-sectional area adjacent to its second end, and the second cross-sectional area is larger than the first cross-sectional area. The side walls include a plurality of flow guiding protrusions, and each flow guiding protrusion extends outwardly away from the internal space of the intake space and extends from a location adjacent to the first end of the impeller with an upward slope in a direction opposite to the rotation direction of the rotational assembly. Each of the flow guiding protrusions extends from a location adjacent to the first end of the impeller to a location adjacent to the second end of the impeller. Each of the flow guiding protrusions has a leading edge and a trailing edge with respect to the rotation direction, and each of the flow guiding protrusions has a fluid flow path extending along at least a portion of its leading edge.

[0012] In one or more embodiments, each flow guiding protrusion has an inner surface that is offset from its outer surface by a substantially uniform distance such that each flow guiding protrusion defines a cavity within the inner surface of the sidewall. In one or more embodiments, each fluid flow path of the flow guiding protrusion extends only along one central portion of each of the flow guiding protrusions, thereby defining a first fluid flow stage between the first end of the impeller and the first end of the fluid flow path, a second fluid flow stage between the first end and the second end of the fluid flow path, and a third fluid flow stage between the second end of the fluid flow path and the second end of the impeller.

[0013] In one or more embodiments, the rotational flow amplification body has a central passage, and a plurality of vanes extend from the inner surface of the rotational flow amplification body that defines the central passage, and each of the vanes extends with an upward inclination from a location adjacent to the first end of the rotational flow amplification body in a direction opposite to the rotational direction of the rotational assembly.

[0014] In one or more embodiments, each of the vanes has a cup-shaped surface on the side facing downstream thereof. In one or more embodiments, each of the vanes extends continuously along substantially the entire length of the inner surface of the rotational flow amplification body.

[0015] These and other objects, embodiments, advantages and / or features of the present invention will become readily apparent by further examining the following specification, the related drawings and the appended claims.

Brief Description of the Drawings

[0016]

Figure 1

Figure 2A

Figure 2B

Figure 2C

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

DETAILED DESCRIPTION OF THE INVENTION

[0017] FIGS. 1 - 8 show an electric submersible pump (i.e., pump 100) according to one or more embodiments disclosed herein configured to be used with a flowing fluid material such as a liquid. Pump 100 employs a structural arrangement that advantageously reduces pumping pressure loss, reduces pumping energy, provides improved volumetric flow efficiency resulting from increased flow velocity, and alleviates, if not eliminates, common cavitation problems. These enhanced functionalities result in improved performance, reliability, and durability.

[0018] As best shown in FIGS. 1, 2A, and 2B, pump 100 includes a rotating assembly 102 and a rotating assembly housing 104. The rotating assembly housing 104 has an internal space S1 that extends along the central axis A of the rotating assembly housing 104. The rotating assembly 102 is disposed within the internal space S1 of the rotating assembly housing 104. The rotating assembly 102 has a rotating shaft R1 that extends on the same straight line as the central longitudinal axis A of the rotating assembly housing 104.

[0019] As shown in FIGS. 2A - 2C, the rotary assembly 102 has a plurality of in - line flow guiding portions, namely a flow pressurizing portion 102A, a rotary flow amplifying portion 102B, and a flow outlet portion 102C. The downstream end of the flow pressurizing portion 102A engages with the upstream end of the rotary flow amplifying portion 102B. The downstream end of the rotary flow amplifying portion 102B engages with the upstream end of the flow outlet portion 102C. The center - line longitudinal axis of each of the flow guiding portions (center - line longitudinal axes A1, A2, A3 respectively) extends on the same straight line as the rotation axis R1 of the rotary assembly 102.

[0020] As will be described in more detail below, due to the rotation of the rotary assembly 102 relative to the rotary assembly housing 104, the fluid existing outside the input end IE of the submersible pump 100 is drawn into the internal space S1 of the rotary assembly housing 104 through the inlet port 108 in the rotary assembly housing 104. To limit the entry of debris, a filter body 109 may be provided to cover the inlet port 108. The rotation further draws the fluid drawn into the internal space S1 of the rotary assembly housing 104 into the internal space S2 of the flow pressurizing portion 102A and pressurizes it therein. The pressurized fluid is urged through the rotary flow amplifying portion 102B and given a rotary flow centered on the rotation axis R1. Thereafter, the flow of the rotary fluid is focused by the flow outlet portion 102C before being output through the outlet port 112 of the flow outlet portion 102C at the outlet end OE of the rotary assembly housing 104. The rotation also causes fluid to pass through the internal space S1 of the rotary assembly housing 104 between the rotary assembly 102 and the inner surface of the rotary assembly housing 104 to provide cooling and lubrication at the contact points between the rotary assembly 102 and the rotary assembly housing 104.

[0021] The water pump 100 may include a motor 1 for causing rotation of the rotary assembly 102 relative to the rotary assembly housing 104. The motor 1 may be connected to the rotary assembly 102 and the rotary assembly housing 104 by any suitable means that enables rotation of the rotary assembly 102 relative to the rotary assembly housing 104. For example, the body 5 (e.g., housing or casing) of the motor 1 may be attached to the rotary assembly housing 104, and the rotational power output portion 10 of the motor 1 may be attached to the rotary assembly 102 to enable the rotational power generated by the motor 1 to be imparted to the rotary assembly 102. The motor 1 may be attached to the rotary assembly 102 via a coupler 105 having a first portion engaged with the motor 1 and a second portion engaged with the rotary assembly 102 and suppressing relative rotational movement therebetween.

[0022] In one or more preferred embodiments, the motor 1, the rotary assembly 102, and the rotary assembly housing 104 are jointly configured to maintain the rotary assembly 102 in a compression engagement state with the rotary assembly housing 104. Such compression engagement serves at least two purposes. The first purpose is for the rotary assembly 102 to rotate in a controlled manner about the rotation axis R1 at one or more rotational speeds. For this purpose, the attachment of the motor 1 to the rotary assembly housing 104 can function to radially constrain the adjacent end of the rotary assembly 102 to rotate in a controlled manner about the rotation axis R1. Optionally or additionally, a support (e.g., bracket) may be positioned between the motor and the rotary assembly 102 to effect or enhance such radial constraint of the adjacent end of the rotary assembly 102. The second purpose is for uncontrolled axial movement of the rotary assembly 102 relative to the rotary assembly housing 104 along the central axis A of the rotary assembly housing 104 to be controlled (e.g., suppressed) during such rotation of the rotary assembly 102.

[0023] As best shown in FIGS. 2A-2C, to support the aforementioned rotational considerations, the submersible pump 100 preferably includes a plurality of journal bearings 114 and one or more thrust bearings 116. The journal bearings 114 are axially spaced from each other and are disposed between the outer surface 103 of the rotating assembly 102 and the inner surface (i.e., the central passage defining surface) 118 of the rotating assembly housing 104. The journal bearings 114, the rotating assembly 102, and the inner surface 118 of the rotating assembly housing 104 of the central passage 120 are configured together to radially constrain the rotating assembly 102 with respect to the inner surface 118 of the rotating assembly housing 104, i.e., to effect rotation of the rotating assembly 102 in a controlled manner about the axis of rotation R1. In a preferred embodiment, the journal bearings 114 are integral with the outer surface 103 of the rotating assembly 102 that defines its outer surface 103, and each engages a mating portion of the inner surface 118 of the rotating assembly housing 104.

[0024] As best shown in FIG. 7, each of the journal bearings 114 may include one or more grooves 115. Each groove 115 extends across the entire width of each of the journal bearings 114. In a preferred embodiment, rotation of the rotating assembly 102 causes the flow pressurizing portion 102A to urge a portion of the fluid drawn into the internal space S1 of the rotating assembly housing 104 along the central passage 120 of the rotating assembly housing 104 between the rotating assembly 102 and the inner surface 118 of the rotating assembly housing 104. Each groove 115 functions as a flow passage to allow the fluid flow to easily cross each of the journal bearings 114. Advantageously, the fluid flow between the rotating assembly 102 and the inner surface 118 of the rotating assembly housing 104 functions to cool and lubricate the contact points between the journal bearings 114 and the mating portions of the rotating assembly housing 104.

[0025] One or more thrust bearings 116 are located at the outlet end OE of the submersible pump 100 between the end face 122 of the rotating assembly 102 and the inner end face 124 of the rotating assembly housing 104. The end face 122 of the rotating assembly 102, the inner end face 124 of the rotating assembly housing 104, and the one or more thrust bearings 116 (in combination with the implemented means for biasing the rotating assembly 102 in the downstream direction) are jointly configured to axially restrain the rotating assembly 102 with respect to the rotating assembly housing 104 while allowing a uniform and controlled rotational movement about the rotation axis R1. In a preferred embodiment, a cylindrical roller thrust bearing is utilized between the end face 122 of the rotating assembly 102 and the inner end face 124 of the rotating assembly housing 104 to axially restrain the rotating assembly 102 with respect to the rotating assembly housing 104.

[0026] Regarding the implemented means for biasing the rotating assembly 102 in the downstream direction, the rotating assembly 102 may be biased toward the outlet end OE of the submersible pump 100 to create a compressive force at the interface between the one or more thrust bearings 116, the rotating assembly 102, and the rotating assembly housing 104. In one example, the motor 1 may engage directly (e.g., fixedly) with the rotating assembly 102 to bias the rotating assembly 102 toward the closed end face 124 of the rotating assembly housing 104 (i.e., in the downstream direction). In another example, an elastic biasing member (e.g., one or more compression springs such as disc spring washers) may be present between the motor 1 and the rotating assembly 102 to bias the rotating assembly 102 toward the closed end face 124 of the rotating assembly housing 104.

[0027] In one or more embodiments, forcing the rotary assembly 102 downstream to create a compressive force at the interface between the one or more thrust bearings 116, the rotary assembly 102, and the rotary assembly housing 104 can be achieved by utilizing a motor mount that interconnects and engages with the rotary assembly housing 104 to bias the motor 1 toward the downstream end of the rotary assembly housing 104 for compression engagement with the one or more thrust bearings 116. The interconnected arrangement of the motor mount and the rotary assembly housing 104 secures the motor mount to the rotary assembly housing 104 and biases the rotary assembly 102 against the one or more thrust bearings 116. For example, the motor mount can include a body having a threaded portion that engages a mating threaded portion of the rotary assembly housing 104, through which an axial compressive (i.e., preload) force can be exerted on the interface between the one or more thrust bearings 116, the rotary assembly 102, and the rotary assembly housing 104. The motor mount may include an elastic member (e.g., a compression spring) that exerts a compressive force on the motor 1 in response to the motor mount being interconnected and engaged with the rotary assembly housing 104.

[0028] As best shown in FIGS. 2A, 3, and 4, the rotary assembly 102 includes an impeller 130, a rotating flow amplification body 132, and an outlet body 134. As described above, the rotary assembly 102 has a plurality of in-line flow guiding portions, namely, a flow pressurizing portion 102A, a rotating flow amplification portion 102B, and a flow outlet portion: 102C. The impeller 130 is one embodiment of the flow pressurizing portion 102A. The rotating flow amplification body 132 is one embodiment of the rotating flow amplification portion 102B. The outlet body 134 is one embodiment of the flow outlet portion 102C.

[0029] The impeller 130 has side walls 136 that extend around the axis of rotation R1 and define an internal space S2 of the impeller. The side walls 136 are tapered such that the impeller 130 has a first cross-sectional area adjacent to the first end EP130-1 and a second cross-sectional area adjacent to the second end EP130-2. The second cross-sectional area is larger than the first cross-sectional area. In a preferred embodiment, the impeller 130 is in the form of an inverted frustum pyramid. The centerline longitudinal axis A1 of the impeller 130 extends collinearly with the axis of rotation R1.

[0030] The side walls 136 include a plurality of flow guiding protrusions 138 each extending outwardly from the internal space S2 of the impeller 130. Each of the flow guiding protrusions 138 extends from a location adjacent to the first end EP130-1 of the impeller 130 to a location adjacent to the second end EP130-2 of the impeller 130. Each of the flow guiding protrusions 138 has a leading edge LE and a trailing edge TE with respect to the direction of rotation RD. Each of the flow guiding protrusions 138 has a fluid flow path 140 extending therethrough along at least a portion of the leading edge LE.

[0031] In one or more embodiments, the inlet port 108 can be inclined to have the same or a similar inclination as the protrusions 138 of the impeller 130. In one or more embodiments, the inlet port 108 may include protrusions on the inner surface of the rotary assembly housing 104 having the same or a similar profile as the protrusions 138 of the impeller 130. Preferably, the inlet port protrusions of the rotary assembly housing 104 extend inwardly from the outer wall of the rotary assembly housing 104. Such an inclination of the inlet port and the arrangement of the inlet port protrusions have a beneficial effect on the flow of fluid entering the internal space S of the impeller 130 through the inlet port.

[0032] Each of the flow guiding protrusions 138 extends with an upward inclination from a location adjacent to the first end EP130-1 of the impeller 130 in a direction opposite to the rotational direction RD of the rotary assembly 102. The term "upward inclination" is disclosed herein to include at least a portion of the flow guiding protrusion that extends in a non-parallel direction with respect to a reference axis extending radially from the rotation axis R1, i.e., the leading edge LE faces upstream. For example, the flow guiding protrusion 138 may have a straight longitudinal axis that is oblique with respect to the rotation axis, or may have a longitudinally axis that is at least partially curved such that at least a portion of the longitudinal axis is oblique with respect to the rotation axis.

[0033] Preferably, as best shown in FIGS. 5 and 6, each flow guiding protrusion 138 has an inner surface 136A and an outer surface 136B, i.e., opposing surfaces of the side wall 136. The inner surface 136A is offset from the outer surface 136B by a substantially uniform distance (e.g., the thickness of the side wall 136), whereby each flow guiding protrusion 138 defines a louver-shaped body that protrudes outwardly from the outer surface of the impeller 130 and forms a respective cavity within the inner surface of the impeller 130. Preferably, as best shown in FIG. 6, the fluid flow path 140 of each flow guiding protrusion 138 extends only along one central portion of each of the flow guiding protrusions. Thus, the first fluid flow stage FFS1 of each flow guiding protrusion 138 is defined between the first end EP130-1 of the impeller 130 and the lower end (i.e., the first end) of the fluid flow path 140, the second fluid flow stage FFS2 is defined between the lower end of the fluid flow path 140 and the second end (i.e., the upper end) of the fluid flow path 140, and the third fluid flow stage FFS3 is defined between the upper end of the fluid flow path 140 and the second end EP130-2 of the impeller 130. The first fluid flow stage FFS1 is the lowest region on the impeller 130, has the smallest diameter, has the smallest angular cut, and the lower corner may be boxed or otherwise closed.

[0034] The rotation flow amplification body 132 has a first end EP132-1 that engages with the second end EP130-2 of the impeller 130 so as to suppress unrestricted rotational movement between the second end EP130-2 of the impeller 130. In a preferred embodiment, such engagement includes a first interconnect interface 142 in the form of interconnect shoulders 142A, 142B. The interconnect shoulders 142A, 142B may have a trapezoidal profile such that the application of torque draws the interfaces into an interconnected configuration, i.e., considering mating tapered edge surfaces of the trapezoidal profile. Advantageously, the interconnect shoulders having a trapezoidal profile provide a secure locking interface that resists the separation of the various parts resulting from vibrations within the pump 100 during operation (i.e., application of rotational torque). In certain applications, the rotation flow amplification body according to the disclosure herein can be configured to be stackable (e.g., via end-to-end mating of opposing interconnect interfaces) for purposes such as enhancing downhole depth pumping performance.

[0035] The rotation flow amplification body 132 has a central passage 144. Preferably, the central passage 144 of the rotation flow amplification body 132 is circular and has a uniform maximum diameter. Preferably, the centerline axis A2 of the rotation flow amplification body 132 extends on the same straight line as the rotation axis R1, and the central passage 144 of the rotation flow amplification body 132 extends continuously into the internal space S1 of the impeller 130. A plurality of vanes 146 (e.g., spirals such as tapered semi-helices) extend from the inner surface 148 of the outer wall 149 that defines the central passage 144 of the rotation flow amplification body 132. Each of the vanes 146 extends from a location adjacent to the first end of the rotation flow amplification body in a direction opposite to the rotation direction RD with an upward inclination. Each of the vanes 146 can extend continuously along substantially the entire length of the inner surface 148 of the rotation flow amplification body 132. Each vane 146 preferably has the same overall length and the same profile.

[0036] Preferably, as shown in FIGS. 2A and 2B, the downstream facing surface 146A of each vane 146 and the inner surface 148 of the rotational flow amplification body 132 jointly form a cup-shaped surface 150. The cup-shaped surface 150 may extend along all or part of the entire length of each of the vanes 146. The cup-shaped surface 150 forms an elongated confinement space 151 in which a portion of the fluid in the central passage 144 is (at least temporarily) confined during rotation of the rotary assembly 102. Advantageously, this confinement of the fluid results in an increase in the amount of energy imparted to the fluid confined by the rotational flow amplification body 132 as compared to vanes that do not form the cup-shaped surface and the resulting confinement space. The greater amount of energy results from both an increase in the magnitude of the force imparted to the fluid confined by the cup-shaped surface 150 and the duration that such confined fluid remains within the confinement space 151. In one or more embodiments, the cup-shaped surface 150 and the confinement space 151 may be configured according to a Pelton cup-shaped blade.

[0037] As best shown in FIG. 8, each vane 146 can be inclined at an angle Θ (e.g., 45 degrees or more with respect to a radial reference line). In addition to the functionality of rotational flow amplification, such an inclination serves to help generate a strong axial load during rotation of the rotary assembly 102. The width and angle of the vanes 146 can be such that the inner edges 153 of each vane 146 are spaced apart from the other vanes 146, thereby opening (i.e., unobstructed) the central region of the rotational flow amplification body 132. This open central region is a location where the fluids flowing through the rotational flow amplification body 132 can merge and any suspended particles can pass freely without causing blockage. At the second end EP132-2 of the rotational flow amplification body 132, each vane 146 may have a radius at which each vane 146 terminates to allow for a wider flow and assist the rotational flow of the fluid as the fluid enters the outlet body 132.

[0038] As best shown in FIGS. 2A and 2C, the outlet body 132 has a first end EP134-1 that engages the second end EP132-2 of the rotational flow amplification body 132 to inhibit unrestricted rotational movement therebetween. In a preferred embodiment, such engagement includes a first interconnect interface 152 in the form of interconnect shoulders 152A, 152B. The interconnect shoulders 152A, 152B may have a trapezoidal profile such that application of torque draws the interfaces into an interconnected configuration, i.e., considering mating tapered edge surfaces of a trapezoidal profile.

[0039] The outlet body 134 has a central passage 154 that terminates at an outlet port 112 (i.e., the fluid outlet of the pump 100). Preferably, the centerline axis A3 of the outlet body 134 extends collinearly with the rotational axis R1, and the central passage 154 of the outlet body 134 extends continuously with the central passage 144 of the rotational flow amplification body 132. The central passage 154 of the outlet body 134 preferably has a uniform diameter portion 154A and a tapered portion 154B downstream of the uniform diameter portion 154A. The uniform diameter portion 154A is a flow gate 156 that connects to the tapered portion 154B. In a preferred embodiment, the tapered portion 154B has a 3:1 tapered taper over its length relative to the inner diameter of the central passage 144 of the rotational flow amplification body 132. The tapered portion 154B may have a linear or non-linear inner wall surface (as shown) as desired. The flow gate 156 may be preceded by a similarly uniform diameter portion of the rotational flow amplification body 132 downstream of the terminal end of the vane 146.

[0040] Next, referring to the operation of the pump 100, the motor 1 serves to rotate the rotating assembly 102 relative to the rotating assembly housing 104. With at least the inlet end IE of the pump 100 positioned within a fluid source (e.g., water), this rotation results in the intake, pressurization, rotational flow conversion, and output of fluid from the pump. In contrast to conventional ESPs, the operation of the pump 100 (i.e., the pump according to one or more embodiments of the disclosure made herein) advantageously provides enhanced operating functionality that results in improved performance, reliability, and durability. These enhanced operating functionalities result from the structural arrangement of the pump 100 that advantageously reduces pump pressure losses, reduces pump energy, and provides improved volumetric flow efficiency resulting from increased flow rates.

[0041] Advantageously, the rotation of the rotating assembly 102 generates a total dynamic head (TDH) that increases along with the net positive suction head (NPSH) formed at the fluid inlet of the impeller 130. NPSH is a measure of the pressure that the fluid experiences on the suction side of the pump. Thus, with respect to the pump 100, NPSH, in conjunction with the siphon effect, contributes to the acceleration of the fluid towards the rotational flow amplification body 132.

[0042] Rotation of the impeller 130 (i.e., the flow pressurizing portion of the rotating assembly 102) results in the intake and pressurization of the fluid in which at least the inlet end of the pump 100 is located. As described above with reference to FIG. 6, each fluid flow path 140 of the flow guiding protrusions 138 extends only along the central portion of each of the flow guiding protrusions such that the impeller 130 preferably includes a first fluid flow stage FFS1 (i.e., the portion of the impeller below the lower edge of the fluid flow path 140), a second fluid flow stage FFS2 (i.e., the portion of the impeller extending vertically along the length of the fluid flow path 140), and a third fluid flow stage FFS3 (i.e., the portion of the impeller above the upper edge of the fluid flow path 140). In this regard, each of the flow guiding protrusions 138 has three different functions. The first fluid flow stage FFS1 generates a siphon action that promotes the flow of fluid from the outside of the impeller 130 into the internal space S2 of the second fluid flow stage FFS2. In combination with the siphon action of the first fluid flow stage FFS1, the second fluid flow stage FFS2 draws the fluid into the internal space S2 of the second fluid flow stage FFS2 and compresses the fluid. The inner profile of the impeller 130 in the second fluid flow stage FFS2 and the third fluid flow stage FFS3 draws the fluid towards the rotation axis R1, begins to impart a rotational flow profile to the fluid, and pressurizes the fluid with respect to its inlet pressure. In this regard, after being supplied to the impeller 130, the fluid is pressurized to exhibit at least a partial rotational flow profile (i.e., in contrast to a random or laminar profile) and supplied into the rotational flow amplification body 132 (i.e., the rotational flow amplification portion of the rotating assembly 102).

[0043] Rotation of the rotation flow amplification body 132 (i.e., the rotation flow amplification part of the rotation assembly 102) results in a continuous conversion of the fluid into a rotating flow and an increase in any associated pressurization. For this purpose, the rotation flow amplification body 132 generates a fluid rotation (e.g., 360-degree fluid rotation) over the entire length of the rotation flow amplification body 132. Each vane 146 and the outer wall 149 jointly define their respective open surface flow chambers, and a portion of the fluid moves through the open surface flow chambers, thereby amplifying the rotating flow of the fluid initially generated within the impeller 130. The upstream end face of each vane 146 may be spaced apart from the impeller 130 to assist in the uniform mixing of the fluid when the fluid flows into the rotation flow amplification body 132.

[0044] The outlet body 134 (i.e., the flow outlet part of the rotation assembly 102) is the third stage and the final stage of the pump 100. The function of the outlet body 134 is to merge the streams of the rotating fluid flow exiting from the rotation flow amplification body 132, i.e., the fluid flows from the open surface flow chambers and the open central region of the rotation flow amplification body 132. The taper over the straight length of the tapered portion 134B of the outlet body 134 generates a compression strength within the streams of the rotating fluid flow. The kinetic energy is accumulated within this straight length in both its uniform profile and intensity. When the fluid exits the outlet body 134, its rotational flow profile is defined, and a focus of the kinetic energy in the output fluid flow is generated. The lifetime and flow distance of the focus are defined and controlled by parameters such as, for example, the rotational speed, fluid viscosity, transfer pipe diameter / length, etc.

[0045] Although the present invention has been described with reference to several exemplary embodiments, it is understood that the terms used are terms of description and illustration, not of limitation. Changes may be made within the scope and spirit of the present invention without departing from it in all aspects, and such changes can be made within the scope of the appended claims as presently stated and amended. The present invention has been described with reference to specific means, materials, and embodiments, but the present invention is not intended to be limited to the disclosed details. Rather, the present invention extends to all functionally equivalent technologies, structures, methods, and uses that fall within the scope of the appended claims.

Claims

1. A submersible pump, comprising: a rotating assembly having a plurality of in-line flow guiding portions, wherein the longitudinal axis of the center line of each of the flow guiding portions extends on the same straight line as the rotation axis of the rotating assembly, the downstream end of the flow pressurizing portion engages with the upstream end of the rotational flow amplification portion, and the downstream end of the rotational flow amplification portion engages with the upstream end of the flow outlet portion; and a rotating assembly housing having an internal space extending along its longitudinal axis of the center line, wherein the rotating assembly is disposed within the internal space of the rotating assembly housing.

2. The rotational flow amplification portion includes a plurality of bearings integral with its outer surface, each of the bearings having a circumferential outer surface that engages a mating portion of the inner surface of the rotating assembly housing that defines the internal space. The submersible pump according to claim 1.

3. Each of the bearings includes a groove within its circumferential outer surface. The submersible pump according to claim 2.

4. The internal space of the flow pressurizing portion continuously extends into the central passage of the rotational flow amplification portion, and the central passage of the rotational flow amplification portion continuously extends into the central passage of the flow outlet portion. The submersible pump according to claim 1.

5. The closed end of the internal space of the flow pressurizing portion, on the side opposite to its downstream end, has a maximum inner diameter smaller than the maximum inner diameter at the downstream end of the internal space of the flow pressurizing portion, the internal space of the flow pressurizing portion has the same maximum inner diameter at its downstream end as the maximum inner diameter of the central passage of the rotational flow amplification portion, the central passage of the rotational flow amplification portion has the same maximum inner diameter as the maximum inner diameter at the upstream end of the central passage of the flow outlet portion, and the central passage of the flow outlet portion has a cross-sectional area that tapers from the maximum inner diameter at its upstream end to a smaller inner diameter at its downstream end along its length. The submersible pump according to claim 4.

6. The flow pressurizing portion includes an impeller having side walls that extend around the rotation axis and define an internal space of the impeller, the side walls being tapered such that the impeller has a first cross-sectional area adjacent to its first end and a second cross-sectional area adjacent to its second end, and the second cross-sectional area is larger than the first cross-sectional area. The side wall includes a plurality of flow guiding protrusions, each of which extends outwardly away from the internal space of the impeller and extends from a location adjacent to the first end of the impeller with an inclined portion in a direction opposite to the rotation direction of the rotary assembly. Each of the flow guiding protrusions extends from a location adjacent to the first end of the impeller to a location adjacent to the second end of the impeller. Each of the flow guiding protrusions has a leading edge and a trailing edge with respect to the rotation direction. The underwater pump according to claim 1, wherein each of the flow guiding protrusions has a fluid flow path extending through the flow guiding protrusion at its leading edge.

7. The fluid flow path of each of the flow guiding protrusions extends only along a central portion of each of the flow guiding protrusions, thereby defining a first fluid flow stage between the first end of the impeller and the first end of the fluid flow path, a second fluid flow stage between the first end and the second end of the fluid flow path, and a third fluid flow stage between the second end of the fluid flow path and the second end of the impeller. The underwater pump according to claim 6.

8. The underwater pump according to claim 6, wherein each of the flow guiding protrusions defines a cavity within the inner surface of the side wall.

9. The rotary flow amplification body has an elongated central passage. A plurality of vanes extend from the inner surface of the rotary flow amplification body defining the elongated central passage. The underwater pump according to claim 6, wherein each of the vanes extends from a location adjacent to the first end of the rotary flow amplification body with an inclined portion in a direction opposite to the rotation direction of the rotary assembly.

10. The underwater pump according to claim 9, wherein each of the vanes has a cup-shaped surface on the side facing downstream thereof.

11. The rotary flow amplification body has an elongated central passage. A plurality of vanes extend from the inner surface of the rotary flow amplification body defining the elongated central passage. The underwater pump according to claim 1, wherein each of the vanes extends from a location adjacent to the first end of the rotary flow amplification body with an inclined portion in a direction opposite to the rotation direction of the rotary assembly.

12. The underwater pump according to claim 11, wherein each of the vanes has a cup-shaped surface on the side facing downstream thereof.

13. The underwater pump according to claim 11, wherein each of the vanes extends continuously along the entire length of the inner surface of the rotary flow amplification body.

14. The internal space of the flow pressurizing portion extends continuously into the central passage of the rotary flow amplification portion. The central passage of the rotary flow amplification portion extends continuously into the central passage of the flow outlet portion. The closed end of the internal space of the flow pressurizing portion on the side opposite to its downstream end has a maximum inner diameter smaller than the maximum inner diameter at the downstream end of the internal space of the flow pressurizing portion. The internal space of the flow pressurizing portion has the same maximum inner diameter at its downstream end as the maximum inner diameter of the central passage of the rotary flow amplification portion. The central passage of the rotary flow amplification portion has the same maximum inner diameter as the maximum inner diameter at the upstream end of the central passage of the flow outlet portion. The underwater pump according to claim 11, wherein the central passage of the flow outlet portion has a cross-sectional area that tapers along its length from the maximum inner diameter at its upstream end to a smaller inner diameter at its downstream end.

15. The underwater pump according to claim 14, wherein each of the vanes has a cup-shaped surface on the side facing downstream.

16. The underwater pump according to claim 15, wherein each of the vanes extends continuously along the entire length of the inner surface of the rotary flow amplification body.

17. The first in-line flow guiding portion of the in-line flow guiding portions includes an impeller. The second in-line flow guiding portion of the in-line flow guiding portions includes a rotary flow amplification body. The underwater pump according to claim 1, wherein the third in-line flow guiding portion of the in-line flow guiding portions includes an outlet body.

18. The impeller has side walls that extend around a rotation axis and define an internal space of the impeller. The side walls are tapered such that the impeller has a first cross-sectional area adjacent to its first end and a second cross-sectional area adjacent to its second end. The second cross-sectional area is larger than the first cross-sectional area. The side walls include a plurality of flow guiding protrusions, each of which extends outwardly away from the internal space of the impeller and extends from a location adjacent to the first end of the impeller with an inclined portion in a direction opposite to the rotation direction of the rotary assembly. Each of the flow guiding protrusions extends from a location adjacent to the first end of the impeller to a location adjacent to the second end of the impeller. Each of the flow guiding protrusions has a leading edge and a trailing edge with respect to the rotational direction. The underwater pump according to claim 17, wherein each of the flow guiding protrusions has a fluid flow path extending through the flow guiding protrusion along at least a portion of its leading edge.

19. The rotational flow amplification body has a first end engaged with the second end of the impeller so as to suppress unrestricted rotational movement between the second end of the impeller and the rotational flow amplification body at least in the rotational direction. The rotational flow amplification body has an elongated central passage. The central axis of the rotational flow amplification body extends on the same straight line as the rotational axis. A plurality of vanes extend from the inner surface of the rotational flow amplification body defining the elongated central passage. The underwater pump according to claim 18, wherein each of the vanes extends from a location adjacent to the first end of the rotational flow amplification body with an inclined portion in a direction opposite to the rotational direction of the rotational assembly.

20. The outlet body has a first end engaged with the second end of the rotational flow amplification body so as to suppress unrestricted rotational movement between the second end of the rotational flow amplification body and the outlet body at least in the rotational direction. The underwater pump according to claim 19, wherein the central axis of the outlet body extends on the same straight line as the rotational axis.

21. The rotational flow amplification portion includes a plurality of bearings integral with its outer surface. The underwater pump according to claim 19, wherein each of the bearings has a circumferential outer surface engaged with a fitting portion of the inner surface of the rotational assembly housing defining its internal space.

22. The underwater pump according to claim 19, wherein each of the vanes has a cup-shaped surface on the side facing downstream thereof.

23. The underwater pump according to claim 19, wherein each of the vanes extends continuously along the entire length of the inner surface of the rotational flow amplification body.

24. The underwater pump according to claim 18, wherein each of the flow guiding protrusions has an inner surface offset by a uniform distance from its outer surface so that the flow guiding protrusions define a cavity within the inner surface of the side wall facing the protrusions.

25. Each of the fluid flow paths of the flow guiding protrusions extends only along one central portion of each of the flow guiding protrusions, whereby a first fluid flow stage between the first end of the impeller and the first end of the fluid flow path, a second fluid flow stage between the first end and the second end of the fluid flow path, and a third fluid flow stage between the second end of the fluid flow path and the second end of the impeller are defined. The submersible pump according to claim 18.

26. Each of the flow guiding protrusions has an inner surface offset by a uniform distance from its outer surface so that each of the flow guiding protrusions defines a cavity within the inner surface of the side wall facing the protrusion. The submersible pump according to claim 25.

27. The rotational flow amplification body has a first end engaged with the second end of the impeller so as to suppress unrestricted rotational movement between the second end of the impeller and the rotational flow amplification body, at least in the rotational direction. The rotational flow amplification body has an elongated central passage. The central axis of the rotational flow amplification body extends on the same straight line as the rotation axis. A plurality of vanes extend from the inner surface of the rotational flow amplification body defining the elongated central passage. Each of the vanes extends with an inclined portion from a location adjacent to the first end of the rotational flow amplification body in a direction opposite to the rotational direction of the rotational assembly. The submersible pump according to claim 26.

28. The outlet body has a first end engaged with the second end of the rotational flow amplification body so as to suppress unrestricted rotational movement between the second end of the rotational flow amplification body and the outlet body, at least in the rotational direction. The central axis of the outlet body extends on the same straight line as the rotation axis. The submersible pump according to claim 27.

29. The rotational flow amplification portion includes a plurality of bearings integral with its outer surface. Each of the bearings has a circumferential outer surface that engages a fitting portion of the inner surface of the rotational assembly housing that defines its internal space. The submersible pump according to claim 27.

30. Each of the vanes has a cup-shaped surface on the side facing downstream. Each of the vanes extends continuously along the entire length of the inner surface of the rotational flow amplification body. The submersible pump according to claim 27.

31. One of the in-line flow guiding portions includes a rotational flow amplification body. The rotational flow amplification portion includes a plurality of bearings integral with its outer surface. The water pump according to claim 1, wherein each of the bearings has a circumferential outer surface that engages with a fitting portion on the inner surface of the rotary assembly housing that defines the inner space thereof.

32. One of the in-line flow guiding portions includes a rotary flow amplification body, a plurality of vanes extending from the inner surface of the rotary flow amplification body that defines an elongated central passage of the rotary flow amplification body, each of the vanes extending from a location adjacent to the first end of the rotary flow amplification body with an inclined portion in a direction opposite to the rotary direction of the rotary assembly, each of the vanes having a cup-shaped surface on the side facing downstream thereof, The water pump according to claim 1, wherein each of the vanes extends continuously along the entire length of the inner surface of the rotary flow amplification body.

33. The water pump according to claim 32, wherein each of the vanes has a cup-shaped surface on the side facing downstream thereof.

34. The water pump according to claim 33, wherein each of the vanes extends continuously along the entire length of the inner surface of the rotary flow amplification body.

Images