Patent Application
20180216622
The field of the disclosure relates generally to centrifugal pump assemblies, and more specifically, to centrifugal pump assemblies that include an axial flux electric motor coupled to an impeller.
At least some known centrifugal pumps include an impeller for channeling a fluid through the pump. The impeller is coupled to a shaft via a hydrostatic bearing, which is coupled to a rotor of an electric motor such that rotation of the rotor causes rotation of the bearing and the impeller. In at least some known electric motors, a separate pump is used to deliver a pressurized fluid flow required for operation of the hydrostatic bearing. An additional pump increases both the complexity and cost of the pump system, which may inhibit the use of hydrostatic bearings in cost sensitive applications.
Furthermore, at least some known centrifugal pumps include hydrodynamic bearings. When designing a hydrodynamic bearing there are a number of factors to consider. One of them is the ability of the bearing to hydro dynamically ‘lift’ in operation and separate the rotating bearing component from the stationary bearing component. It is critical the bearing ‘lifts’ to ensure correct operation. If the bearing does not ‘lift’ there will be large friction between the two bearing materials causing large friction torque resistance, drag torque resistance and material ware. To ensure bearing lift, the bearing is designed to have a pressure velocity (PV) factor to fall within a predetermined range. The PV factor is based on the velocity of the rotating component and the coefficient of friction between the rotating bearing component and the stationary bearing component. However, at least some known rotating bearing components are flat disks, leading to a velocity differential between the inner diameter and the outer diameter of the disk. This velocity differential leads to a wide range of PV factors, at least some of which may be outside the desired range. Operational of the hydrodynamic bearing outside the desired PV factor range may lead to inefficient operation of the pump assembly and/or to a shortened service lifetime of the bearing components.
In one aspect, an electric motor assembly is provided. The electric motor assembly includes a bearing assembly including a rotating component and at least one stationary component. The electric motor assembly also includes an impeller coupled to the rotating component. The impeller includes an inlet and an outlet and is configured to direct a fluid between the inlet and the outlet. The electric motor assembly also includes a rotor assembly directly coupled to the impeller. A fluid flow channel is defined between the rotating component and the at least one stationary component. The flow channel includes a first end proximate the impeller outlet and a second end proximate the impeller inlet.
In another aspect, a pump assembly is provided. The pump assembly includes a pump housing and a motor housing coupled to the pump housing. The pump assembly also includes an electric motor assembly including a bearing assembly including a rotating component and at least one stationary component. The electric motor assembly also includes an impeller coupled to the rotating component. The impeller includes an inlet and an outlet and is configured to direct a fluid between the inlet and the outlet. The electric motor assembly also includes a rotor assembly directly coupled to the impeller. A fluid flow channel is defined between the rotating component and the at least one stationary component. The flow channel includes a first end proximate the impeller outlet and a second end proximate the impeller inlet.
In yet another aspect, a method of assembling a pump assembly is provided. The method includes providing a bearing assembly including a rotating component and at least one stationary component. The method also includes coupling an impeller to the rotating component, wherein the impeller includes an inlet and an outlet and is configured to direct a fluid therebetween. A rotor assembly is directly coupled to the impeller. The method also includes defining a fluid flow channel between the rotating component and the at least one stationary component. The flow channel includes a first end proximate the impeller outlet and a second end proximate the impeller inlet.
In one aspect, a hydrodynamic bearing assembly is provided. The hydrodynamic bearing assembly includes a first stationary component, a shaft coupled to the first stationary component, and a second stationary component coupled to the shaft opposite the first stationary component. The hydrodynamic bearing assembly also includes a rotating component coupled to the shaft between the first stationary component and the second stationary component. The rotating component includes a first end surface including a first diameter and an opposing second end surface including a second diameter that is greater than the first diameter.
In another aspect, a pump assembly is provided. The pump assembly includes a hydrodynamic bearing assembly includes a first stationary component, a shaft coupled to the first stationary component, and a second stationary component coupled to the shaft opposite the first stationary component. The hydrodynamic bearing assembly also includes a rotating component coupled to the shaft between the first stationary component and the second stationary component. The rotating component includes a first end surface including a first diameter and an opposing second end surface including a second diameter that is greater than the first diameter. The pump assembly also includes an impeller coupled to the rotating component and a rotor assembly directly coupled to the impeller.
Although specific features of various embodiments may be shown in some drawings and not in others, this is for convenience only. Any feature of any drawing may be referenced and/or claimed in combination with any feature of any other drawing.
In the exemplary embodiment, impeller 104 is positioned within pump housing 106 and includes an inlet ring 118 that defines an inlet opening 120. Impeller 104 also includes a rear plate 122 and a plurality of blades 124 coupled between inlet ring 118 and rear plate 122. As described in further detail herein, rear plate 122 of impeller 102 is coupled directly to motor assembly 102 such that motor assembly 102 is configured to rotate impeller 102 about a rotational axis 126. In operation, motor 102 rotates impeller 104 about axis 126 to draw fluid in an axial direction into pump housing 106 through housing inlet 110. The fluid is channeled through inlet opening 120 in inlet ring 118 and turned by blades 124 within channel 114 to direct the fluid along wall 112 and radially through housing outlet 116. The amount of fluid moved by pump assembly 100 increases as impeller 104 speed increases such that impeller 104 generates high velocity fluid flow that is exhausted from outlet 116.
Impeller 104 imparts kinetic energy into the pumped fluid as it rotates that causes the fluid to pressurize. That is, an area 127 of negatively pressurized fluid exists upstream of impeller 104, and more specifically, upstream of impeller blades 124 proximate inlets 110 and 120. Correspondingly, an area 129 of positively pressurized fluid exists downstream of impeller 104 proximate outlet 116 of housing 106. As such, rotation of impeller 104 causes a pressure differential across impeller 104. In the exemplary embodiment, the negatively pressurized fluid imparts an axial suction force 128 on impeller 104. Axial force 128 acts in an axial direction away from motor assembly 102 through pump housing inlet 110. As the speed of impeller 104 increases, both the pressure of the fluid and the resulting axial suction force 128 also increase correspondingly. That it, the magnitude of axial suction force 128 is based on the rotational speed of impeller 104.
In the exemplary embodiment, motor assembly 102 includes a stator assembly 130 including a magnetic stator core 134 and a plurality of conductor coils 136 positioned within motor housing 108. Motor assembly 102 also includes a bearing assembly 138 and a rotor assembly 140. Each conductor coil 136 includes an opening (not shown) that closely conforms to an external shape of one of a plurality of stator core teeth (not shown) such that each stator tooth is configured to be positioned within a conductor coil 136. Motor assembly 102 may include one conductor coil 136 per stator tooth or one conductor coil 136 positioned on every other tooth.
In the exemplary embodiment, a variable frequency drive (not shown) provides a signal, for example, a pulse width modulated (PWM) signal, to motor 102. In an alternative embodiment, motor 102 may include a controller (not shown) coupled to conductor coils 136 by wiring. The controller is configured to apply a voltage to one or more of conductor coils 136 at a time for commutating conductor coils 136 in a preselected sequence to rotate rotor assembly 140 about axis 126.
Rotor assembly 140 is positioned within pump housing 106 proximate cavity 114 and includes a back iron or rotor disk 146 having at least a first axial surface 148. In the exemplary embodiment, rotor assembly 140 also includes a plurality of permanent magnets 152 coupled directly to rotor disk 146. In another embodiment, rotor assembly 140 includes a magnet retainer (not shown) coupled to rotor disk 146 opposite impeller 104, and permanent magnets 152 are coupled to the magnet retainer.
As best shown in
In the exemplary embodiment, rotor assembly 140 is positioned adjacent stator assembly 130 to define an axial gap 154 therebetween. A liner (not shown) surrounds stator assembly 130 to prevent core 134 and coils 136 from being exposed to the fluid within housings 106 and 108. As described above, voltage is applied to coils 136 in sequence to cause rotation of rotor assembly 140. More specifically, coils 136 control the flow of magnetic flux between magnetic stator core 134 and permanent magnets 152. Magnets 152 are attracted to magnetic stator core 134 such that an axial magnetic force (not shown) is ever-present across gap 154. As such, stator core 134 of stator assembly 130 imparts the axial magnetic force to rotor assembly 140 in an axial direction away from impeller 104. More specifically, the axial magnetic force acts in a direction opposite of axial suction force 128 of impeller 104. As the size of axial gap 154 decreases, the axial magnetic force between stator assembly 130 and rotor assembly 140 increases. That is, the magnitude of the axial magnetic force is based on a length of axial gap 154.
In the exemplary embodiment, impeller 104 includes a cylindrical extension 157 that extends axially from rear plate 122 towards motor housing 108. More specifically, extension 157 extends axially passed rotor assembly 140 and into an opening 132 defined by stator core 134 to at least partially axially overlap with stator assembly 130. Furthermore, extension 157 is coupled to a rotating component 170 of bearing assembly 138. Rotating component 170 circumscribes a stationary shaft 172 of bearing assembly 138 and is positioned axially between a first stationary component 174 and a second stationary component 176 of bearing assembly 138. In the exemplary embodiment, bearing assembly 138 includes a hydrodynamic bearing.
As best shown in
As shown in
In operation, conductor coils 136 coupled to stator core 134 are energized in a chronological sequence that provides an axial magnetic field which moves clockwise or counterclockwise around stator core 134 depending on the pre-determined sequence or order in which conductor coils 136 are energized. This moving magnetic field intersects with the flux field created by the plurality of permanent magnets 152 to cause rotor assembly 140 to rotate about axis 126 relative to stator assembly 130 in the desired direction. As described herein, because rotor disk 146 is directly coupled to impeller 104, rotation of rotor disk 146 causes rotation of impeller 104, which pressurizes the fluid flowing through impeller 104 from inlet 120 to outlet 116. The resulting pressure differential across impeller 104, and rotor assembly 140, and locating channel inlet 180 on positive pressure side 129 and channel outlet 182 on negative pressure side 127 of impeller 104 forces fluid through flow channel 178. The fluid through channel 178 pressurizes bearing assembly 138 and overcomes the axial magnetic force between stator assembly 130 and rotor assembly 140 to enable operation of assembly 100 as described herein. Accordingly, the pressure differential across impeller 104 and rotor assembly 140 enables pressurization of bearing assembly 138 without requiring a separate pump.
As shown in
In operation, conductor coils 136 coupled to stator core 134 are energized in a chronological sequence that provides an axial magnetic field which moves clockwise or counterclockwise around stator core 134 depending on the pre-determined sequence or order in which conductor coils 136 are energized. This moving magnetic field intersects with the flux field created by the plurality of permanent magnets 152 to cause rotor assembly 140 to rotate about axis 126 relative to stator assembly 130 in the desired direction. As described herein, because rotor disk 146 is directly coupled to impeller 104, rotation of rotor disk 146 causes rotation of impeller 104, which pressurizes the fluid flowing through impeller 104 from inlet 120 to outlet 116. The resulting pressure differential across impeller 104, and rotor assembly 140, and locating channel inlet 180 on positive pressure side 129 and channel outlet 182 on negative pressure side 127 of impeller 104 forces fluid through flow channel 190. The fluid through channel 190 pressurizes bearing assembly 138 and overcomes the axial magnetic force between stator assembly 130 and rotor assembly 140 to enable operation of assembly 100 as described herein. Accordingly, the pressure differential across impeller 104 and rotor assembly 140 enables pressurization of bearing assembly 138 without requiring a separate pump.
In the embodiment, to ensure bearing lift, bearing assembly 138 is designed to have a pressure velocity (PV) factor to fall within a predetermined range. The PV factor is based on the velocity of rotating component 202 and the coefficient of friction between rotating component 202 and second stationary component 176. However, as shown in
As shown in
As shown in
As can be seen, the shape of body surface 210 causes rotating component 202 to have a diameter that changes based on a location along the axial length of rotating component 202. The changing diameter causes a distributed force, illustrated by arrows 212, along first end surface 206 and body surface 210. Arrows indicate that as the diameter of rotating component 202 increases along axis 126, less axial force is imparted to rotating component 202 such that more force is imparted to rotating component proximate first end surface 206 than proximate second end surface 208. As shown in
Referring back to
Referring back to
In operation, conductor coils 136 coupled to stator core 134 are energized in a chronological sequence that provides an axial magnetic field which moves clockwise or counterclockwise around stator core 134 depending on the pre-determined sequence or order in which conductor coils 136 are energized. This moving magnetic field intersects with the flux field created by the plurality of permanent magnets 152 to cause rotor assembly 140 to rotate about axis 126 relative to stator assembly 130 in the desired direction. As described herein, because rotor disk 146 is directly coupled to impeller 104, rotation of rotor disk 146 causes rotation of impeller 104, which pressurizes the fluid flowing through impeller 104 from inlet 120 to outlet 116. The resulting pressure differential across impeller 104, and rotor assembly 140, and locating channel inlet 180 on positive pressure side 129 and channel outlet 182 on negative pressure side 127 of impeller 104 forces fluid through flow channel 178. The fluid through channel 178 pressurizes bearing assembly 138 and overcomes the axial magnetic force between stator assembly 130 and rotor assembly 140 to enable operation of assembly 100 as described herein.
The apparatus, methods, and systems described herein provide a pump assembly having an electric motor coupled to an impeller. More specifically, a rotor assembly of the motor is directly coupled to the impeller. The impeller includes an inlet and an outlet and is configured to direct a fluid therebetween and is also coupled to a rotating component of a bearing assembly. A fluid flow channel is defined between the rotating component and at least one stationary component of the bearing assembly. The flow channel includes an inlet proximate the impeller outlet and an outlet proximate the impeller inlet. As described herein, because the rotor disk is directly coupled to the impeller, rotation of the rotor disk causes rotation of the impeller, which pressurizes the fluid flowing from the impeller inlet to the impeller outlet. The resulting pressure differential across the impeller combined with locating the channel inlet on the positive pressure side of the impeller and locating the channel outlet on the negative pressure side of the impeller forces fluid through the flow channel. The fluid through the flow channel pressurizes the bearing assembly to enable operation of assembly 100 as described herein without requiring a separate pump.
Furthermore, tapering the diameter of the rotating component of the bearing assembly over its length to have a graduated distributed force compensates for the graduated velocity along the radius of the rotating component's end surface. Such a configuration results in an optimal, narrower, PV factor range over the radius the end surface. A substantially constant PV factor across the rotating component end surface leads to more efficient operation of the bearing assembly and an increased service lifetime of its rotating and stationary components.
Exemplary embodiments of the centrifugal pump assembly are described above in detail. The centrifugal pump assembly and its components are not limited to the specific embodiments described herein, but rather, components of the systems may be utilized independently and separately from other components described herein. For example, the components may also be used in combination with other machine systems, methods, and apparatuses, and are not limited to practice with only the systems and apparatus as described herein. Rather, the exemplary embodiments can be implemented and utilized in connection with many other applications.
Although specific features of various embodiments of the disclosure may be shown in some drawings and not in others, this is for convenience only. In accordance with the principles of the disclosure, any feature of a drawing may be referenced and/or claimed in combination with any feature of any other drawing.
This written description uses examples to disclose the invention, including the best mode, and to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims.
