Rotor and balancing method with balancing features

Abstract

This invention relates to a rotor with balancing features and a balancing method. A rotor for a fluid machine includes an impeller having a plurality of blades. Furthermore, the rotor includes an inter-blade region circumferentially defined relative to an axis of rotation between a first blade and a second blade. The rotor also includes a balancing mark portion located on the impeller and within the inter-blade region. The balancing mark portion is elongated and has a first end and a second end. The first and second ends axially step into the inter-blade region. The balancing mark portion extends arcuately between the first and second ends. The balancing mark portion has a depth that varies as it extends arcuately between the first and second ends. The balancing mark portion has a width that varies as it extends arcuately between the first and second ends.

Description

Technical Field

[0001] This disclosure generally relates to rotors for rotating machines, and more specifically, to rotors having balancing characteristics and methods for balancing rotors, such as the rotors of turbochargers. Background Technology

[0002] Fluid machines include rotors supported for rotation within them. These rotors rotate to convert the energy of a fluid into mechanical energy, or vice versa. For example, a vehicle turbocharger includes a rotor that rotates within a housing. This rotor can be driven to rotate to improve the performance of an internal combustion engine. More specifically, these devices can improve engine efficiency and power output by forcing additional air into the engine's combustion chamber.

[0003] The rotor is preferably supported for balanced rotation about its axis of rotation. If the rotor is sufficiently balanced, unwanted vibrations or other loads can be reduced. However, the balancing method may adversely affect the rotor's strength or other properties. Furthermore, it may be impossible to obtain sufficient access to the rotor to perform conventional balancing methods. Additionally, balancing methods may be difficult, inconvenient, labor-intensive, etc.

[0004] Therefore, it is desirable to provide a rotor with improved balancing characteristics. It is also desirable to provide a balancing method that accurately and precisely balances the rotor while maintaining its integrity. Furthermore, it is desirable to provide an improved balancing method that is convenient, accurate, and improves manufacturing efficiency. Other desirable features and characteristics of this disclosure will become apparent from the following detailed description and appended claims, taken in conjunction with the accompanying drawings and this background discussion. Summary of the Invention

[0005] In one embodiment, a rotor for a fluid machine is disclosed. The rotor includes an impeller supported for rotation about an axis of rotation. The rotor also includes a plurality of blades included on the impeller. Furthermore, the rotor includes an inter-blade region circumferentially defined relative to the axis of rotation between a first blade and a second blade of the plurality of blades. Additionally, the rotor includes a balancing mark located on the impeller and within the inter-blade region. The balancing mark is elongated and has a first end and a second end. The first and second ends enter the inter-blade region in a stepped manner axially. The balancing mark extends arcuately between the first and second ends. The balancing mark has a depth that varies as it extends arcuately between the first and second ends. The balancing mark has a width that varies as it extends arcuately between the first and second ends.

[0006] Furthermore, a method for balancing the rotor of a fluid machine is disclosed. The method includes supporting an impeller for rotation about a rotation axis. The impeller includes a plurality of blades. The impeller also includes an inter-blade region circumferentially defined relative to the rotation axis between a first blade and a second blade. The method further includes forming a balancing mark portion on the impeller and in the inter-blade region. The balancing mark portion is elongated and has a first end and a second end. The first end and the second end enter the inter-blade region in a stepped manner axially. The balancing mark portion extends arcuately between the first end and the second end. The balancing mark portion has a depth that varies as it extends arcuately between the first end and the second end. The balancing mark portion has a width that varies as it extends arcuately between the first end and the second end.

[0007] In another embodiment, a fluid charger device is disclosed. The fluid charger device includes a housing and a rotor supported for rotation within the housing, the rotor being rotated about a rotation axis. The fluid charger device also includes an impeller of the rotor, the impeller comprising a plurality of blades and defining a direction of rotation about the rotation axis. The fluid charger device also includes an inter-blade region circumferentially defined relative to the fluid axis between a first blade and a second blade of the plurality of blades. Additionally, the fluid charger device includes a balancing mark portion located on the impeller and in the inter-blade region. The balancing mark portion is elongated and has a first end and a second end. The first end and the second end enter the inter-blade region in a stepped manner axially. The balancing mark portion extends arcuately between the first end and the second end. The balancing mark portion has a depth that varies as it extends arcuately between the first end and the second end. The balancing mark portion has a width that varies as it extends arcuately between the first end and the second end. The first end and the second end are cup-shaped ends. Furthermore, relative to the direction of rotation, the first blade includes a pressure side, and the second blade includes a suction side. The pressure side extends across the inter-blade region towards the suction side. The first end is positioned near the pressure side of the first blade, and the second end is positioned near the suction side of the second blade. The first end is deeper and wider than the second end. Attached Figure Description

[0008] The present disclosure will be described below in conjunction with the accompanying drawings, in which the same reference numerals denote the same elements, and wherein:

[0009] Figure 1 This is a schematic diagram of a turbocharger system having a balanced rotor according to an exemplary embodiment of the present disclosure;

[0010] Figure 2 It is an embodiment with a balance mark section according to an exemplary embodiment. Figure 1A front view of the compressor impeller of the rotor;

[0011] Figure 3 It is along Figure 2 A sectional view of the compressor impeller taken from line 3-3;

[0012] Figure 4 This illustration shows the balance according to an exemplary embodiment. Figure 2 and Figure 3 A flowchart of the rotor method;

[0013] Figure 5 This is for balancing according to an exemplary embodiment. Figure 2-3 A schematic diagram of the rotor's balancing system;

[0014] Figure 6 This is a schematic side view of a compressor impeller and a cutting tool for forming a balancing feature, according to an exemplary embodiment;

[0015] Figure 7 This is a schematic end view of a compressor impeller and a cutting tool according to an exemplary embodiment;

[0016] Figure 8 This is a schematic end view of the compressor impeller and cutting tool according to an additional exemplary embodiment;

[0017] Figure 9 It is an example of a device with a balance mark according to an additional exemplary embodiment of this disclosure. Figure 1 A front view of the compressor impeller of the rotor;

[0018] Figure 10 It is an embodiment with a balance mark portion according to an additional exemplary embodiment of this disclosure. Figure 1 A front view of the compressor impeller of the rotor; and

[0019] Figure 11 It is an example of a device with a balance mark according to an additional exemplary embodiment of this disclosure. Figure 1 Front view of the compressor impeller rotor. Detailed Implementation

[0020] The following detailed description is exemplary in nature only and is not intended to limit this disclosure or its application and use. Furthermore, there is no intention to be bound by the foregoing background information or any theory set forth in the following detailed description.

[0021] Broadly speaking, the exemplary embodiments disclosed herein include a rotor of fluid machinery, such as a turbocharger or other filling device for a vehicle. The rotor may include an impeller supported for rotation about an axis of rotation, such as a compressor impeller. The impeller may include a plurality of blades spaced apart about the axis of rotation. Furthermore, the rotor may include at least one balancing mark portion, such as a recess, groove, notch, channel, or other aperture, included in the inter-blade region of the impeller. The balancing mark portion may be elongated and may include a defined and shaped first end and a second end. At least one end may be cup-shaped (i.e., cup-shaped in form) to include a three-dimensional profile, and the elongated balancing mark portion may extend away from the cup-shaped end. In some embodiments, both the first and second ends may be shaped to have cup-shaped, profiled surfaces, and the elongated balancing mark portion may extend between them. Width and / or depth may vary between the first and second ends. The width, depth, position, and / or other features of the balancing feature may be configured to reduce rotor imbalance. Furthermore, these features may be configured according to predetermined characteristics of the impeller. For example, the width, depth, location, and / or other features can be configured according to the known stress profile of the impeller. In some embodiments, for example, the deepest and / or widest portion of the balancing mark can be positioned closer to the pressure side of a blade, while the shallower and narrower portions can be positioned closer to the suction side of an adjacent blade. In the illustrated embodiment, a higher stress margin can typically be present on the pressure side; therefore, more material can be obtained for removal without negatively impacting impeller strength, robustness, etc. Furthermore, the balancing mark can be angularly and radially positioned at predetermined locations and can extend along a predetermined region of the impeller. The balancing mark can be positioned according to specific characteristics of the impeller. Methods for manufacturing these rotors and methods for balancing these rotors are also disclosed according to exemplary embodiments of this disclosure.

[0022] Therefore, the rotor can be accurately and precisely balanced using balancing markings, such as holes, recesses, grooves, and notches, tailored to specific impellers and impeller configurations. This teaching provides high-quality, balanced rotors and efficient methods for manufacturing such rotors.

[0023] Figure 1 This is a schematic diagram of an exemplary turbocharger system 100 including a turbocharger 112. The turbocharger 112 generally includes a turbocharger housing 101 and a rotor 102. The rotor 102 is configured to rotate within the turbocharger housing 101 about a rotor rotation axis 103. The rotor 102 may be supported for rotation about the axis 103 via one or more bearings (not shown). In some embodiments, the rotor 102 may be rotatably supported by a thrust bearing and a plurality of journal bearings. Alternatively, other bearings may also be included.

[0024] As shown in the illustrated embodiment, the turbocharger housing 101 may include a turbine housing 105, a compressor housing 107, and a bearing housing 109. The bearing housing 109 may be disposed between the turbine housing 105 and the compressor housing 107. Furthermore, in some embodiments, the bearing housing 109 may also include a bearing for the rotor 102.

[0025] Additionally, rotor 102 includes a turbine impeller 111, a compressor impeller 113, and a shaft 115. The turbine impeller 111 is substantially located within the turbine housing 105. The compressor impeller 113 is substantially located within the compressor housing 107. Shaft 115 extends along the axis of rotation 103, passing through a bearing housing 109, to connect the turbine impeller 111 to the compressor impeller 113. Therefore, the turbine impeller 111 and the compressor impeller 113 rotate together about axis 103.

[0026] Turbine housing 105 and turbine impeller 111 cooperate to form a turbine (i.e., turbine stage), which causes circumferential reception of a high-pressure and high-temperature exhaust flow 121 from an engine (e.g., from exhaust manifold 123 of internal combustion engine 125). Turbine impeller 111, and thus rotor 102, is driven by the high-pressure and high-temperature exhaust flow 121 to rotate about axis 103, which becomes a low-pressure and low-temperature exhaust flow 127 released into downstream exhaust pipe 126. In other embodiments, engine 125 may be of another type, such as a diesel fuel engine.

[0027] The compressor housing 107 and compressor impeller 113 form a compressor (i.e., a compressor section, compressor stage). The compressor impeller 113, driven by the rotation of the exhaust-driven turbine impeller 111, is configured to compress received input air 131 (e.g., ambient air, or pre-pressurized air from a previous stage in a multi-stage compressor) into a pressurized airflow 133 that is circumferentially ejected from the compressor housing 107. The compressor housing 107 may have a shape (e.g., a volute shape or others) configured to guide and pressurize the air blown out from the compressor impeller 113. Due to the compression process, the pressurized airflow 133 is characterized by an increased temperature exceeding that of the input air 131.

[0028] The pressurized airflow 133 can be directed through an air cooler 144 (i.e., an intercooler), such as a convection-cooled booster air cooler. The air cooler 144 can be configured to dissipate heat from the pressurized airflow 133, thereby increasing its density. The resulting cooled and pressurized output airflow 146 is directed into the intake manifold 148 of the internal combustion engine 125, or alternatively, into a subsequent stage, cascaded compressor. The operation of system 100 can be controlled by an ECU 150 (engine control unit) connected to the rest of the system via a communication connection 152.

[0029] Now for reference Figure 2 and Figure 3 Additional details about rotor 102 will be discussed below with reference to exemplary embodiments. Specifically, a compressor impeller 113 of rotor 102 is illustrated with reference to an exemplary embodiment. As will be discussed, compressor impeller 113 may include one or more balancing features 170 that balance rotor 102 during rotation about axis 103. It will be appreciated that one or more balancing features 170 may be included on rotor 102 at locations other than compressor impeller 113 without departing from the scope of this disclosure. Furthermore, it will be appreciated that balancing features 170 may be included on another rotor (e.g., the rotor of a booster or electric booster (e-charger)) without departing from the scope of this disclosure.

[0030] In some embodiments, the compressor impeller 113 may be a single, integral component made of metal or other materials. In some embodiments, the compressor impeller 113 may be formed at least partially by a casting process.

[0031] As shown, the compressor impeller 113 may include a hub 162. The hub 162 may be cylindrical and may receive a shaft 115 of the rotor 102. The hub 162 may be secured to the shaft 115 (e.g., with a nut or other fastener) for rotation with it.

[0032] The compressor impeller 113 may also include a back plate 164. The back plate 164 may extend radially away from the hub 162 and may terminate radially at an outer rim edge 165. The outer rim edge 165 may be substantially circular, may extend continuously about axis 103, and may be substantially centered on axis 103. The back plate 164 may also include a front face 167 and a back face 169. Both the front face 167 and the back face 169 may extend radially between axis 103 and outer rim edge 165. The back face 169 may generally face the turbine impeller 111 of rotor 102. Figure 1 The front face 167 may face generally in the opposite direction (away from the turbine impeller 111). The front face 167 may be profiled and may extend substantially axially (i.e., along axis 103) close to the hub 162, substantially radially close to the outer rim edge 165, and may have a gradually concave profile between the hub 162 and the outer rim edge 165.

[0033] The compressor impeller 113 may also include a plurality of blades 166. The blades 166 may be relatively thin and may be attached to the front face 167 of the back plate 164. The blades 166 may protrude from the front face 167. The blades 166 may also be arranged about the axis of rotation 103 and may extend outward therefrom. The outer radial ends of the blades 166 may terminate at the outer rim edge 165. The blades 166 may be substantially uniformly spaced in the circumferential direction about the axis 103. The blades 166 may have a predetermined shape, profile, size, etc., for moving the input air 131 through the compressor housing 107, compressing the input air 131, and generating a pressurized airflow 133 as the rotor 102 rotates about the axis 103.

[0034] It will be appreciated that the blades 166 can have a variety of different configurations without departing from the scope of this disclosure. In the illustrated embodiment, for example, the compressor impeller 113 may have a splitter blade wheel configuration, wherein every other blade 166 is shorter than the adjacent full blade. Furthermore, the blades 166 may have a rearwardly curved impeller element configuration such that at least some of the blades 166 (e.g., so-called "full blades") are curved rearward relative to the direction of rotation, which is clockwise, as indicated by arrow 149.

[0035] The plurality of blades 166 may include a first blade 141 and an adjacent second blade 142. In some embodiments, the first blade 141 may be axially longer than the second blade 142 (i.e., may project outwardly further axially from the back plate 164). Furthermore, the first blade 141 may also include a pressure side 143 and a suction side 145. The impeller 113 may also include a pressure-side fillet 147, which may be concave, to define a smooth transition between the front surface 167 and the pressure side 143 of the first blade 141. Similarly, the impeller 113 may include a suction-side fillet 151, which may be concave, to define a smooth transition between the front surface 167 and the suction side 145 of the first blade 141. Likewise, the second blade 142 may also include a pressure side 153 and a suction side 155. A pressure-side fillet 157 may be present, which may be concave, to define a smooth transition between the front surface 167 and the pressure side 153 of the second blade 142. Similarly, a suction-side rounded corner 159 may exist, which may be concave, to define a smooth transition between the front side 167 and the suction side 155 of the second blade 142.

[0036] Furthermore, the compressor impeller 113 may include a plurality of inter-blade regions between adjacent blades of blades 166 defined on the front surface 167 of the compressor impeller 113. This may include an inter-blade region 168 defined between a first blade 141 and a second blade 142. The inter-blade region 168 may extend radially between the hub 162 and the outer rim edge 165 (i.e., may extend circumferentially relative to the axis of rotation 103). Furthermore, the inter-blade region 168 may also be contoured along the radiating direction of the impeller 113 (i.e., curved as the region 168 extends radially between the hub 162 and the outer rim edge 165). This contour in the radiating direction may correspond to the contour of the plurality of blades 166. Furthermore, the width of the inter-blade region 168 (measured circumferentially between the first and second blades 141, 142) may be tapered and may gradually increase in the radial direction from the hub 162 to the outer rim edge 165.

[0037] Furthermore, the compressor impeller 113 may include a balancing feature 170. Typically, the balancing feature 170 distributes the weight of the rotor 102 such that the center of gravity of the rotor 102 is substantially located on the axis 103. The balancing feature 170 can improve imbalances, for example, due to the superposition of manufacturing and assembly tolerances associated with the rotor 102. Therefore, the balancing feature 170 can provide substantially balanced rotation of the rotor 102 about the axis 103. While the balancing feature 170 is included on the compressor impeller 113 in the illustrated embodiment, it will be appreciated that the turbine impeller 111 may include the balancing feature 170 in some embodiments of this disclosure.

[0038] The balancing feature 170 may include one or more marking portions, including recesses, grooves, channels, or other holes. In some embodiments, the back plate 164 may include a first balancing marking portion 172 that provides balancing with respect to a first plane (e.g., a plane normal to axis 103). Figure 2 and Figure 3 In addition, such as Figure 2 As shown, the hub 162 may include a second balancing mark 171 that balances the rotor 102 relative to a plane parallel to the axis 103. Thus, the balancing marks 171 and 172 can cooperate to provide two-plane balance for the rotor 102.

[0039] like Figure 2 and Figure 3 As shown, the first balance mark portion 172 may include an elongated recess, groove, notch, or recess. The first balance mark portion 172 may be formed at least partially within the inter-blade region 168 of the front surface 167 of the impeller 113. The first balance mark portion 172 may be recessed within the front surface 167.

[0040] like Figure 2As shown, the balance mark portion 172 may extend along axis 161 across the inter-blade region 168 and may include a first end 174 and a second end 176. Axis 161 may be arcuate and substantially centered on axis 103 so as to be substantially concentric with the outer rim edge 165. Axis 161 may be radially spaced inward from the outer rim edge 165 at a distance.

[0041] like Figure 2 As shown, the balancing mark portion 172 may have a width 180 (i.e., width dimension), which can be measured transversely to axis 161. The width 180 can be measured radially relative to axis 103 between the inner edge 192 and the outer edge 194 of the mark portion 172. Figure 2 As shown, the width 180 can vary as the balance mark portion 172 extends arcuately between the first end 174 and the second end 176.

[0042] In some embodiments, the balance mark portion 172 may have an elongated bean shape. The inner edge 192 may be more contoured than the outer edge 194.

[0043] In addition, such as Figure 2 As shown, the first end 174 may be recessed into the pressure-side fillet 147. The second end 176 may terminate at or before reaching the suction-side fillet 159. In other words, the suction-side fillet 159 may not be interrupted by the second end 176.

[0044] The width 180 of the balancing mark portion 172 can be configured to reduce the imbalance of the rotor 102. Furthermore, the width 180 can vary according to the specific stress distribution of the impeller 113. For example, a larger stress margin can exist on the pressure side 143 compared to the suction side 155 of the adjacent blade 166. Thus, the width 180 can be larger closer to the first end 174 compared to the second end 176. In other words, more material can be available for removal at the pressure side 143; therefore, the balancing mark portion 172 can be wider at the first end 174 without negatively affecting the strength or robustness of the impeller 113.

[0045] In addition, such as Figure 3 As shown, the balance mark portion 172 may have a depth 190 (i.e., a depth dimension), which can be measured substantially in the axial direction along axis 103. The depth 190 can be measured in the axial direction and can be the distance recessed from the front surface 167 in the region adjacent to the balance mark portion 172. Figure 3 As shown, the depth 190 can vary as the balance mark portion 172 extends arcuately between the first end 174 and the second end 176.

[0046] The depth 190 of the balancing mark portion 172 can be configured to reduce the imbalance of the rotor 102. Furthermore, the depth 190 can vary according to the specific stress distribution of the impeller 113. As mentioned, a larger stress margin can exist on the pressure side 143 compared to the suction side 155. Thus, the depth 190 can be larger closer to the first end 174 than the second end 176. Furthermore, as... Figure 3 As shown, the depth 190 can vary to define the first segment 195 and the second segment 196. The second segment 196 can be shallower than the first segment 195.

[0047] In addition, such as Figure 3 As shown, the first end 174 can be a cup-shaped end (i.e., cup-shaped in shape). In other words, the first end 174 can have a hemispherical or ball-segment-shaped concave profile on its outer edge, except where the marking portion 172 extends from the first end 174 toward the second end 176. Similarly, the second end 176 can be a cup-shaped end (i.e., cup-shaped in shape). Thus, the second end 176 can have a hemispherical or ball-segment-shaped concave profile on its outer edge, except where the marking portion 172 extends from the second end 176 toward the first end 174. Both the first end 174 and the second end 176 can be cup-shaped in shape. The depth 190 of the marking portion 172 can vary between the cup-shaped first end 174 and the cup-shaped second end 176. Figure 3 As shown, a first step 182 may exist at the transition between the cup-shaped contoured surface of the front side 167 and the first end 174. Similarly, a second step 184 may exist at the transition between the contoured surface of the front side 167 and the second end 176. The balancing mark portion 172 may be stepped in the axial direction along the axis 103 at the steps 182 and 184, and the inner edge 192 and the outer edge 194 may be continuous with the edges defined at the first step 182 and the second step 184.

[0048] Therefore, the marking portion 172 can be formed with high precision and accuracy along its elongated length. The width 180 and depth 190 can vary according to the angular position within the inter-blade region 168. In some embodiments, the ends 174, 176 can be formed with a high degree of contour to precisely balance the rotor 102 while maintaining the high strength and robustness of the impeller 113. The balancing marking portion 172 can be customized for a specific impeller 113, a specific impeller configuration, a specific stress distribution of the impeller 113, etc.

[0049] Furthermore, the location of the marking portion 172 may be advantageous because it is highly accessible (e.g., during the machining process). Additionally, a relatively large area exists at this location for balancing the marking portion 172. Therefore, the balancing process can be performed with high precision and accuracy.

[0050] Now for reference Figure 4 The method 1500 for balancing the rotor 102 and forming the balancing mark portion 172 will be discussed according to exemplary embodiments of the present disclosure. In some embodiments, a balancing device 1600 may be used. Figure 5 To execute method 1500.

[0051] The embodiments of this disclosure are described herein in terms of functional and / or logical block components and various processing steps. It should be understood that such block components can be implemented by any number of hardware, software, and / or firmware components configured to perform specified functions. For example, embodiments of this disclosure may employ various integrated circuit components, such as memory elements, digital signal processing elements, logic elements, lookup tables, etc., which, under the control of one or more microprocessors or other control devices, can perform multiple functions. Furthermore, those skilled in the art will appreciate that embodiments of this disclosure can be implemented in conjunction with any number of systems, and the air quality control system described herein is merely one exemplary embodiment of this disclosure.

[0052] For the sake of brevity, conventional techniques related to signal processing, data transmission, signaling, control, and other functional aspects of the system (and its various operating components) may not be described in detail herein. Furthermore, the connecting lines shown in the various figures included herein are intended to illustrate exemplary functional relationships and / or physical couplings between various elements. It should be noted that many alternative or additional functional relationships or physical connections may exist in the embodiments of this disclosure.

[0053] like Figure 5 As shown, the balancing device 1600 can support the rotor 102 for rotation about the axis 103. During the balancing method 1500, the rotor 102 can be supported within the bearing housing 109. More specifically, as... Figure 5 As shown, rotor 102 may include compressor impeller 113, shaft 115, and turbine impeller 111. Rotor 102 may be supported on one or more bearings and may be disposed within bearing housing 109. The front face 167 of compressor impeller 113 may remain exposed outside bearing housing 109 during balancing method 1500.

[0054] The balancing device 1600 may also include a cutting tool 1602. The cutting tool 1602 may be one of a variety of tools used to remove material from a workpiece. For example, such as... Figure 5As shown, the cutting tool 1602 may include a cutter 1604, such as a ball-end or hemispherical end mill. The cutter 1604 may have any suitable radius and may be operatively connected to a milling machine. However, it will be appreciated that different cutting tools 1602 may be used to employ method 1500 without departing from the scope of this disclosure.

[0055] The balancing device 1600 may also include a control system 1606. The control system 1606 may be configured as a computing device having at least one processor 1608 and a memory device 1609. The control system 1606 may communicate with the actuator system 1616. The control system 1606 may include hardwired computing circuitry (or circuitry). The control system 1606 may also be configured as a hydraulic, electric, or electrohydraulic controller, or other. Thus, the control system 1606 may be configured to perform various calculation and control functions concerning the actuator system 1616.

[0056] Actuator system 1616 may include one or more electric motors, hydraulic actuators, pneumatic actuators, etc. In some embodiments, actuator system 1616 may selectively actuate rotor 102 relative to cutter 1604. For example, actuator system 1616 may selectively rotate rotor 102 about axis 103, as indicated by arrow 1622. In some embodiments, actuator system 1616 may selectively rotate rotor 102 in a clockwise or counterclockwise direction. Additionally, actuator system 1616 may selectively actuate cutter 1604 relative to rotor 102. For example, actuator system 1616 may selectively rotate cutter 1604 about cutter axis 1605. In some embodiments, cutter axis 1605 may be positioned at an acute angle 1607 relative to axis 103 of rotor 102. (Cutter axis 1605 may be located at...) Figure 5 (Within the plane.) Additionally, the actuator system 1616 can linearly (telescopically) actuate the cutter 1604 back and forth along the cutter axis 1605, as shown by arrow 1620. Furthermore, the actuator system 1616 can selectively move the cutter 1604 linearly along and substantially parallel to the axis 103 of the rotor 102, as shown by arrow 1624.

[0057] The control system 1606 may include various modules. As used herein, the term "module" means any hardware, software, firmware, electronic control components, processing logic, and / or processor device, individually or in any combination, including but not limited to: application-specific integrated circuits (ASICs), electronic circuits, processors (shared, dedicated, or grouped) and memories executing one or more software or firmware programs, combinational logic circuits, and / or other suitable components that provide the aforementioned functionality.

[0058] In some embodiments, the control system 1606 may include an actuator module 1612. The actuator module 1612 may be used to generate control signals or control commands and output them to the actuator system 1616 for selectively moving the cutter 1604 relative to the rotor 102 and / or selectively moving the rotor 102 relative to the cutter 1604. The control system 1606 may also include an imbalance detection module 1610. The imbalance detection module 1610 may be used to detect that the rotor 102 is unbalanced with respect to rotation about axis 103. The imbalance detection module 1610 may also detect the amount or degree of imbalance of the rotor 102. In some embodiments, the imbalance detection module 1610 is operatively connected to a sensor, such as a vibration sensor, which detects imbalance in the rotation of the rotor 102 during rotation. Furthermore, the control system 1606 may include a balance model module 1614. The balance model module 1614 may be used to generate an electronic (computerized) module of the rotor 102 with a balance mark portion 172 adapted to balance the rotor 102. Module 1614 can determine the width 180, depth 190, position, and / or other characteristics of the balancing mark 172. Module 1614 can determine these characteristics for adequately balancing the rotation of the rotor 102, while also taking into account the stress distribution of the impeller 113. Once module 1614 generates the model, it can be stored in memory device 1609.

[0059] like Figure 4 As shown, method 1500 can begin at 1502, where an imbalance test of rotor 102 is performed. For example, actuator module 1612 can generate control commands for rotating rotor 102 about axis 103. Rotor 102 can rotate continuously for a predetermined amount of time and at a predetermined angular velocity. Simultaneously, one or more vibration sensors can detect the amount of vibration in rotor 102. Imbalance detection module 1610 can receive vibration data from the sensors, process the signals, and calculate and determine the imbalance in rotor 102.

[0060] Next, at 1504 of method 1500, the control system 1606 may determine whether the rotor 102 is sufficiently balanced. For example, the imbalance detected at 1502 may be compared with a predetermined threshold amount of imbalance. This predetermined threshold may be stored in a memory device 1609 and may be accessed by the control system 1606 when making the determination at 1504. If the amount of imbalance detected at 1502 is lower than the predetermined threshold (i.e., the rotor is sufficiently balanced), the method may proceed as follows: Figure 4 The process terminates as shown. Conversely, if at 1504 the control system 1606 determines that the detected imbalance is above a threshold, then method 1500 may continue at 1506.

[0061] At 1506, the balancing model module 1614 can be used to generate a computer model of the rotor 102 having one or more balancing marks 172 suitable for balancing the rotation of the rotor 102. The balancing model module 1614 can rely on computerized logic and modeling software to determine the size, dimensions, etc., of the balancing marks 172, and the placement of such marks 172 on the compressor impeller 113. In some embodiments, the marks 172 generated in the model can be sized, shaped, and placed on the compressor impeller 113, as described above regarding... Figure 2 and Figure 3 The discussion.

[0062] A model can also be generated to indicate how the actuator system 1616 should be used to form the mark portion 172. In other words, the model can be used to generate control signals for the actuator system 1616 to move the cutter 1604 and / or impeller 113 to form the mark portion 172. Once the balancing model module 1614 generates a model of the balanced rotor 102, the model can be stored in the memory device 1609. It will be appreciated that the model can also determine the process steps used to create the balanced mark portion 172.

[0063] Next, at 1508 of method 1500, the rotor 102 can be machined according to the model generated at 1506 to create the balance mark section 172. Specifically, the actuator module 1612 can access the model (generated at 1506 and stored in the memory device 1609) and actuate the rotor 102 and / or the cutter 1604 according to the model.

[0064] Actuator module 1612 can generate control signals according to the model to rotate cutter 1604 about cutter axis 1605 at a predetermined angular velocity. According to the model generated at 1506, actuator module 1612 can also generate control commands and send them to cutter 1604 to move cutter 1604 along cutter axis 1605 (at least partially along axis 103) and position cutter 1604 at a radial distance 1660 away from axis 103. According to the model, actuator module 1612 can also generate control commands to move cutter 1604 parallel to axis 103 toward the impeller and to a predetermined depth 190 into the back plate 164 of compressor impeller 113. This movement allows cutter 1604 to contact and remove material from compressor impeller 113, such as... Figure 6 As presented in the document.

[0065] In addition, control commands can be generated to move the cutter 1604 axially (parallel to axis 103, along the axis, etc.) and away from the back plate 164, for example at the first end 174 or the second end 176. In doing so, the cutter 1604 can form a cup-shaped first end 174 and / or a cup-shaped second end 176 before being withdrawn from the impeller 113.

[0066] In addition, such as Figure 7 and Figure 8 As shown, actuator module 1612 can generate control commands based on this model to rotate rotor 102 about axis 103 by a predetermined angular displacement. Figure 7 In some embodiments shown, the compressor impeller 113 is rotatable clockwise about axis 103. Figure 8 In the additional embodiment shown, the compressor impeller 113 can rotate counterclockwise about axis 103. Furthermore, in some embodiments, the cutter 1604 can be held in a fixed angular position relative to axis 103 during the processing. Additionally, according to the model generated at 1506, the cutter 1604 and / or impeller 113 can move axially simultaneously while the compressor impeller 113 rotates. This provides the width 180 and depth 190 varied as discussed above.

[0067] In some embodiments, the entire marking portion 172 can be generated in a single pass, wherein the cutter 1604 and the impeller 113 move relative to each other in both the axial and angular (circumferential) directions. Therefore, the marking portion 172 can be formed in an efficient manner. However, in other embodiments, the marking portion 172 can be generated by multiple passes of the cutter 1604, and with each pass, the cutter 1604 can gradually move deeper and deeper into the back plate 164 until the marking portion 172 is fully formed.

[0068] Once the mark 172 is formed at 1508, method 1500 can cycle back to 1502, where the imbalance of impeller 113 can be rechecked. Then, at 1504, if it is determined that impeller 113 is sufficiently balanced, method 1500 can terminate. However, if impeller 113 exhibits significant imbalance, method 1500 can continue to 1506, where an updated model can be generated, and subsequently, the mark 172 can be reshaped and / or new marks 172 can be added to impeller 113. Method 1500 can continue until impeller 113 is sufficiently balanced.

[0069] Therefore, the rotor of a fluid machine can be accurately and precisely balanced in an efficient and repeatable manner according to this teaching. The balancing mark can be formed and shaped to be tailored to the impeller 113 without compromising the impeller's strength and robustness.

[0070] Figure 9The accompanying diagram illustrates an additional embodiment. (and...) Figure 1-3 The features corresponding to those features are indicated by corresponding reference numerals increased by 100. The marking portion 272 may extend along its arcuate axis 261 within the inter-blade region 268 between the first end 274 and the second end 276. The marking portion 272 may be substantially centered on the axis 261. Furthermore, in some embodiments, the width 280 may vary as the marking portion 272 extends along the axis 261 between the first end 274 and the second end 276. Furthermore, similar to... Figure 3 In some embodiments, the depth of the marking portion 272 can vary as the marking portion 272 extends along the axis 261 between the first end 274 and the second end 276. Furthermore, in some embodiments, both the first end 274 and the second end 276 can be cup-shaped, similar to the above-mentioned… Figure 3 Examples of the discussion.

[0071] The arcuate axis 261 may be arcuate, causing the marking portion 272 to be bow-shaped and curved along the inter-blade region 268. For reference purposes, the arcuate axis 261 may be curved and arcuate relative to the second axis 299. In some embodiments, the arcuate axis 261 of the marking portion 272 may be circular and centered on the second axis 299. Furthermore, the second axis 99 may also be misaligned with the axis of rotation 203. The axis 299 may be parallel to the axis of rotation 203; however, the axis 299 may be radially spaced from it. However, it will be appreciated that in other embodiments of this disclosure, the marking portion 272 may be arcuate relative to the axis 299 along a non-circular path.

[0072] Furthermore, the arcuate axis 261 may be bow-shaped, arc-shaped, or curved relative to the outer rim edge 265. For example, the arcuate axis 261 may be bow-shaped from an adjacent portion of the outer rim edge 265 inward and slightly towards the rotation axis 203. Additionally, as shown in the illustrated embodiment, the first end 274 may be positioned further radially outward from the rotation axis 203 than the second end 276. The balancing mark portion 272 may be arranged along areas of the impeller that typically experience less stress, including areas where more material can be removed, etc.

[0073] Figure 10 The diagram illustrates another embodiment. (and...) Figure 1-3 The features corresponding to those features are indicated by corresponding reference numerals increased by 200. The marking portion 372 may extend along its arcuate axis 361 within the inter-blade region 368 between the first end 374 and the second end 376. Furthermore, in some embodiments, the width 380 may vary as the marking portion 372 extends along the axis 361 between the first end 374 and the second end 376. Furthermore, similar to... Figure 3In some embodiments, the depth of the marking portion 372 can vary as the marking portion 372 extends along the axis 361 between the first end 374 and the second end 376. Furthermore, in some embodiments, both the first end 374 and the second end 376 can be cup-shaped, similar to the above-mentioned… Figure 3 Examples of the discussion.

[0074] The arcuate axis 361 may be arcuate relative to the second axis 399. In some embodiments, axis 361 may be centered on the second axis 399. Furthermore, the second axis 99 may also be misaligned with the axis of rotation 303. Axis 399 may be parallel to the axis of rotation 303; however, axis 399 may be radially separated from it.

[0075] Furthermore, the arcuate axis 361 may be arcuate outward toward the adjacent portion of the outer rim edge 365 of the impeller, wherein the first end 374 is positioned further radially outward from the rotation axis 303 than the second end 376. Additionally, the arcuate axis 361 is arcuate in a direction roughly parallel to the contour of the blades and the inter-blade region 368. The balancing mark portion 372 may be arranged along areas of the impeller that typically experience less stress, including areas where more material can be removed, etc.

[0076] Figure 11 The accompanying diagram illustrates an additional embodiment. (and...) Figure 1-3 The features corresponding to those features are indicated by corresponding reference numerals increased by 300. The marking portion 472 may extend along its arcuate axis 461 within the inter-blade region 468 between the first end 474 and the second end 476. Furthermore, in some embodiments, the width 480 may vary as the marking portion 472 extends along the axis 461 between the first end 474 and the second end 476. Furthermore, similar to... Figure 3 In some embodiments, the depth of the marking portion 472 can vary as the marking portion 472 extends along axis 461 between the first end 474 and the second end 476. Furthermore, in some embodiments, both the first end 474 and the second end 476 can be cup-shaped, similar to the above-mentioned… Figure 3 Examples of the discussion.

[0077] The arcuate axis 461 may be arcuate relative to the second axis 499. In some embodiments, axis 461 may be centered on the second axis 499. Furthermore, the second axis 99 may also be misaligned with the rotation axis 403. Axis 499 may be parallel to the rotation axis 403; however, axis 499 may be radially separated from it.

[0078] Furthermore, the arcuate axis 461 may be arc-shaped outward toward the adjacent portion of the outer rim edge 465 of the impeller. Moreover, the arcuate axis 461 may also be arc-shaped opposite to the rotation direction of the impeller, as shown. Additionally, as shown in the illustrated embodiment, the first end 474 may be positioned further radially inward from the rotation axis 403 than the second end 476. The balancing mark portion 472 may be arranged along areas of the impeller that typically experience less stress, including areas where more material can be removed, etc. Therefore, in some embodiments, the first end 474 may define the deepest portion of the mark portion 472, and the mark portion 472 may gradually become shallower until it terminates at the formed second end 476.

[0079] While at least one exemplary embodiment has been presented in the foregoing detailed description, it should be appreciated that numerous variations exist. It should also be appreciated that the one or more exemplary embodiments described are merely examples and are not intended to limit the scope, applicability, or construction of this disclosure in any way. Rather, the foregoing detailed description will provide those skilled in the art with a convenient roadmap for implementing exemplary embodiments of this disclosure. It is to be understood that various changes may be made to the function and arrangement of the elements described in the exemplary embodiments without departing from the scope of this disclosure as set forth in the appended claims.

Claims

1. A rotor for a fluid machine, comprising: The impeller is supported for rotation about an axis of rotation; The impeller includes multiple blades; The inter-blade region between the first and second blades of the plurality of blades is defined circumferentially relative to the axis of rotation; as well as A balance mark portion located on the impeller and in the area between the blades, the balance mark portion being elongated and having a first end and a second end, the first end and the second end axially stepping into the area between the blades, the balance mark portion extending arcuately between the first end and the second end, the balance mark portion having a depth varying as the balance mark portion extends arcuately between the first end and the second end, and the balance mark portion having a width varying as the balance mark portion extends arcuately between the first end and the second end; The balance mark extends along an arcuate axis between the first end and the second end; The impeller defines a direction of rotation about the axis of rotation, the arcuate axis is bow-shaped between the first end and the second end, and the arcuate axis is bow-shaped opposite to the direction of rotation.

2. The rotor according to claim 1, wherein, The first blade includes a pressure side, and the second blade includes a suction side, the pressure side extending across the inter-blade region towards the suction side; Wherein, the first end is disposed near the pressure side of the first blade, and wherein the second end is disposed near the suction side of the second blade; and The first end is deeper than the second end.

3. The rotor according to claim 2, wherein, The depth is greatest at the first end.

4. The rotor according to claim 2, wherein, The impeller includes a first rounded corner at the transition between the inter-blade region and the first blade, wherein the impeller includes a second rounded corner at another transition between the inter-blade region and the second blade; and Wherein, the first end is recessed into the first rounded corner; and Wherein, the second rounded corner is not interrupted by the second end.

5. The rotor according to claim 2, wherein, The impeller includes a first rounded corner at the transition between the inter-blade region and the first blade, wherein the impeller includes a second rounded corner at another transition between the inter-blade region and the second blade; Wherein, the first fillet is not interrupted by the first end; and Wherein, the second rounded corner is not interrupted by the second end.

6. The rotor according to claim 1, wherein, The arc-shaped axis is substantially centered on the axis of rotation.

7. The rotor according to claim 1, wherein, The balance mark extends in an arc shape; and The balance mark is offset from the center relative to the rotation axis.

8. The rotor according to claim 7, wherein, The impeller defines a direction of rotation about the axis of rotation, wherein the arcuate axis is bow-shaped between the first end and the second end, and wherein the arcuate axis is bow-shaped along the direction of rotation.

9. The rotor according to claim 7, wherein, The impeller includes an outer rim edge, the outer rim edge having a portion adjacent to the balance mark portion; The arcuate axis is bow-shaped between the first end and the second end, and the portion of the arcuate axis toward the outer rim edge is bow-shaped.

10. The rotor according to claim 7, wherein, The impeller includes an outer rim edge, the outer rim edge having a portion adjacent to the balance mark portion; The arcuate axis is bow-shaped between the first end and the second end, and the portion of the arcuate axis away from the outer rim edge is bow-shaped.

11. A method for balancing the rotor of a fluid machine, comprising: A support impeller is provided for rotation about an axis of rotation. The impeller includes a plurality of blades and an inter-blade region circumferentially defined relative to the axis of rotation between a first blade and a second blade of the plurality of blades. as well as A balancing mark portion is formed on the impeller and in the region between the blades. The balancing mark portion is elongated and has a first end and a second end. The first end and the second end enter the region between the blades in an axially stepped manner. The balancing mark portion extends arcuately between the first end and the second end. The balancing mark portion has a depth that varies as it extends arcuately between the first end and the second end. The balancing mark portion has a width that varies as it extends arcuately between the first end and the second end. The balance mark extends along an arcuate axis between the first end and the second end; The impeller defines a direction of rotation about the axis of rotation, the arcuate axis is bow-shaped between the first end and the second end, and the arcuate axis is bow-shaped opposite to the direction of rotation.

12. The method of claim 11, further comprising determining a balancing model for an impeller, the impeller being supported for rotation about an axis of rotation; in, Forming the balance mark section includes removing material from the impeller in the inter-blade region using a removal tool, based on a determined balance model.

13. The method according to claim 12, wherein, The first blade includes a pressure side, and the second blade includes a suction side, the pressure side extending across the inter-blade region towards the suction side; Wherein, the first end is disposed near the pressure side of the first blade, and wherein the second end is disposed near the suction side of the second blade; and The formation of the balance mark portion includes forming the first end to be deeper than the second end.

14. The method according to claim 13, wherein, Forming the balance mark portion includes forming the first end to have the maximum depth at the first end.

15. The method according to claim 14, wherein, The impeller includes a first rounded corner at the transition between the inter-blade region and the first blade, wherein the impeller includes a second rounded corner at another transition between the inter-blade region and the second blade; and The formation of the balance mark portion includes recessing the first end into the first rounded corner and ensuring that the second rounded corner is not interrupted by the second end.

16. The method of claim 14, wherein, The impeller includes a first rounded corner at the transition between the inter-blade region and the first blade, wherein the impeller includes a second rounded corner at another transition between the inter-blade region and the second blade; and The formation of the balance mark portion includes ensuring that the first rounded corner is not interrupted by the first end and that the second rounded corner is not interrupted by the second end.

17. The method of claim 11, further comprising providing a cutting tool configured to remove material from the impeller; and in, Forming the balance mark includes moving at least one of the cutting tool and the impeller relative to the other in an axial direction and along an arcuate axis between the first end and the second end, wherein the arcuate axis is substantially centered on the axis of rotation.

18. The method of claim 11, further comprising providing a cutting tool configured to remove material from the impeller; and in, Forming the balance mark portion includes moving at least one of the cutting tool and the impeller relative to the other in an axial direction and along an arcuate axis between the first end and the second end, such that the balance mark portion extends arcuately and that the balance mark portion is off-center relative to the axis of rotation.

19. A fluid booster device, comprising: case; A rotor supported for rotation within the housing, the rotor being used to rotate about an axis of rotation; The rotor has an impeller comprising a plurality of blades and defining a direction of rotation about the axis of rotation; The inter-blade region between the first and second blades of the plurality of blades is defined circumferentially relative to the axis of rotation; as well as A balance mark portion located on the impeller and in the area between the blades, the balance mark portion being elongated and having a first end and a second end, the first end and the second end being axially stepped into the area between the blades, the balance mark portion extending arcuately between the first end and the second end, the balance mark portion having a depth varying as the balance mark portion extends arcuately between the first end and the second end, the balance mark portion having a width varying as the balance mark portion extends arcuately between the first end and the second end, the first end and the second end being cup-shaped ends; as well as Relative to the direction of rotation, the first blade includes a pressure side and the second blade includes a suction side, the pressure side extending across the inter-blade region towards the suction side, the first end being disposed near the pressure side of the first blade and the second end being disposed near the suction side of the second blade, the first end being deeper and wider than the second end; The balance mark extends along an arcuate axis between the first end and the second end; The impeller defines a direction of rotation about the axis of rotation, the arcuate axis is bow-shaped between the first end and the second end, and the arcuate axis is bow-shaped opposite to the direction of rotation.

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