US20080056912A1 - Pump system and method using planetary gear assembly - Google Patents
Pump system and method using planetary gear assembly Download PDFInfo
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- US20080056912A1 US20080056912A1 US11/513,522 US51352206A US2008056912A1 US 20080056912 A1 US20080056912 A1 US 20080056912A1 US 51352206 A US51352206 A US 51352206A US 2008056912 A1 US2008056912 A1 US 2008056912A1
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- Prior art keywords
- clutch
- pump
- pump system
- motor
- gear
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/021—Units comprising pumps and their driving means containing a coupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/021—Units comprising pumps and their driving means containing a coupling
- F04D13/022—Units comprising pumps and their driving means containing a coupling a coupling allowing slip, e.g. torque converter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/028—Units comprising pumps and their driving means the driving means being a planetary gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/12—Combinations of two or more pumps
- F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
- F04D15/029—Stopping of pumps, or operating valves, on occurrence of unwanted conditions for pumps operating in parallel
Definitions
- Pumps may be used in a wide variety of applications to transfer a liquid, such as water, from one location to another.
- a liquid such as water
- one or more pumps may transfer a large quantity of water from a lake, cooling pond, river, or ocean to a remote facility or site.
- the one or more pumps may transfer the liquid, e.g., water, horizontally for miles to reach the remote facility or site.
- the start up and shut down stages may adversely affect the pump and associated components due to transient hydraulic instabilities.
- the hydraulic instabilities associated with the start up and shut down stages generally increase with greater vertical and horizontal distances between the pump and the remote site.
- the transient hydraulic instabilities generally reduce the life of the pump and associated components. For example, an abrupt change in the flow or pressure within the pumping system can result in water hammer, which may cause piping failures, broken pump shafts, motor damage, structural damage, broken pipe hangers, mechanical seal failures, and so forth.
- the pumps and motors in certain pumping systems may be very large and expensive due to various operational parameters.
- the desired speed of the pump may be significantly below the nominal speed of a typical two or four pole motor.
- the motor cost, size and weight generally increase dramatically with corresponding increases in the horse power ratings, e.g., greater than one thousand horse power.
- the increased size and weight of the motor generally results in a larger pump and support structure.
- a pump system includes a motor-to-pump transmission having a planetary gear assembly and a clutch or brake mechanism.
- a pump system includes a transmission having a housing with a motor mount and a pump mount, a central or sun gear disposed in the housing, a plurality of planet gears disposed in the housing, wherein the plurality of planet gears is disposed about and engaged with the central gear.
- the transmission also includes an outer ring gear disposed in the housing, wherein the outer ring gear is disposed about and engaged with the plurality of planet gears.
- FIG. 1 is a block diagram illustrating an embodiment of a liquid transfer or pumping system having a planetary gear system coupled to a motor and a pump;
- FIG. 2 is a block diagram of an embodiment of a modular pumping system having a planetary gear system
- FIG. 3 is a block diagram of an embodiment of a modular drive system
- FIG. 4 is a block diagram of an embodiment of a modular pump system
- FIG. 5 is a perspective view of an embodiment of a vertical pump drive having a motor coupled to an integral planetary gear and clutch module;
- FIG. 6 is an exploded perspective view of an embodiment of the vertical pump drive as illustrated in FIG. 5 ;
- FIG. 7 is an exploded perspective view of an embodiment of the integral planetary gear and clutch module as illustrated in FIGS. 5 and 6 ;
- FIG. 8 is a cross-sectional view of an embodiment of the integral planetary gear and clutch module as illustrated in FIGS. 5-7 ;
- FIG. 9 is a cross-sectional view of an embodiment of a planetary or epicyclic gear assembly disposed within the integral planetary gear and clutch module as illustrated in FIGS. 5-8 ;
- FIG. 10 is a flow chart of an embodiment of a start up process for the vertical pump drive as illustrated in FIGS. 5-9 .
- FIG. 1 is a block diagram of an embodiment of a liquid transfer or pumping system 10 having one or more planetary gear systems disposed between respective motors and pumps.
- the planetary gear system is used simply for convenience, and is intended to cover either a planetary gear system (e.g., 146 ) or a planetary gear system with a clutch or a brake mechanism (e.g., 150 ).
- various transmissions and/or clutch systems including 146 and 148 may be exchanged with one another based on the specific parameters of the pumping application.
- FIGS. 1 is a block diagram of an embodiment of a liquid transfer or pumping system 10 having one or more planetary gear systems disposed between respective motors and pumps.
- the planetary gear system is used simply for convenience, and is intended to cover either a planetary gear system (e.g., 146 ) or a planetary gear system with a clutch or a brake mechanism (e.g., 150 ).
- various transmissions and/or clutch systems including 146 and 148 may be exchanged
- each of the planetary gear systems generally includes a planetary gear assembly, which also may include a clutch or brake assembly to vary (e.g., increase or decrease) the output from the motor to the respective pump.
- a control start transmission module 148 may be used with or without a planetary gear assembly.
- the liquid transfer or pumping system 10 may include a first or vertical pump arrangement 12 , a second or horizontal pump arrangement 14 , and a third or horizontal pump arrangement 16 .
- the first or vertical pump arrangement 12 includes a motor 18 , a planetary gear system 20 coupled to the motor 18 , a pump 22 coupled to the planetary gear system 20 , and a control unit 24 communicatively coupled to one or more of the vertically arranged components 18 , 20 , and 22 .
- the control unit 24 may include a pump speed and/or thrust controller to vary the pumping speed and, thus, thrust based on various conditions in the liquid transfer or pumping system 10 .
- embodiments of the planetary gear system 10 enable use of significantly smaller sized motors and support structures, thereby reducing costs and complexities of the pumping system 10 .
- the planetary gear system 20 enables a substantial reduction in the dimensions, weight, and general size of the motor 18 to drive the pump 22 .
- the smaller size of the motor 18 enables a reduction in the dimensions, weight, and general size of a support structure 26 , which may be configured to support the motor 18 , the planetary gear system 20 , and the pump 22 .
- embodiments of the planetary gear system 20 enable a generally smooth and gradual transition during start up, shut down, or other stages or periods involving hydraulic instabilities.
- the planetary gear system 20 may gradually change (e.g., increase or decrease) the speed of the pump 22 during transient stages (e.g., startup or shutdown), thereby reducing the possibility of water hammer and other undesirable abrupt changes in the pumping system 10 .
- a clutch mechanism e.g., a wet clutch
- the planetary gear system 20 may be controlled to vary a degree of slip between clutch plates, thereby varying the output speed to the pump 22 . In this manner, the planetary gear system 20 can gradually change the pump speed based on various input/sensed parameters.
- the pump 22 is submerged in water below a water line 28 , while the motor 18 , the planetary gear system 20 , and the control unit 24 are disposed above the water line 28 .
- the illustrated planetary gear system 20 is coupled to the pump 22 by a shaft 30 .
- the motor 18 , the planetary gear system 20 , and the pump 22 may be coupled directly together and mounted above the water line 28 , while an intake conduit extends to a point below the water line 28 .
- the pump 22 includes one or more fluid inlets 32 and one or more fluid outlets 34 submerged below the water line 28 along with the rest of the pump 22 .
- the illustrated pump 22 includes one or more fluid passages 36 having one or more pump impellers 38 disposed between the fluid inlet 32 and the fluid outlet 34 .
- the pump 22 also can include one or more check valves, manual valves, or electromechanical valves.
- the check valves generally reduce or prevent flow of fluid from the fluid outlet 34 back through the fluid passages 36 to the fluid inlet 32 .
- the electromechanical valves also can be controlled via the control unit 24 .
- an electromechanical valve 40 is coupled to the pump 22 at or near the fluid outlet 34 .
- a water or fluid conduit 42 is coupled to the electromechanical valve 40 and extends both vertically and horizontally to a remote site 44 .
- the illustrated fluid conduit 42 includes a relatively short horizontal conduit portion 46 , a vertical conduit portion 48 , and a relatively long horizontal conduit portion 50 .
- the vertical conduit portion 48 may have a relatively short length, height, or head between the horizontal conduit portions 46 and 50 , while the long horizontal conduit portion 50 may extend for miles to the remote site 44 .
- another electromechanical valve 52 may be coupled to the fluid conduit 42 .
- the remote site 44 also can include one or more fluid delivery or distribution systems, such as systems 54 , 56 , and 58 .
- These systems 54 , 56 , and 58 each can include a motor, a planetary gear system (with or without a clutch or brake mechanism), and a pump to transport the water or fluid to another downstream location as indicated by arrows 60 , 62 , and 64 .
- the control unit 24 is communicatively coupled to a plurality of sensors disposed in the first or vertical pump arrangement 12 and along the water or fluid conduit 42 to the remote site 44 .
- the illustrated control unit 44 is communicatively coupled to sensors 66 , 68 , 70 , and 72 disposed on, within, or in proximity to the motor 18 .
- the illustrated control unit 24 is communicatively coupled to sensors 74 , 76 , 78 , and 80 disposed on, within, or in general proximity to the planetary gear system 20 .
- the control unit 24 also may be coupled to one or more sensors 82 disposed on or adjacent the shaft 30 extending between the planetary gear system 20 and the pump 22 .
- the illustrated control unit 24 is communicatively coupled to sensors 84 , 86 , 88 , 90 , 92 , 94 , and 96 disposed on, within, or in proximity to various portions of the pump 22 .
- the sensors 90 , 92 , 94 , and 96 may be disposed outside or at least partially or entirely within the one or more fluid passages 36 of the pump 22 .
- the illustrated control unit 24 can be coupled to one or more sensors 98 and 100 disposed outside or at least partially inside or within the fluid conduit 42 , such as at a top portion of the vertical conduit portion 48 .
- the sensors 66 - 100 may include temperature sensors, pressure sensors, voltage sensors, current sensors, torque sensors, mechanical speed sensors (e.g., linear or rotational speed), fluid speed sensors, fluid mass or volumetric flow rate sensors, and so forth. These sensors 66 - 100 generally provide feedback to the control unit 24 , which can then respond in a closed loop to adjust characteristics of the motor 18 , the planetary gear system 20 , and/or the pump 22 . For example, as discussed in detail below, the feedback from the sensors 66 - 100 may trigger the control unit 24 to increase or decrease the speed of the motor 18 .
- the feedback from the sensors 66 - 100 also may trigger the control unit 24 to increase or decrease the engagement of a clutch (e.g., a wet clutch) disposed within the planetary gear system 20 , thereby selectively increasing or decreasing an output rate of rotation 102 of the shaft 30 .
- a clutch e.g., a wet clutch
- the feedback controlled rate of rotation 102 alters the general speed or flow rate of the pump 22 .
- this feedback control of the motor 18 , the planetary gear system 20 , and the pump 22 enables a more gradual start up or shut down of the vertical pump arrangement 12 , thereby substantially reducing the possibility of abrupt hydraulic changes or damage in the liquid transfer or pumping system 10 .
- the feedback control may continue until the liquid transfer or pumping system 10 reaches a hydraulically stable condition between the pump 22 and the remote site 44 , for example.
- the feedback control also may continue after reaching a hydraulically stable condition, thereby providing a response mechanism for any changes in the system 10 .
- the second and third horizontal pump arrangement 14 and 16 as illustrated in FIG. 1 include motors 104 and 106 , planetary gear systems 108 and 110 coupled to the respective motors 104 and 106 , and pumps 112 and 114 coupled to the respective planetary gear systems 108 and 110 .
- the illustrated horizontal pump arrangements 14 and 16 include control units 116 and 118 communicatively coupled to the components.
- the control unit 116 is communicatively coupled to a plurality of sensors 120 disposed on, within, or in general proximity to the motor 104 , the planetary gear system 108 , and the pump 112 .
- the illustrated control unit 118 is communicatively coupled to a plurality of sensors 122 disposed on, within, or in general proximity to the motor 106 , the planetary gear system 110 , and the pump 114 .
- sensors 120 and 122 can include a variety of sensors, such as those described above with reference to sensors 66 - 100 .
- the second and third horizontal pump arrangement 14 and 16 include the pumps 112 and 114 coupled to the respective planetary gear systems 108 and 110 .
- the arrangements 14 and 16 may include other loads or machinery, such as conveyer belts, coupled to the planetary gear systems 108 and 110 and the corresponding motors 104 and 106 .
- the illustrated liquid transfer or pump system 10 can include a central control system 124 communicatively coupled to one or more of the pump arrangements 12 , 14 , and 16 and the remote site 44 .
- the central control system 124 also may be communicatively coupled to one or more sensors disposed throughout the overall liquid transfer or pumping system 10 .
- the illustrated central control system 124 is communicatively coupled to the electromechanical valve 52 and additional sensors 126 and 128 disposed along the water or fluid conduit 42 at or near the remote site 44 .
- the central control system 124 can transmit, receive, and generally exchange sensed feedback, data, and commands with the control units 24 , 116 , and 118 associated with the first or vertical pump arrangement 12 , the second or horizontal pump arrangement 14 , and the third or horizontal pump arrangement 16 as well as the remote site 44 .
- various feedback may be employed by the central control system 124 and the various control units 24 , 116 , and 118 to alter the operational characteristics of the motors 18 , 104 , and 106 , the corresponding planetary gear systems 20 , 108 , and 110 , and the corresponding pumps 22 , 112 , and 114 .
- FIG. 2 is a block diagram of an exemplary embodiment of a modular pumping system 130 having the planetary gear system 20 .
- the planetary gear system 20 enables a substantial motor size reduction from a standard large direct drive motor 132 to a relatively small high speed motor 18 as illustrated by arrows 134 .
- the standard large direct drive motor 132 may have a speed output in the range of 400-600 RPM and a torque output of about 1 ⁇ 10 6 inch-pounds.
- the relatively small high speed motor 18 may have a speed output in the range of 1800-3600 RPM and a torque output of about 175 ⁇ 10 3 inch-pounds.
- the smaller motor tends to be more efficient and also has a higher power factor.
- the planetary gear system 20 also enables a substantial support size reduction from a standard large direct driven support structure 136 to a relatively small support structure 26 as indicated by arrows 138 .
- the motor 132 and the support structure 136 have significantly greater dimensions, weight, and overall size in a direct drive configuration without the intermediate planetary gear system 20 .
- the planetary gear system 20 substantially reduces the costs, support structures, and general complexities of the larger direct drive configuration of the motor 132 and the support structure 136 .
- the planetary gear system 20 also simplifies the installation, access, handling, and general maintenance of the modular pumping system 130 .
- the reduced size as illustrated by the small high speed motor 18 and the small support structure 26 can allow additional mounting arrangements of the modular pumping system 130 .
- the modular pumping system 130 may be mounted entirely above the water line or other body of liquid.
- the modular pumping system 130 also enables a variety of different small high speed motors 18 , planetary gear systems 20 , and pumps 22 to be selectively coupled together to meet the demands of a particular pumping application.
- a particular application may have a shorter or longer horizontal run of fluid conduit, a larger or smaller head or vertical run of fluid conduit, a smaller or greater desired fluid flow rate, and so forth.
- FIG. 3 is a block diagram of an exemplary embodiment of a modular drive system 140 having a family of interchangeable motors or motor modules 142 and different families of interchangeable transmission modules 144 .
- the family of interchangeable motors or motor modules 142 may include different sizes or motor parameters, such as speed, horse power, torque, variable speeds, and so forth.
- the different families of interchangeable transmission modules 144 may include a plurality of different motor-to-pump transmissions, which may include planetary gear assemblies, clutches, pump speed and/or thrust controllers, and combinations thereof.
- the different families of interchangeable transmission modules 144 may include a plurality or family of planetary gear modules 146 , a plurality or family of control start transmission modules 148 , and plurality or family of integral planetary gear and clutch modules 150 , a plurality or family of planetary gear modules 152 respectively coupled to a plurality or family of clutch modules 154 , and a plurality or family of clutch modules 156 respectively coupled to a plurality or family of planetary gear modules 158 .
- each planetary gear module 146 may include a central sun gear, a plurality of planet gears disposed about the central or sun gear, and an outer ring gear disposed about the plurality of planet gears.
- the control start transmission module 148 may include one or more gear reduction mechanisms, one or more clutch mechanisms, and one or more feedback control mechanisms to enable variable speed output from the motor 142 in response to various feedback data.
- the integral planetary gear and clutch module 150 may include a planetary gear assembly, such as a central or sun gear, a plurality of surrounding planet gears, and a surrounding ring gear.
- the integral planetary gear and clutch module 150 may include a variety of clutch mechanisms, such as a wet clutch, disposed near an input or an output drive shaft.
- the clutch mechanism may be disposed before, after, or simultaneous with the gear reduction mechanisms in a common housing.
- the planetary gear modules 152 and clutch modules 154 are generally configured to engage the motor 142 with a shaft between the clutch module 154 and the motor 142 .
- each set of clutch module 156 and corresponding planetary gear module 158 is configured to engage a selected motor 142 with a shaft between the planetary gear module 158 and the motor 142 .
- the modular drive system 140 as illustrated in FIG. 3 enables a variety of configurations between different motors 142 and different transmission modules 144 .
- the different motors 142 can have different operational characteristics
- each module 146 , 148 , 150 , 152 , 154 , 156 , and 158 in the different families of interchangeable transmission modules 144 can have different gear ratios, clutch features, and so forth.
- the gear ratios in each family can include a series of incrementally increasing gear ratios from a base ratio to a max ratio.
- each clutch in the different families can include a series or set of incrementally increasing ranges of clutch play and other operational ranges. Therefore, the different modules can be coupled together to suit a particular application or load, such as a pumping application, a conveyer belt application, and so forth.
- FIG. 4 is a block diagram of an exemplary embodiment of a modular pump system 160 including the different families of interchangeable transmission modules 144 as illustrated and described above with reference to FIG. 3 , further including a plurality or family of interchangeable pump or pump modules 162 .
- the different families of interchangeable transmission modules 144 may include a plurality or family or planetary gear modules 146 , a plurality or family of control start transmission modules 148 , a plurality or family of integral planetary gear and clutch modules 150 , a plurality or family of planetary gear modules 152 respectively coupled with clutch modules 154 , and a plurality or family of clutch modules 156 respectively coupled with planetary gear modules 158 .
- these different modules 144 may have a variety of different gear ratios, clutch ranges, and so forth.
- the family of interchangeable pumps or pump modules 162 may have a series of pumps having incrementally changing pump features, such as pump speed, flow rate, output thrust, and so forth.
- the modular pump system 160 enables a wide range of different configurations of the transmission modules 144 and the pumps or pump modules 162 to meet the demands of a particular pumping application, such as a vertical pumping application.
- FIG. 5 is a perspective view of an exemplary vertical pump drive 170 having an embodiment of the motor 18 coupled to an embodiment of the planetary gear system 20 as discussed above with reference to FIGS. 1 and 2 .
- the motor 18 includes a central motor structure 172 , opposite perforated venting portions 174 and 176 , an embodiment of the control unit 24 , an upper support structure 178 , and a lower support structure 180 .
- the lower support structure 180 may include a mount panel 181 , an opposite panel 182 , and intermediate ribs or support members 183 .
- the illustrated planetary gear system 20 may include or embody an integral planetary gear and clutch module, such as mentioned above with reference to module 150 as illustrated in FIGS. 3 and 4 .
- the integral planetary gear and clutch module 20 may be selectively mounted and dismounted with the motor 18 and one or more alternative motors to meet the demands of a particular load or application, such as a vertical and/or horizontal pumping application.
- FIG. 6 is an exploded perspective view of the vertical pump drive 170 as illustrated in FIG. 5 , further illustrating the integral planetary gear and clutch module 20 exploded from the motor 18 .
- the motor 18 includes a motor output shaft or drive shaft 184 extending outwardly from the mount panel 181 .
- the motor output shaft or drive shaft 184 may include a variety of coupling mechanisms to engage with the integral planetary gear and clutch module 20 .
- the illustrated drive shaft 184 includes a key slot 186 .
- the integral planetary gear and clutch module 20 includes a casing or enclosure 188 having support ribs 190 extending lengthwise between a first flange or motor mount 192 and a second flange or pump mount 194 .
- the integral planetary gear and clutch module 20 also includes an output shaft 196 extending outwardly from the central flange or pump mount 194 . Similar to the drive shaft 184 , the output shaft 196 may have a variety of different coupling mechanisms to connect with a pump, machine, or other load. However, the illustrated output shaft 196 includes a key slot 198 .
- FIG. 7 is an exploded perspective view of an exemplary embodiment of the integral planetary gear and clutch module 20 as illustrated in FIGS. 5 and 6 , further illustrating an embodiment of a gear system 200 and a clutch system 202 .
- the gear system 200 includes a planetary or epicyclic gear assembly 204 , an outer ring gear 206 , and a clutch-gear interface bearing 208 (e.g., a radial bearing).
- the illustrated planetary gear assembly 204 includes a gear carrier 210 having a first annular portion or support structure 212 , a second annular or support structure 214 , and a third annular or intermediate support structure 216 disposed between the structures 212 and 214 (see FIGS. 7 and 8 ).
- the planetary gear assembly 204 includes a plurality of planet gears 218 disposed in planet gear receptacles or engagement openings 220 within the intermediate support structure 216 of the gear carrier 210 .
- the planetary gear assembly 204 may include a set of 3, 4, 5, 6, or more planet gears 218 and corresponding engagement openings 220 .
- the planetary gear assembly 204 includes a planet shaft 222 for each respective planet gear 218 to rotate about within the engagement opening 220 .
- the planetary gear assembly 204 also includes the output shaft 196 extending through the support structure 214 into the interior of the intermediate support structure 216 to a central or sun gear 224 , which engages each of the planet gears 218 as illustrated and discussed below with reference to FIG. 8 .
- the planetary gear assembly 204 extends partially into and mates with the ring gear 206 .
- the ring gear 206 has a generally cylindrical interior 226 having first and second inner annular gear portions or inner teeth 228 and 230 , which are generally offset from one another by an annular separation portion 232 having a ring slot 234 .
- the ring gear 206 also may include a plurality of lubrication passages 236 extending from a generally cylindrical exterior 238 to the generally cylindrical interior 226 .
- the planetary gear assembly 204 is inserted into the ring gear 206 , such that each of the planet gears 218 engages the inner teeth 230 .
- bearing 208 may be disposed about the support structure 212 of the planetary gear assembly 204 , such that the gear carrier 210 may rotatingly engage a portion of the clutch system 202 .
- the illustrated bearing 208 includes inner and outer bearing sleeves 240 and 242 disposed concentrically about a plurality of roller members 244 .
- the illustrated clutch system 202 of FIG. 7 includes a first clutch support or annular engagement member 246 and a second clutch support or annular clutch pressure plate 248 .
- the engagement member 246 may be described as a clutch carrier, and the clutch pressure plate 248 may be described as a clutch pack backing ring.
- the engagement member 246 and pressure plate 248 are disposed about an annular piston or clutch control mechanism 250 and a set of alternating inner and outer geared clutch plates 252 .
- the set of clutch plates 252 may be described as a clutch pack.
- the engagement member 246 includes a disc portion 254 and an outer annular gear portion or outer teeth 256 .
- the illustrated engagement member 246 includes a piston interface or seal portion 258 disposed in the region between the disc portion 254 and the outer teeth 256 .
- the illustrated set of alternating clutch plates 252 includes a first set of clutch plates 260 and a second set of clutch plates 262 .
- the clutch plates 260 include inner teeth 264
- the clutch plates 262 include outer teeth 266 .
- these clutch plates 260 and 262 may be alternated one after the other, such that the inner and outer teeth 264 and 266 alternate in a corresponding manner.
- the clutch system 202 also may include an annular retainer or clutch securement ring 268 , which engages or generally interlocks with the ring slot 234 disposed within the ring gear 206 .
- the clutch securement ring 268 secures the pressure plate 248 adjacent the inner teeth 228 inside the ring gear 206 .
- the clutch plates 252 may be inserted into the ring gear 206 , such that the clutch plates 262 having the outer teeth 262 engage with the inner teeth 228 .
- the illustrated clutch control mechanism 250 may be assembled in movable engagement between the engagement member 246 and the clutch pressure plate 248 .
- the outer teeth 256 extend into the set of alternating clutch plates 252 within the ring gear 206 .
- the outer teeth 256 engage with the inner teeth 264 of the alternating clutch plates 260 .
- the bearing 208 generally extends into the outer teeth 256 , such that the outer bearing sleeve 242 fits within an inner cylindrical portion or bearing interface 270 of the engagement member 246 .
- the bearing 208 also extends around the support structure 212 and engages the intermediate support structure 216 of the planetary gear assembly 204 when assembled within the ring gear 206 .
- the integral planetary gear and clutch module 20 may include a drive gear or outer annular gear 272 secured about or generally coupled with the shaft 184 of the motor 18 .
- a drive gear coupling or inner annular gear 274 may be disposed about the gear 272 and a portion of the sun gear 224 , as illustrated and described below with reference to FIG. 8 .
- the gears 272 and 274 may be described as a spline hub and a spline coupling, respectively.
- the module 20 may include a plurality of annular support structures, seals, shock absorbent mechanisms, bearings, and so forth.
- annular structures or assemblies 276 , 278 , and 280 may be disposed between the planetary gear assembly 204 and an inner portion of the enclosure 188 .
- the assemblies 276 , 278 , and 280 include a radial bearing, a thrust plate, and a thrust bearing, respectively.
- the output shaft 196 of the planetary gear assembly 204 extends through a shaft opening 282 having a shaft flange 284 and an annular seal 286 disposed in the enclosure 188 .
- FIG. 8 is a cross-sectional view of the integral planetary gear and clutch module 20 as illustrated in FIG. 7 , further illustrating the gear system 200 and the clutch system 202 integrally assembled within the enclosure 188 .
- the engagement member 246 has the disc portion 254 disposed adjacent the ring gear 206 , while the outer teeth 256 extend into the ring gear 206 .
- the outer teeth 256 are disposed concentrically within the inner teeth 228 of the ring gear 206 .
- the alternating clutch plates 252 are disposed between the outer teeth 256 and the ring gear 206 in engagement with both the outer teeth 256 and the inner teeth 228 .
- the clutch pressure plate 248 is secured by the ring 268 directly adjacent the clutch plates 252 within the ring gear 206 .
- the clutch control mechanism 250 is disposed between the engagement member 246 and the clutch plates 252 .
- the engagement member 246 is generally secured within the enclosure 188 via one or more outer securement portions or mechanisms 288 , while the ring gear 206 can selectively rotate or become fixed with respect to a central axis 290 .
- the clutch control mechanism 250 may be variably engaged or disengaged to move toward or away from the clutch plates 252 , as indicated by arrow 292 .
- the seal portion 258 disposed on the engagement member 246 may include one or more ring seals and or fluid passages to increase or decrease fluid pressure against the clutch control mechanism 250 . In this manner, the clutch control mechanism 250 can increase or decrease the pressure on the clutch plates 252 between the clutch control mechanism 250 and the clutch pressure plate 248 .
- the clutch plates 260 are generally geared or secured to the outer teeth 256 on the engagement member 246 .
- the clutch plates 262 are generally geared or secured to the ring gear 206 . If the pressure or force is relatively low between the clutch control mechanism 250 and the clutch pressure plate 248 , then the clutch plates 260 and 262 can generally slide or rotate with respect to one another without any substantial torque transference. As appreciated, a quantity of cooling oil is pumped into the interior of the module 20 , such that a film or amount of the oil resides between the alternating clutch plates 260 and 262 .
- Torque is generally transmitted between the clutch plates 260 and 262 via shearing of the oil film separating the plates 260 and 262 , thereby at least substantially reducing or eliminating wear on the facing surfaces of the plates 260 and 262 .
- the clutch may be described as a wet clutch. If the pressure or force is increased between the clutch control mechanism 250 and the clutch pressure plate 248 , then the increasing shear in the oil film between the clutch plates 260 and 262 will gradually restrict and eventually prevent rotation between the clutch plates 260 and 262 . As a result, full engagement of the clutch control mechanism 250 will gradually slow the rotation and fix the ring gear 206 within the enclosure 188 . As a result of this gradual fixation of the ring gear 206 , the planetary gear assembly 204 will gradually start and increase rotation about the central axis 290 within the ring gear 206 .
- the illustrated planetary gear assembly 204 is rotatingly coupled to or geared with both the motor shaft 184 and the ring gear 206 .
- the sun gear 224 of the planetary gear assembly 204 may be coupled to the motor shaft 184 via the gear 272 and the gear 274 .
- the gear 274 extends partially around and is geared with both the gear 272 and the sun gear 224 .
- the sun gear 224 also rotates as indicated by arrow 294 .
- each of the planet gears 218 is rotatingly coupled to or generally geared with the sun gear 224 as well as the inner teeth 230 of the ring gear 206 .
- the planet gears 218 also include one or more bearing structures or assemblies 296 disposed along the planet shafts 222 between the support structures 212 and 214 of the gear carrier 210 .
- the sun gear 224 rotates as indicated by arrow 294
- the planet gears 218 rotate about the respective planet shafts 222 as indicated by arrows 298 .
- the planet gears 218 force the ring gear 206 to rotate about the planetary gear assembly 204 or, alternatively or simultaneously, the planet gears 218 cause the planetary gear assembly 204 along with the output shaft 196 to rotate about the central axis 290 .
- the rotation of the planet gears 218 will generally cause the ring gear 206 to rotate about the central axis 290 without any corresponding rotation of the planetary gear assembly 204 .
- the clutch control mechanism 250 gradually increases the friction between the first and second sets of clutch plates 260 and 262 , the ring gear 206 will gradually become fixed causing the planetary gear assembly 204 to rotate within the ring gear 206 .
- FIG. 9 is a cross-sectional view of an embodiment of the integral planetary gear and clutch module 20 as illustrated in FIGS. 5-8 , further illustrating the interrelationship between the ring gear 206 , a set of four planet gears 218 , and the sun gear 224 of the gear system 200 .
- the motor 18 rotatingly drives the sun gear 224 in a first rotational direction (e.g., counter clockwise) as indicated by arrow 300 .
- the shaft 184 of the motor 18 is coupled to the sun gear 224 by the gear 272 and the gear 274 .
- the drive shaft 184 and the gears 272 , 274 , and 224 all rotate together about the same central axis 290 and, thus, generally have the same rate of angular rotation or rotational speed, e.g., rotations per minute (RPM).
- RPM rotations per minute
- the speed generally refers to rate of angular rotation or rotational speed, rather than the surface speed or tangential speed at the interface between engaging gears, shafts, or other rotating components.
- the sun gear 224 drives three or more (e.g., four planet gears 218 ) in a second rotational direction (e.g., clockwise) as indicated by arrows 302 .
- the four planet gears 218 rotate in an opposite rotational direction relative to the sun gear 224 .
- the planet gears 218 engage the ring gear 206 to cause rotation of the gear carrier 210 as indicated by arrow 304 , or to cause rotation of the ring gear 206 as indicated by arrow 306 , or a combination thereof.
- the planet gears 218 generally impart all of the speed and torque to cause the gear carrier 210 to rotate in a third rotational direction (e.g., counterclockwise) within the stationary outer ring gear 206 as indicated by arrow 304 .
- the gear carrier 210 of the planetary gear assembly 204 may remain at least substantially or entirely stationary within the ring gear 206 .
- the planet gears 218 may impart a substantial portion or all of the speed and torque to the ring gear 206 to cause rotation of the ring gear 206 in a fourth rotational direction (e.g., clockwise) as indicated by arrow 306 .
- a fourth rotational direction e.g., clockwise
- the planet gears 218 may engage with the ring gear 206 to cause some counterclockwise rotation of the gear carrier 210 and some clockwise rotation of the ring gear 206 as indicated by arrows 304 and 306 .
- operation of the clutch system 202 can gradually slow or stop the clockwise rotation of the ring gear 206 , while simultaneously ramping up or increasing the counterclockwise rotation of the gear carrier 210 and the corresponding output shaft 196 .
- the planet gears 218 have a radius or diameter substantially larger than the radius or diameter of the sun gear 224
- the ring gear 206 has a radius or diameter substantially larger than radius or diameter of the planet gears 218 and the sun gear 224 .
- the gear ratio depends on the sun gear 224 and the ring gear 206 in the illustrated embodiment. Specifically, the gear ratio may be calculated as:
- the gear ratio generally increases as the diameter and number of teeth in the ring gear 206 increases relative to the sun gear 224 .
- the gear ratio may be in the range of about 3:1 to about 9:1, or in the range of about 4.5:1 to about 5:1.
- the gear system 200 can substantially reduce the speed and substantially increase the torque of the motor 18 , while the clutch system 202 can gradually or progressively impart the rotation of the motor output shaft or drive shaft 184 to the output shaft 196 of the integral planetary gear and clutch module 20 .
- the gear system 200 may reduce the output speed of the motor 18 from about 1800-3600 RPM to about 200-1000 RPM (or about 200-800 RPM) at the pump 22 .
- the gear system 200 also may increase the torque to between about 10,000 inch-pounds and 2,000,000 inch-pounds at the pump 22 .
- the module 20 as illustrated in FIG. 9 may represent a planetary gear system 200 without a corresponding clutch system 202 as illustrated in FIG. 7 .
- the ring gear 206 may be fixably disposed within the enclosure 188 of the module 20 , rather than selectively rotating or becoming stationary in response to the clutch system 202 as illustrated in FIG. 7 .
- the motor output shaft or drive shaft 184 causes rotation of the sun gear 224 as indicated by arrow 300 , which in turn causes rotation of the planet gears 218 as indicated by arrow 302 .
- the planet gears 218 rotate along the inner teeth 230 of the ring gear 206 to cause rotation of the gear carrier 210 as indicated by arrow 304 .
- the ring gear 206 is stationary in this alternative embodiment, such that all of the speed and torque is transmitted to the gear carrier 210 rather than the ring gear 206 .
- the module 20 may include or exclude the clutch system 202 in various embodiments.
- other embodiments of the module 20 may include other forms or types of clutch systems, other arrangements or gear ratios of the planetary gear assembly 204 , and so forth.
- the module 20 substantially increases torque and decreases speed of the motor 18 .
- each of these embodiments enables the use of a substantially smaller motor 18 and a substantially smaller support structure 26 , thereby reducing costs and complexities associated with pumping a large body of water to a remote site as discussed above.
- FIG. 10 is a flow chart of an exemplary embodiment of a pumping process 310 using an embodiment of the planetary gear system 20 as discussed in detail above.
- the process 310 includes opening one or more valves to full open flow positions at or between a pump and a remote site (block 312 ).
- the process 310 also includes soft starting the motor at normal operating conditions without a load on the motor (block 314 ).
- the soft start process 314 may involve starting up the motor with a clutch at least partially or completely disconnected from the load, e.g., a pump disposed within a liquid.
- the process 310 further includes engaging a planetary gear/clutch system between the motor and the pump.
- the engagement process 316 may involve an initial engagement of clutch plates, such as wet clutch plates, between the motor and the pump.
- the process 310 may then proceed by increasing engagement between the motor and the pump via the planetary gear/clutch system to increase the speed of the pump (block 318 ).
- the process 310 may slowly compress the clutch plates together, thereby causing friction and torque to cause a gradual increase in the rotation of the planetary gear assembly between the motor and the pump.
- the process 310 may include monitoring one or more parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback for controlling the operation of the planetary gear/clutch system.
- the process 310 may query whether or not the feedback is acceptable. If the process 310 identifies the feedback 322 as unacceptable, then the process 310 may respond by decreasing engagement between the motor and the pump via the planetary gear/clutch system to decrease the speed of the pump (block 324 ). In turn, the process 310 loops back or continues by monitoring parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback (block 320 ).
- the process 310 may proceed to query whether or not the planetary gear/clutch system is in full engagement between the motor and the pump (block 326 ). If the process 310 determines that the planetary gear/clutch system is in full engagement at block 326 , then the process 310 may continue or loop back to monitor parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback (block 320 ).
- the process 310 may loop back or continue by increasing engagement between the motor and the pump via the planetary gear/clutch system to increase the speed of the pump (block 318 ). Again, the process 310 continues to loop through blocks 320 , 322 , 324 , and 326 . In this manner, the pumping process 310 operates in a closed loop to gradually increase or decrease the speed of the pump using the planetary gear/clutch system and feedback obtained throughout the pumping system.
- the illustrated process 310 may be applied to a start up procedure, a shut down procedure, a transient hydraulic instability condition, and so forth. By using the process 310 , the pump can gradually increase or decrease to the desired operating speed with a substantially reduced possibility of water hammer or other damaging hydraulic effects.
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Abstract
In one embodiment, a pump system includes a motor-to-pump transmission having a planetary gear assembly and a clutch. In another embodiment, a pump system includes a transmission having a housing with a motor mount and a pump mount, a central gear disposed in the housing, a plurality of planet gears disposed in the housing, wherein the plurality of planet gears is disposed about and engaged with the central gear. The transmission also includes an outer ring gear disposed in the housing, wherein the outer ring gear is disposed about and engaged with the plurality of planet gears.
Description
- This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the present invention, which are described and/or claimed below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present invention. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.
- Pumps may be used in a wide variety of applications to transfer a liquid, such as water, from one location to another. For example, one or more pumps may transfer a large quantity of water from a lake, cooling pond, river, or ocean to a remote facility or site. In certain applications, the one or more pumps may transfer the liquid, e.g., water, horizontally for miles to reach the remote facility or site.
- Unfortunately, the start up and shut down stages may adversely affect the pump and associated components due to transient hydraulic instabilities. The hydraulic instabilities associated with the start up and shut down stages generally increase with greater vertical and horizontal distances between the pump and the remote site. Unfortunately, the transient hydraulic instabilities generally reduce the life of the pump and associated components. For example, an abrupt change in the flow or pressure within the pumping system can result in water hammer, which may cause piping failures, broken pump shafts, motor damage, structural damage, broken pipe hangers, mechanical seal failures, and so forth.
- In addition, the pumps and motors in certain pumping systems may be very large and expensive due to various operational parameters. For example, in high-flow, low-head, vertical pumping systems, the desired speed of the pump may be significantly below the nominal speed of a typical two or four pole motor. Unfortunately, the motor cost, size and weight generally increase dramatically with corresponding increases in the horse power ratings, e.g., greater than one thousand horse power. In turn, the increased size and weight of the motor generally results in a larger pump and support structure.
- Certain aspects commensurate in scope with the originally claimed invention are set forth below. It should be understood that these aspects are presented merely to provide the reader with a brief summary of certain forms the invention might take and that these aspects are not intended to limit the scope of the invention. Indeed, the invention may encompass a variety of aspects that may not be set forth below.
- In one embodiment, a pump system includes a motor-to-pump transmission having a planetary gear assembly and a clutch or brake mechanism. In another embodiment, a pump system includes a transmission having a housing with a motor mount and a pump mount, a central or sun gear disposed in the housing, a plurality of planet gears disposed in the housing, wherein the plurality of planet gears is disposed about and engaged with the central gear. The transmission also includes an outer ring gear disposed in the housing, wherein the outer ring gear is disposed about and engaged with the plurality of planet gears.
- These and other features, aspects, and advantages of the present technique will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
-
FIG. 1 is a block diagram illustrating an embodiment of a liquid transfer or pumping system having a planetary gear system coupled to a motor and a pump; -
FIG. 2 is a block diagram of an embodiment of a modular pumping system having a planetary gear system; -
FIG. 3 is a block diagram of an embodiment of a modular drive system; -
FIG. 4 is a block diagram of an embodiment of a modular pump system; -
FIG. 5 is a perspective view of an embodiment of a vertical pump drive having a motor coupled to an integral planetary gear and clutch module; -
FIG. 6 is an exploded perspective view of an embodiment of the vertical pump drive as illustrated inFIG. 5 ; -
FIG. 7 is an exploded perspective view of an embodiment of the integral planetary gear and clutch module as illustrated inFIGS. 5 and 6 ; -
FIG. 8 is a cross-sectional view of an embodiment of the integral planetary gear and clutch module as illustrated inFIGS. 5-7 ; -
FIG. 9 is a cross-sectional view of an embodiment of a planetary or epicyclic gear assembly disposed within the integral planetary gear and clutch module as illustrated inFIGS. 5-8 ; and -
FIG. 10 is a flow chart of an embodiment of a start up process for the vertical pump drive as illustrated inFIGS. 5-9 . - One or more specific embodiments of the present invention will be described below. In an effort to provide a concise description of these embodiments, all features of an actual implementation may not be described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers' specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.
-
FIG. 1 is a block diagram of an embodiment of a liquid transfer orpumping system 10 having one or more planetary gear systems disposed between respective motors and pumps. In the following discussion, the planetary gear system is used simply for convenience, and is intended to cover either a planetary gear system (e.g., 146) or a planetary gear system with a clutch or a brake mechanism (e.g., 150). In certain modular systems as discussed below with reference toFIGS. 3 and 4 , various transmissions and/or clutch systems including 146 and 148 may be exchanged with one another based on the specific parameters of the pumping application. In the embodiments as discussed below with reference toFIGS. 1 , 2, and 5-10, each of the planetary gear systems generally includes a planetary gear assembly, which also may include a clutch or brake assembly to vary (e.g., increase or decrease) the output from the motor to the respective pump. However, in other embodiments, such as illustrated inFIGS. 3 and 4 , a controlstart transmission module 148 may be used with or without a planetary gear assembly. - As illustrated in
FIG. 1 , the liquid transfer orpumping system 10 may include a first orvertical pump arrangement 12, a second orhorizontal pump arrangement 14, and a third orhorizontal pump arrangement 16. In certain embodiments, the first orvertical pump arrangement 12 includes amotor 18, aplanetary gear system 20 coupled to themotor 18, apump 22 coupled to theplanetary gear system 20, and acontrol unit 24 communicatively coupled to one or more of the vertically arrangedcomponents control unit 24 may include a pump speed and/or thrust controller to vary the pumping speed and, thus, thrust based on various conditions in the liquid transfer orpumping system 10. - As discussed in further detail below, embodiments of the
planetary gear system 10 enable use of significantly smaller sized motors and support structures, thereby reducing costs and complexities of thepumping system 10. For example, theplanetary gear system 20 enables a substantial reduction in the dimensions, weight, and general size of themotor 18 to drive thepump 22. In turn, the smaller size of themotor 18 enables a reduction in the dimensions, weight, and general size of asupport structure 26, which may be configured to support themotor 18, theplanetary gear system 20, and thepump 22. - In addition, embodiments of the
planetary gear system 20 enable a generally smooth and gradual transition during start up, shut down, or other stages or periods involving hydraulic instabilities. In other words, theplanetary gear system 20 may gradually change (e.g., increase or decrease) the speed of thepump 22 during transient stages (e.g., startup or shutdown), thereby reducing the possibility of water hammer and other undesirable abrupt changes in thepumping system 10. For example, a clutch mechanism (e.g., a wet clutch) of theplanetary gear system 20 may be controlled to vary a degree of slip between clutch plates, thereby varying the output speed to thepump 22. In this manner, theplanetary gear system 20 can gradually change the pump speed based on various input/sensed parameters. - In the illustrated embodiment, the
pump 22 is submerged in water below awater line 28, while themotor 18, theplanetary gear system 20, and thecontrol unit 24 are disposed above thewater line 28. In addition, the illustratedplanetary gear system 20 is coupled to thepump 22 by ashaft 30. In other embodiments, themotor 18, theplanetary gear system 20, and thepump 22 may be coupled directly together and mounted above thewater line 28, while an intake conduit extends to a point below thewater line 28. However, in the illustrated embodiment, thepump 22 includes one ormore fluid inlets 32 and one ormore fluid outlets 34 submerged below thewater line 28 along with the rest of thepump 22. - Although the
pump 22 may include a variety of pumping features, the illustratedpump 22 includes one ormore fluid passages 36 having one ormore pump impellers 38 disposed between thefluid inlet 32 and thefluid outlet 34. Thepump 22 also can include one or more check valves, manual valves, or electromechanical valves. For example, the check valves generally reduce or prevent flow of fluid from thefluid outlet 34 back through thefluid passages 36 to thefluid inlet 32. The electromechanical valves also can be controlled via thecontrol unit 24. In the illustrated embodiment, anelectromechanical valve 40 is coupled to thepump 22 at or near thefluid outlet 34. - In addition, a water or
fluid conduit 42 is coupled to theelectromechanical valve 40 and extends both vertically and horizontally to aremote site 44. For example, the illustratedfluid conduit 42 includes a relatively shorthorizontal conduit portion 46, avertical conduit portion 48, and a relatively longhorizontal conduit portion 50. In some embodiments, thevertical conduit portion 48 may have a relatively short length, height, or head between thehorizontal conduit portions horizontal conduit portion 50 may extend for miles to theremote site 44. At theremote site 44, anotherelectromechanical valve 52 may be coupled to thefluid conduit 42. Theremote site 44 also can include one or more fluid delivery or distribution systems, such assystems systems arrows - In the illustrated embodiment of
FIG. 1 , thecontrol unit 24 is communicatively coupled to a plurality of sensors disposed in the first orvertical pump arrangement 12 and along the water orfluid conduit 42 to theremote site 44. For example, the illustratedcontrol unit 44 is communicatively coupled tosensors motor 18. In addition, the illustratedcontrol unit 24 is communicatively coupled tosensors planetary gear system 20. Thecontrol unit 24 also may be coupled to one ormore sensors 82 disposed on or adjacent theshaft 30 extending between theplanetary gear system 20 and thepump 22. Furthermore, the illustratedcontrol unit 24 is communicatively coupled tosensors pump 22. For example, thesensors fluid passages 36 of thepump 22. In addition, the illustratedcontrol unit 24 can be coupled to one ormore sensors 98 and 100 disposed outside or at least partially inside or within thefluid conduit 42, such as at a top portion of thevertical conduit portion 48. - In general, the sensors 66-100 may include temperature sensors, pressure sensors, voltage sensors, current sensors, torque sensors, mechanical speed sensors (e.g., linear or rotational speed), fluid speed sensors, fluid mass or volumetric flow rate sensors, and so forth. These sensors 66-100 generally provide feedback to the
control unit 24, which can then respond in a closed loop to adjust characteristics of themotor 18, theplanetary gear system 20, and/or thepump 22. For example, as discussed in detail below, the feedback from the sensors 66-100 may trigger thecontrol unit 24 to increase or decrease the speed of themotor 18. The feedback from the sensors 66-100 also may trigger thecontrol unit 24 to increase or decrease the engagement of a clutch (e.g., a wet clutch) disposed within theplanetary gear system 20, thereby selectively increasing or decreasing an output rate ofrotation 102 of theshaft 30. In turn, the feedback controlled rate ofrotation 102 alters the general speed or flow rate of thepump 22. In certain embodiments, this feedback control of themotor 18, theplanetary gear system 20, and thepump 22 enables a more gradual start up or shut down of thevertical pump arrangement 12, thereby substantially reducing the possibility of abrupt hydraulic changes or damage in the liquid transfer orpumping system 10. The feedback control may continue until the liquid transfer orpumping system 10 reaches a hydraulically stable condition between thepump 22 and theremote site 44, for example. The feedback control also may continue after reaching a hydraulically stable condition, thereby providing a response mechanism for any changes in thesystem 10. - Similar to the first or
vertical pump arrangement 12, the second and thirdhorizontal pump arrangement FIG. 1 includemotors planetary gear systems respective motors planetary gear systems horizontal pump arrangements control units control unit 116 is communicatively coupled to a plurality ofsensors 120 disposed on, within, or in general proximity to themotor 104, theplanetary gear system 108, and thepump 112. Similarly, the illustratedcontrol unit 118 is communicatively coupled to a plurality ofsensors 122 disposed on, within, or in general proximity to themotor 106, theplanetary gear system 110, and thepump 114. Thesesensors FIG. 1 , the second and thirdhorizontal pump arrangement pumps planetary gear systems arrangements planetary gear systems motors - In addition, the illustrated liquid transfer or
pump system 10 can include acentral control system 124 communicatively coupled to one or more of thepump arrangements remote site 44. Thecentral control system 124 also may be communicatively coupled to one or more sensors disposed throughout the overall liquid transfer orpumping system 10. For example, the illustratedcentral control system 124 is communicatively coupled to theelectromechanical valve 52 andadditional sensors fluid conduit 42 at or near theremote site 44. In operation, thecentral control system 124 can transmit, receive, and generally exchange sensed feedback, data, and commands with thecontrol units vertical pump arrangement 12, the second orhorizontal pump arrangement 14, and the third orhorizontal pump arrangement 16 as well as theremote site 44. Again, various feedback may be employed by thecentral control system 124 and thevarious control units motors planetary gear systems -
FIG. 2 is a block diagram of an exemplary embodiment of amodular pumping system 130 having theplanetary gear system 20. In the illustrated embodiment, theplanetary gear system 20 enables a substantial motor size reduction from a standard largedirect drive motor 132 to a relatively smallhigh speed motor 18 as illustrated byarrows 134. For example, the standard largedirect drive motor 132 may have a speed output in the range of 400-600 RPM and a torque output of about 1×106 inch-pounds. In contrast, the relatively smallhigh speed motor 18 may have a speed output in the range of 1800-3600 RPM and a torque output of about 175×103 inch-pounds. The smaller motor tends to be more efficient and also has a higher power factor. These features can significantly lower the life cycle operating costs. - As a result of the substantially reduced motor size, the
planetary gear system 20 also enables a substantial support size reduction from a standard large direct drivensupport structure 136 to a relativelysmall support structure 26 as indicated byarrows 138. As appreciated in view of the foregoing examples, themotor 132 and thesupport structure 136 have significantly greater dimensions, weight, and overall size in a direct drive configuration without the intermediateplanetary gear system 20. Thus, theplanetary gear system 20 substantially reduces the costs, support structures, and general complexities of the larger direct drive configuration of themotor 132 and thesupport structure 136. - The
planetary gear system 20 also simplifies the installation, access, handling, and general maintenance of themodular pumping system 130. For example, the reduced size as illustrated by the smallhigh speed motor 18 and thesmall support structure 26 can allow additional mounting arrangements of themodular pumping system 130. By further example, themodular pumping system 130 may be mounted entirely above the water line or other body of liquid. Themodular pumping system 130 also enables a variety of different smallhigh speed motors 18,planetary gear systems 20, and pumps 22 to be selectively coupled together to meet the demands of a particular pumping application. For example, a particular application may have a shorter or longer horizontal run of fluid conduit, a larger or smaller head or vertical run of fluid conduit, a smaller or greater desired fluid flow rate, and so forth. -
FIG. 3 is a block diagram of an exemplary embodiment of amodular drive system 140 having a family of interchangeable motors ormotor modules 142 and different families ofinterchangeable transmission modules 144. For example, the family of interchangeable motors ormotor modules 142 may include different sizes or motor parameters, such as speed, horse power, torque, variable speeds, and so forth. In addition, the different families ofinterchangeable transmission modules 144 may include a plurality of different motor-to-pump transmissions, which may include planetary gear assemblies, clutches, pump speed and/or thrust controllers, and combinations thereof. As illustrated, the different families ofinterchangeable transmission modules 144 may include a plurality or family ofplanetary gear modules 146, a plurality or family of controlstart transmission modules 148, and plurality or family of integral planetary gear andclutch modules 150, a plurality or family ofplanetary gear modules 152 respectively coupled to a plurality or family ofclutch modules 154, and a plurality or family ofclutch modules 156 respectively coupled to a plurality or family ofplanetary gear modules 158. - For example, as discussed in further detail below, each
planetary gear module 146 may include a central sun gear, a plurality of planet gears disposed about the central or sun gear, and an outer ring gear disposed about the plurality of planet gears. The controlstart transmission module 148 may include one or more gear reduction mechanisms, one or more clutch mechanisms, and one or more feedback control mechanisms to enable variable speed output from themotor 142 in response to various feedback data. The integral planetary gear andclutch module 150 may include a planetary gear assembly, such as a central or sun gear, a plurality of surrounding planet gears, and a surrounding ring gear. In addition, the integral planetary gear andclutch module 150 may include a variety of clutch mechanisms, such as a wet clutch, disposed near an input or an output drive shaft. In other words, the clutch mechanism may be disposed before, after, or simultaneous with the gear reduction mechanisms in a common housing. Theplanetary gear modules 152 andclutch modules 154 are generally configured to engage themotor 142 with a shaft between theclutch module 154 and themotor 142. In contrast, each set ofclutch module 156 and correspondingplanetary gear module 158 is configured to engage a selectedmotor 142 with a shaft between theplanetary gear module 158 and themotor 142. - In view of these different features, the
modular drive system 140 as illustrated inFIG. 3 enables a variety of configurations betweendifferent motors 142 anddifferent transmission modules 144. Again, thedifferent motors 142 can have different operational characteristics, while eachmodule interchangeable transmission modules 144 can have different gear ratios, clutch features, and so forth. For example, the gear ratios in each family can include a series of incrementally increasing gear ratios from a base ratio to a max ratio. Similarly, each clutch in the different families can include a series or set of incrementally increasing ranges of clutch play and other operational ranges. Therefore, the different modules can be coupled together to suit a particular application or load, such as a pumping application, a conveyer belt application, and so forth. -
FIG. 4 is a block diagram of an exemplary embodiment of a modular pump system 160 including the different families ofinterchangeable transmission modules 144 as illustrated and described above with reference toFIG. 3 , further including a plurality or family of interchangeable pump or pumpmodules 162. Again, the different families ofinterchangeable transmission modules 144 may include a plurality or family orplanetary gear modules 146, a plurality or family of controlstart transmission modules 148, a plurality or family of integral planetary gear andclutch modules 150, a plurality or family ofplanetary gear modules 152 respectively coupled withclutch modules 154, and a plurality or family ofclutch modules 156 respectively coupled withplanetary gear modules 158. Again, thesedifferent modules 144 may have a variety of different gear ratios, clutch ranges, and so forth. Similarly, the family of interchangeable pumps or pumpmodules 162 may have a series of pumps having incrementally changing pump features, such as pump speed, flow rate, output thrust, and so forth. As a result, the modular pump system 160 enables a wide range of different configurations of thetransmission modules 144 and the pumps or pumpmodules 162 to meet the demands of a particular pumping application, such as a vertical pumping application. -
FIG. 5 is a perspective view of an exemplaryvertical pump drive 170 having an embodiment of themotor 18 coupled to an embodiment of theplanetary gear system 20 as discussed above with reference toFIGS. 1 and 2 . In the illustrated embodiment, themotor 18 includes acentral motor structure 172, opposite perforated ventingportions control unit 24, anupper support structure 178, and alower support structure 180. Thelower support structure 180 may include amount panel 181, anopposite panel 182, and intermediate ribs orsupport members 183. The illustratedplanetary gear system 20 may include or embody an integral planetary gear and clutch module, such as mentioned above with reference tomodule 150 as illustrated inFIGS. 3 and 4 . The integral planetary gear andclutch module 20 may be selectively mounted and dismounted with themotor 18 and one or more alternative motors to meet the demands of a particular load or application, such as a vertical and/or horizontal pumping application. -
FIG. 6 is an exploded perspective view of thevertical pump drive 170 as illustrated inFIG. 5 , further illustrating the integral planetary gear andclutch module 20 exploded from themotor 18. As illustrated inFIG. 6 , themotor 18 includes a motor output shaft or driveshaft 184 extending outwardly from themount panel 181. The motor output shaft or driveshaft 184 may include a variety of coupling mechanisms to engage with the integral planetary gear andclutch module 20. However, the illustrateddrive shaft 184 includes akey slot 186. The integral planetary gear andclutch module 20 includes a casing orenclosure 188 havingsupport ribs 190 extending lengthwise between a first flange ormotor mount 192 and a second flange or pumpmount 194. The integral planetary gear andclutch module 20 also includes anoutput shaft 196 extending outwardly from the central flange or pumpmount 194. Similar to thedrive shaft 184, theoutput shaft 196 may have a variety of different coupling mechanisms to connect with a pump, machine, or other load. However, the illustratedoutput shaft 196 includes akey slot 198. -
FIG. 7 is an exploded perspective view of an exemplary embodiment of the integral planetary gear andclutch module 20 as illustrated inFIGS. 5 and 6 , further illustrating an embodiment of agear system 200 and aclutch system 202. In the illustrated embodiment, thegear system 200 includes a planetary orepicyclic gear assembly 204, anouter ring gear 206, and a clutch-gear interface bearing 208 (e.g., a radial bearing). For example, the illustratedplanetary gear assembly 204 includes agear carrier 210 having a first annular portion orsupport structure 212, a second annular orsupport structure 214, and a third annular orintermediate support structure 216 disposed between thestructures 212 and 214 (seeFIGS. 7 and 8 ). In addition, theplanetary gear assembly 204 includes a plurality of planet gears 218 disposed in planet gear receptacles orengagement openings 220 within theintermediate support structure 216 of thegear carrier 210. For example, theplanetary gear assembly 204 may include a set of 3, 4, 5, 6, or more planet gears 218 andcorresponding engagement openings 220. In addition, theplanetary gear assembly 204 includes aplanet shaft 222 for eachrespective planet gear 218 to rotate about within theengagement opening 220. Theplanetary gear assembly 204 also includes theoutput shaft 196 extending through thesupport structure 214 into the interior of theintermediate support structure 216 to a central orsun gear 224, which engages each of the planet gears 218 as illustrated and discussed below with reference toFIG. 8 . Theplanetary gear assembly 204 extends partially into and mates with thering gear 206. - As illustrated in
FIG. 7 , thering gear 206 has a generallycylindrical interior 226 having first and second inner annular gear portions orinner teeth annular separation portion 232 having aring slot 234. Thering gear 206 also may include a plurality oflubrication passages 236 extending from a generallycylindrical exterior 238 to the generallycylindrical interior 226. As discussed in further detail below, theplanetary gear assembly 204 is inserted into thering gear 206, such that each of the planet gears 218 engages theinner teeth 230. In addition, thebearing 208 may be disposed about thesupport structure 212 of theplanetary gear assembly 204, such that thegear carrier 210 may rotatingly engage a portion of theclutch system 202. The illustratedbearing 208 includes inner and outer bearingsleeves 240 and 242 disposed concentrically about a plurality ofroller members 244. - The illustrated
clutch system 202 ofFIG. 7 includes a first clutch support orannular engagement member 246 and a second clutch support or annularclutch pressure plate 248. In certain embodiments, theengagement member 246 may be described as a clutch carrier, and theclutch pressure plate 248 may be described as a clutch pack backing ring. Theengagement member 246 andpressure plate 248 are disposed about an annular piston orclutch control mechanism 250 and a set of alternating inner and outer gearedclutch plates 252. In certain embodiments, the set ofclutch plates 252 may be described as a clutch pack. As illustrated, theengagement member 246 includes adisc portion 254 and an outer annular gear portion orouter teeth 256. In addition, the illustratedengagement member 246 includes a piston interface orseal portion 258 disposed in the region between thedisc portion 254 and theouter teeth 256. - The illustrated set of alternating
clutch plates 252 includes a first set ofclutch plates 260 and a second set ofclutch plates 262. Theclutch plates 260 includeinner teeth 264, while theclutch plates 262 includeouter teeth 266. In assembly, theseclutch plates outer teeth - The
clutch system 202 also may include an annular retainer orclutch securement ring 268, which engages or generally interlocks with thering slot 234 disposed within thering gear 206. As discussed below, theclutch securement ring 268 secures thepressure plate 248 adjacent theinner teeth 228 inside thering gear 206. In addition, theclutch plates 252 may be inserted into thering gear 206, such that theclutch plates 262 having theouter teeth 262 engage with theinner teeth 228. Furthermore, the illustratedclutch control mechanism 250 may be assembled in movable engagement between theengagement member 246 and theclutch pressure plate 248. - As further illustrated in
FIG. 7 , when theclutch system 202 is assembled with thegear system 200, theouter teeth 256 extend into the set of alternatingclutch plates 252 within thering gear 206. In this configuration, theouter teeth 256 engage with theinner teeth 264 of the alternatingclutch plates 260. Furthermore, the bearing 208 generally extends into theouter teeth 256, such that the outer bearing sleeve 242 fits within an inner cylindrical portion or bearinginterface 270 of theengagement member 246. The bearing 208 also extends around thesupport structure 212 and engages theintermediate support structure 216 of theplanetary gear assembly 204 when assembled within thering gear 206. - In addition to these features of the
gear system 200 andclutch system 202, the integral planetary gear andclutch module 20 may include a drive gear or outerannular gear 272 secured about or generally coupled with theshaft 184 of themotor 18. In addition, a drive gear coupling or innerannular gear 274 may be disposed about thegear 272 and a portion of thesun gear 224, as illustrated and described below with reference toFIG. 8 . In certain embodiments, thegears module 20 may include a plurality of annular support structures, seals, shock absorbent mechanisms, bearings, and so forth. For example, annular structures orassemblies planetary gear assembly 204 and an inner portion of theenclosure 188. In certain embodiments, theassemblies output shaft 196 of theplanetary gear assembly 204 extends through ashaft opening 282 having ashaft flange 284 and anannular seal 286 disposed in theenclosure 188. -
FIG. 8 is a cross-sectional view of the integral planetary gear andclutch module 20 as illustrated inFIG. 7 , further illustrating thegear system 200 and theclutch system 202 integrally assembled within theenclosure 188. For example, as illustrated inFIG. 8 , theengagement member 246 has thedisc portion 254 disposed adjacent thering gear 206, while theouter teeth 256 extend into thering gear 206. Specifically, theouter teeth 256 are disposed concentrically within theinner teeth 228 of thering gear 206. The alternatingclutch plates 252 are disposed between theouter teeth 256 and thering gear 206 in engagement with both theouter teeth 256 and theinner teeth 228. In addition, theclutch pressure plate 248 is secured by thering 268 directly adjacent theclutch plates 252 within thering gear 206. - Opposite from the
plate 248, theclutch control mechanism 250 is disposed between theengagement member 246 and theclutch plates 252. In the illustrated embodiment, theengagement member 246 is generally secured within theenclosure 188 via one or more outer securement portions ormechanisms 288, while thering gear 206 can selectively rotate or become fixed with respect to acentral axis 290. More specifically, theclutch control mechanism 250 may be variably engaged or disengaged to move toward or away from theclutch plates 252, as indicated byarrow 292. For example, theseal portion 258 disposed on theengagement member 246 may include one or more ring seals and or fluid passages to increase or decrease fluid pressure against theclutch control mechanism 250. In this manner, theclutch control mechanism 250 can increase or decrease the pressure on theclutch plates 252 between theclutch control mechanism 250 and theclutch pressure plate 248. - As discussed above, the
clutch plates 260 are generally geared or secured to theouter teeth 256 on theengagement member 246. However, theclutch plates 262 are generally geared or secured to thering gear 206. If the pressure or force is relatively low between theclutch control mechanism 250 and theclutch pressure plate 248, then theclutch plates module 20, such that a film or amount of the oil resides between the alternatingclutch plates clutch plates plates plates clutch control mechanism 250 and theclutch pressure plate 248, then the increasing shear in the oil film between theclutch plates clutch plates clutch control mechanism 250 will gradually slow the rotation and fix thering gear 206 within theenclosure 188. As a result of this gradual fixation of thering gear 206, theplanetary gear assembly 204 will gradually start and increase rotation about thecentral axis 290 within thering gear 206. - Specifically, the illustrated
planetary gear assembly 204 is rotatingly coupled to or geared with both themotor shaft 184 and thering gear 206. For example, as discussed above, thesun gear 224 of theplanetary gear assembly 204 may be coupled to themotor shaft 184 via thegear 272 and thegear 274. As illustrated inFIG. 8 , thegear 274 extends partially around and is geared with both thegear 272 and thesun gear 224. Thus, as themotor shaft 184 rotates about thecentral axis 290, thesun gear 224 also rotates as indicated byarrow 294. - Again, as discussed above, each of the planet gears 218 is rotatingly coupled to or generally geared with the
sun gear 224 as well as theinner teeth 230 of thering gear 206. As illustrated, the planet gears 218 also include one or more bearing structures orassemblies 296 disposed along theplanet shafts 222 between thesupport structures gear carrier 210. Thus, as thesun gear 224 rotates as indicated byarrow 294, the planet gears 218 rotate about therespective planet shafts 222 as indicated byarrows 298. - In turn, the planet gears 218 force the
ring gear 206 to rotate about theplanetary gear assembly 204 or, alternatively or simultaneously, the planet gears 218 cause theplanetary gear assembly 204 along with theoutput shaft 196 to rotate about thecentral axis 290. For example, if theoutput shaft 196 of theplanetary gear assembly 204 is coupled to a load and theclutch control mechanism 250 is not sufficiently engaged to overcome the load, then the rotation of the planet gears 218 will generally cause thering gear 206 to rotate about thecentral axis 290 without any corresponding rotation of theplanetary gear assembly 204. However, as theclutch control mechanism 250 gradually increases the friction between the first and second sets ofclutch plates ring gear 206 will gradually become fixed causing theplanetary gear assembly 204 to rotate within thering gear 206. -
FIG. 9 is a cross-sectional view of an embodiment of the integral planetary gear andclutch module 20 as illustrated inFIGS. 5-8 , further illustrating the interrelationship between thering gear 206, a set of fourplanet gears 218, and thesun gear 224 of thegear system 200. In the illustrated embodiment, themotor 18 rotatingly drives thesun gear 224 in a first rotational direction (e.g., counter clockwise) as indicated byarrow 300. As discussed above with reference toFIG. 7 , theshaft 184 of themotor 18 is coupled to thesun gear 224 by thegear 272 and thegear 274. Thedrive shaft 184 and thegears central axis 290 and, thus, generally have the same rate of angular rotation or rotational speed, e.g., rotations per minute (RPM). For purposes of discussion, the speed generally refers to rate of angular rotation or rotational speed, rather than the surface speed or tangential speed at the interface between engaging gears, shafts, or other rotating components. - Turning now to the
gear system 200, thesun gear 224 drives three or more (e.g., four planet gears 218) in a second rotational direction (e.g., clockwise) as indicated byarrows 302. Thus, the fourplanet gears 218 rotate in an opposite rotational direction relative to thesun gear 224. In turn, the planet gears 218 engage thering gear 206 to cause rotation of thegear carrier 210 as indicated byarrow 304, or to cause rotation of thering gear 206 as indicated byarrow 306, or a combination thereof. - In other words, if the
clutch system 202 is operated to completely fix thering gear 206 within the integral planetary gear andclutch module 20, then the planet gears 218 generally impart all of the speed and torque to cause thegear carrier 210 to rotate in a third rotational direction (e.g., counterclockwise) within the stationaryouter ring gear 206 as indicated byarrow 304. Alternatively, if theclutch system 202 is operated to allow complete or free rotation of thering gear 206 and if a load is coupled to theoutput shaft 196, then thegear carrier 210 of theplanetary gear assembly 204 may remain at least substantially or entirely stationary within thering gear 206. In this scenario, the planet gears 218 may impart a substantial portion or all of the speed and torque to thering gear 206 to cause rotation of thering gear 206 in a fourth rotational direction (e.g., clockwise) as indicated byarrow 306. However, if theclutch system 202 is partially engaged and if the load is coupled to theoutput shaft 196, then the planet gears 218 may engage with thering gear 206 to cause some counterclockwise rotation of thegear carrier 210 and some clockwise rotation of thering gear 206 as indicated byarrows clutch system 202 can gradually slow or stop the clockwise rotation of thering gear 206, while simultaneously ramping up or increasing the counterclockwise rotation of thegear carrier 210 and thecorresponding output shaft 196. - In the illustrated embodiment, the planet gears 218 have a radius or diameter substantially larger than the radius or diameter of the
sun gear 224, while thering gear 206 has a radius or diameter substantially larger than radius or diameter of the planet gears 218 and thesun gear 224. In general, the gear ratio depends on thesun gear 224 and thering gear 206 in the illustrated embodiment. Specifically, the gear ratio may be calculated as: -
Gear Ratio=(Teeth in Ring Gear)/(Teeth in Sun Gear)+1 - As a result, the gear ratio generally increases as the diameter and number of teeth in the
ring gear 206 increases relative to thesun gear 224. In certain embodiments, the gear ratio may be in the range of about 3:1 to about 9:1, or in the range of about 4.5:1 to about 5:1. Accordingly, thegear system 200 can substantially reduce the speed and substantially increase the torque of themotor 18, while theclutch system 202 can gradually or progressively impart the rotation of the motor output shaft or driveshaft 184 to theoutput shaft 196 of the integral planetary gear andclutch module 20. For example, thegear system 200 may reduce the output speed of themotor 18 from about 1800-3600 RPM to about 200-1000 RPM (or about 200-800 RPM) at thepump 22. Thegear system 200 also may increase the torque to between about 10,000 inch-pounds and 2,000,000 inch-pounds at thepump 22. - In certain embodiments, the
module 20 as illustrated inFIG. 9 may represent aplanetary gear system 200 without a correspondingclutch system 202 as illustrated inFIG. 7 . In other words, thering gear 206 may be fixably disposed within theenclosure 188 of themodule 20, rather than selectively rotating or becoming stationary in response to theclutch system 202 as illustrated inFIG. 7 . In this alternative embodiment, the motor output shaft or driveshaft 184 causes rotation of thesun gear 224 as indicated byarrow 300, which in turn causes rotation of the planet gears 218 as indicated byarrow 302. However, rather than allowing any selective movement of thering gear 206, the planet gears 218 rotate along theinner teeth 230 of thering gear 206 to cause rotation of thegear carrier 210 as indicated byarrow 304. Again, thering gear 206 is stationary in this alternative embodiment, such that all of the speed and torque is transmitted to thegear carrier 210 rather than thering gear 206. - Thus, the
module 20 may include or exclude theclutch system 202 in various embodiments. Furthermore, other embodiments of themodule 20 may include other forms or types of clutch systems, other arrangements or gear ratios of theplanetary gear assembly 204, and so forth. Again, themodule 20 substantially increases torque and decreases speed of themotor 18. As a result, each of these embodiments enables the use of a substantiallysmaller motor 18 and a substantiallysmaller support structure 26, thereby reducing costs and complexities associated with pumping a large body of water to a remote site as discussed above. -
FIG. 10 is a flow chart of an exemplary embodiment of apumping process 310 using an embodiment of theplanetary gear system 20 as discussed in detail above. As illustrated, theprocess 310 includes opening one or more valves to full open flow positions at or between a pump and a remote site (block 312). Theprocess 310 also includes soft starting the motor at normal operating conditions without a load on the motor (block 314). For example, thesoft start process 314 may involve starting up the motor with a clutch at least partially or completely disconnected from the load, e.g., a pump disposed within a liquid. Atblock 316, theprocess 310 further includes engaging a planetary gear/clutch system between the motor and the pump. For example, theengagement process 316 may involve an initial engagement of clutch plates, such as wet clutch plates, between the motor and the pump. Theprocess 310 may then proceed by increasing engagement between the motor and the pump via the planetary gear/clutch system to increase the speed of the pump (block 318). For example, theprocess 310 may slowly compress the clutch plates together, thereby causing friction and torque to cause a gradual increase in the rotation of the planetary gear assembly between the motor and the pump. - At
block 320, theprocess 310 may include monitoring one or more parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback for controlling the operation of the planetary gear/clutch system. Atblock 322, theprocess 310 may query whether or not the feedback is acceptable. If theprocess 310 identifies thefeedback 322 as unacceptable, then theprocess 310 may respond by decreasing engagement between the motor and the pump via the planetary gear/clutch system to decrease the speed of the pump (block 324). In turn, theprocess 310 loops back or continues by monitoring parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback (block 320). - If the
process 310 identifies the feedback as acceptable atblock 322, then theprocess 310 may proceed to query whether or not the planetary gear/clutch system is in full engagement between the motor and the pump (block 326). If theprocess 310 determines that the planetary gear/clutch system is in full engagement atblock 326, then theprocess 310 may continue or loop back to monitor parameters of the motor, the pump, the planetary gear/clutch system, and the overall system to provide feedback (block 320). Otherwise, if theprocess 310 determines that the planetary gear/clutch system is not fully engaged between the motor and the pump atblock 326, then theprocess 310 may loop back or continue by increasing engagement between the motor and the pump via the planetary gear/clutch system to increase the speed of the pump (block 318). Again, theprocess 310 continues to loop throughblocks pumping process 310 operates in a closed loop to gradually increase or decrease the speed of the pump using the planetary gear/clutch system and feedback obtained throughout the pumping system. The illustratedprocess 310 may be applied to a start up procedure, a shut down procedure, a transient hydraulic instability condition, and so forth. By using theprocess 310, the pump can gradually increase or decrease to the desired operating speed with a substantially reduced possibility of water hammer or other damaging hydraulic effects. - While the invention may be susceptible to various modifications and alternative forms, specific embodiments have been shown by way of example in the drawings and have been described in detail herein. However, it should be understood that the invention is not intended to be limited to the particular forms disclosed. Rather, the invention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention as defined by the following appended claims.
Claims (21)
1. A pump system, comprising:
a motor-to-pump transmission, comprising:
a planetary gear assembly; and
a clutch.
2. The pump system of claim 1 , wherein planetary gear assembly comprises a sun gear, a plurality of planet gears disposed about and engaged with the sun gear, and a ring gear disposed about and engaged with the plurality of planet gears.
3. The pump system of claim 2 , wherein the ring gear is rotatable.
4. The pump system of claim 2 , wherein the clutch is engageable to change the ring gear between rotatable and fixed conditions.
5. The pump system of claim 2 , wherein the clutch comprises first ring-shaped clutch plates having external teeth engaged with the ring gear and second ring-shaped clutch plates having internal teeth engaged with a gear coupled to a clutch support.
6. The pump system of claim 1 , wherein the clutch comprises a wet clutch.
7. The pump system of claim 1 , wherein the pump system is configured to be at least partially submerged.
8. The pump system of claim 1 , wherein the pump system is configured to pump fluid at least partially along a generally vertical path.
9. The pump system of claim 1 , comprising a motor, a pump, or a combination thereof coupled to the motor-to-pump transmission.
10. A pump system, comprising:
a transmission, comprising:
a housing having a motor mount and a pump mount;
a central gear disposed in the housing;
a plurality of planet gears disposed in the housing, wherein the plurality of planet gears is disposed about and engaged with the central gear; and
an outer ring gear disposed in the housing, wherein the outer ring gear is disposed about and engaged with the plurality of planet gears.
11. The pump system of claim 10 , comprising a clutch coupled to the transmission.
12. The pump system of claim 11 , wherein the clutch is disposed in the housing.
13. The pump system of claim 12 , wherein the clutch is engageable directly or indirectly with the outer ring gear.
14. The pump system of claim 13 , wherein the clutch comprises a set of clutch plates and a piston configured to compress the set of clutch plates between opposite clutch supports.
15. The pump system of claim 11 , wherein the transmission is configured to substantially decrease speed and to substantially increase torque from a small high speed motor to a pump.
16. The pump system of claim 10 , wherein the pump system is configured to be at least partially submerged, the pump system is configured to pump fluid at least partially along a generally vertical path, or a combination thereof.
17. The pump system of claim 10 , comprising a motor coupled to the transmission.
18. The pump system of claim 10 , comprising a pump coupled to the transmission.
19. The pump system of claim 10 , comprising a motor and a pump coupled to the transmission in a generally vertical pumping arrangement.
20. A method, comprising:
reducing speed and increasing torque from a motor to a pump via a planetary gear assembly.
21. The method of claim 20 , comprising varying engagement between the motor and the pump via a clutch.
Priority Applications (1)
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US11/513,522 US20080056912A1 (en) | 2006-08-31 | 2006-08-31 | Pump system and method using planetary gear assembly |
Applications Claiming Priority (1)
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US11/513,522 US20080056912A1 (en) | 2006-08-31 | 2006-08-31 | Pump system and method using planetary gear assembly |
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US20080056912A1 true US20080056912A1 (en) | 2008-03-06 |
Family
ID=39151800
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US11/513,522 Abandoned US20080056912A1 (en) | 2006-08-31 | 2006-08-31 | Pump system and method using planetary gear assembly |
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US20100018505A1 (en) * | 2008-07-24 | 2010-01-28 | Gm Global Technology Operations, Inc. | Method and apparatus for supporting stop-and-go engine functionality |
US20100098572A1 (en) * | 2008-10-16 | 2010-04-22 | Giuseppe Rago | High speed gear pump |
EP3009679A1 (en) * | 2014-10-14 | 2016-04-20 | Carpegen GmbH | Hose pump and device for analysing a chemical or biological sample |
US10221938B2 (en) * | 2014-05-23 | 2019-03-05 | Qinetiq Limited | Apparatus for managing fluid flow in a vehicle |
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US4086019A (en) * | 1974-01-31 | 1978-04-25 | Compair Industrial Limited | Transmission means for centrifugal compressors |
US20040165995A1 (en) * | 2001-11-30 | 2004-08-26 | Yasushi Suzuki | Hybrid compressor device |
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Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
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US20100018505A1 (en) * | 2008-07-24 | 2010-01-28 | Gm Global Technology Operations, Inc. | Method and apparatus for supporting stop-and-go engine functionality |
US7690344B2 (en) * | 2008-07-24 | 2010-04-06 | Gm Global Technology Operations, Inc. | Method and apparatus for supporting stop-and-go engine functionality |
US20100100301A1 (en) * | 2008-07-24 | 2010-04-22 | Qi Ma | Method and apparatus for supporting stop-and-go engine functionality |
US7784441B2 (en) | 2008-07-24 | 2010-08-31 | Gm Global Technology Operations, Inc. | Method and apparatus for supporting stop-and-go engine functionality |
US20100098572A1 (en) * | 2008-10-16 | 2010-04-22 | Giuseppe Rago | High speed gear pump |
US8292597B2 (en) | 2008-10-16 | 2012-10-23 | Pratt & Whitney Canada Corp. | High-speed gear pump |
US10221938B2 (en) * | 2014-05-23 | 2019-03-05 | Qinetiq Limited | Apparatus for managing fluid flow in a vehicle |
EP3851706A1 (en) * | 2014-05-23 | 2021-07-21 | Qinetiq Limited | Apparatus for managing fluid flow in a vehicle |
EP3009679A1 (en) * | 2014-10-14 | 2016-04-20 | Carpegen GmbH | Hose pump and device for analysing a chemical or biological sample |
WO2016058926A1 (en) * | 2014-10-14 | 2016-04-21 | Carpegen Gmbh | Hose pump and device for analysing a chemical or biological sample |
CN107076136A (en) * | 2014-10-14 | 2017-08-18 | 柯蒂斯有限责任公司 | Peristaltic pump and the device analyzed chemical example or biological sample |
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