Patent Application
20160281697
The present disclosure relates generally to a fuel system and, more particularly, to a fuel system having serially arranged in-tank pumps.
Gaseous fuel powered engines are common in many applications. For example, the engine of a locomotive can be powered by natural gas (or another gaseous fuel) alone or in combination with another liquid or gaseous fuel (e.g., diesel fuel). Natural gas may be more abundant and, therefore, less expensive than other liquid fuels. In addition, natural gas may burn cleaner in some applications, and produce less greenhouse gas.
Natural gas, when used in a mobile application, may be stored in a liquid state onboard the associated machine. This may require the natural gas to be stored at cold temperatures, typically about −100 to −162° C. The liquefied natural gas is then drawn from the tank by gravity and/or by a boost pump, and directed to a high-pressure pump. The high-pressure pump further increases a pressure of the fuel and directs the fuel to the machine's engine. In some applications, the liquid fuel may be gasified prior to injection into the engine and/or used in conjunction with diesel fuel (or another fuel) before combustion.
An exemplary fuel system used to pump cryogenic fluids is disclosed in U.S. Patent Application Publication No. 2013/0283824 (the '824 publication) of Madison that published on Oct. 31, 2013. In particular, the '824 publication discloses a configuration of cryogenic pumps used to pump LNG. A single liquid vessel is provided, and two electrically driven centrifugal-type pumps are disposed in series with each other, inside of vessel. Each pump is provided with its own shaft, and the two pumps are operated at different speeds. A lower of the two pumps in the vessel draws in fluid directly from the vessel, and discharges the fluid to an intake of an upper of the two pumps. A high-pressure liquid inlet provides fluid to the vessel, and a two-phase outlet is connected to the upper pump. The pumps hang from a top support plate surrounding the vessel.
While the pump configuration of the '824 publication may be acceptable in some applications, it could have limited applicability. In particular, centrifugal type pumps may not be capable of generating pressures high enough for some applications. In addition, it may be difficult in some applications to supply each of the pumps with electrical power and to separately control the speeds of the pumps. Further, drawing fluid directly from the tank may allow for contamination and/or damage of the pumps.
The disclosed fuel system is directed to overcoming one or more of the problems set forth above.
In one aspect, the present disclosure is directed to a pump system. The pump system may include a first pump having a first end, a second end, a reservoir located at the second end, and at least one pump mechanism configured to receive fluid from the reservoir. The pump system may also include a second pump mounted to the first pump at the second end and having at least one pump mechanism configured to discharge fluid into the reservoir of the first pump. The pump system may further include a mechanical input operatively connected to the at least one pump mechanism of each of the first and second pumps.
In another aspect, the present disclosure is directed to another pump system. This pump system may include a fluid tank; and a piston pump having a first end mounted to the fluid tank, and a second end hanging inside the fluid tank. The pump system may further include a centrifugal pump mounted to the second end of the piston pump and configured to transfer fluid from the fluid tank to the piston pump.
In yet another aspect, the present disclosure is directed to fuel system. The fuel system may include a fuel tank, and a piston pump having a first end mounted to the fuel tank, a second end hanging inside the fuel tank, and a plunger configured to pressurize liquid fuel received from a reservoir located at the second end. The fuel system may also include a centrifugal pump mounted to the second end of the piston pump and configured to transfer liquid fuel from the fuel tank into the reservoir of the piston pump, and a filter disposed at an inlet of the centrifugal pump inside the fuel tank. The fuel system may further include a shaft extending into the fuel tank and configured to operatively drive the piston and centrifugal pumps, and an external electric motor operatively connected to the shaft. The fuel system may additionally include a vaporizer configured to receive pressurized liquid fuel from the piston pump and to vaporize the pressurized liquid fuel, an accumulator configured to receive vaporized fuel from the vaporizer, and a regulator located downstream of the accumulator.
Tank 14 may be a cryogenic tank configured to hold the natural gas in its liquefied state. In the exemplary embodiment, tank 14 has an inner wall 26 separated from an outer wall 28 by an air gap. In some embodiments, an insulating layer 30 may be disposed in the air gap (e.g. on inner wall 26). The air gap, together with the insulating layer 30, may function to maintain a temperature of the natural gas below its boiling temperature of about −100-162° C.
Tank 14 may be generally cylindrical, having a top 32 and a bottom 34. Top 32 may have an opening 36 formed therein that passes through both of inner and outer walls 26, 28. Opening 36 may be generally aligned with a central axis 38 of symmetry. Bottom 34 may be closed.
Pump system 16 may be at least partially submerged inside of tank 14, for example inside a centralized socket formed in tank 14. In particular, pump system 16 may include a high-pressure pump 40 that is connected at a base end to tank 14 at top 32, and a boost pump 42 that hangs from a distal end of high-pressure pump 40. By being connected to tank 40 at only one end, high-pressure and boost pumps 40, 42 may be allowed to expand and contract due to normal thermal loading without inducing stresses in tank 14 that could damage tank 14. An electric motor 44 (or other power source) may be located outside of tank 14, and connected to drive both of high-pressure and boost pumps 40, 42 via a belt 46 and a mechanical input 48. In the disclosed embodiment, mechanical input 48 is a shaft. In other exemplary embodiments, however, mechanical input 48 could be a gear train, if desired. In either of these arrangements, an output rotation of motor 44 may cause belt 46 to induce a corresponding input rotation of mechanical input 48. This corresponding input rotation may be simultaneously transmitted to both of high-pressure and boost pumps 40 with equal speed.
High-pressure and boost pumps 40, 42 may be serially arranged. That is, when driven by mechanical input 48, boost pump 42 may draw liquid fuel through a filter 50, and generate a low-pressure feed directed into high-pressure pump 40. High-pressure pump 40 may then further increase the pressure of the fuel, and direct high-pressure fuel to vaporizer 18 via passage 24.
An exemplary pump system 16 is shown in
High-pressure pump 40 may be an axial piston type of pump. In particular, a pump shaft 62 may be rotatably supported within a housing 64, and connected at a top end to mechanical input 48 (e.g., via a splined interface) and at a bottom end to a load plate 66. Load plate 66 may be oriented at an oblique angle relative to axis 38, such that the input rotation of shaft 62 may be converted into a corresponding undulating motion of load plate 66. A plurality of tappets 68 may slide along a lower face of load plate 66, and a push rod 70 may be associated with each tappet 68. In this way, the undulating motion of load plate 66 may be transferred through tappets 68 to push rods 70 and to plungers 88 and used to pressurize the fluid passing through high-pressure pump 40. A resilient member, for example a coil spring 72, may be associated with each push rod 70 and configured to bias the associated tappet 68 into engagement with load plate 66. Each push rod 70 may be a single-piece component or, alternatively, be comprised of multiple pieces, as desired. Many different shaft/load plate configurations may be possible, and the oblique angle of shaft 62 may be fixed or variable, as desired. In the disclosed embodiment, the oblique angle of shaft 62 is fixed, and a variable output of high-pressure pump 40 is obtained via speed adjustment of motor 44 (referring to
Manifold section 56 of high-pressure pump 40 may include a manifold 74 that performs several different functions. In particular, manifold 74 may function as a guide for push rods 70, as a mounting pad for a plurality of pump mechanisms 76, and as a distributer/collector of fluids for pump mechanisms 76. Manifold 74 may connect to warm end 52, and have formed therein a common high-pressure outlet (“outlet”) 78 in fluid communication with each of pump mechanism 76.
Reservoir section 58 may include a close-ended jacket 80 connected to manifold section 56 (e.g., to a side of manifold 74 opposite warm end 52) by way of a seal and/or an insulating plate (not shown) to form an internal reservoir 82. Reservoir 82 may be in open fluid communication with boost pump 42 via a low-pressure inlet (“inlet”) 84. In some embodiments, a check valve (not shown) may be installed at inlet 82 to ensure unidirectional flow into reservoir 82, if desired.
Any number of pump mechanisms 76 may be connected to manifold 74 and extend into reservoir 82. As shown in
One or more valve elements (not shown) that facilitate fluid pumping during the motion of plungers 88 between BDC and TDC positions may be housed within the closed end (e.g., within a head portion) of barrel 86. The valve element(s) may include, for example, one or more check valves that allow fuel from reservoir 82 to enter barrel 86 during the retracting motion of push rods 70, and that direct high-pressure fluid from barrel 86 to passage 60 during the extending motion of push rods 70. The high-pressure discharge from all pump mechanisms 76 may join each other inside manifold 74 for discharge from high-pressure pump 40 via high-pressure outlet 78 and passage 60.
Boost pump 42 may embody a centrifugal type pump hanging from the distal end of high-pressure pump 40. In particular, boost pump 42 may have a closed end mounted to the distal end of high-pressure pump 40, and an open end located opposite the closed end and nearest a bottom of tank 14. The open end may be at least partially submerged within tank 14. A shaft 89 may be connected to shaft 62 of high-pressure pump 40 (e.g., via a splined interface), and also connected with one or more impellers 90 located inside a volute housing 92 of boost pump 42. In this configuration, the input rotation of mechanical input 48 may be transmitted through shaft 62 of high-pressure pump 40 and shaft 89 of boost pump 42 to impeller(s) 90, causing impeller(s) 90 to rotate. As impeller(s) 90 rotates, fuel from inside tank 14 may be drawn through filter 50 into a suction nozzle 94 of volute housing 92 at the open end of boost pump 42. Impeller(s) 90 may increase a pressure of the fuel and direct the pressurized fuel through inlet 84 into reservoir 82. The pressure achieved by boost pump 42 may be sufficient to push plungers 88 back to their TDC positions as push rods 70 are retracted.
Filter 50 may be a generally hollow and porous sleeve that is placed around boost pump 42. In some embodiments, filter 50 may also extend a distance over cold end 54 so as to increase a flow area through filter 50. A top end of filter 50 may annularly seal against an outer surface of housing 64 of high-pressure pump 40, and a lower end of filter 50 may seal against the bottom surface of tank 14, such that unfiltered fuel may not flow around ends of filter 50. In the disclosed embodiment, filter 50 is fabricated from a stainless steel mesh having openings with a diameter of about 3-4 microns, although other types of filters (e.g., edge filters ceramic filters, sintered metal filters, etc.) could be utilized.
Vaporizer 18 (referring back to
Accumulator 20 may embody a high-pressure vessel configured to store pressurized natural gas for future use by engine 12. As a pressure of the natural gas from vaporizer 18 exceeds a pressure of accumulator 20, the natural gas may flow into accumulator 20. Because the natural gas therein is compressible, it may act like a spring and compress as more natural gas flows in. When the pressure of the natural gas at an outlet of accumulator 20 drops below the pressure inside of accumulator 20, the compressed natural gas may expand and exit accumulator 20. It is contemplated that accumulator 20 may alternatively embody a membrane/spring-biased or bladder type of accumulator, if desired.
Vent 22a and regulator 22b, while used for different purposes, may function in a similar way. Specifically, vent 22a may be configured to selectively allow gaseous fuel to discharge from accumulator 20 to the atmosphere in a controlled manner (i.e., at a control pressure and temperature) that does not compromise the integrity of vent 22a. Regulator 22b may similarly allow gaseous fuel to discharge from accumulator 20 in a controlled manner. In contrast to vent 22a, however, regulator 22b may direct the discharging gaseous fuel to engine 12 via one or more supply lines 96. It is contemplated that vent 22a and regulator 22b may control the gaseous fuel to discharge at the same rates and pressures or at different rates and pressures, as desired. It is contemplated that regulator 22b may control the gaseous fuel to discharge at any desired rate and/or pressure (e.g., at a variable rate and/or pressure) demanded by engine 12.
The disclosed fuel system finds potential application in any mobile (e.g., locomotive) or stationary (e.g., power generation) application having an internal combustion engine. The disclosed fuel system finds particular applicability in cryogenic applications, for example applications having engines that burn LNG fuel. The disclosed fuel system may provide a high-pressure supply of gaseous fuel in a compact, simple, and robust configuration. Operation of pump system 16 will now be explained.
Referring to
At this same time, the rotation of shaft 62 may cause load plate 66 to undulate in an axial direction. This undulation may result in translational movement of tappets 68 and corresponding movements of push rods 70. As push rods 70 retract from barrels 86, the pressure of the liquid fuel in reservoir 82 may cause liquid fuel to enter barrels 86 and push plungers 88 upward. As push rods 70 extend back into barrels 86, push rods 70 may force plungers 88 downward. The downward movement of plungers 88 may push the liquid fuel from barrels 86 at an elevated pressure. The high-pressure fuel may flow through high-pressure outlet 78 into passage 60, and discharge from pump system 16 into passage 24.
The high-pressure liquid fuel may then pass through vaporizer 18, where the fuel is vaporized, before being collected in accumulator 20. The collected gaseous fuel may then be regulated into engine 12.
It should be noted that, although high-pressure and boost pumps 40, 42 may be driven at the same speed via mechanical input 48, that speed may be a function of engine demand for high-pressure fuel from only high-pressure pump 40. In other words, the speed of mechanical input 48 may be adjusted to accommodate a demand for fuel from high-pressure pump 40, and boost pump 42 may be required to maintain a minimum pressure inside reservoir 82 regardless of the speed. Accordingly, boost pump 42 may be sized (e.g., the size and/or number of impellers 90 selected, the size and shape of the volute designed, etc.) to ensure that reservoir 82 is always pressurized throughout a range of input speeds (e.g., even at a lowest speed expected). In some instances, boost pump 42 may supply more low-pressure feed than is required. In these instances, reservoir 82 may need to be selectively relieved of pressure or otherwise bypassed.
Because the disclosed fuel system may utilize two different types of pumps, benefits associated with each type of pump can be realized. For example, the simplicity and efficiency of a centrifugal type of boost pump may be coupled with the higher-pressures attainable from a piston type of pump. This combination of benefits may increase the applicability of fuel system 10. In addition, because none of the pumps of fuel system 10 may directly require electrical power to be routed to them, the mounting of the pumps inside tank 14 may be simple and robust. And because the pumps may not need to be separately speed-controlled, fuel system 10 may be even further simplified. In addition, because the liquid fuel passing through both pumps of fuel system 10 may first be filtered by a common filter, longevity of the pumps may be ensured while keeping a cost of fuel system 10 low.
It will be apparent to those skilled in the art that various modifications and variations can be made to the fuel and pump systems of the present disclosure. Other embodiments of the fuel and pump systems will be apparent to those skilled in the art from consideration of the specification and practice of the systems disclosed herein. It is intended that the specification and examples be considered as exemplary only, with a true scope being indicated by the following claims and their equivalents.
