Very low NPSH cryogenic pump and mobile LNG station

• US 6,006,525 A
• Filed: 06/20/1998
• Issued: 12/28/1999
• Est. Priority Date: 06/20/1997
• Status: Expired due to Fees

• Current Assignee: Dorothy Scott Tyree Alves
• Original Assignee: Lewis Tyree Jr
• Inventors: Tyree, Lewis Jr.
• Primary Examiner(s): DOERRLER, WILLIAM CHARLES
• Application Number:
  US09/100,420
• Time in Patent Office: 556 Days
• Field of Search: 62/50.1, 62/50.6, 62/50.7, 62/55.5, 62/50.3, 62/53.2, 62/239, 62/331, 62/323.1, 62/323.2, 417/901, 417/546
• US Class Current: 62/50.6
• CPC Class Codes: F02M 21/0215 Mixtures of gaseous fuels; Natural gas; Biogas; Mine gas; Landfill gas
• CPC Class Codes: F02M 21/0221 Fuel storage reservoirs, e.g. cryogenic tanks
• CPC Class Codes: F02M 21/0242 Shut-off valves; Check valves; Safety valves; Pressure relief valves
• CPC Class Codes: F02M 21/0245 High pressure fuel supply systems; Rails; Pumps; Arrangement of valves
• CPC Class Codes: F02M 21/0287 characterised by the transition from liquid to gaseous phase F02M21/06 takes precedence; Injection in liquid phase; Cooling and low temperature storage
• CPC Class Codes: F02M 21/029 Arrangement on engines or vehicle bodies; Conversion to gaseous fuel supply systems
• CPC Class Codes: F04B 15/08 the liquids having low boiling points
• CPC Class Codes: F04B 3/003 with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other
• CPC Class Codes: F17C 2205/0335 Check-valves or non-return valves
• CPC Class Codes: F17C 2221/033 Methane, e.g. natural gas, CNG, LNG, GNL, GNC, PLNG
• CPC Class Codes: F17C 2223/0161 cryogenic, e.g. LNG, GNL, PLNG
• CPC Class Codes: F17C 2223/033 Small pressure, e.g. for liquefied gas
• CPC Class Codes: F17C 2227/0142 with specified pump type, e.g. piston or impulsive type
• CPC Class Codes: F17C 2227/0178 in the vessel
• CPC Class Codes: F17C 2227/0313 by forced circulation, e.g. using a fan
• CPC Class Codes: F17C 2227/0393 using a vaporiser
• CPC Class Codes: F17C 2260/035 of fluid
• CPC Class Codes: F17C 2265/066 for feeding engines for propulsion
• CPC Class Codes: F17C 2270/0171 Trucks
• CPC Class Codes: F17C 2270/05 for industrial use
• CPC Class Codes: F17C 9/02 : with change of state, e.g. vaporisation
• CPC Class Codes: Y02T 10/30 : Use of alternative fuels, e.g. biofuels

Abstract

A reciprocating cryogenic pump, suitable for medium and high pressures having very low net positive suction head (NPSH) requirements. The pump comprises a cylinder having both liquid inlets and vapor outlets, and two interacting pistons, each piston reciprocably movable within the cylinder, and each piston having flow conduits there through generally co-axial with the piston and with the cylinder. The conduit of one piston preferentially connects to the liquid inlets and the conduit of the other piston preferentially connects to the vapor outlets, which are at a higher elevation than the liquid inlets. Both conduits are selectively and mechanically opened to the pumping chamber by the reciprocating motion, and the pump is oriented to allow liquid flowing into the pumping chamber by the natural tendency of liquid to flow downwards and residual vapor to leave the pumping chamber by the natural tendency of vapor to flow upwards, an act that in encouraged by the conduit connecting to the vapor outlets being opened before the conduit connecting to the liquid inlets. One use of this pump is for any on-board, mobile (truck, rail or ship), LNG fuel systems for Diesel engines.

Claims

1. In a station for pumping a low NPSH cryogenic liquid to about medium or high pressures, the station comprising:

insulated storage tank means for holding said cryogenic liquid to be pumped and, above said liquid, vapor holding means for the respective vapor phase of said liquid in the ullage volume of said tank means,

a reciprocating pump mounted to said tank in an inclined or vertical position having,

cylinder means,

piston means reciprocally movable within said cylinder means,

liquid outlet valve means mounted in a closure attached to the discharge end of said cylinder means,

combination valve means for liquid inlet and vapor outlet into and out of said cylinder,

piston rod means reciprocally movable generally along the axis of said cylinder means in a direction toward said outlet valve means and in a reciprocal direction causing a compression stroke and then an intake stroke by said piston means to which said rod means is linked, said rod means and said piston means loosely connected so that they form said combination valve means,

said cylinder means, said outlet valve means and said closure, said combination valve means and the compression face of said reciprocally moving piston means defining a pumping chamber,

said cylinder means, said rod means, said combination valve means, and the intake face of said reciprocally moving piston defining part of an annular intake chamber,

conduit or conduits having one end in communication with said liquid in said storage tank means and the other end in communication with said intake chamber or extensions thereof, said conduit or conduits located generally above that portion of said intake chamber that said piston traverses during said intake stroke,

drive means attached to the upper end of said rod means for providing a reciprocating motion causing said intake and said compression strokes by said piston means,

pressure seal means located between said cylinder means and said piston means so as to reduce leakage between said compression chamber and said intake chamber during said compression stroke,

said combination valve means operatively associated with said rod means and said piston means in a lost motion type arrangement, whereby said combination valve means is mechanically caused to open during said intake stroke and to close during said compression stroke,

said combination valve means and said intake chamber located above said compression chamber so that when said combination valve means is open, either said liquid can flow downwardly from said intake chamber into said compression chamber, or said vapor can flow upwards from said compression chamber into said intake chamber, all as influenced by gravity or the changes in relative size of said compression and intake chambers and

said outlet valve means being a check valve type responsive to the flow therethrough of said liquid caused by said compression stroke or by the lack of flow caused by said intake stroke;

the improvement comprising;

said conduit or conduits consisting of first conduit or conduits and second conduit or conduits, the ends of said first conduit or conduits in communication with said storage tank means at a higher elevation than the ends of said second conduit or conduits,

whereby during said intake or compression strokes, said vapor formed in said pump collects in said intake chamber and returns to said ullage volume of said tank means by said first conduit or conduits and said liquid tends to flow into said intake chamber by said second conduit or conduits, thereby the flow of said vapor leaving tending to not impede the flow of said liquid entering, said vapor resulting from said liquid vaporizing due to contact with portions of said pumping chamber that had been warmed by friction of said seals means, or caused by said liquid that had been warmed by the heat of compression but not discharged from said pumping chamber and upon being depressurized during said intake stroke, or caused by heat incursion, or caused by any other reason, thereby reducing the volumetric efficiency of said pump,

and whereby any of said vapor, produced during said compression stroke by leakage of said seal means of said liquid thereby passing from said compression chamber to said intake chamber, then returns to said tank means by said first conduit or conduits, thereby not disturbing said liquid about to enter said intake chamber via said second conduit or conduits, said leakage thereby not reducing the volumetric efficiency of said pump.

2. A station according to claim 1, wherein said piston means of said pump forms part of a conduit connecting said intake chamber, said combination valve means and said compression chamber, the portion of said piston means adjacent said intake chamber being shaped so that it dynamically induces flow of said liquid therethrough and into said compression chamber during said intake stroke,

whereby the filling of said compression chamber with said liquid is enhanced by the movement of said piston means through said liquid in said intake chamber during said intake stroke.

3. A station according to claim 1, wherein said seal means of said pump contains low frictional heat generation type pressure seal means,

whereby heat generation is minimized and thereby heat tending to vaporize said liquid entering said pumping chamber is also minimized.

4. A station according to claim 3, wherein said low heat type seal means include labyrinth type seal means,

whereby the sealing effect of said seal means is from a close or a series of close fits rather than pressure induced contact of said seal means with the opposite surface.

5. A station according to claim 4, wherein said labyrinth type seal means and their supports are constructed from materials that maintain a close fit between said piston means and said cylinder means by differential contraction of the materials of construction of said seal means and said cylinder means when operating at cryogenic temperatures,

whereby the close fit and reduced seal leakage is enhanced by the low operating temperature of said pump.

6. A station according to claim 1, wherein a vaporizer for warming said pumped cryogenic liquid is provided,

whereby said pumped cryogenic liquid can be provided in a gaseous state at about medium or high pressures.

7. A station according to claim 6, wherein said station is located on a vehicle utilizing said pumped cryogenic liquid in said gaseous state as fuel for an engine providing power for a use on said vehicle,

whereby said vehicle utilizes said cryogenic liquid as pressurized gaseous fuel for power generation.

8. A station according to claim 7, wherein said vehicle utilizes refrigeration as well as power and wherein said vaporizer includes heat transfer means between said vaporizer and the refrigeration means of said vehicle for utilizing at least some of the refrigeration potential of said cryogenic liquid by said refrigeration means of said vehicle,

whereby the refrigeration potential of said cryogenic liquid is employed in providing refrigeration to said vehicle.

9. A station according to claim 8, wherein said transfer means includes a phase change material to accept and store said refrigeration potential for subsequent use by said vehicle,

whereby the use of said cryogenic liquid in said gaseous state for both power and for refrigeration can be decoupled timewise.

10. A station according to claim 9, wherein said phase change material is liquid-solid-liquid carbon dioxide,

whereby the advantages of non-toxic carbon dioxide can be utilized as said phase change material.

11. A station according to claim 1 wherein said tank means includes sump means in its lower portion to receive the cold end of said pump,

whereby said tank may be more fully emptied of said cryogenic liquid by said pump.

12. A station according to claim 1, wherein said pumping chamber has a compression ratio of at least 20 to 1, thereby discharging most of said liquid from said pumping chamber at the end of said compression strokes,

whereby reducing the amount of said vapor produced by residual amounts of said liquid flashing upon depressurized by the opening of said combination valve means.

13. An inclined or vertical reciprocating pump for pumping low NPSH cryogenic liquids to about medium or high pressures, the pump comprising:

cylinder means,

piston means reciprocally movable within said cylinder means,

liquid outlet valve means mounted in a closure attached to the discharge end of said cylinder means,

combination valve means for liquid inlet and vapor outlet into and out of said cylinder means,

piston rod means reciprocally movable generally along the axis of said cylinder means in a direction toward said outlet valve means and in a reciprocal direction causing a compression stroke and then an intake stroke by said piston means to which said rod means is linked, said rod means and said piston means loosely connected so that they form said combination valve means,

said cylinder means, said outlet valve means and said closure, said combination valve means and said the compression face of said reciprocally moving piston means defining a pumping chamber,

said cylinder means, said rod means, said combination valve means, and the intake face of said reciprocally moving piston defining part of an annular intake chamber in which said combination valve means is in the lower portion,

conduit or conduits having one end in communication with said intake chamber or extensions thereof and the other end in communication with said compression chamber, said conduit or conduits located generally above said compression chamber and are open or closed as determined by the action of said combination valve means,

drive means attached to the upper end of said rod means for providing a reciprocating motion causing said intake stroke and said compression stroke by said piston means,

pressure seal means located between said cylinder means and said piston means so as to reduce leakage between said compression chamber and said intake chamber during said compression stroke,

said combination valve means operatively associated with said rod means and said piston means in a lost motion type arrangement, whereby said combination valve means is mechanically caused to open during said intake stroke and to close during said compression stroke,

said combination valve means and said intake chamber located above said compression chamber so that when said combination valve means is open, either said liquid can flow downwardly from said intake chamber into said compression chamber or said vapor can flow upwardly from said compression chamber into said intake chamber as influenced by gravity, or the enlargement of said compression chamber and the contraction of said intake chamber or other reasons and,

said outlet valve means being a check valve type responsive to the flow therethrough of said liquid caused by said compression stroke or by the lack of flow caused by said intake stroke,

the improvement comprising;

(a) said piston means consisting of a first piston means and a second piston means,

(b) said movable combination valve means consisting of a first combination valve means and a second combination valve means,

(c) said first combination valve means operatively associated with said piston rod means and said first piston means, in a lost motion type arrangement, whereby said first combination valve means is mechanically caused to open during said intake stroke and to close during said compression stroke,

(d) said second combination valve means operatively associated with said first piston means and said second piston means, in a lost motion type arrangement, whereby said second combination valve means are mechanically caused to open during said intake stroke and to close during said compression stroke and

(e) said conduit or conduits consisting of a first conduit and a second conduit;

whereby once both said combination valve means are open, said liquid can flow into said compression chamber without said flow being impeded by the flow of vapor caused by the displacement of said vapor by said entering liquid, as well as vapor created from other reasons, both said first and said second combination valve means alternately opening and closing said first conduit and said second conduit to flow, said first inlet valve means closing said first conduit to flow when said rod means moves in said compression stroke in a direction towards and contacts said first piston means, said second combination valve means closing said third conduit to flow as said rod means and said first piston means continues said compression stroke, causing said first piston means to contact said second piston means, said first and second piston means each having said conduit therethrough generally co-axial with said cylinder.

14. A pump according to claim 13, wherein said first combination valve means opens before said second combination valve means opens, as caused by the motion of said piston rod means as it begins said intake stroke,

whereby providing a separate first conduit between said pumping chamber and said intake chamber thereby providing flow path when said first combination valve is open so that said vapor may begin to leave said pumping chamber by a separate conduit before said liquid enters said pumping chamber, and providing a separate second conduit between said pumping chamber and said intake chamber providing a flow path so that said liquid may flow into said pumping chamber essentially unimpeded by said vapor leaving said pumping chamber.

15. A pump according to claim 13, wherein during said intake stroke, the end of said first conduit that is in communication with said intake chamber is at a higher elevation than that of said second conduit that is in communication with said intake chamber,

whereby any of said vapor returning to said intake chamber from said compression chamber tends to enter said intake chamber at a higher elevation than said liquid leaving said intake chamber thereby said leaving vapor tending to not impede the flow of said entering liquid.

16. A pump according to claim 13, wherein said second piston means forms part of a conduit connecting said intake chamber, said combination valve means and said compression chamber, the portion of said second piston means adjacent said intake chamber being shaped so that it induces flow of said liquid therethrough and into said compression chamber during said intake stroke,

whereby the filling of said compression chamber with said liquid is enhanced by the movement of said second piston means during said intake stroke.

17. A pump according to claim 13, wherein said intake chamber and said pump include connection means to a source of cryogenic liquid to be pumped including a third conduit or conduits and also connected to the vapor phase of said liquid source by a fourth conduit or conduits, said third conduit or conduits connected to said pump at a lower elevation than said fourth conduit or conduits,

whereby during said intake stroke the effects of gravity tends to cause said vapor to rise and to leave said intake chamber and said pump and to return to the vapor phase of said source of said source by said third conduit or conduits and tends to cause said liquid to flow into said pump and intake chamber by said fourth conduit or conduits, thereby the flow of said leaving vapor not impeding the flow of said entering liquid, said vapor being caused by liquid vaporizing due to contact with any portion of said pumping chamber that had been warmed by frictional action of said seal means or caused by said liquid that had been warmed by the heat of compression but had not been discharged from said pumping chamber during said compression stroke thereby becoming partially vapor upon being depressurized during said intake stroke or leakage past said seals or caused by heat incursion or caused by any other reason, thereby reducing the volumetric efficiency or causing vapor locking of said pump.

18. A pump according to claim 13, wherein said seal means contains low frictional heat generation type pressure seal means, whereby residual heat does not tend to vaporize said liquid entering said pumping chamber.

19. A pump according to claim 18, wherein said low frictional heat type seal means include labyrinth type seal means,

whereby sealing effect is produced by a series of close fits rather than rubbing contact.

20. A pump according to claim 19, wherein said labyrinth type seals and their supports are constructed from materials that form a close fit between the piston and cylinder means upon being cooled to cryogenic temperatures by contracting, whereby the close fit is enhanced by the low operating temperature of the pump.

21. A pump according to claim 13, wherein said pumping chamber has a compression ratio of at least 20 to 1, whereby most of the compressed liquid is discharged from the pumping chamber at the end of each compression stroke, thereby reducing the amount of vapor produced by this residual liquid flashing upon being depressurized by opening of said combination valve.

22. The method of causing a reciprocating pump to fill its pumping chamber with a cryogenic liquid from a source of said liquid under very low NPSH conditions comprising the steps of:

(a) mounting said pump in a vertical or inclined position,

(b) mechanically opening a first and a second intake valve,

(c) providing an upwardly inclined path or conduit through said opened first intake valve preferentially arranged for cryogenic vapor to exit said pumping chamber and said pump and return to said source,

(d) providing a downwardly inclined path or conduit preferentially arranged for said liquid to leave said source and enter said pump at a lower elevation than said upwardly inclined path and to enter said pumping chamber through said mechanically opened second intake valve,

whereby said pump both empties said pumping chamber of said vapor and fills said pumping chamber with said liquid to be pumped by utilizing the effects of gravity.

23. The method in accordance with claim 22 comprising the additional step of:

(a) placing said pump in an insulated storage tank in a manner so that by effects of gravity, any of said cryogenic liquid in said tank flows into said pump and pumping chamber and any of said cryogenic vapor from said pumping chamber and said pump flows into said tank,

whereby said pump and said tank are one unit and are ready to operate at any time that said liquid is in said tank.

24. The method in accordance with claim 23 comprising the additional step of:

(a) mounting said pump wherein said pumping chamber extends into a sump connected to said tank,

whereby said tank may be more nearly emptied of said liquid by said pump.

25. The method of utilizing for a vehicle a first liquid, a cryogenic fuel used both as as a power source for an engine and as a source of refrigeration, and a second liquid, an expendable cryogen used as a source of refrigeration, comprising the steps of:

(a) mounting on said vehicle a first tank for storing said first liquid and a second tank for storing said second liquid, said vehicle containing both said engine capable of utilizing the vapor phase of said first liquid as said fuel and a cooling system using said second liquid as an expendable cryogen as refrigeration source for cooling a portion of said vehicle,

(b) providing a system to pressurize said first liquid,

(c) connecting the outlet of said first tank and said pressurizing system to a vaporizing system, containing a phase change material, for warming said first liquid and cooling said phase change material,

(d) operating said engine and supplying the now pressurized, warmed and vaporized first liquid as said fuel to said engine,

(e) connecting said phase change material to said vehicle'"'"'s said cooling system,

(f) connecting said second tank to said cooling system,

(g) operating said cooling system so as to provide cooling to said vehicle, utilizing both the cooling available from said second liquid and the cooling available from said phase change material,

whereby the pressurized vapor phase of said first liquid is supplied to said vehicle'"'"'s engine, and cooling resulting from said first liquid'"'"'s warming and vaporization is subsequently utilized for cooling of said vehicle,

and whereby the cooling resulting from said first liquid'"'"'s vaporization and warming is decoupled timewise from that cooling'"'"'s use in cooling of said vehicle,

and whereby the amount of said second liquid required for cooling of said vehicle is reduced by the amount of cooling obtained from said first liquid'"'"'s vaporization and warming.

26. The method of claim 25 comprising the additional step of:

(a) providing carbon dioxide as said phase change material,

whereby a solid-vapor phase change material at the useful temperature of near minus 70°

F. may be employed.

27. The method of claim 25 comprising the additional steps of;

(a) providing liquefied natural gas (LNG) as said first liquid,

(b) providing liquefied carbon dioxide or liquefied nitrogen as said second liquid,

whereby LNG may be utilized as both a fuel and source of refrigeration for said vehicle,

and whereby carbon dioxide or nitrogen may be used as a source of expendable refrigeration for said vehicle.