CA1156475A - Rotary driven on fluid pumping and heating system - Google Patents

Abstract

ABSTRACT OF THE DISCLOSURE
The system utilizes a heat engine which provides shaft power and heat such as a conventional diesel engine in which part of the shaft power drive a pump for fluid to be heated; for example, a cryogenic liquid. The engine heat is used to heat and/or vaporize the cryogenic liquid in a heat exchanger. The heat available from the engine for transfer to the liquid to be vaporized is proportional to the power level of the engine. The heat required to heat the fluid to a desired temperature is proportional to the flow rate of the cryogenic liquid. By providing a loading on the engine which is proportional to the fluid flow rate, a sufficient amount of heat is provided to effect complete vaporization of the liquid, the amount of heat being directly propor-tional to the flow rate of the liquid. The loading of the engine can be accomplished by a power absorbing hydraulic drive connected to the engine shaft with the hydraulic medium used to drive the cryogenic liquid pump. A rotary hydraulic drive and multi-section rotary driven fluid pump is provided to achieve vibration free, smooth operation in simplified, closed loop hydraulic drive circuit. A dual rotary system is also disclosed.

Description

1 ~5~75

2 This invention relates c~enerally to fluid pump-

3 ing and heating systems and more particu]arly to an improved a system for pumping and heating and/or vaporizing fluids 5 such as cryogenic ~iquids which is particularly adap,ed for 6 employing a rotary driven LN pumping system.

8 This invention is an improvement of that disclosed in our 9 U.S. Patent ~4197712 issued April 15, 1980. As therein 10 disclosed, the invention is concerned with adding heat to 11 a fluid as it is being pumped from a low pressure to a `12high pressure by means of a heat engine, such as a diesel 13engine. The engine uses the combustion of fuel to produce 14shaft power and heat both of which are used to convert the 15condition of the fluid from liquid at ambient pressure to a 16gas at high pressure, deliverable at an adjustable flow 17rate commensurate with the speed of operation of the engine.

19S~stems for pumping and heating a fluid to a desired 20temperature, as for example heating liquid nitrogen from 21_3~oo F. to provide gaseous nitrogen at a desired pres-22sure and temperature, for example 5000 psi and 70 F., are 23well Xnown in the art. ~he ~7aporized nitrogen can be used 24to displace fluid in oil wells, or for purposes of purging ~5tanXs in ships or purging pipelines, or for simply filling nitl~ogen gas storage bottles.

28Heretolore~ the ~nown s~stems usually required burners;
29 direct fired units, boiler systems and the like to effect 30the heating and/or vaporization. Thus, in addition to an 31 /// ' I

I 15~17~

1 internal combustion engine for driving the cryogenic pump, 2 an additional burner for vapori~ation is used.
3 Heat engines are devices which convert combus-

4 tion energy into shaft power and heat. Heat rejected from a heat engine is commonly called "wastel' heat because this 6 heat is used by the engine but is not converted into shaft 7 power. In the present invention this heat is not wasted 8 It is used to heat the fluid being pumped. The present in-g vention is particularly concerned with those circumstances in 10 which the heat required is less than the heat which may be 11 conveniently extracted from the so-called waste heat. Under 12 these conditions, the methods of this invention increase 13 the engine power level so as to increase the amount of heat 14 rejected from the engine so that an adequate amount can be 15 extracted for heating the fluid.
16 More particularly, the present invention includes 17 pumping the fluid to be heated along a flow path. An engine 18 which supplies shaft power and heat such as a diesel engine 19 is provided and part of the shaft power is used to effect the 20 pumping. This shaft power is then further loaded so that the 2~ engine operates at a greater power level than necessary to 22 effect the pumping to thereby provide increased heat from the 23 engine. Finally, a heat exchange is effected between the 24 engine heat and fluid passing along the flow path to thexeby 25 heat the fluid, the amount of heat provided being directly ~6 proportional to the flow rate of the fluid. As a conse-27 quence, separate burners, direct fired units, boiler systems 28 and the like, are not required. Moreover, the heat of the 29 engine which is normally wasted is utilized in the heating 30 process, thereby providing a more efficient system.

1 ~ 56~7~

1 For use in vaporizing liquid nitrogen, the 2 referenced system of U.S. Patent 4,197,712 comprises a 3 LN2~ GN2 flow line including a cryogenic pump, an 4 engine coolant loop, and a hydraulic pump drive loop in-

5 cluding a load. Work is done by the engine shaft to ~rive

6 the cryogenic pump, hydraulic loop and load which is trans-

7 ferred by a hydraulic me~ium heat exchanger to the coolant

8 loop. The heat produced in the engine is transferred to g the coolant loop by the engine itself and combined with 10 that of the first heat exchanger to be transferred to the 11 LN2 ~ GN2 line by a vaporize heat exchanger.
12 More speci~ically, the loading means inc]udes a 13 hydraulic drive connected to a fluid pump such as a cryo-14 genic pump, this hydraulic drive in turn being powered from 15 a hydraulic pump connected to the engine shaft. A back 16 pressure valve is provided in the circulation path of the 1~ hydraulic medium for the hydraulic pump thereby loading the 18 hydraulic pump and engine shaft. The engine includes a 19 coolant medium and a radiator for the coolant medium.
20 The coolant pump is driven by the engine for circulating the 2~ coolant medium through the engine, the heat exchanger, and 22 the radiator. The coolant picks up heat from the engine 23 and from the hydraulic medium and delivers this heat to the 24 fluid being pumped in the heat exchanger. Any excess heat 2~ is then removed from the coolant in the radiator.
~6 The operation of the fluid or cryogenic pump 27 is derived from the engine shaft. The amount of engine 28 heat available is proportional to the engine shaft power.
29 The amount of heat required to heat the fluid being pumped to ///

1 15~7~

la desixed temperature is proportional t~ the flo~ rate of 2 the fluid. By loading the engine so that the engine shaft 3power is proportional to the fluid flow rate, the amount of 4heat a~ailable is proportional to the fluid flow rate and shence can be made approxomately equal to the amount of heat 6 required.
7 Thus because the purpose of this invention is gprimarily to heat a pumped fluid, it will be instructive to gconsider the heat balance of a typical system. All of the energy required for operation of the system is provided by combustion of fuel in a diesel engine. The diesel engine 12drives a hydraulic pump and the hydraulic medium drives a 13crYogenic pump to pump liquid nitrogen. The engine is loaded 14by the hydraulic pump which pumps through a backpressuxe 15valve set at a pressure level higher than the pressure 16required to operate the cryogenic pump driv~. The heat for 17vaporizing the liquid nitrogen is obtained from the work 18done on the nitrogen and hydraulic fluid, from the engine l9heat through the engine coolant, and possibly the engine 20exhaust gas.
2~ The shaft power drives the hydraulic pump which 22transfers a portion of this energy into pump work in the 23nitrogen pump. The balance of the hydraulic pump work 24including pump lnefficiency appears as heat in the hy-25draulic oil and is rejected into coolant in an oil-coolant ~6heat exchanger.
27 Heat from the coolant is transferred to the nitro-28gen in the vaporizer. Any excess is rejected to the air which 29passes over the engine radiator. ~hen no nitrogen is be1ng 30pumped, the radiator rejects all of the coolant heat.

1 1 5 ~
In one system for carryiny on the foregoing, the shaft ou~put can be supplied to a ram cylinder for recipro-catingly driving an ac-tuating member on a cryogenic pump.
~owever, that such a system requires various flow reversing valves together with a plurality of in-terconnection lines for its operation, all of which use subjec-t to considerable surge pressures as the cylinder direction is reversed in eaeh cycle. These surge pressures cause mechanical problems in the form of broken lines, leakage and undue wear due to excessive vibration of the unit and components.
There is therefore a need for improved system for Fluid Heating and Pumping which will overcome the foregoing deficiencies.
The invention is illustrated, by way of example, in the drawings, in which:
Figure 1 is a schematic block diagram of a vapo-rizer system constructed in accordance with the present invention.
Figure 2 is a more detailed schematic block diagram of a vaporizer system for Figure 1, using a closed loop rotary hydraulic drive.
Figure 3 is a detailed schematic hydraulic diagram of a dual rotary driven pumping system construeted in accordanee with Figure 2. Figure 3 oecupies two sheets.

6 4 ~ ~

2 Referring first to the top portion of Fig.l, 3 the vaporizer system includes a vaporizer heat exchanyer 10 4 positioned in the ~low path along which fluid to be vapor-5 ized is pumped as by a fluid pump 11 from a sultabl.e supply 6 ~an~ 12.
7 ~here the fluid to be vaporized constitutes a 8 cryogenic liquid such as nitrogen, the resulting gaseous

9 nitrogen at the outlet of the heat exchanger 10 might be

10 utilized as a fluid displacement medium Eor an oil well

11 indicated schematically at 13. While the principal embodi-~2 ment of this invention will be described with respect to 13 vaporization of a cryogenic liquid such as nitrogen, it 14 should be understood that the basic method and system 1~ are applicable to tXe heating and/or vaporization of other 16 fluiaS
17 Still referring to Fig. 1 there is shown in the 1~ lower center protion a heat engine 14 which may be any 19 suitable type of heat engine such as a gasoline engine or 20 diesel engine which provides shaft power as well as heat.
2~ In Fig. 1, the shaft for engine 14 is schematically indicat--22 ed by the heavy dashed-dot line 15, part of the power from 23 the shaft being utilized to drive the fluid pump 11.
24 Associated with the engine 14 is radiator 16 25 shown to the left in Fig.l through which a coolant medium is circulated as by means of a coolant pump 17 driven by 27 the shaft 15. A loading means for loading the shaft of 28 the engine 14 is indicated by the block 18 and takes two 29 different forms in the two embodiments to be subsequently 30 described. In both of these embodiments, however, the 1:~5~475 1 coolant pump 17 will pass a cooling medium from the engine 2 14 through the heat exchanger 10 in heat exchanging relation-3 ship with the fluid from pump 11 to vaporize this fluid, 4 and thence through a temperatuxe control 19 and the radiator 5 16 back to the heat engine. As will become clearer as the 6 description proceeds, the temperature control 19 controls the 7 radiator in a manner to radiate away excess heat in the cool-8 ant not absorbed in the heat exchanger 10 during the vaporiza-9 tion process.
Also illustrated to the lower right of Fig. 1 is a 11 control panel 20 which incorporates the various pressure

12 and temperature gauges and engine monitoring equipment.

13 It will be noted in Fig. 1 that there is not re-

14 quired any separate burner or boiler for effecting the vapor-

15 ization and as a consequence, the entire system is more

16 portable than would otherwise be the case. In this respect,

17 there is-indicated schematically in Fig. 1 a skid structure

18 21 for supporting the basic components described so that the

19 entire system can be transported to a particular site such

20 as an oil field or even to an offshore drilling rig and 2~ vaporization of the cryogenic liquid nitrogen carried out.

~6 1 15~47~

Referring now to Fig. 2, there are iLlustrated several of the basic components of Fig. 1 together with a first type of loading means enclosed within the dashed-dot lines 18 in accord with an actual embodiment of this invention presently in use. As mentioned, this particular embodiment is uti-lized to vaporize cryogenic liquid nitrogen and as depicted in Fig. 2, the liquid nitrogen (LN2) is pumped from an appropriate supply tank through the cryogenic pump 11 to the vaporizer heat exchanger 10 and thence will emerge as gas-eous nitrogen (GN2).
The loading means of Fig. 2 includes a hydraulic drive32 connected to the cryogenic pump 11 as indicated by the heavy dashed-dot line 23. A hydraulic pump 24 also desig-nated PB in Fig. 2 is connected to the shaft 15 of the diesel engine 14 for circulating an appropriate hydraulic medium to operate the hydraulic motor 22. Thus, the hy-draulic medium passes from a hydraulic medium heat exchanger 27, through pump 24 and back pressure valve 28, also de-signated PVl, in a simple closed loop.
The hydraulic medium heat exchanger 27 is in the flow path of the coolant medium passing from the vaporizer heat exchanger 10 to the temperature control 19 and radiator 16, this hydraulic medium heat exchanger serving to cool the hydraulic fluid.
In Fig. 2, the fluid flow path for the cryogenic liquid is indicated in the upper portion at 30, the circulating path ~, ~ :~ 56475 for the coolant medium at 31 and the hydraulic circulating path at 32. Accumulators or surge tanks in the ni-trogen flow path 30 and accumulators or surge tanks 34 in the hydraulic medium flow path may be provided for smoothing out the flow. Safety pressure relief valves may be provided such as indicated in the flow path 30 at 55, and similarly pressure responsive bypass valves such as indicated at 38 may be provided.
Thus, a closed loop is provided which lncorporates the hydraulic pump 24, the hydraulic drive 22, and hydraulic heat exchanger 27.
A manual bypass valve 36 is provided to allow a small flow of liquid nitrogen around the vaporizer heat exchanger 10 to permit a reduction or "tempering" of the discharge temperature of the GN2 when this is desired.
Finally, there are depicted schematically in Fig. 2 various temperature gauges Tg and pressure gauges Pg in various ones of the circulating paths for monitoring pur-poses. These latter gauges would be located on the control panel 20 described in Fig. 1. It will be understood in an actual embodiment that further valves and gauges as well as surge tanks would be provided at appropriate locations along with priming valves and the like.
As shown more particularly in Figure 3, hydraulic motor 22 and fluid pump 11 may both be of the rotary drive type to thereby lessen or eliminate pressure surges in the lines.
Preferably, the fluid pump is of the multisection type (three sections), each section of which is staggered with ~.~

1 ~ 56~75 1 respect to the others in order to smooth out the load it 2 presents to the hydraulic drive. This reslllts in a substan-3 tially vibration-free system. In addition, the hydraulic 4 drive system operates as a closed loop system to eliminate reservoirs and secondary pumps and to facilitate parallel 6 operations.
7 In Fig. 2, the hydraulic medium pump 24 connected to 8 the diesel engine shaft 15 constitutes a hydrostatic trans-9 mission-variable aisplacement pump to enable ad~ustment of the flow rate of the hydraulic medium for a given ~ack 11 pressure set by the back pressure valve 28 in the flow line 12 3~ It will be appreciated that the higher the back pres-13 sure provided by the valve 28 the greater will be the load 14 applied to the shaft 15 by the pump 24 if the pump rate is to remain constant. Actually, a given back pressure is set 16 by the valve 28 and the variable displacement pump 24 ad-17 justed to provide a flow rate for the cryogenic liquid such 18 that all the liquid will be vaporized by the heat generated 19 in the engine and transferred by the coolant medium. In other words, a proportionality between the flow rate and

21 heat available for vaporizing the liquid is always maintained.

22 The flow rate provided by the cryo~enic pump 11 depends on

23 the rate of operation of the hydraulic fluid through the

24 hydraulic pump 24. Because the valve 28 maintains a constant back pressure on the hydraulic pump independent of the flow 2~ rate of hydraulic fluid, the power required to drive the 27 hydraulic pump is proportional to the hydraulic fluid flow 28 rate. Since the pump 24 is driven by the engine shaft, it 1 1 5647~
1 will be ap~reciated that the ~ngin~ powe~ is ~roportional to 2 the flow rate of the cryogenic liquid through the vaporizer 3 heat exchanger 10. Further, ~he heat developed by the engine 4 is appro~imately proportional to the power of the engine and thus for an increased flow rate there will be provided increased 6 heat in the vaporizer heat exchanger 10 from the coolant 7 medium passing through the diesel engine 14.
8 It will thus be evident from the foregoing that the avail-9 able heat provided by the coolant medium in the vaporizer heat exchanger 10 is approximately equal to the heat required for 11 complete vaporization of the cryogenic liquid at the particu-12 lar flow rate. Essentially, the hydraulic drive and pump 24 13 embodied in the loading means 18 of Fig. 2 absorbs the diesel 14 engine shaft power resulting in the generation of the necessary heat by the engine for vaporization.
16 It will be appreciated that the heat generated by the 17 engine is not exactly proportional to the power ~enerated.
18 At low engine power levels and at very high speeds the heat 19 generated per unit power increased. The engine generates a significant amount of heat even at idle conditions or when 21 no power is being generated. To allow for these variations 22 the system must be designed so that the available heat always 23 equals or exceeds the heat required to vaporize the cryogenic 24 liquid~ As a result, there will occur some regimes of engine operation where there is excess heat which must be dissipated.
26 The radiator 16, as mentioned briefly heretofore, serves 27 to radiate away any excess heat above that necessary to effect 28 the desired vaporization of the cryogenic liquid. Any such 29 ~/
~//

1 excess heat wou~.d be in the ciiculating coolant medillrn pas-2 sing to the radiator by way of the temperature control 19.
3 The temperature control 19 may comprise si.rnply a thermally-4 responsive valve arran~ement to permit passage of the coolant medium directly to the diesel engine in the event no excess ~ heat is present (the coolant medi.um simply bypasses the 7 radiator 16), or pass a p~rtion of the coolant medium through 8 the radiator 16 to radiate away the excess heat. By utilizing 9 a thermostatic control for the valve, the operation is com-pletely automatic and self-regulating.

~i ;

23 .
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26

27

28

29 -13-~ ~ 5~7~

1 Referring now to both Fiyures 2 and 3 the hydraulic 2 drive circuit of the present invention i5 characteri7ed by 3 rotary driven closed loop system. Thus,the shaft power output 4 of the en~ine operates the hydraulic pump and load loop 32 5 including one side of hydraulic medium heat exchanger 27, the 6 other side of ~hich is tied into the engine thermal cooling 7 loop so that the heat generated in the loop 32 is exchanged 8 into loop 31 and thence to the vaporizer heat exchanger 10.
9 The loop 32 is provided with a control mechanism in the form 10 of a charge pump 25 which serves to keep the closed loop 11 charged with oil and to make up for any leaks that exist in 12 the system. Pump 25 is a small pump which draws from an 13 associated reservoir 25-1 at a relatively low flow rate 14 bet~een the two, bathe the principal pump 24 in fresh cool 15 liquid from the reservoir for cooling purposes and to flush 16 out hot oil generated by the inefficiency of the pump. The 17 charge pump also serves to generate a charge pressure to 18 drive a servo valve (not shown) which is manually controlled 19 by the operator to operate a piston integral with pump 24 20 to push on a swash plate which varies the displacement of the 2i pump. Valve Vl serves as a sequencing valve or load valve 22 and serves to keep the pressure constant between it and the 23 pump output, so that it effectually serves as a variable 24 orifice and thus variable load on the pump and engine. By 25 utilizing a rotary driven hydraulic drive the load and ~6 system can be kept relatively free of pulsations thereby 27 eliminating the need for an independent partially open break 28 in the loop 32 as was previously disclosed in our original ~9 1 ~564~
1 U. S. patent 4,197,712.
2 Referring now to Figure 3 there is shown a complete 3 and detailed hydraulic circuit diagram for a dual rotary driven 4 hydraulic system constructed in accordance with the present 5 invention. Thus, two separate hydraulic drives and a cryogenic 6 pump circuits are provided, each of which has been given like 7 numbers to those of Figure 2 with the addition of a -1, for the 8 first circuit and a -2, for the second. It will be understood 9 that a plurality of such circuits could be provided, two being 10 sufficient for the purposes of illustration herein. The circuits 11 are operated in parallel to each other except that means is 12 provided for combining the flow and output of the several 13 cryogenic pumps together before passed through the vaporizer 14 heat exchanger means 10, which may include a plurality of heat 1~ exchangers for convenience of construction. The hydraulic pumping 16circuits are operated in parallel and are driven together. The 17 pumps are turning all the time due to the nature of the system, but they are not pumping hydraulic fluid unless they are actuated 19by the system previously discussed in connection with the output 20Of charge pump 25. Thus, one system can be at zero speed, while 21 the other is operating at full speed independently of each other.
22 It will be noted that each of the hydraulic drive 23circuits is identical and each cryogenic pump includes a multi-24section construction which is arrange to operate in sequence 120 2~out-o~-phase with-each other, so that the three sections shown 26provide a relatively even load for the motor. Each of the pump 27 sections is provided with a vibration dampener UI4, VI5, VI6 28to further decrease pulsations. The input to each of the 29positive displace-1 156~7$

1 ment sequentially driven piston p~lmps PN2 is provide~ additionally 2 with a priming pump circuit inclucling a hydraulic motor Ml which 3 is driven by a pump on one of the engine shafts. The output 4 of the motor drives the centrifugal pump PNl for raising the 5 inlet pressure of liquid nitrogen delivered to the pumps PN2 6 to provide cavitation suppression and to provide a cooliny 7 fluid stream for maintaining the pumps PN2 at liquid nitrogen 8 temperatures even if the system is idling.
9 The following is a parts list and description which 10 identified by the drawing call-out number given in Figure 3.

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Claims (8)

The embodiments of the invention in which an exclu-sive property or privilege is claimed are defined as follows:-

1. A fluid pumping and heating system including a heat exchanger, a fluid pump for passing a fluid to be heated to a desired temperature through said heat exchanger, a heat engine which provides shaft power and heat output, part of said shaft power being used to operate said fluid pump and said heat being used in said heat exchanger, loading means for increasing the pumping load on the engine shaft to thereby provide sufficient heat to heat said fluid in said heat ex-changer to a pre-determined temperature, the amount of heat provided being directly proportional to the flow rate of said fluid provided by said fluid pump, said loading means further including a hydraulic drive and a hydraulic pump connected to the engine shaft for circulating a hydraulic medium to operate said hydraulic drive, said fluid pump being of the type including a rotary actuating member, and said hydraulic drive being of the type comprising a rotary motor having a rotary output shaft member.

2. A fluid pumping and heating system as in Claim 1 in which said hydraulic pump, said loading means, said hydraulic drive, and said hydraulic medium heat exchanger are connected together to form a closed loop hydraulic system.

3. A system as in Claim 1 in which said fluid pump comprises a multiple section pump, each section of which is staggered in operation with respect to the next.

4. A system as in Claim 3 further including a vibra-tion damper connected in series to the input of each section of said pump.

5. A system as in Claim 3 in which said fluid pump is a three-section pump, each section of which is operable 170° out of phase with respect to the preceding section.

6. A system as in Claim 1 in which said fluid pump comprises a plurality of parallel connected fluid pumps together with means for combining their outputs together and delivering the same to said heat exchanger, and in which said hydraulic drive comprises a plurality of hydraulic drives respectively connected to one of said plurality of fluid pumps, said hydraulic motor comprising a plurality of hydraulic motors, each of which is connected to a respective on of said hydraulic drives, whereby each of said hydraulic pump, hydraulic drive and fluid pump forms a linkage capable of operations independently of the others.

7. A system as in Claim 6 in which said heat exchanger comprises a plurality of parallel connected units connected to the output of said fluid pumps through a common line.

8. A system as in Claim 1 further including a priming pump connected in series at the inlet of said fluid pump, said priming pump serving to provide a continuous cooling of the fluid pump and to provide an inlet pressure to prevent cavitation.