CA2705253A1 - A method and apparatus for cooling a process stream - Google Patents
A method and apparatus for cooling a process stream Download PDFInfo
- Publication number
- CA2705253A1 CA2705253A1 CA2705253A CA2705253A CA2705253A1 CA 2705253 A1 CA2705253 A1 CA 2705253A1 CA 2705253 A CA2705253 A CA 2705253A CA 2705253 A CA2705253 A CA 2705253A CA 2705253 A1 CA2705253 A1 CA 2705253A1
- Authority
- CA
- Canada
- Prior art keywords
- coolant
- stream
- cooling
- cooled
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 185
- 238000000034 method Methods 0.000 title claims abstract description 132
- 230000008569 process Effects 0.000 title claims abstract description 108
- 239000002826 coolant Substances 0.000 claims abstract description 230
- 239000000872 buffer Substances 0.000 claims abstract description 32
- 230000004044 response Effects 0.000 claims abstract description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 37
- 239000003570 air Substances 0.000 claims description 18
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 14
- 239000003507 refrigerant Substances 0.000 claims description 14
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 12
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 239000003345 natural gas Substances 0.000 claims description 7
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 claims description 6
- 239000001294 propane Substances 0.000 claims description 6
- 238000005057 refrigeration Methods 0.000 claims description 5
- 238000010521 absorption reaction Methods 0.000 claims description 4
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 claims description 4
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 claims description 3
- 229910021529 ammonia Inorganic materials 0.000 claims description 3
- 239000012080 ambient air Substances 0.000 claims description 2
- 239000000498 cooling water Substances 0.000 claims 1
- 239000007788 liquid Substances 0.000 description 5
- 230000009467 reduction Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 239000002253 acid Substances 0.000 description 3
- 150000001412 amines Chemical class 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 230000003134 recirculating effect Effects 0.000 description 3
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 239000000654 additive Substances 0.000 description 2
- 239000003139 biocide Substances 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 235000009508 confectionery Nutrition 0.000 description 2
- 238000011437 continuous method Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000006735 deficit Effects 0.000 description 2
- 239000003112 inhibitor Substances 0.000 description 2
- 238000009413 insulation Methods 0.000 description 2
- 239000012536 storage buffer Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 239000002250 absorbent Substances 0.000 description 1
- 230000002745 absorbent Effects 0.000 description 1
- 239000007798 antifreeze agent Substances 0.000 description 1
- -1 antiscalants Substances 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000001311 chemical methods and process Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 239000003949 liquefied natural gas Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/04—Refrigerant level
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
Abstract
The invention provides a method of cooling a process stream, the method comprising at least the steps of : (a) heat exchanging a first coolant supply stream in a first cooling circuit against a process stream at a first process temperature to produce a first coolant return stream and a cooled process stream; (b) passing the first coolant return stream to a first coolant return tank to provide warmed first coolant; (c) withdrawing a portion of the warmed first coolant from the first coolant return tank as a warmed first coolant stream; (d) heat exchanging a cooled second coolant stream in a second cooling circuit against the warmed first coolant stream to produce a cooled first coolant stream, (e) passing the cooled first coolant stream to a first coolant supply tank to provide cooled first coolant; (f ) withdrawing a portion of the cooled first coolant from the first coolant supply tank as the first coolant supply stream; wherein the rate of flow of the warmed first coolant stream in step (c) is controlled in response to the cooling duty available from the second cooling circuit and the flow from the supply to the return buffer is controlled by the required cooling of the process stream and wherein the difference between the minimum and maximum cooling duty of the process stream over a time period is larger than the difference between the minimum and maximum cooling duty of the second cooling circuit over said time period.
Description
A METHOD AND APPARATUS FOR COOLING A PROCESS STREAM
The invention relates to a method of cooling a process stream, such as a liquid or gaseous stream in a process plant such as a refinery, Liquefying Natural Gas plant or chemical plant, particularly a process stream derived from the treatment of natural gas, and an apparatus for use in such a method.
The invention is aimed at providing a method and apparatus which can be designed to have a lower capacity compared to conventional units, while still providing comparable cooling performance. Such a reduction in design capacity provides significant savings in capital expenditure, allowing the use of smaller equipments, such as heat exchangers, compressors and condensers.
The invention provides method of cooling a process stream, the method comprising at least the steps of:
(a) heat exchanging a first coolant supply stream in a first cooling circuit against a process stream at a first process temperature to produce a first coolant return stream and a cooled process stream;
(b) passing the first coolant return stream to a first coolant return tank to provide warmed first coolant;
(c) withdrawing a portion of the warmed first coolant from the first coolant return tank as a warmed first coolant stream;
(d) heat exchanging a cooled second coolant stream in a second cooling circuit against the warmed first coolant stream to produce a cooled first coolant stream, (e) passing the cooled first coolant stream to a first coolant supply tank to provide cooled first coolant;
The invention relates to a method of cooling a process stream, such as a liquid or gaseous stream in a process plant such as a refinery, Liquefying Natural Gas plant or chemical plant, particularly a process stream derived from the treatment of natural gas, and an apparatus for use in such a method.
The invention is aimed at providing a method and apparatus which can be designed to have a lower capacity compared to conventional units, while still providing comparable cooling performance. Such a reduction in design capacity provides significant savings in capital expenditure, allowing the use of smaller equipments, such as heat exchangers, compressors and condensers.
The invention provides method of cooling a process stream, the method comprising at least the steps of:
(a) heat exchanging a first coolant supply stream in a first cooling circuit against a process stream at a first process temperature to produce a first coolant return stream and a cooled process stream;
(b) passing the first coolant return stream to a first coolant return tank to provide warmed first coolant;
(c) withdrawing a portion of the warmed first coolant from the first coolant return tank as a warmed first coolant stream;
(d) heat exchanging a cooled second coolant stream in a second cooling circuit against the warmed first coolant stream to produce a cooled first coolant stream, (e) passing the cooled first coolant stream to a first coolant supply tank to provide cooled first coolant;
(f) withdrawing a portion of the cooled first coolant from the first coolant supply tank as the first coolant supply stream; wherein the rate of flow of the warmed first coolant stream in step (c) is controlled in response to the cooling duty available from the second cooling circuit and the flow from the supply to the return buffer is controlled by the required cooling of the process stream and wherein the difference between the minimum and maximum cooling duty of the process stream over a time period is larger than the difference between the minimum and maximum cooling duty of the second cooling circuit over said time period.
Conventionally, a first cooling circuit which is heat exchanged against a process stream is operated to provide a particular cooling duty, corresponding to the peak capacity required of the cooling circuit said peak capacity being set by the process stream. This is achieved by providing a corresponding heat rejection to a second cooling circuit, which is for instance a closed refrigeration cycle.
However, the amount of heat which can be rejected to the second cooling circuit can change as a result of external conditions, such as ambient temperature.
Additionally, the required heat rejection from the process can change as a result of the same external conditions. Indeed, the temperature variance between day and night in some climates may be more than 10 C, sometimes more than 20 C, and even more than 30 C.
At low ambient temperature the second cooling circuit can provide greater cooling to the first cooling circuit, however the required cooling of the process by the first circuit is less. In the method of the present invention, the rate of flow of the warmed first coolant stream from return to supply tank is controlled in response to the cooling duty available from the second cooling circuit; whereas the flow of the cooled first coolant from the supply to the return buffer is controlled by the required cooling of the process. When more heat can be rejected to the second cooling circuit, the flow rate of the warmed first coolant stream can be increased, so that more warmed first coolant is heat exchanged against cooled second coolant in step (d), providing more cooled first coolant which can be accumulated in the cooled first coolant buffer supply tank. When more heat needs to be rejected from the process, the cooled 1St coolant flow from supply to return buffer is increased.
When ambient temperatures increase, the amount of cooling provided by the second cooling circuit to the first cooling circuit decreases and the rate of flow of the warmed first coolant stream can be correspondingly reduced. Should the cooling duty placed on the first cooling circuit by the process stream increase, the flow rate of the first coolant supply stream can be increased in order to ensure that the cooled process stream is provided at a controlled, preferably constant, temperature.
Increasing the flow rate of the first coolant supply stream, for example due to an increased cooling requirement of the process stream, may consume more cooled first coolant than is being supplied by the cooled first coolant stream (by heat exchange with the second cooling circuit). However, the accumulated cooled first coolant in the cooled first coolant buffer supply tank allows the effective operation of the cooling apparatus to be maintained.
Conventionally, a first cooling circuit which is heat exchanged against a process stream is operated to provide a particular cooling duty, corresponding to the peak capacity required of the cooling circuit said peak capacity being set by the process stream. This is achieved by providing a corresponding heat rejection to a second cooling circuit, which is for instance a closed refrigeration cycle.
However, the amount of heat which can be rejected to the second cooling circuit can change as a result of external conditions, such as ambient temperature.
Additionally, the required heat rejection from the process can change as a result of the same external conditions. Indeed, the temperature variance between day and night in some climates may be more than 10 C, sometimes more than 20 C, and even more than 30 C.
At low ambient temperature the second cooling circuit can provide greater cooling to the first cooling circuit, however the required cooling of the process by the first circuit is less. In the method of the present invention, the rate of flow of the warmed first coolant stream from return to supply tank is controlled in response to the cooling duty available from the second cooling circuit; whereas the flow of the cooled first coolant from the supply to the return buffer is controlled by the required cooling of the process. When more heat can be rejected to the second cooling circuit, the flow rate of the warmed first coolant stream can be increased, so that more warmed first coolant is heat exchanged against cooled second coolant in step (d), providing more cooled first coolant which can be accumulated in the cooled first coolant buffer supply tank. When more heat needs to be rejected from the process, the cooled 1St coolant flow from supply to return buffer is increased.
When ambient temperatures increase, the amount of cooling provided by the second cooling circuit to the first cooling circuit decreases and the rate of flow of the warmed first coolant stream can be correspondingly reduced. Should the cooling duty placed on the first cooling circuit by the process stream increase, the flow rate of the first coolant supply stream can be increased in order to ensure that the cooled process stream is provided at a controlled, preferably constant, temperature.
Increasing the flow rate of the first coolant supply stream, for example due to an increased cooling requirement of the process stream, may consume more cooled first coolant than is being supplied by the cooled first coolant stream (by heat exchange with the second cooling circuit). However, the accumulated cooled first coolant in the cooled first coolant buffer supply tank allows the effective operation of the cooling apparatus to be maintained.
The method of the present invention therefore enables a reduction in the capacity of the second cooling circuit compared to a conventional circuit which is designed to meet the peak load placed on the apparatus by the process stream. Instead of designing an apparatus for peak conditions e.g. maximum ambient temperatures (a capacity which is only partially used at lower ambient conditions), the first and second cooling circuits can be designed for a lower capacity. Any deficit of cooled first coolant (produced by heat exchange with the second cooling circuit) required to cool the process stream can be met by cooled first coolant from the cooled first coolant buffer supply tank. During lower ambient temperatures, the cooling capacity of the second cooling circuit can be higher than required by the first cooling circuit to cool the process stream, and so excess cooled first coolant can be produced and stored in the cooled first coolant supply tank.
Preferably the method is operated such that the sum of the amount of warmed first coolant in the first coolant return tank and the amount of cooled first coolant in the first coolant supply tank is held at a constant value. The relative amounts of first coolant can, of course, vary between the first coolant supply and return tanks.
The present invention therefore permits a cooling apparatus to be provided with a lower capacity than a conventional unit. For instance a capacity reduction to about 60% of the conventional capacity needed can be provided for the second cooling circuit, leading to large reductions in capital expenditure, even despite the additional buffer tanks and circulation pumps needed.
Preferably the method is operated such that the sum of the amount of warmed first coolant in the first coolant return tank and the amount of cooled first coolant in the first coolant supply tank is held at a constant value. The relative amounts of first coolant can, of course, vary between the first coolant supply and return tanks.
The present invention therefore permits a cooling apparatus to be provided with a lower capacity than a conventional unit. For instance a capacity reduction to about 60% of the conventional capacity needed can be provided for the second cooling circuit, leading to large reductions in capital expenditure, even despite the additional buffer tanks and circulation pumps needed.
-Preferably, the method of the invention is a continuous method for at least 24 hours and contains at least one day and night cycle i.e. steps (a) to (g) are repeated over at least one day and night cycle. More 5 preferably, the method is a continuous method with a duration of one week, preferably one month, more preferably 6 months, and even more preferably one year.
The process stream cooled in heat exchange step (a) may be any liquid or gaseous stream. For example, the process stream cooled in heat exchange step (a) may be a liquid or gaseous stream derived from the treatment of natural gas. Preferably, the process stream is an amine stream from an acid gas treatment unit or a sweet or sour natural gas stream.
The process stream is provided at a first process temperature, which is for example in the range of 20 to 65 C. The process stream can be provided by pre-cooling a warm process stream with an air cooler. The effectiveness of an air cooler will vary depending upon ambient conditions, such as ambient temperature. This is because the air cooler is designed to provide a particular cooling duty under maximum ambient temperatures. At lower than maximum temperatures, the process stream will exit the air cooler with a lower temperature than that provided under peak conditions.
Consequently, the cooling duty placed on the first cooling circuit by the process stream will be less. The flow rate of the first coolant supply stream can thus be reduced, lowering the consumption of cooled first coolant from the cooled first coolant supply tank.
Cooled first coolant can therefore be accumulated in the cooled first coolant supply tank, for use when the cooling duty on the first cooling circuit increases.
The process stream cooled in heat exchange step (a) may be any liquid or gaseous stream. For example, the process stream cooled in heat exchange step (a) may be a liquid or gaseous stream derived from the treatment of natural gas. Preferably, the process stream is an amine stream from an acid gas treatment unit or a sweet or sour natural gas stream.
The process stream is provided at a first process temperature, which is for example in the range of 20 to 65 C. The process stream can be provided by pre-cooling a warm process stream with an air cooler. The effectiveness of an air cooler will vary depending upon ambient conditions, such as ambient temperature. This is because the air cooler is designed to provide a particular cooling duty under maximum ambient temperatures. At lower than maximum temperatures, the process stream will exit the air cooler with a lower temperature than that provided under peak conditions.
Consequently, the cooling duty placed on the first cooling circuit by the process stream will be less. The flow rate of the first coolant supply stream can thus be reduced, lowering the consumption of cooled first coolant from the cooled first coolant supply tank.
Cooled first coolant can therefore be accumulated in the cooled first coolant supply tank, for use when the cooling duty on the first cooling circuit increases.
By providing a buffer supply tank and a buffer return tank, the present invention allows the flow rate of the first coolant supply stream, which cools the process stream, to be varied independently from the flow rate of the warmed first coolant stream, which ejects heat to the second cooling circuit.
The first cooling circuit is preferably a closed recirculating cooling circuit. Similarly, it is preferred that the second cooling circuit is a closed recirculating cooling circuit.
The first cooling circuit utilizes a first coolant.
Preferably, the first coolant comprises water. More preferably, the first coolant consists essentially of water. In such cases, the first coolant may also contain standard water additives, such as antifoams, antiscalants, biocides and corrosion inhibitors. The first coolant supply stream would thus be a chilled water supply stream. The first coolant return stream would therefore be a warmed water return stream.
In the second cooling circuit is preferably a heat pump, more preferably a chiller system of the compression or absorption type. The heated second coolant stream produced in step (d) may be passed to a cooling system to regenerate the cooled second coolant stream. If the second coolant circuit is an absorption cycle, the second coolant may comprise water with a lithium bromide absorbent. If the second cooling circuit is a compression cycle, the cooling system may comprise a compressor, a condenser and an expansion device. In the latter case, the second coolant comprises a refrigerant, for example propane, ammonia, R-134a or any other commercially available refrigerant.
The first cooling circuit is preferably a closed recirculating cooling circuit. Similarly, it is preferred that the second cooling circuit is a closed recirculating cooling circuit.
The first cooling circuit utilizes a first coolant.
Preferably, the first coolant comprises water. More preferably, the first coolant consists essentially of water. In such cases, the first coolant may also contain standard water additives, such as antifoams, antiscalants, biocides and corrosion inhibitors. The first coolant supply stream would thus be a chilled water supply stream. The first coolant return stream would therefore be a warmed water return stream.
In the second cooling circuit is preferably a heat pump, more preferably a chiller system of the compression or absorption type. The heated second coolant stream produced in step (d) may be passed to a cooling system to regenerate the cooled second coolant stream. If the second coolant circuit is an absorption cycle, the second coolant may comprise water with a lithium bromide absorbent. If the second cooling circuit is a compression cycle, the cooling system may comprise a compressor, a condenser and an expansion device. In the latter case, the second coolant comprises a refrigerant, for example propane, ammonia, R-134a or any other commercially available refrigerant.
It is preferred that heat exchange step (a) is carried out in a first heat exchanger. It is further preferred that heat exchange step (d) is carried out in a second heat exchanger. The heat exchange may be achieved through direct contact of the process stream and the first coolant supply stream in step (a) or the warmed first coolant stream and the cooled second coolant stream in step (d). Alternatively, indirect heat exchange may be used in steps (a) and (d), and this is preferred. Indirect heat exchange may be carried out in a shell and tube heat exchanger, an EM baffle heat exchanger, a plate and frame heat exchanger or a fin tube heat exchanger.
In a further embodiment, the present invention provides an apparatus for cooling a process stream, said apparatus at least comprising:
a first cooling circuit comprising a first heat exchanger, a first coolant return tank, a second heat exchanger and a first coolant supply tank, said first heat exchanger having a first inlet which is connected to a process stream line, a first outlet which is connected to a cooled process stream line, a second inlet which is connected to the outlet of the first coolant supply tank and a second outlet which is connected to the inlet of the first coolant return tank, said second heat exchanger having a first inlet which is connected to the outlet of the first coolant return tank, and a first outlet which is connected to the inlet of the first coolant supply tank; and a second cooling circuit comprising the second heat exchanger and a cooling system, said second heat exchanger having a second inlet connected to the outlet of the cooling system and a second outlet connected to the inlet of the cooling system.
It is preferred that the cooling system of the second cooling circuit comprises a compressor, a condenser, and an expansion device. The compressor can have an inlet connected to the second outlet of second heat exchanger and an outlet connected to an inlet of the condenser.
The condenser can have an outlet connected to an inlet of the expansion device, with the expansion device having an outlet connected to the second inlet of the second heat exchanger.
Furthermore, an air cooler may be provided upstream of the first heat exchanger in the process stream, for example by connecting the first inlet of the first heat exchanger to the outlet of the air cooler.
In a further aspect of the invention, a first pump can be provided between the outlet of first coolant return tank and the first inlet of second heat exchanger. Furthermore, a second pump can be provided between the outlet of first coolant supply tank and the second inlet of the first heat exchanger. These pumps can control the flow rate of the first coolant supply stream and the warmed first coolant stream. The flow can also be controlled using control valves. It will be apparent that the first pump (or a further pump) could be placed in the cooled first coolant stream rather than the warmed first coolant stream. Similarly, the second pump (or a further pump) could also be placed in the first coolant return stream rather than the first coolant supply stream.
In another aspect, the coolant flow through the first heat exchanger (process/first coolant) can be adjusted to maintain a constant controlled process outlet temperature ex first heat exchanger. Depending on the process flow rate, physical properties and specifically its temperature (downstream the air cooler) at the inlet of the first heat exchanger, the required heat transfer rate (to maintain a controlled process temperature ex first heat exchanger) in the first heat exchanger varies. The actual heat duty can be manipulated in different ways. Preferably, the temperature in the process stream exiting the first heat exchanger is measured by a sensor and said temperature sensor is connected to a processor which determines the cooled first coolant flow to the first heat exchanger and thereby manipulating the heat duty in first heat exchanger.). The person skilled in the art may readily find alternative control schemes.
In yet another aspect, a temperature sensor is provided in the cooled chilled water ex second heat exchanger (chilled water vs. refrigerant), said temperature being connected to a processor and said processor manipulating the chilled water flow through the second heat exchanger to maintain a constant chilled water supply temperature.
The duty of the refrigerant cycle can be manipulated in order to match the required cooling. For example level control on the chilled water supply tank can manipulate the duty (e.g. refrigerant compressor duty control system) of the refrigerant cycle, so varying the refrigerant supply to the refrigerant/chilled water heat exchanger.
The described control schemes maintain constant and controlled temperatures in the supply and the return tanks. Alternative control schemes may readily be found but always aiming at restoring the buffer of cooled first coolant in the supply tank when the duty of the second cooling circuit exceeds the cooling duty of the process.
Hereinafter the invention will be further illustrated by the following non-limiting drawings.
Figure 1 schematically shows a process scheme in accordance with an embodiment of the present invention.
Figure 2 shows a plot of the levels of the cooled and warmed primary coolant buffer tanks over time when carrying out the method of the present invention.
For the purpose of this description, a single reference number will be assigned to a line as well as a stream carried in that line. Same reference numbers refer to similar components.
Figure 1 is a schematic diagram showing an apparatus of the present invention 1 comprising a process cascade 2, a first cooling circuit 10 and a second cooling circuit 60. First cooling circuit 10 is used to cool process stream 6. Process stream 6 is a liquid or gaseous stream preferably in a refinery, natural gas treatment plant, liquefied natural gas, Gas-to-Liquids (also known as Shell Middle Distillate Synthesis) or chemical process plant, for example an amine stream from an acid gas treatment unit or a sweet or sour natural gas stream.
The present invention is directed towards the cooling of the process stream. Process stream 6 is provided at a first process temperature, which is preferably in the range of 20 to 65 C. Process stream 6 is passed to first heat exchanger 20 via first inlet 7 where it is heat exchanged against a first coolant supply stream 52 to provide a cooled process stream 9 at first outlet 8.
Cooled process stream 9 is produced at a second process temperature, which is preferably in the range of 0 to 35 C, preferably 25 C. Cooled process stream 9 can then be passed on to other units for further processing.
For instance, when process stream 6 is an amine stream from an acid gas treatment unit, it can be passed to a regeneration column after cooling.
First cooling circuit 10 is used to provide the cooling duty necessary to cool process stream 6. First cooling circuit 10 is preferably a closed loop cooling circuit. First cooling circuit 10 comprises a first coolant which preferably comprises water, more preferably the first coolant consists essentially of water, even more preferably for low temperatures a mixture of water and glycol or other anti-freeze agent.
In this case, the coolant water stream may also contain standard closed loop water additives, such as antiscalants, biocides and corrosion inhibitors.
First coolant supply stream 52, which is preferably a chilled water stream, is provided at a first coolant supply temperature, which can be in the range of 5 to C. First coolant supply stream 52 is passed to first heat exchanger 20 via second inlet 53, where it cools process stream 6 and is itself warmed to produce a first coolant return stream 22 at second outlet 21. First 25 coolant return stream 22 has a first coolant return temperature, which can be in the range of 10 to 45 C.
First coolant return stream 22 is passed to a first coolant return tank 30 via inlet 23. First coolant return tank 30 provides a storage buffer for the warmed 30 first coolant. Return tank 30 may be provided with insulation, in order to minimise heat ingress from surroundings. Return tank 30 operates to buffer the warmed first coolant between the first and second heat exchangers. The warmed first coolant is drawn from return tank 30 via outlet 32 as warmed first coolant stream 32.
When the cooling duty placed on the first cooling circuit 10 by process stream 6 is greater than the heat which can be ejected to second cooling circuit 60, the rate of flow of first coolant return stream 22 will be more than the rate of flow of warmed first coolant stream 32, and the level of warmed first coolant in return tank 30 will rise.
When the cooling duty placed on the first cooling circuit 10 by process stream 6 is less than the heat which can be rejected to second cooling circuit 60, the rate of flow of first coolant return stream 22 will be less than the rate of flow of warmed first coolant stream 32, and the level of warmed first coolant in return tank 30 will fall.
After exiting return tank 30, warmed first coolant stream 32 is passed to first inlet 33 of second heat exchanger 40, where it is cooled against cooled second coolant stream 72 to regenerate cooled first coolant stream 42 via outlet 41. Cooled first coolant stream 42 is produced at the first coolant supply temperature, which can be in the range of 5 to 30 C, as discussed above.
Cooled first coolant stream 42 is passed to first coolant supply tank 50 via inlet 43. Supply tank 50 provides a storage buffer for the cooled first coolant.
It is preferred that supply tank 50 is provided with insulation, in order to minimise heat ingress from the surroundings. Supply tank 50 operates to buffer the cooled first coolant between the second and first heat exchangers. The cooled first coolant is drawn from supply tank 50 via outlet 51 as first coolant supply stream 52.
When the cooling duty placed on first cooling circuit by process stream 6 is greater than the heat which 5 can be ejected to second cooling circuit 60, the rate of flow of cooled first coolant stream 42 will be less than the rate of flow of first coolant supply stream 52, and the level of cooled first coolant in supply tank 50 will fall.
10 When the cooling duty placed on first cooling circuit 10 by process stream 6 is less than the heat which can be ejected to cooling circuit 60, the rate of flow of cooled first coolant stream 42 will be greater than the rate of flow of first coolant supply stream 52, and the level of cooled first coolant in supply tank 50 will rise.
From the foregoing discussion, it will be apparent that the flow rate of warmed first coolant stream 32 should be equal to the flow rate of cooled first coolant stream 42 in order to provide a uniform flow through second heat exchanger 40. Similarly, the flow rate of first coolant supply stream 52 should be equal to the flow rate of first coolant return stream 22 in order to provide a uniform flow through first heat exchanger 20.
However, there is no requirement in the present invention that the flow rate of cooled first coolant supply stream 52 (or first coolant return stream 22) should be the same as warmed first coolant stream 32 (or cooled first coolant stream 42). Indeed, the method and apparatus of the present invention can provide unequal flows of streams 52 and 22 compared to streams 32 and 42. Consequently, the levels of warmed and cooled first coolant in return tank 30 and supply tank 50 respectively can be varied in response to changes in the cooling duty required by process stream 6 and the heat which can be ejected to second cooling circuit 60.
By buffering the cooled first coolant in supply tank 50 and warmed first coolant in return tank 30, it is possible to compensate for changes in ambient temperature. The ambient temperature can effect both the cooling duty which can be provided by second cooling circuit 60 (and hence the amount of heat which can be ejected by the first coolant circuit) and the temperature of process stream 6 (and hence the cooling duty required of first refrigerant circuit 20).
For instance, at low ambient temperatures, such as at night, the second cooling circuit 60 can generate more cold. This is because lower temperatures can be achieved in the second cooling system, for example in the condenser of the discharge of the second coolant compressor, when the ambient temperature is lower. The generation of more cold in second cooling circuit 60 allows more heat to be removed from the first cooling circuit 10. Under these conditions, the cooling capacity of the of the second cooling circuit 60 can be higher than required by process stream 6, and cooled first coolant can be accumulated in supply buffer 50, because the rate at which warmed first coolant stream 32 is cooled in second heat exchanger 40 can be increased. The excess cooled first coolant in supply buffer 50 can be stored for use when the cooling duty on the first cooling circuit 10 increases, for instance at high ambient temperatures.
Instead of designing the second cooling circuit to generate all the cold required by first cooling circuit 10 under peak conditions (e.g. during operation at maximum ambient temperatures) i.e. a peak capacity which is only partially used during lower ambient temperatures, second cooling circuit 60 can be designed for a lower capacity in accordance with the present invention.
At high ambient temperatures, such as during the day, the second cooling circuit 60 will be operating closer to, or at its maximum capacity, which is still lower than the peak capacity of first heat exchanger 20. Any deficit of cooled first coolant produced by heat exchange against the second cooling circuit during high ambient temperature conditions is met by the buffered cooled first coolant from first coolant supply tank 50.
During lower ambient conditions, the cooling capacity of the second cooling circuit 60 is higher than actually required by process stream 6, so that additional cooled first coolant can be generated in second heat exchanger 40 to restore the level in first coolant supply tank 50.
As discussed above, the first coolant increases in temperature due to the cold ejected by the heat exchange between first coolant supply stream 52 and process stream 4. Second cooling circuit 60 provides cooling to the first coolant in first cooling circuit 10.
Second cooling circuit 60 is preferably a closed recirculating cooling circuit. Second cooling circuit 60 comprises second heat exchanger 40 and a cooling system 70. Cooling system 70 generates the cooled second coolant stream 72 which is fed to second inlet 73 of second heat exchanger 40. In second heat exchanger 40, cooled second coolant stream 72 is heat exchanged against warmed first coolant stream 32 to produce a heated second coolant stream 46 at the second outlet 45 of second heat exchanger 40 and cooled first coolant stream 42. Heated second coolant stream 46 is then returned to cooling system 70 via inlet 47.
In the embodiment shown in Figure 1, the second cooling circuit is a compression cycle. More particularly, the compression cycle is a refrigeration cycle in which the second coolant is propane. In such a case, cooling system 70 will comprise a compressor, a condenser and an expansion device (not shown). The compressor has an inlet which is connected to the second outlet 45 of second heat exchanger 40. The compressor also has an outlet which is connected to the inlet of a condenser. The condenser has an outlet which is connected to the inlet of an expansion device, such as an expansion valve. The expansion device has an outlet which is connected to the second inlet 73 of second heat exchanger 40. The operation of such refrigeration systems is well known and will not be discussed in greater detail here.
A further advantage of the present invention is that by buffering the cooled first coolant in supply tank 50 and warmed first coolant in return tank 30, it is possible to compensate for changes in the temperature of process stream 6.
In the embodiment shown is Figure 1, an air cooler 80 is provided upstream of first heat exchanger 20 in process cascade 2. Process stream 6 is produced by air cooler 80 at outlet 5 and passed to first inlet 7 of first heat exchanger 20. Air cooler 80 is supplied by warm process stream 3 via inlet 4. Air cooler 80 cools warm process stream 3, preferably to a temperature in the range of 40 to 65 C. However, the temperature to which warm process stream 3 is cooled will depend on the ambient air temperature drawn through air cooler 80.
In a further embodiment, the present invention provides an apparatus for cooling a process stream, said apparatus at least comprising:
a first cooling circuit comprising a first heat exchanger, a first coolant return tank, a second heat exchanger and a first coolant supply tank, said first heat exchanger having a first inlet which is connected to a process stream line, a first outlet which is connected to a cooled process stream line, a second inlet which is connected to the outlet of the first coolant supply tank and a second outlet which is connected to the inlet of the first coolant return tank, said second heat exchanger having a first inlet which is connected to the outlet of the first coolant return tank, and a first outlet which is connected to the inlet of the first coolant supply tank; and a second cooling circuit comprising the second heat exchanger and a cooling system, said second heat exchanger having a second inlet connected to the outlet of the cooling system and a second outlet connected to the inlet of the cooling system.
It is preferred that the cooling system of the second cooling circuit comprises a compressor, a condenser, and an expansion device. The compressor can have an inlet connected to the second outlet of second heat exchanger and an outlet connected to an inlet of the condenser.
The condenser can have an outlet connected to an inlet of the expansion device, with the expansion device having an outlet connected to the second inlet of the second heat exchanger.
Furthermore, an air cooler may be provided upstream of the first heat exchanger in the process stream, for example by connecting the first inlet of the first heat exchanger to the outlet of the air cooler.
In a further aspect of the invention, a first pump can be provided between the outlet of first coolant return tank and the first inlet of second heat exchanger. Furthermore, a second pump can be provided between the outlet of first coolant supply tank and the second inlet of the first heat exchanger. These pumps can control the flow rate of the first coolant supply stream and the warmed first coolant stream. The flow can also be controlled using control valves. It will be apparent that the first pump (or a further pump) could be placed in the cooled first coolant stream rather than the warmed first coolant stream. Similarly, the second pump (or a further pump) could also be placed in the first coolant return stream rather than the first coolant supply stream.
In another aspect, the coolant flow through the first heat exchanger (process/first coolant) can be adjusted to maintain a constant controlled process outlet temperature ex first heat exchanger. Depending on the process flow rate, physical properties and specifically its temperature (downstream the air cooler) at the inlet of the first heat exchanger, the required heat transfer rate (to maintain a controlled process temperature ex first heat exchanger) in the first heat exchanger varies. The actual heat duty can be manipulated in different ways. Preferably, the temperature in the process stream exiting the first heat exchanger is measured by a sensor and said temperature sensor is connected to a processor which determines the cooled first coolant flow to the first heat exchanger and thereby manipulating the heat duty in first heat exchanger.). The person skilled in the art may readily find alternative control schemes.
In yet another aspect, a temperature sensor is provided in the cooled chilled water ex second heat exchanger (chilled water vs. refrigerant), said temperature being connected to a processor and said processor manipulating the chilled water flow through the second heat exchanger to maintain a constant chilled water supply temperature.
The duty of the refrigerant cycle can be manipulated in order to match the required cooling. For example level control on the chilled water supply tank can manipulate the duty (e.g. refrigerant compressor duty control system) of the refrigerant cycle, so varying the refrigerant supply to the refrigerant/chilled water heat exchanger.
The described control schemes maintain constant and controlled temperatures in the supply and the return tanks. Alternative control schemes may readily be found but always aiming at restoring the buffer of cooled first coolant in the supply tank when the duty of the second cooling circuit exceeds the cooling duty of the process.
Hereinafter the invention will be further illustrated by the following non-limiting drawings.
Figure 1 schematically shows a process scheme in accordance with an embodiment of the present invention.
Figure 2 shows a plot of the levels of the cooled and warmed primary coolant buffer tanks over time when carrying out the method of the present invention.
For the purpose of this description, a single reference number will be assigned to a line as well as a stream carried in that line. Same reference numbers refer to similar components.
Figure 1 is a schematic diagram showing an apparatus of the present invention 1 comprising a process cascade 2, a first cooling circuit 10 and a second cooling circuit 60. First cooling circuit 10 is used to cool process stream 6. Process stream 6 is a liquid or gaseous stream preferably in a refinery, natural gas treatment plant, liquefied natural gas, Gas-to-Liquids (also known as Shell Middle Distillate Synthesis) or chemical process plant, for example an amine stream from an acid gas treatment unit or a sweet or sour natural gas stream.
The present invention is directed towards the cooling of the process stream. Process stream 6 is provided at a first process temperature, which is preferably in the range of 20 to 65 C. Process stream 6 is passed to first heat exchanger 20 via first inlet 7 where it is heat exchanged against a first coolant supply stream 52 to provide a cooled process stream 9 at first outlet 8.
Cooled process stream 9 is produced at a second process temperature, which is preferably in the range of 0 to 35 C, preferably 25 C. Cooled process stream 9 can then be passed on to other units for further processing.
For instance, when process stream 6 is an amine stream from an acid gas treatment unit, it can be passed to a regeneration column after cooling.
First cooling circuit 10 is used to provide the cooling duty necessary to cool process stream 6. First cooling circuit 10 is preferably a closed loop cooling circuit. First cooling circuit 10 comprises a first coolant which preferably comprises water, more preferably the first coolant consists essentially of water, even more preferably for low temperatures a mixture of water and glycol or other anti-freeze agent.
In this case, the coolant water stream may also contain standard closed loop water additives, such as antiscalants, biocides and corrosion inhibitors.
First coolant supply stream 52, which is preferably a chilled water stream, is provided at a first coolant supply temperature, which can be in the range of 5 to C. First coolant supply stream 52 is passed to first heat exchanger 20 via second inlet 53, where it cools process stream 6 and is itself warmed to produce a first coolant return stream 22 at second outlet 21. First 25 coolant return stream 22 has a first coolant return temperature, which can be in the range of 10 to 45 C.
First coolant return stream 22 is passed to a first coolant return tank 30 via inlet 23. First coolant return tank 30 provides a storage buffer for the warmed 30 first coolant. Return tank 30 may be provided with insulation, in order to minimise heat ingress from surroundings. Return tank 30 operates to buffer the warmed first coolant between the first and second heat exchangers. The warmed first coolant is drawn from return tank 30 via outlet 32 as warmed first coolant stream 32.
When the cooling duty placed on the first cooling circuit 10 by process stream 6 is greater than the heat which can be ejected to second cooling circuit 60, the rate of flow of first coolant return stream 22 will be more than the rate of flow of warmed first coolant stream 32, and the level of warmed first coolant in return tank 30 will rise.
When the cooling duty placed on the first cooling circuit 10 by process stream 6 is less than the heat which can be rejected to second cooling circuit 60, the rate of flow of first coolant return stream 22 will be less than the rate of flow of warmed first coolant stream 32, and the level of warmed first coolant in return tank 30 will fall.
After exiting return tank 30, warmed first coolant stream 32 is passed to first inlet 33 of second heat exchanger 40, where it is cooled against cooled second coolant stream 72 to regenerate cooled first coolant stream 42 via outlet 41. Cooled first coolant stream 42 is produced at the first coolant supply temperature, which can be in the range of 5 to 30 C, as discussed above.
Cooled first coolant stream 42 is passed to first coolant supply tank 50 via inlet 43. Supply tank 50 provides a storage buffer for the cooled first coolant.
It is preferred that supply tank 50 is provided with insulation, in order to minimise heat ingress from the surroundings. Supply tank 50 operates to buffer the cooled first coolant between the second and first heat exchangers. The cooled first coolant is drawn from supply tank 50 via outlet 51 as first coolant supply stream 52.
When the cooling duty placed on first cooling circuit by process stream 6 is greater than the heat which 5 can be ejected to second cooling circuit 60, the rate of flow of cooled first coolant stream 42 will be less than the rate of flow of first coolant supply stream 52, and the level of cooled first coolant in supply tank 50 will fall.
10 When the cooling duty placed on first cooling circuit 10 by process stream 6 is less than the heat which can be ejected to cooling circuit 60, the rate of flow of cooled first coolant stream 42 will be greater than the rate of flow of first coolant supply stream 52, and the level of cooled first coolant in supply tank 50 will rise.
From the foregoing discussion, it will be apparent that the flow rate of warmed first coolant stream 32 should be equal to the flow rate of cooled first coolant stream 42 in order to provide a uniform flow through second heat exchanger 40. Similarly, the flow rate of first coolant supply stream 52 should be equal to the flow rate of first coolant return stream 22 in order to provide a uniform flow through first heat exchanger 20.
However, there is no requirement in the present invention that the flow rate of cooled first coolant supply stream 52 (or first coolant return stream 22) should be the same as warmed first coolant stream 32 (or cooled first coolant stream 42). Indeed, the method and apparatus of the present invention can provide unequal flows of streams 52 and 22 compared to streams 32 and 42. Consequently, the levels of warmed and cooled first coolant in return tank 30 and supply tank 50 respectively can be varied in response to changes in the cooling duty required by process stream 6 and the heat which can be ejected to second cooling circuit 60.
By buffering the cooled first coolant in supply tank 50 and warmed first coolant in return tank 30, it is possible to compensate for changes in ambient temperature. The ambient temperature can effect both the cooling duty which can be provided by second cooling circuit 60 (and hence the amount of heat which can be ejected by the first coolant circuit) and the temperature of process stream 6 (and hence the cooling duty required of first refrigerant circuit 20).
For instance, at low ambient temperatures, such as at night, the second cooling circuit 60 can generate more cold. This is because lower temperatures can be achieved in the second cooling system, for example in the condenser of the discharge of the second coolant compressor, when the ambient temperature is lower. The generation of more cold in second cooling circuit 60 allows more heat to be removed from the first cooling circuit 10. Under these conditions, the cooling capacity of the of the second cooling circuit 60 can be higher than required by process stream 6, and cooled first coolant can be accumulated in supply buffer 50, because the rate at which warmed first coolant stream 32 is cooled in second heat exchanger 40 can be increased. The excess cooled first coolant in supply buffer 50 can be stored for use when the cooling duty on the first cooling circuit 10 increases, for instance at high ambient temperatures.
Instead of designing the second cooling circuit to generate all the cold required by first cooling circuit 10 under peak conditions (e.g. during operation at maximum ambient temperatures) i.e. a peak capacity which is only partially used during lower ambient temperatures, second cooling circuit 60 can be designed for a lower capacity in accordance with the present invention.
At high ambient temperatures, such as during the day, the second cooling circuit 60 will be operating closer to, or at its maximum capacity, which is still lower than the peak capacity of first heat exchanger 20. Any deficit of cooled first coolant produced by heat exchange against the second cooling circuit during high ambient temperature conditions is met by the buffered cooled first coolant from first coolant supply tank 50.
During lower ambient conditions, the cooling capacity of the second cooling circuit 60 is higher than actually required by process stream 6, so that additional cooled first coolant can be generated in second heat exchanger 40 to restore the level in first coolant supply tank 50.
As discussed above, the first coolant increases in temperature due to the cold ejected by the heat exchange between first coolant supply stream 52 and process stream 4. Second cooling circuit 60 provides cooling to the first coolant in first cooling circuit 10.
Second cooling circuit 60 is preferably a closed recirculating cooling circuit. Second cooling circuit 60 comprises second heat exchanger 40 and a cooling system 70. Cooling system 70 generates the cooled second coolant stream 72 which is fed to second inlet 73 of second heat exchanger 40. In second heat exchanger 40, cooled second coolant stream 72 is heat exchanged against warmed first coolant stream 32 to produce a heated second coolant stream 46 at the second outlet 45 of second heat exchanger 40 and cooled first coolant stream 42. Heated second coolant stream 46 is then returned to cooling system 70 via inlet 47.
In the embodiment shown in Figure 1, the second cooling circuit is a compression cycle. More particularly, the compression cycle is a refrigeration cycle in which the second coolant is propane. In such a case, cooling system 70 will comprise a compressor, a condenser and an expansion device (not shown). The compressor has an inlet which is connected to the second outlet 45 of second heat exchanger 40. The compressor also has an outlet which is connected to the inlet of a condenser. The condenser has an outlet which is connected to the inlet of an expansion device, such as an expansion valve. The expansion device has an outlet which is connected to the second inlet 73 of second heat exchanger 40. The operation of such refrigeration systems is well known and will not be discussed in greater detail here.
A further advantage of the present invention is that by buffering the cooled first coolant in supply tank 50 and warmed first coolant in return tank 30, it is possible to compensate for changes in the temperature of process stream 6.
In the embodiment shown is Figure 1, an air cooler 80 is provided upstream of first heat exchanger 20 in process cascade 2. Process stream 6 is produced by air cooler 80 at outlet 5 and passed to first inlet 7 of first heat exchanger 20. Air cooler 80 is supplied by warm process stream 3 via inlet 4. Air cooler 80 cools warm process stream 3, preferably to a temperature in the range of 40 to 65 C. However, the temperature to which warm process stream 3 is cooled will depend on the ambient air temperature drawn through air cooler 80.
For instance, at lower ambient temperatures, such as during the night, the first process temperature of process stream 6, downstream of air cooler 80 will be lower than during high ambient temperature. This is because air cooler 80 can provide greater cooling to warm process stream 3 because the surrounding air is cooler than during the day. Thus, if a constant second process temperature for cooled process stream 9 is to be maintained downstream of first heat exchanger 20, the cooling duty required of first cooling circuit 10 during low ambient temperatures is less. Under such low ambient temperatures, the flow rate of first coolant supply stream 52 can be reduced, because the cooling duty placed on first cooling circuit 10 by process stream 6 is less. A reduction in the flow rate of first coolant supply stream 52 allows cooled first coolant to be accumulated in supply buffer tank 50, because the flow rate of first coolant supply stream 52 will be less than the flow rate of cooled first coolant stream 42.
At higher ambient temperatures, such as during the day, the first process temperature of process stream 6 will be higher than at night, because air cooler 80 will not be able to provide as much cooling to warm process stream 3. A higher cooling duty will therefore be placed upon first cooling circuit 10. In order to provide more cold to process stream 6 in order to maintain the second process temperature downstream of first heat exchanger 20 at a constant temperature, the flow rate of first coolant supply stream 52 can be increased. When this flow rate becomes greater than the flow rate of warmed first coolant stream 32 into second heat exchanger 40, the cooled first coolant in supply buffer tank 50 will be consumed and the level of first coolant in the tank will drop.
From the foregoing discussion, it is evident that the effect of ambient temperature on the cooling duty available from second cooling circuit 60 and the effect of ambient temperature on the first temperature of process stream 6 operate in combination. In particular, at lower ambient temperatures, second cooling circuit 60 can provide a higher cooling duty, allowing greater heat rejection in the first cooling circuit 10, increasing the level of cooled first coolant in supply buffer tank 50. At the same time, the cooling duty placed upon the first cooling circuit by process stream 6 is reduced because air cooler 80 can provide greater cooling, reducing the first process temperature of process stream 6, allowing more cooled first coolant to be accumulated in supply buffer tank 50.
These effects allow the level of cooled first coolant in supply tank 50 to be increased at lower ambient temperatures, such that when the temperatures increase during the day, and the cooling duty available from second cooling circuit 60 decreases, and the cooling duty placed on the first cooling circuit 10 by process stream 6 increases, a reserve of cooled first coolant is available in supply buffer tank 50 to meet the increased cooling demands.
In this way, the second cooling circuit of the present invention can be provided with a lower capacity than conventional units, which results in corresponding savings in capital expenditure, while still meeting the same operational requirements. This will be explained in greater detail in the following non-limiting Example.
At higher ambient temperatures, such as during the day, the first process temperature of process stream 6 will be higher than at night, because air cooler 80 will not be able to provide as much cooling to warm process stream 3. A higher cooling duty will therefore be placed upon first cooling circuit 10. In order to provide more cold to process stream 6 in order to maintain the second process temperature downstream of first heat exchanger 20 at a constant temperature, the flow rate of first coolant supply stream 52 can be increased. When this flow rate becomes greater than the flow rate of warmed first coolant stream 32 into second heat exchanger 40, the cooled first coolant in supply buffer tank 50 will be consumed and the level of first coolant in the tank will drop.
From the foregoing discussion, it is evident that the effect of ambient temperature on the cooling duty available from second cooling circuit 60 and the effect of ambient temperature on the first temperature of process stream 6 operate in combination. In particular, at lower ambient temperatures, second cooling circuit 60 can provide a higher cooling duty, allowing greater heat rejection in the first cooling circuit 10, increasing the level of cooled first coolant in supply buffer tank 50. At the same time, the cooling duty placed upon the first cooling circuit by process stream 6 is reduced because air cooler 80 can provide greater cooling, reducing the first process temperature of process stream 6, allowing more cooled first coolant to be accumulated in supply buffer tank 50.
These effects allow the level of cooled first coolant in supply tank 50 to be increased at lower ambient temperatures, such that when the temperatures increase during the day, and the cooling duty available from second cooling circuit 60 decreases, and the cooling duty placed on the first cooling circuit 10 by process stream 6 increases, a reserve of cooled first coolant is available in supply buffer tank 50 to meet the increased cooling demands.
In this way, the second cooling circuit of the present invention can be provided with a lower capacity than conventional units, which results in corresponding savings in capital expenditure, while still meeting the same operational requirements. This will be explained in greater detail in the following non-limiting Example.
Example 1 A closed loop chilled water circuit is provided as the first cooling circuit. The first coolant supply stream (chilled water) has a temperature of 25 C, and the first coolant return stream (warmed water) has a temperature of 40 C. A propane compression refrigeration cycle is provided as the second cooling circuit.
Following the method of the invention, an apparatus was constructed with a capacity of 58% of the equipment required for conventional peak capacity operation. In particular, a 70 MW chilled water/refrigerant heat exchanger (the second heat exchanger) and refrigerant system with a capacity of 70 MW heat rejection from circuit 1, with an additional 40 000 m3 chilled water supply and return tank capacity was found to provide equivalent performance including peak heat rejection from process up to 120 MW. Without the invention the second circuit (refrigerant, including compressors) would have been designed for 120 MW. The compressor and the rest of the propane cooling cycle (second cooling circuit) was so reduced to 58% of the equivalent equipment capacity required for conventional operation.
Figure 2 is a plot showing the variation in the levels of the chilled water buffer supply tank 50 and the warmed water buffer return tank 30 over time for the apparatus of the Example. In this experiment, the maximum level of chilled water in chilled water supply tank 50 was set at 90% and the minimum level of warmed water buffer return tank 30 was set at 10%.
From Figure 2, it is apparent that the troughs in the level of buffer supply tank 50, which occur when the difference between the flow rate of chilled water supply stream 52 and warmed water return stream 32 are at a maximum, are mirrored by peaks in the level of warmed coolant in buffer return tank 30. This situation occurred at peak ambient temperatures during the day, when the cooling duty placed upon first cooling circuit is at a maximum.
During lower ambient conditions at night, the level of chilled water in buffer supply tank 50 was restored as the cooling duty placed on first cooling circuit 10 10 decreased, and more cooling was provided by second cooling circuit 60, while less cooling was required by process stream 6.
The day and night cycles shown in the centre of the plot of Figure 2 occurred when extremely day-time ambient temperatures were experienced. The chilled water level in the buffer supply tank 50 was unable to return to a level of 90% over a single day/ night cycle. Such a situation arose when the cooling duty placed upon the first cooling circuit over a 24 hour period was greater than the available heat rejection to the second cooling circuit. However, the apparatus of the invention still functioned effectively because additional chilled water was stored in buffer supply tank 50. During the hottest day, the buffer supply tank level was reduced to a minimum level of approximately 35%, and recovered to a level of approximately 75% that night. Three subsequently hot days reduced the level of chilled water in the buffer supply tank to approximately 45%. However, the apparatus recovered to equilibrium levels of chilled water and warmed water thereafter when the ambient conditions return to a normal cycle.
The person skilled in the art will readily understand that many modifications may be made without departing from the scope of the invention. For example, alternative constructions can be provided for the second coolant system utilising an absorption system rather than compression system described with reference to Figure 1.
Following the method of the invention, an apparatus was constructed with a capacity of 58% of the equipment required for conventional peak capacity operation. In particular, a 70 MW chilled water/refrigerant heat exchanger (the second heat exchanger) and refrigerant system with a capacity of 70 MW heat rejection from circuit 1, with an additional 40 000 m3 chilled water supply and return tank capacity was found to provide equivalent performance including peak heat rejection from process up to 120 MW. Without the invention the second circuit (refrigerant, including compressors) would have been designed for 120 MW. The compressor and the rest of the propane cooling cycle (second cooling circuit) was so reduced to 58% of the equivalent equipment capacity required for conventional operation.
Figure 2 is a plot showing the variation in the levels of the chilled water buffer supply tank 50 and the warmed water buffer return tank 30 over time for the apparatus of the Example. In this experiment, the maximum level of chilled water in chilled water supply tank 50 was set at 90% and the minimum level of warmed water buffer return tank 30 was set at 10%.
From Figure 2, it is apparent that the troughs in the level of buffer supply tank 50, which occur when the difference between the flow rate of chilled water supply stream 52 and warmed water return stream 32 are at a maximum, are mirrored by peaks in the level of warmed coolant in buffer return tank 30. This situation occurred at peak ambient temperatures during the day, when the cooling duty placed upon first cooling circuit is at a maximum.
During lower ambient conditions at night, the level of chilled water in buffer supply tank 50 was restored as the cooling duty placed on first cooling circuit 10 10 decreased, and more cooling was provided by second cooling circuit 60, while less cooling was required by process stream 6.
The day and night cycles shown in the centre of the plot of Figure 2 occurred when extremely day-time ambient temperatures were experienced. The chilled water level in the buffer supply tank 50 was unable to return to a level of 90% over a single day/ night cycle. Such a situation arose when the cooling duty placed upon the first cooling circuit over a 24 hour period was greater than the available heat rejection to the second cooling circuit. However, the apparatus of the invention still functioned effectively because additional chilled water was stored in buffer supply tank 50. During the hottest day, the buffer supply tank level was reduced to a minimum level of approximately 35%, and recovered to a level of approximately 75% that night. Three subsequently hot days reduced the level of chilled water in the buffer supply tank to approximately 45%. However, the apparatus recovered to equilibrium levels of chilled water and warmed water thereafter when the ambient conditions return to a normal cycle.
The person skilled in the art will readily understand that many modifications may be made without departing from the scope of the invention. For example, alternative constructions can be provided for the second coolant system utilising an absorption system rather than compression system described with reference to Figure 1.
Claims (8)
1. A method of cooling a process stream, the method comprising at least the steps of:
(a) heat exchanging a first coolant supply stream in a first cooling circuit against a process stream at a first process temperature to produce a first coolant return stream and a cooled process stream;
(b) passing the first coolant return stream to a first coolant return tank to provide warmed first coolant;
(c) withdrawing a portion of the warmed first coolant from the first coolant return tank as a warmed first coolant stream;
(d) heat exchanging a cooled second coolant stream in a second cooling circuit against the warmed first coolant stream to produce a cooled first coolant stream, (e) passing the cooled first coolant stream to a first coolant supply tank to provide cooled first coolant;
(f) withdrawing a portion of the cooled first coolant from the first coolant supply tank as the first coolant supply stream; wherein the rate of flow of the warmed first coolant stream in step (c) is controlled in response to the cooling duty available from the second cooling circuit and the flow from the supply to the return buffer is controlled by the required cooling of the process stream and wherein the difference between the minimum and maximum cooling duty of the process stream over a time period is larger than the difference between the minimum and maximum cooling duty of the second cooling circuit over said time period.
(a) heat exchanging a first coolant supply stream in a first cooling circuit against a process stream at a first process temperature to produce a first coolant return stream and a cooled process stream;
(b) passing the first coolant return stream to a first coolant return tank to provide warmed first coolant;
(c) withdrawing a portion of the warmed first coolant from the first coolant return tank as a warmed first coolant stream;
(d) heat exchanging a cooled second coolant stream in a second cooling circuit against the warmed first coolant stream to produce a cooled first coolant stream, (e) passing the cooled first coolant stream to a first coolant supply tank to provide cooled first coolant;
(f) withdrawing a portion of the cooled first coolant from the first coolant supply tank as the first coolant supply stream; wherein the rate of flow of the warmed first coolant stream in step (c) is controlled in response to the cooling duty available from the second cooling circuit and the flow from the supply to the return buffer is controlled by the required cooling of the process stream and wherein the difference between the minimum and maximum cooling duty of the process stream over a time period is larger than the difference between the minimum and maximum cooling duty of the second cooling circuit over said time period.
2. A method according to claim 1 wherein the second cooling circuit is any chiller system, such as compression refrigeration systems with refrigerants such as propane, ammonia, R-134a or absorption chilling systems based on Lithium Bromide.
3. A method according to any one of the preceding claims wherein the first coolant comprises water.
4. A method according to claim 3, wherein the first coolant is a refrigerant, preferably propane, ammonia, R-134a or any other commercially available coolant and wherein the second coolant is cooling water or ambient air.
5. A method according to any one of the preceding claims wherein the sum of the amount of warmed first coolant in the first coolant return tank and the amount of cooled first coolant in the first coolant supply tank is held at a constant value.
6. A method according to any one of the preceding claims wherein steps (a) to (g) are repeated over at least one day and night cycle.
7. An apparatus (1) for cooling a process stream, such as a stream derived from natural gas, the apparatus at least comprising:
a first cooling circuit (10) comprising a first heat exchanger (20), a first coolant return tank (30), a second heat exchanger (40) and a first coolant supply tank (50), said first heat exchanger (20) having a first inlet (7) which is connected to a process stream line (6), a first outlet (8) which is connected to a cooled process stream line (9), a second inlet (53) which is connected to the outlet (51) of the first coolant supply tank (50) and a second outlet (21) which is connected to the inlet (23) of the first coolant return tank (30), said second heat exchanger (40) having a first inlet (33) which is connected to the outlet (31) of the first coolant return tank (30), and a first outlet (41) which is connected to the inlet (43) of the first coolant supply tank (50);
and a second cooling circuit (60) comprising the second heat exchanger (40) and a cooling system (70), said second heat exchanger (40) having a second inlet (73) connected to the outlet (71) of the cooling system and a second outlet (45) connected to the inlet (47) of the cooling system (70), wherein the cooling system (70) of the second cooling circuit (60) comprises a compressor, a condenser, and an expansion device, said compressor having an inlet connected to the second outlet of second heat exchanger (40), an outlet connected to an inlet of the condenser, said condenser having an outlet connected to an inlet of the expansion device and said expansion device having an outlet connected to the second inlet (73) of the second heat exchanger (40) and wherein the first inlet (7) of first heat exchanger (20) is connected to the outlet (5) of an air cooler (80).
a first cooling circuit (10) comprising a first heat exchanger (20), a first coolant return tank (30), a second heat exchanger (40) and a first coolant supply tank (50), said first heat exchanger (20) having a first inlet (7) which is connected to a process stream line (6), a first outlet (8) which is connected to a cooled process stream line (9), a second inlet (53) which is connected to the outlet (51) of the first coolant supply tank (50) and a second outlet (21) which is connected to the inlet (23) of the first coolant return tank (30), said second heat exchanger (40) having a first inlet (33) which is connected to the outlet (31) of the first coolant return tank (30), and a first outlet (41) which is connected to the inlet (43) of the first coolant supply tank (50);
and a second cooling circuit (60) comprising the second heat exchanger (40) and a cooling system (70), said second heat exchanger (40) having a second inlet (73) connected to the outlet (71) of the cooling system and a second outlet (45) connected to the inlet (47) of the cooling system (70), wherein the cooling system (70) of the second cooling circuit (60) comprises a compressor, a condenser, and an expansion device, said compressor having an inlet connected to the second outlet of second heat exchanger (40), an outlet connected to an inlet of the condenser, said condenser having an outlet connected to an inlet of the expansion device and said expansion device having an outlet connected to the second inlet (73) of the second heat exchanger (40) and wherein the first inlet (7) of first heat exchanger (20) is connected to the outlet (5) of an air cooler (80).
8. An apparatus according to claim 7 wherein a first pump is provided between the outlet (31) of first coolant return tank (30) and the first inlet (33) of second heat exchanger (40) and a second pump is provided between the outlet (51) of first coolant supply tank (50) and the second inlet (53) of the first heat exchanger (20), wherein a temperature sensor is provided in stream line (9) at the outlet (8) of heat exchanger (20)to detect the temperature in process stream line (9), said temperature sensor being connected to a first processor which determines the net supply of first coolant via the first pump to first heat exchanger (20) and wherein a temperature sensor is provided between the outlet (41) of second heat exchanger (40) and the inlet (43) of first coolant supply tank (50), said sensor being connected to a second processor which determines the supply of first coolant via the second pump to second heat exchanger (40) and wherein a level sensor is provided in first coolant supply tank (50), said level sensor being connected to a third processor which determines the duty of the cooling system (70).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP07120806 | 2007-11-15 | ||
| EP07120806.0 | 2007-11-15 | ||
| PCT/EP2008/065562 WO2009063055A1 (en) | 2007-11-15 | 2008-11-14 | A method and apparatus for cooling a process stream |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2705253A1 true CA2705253A1 (en) | 2009-05-22 |
Family
ID=39446108
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2705253A Abandoned CA2705253A1 (en) | 2007-11-15 | 2008-11-14 | A method and apparatus for cooling a process stream |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20100275645A1 (en) |
| CN (1) | CN101896780A (en) |
| AU (1) | AU2008322843B2 (en) |
| CA (1) | CA2705253A1 (en) |
| EA (1) | EA201000802A1 (en) |
| WO (1) | WO2009063055A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101947359B (en) * | 2010-09-16 | 2013-06-26 | 武汉依瑞德医疗设备新技术有限公司 | Magnetic field stimulator and cooling method thereof |
| US9557102B2 (en) | 2013-06-19 | 2017-01-31 | Bechtel Hydrocarbon Technology Solutions, Inc. | Systems and methods for natural gas liquefaction capacity augmentation |
| CN104611081B (en) * | 2015-01-23 | 2017-01-04 | 西安交通大学 | A kind of de-hydrocarbon experimental provision of natural gas swell refrigeration dehydration |
| US9827602B2 (en) | 2015-09-28 | 2017-11-28 | Tesla, Inc. | Closed-loop thermal servicing of solvent-refining columns |
| CN108474520B (en) * | 2015-12-31 | 2021-08-13 | 国际壳牌研究有限公司 | Method for filling transport equipment with liquefied gaseous fuel |
| KR102476168B1 (en) | 2016-12-23 | 2022-12-09 | 쉘 인터내셔날 리써취 마트샤피지 비.브이. | Liquefied gas transport vessel and method of operating the vessel |
| US11639824B2 (en) | 2020-04-30 | 2023-05-02 | Air Products And Chemicals, Inc. | Process for enhanced closed-circuit cooling system |
| KR102228198B1 (en) | 2020-09-02 | 2021-03-17 | 쿠팡 주식회사 | Electronic apparatus and information providing method thereof |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61125562A (en) * | 1984-11-24 | 1986-06-13 | 日立造船株式会社 | Absorption type refrigeration system |
| US5596878A (en) * | 1995-06-26 | 1997-01-28 | Thermo King Corporation | Methods and apparatus for operating a refrigeration unit |
| FR2787870B1 (en) * | 1998-12-24 | 2001-02-02 | Inst Francais Du Petrole | METHOD AND SYSTEM FOR FRACTIONATION OF A HIGH PRESSURE GAS |
| US6148634A (en) * | 1999-04-26 | 2000-11-21 | 3M Innovative Properties Company | Multistage rapid product refrigeration apparatus and method |
| EP1134514A1 (en) * | 2000-03-17 | 2001-09-19 | Société des Produits Nestlé S.A. | Refrigeration system |
| US6293106B1 (en) * | 2000-05-18 | 2001-09-25 | Praxair Technology, Inc. | Magnetic refrigeration system with multicomponent refrigerant fluid forecooling |
| WO2001090663A1 (en) * | 2000-05-26 | 2001-11-29 | Thermal Energy Accumulator Products Pty Ltd | A multiple-use super-efficient heating and cooling system |
| US7356997B2 (en) * | 2002-05-29 | 2008-04-15 | Gruber Duane A | Chilled water storage for milk cooling process |
| JP2007071519A (en) * | 2005-09-09 | 2007-03-22 | Sanden Corp | Cooling system |
-
2008
- 2008-11-14 CA CA2705253A patent/CA2705253A1/en not_active Abandoned
- 2008-11-14 AU AU2008322843A patent/AU2008322843B2/en not_active Ceased
- 2008-11-14 US US12/742,674 patent/US20100275645A1/en not_active Abandoned
- 2008-11-14 WO PCT/EP2008/065562 patent/WO2009063055A1/en active Application Filing
- 2008-11-14 CN CN2008801199439A patent/CN101896780A/en active Pending
- 2008-11-14 EA EA201000802A patent/EA201000802A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| AU2008322843B2 (en) | 2011-11-10 |
| EA201000802A1 (en) | 2010-12-30 |
| WO2009063055A1 (en) | 2009-05-22 |
| AU2008322843A1 (en) | 2009-05-22 |
| US20100275645A1 (en) | 2010-11-04 |
| CN101896780A (en) | 2010-11-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| AU2008322843B2 (en) | A method and apparatus for cooling a process stream | |
| US11815283B2 (en) | Using liquid to air membrane energy exchanger for liquid cooling | |
| US6324867B1 (en) | Process and system for liquefying natural gas | |
| AU2009237550A1 (en) | Evaporative cooling tower enhancement through cooling recovery | |
| JP2007303759A (en) | Operation control method of ice thermal storage system | |
| Shanmugam et al. | An ultra-low ammonia charge system for industrial refrigeration | |
| JP5246891B2 (en) | Heat pump system | |
| US20130027879A1 (en) | Method for regulating a cooling system | |
| CN110608492B (en) | Precooling evaporative condensing air conditioning system and control method thereof | |
| JP6319902B2 (en) | Ice rink cooling equipment and cooling method | |
| KR20130065255A (en) | Natural gas liquefaction system | |
| JPWO2017051532A1 (en) | Cooling system and cooling method | |
| KR102660791B1 (en) | Ice making apparatus using waste ice water | |
| US20240230176A9 (en) | Closed loop chiller system having single pass recycled water loop | |
| AU2017341387B2 (en) | System for treating and cooling a hydrocarbon stream | |
| JP2602982B2 (en) | Cooling system | |
| JP2006153373A (en) | Cooling device | |
| AU2013203082A1 (en) | Method and system for utilising waste heat generated from the processing of natural gas to produce liquefied natural gas | |
| JP2024532517A (en) | Apparatus and method for filling pressurized gas tanks | |
| CN117329763A (en) | Air separation nitrogen water precooling system and precooling method thereof | |
| CN102466390A (en) | Nitrogen yield increasing method for use in air separation unit | |
| LePree | Just Cool It! | |
| JPWO2017164201A1 (en) | COOLING SYSTEM AND COOLING SYSTEM CONTROL METHOD | |
| JPH06185855A (en) | Cooling method for raw air | |
| JPH05332498A (en) | Holding of internal pressure in liquid helium storing tank in transfer of liquid helium and device therefor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |
Effective date: 20131114 |