Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28B—STEAM OR VAPOUR CONDENSERS
  • F28B9/00—Auxiliary systems, arrangements, or devices
  • F28B9/04—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid
  • F28B9/06—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid with provision for re-cooling the cooling water or other cooling liquid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
  • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
  • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
  • F28F2250/06—Derivation channels, e.g. bypass

Definitions

• the present invention relates to a method for providing a cooling medium with a regulated flow temperature in a secondary circuit, wherein the cooling medium in the secondary circuit receives heat from one or more process coolers and then gives off heat to primary water in a primary circuit before it again flows to the process coolers. Furthermore, the invention relates to a device for carrying out the method according to the invention, wherein the device comprises one or more process coolers in the secondary circuit and at least one temperature sensor in the flow to the process coolers.
• the cooling medium in the secondary circuit flows with a certain flow temperature into one or more process coolers and absorbs heat from the process, where it heats up. In order to bring the cooling medium back to the desired flow temperature, it is fed to one or more heat exchangers, in which it is cooled by primary water.
• the cycle of primary water such as recooling water, river water or
• Seawater is called the primary cycle. Accordingly, the heat exchangers in which the cooling medium is cooled by the primary water, called the primary heat exchanger.
• the division of the cooling into a primary circuit through which a primary water flows and a secondary circuit through which a cooling medium flows is an established technique and offers several advantages. In the case of a leak on an apparatus or a process cooler, harmful substances may possibly enter the cooling medium, but the primary water in the primary circuit is spared from contamination. On the other hand, because the secondary circuit is closed, the process coolers in the system pollute less than, for example, direct cooling with river water.
• the primary heat exchangers are usually designed with regard to number and dimensioning in such a way that they can extract enough heat from the cooling medium in the event of high load.
• the high load case a state is assumed in which the temperature difference between the entering into the heat exchanger cooling medium and the incoming primary water has a certain minimum allowable value. For a given value for the incoming cooling medium, this results in a maximum permissible value for the incoming primary water.
• the high load case is therefore usually given in the summer months, in which river water can reach, for example, temperatures of 28 ° C or more.
• a reduced load case when the temperature difference between cooling medium entering the primary heat exchangers and entering primary water assumes large values. In Central Europe, this occurs usually in the winter months, when the temperature of river water can drop to levels of 4 ° C or below, for example. Furthermore, it is spoken of a reduced load case, when only little heat from the cooling medium in the secondary circuit must be transferred to the primary water, for example, when a system is not operated at maximum capacity or is completely turned off, so that less heat from the cooling medium to the primary water in the primary cooler is transmitted. In these cases, keeping the flow temperature of the cooling medium to the process coolers at the same value as in the case of high load, less primary water is required, so that usually the flow rate of primary water is reduced to the primary heat exchangers.
• the cooling medium in the secondary circuit of one or more process coolers absorbs heat and then gives off heat to primary water in a primary circuit before it flows back to the process coolers.
• a bypass line for bypassing the primary heat exchanger branches off in the secondary circuit. The bypass line opens into the Conduction of the secondary circuit from the primary heat exchangers to the process coolers.
• supply temperature is understood here and below to mean the temperature in the secondary circuit in the flow to the process coolers.
• "Supply to the process coolers” is the section of the secondary circuit which is located between the inlet of the bypass line into the secondary circuit and the first process heat exchanger
• “Overrun” refers to the section of the secondary circuit between the outlet of the at least one process heat exchanger and the branch of the by-pass line Outlet lines from the process heat exchangers and the bypass of the bypass line is located.
• a temperature sensor is in the flow to the process coolers, and the bypass line is provided with an actuator, by means of which the flow temperature to the process coolers in the secondary circuit can be controlled. It is also possible to provide a plurality of temperature sensors in the flow to the process coolers, for example to realize a redundant measurement. Suitable temperature sensors, for example thermocouples, detect the temperature of the flowing cooling medium and provide a value for forwarding to a control device.
• a temperature sensor or are several temperature sensors in the wake of the secondary circuit there is a temperature sensor or are several temperature sensors in the wake of the secondary circuit, and the bypass line is provided with an actuator by means of which the flow temperature to the process coolers in the secondary circuit is controlled.
• Suitable actuators make it possible to set the flow through the bypass line between a minimum value and a maximum value.
• the minimum value is zero, which means a completely closed bypass line.
• the maximum value preferably corresponds to a completely open bypass line. Any values for the flow can be set between the extreme values, preferably steplessly continuously.
• Suitable actuators are known to the person skilled in the art, e.g. Flaps, ball valves or three-way valves.
• a control device which has a setpoint for the flow temperature. From a comparison of the setpoint with the detected by the temperature sensor flow temperature, the control device generates an output signal for forwarding to the actuator.
• the temperature of the cooling medium flowing through the bypass line is higher than the temperature of the cooling medium flowing from the primary heat exchangers to the process coolers.
• the regulation therefore provides for the current through the bypass line to be reduced in the event of a flow temperature that is too high in comparison with the setpoint value and accordingly to increase the flow through the bypass line when the flow temperature is too low compared to the setpoint value.
• a control device is provided which has a setpoint for the follow-up temperature.
• the control device From a comparison of the setpoint with the detected by the temperature sensor follow-up temperature, the control device generates an output signal for forwarding to the actuator.
• the control provides for the current through the bypass line to be reduced when the overrun temperature is too high compared to the setpoint value, and the current through the bypass line to be increased accordingly when the setpoint temperature is too low compared to the setpoint value.
• the flow of the cooling medium through the bypass line can also be influenced by the fact that actuators are present in the cooling medium lines to the primary heat exchangers or from the primary heat exchangers and adjusted in their degrees of opening.
• a regulation of the bypass current by influencing an actuator in the bypass line is easier to implement and is therefore preferred.
• the control device may be an independent device, such as a compact controller, which is connected in terms of information technology with the temperature sensor and the actuator.
• the control device can also be realized in combination with the actuator, for example in the form of a control valve.
• the control device can also be integrated in a higher-level system for process control, for example in a process control system.
• the primary heat exchangers are designed with regard to number and dimensioning to a high load case.
• the cooling capacity of the primary circuit is adjusted by switching off one or more of the primary heat exchangers, whereby at least one primary heat exchanger remains in operation.
• high load case and low load case are understood to mean operating states as defined above.
• the primary heat exchangers are designed such that in a reduced load, a heat exchanger is sufficient to cool the cooling medium to the desired flow temperature by utilizing a maximum allowable temperature difference between primary water inlet and outlet.
• a heat exchanger is provided, which are preferably also individually designed for the maximum permissible temperature difference between primary water inlet and outlet, and are in total suitable for the minimum temperature difference in the high load case.
• the maximum permissible temperature difference between primary water inlet and outlet is often prescribed by the authorities, for example to a value of 15 K.
• the bypass line is preferably designed in terms of their capacity such that the control range of the bypass line is sufficient to control the flow temperature in the secondary circuit bumplessly when switching off and the connection of a primary heat exchanger.
• the design of the bypass line is further preferably considered that daytime fluctuations in the primary water temperature can be compensated solely by regulating the flow through the bypass line. A connection or disconnection of primary heat exchangers is not provided for this case.
• the flow of primary water through the primary heat exchanger or is kept substantially constant.
• the flow is not actively regulated, but results from the pressure difference between the primary water side inlet and the outlet of the primary heat exchanger. With fluctuations of this pressure difference also arise
• the capacity adjustment is made by switching on or off of primary heat exchangers such that the pressure drop of the primary water when flowing through the primary heat exchanger in operation in each case at least 300 mbar, more preferably at least 800 mbar.
• the at least two primary heat exchangers can be interconnected in different ways.
• the primary heat exchangers are preferably connected in parallel both on the side of the primary circuit and on the side of the secondary circuit. All heat exchangers known to the person skilled in the art for this purpose can be used as the primary heat exchanger, preferably plate heat exchangers or tube bundle heat exchangers are used, particularly preferably sealed or welded plate heat exchangers.
• the most preferred plate heat exchangers are usually designed for a high pressure loss. This is advantageous if the bypass is to be realized without additional conveying devices such as pumps.
• the primary water is recooling water, river water, sea water or brackish water.
• “Recooling water” is understood to mean water that has been cooled by a device such as a cooling tower or a recooling plant in process engineering plants.
• the invention offers several advantages.
• the provision of at least two primary heat exchangers working together in the High load case provide the required cooling capacity, but in partial load can be partially shut down, makes it possible to operate the individual primary heat exchanger with almost constant flow on the primary water side, which prevents premature fouling.
• this offers the possibility, in the case of reduced load, the primary heat exchanger alternately on and off, which allows easy inspection and possibly maintenance or cleaning.
• the minimum amount of primary water required to provide the cooling capacity is significantly reduced.
• Another advantage is the fact that a control of the flow temperature by means of the bypass flow is much easier, faster and more robust to accomplish than a regulation on the flow rate of primary water, as practiced in the prior art.
• Fig. 1 Schematic diagram of a cooling system according to the prior art
• FIG. 2 shows a schematic diagram of a cooling system according to the invention
• FIG. 3 shows a schematic diagram of a cooling system according to the invention with secondary-side series connection of the primary heat exchanger
• FIG. 4 shows a schematic diagram of a cooling system according to the invention with primary side flexible interconnection of the primary heat exchanger
• Fig. 5 Time course of the primary water temperature and the number of primary heat exchangers in operation
• FIG. 1 shows a cooling system according to the prior art in which a cooling medium flows to process coolers 22 in a secondary circuit 20, absorbs heat there and gives off heat to primary water in a primary circuit 10 in a primary heat exchanger 12, before it flows back to the process coolers 22.
• the process coolers can be of different designs, for example plate, tube bundle, spiral heat exchangers or casings of tubes or containers for their cooling.
• the flow temperature of the cooling medium before the process coolers 22 is detected by means of a temperature sensor and regulated by a control device 24 to a specific setpoint.
• the amount of primary water in the primary circuit 10 acts as a control variable for the control.
• FIG. 2 shows a first preferred embodiment of the method according to the invention.
• the cooling medium leaving the process cooler 22 is passed through two primary heat exchangers 12, 14, where it gives off heat to primary water in a primary circuit 10.
• the primary heat exchangers are connected in parallel both on the side of the primary circuit and on the side of the secondary circuit.
• 14 branches off a bypass line 26, which opens after the exit of the cooling medium from the primary heat exchangers back into the secondary circuit 20.
• the control 24 of the flow temperature tur of the cooling medium to the process coolers 22 via the adjustment of the current in the bypass line.
• both primary heat exchangers 12 and 14 are in operation, while in the low load case, the capacity of a primary heat exchanger is sufficient to sufficiently cool the cooling medium in the secondary circuit 20. In this case, one of the primary heat exchangers is switched off by closing the corresponding valves in the secondary circuit.
• FIG. 3 shows a further preferred embodiment of the method according to the invention.
• the primary heat exchangers 12 and 14 are connected in parallel by the primary circuit and in series by the secondary circuit.
• bypasses are provided in the secondary circuit which can be switched on and off via valves.
• FIG 4 shows a further preferred embodiment of the method according to the invention, in which the primary heat exchangers 12, 14 are connected in parallel on the secondary side.
• the interconnection is kept flexible.
• the primary heat exchangers 12, 14 can be switched off alternately by closing the corresponding valves in the secondary circuit.
• the illustrations are for illustration only. Of the representations deviating configurations and interconnections are of course also fall under the invention falling, as long as the regulation of the flow temperature in the secondary circuit is done by adjusting the bypass current.
• the number of heat exchangers shown in the figures is merely exemplary and not limited thereto. It is advantageous if more than two primary heat exchangers are present. The more primary heat exchangers are available, the more flexible it is possible to switch on and off individual primary heat exchangers in order to optimally match the currently available load case. On the other hand, this also increases the investment costs. Preferably, two to three primary heat exchangers are provided.
• a selection criterion for the number of primary heat exchangers can be derived from the temperature gradients of the primary water.
• the optimum number of primary heat exchangers is estimated by the quotient of the maximum permissible temperature difference and the typical temperature difference in the case of high load. For example, for the location Ludwigshafen am Rhein, Germany, the maximum allowable temperature difference between primary water entry and exit is 15 K when using river water as primary water. In addition, the water returned to the river must not exceed 33 ° C. In high load case in the summer months, in which the river water
• FIG. 5 schematically shows the time profile of the primary water temperature T (dashed curve) and the number of primary heat exchangers N in operation (solid lines, right-hand scale) over a period of 12 months.
• T dashed curve
• N the number of primary heat exchangers N in operation
• the primary water used is river water, which has the lowest temperature in the winter months of December and January, eg 4 ° C.
• the maximum permissible temperature difference can be fully exploited, so that a primary heat exchanger is sufficient to sufficiently cool the cooling medium in the secondary circuit.
• another primary heat exchanger is put into operation. Assuming a fluctuation range of 3 K and a maximum value of 33 ° C for the water discharged into the flow, this results in a value of 15 ° C, from which the second primary heat exchanger is put into operation. In the example according to FIG. 5 this is the case in the middle of April.
• the temperature of the river water rises to a level above which the third primary heat exchanger becomes necessary in order reliably to dissipate the required amount of heat and not to exceed the maximum value of 33 ° C.
• three primary heat exchangers are in operation until the river water temperature has fallen again enough that two primary heat exchangers are sufficient, in the example at the beginning of September.
• the river water temperature has dropped even further, eg below 15 ° C, so that once again a primary heat exchanger is sufficient.
• the method according to the invention causes flexible cooling capacities to be made available adapted to the current needs.
• a primary heat exchanger for a period of five and a half months, two primary heat exchangers and for a period of three months, three primary heat exchangers in operation.
• the required amount of primary water On the primary water side, each primary heat exchanger flows through a substantially constant amount of water, which prevents soiling and fouling. Except in the summer months, the heat exchangers that are currently not in operation can be easily maintained and cleaned without affecting the operation of the systems in the secondary circuit.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Motor Or Generator Cooling System (AREA)

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• 2013
  • 2013-04-23 IN IN8409DEN2014 patent/IN2014DN08409A/en unknown
  • 2013-04-23 EP EP13720299.0A patent/EP2841869B1/de active Active
  • 2013-04-23 KR KR1020147032536A patent/KR20150003848A/ko not_active Application Discontinuation
  • 2013-04-23 CN CN201380022036.3A patent/CN104246418A/zh active Pending
  • 2013-04-23 ES ES13720299T patent/ES2704988T3/es active Active
  • 2013-04-23 JP JP2015507499A patent/JP2015514957A/ja active Pending
  • 2013-04-23 WO PCT/EP2013/058377 patent/WO2013160293A1/de active Application Filing

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