CA1070669A - Process and apparatus for the cyclic heating and cooling of processing equipment - Google Patents
Process and apparatus for the cyclic heating and cooling of processing equipmentInfo
- Publication number
- CA1070669A CA1070669A CA277,753A CA277753A CA1070669A CA 1070669 A CA1070669 A CA 1070669A CA 277753 A CA277753 A CA 277753A CA 1070669 A CA1070669 A CA 1070669A
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- Canada
- Prior art keywords
- heat transfer
- transfer fluid
- user equipment
- zone
- heating
- Prior art date
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- Expired
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/34—Heating or cooling presses or parts thereof
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
- Physical Or Chemical Processes And Apparatus (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Moulds For Moulding Plastics Or The Like (AREA)
- Thermotherapy And Cooling Therapy Devices (AREA)
- Lining Or Joining Of Plastics Or The Like (AREA)
- Casting Or Compression Moulding Of Plastics Or The Like (AREA)
Abstract
LE?
P/2?
PROCESS AND APPARATUS FOR THE
CYCLIC HEATING AND COOLING OF PROCESSING
EQUIPMENT
Abstract of the Disclosure There is disclosed a process and apparatus for the cyclic heating and cooling of processing equipment with a pressurized heat transfer fluid, i. e., water, utilizing heat exchangers for the separate heating and cooling of the heat transfer fluid and including a heat recovery vessel having at least two heat transfer zones wherein heat transfer fluid is stored in such vessels during initial phases of one cycle for use in a subsequent cycle whereby heat transfer fluid at an intermediate temperature level in one zone is passed through such processing equipment prior to the passage of heated or cooled heat transfer fluid through such processing equip-ment from one of such heat exchangers.
P/2?
PROCESS AND APPARATUS FOR THE
CYCLIC HEATING AND COOLING OF PROCESSING
EQUIPMENT
Abstract of the Disclosure There is disclosed a process and apparatus for the cyclic heating and cooling of processing equipment with a pressurized heat transfer fluid, i. e., water, utilizing heat exchangers for the separate heating and cooling of the heat transfer fluid and including a heat recovery vessel having at least two heat transfer zones wherein heat transfer fluid is stored in such vessels during initial phases of one cycle for use in a subsequent cycle whereby heat transfer fluid at an intermediate temperature level in one zone is passed through such processing equipment prior to the passage of heated or cooled heat transfer fluid through such processing equip-ment from one of such heat exchangers.
Description
~07066~
This invention relates to a process and apparatus for heating and cooling processing equipment, and more particularly to a process and apparatus for the cyclic heating and cooling of ; processing equipment utilizing pressurized water as the heat transfer fluid.
In processing equlpment, such as platen presses for pro-ducing decorative melamine and formaldehyde laminates, requiring alternate heating and cooling modes, most of the energy require-ments are for heating and processing equipment rather than heating the material being processed. Furthermore, the alternate heating and cooling of such a heat transfer fluid adds substantially to the energy requirements of the process.
Early efforts to conserve heat were relatively simple. For example, at the end of a heating cycle, the hot fluid was set aside for use in heat-up of the next heating cycle and in like manner, at the end of a cooling cycle, the cold fluid was set aside and stored for use in cool-down at the start of a subsequent cooling cycle. This was facilely accomplished with an unpressurized water by use of separate vessels for the hot and cold fluid, however, w~th a pressurized water, the same vessels must be used, alternating hot and cold fluids and thereby introducing inefficien-cies as a result of cross mixing.
~k -1- ~
~170669 In U. S. Patent 3,109,486, there is disclosed a system including a "regenerative" section which contained relatively cooler water during the heating cycle which, on the start of a cooling cycle, is pumped through a heat exchanger for further S cooling and thence through the processing equipment wherein heat is exchanged by the fluid wile cooling the equipment. The fluid is then returned to the regenerative section. When the water temperature leaving the processing equipment becomes too low to be economically stored, the regenerative section is then by-passed.
Thus, at the end of the cooling cycle, the regenerative section contains hot water originally in the piping and equipment plus some additional water which has first been cooled and then reheated in cooling equipment. The cycle is similar on heating, except that re1atively warmer water in the regenerative section is upwardly displaced into the main section of the accumulator with the hottest water from the accumulator being circulated through the press, cooled and returned to the regenerative section.
The heat saved during a heating cycle is readily calculated by multiplying the mass of high pressure water in the regenerative sect1on by the specific heat and the temperature difference between the start and finish of the heating cycle. The efficiency is adversely affected by using hottest water at the beginning of a heating cycle and cooling water before introduction during a cool-ing cycle, i.e., inefficiences result by using heat or cooled water over large temperatures.
,. ~ .
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.. . . ; , .
~07066 ~9 Various other objects and advantages of the present invention will become apparent from the following detailed des-cription of an exemplary embodiment thereof with the novel features thereof being particularly pointed out in the appended claims.
In accordance with the present invention, there is provided for processing equipment to be heated and cooled, heat exchangers for separately heating and cooling pressurized water, i.e., water under a pressure of at least about 30 psig, and including a heat recovery vessel having at least two heat transfer zones or at least two heat recovery vessels wherein pressurized water is stored in such zones during initial phases of one cycle for use during initial phases of a subsequent cycle whereby heat transfer fluid at an intermediate temperature level in one of such zones is passed through the processing equipment prior to the passage through such processing equipment of heated or cooled pressurized water from one of such heat exchanger, as more clearly hereinafter disclosed. In accordance with my invention, the efficiency of heat recovery is substantially improved (40 to 45%) by such two stage change of water whereby water in the processing equLpment is first displaced by tempered water from a first vessel and then replacing the tempered water after ex-changing heat with the equipment, with water which is fully heated or cooled with such tempered water being stored in a second vessel, as distinguished from no recovery system, and substantially im-proves the effectiveness (at least about 100%) as compared with a recovery system, such as disclosed in the hereinabove mentioned Hanson reference.
In exchanging heat with the process equipment, the tempered water can be heated to a higher temperature while cooling the equipment and cooled to a lower temperature in heating the equip-ment than could fully heated or fully cooled water. Since the quantity of heat recovered varies with the difference between the two final temperatures, heat is more efficiently recovered.
The volume of each of the heat transfer zones is generally between 75 to 125 percent, preferably substantially about equal to the volume of heat transfer conduits within the processing equipment and the volume of conduits to and from such processing equipment.
Description of the Drawing _ _ _ _ _ _ .
The invention will be more clearly understood by reference to the following detailed description of the preferred embodiment thereof when taken in conjunction with the accompanying drawing wherein:
Figure l is a schematic flow diagram thereof; and Figure 2 is a schematic cross section of a heat recovery vessel.
Detailed Description of the Invention Referring now to Figure l, the process and apparatus for heating and cooling processing equipment includes user equipment, generally indicated as lO, such as platen press for decorative laminated a pump ll, heat recovery vessel 12, hot accumulator tank 13 and a cooler 14. The user equipment lO is connected to the discharge side of the pump ll by a conduit 15 with the suction side of the pump 11 being connected to a conduit 16. The down-stream side of the user equipment 10 is connected to a conduit 17. The outlet of the hot accumulator tank 13 is connected by a conduit 18 to the conduit 16 with the inlet to the hot acumula-. 5 tor tank 13 being connected to a conduit 19 under the control of valve 20.
The heat recovery vessel 12 includes upper and lower heat transfer zones 21 and 22, respectively, and is provided with ;` upper, intermediate and lower conduits 23, 24 and 25, respectively.
. 10 The upper conduit 23 of the heat recovery vessel 12 is connected to the conduit 19, and to a conduit 26 under the control of valve 27 with conduit 26 being connected to a conduit 28 under the control of valve 29. The intermediate conduit 24 of the heat recovery vessel 12 is connected to a conduit 42 under the control , 15 of valve 30 and to a conduit 31 under the control of valve 32, with conduit 42 being connected by a conduit 33 in fluid communicationwith the downstream side of the cooler 14 and with nduit 31 being connected by conduit 34 to the conduit 17.
The lower conduit 25 of the heat recovery vessel 12 is connected to conduits 35 and 36 under the control of valves 37 and 38, respectively. The conduit 35 is connected to the conduit 34 with conduit 36 being in fluid communication with the inlet side of the cooler 14. The conduits 42 and 33 are joined to a conduit 39 which is connected to conduit 28. The conduits 28 and 39 are connected by a conduit 40 to the conduit 16.
In operation, assuming initiation of a heating cycle in tempered water has been previously stored in the lower heat trans-fer zone 22 of the vessel 12, in a first stage of heating cycle, . the suction side of the pump 11 is placed in fluid communication - 5 with the upper portion of the lower heat transfer zone 22 of theheat recovery vessel 12 via conduits 24, 42, 39, 40 and 16 by opening the valve 30. The discharge side of the pump 11 is in . fluid communication with the user equipment 10 by the conduit : 15 with the downstream side of the user equipment being in fluid communication with the lower portion of the lower heat transfer ' zone 22 of the heat recovery vessel 12 via conduits 17, 34, 35 and 25 by opening valve 37 whereby tempered water in the upper portion of the vessel 12 is caused to be displaced by cooler water flowing upwardly within the heat recovery vessel 12 since the user equipment had been operating within final stages of i the cooling cycle. The valves 20, 27, 29 and 32 being closed.
'. As hereinabove mentioned, the volume of the heat transfer zones 21 and 22 is between 75 to 125 percent, preferably substan-tially about equal to the volume of the heat transfer conduits within the user equipm~nt 10 and the conduits to and from such user equipment. Thus after a corresponding valumetric replace-ment, the valve 37 is closed and the valves 20 and 32 are opened to permit initiation of a second stage of the heating cycle whereby hot water from the accumulator tank 13 is introduced via conduits 18, 16, and 15 into the user equipment 10.
:
:` :
Tempered cold water is withdrawn from user equipment 10 via conduits 17, 34, 31 and 24 and is introduced into the inter-mediate portion of the heat recovery vessel 12 to displace upwardly into the accumulator tank 13 hot water from the upper heat transfer zone 21 of the heat recovery vessel 12. Second stage heating is effected for a time sufficient to volumetric similarly substantially replace the pressurized water in the heat transfer conduits of the user equipment as well as the associated conduits.
!, It will be appreciated that heat-up times are improved by passing the water stored in upper heat transfer zone 21 of the vessl 12 to hot accumulator tank 13 vice passage through the user equipment 10 .
The final stage of the heating cycle is effected by closing valve 32 and opening valve 27 and gradually opening valve 29 whereby hot heat transfer fluid is withdrawn from the accumulator tank 13 by conduit 18 and combined in conduit 16 with recirculating heat transfer medium in conduit 40 and introduced by conduit 15 into user equipment 10. The heat transfer fluid withdrawn from the user equipment 10 in conduit 17 is split with a portion being passed to hot accumulator tank 13 by conduits 26 and 19 with the remaining portion by-passing accumulator tank 13 by being passed by conduit 28 to conduit 40 as the recirculating heat transfer fluid. The amount of heat transfer fluid by-passing the hot accumulator tank 13 is nominal, if any, at initiation of the final heating stage and is increased as the desired temperature level is reached with concomitant reductions in the flow of fluid from accumulator tank 13.
After a time period determined by the capabilities of the user equipment 10 with regard to the materials being treated, the heating cycle is stopped and first stage of the cooling cycle is initiated. Accordingly, valves 20 and 29 are closed and valve 30 is opened to permit hot heat transfer fluid from the user equip-ment 10 to be introduced by conduits 17, 26, and 23 into the upper portion of the heat recovery zone 21 of the heat recovery vessel 12 to displace downwardly thereby tempered cold heat transfer fluid therein, such displaced fluid being passed to the user equipment 10 by conduits 24, 42, 39, 40, 16 and 15.
As hereinabove discussed with respect to first.and second stages of the heating cycle, after a volume of heat transfer fluid is displaced generally equal to from 75 to 125 percent, preferably substantially equal to the volume of fluid in the user equipment 10 and related conduits, the second stage of the cooling cycle is initiated by closing valves 27 and 30 and by opening valves 32 and 38. Cooled heat transfer fluid is passed by conduit 33, 39, 40, 16 and 15 to user equipment 10 with tempered hot fluid introduced into the intermediate portion of heat recovery vessel 12 by con~
duits 17, 34, 31 and 24 to downwardly displace in the lower heat transfer zone 22 therein cold water which is passed to cooler 14 by conduits 25 and 36.
After a similar volumetric change, the final stage of the cooling cycle is effected by closing valve 32 and opening valve 37 whereby cooled heat transfer fluid continues to be passed to : - `
iO7~669 user equipment 10 from cooler 14 by conduits 33, 39, 40, 16 and 15 with tempered heat transfer fluid being returned to cooler 14 by conduits 17, 34, 35 and 36. During such final cooling stage valve 29 is caused to be gradually opened to effect a by-pass of a portion of the heat transfer to the cooler 14 as the user equipment reaches its lower design temperature. The by-passed fluid is passed from conduit 17 to conduit 40 by line 28 under the control value 29. The amount of fluid by-passing the cooler 14 is increased as such final design temperature is reached.
After a time period similarly dictated by process requirements, the cooling cycle is discontinued and the heating cycle initiated as hereinabove discussed.
As will be appreciated by one skilled in the art, when introducing a hot heat transfer fluid into a heat transfer zone, the hot fluid is into the upper portion thereof to thereby down-wardly displace relatively cooler heat transfer fluid whereas when introducing cool heat transfer fluid into a transfer zone of the heat recovery vessel, the cooled fluid is introduced into the lower portion thereof to thereby upwardly displace warmer water. It will be further appreciated by one skilled in the art that mixing in the heat recovery vessels of the heat transfer medium at various temperature levels durihg fluid should be minimized.
While the hereinabove description describes a heat re-covery vessel having two zones separated by baffles (illustrated by the dotted lines), it will be appreciated that a separate vessel may be employed for each zone, such as illustrated in Figure 2.
The invention has been described with reference to the use of pressurized water as the heat transfer fluid, however, it will be appreciated that other heat transfer fluids may be used. The use of another heat transfer fluid is not contemplated except for a use requiring large temperature range, since such use is inefficient requiring extra volumes of fluid to the system as a result of the specific heat of such heat transfer fluids.
Example of the Invention A 5'x12' platen press having 22 openings is operated with a heat requirement of 10.84 x 106 B.T.U. per cycle within a temperature range of from 90 to 290 F. Use of the process and apparatus of the present invention reduces heat requirements to 6.44 x 10 B.T.U. per cycle as compared to estimated heat requirements of 8.8 B.T.U. per cycle for a system like the one disclosed in the hereinabove mentioned Hanson patent. Savings in energy requirements in the first year are greater than the additional equipment costs to effect such efficiencies.
While not fully illulstrated, the valving arrangement includes automatic on-off and modulating valves in combination to minimize valve requirements.
This invention relates to a process and apparatus for heating and cooling processing equipment, and more particularly to a process and apparatus for the cyclic heating and cooling of ; processing equipment utilizing pressurized water as the heat transfer fluid.
In processing equlpment, such as platen presses for pro-ducing decorative melamine and formaldehyde laminates, requiring alternate heating and cooling modes, most of the energy require-ments are for heating and processing equipment rather than heating the material being processed. Furthermore, the alternate heating and cooling of such a heat transfer fluid adds substantially to the energy requirements of the process.
Early efforts to conserve heat were relatively simple. For example, at the end of a heating cycle, the hot fluid was set aside for use in heat-up of the next heating cycle and in like manner, at the end of a cooling cycle, the cold fluid was set aside and stored for use in cool-down at the start of a subsequent cooling cycle. This was facilely accomplished with an unpressurized water by use of separate vessels for the hot and cold fluid, however, w~th a pressurized water, the same vessels must be used, alternating hot and cold fluids and thereby introducing inefficien-cies as a result of cross mixing.
~k -1- ~
~170669 In U. S. Patent 3,109,486, there is disclosed a system including a "regenerative" section which contained relatively cooler water during the heating cycle which, on the start of a cooling cycle, is pumped through a heat exchanger for further S cooling and thence through the processing equipment wherein heat is exchanged by the fluid wile cooling the equipment. The fluid is then returned to the regenerative section. When the water temperature leaving the processing equipment becomes too low to be economically stored, the regenerative section is then by-passed.
Thus, at the end of the cooling cycle, the regenerative section contains hot water originally in the piping and equipment plus some additional water which has first been cooled and then reheated in cooling equipment. The cycle is similar on heating, except that re1atively warmer water in the regenerative section is upwardly displaced into the main section of the accumulator with the hottest water from the accumulator being circulated through the press, cooled and returned to the regenerative section.
The heat saved during a heating cycle is readily calculated by multiplying the mass of high pressure water in the regenerative sect1on by the specific heat and the temperature difference between the start and finish of the heating cycle. The efficiency is adversely affected by using hottest water at the beginning of a heating cycle and cooling water before introduction during a cool-ing cycle, i.e., inefficiences result by using heat or cooled water over large temperatures.
,. ~ .
..
.. . . ; , .
~07066 ~9 Various other objects and advantages of the present invention will become apparent from the following detailed des-cription of an exemplary embodiment thereof with the novel features thereof being particularly pointed out in the appended claims.
In accordance with the present invention, there is provided for processing equipment to be heated and cooled, heat exchangers for separately heating and cooling pressurized water, i.e., water under a pressure of at least about 30 psig, and including a heat recovery vessel having at least two heat transfer zones or at least two heat recovery vessels wherein pressurized water is stored in such zones during initial phases of one cycle for use during initial phases of a subsequent cycle whereby heat transfer fluid at an intermediate temperature level in one of such zones is passed through the processing equipment prior to the passage through such processing equipment of heated or cooled pressurized water from one of such heat exchanger, as more clearly hereinafter disclosed. In accordance with my invention, the efficiency of heat recovery is substantially improved (40 to 45%) by such two stage change of water whereby water in the processing equLpment is first displaced by tempered water from a first vessel and then replacing the tempered water after ex-changing heat with the equipment, with water which is fully heated or cooled with such tempered water being stored in a second vessel, as distinguished from no recovery system, and substantially im-proves the effectiveness (at least about 100%) as compared with a recovery system, such as disclosed in the hereinabove mentioned Hanson reference.
In exchanging heat with the process equipment, the tempered water can be heated to a higher temperature while cooling the equipment and cooled to a lower temperature in heating the equip-ment than could fully heated or fully cooled water. Since the quantity of heat recovered varies with the difference between the two final temperatures, heat is more efficiently recovered.
The volume of each of the heat transfer zones is generally between 75 to 125 percent, preferably substantially about equal to the volume of heat transfer conduits within the processing equipment and the volume of conduits to and from such processing equipment.
Description of the Drawing _ _ _ _ _ _ .
The invention will be more clearly understood by reference to the following detailed description of the preferred embodiment thereof when taken in conjunction with the accompanying drawing wherein:
Figure l is a schematic flow diagram thereof; and Figure 2 is a schematic cross section of a heat recovery vessel.
Detailed Description of the Invention Referring now to Figure l, the process and apparatus for heating and cooling processing equipment includes user equipment, generally indicated as lO, such as platen press for decorative laminated a pump ll, heat recovery vessel 12, hot accumulator tank 13 and a cooler 14. The user equipment lO is connected to the discharge side of the pump ll by a conduit 15 with the suction side of the pump 11 being connected to a conduit 16. The down-stream side of the user equipment 10 is connected to a conduit 17. The outlet of the hot accumulator tank 13 is connected by a conduit 18 to the conduit 16 with the inlet to the hot acumula-. 5 tor tank 13 being connected to a conduit 19 under the control of valve 20.
The heat recovery vessel 12 includes upper and lower heat transfer zones 21 and 22, respectively, and is provided with ;` upper, intermediate and lower conduits 23, 24 and 25, respectively.
. 10 The upper conduit 23 of the heat recovery vessel 12 is connected to the conduit 19, and to a conduit 26 under the control of valve 27 with conduit 26 being connected to a conduit 28 under the control of valve 29. The intermediate conduit 24 of the heat recovery vessel 12 is connected to a conduit 42 under the control , 15 of valve 30 and to a conduit 31 under the control of valve 32, with conduit 42 being connected by a conduit 33 in fluid communicationwith the downstream side of the cooler 14 and with nduit 31 being connected by conduit 34 to the conduit 17.
The lower conduit 25 of the heat recovery vessel 12 is connected to conduits 35 and 36 under the control of valves 37 and 38, respectively. The conduit 35 is connected to the conduit 34 with conduit 36 being in fluid communication with the inlet side of the cooler 14. The conduits 42 and 33 are joined to a conduit 39 which is connected to conduit 28. The conduits 28 and 39 are connected by a conduit 40 to the conduit 16.
In operation, assuming initiation of a heating cycle in tempered water has been previously stored in the lower heat trans-fer zone 22 of the vessel 12, in a first stage of heating cycle, . the suction side of the pump 11 is placed in fluid communication - 5 with the upper portion of the lower heat transfer zone 22 of theheat recovery vessel 12 via conduits 24, 42, 39, 40 and 16 by opening the valve 30. The discharge side of the pump 11 is in . fluid communication with the user equipment 10 by the conduit : 15 with the downstream side of the user equipment being in fluid communication with the lower portion of the lower heat transfer ' zone 22 of the heat recovery vessel 12 via conduits 17, 34, 35 and 25 by opening valve 37 whereby tempered water in the upper portion of the vessel 12 is caused to be displaced by cooler water flowing upwardly within the heat recovery vessel 12 since the user equipment had been operating within final stages of i the cooling cycle. The valves 20, 27, 29 and 32 being closed.
'. As hereinabove mentioned, the volume of the heat transfer zones 21 and 22 is between 75 to 125 percent, preferably substan-tially about equal to the volume of the heat transfer conduits within the user equipm~nt 10 and the conduits to and from such user equipment. Thus after a corresponding valumetric replace-ment, the valve 37 is closed and the valves 20 and 32 are opened to permit initiation of a second stage of the heating cycle whereby hot water from the accumulator tank 13 is introduced via conduits 18, 16, and 15 into the user equipment 10.
:
:` :
Tempered cold water is withdrawn from user equipment 10 via conduits 17, 34, 31 and 24 and is introduced into the inter-mediate portion of the heat recovery vessel 12 to displace upwardly into the accumulator tank 13 hot water from the upper heat transfer zone 21 of the heat recovery vessel 12. Second stage heating is effected for a time sufficient to volumetric similarly substantially replace the pressurized water in the heat transfer conduits of the user equipment as well as the associated conduits.
!, It will be appreciated that heat-up times are improved by passing the water stored in upper heat transfer zone 21 of the vessl 12 to hot accumulator tank 13 vice passage through the user equipment 10 .
The final stage of the heating cycle is effected by closing valve 32 and opening valve 27 and gradually opening valve 29 whereby hot heat transfer fluid is withdrawn from the accumulator tank 13 by conduit 18 and combined in conduit 16 with recirculating heat transfer medium in conduit 40 and introduced by conduit 15 into user equipment 10. The heat transfer fluid withdrawn from the user equipment 10 in conduit 17 is split with a portion being passed to hot accumulator tank 13 by conduits 26 and 19 with the remaining portion by-passing accumulator tank 13 by being passed by conduit 28 to conduit 40 as the recirculating heat transfer fluid. The amount of heat transfer fluid by-passing the hot accumulator tank 13 is nominal, if any, at initiation of the final heating stage and is increased as the desired temperature level is reached with concomitant reductions in the flow of fluid from accumulator tank 13.
After a time period determined by the capabilities of the user equipment 10 with regard to the materials being treated, the heating cycle is stopped and first stage of the cooling cycle is initiated. Accordingly, valves 20 and 29 are closed and valve 30 is opened to permit hot heat transfer fluid from the user equip-ment 10 to be introduced by conduits 17, 26, and 23 into the upper portion of the heat recovery zone 21 of the heat recovery vessel 12 to displace downwardly thereby tempered cold heat transfer fluid therein, such displaced fluid being passed to the user equipment 10 by conduits 24, 42, 39, 40, 16 and 15.
As hereinabove discussed with respect to first.and second stages of the heating cycle, after a volume of heat transfer fluid is displaced generally equal to from 75 to 125 percent, preferably substantially equal to the volume of fluid in the user equipment 10 and related conduits, the second stage of the cooling cycle is initiated by closing valves 27 and 30 and by opening valves 32 and 38. Cooled heat transfer fluid is passed by conduit 33, 39, 40, 16 and 15 to user equipment 10 with tempered hot fluid introduced into the intermediate portion of heat recovery vessel 12 by con~
duits 17, 34, 31 and 24 to downwardly displace in the lower heat transfer zone 22 therein cold water which is passed to cooler 14 by conduits 25 and 36.
After a similar volumetric change, the final stage of the cooling cycle is effected by closing valve 32 and opening valve 37 whereby cooled heat transfer fluid continues to be passed to : - `
iO7~669 user equipment 10 from cooler 14 by conduits 33, 39, 40, 16 and 15 with tempered heat transfer fluid being returned to cooler 14 by conduits 17, 34, 35 and 36. During such final cooling stage valve 29 is caused to be gradually opened to effect a by-pass of a portion of the heat transfer to the cooler 14 as the user equipment reaches its lower design temperature. The by-passed fluid is passed from conduit 17 to conduit 40 by line 28 under the control value 29. The amount of fluid by-passing the cooler 14 is increased as such final design temperature is reached.
After a time period similarly dictated by process requirements, the cooling cycle is discontinued and the heating cycle initiated as hereinabove discussed.
As will be appreciated by one skilled in the art, when introducing a hot heat transfer fluid into a heat transfer zone, the hot fluid is into the upper portion thereof to thereby down-wardly displace relatively cooler heat transfer fluid whereas when introducing cool heat transfer fluid into a transfer zone of the heat recovery vessel, the cooled fluid is introduced into the lower portion thereof to thereby upwardly displace warmer water. It will be further appreciated by one skilled in the art that mixing in the heat recovery vessels of the heat transfer medium at various temperature levels durihg fluid should be minimized.
While the hereinabove description describes a heat re-covery vessel having two zones separated by baffles (illustrated by the dotted lines), it will be appreciated that a separate vessel may be employed for each zone, such as illustrated in Figure 2.
The invention has been described with reference to the use of pressurized water as the heat transfer fluid, however, it will be appreciated that other heat transfer fluids may be used. The use of another heat transfer fluid is not contemplated except for a use requiring large temperature range, since such use is inefficient requiring extra volumes of fluid to the system as a result of the specific heat of such heat transfer fluids.
Example of the Invention A 5'x12' platen press having 22 openings is operated with a heat requirement of 10.84 x 106 B.T.U. per cycle within a temperature range of from 90 to 290 F. Use of the process and apparatus of the present invention reduces heat requirements to 6.44 x 10 B.T.U. per cycle as compared to estimated heat requirements of 8.8 B.T.U. per cycle for a system like the one disclosed in the hereinabove mentioned Hanson patent. Savings in energy requirements in the first year are greater than the additional equipment costs to effect such efficiencies.
While not fully illulstrated, the valving arrangement includes automatic on-off and modulating valves in combination to minimize valve requirements.
Claims (16)
1. In a process for heating and cooling user equipment utilizing pressurized water as a heat transfer fluid in a closed system wherein said system includes heating and cooling zones for heating and cooling said heat tranfer fluid and wherein said system includes a zone for storing heat transfer fluid at intermediate temperature levels, the improvement comprising:
(a) introducing heat transfer fluid from an upper portion of a first storage zone into said user equipment during a first stage of a heating cycle, said heat transfer fluid being at a temperature above the temperature of said user equipment;
(b) introducing heat transfer fluid withdrawn from said user equipment into a lower portion of said first storage zone during step (a) thereby upwardly displacing the heat transfer fluid therein;
(c) discontinuing the flow of heat transfer fluid to said first storage zone;
(d) introducing heat transfer fluid from said heating zone into said user equipment during a second stage of said heating cycle;
(e) introducing heat transfer fluid withdrawn from said user equipment during said second stage of said heating cyle into a lower portion of a second stage storage zone thereby displacing heat transfer fluid contained therein;
(f) passing said displaced heat transfer fluid of step (e) to said heating zone;
(g) switching to said heating zone the flow of heat transfer fluid withdrawn from said user equipment to initiate and finalize said heating cycle;
(h) discontinuing the flow of heat transfer fluid to said user equipment from said heating zone at completion of said heating cycle;
(i) subsequently introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said second storage zone during a first stage of a cooling cycle thereby down-wardly displacing heat transfer fluid therein, said heat transfer fluid being at a temperature below the temperature of said user equipment;
(i) withdrawing and passing to said user equipment, said displaced heat transfer fluid of step (i);
(k) discontinuing the flow of heat transfer to said second storage zone;
(l) introducing heat transfer fluid from said cooling zone into said user equipment during a second stage of said cooling cycle;
(m) introducing heat transfer fluid withdrawn from said user equipment during step (1) into said upper portion of said first storage zone therein by downwardly displacing heat transfer fluid therein;
(n) passing said displaced heat transfer fluid of step (m) to said cooling zone; and (o) switching the flow of heat transfer fluid withdrawn from said user equipment from said first storage zone to said cooling zone to initiate and finalize said cooling cycle.
(a) introducing heat transfer fluid from an upper portion of a first storage zone into said user equipment during a first stage of a heating cycle, said heat transfer fluid being at a temperature above the temperature of said user equipment;
(b) introducing heat transfer fluid withdrawn from said user equipment into a lower portion of said first storage zone during step (a) thereby upwardly displacing the heat transfer fluid therein;
(c) discontinuing the flow of heat transfer fluid to said first storage zone;
(d) introducing heat transfer fluid from said heating zone into said user equipment during a second stage of said heating cycle;
(e) introducing heat transfer fluid withdrawn from said user equipment during said second stage of said heating cyle into a lower portion of a second stage storage zone thereby displacing heat transfer fluid contained therein;
(f) passing said displaced heat transfer fluid of step (e) to said heating zone;
(g) switching to said heating zone the flow of heat transfer fluid withdrawn from said user equipment to initiate and finalize said heating cycle;
(h) discontinuing the flow of heat transfer fluid to said user equipment from said heating zone at completion of said heating cycle;
(i) subsequently introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said second storage zone during a first stage of a cooling cycle thereby down-wardly displacing heat transfer fluid therein, said heat transfer fluid being at a temperature below the temperature of said user equipment;
(i) withdrawing and passing to said user equipment, said displaced heat transfer fluid of step (i);
(k) discontinuing the flow of heat transfer to said second storage zone;
(l) introducing heat transfer fluid from said cooling zone into said user equipment during a second stage of said cooling cycle;
(m) introducing heat transfer fluid withdrawn from said user equipment during step (1) into said upper portion of said first storage zone therein by downwardly displacing heat transfer fluid therein;
(n) passing said displaced heat transfer fluid of step (m) to said cooling zone; and (o) switching the flow of heat transfer fluid withdrawn from said user equipment from said first storage zone to said cooling zone to initiate and finalize said cooling cycle.
2. The process as defined in Claim 1 wherein the volume of heat transfer fluid in a storage zone is from 75 to 125 percent of the volume of transfer fluid in said user equipment and related conduit means.
3. The process as defined in Claim 2 wherein said volumes are substantially about equal.
4. The process as defined in Claim 1 wherein a first portion of said heat transfer fluid withdrawn from said user equipment, during finalization of said heating cycle is returned to said user equipment with the remaining portion being returned to said heating zone.
5. The process as defined in Claim 4 wherein the ratio of first portion to remaining portion of said heat transfer fluid increases during completion of said heating cycle.
6. The process as defined in Claim 1 wherein a first portion of said heat transfer fluid withdrawn from said user equipment, during finalization of said cooling cycle is returned to said user equipment with the remaining portion being returned to said cooling zone.
7. The process as defined in Claim 6 wherein the ratio of said first portion to remaining portion of said heat transfer fluid increases during completion of said cooling cycle.
8. An apparatus for heating and cooling user equipment utilizing pressurized water as a heat transfer fluid in a closed system wherein said system includes heating and cooling means for heating and cooling said heat transfer fluid and wherein said apparatus includes at least two storage zones for storing heat transfer fluid at intermediate temperature levels which comprises:
(a) pump means for passing said heat transfer fluid through said apparatus;
(b) first conduit means for introducing heat transfer fluid from an upper portion of a first heat transfer zone of a storage vessel into said user equipment during a first stage of a heating cycle and for passing heat transfer fluid from a second heat trans-fer zone of said storage vessel to said user equipment during a first stage of a cooling cycle;
(c) a second conduit means for introducing heat transfer fluid withdrawn from said user equipment into a lower portion of said first heat transfer zone of said storage vessel;
(d) third conduit means for introducing heat transfer fluid from said heating means into said user equipment during a second stage of said heating cycle;
(e) fourth conduit means for introducing heat transfer fluid withdrawn from said user equipment during said second stage of said heating cycle into a lower portion of said second heat trans-fer zone of said storage vessel and for introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said first heat transfer zone of said storage vessel during a second stage of said cooling cycle;
(f) fifth conduit means for passing heat transfer fluid from said second heat transfer zone of said storage vessel to said heating means;
(g) sixth conduit means for passing heat transfer fluid withdrawn from said user equipment to said heating means during a final stage of said heating cycle;
(h) seventh conduit means for introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said second heat transfer zone of said storage vessel during a first stage of a cooling cycle;
(i) eighth conduit means for introducing heat transfer fluid from said cooling means into said user equipment during said second stage of said cooling cycle;
(j) ninth conduit means for passing heat transfer fluid from said first heat transfer zone of said storage vessel to said cooling vessel; and (k) tenth conduit means for passing heat transfer fluid with-drawn from said user equipment to said cooling means.
(a) pump means for passing said heat transfer fluid through said apparatus;
(b) first conduit means for introducing heat transfer fluid from an upper portion of a first heat transfer zone of a storage vessel into said user equipment during a first stage of a heating cycle and for passing heat transfer fluid from a second heat trans-fer zone of said storage vessel to said user equipment during a first stage of a cooling cycle;
(c) a second conduit means for introducing heat transfer fluid withdrawn from said user equipment into a lower portion of said first heat transfer zone of said storage vessel;
(d) third conduit means for introducing heat transfer fluid from said heating means into said user equipment during a second stage of said heating cycle;
(e) fourth conduit means for introducing heat transfer fluid withdrawn from said user equipment during said second stage of said heating cycle into a lower portion of said second heat trans-fer zone of said storage vessel and for introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said first heat transfer zone of said storage vessel during a second stage of said cooling cycle;
(f) fifth conduit means for passing heat transfer fluid from said second heat transfer zone of said storage vessel to said heating means;
(g) sixth conduit means for passing heat transfer fluid withdrawn from said user equipment to said heating means during a final stage of said heating cycle;
(h) seventh conduit means for introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said second heat transfer zone of said storage vessel during a first stage of a cooling cycle;
(i) eighth conduit means for introducing heat transfer fluid from said cooling means into said user equipment during said second stage of said cooling cycle;
(j) ninth conduit means for passing heat transfer fluid from said first heat transfer zone of said storage vessel to said cooling vessel; and (k) tenth conduit means for passing heat transfer fluid with-drawn from said user equipment to said cooling means.
9. The apparatus as defined in Claim 8 wherein each of said zones is formed of a separate vessel.
10. The apparatus as defined in Claim 8 wherein the volume of said zones is from 75 to 125 percent of the volume of heat transfer conduit means in said user equipment and said conduit means to and from said user equipment.
11. The apparatus as defined in Claim 10 wherein said volumes are substantially equal.
12. The apparatus as defined in Claim 8 wherein conduit means are provided to by-pass said heating means during finalization of said heating cycle.
13. The apparatus as defined in Claim 8 wherein said first conduit means is comprised of a conduit means for introducing heat transfer fluid from an upper portion of a first heat transfer zone of a storage vessel into said user equipment during a first stage of a heating cycle and a conduit means for introducing heat transfer fluid withdrawn from said user equipment into said upper portion of said first heat transfer zone of said storage vessel during a second stage of said cooling cycle.
14. The apparatus as defined in Claim 9 wherein said fourth conduit means is comprised of a conduit for introducing heat transfer fluid withdrawn from said user equipment during said second stage of said heating cycle into a lower portion of said second heat transfer zone of said storage vessel and a conduit means for passing heat transfer fluid from a second heat transfer zone of said storage vessel to said user equipment during a first stage of a cooling cycle.
15. The apparatus of Claim 8 wherein an eleventh conduit means is provided between said third and sixth conduit means.
16. The apparatus of Claim 8 wherein a twelfth conduit means is provided between said ninth and tenth conduit means.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/690,166 US4071075A (en) | 1976-05-26 | 1976-05-26 | Process and apparatus for the cyclic heating and cooling of processing equipment |
| US05/695,808 US4072184A (en) | 1976-05-26 | 1976-06-14 | Process and apparatus for the cyclic heating and cooling of processing equipment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1070669A true CA1070669A (en) | 1980-01-29 |
Family
ID=27104551
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA277,753A Expired CA1070669A (en) | 1976-05-26 | 1977-05-05 | Process and apparatus for the cyclic heating and cooling of processing equipment |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS52144371A (en) |
| BR (1) | BR7703296A (en) |
| CA (1) | CA1070669A (en) |
| DE (1) | DE2723088C2 (en) |
| GB (1) | GB1526388A (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE8008885L (en) * | 1980-12-17 | 1982-06-18 | Scan Rob Ab | DEVICATION PLANT OF THE TYPE WITH INDIVIDUAL VULKANIZING CHAMBERS |
| SE8008884L (en) * | 1980-12-17 | 1982-06-18 | Scan Rob Ab | DEVICE FOR AUTO CLAV TYPE CONTROL SYSTEM |
| FR2527978A1 (en) * | 1982-06-04 | 1983-12-09 | Ic Entreprise | Combined superheated and cold water storage - for vulcanisation press water bag to reduce vessel and heating costs |
| GB2149492A (en) * | 1983-09-10 | 1985-06-12 | Jespro Limited | Cooling means for a hydraulic system |
| DE3620623C1 (en) * | 1986-06-20 | 1988-02-18 | Schaefer Otmar Ulrich Dipl Ing | Method and device for alternately heating and cooling a heat exchanger |
| DE4120403C2 (en) * | 1991-06-20 | 1996-11-14 | Luckow Hans Juergen | Process for tempering an injection mold |
| DE29508207U1 (en) * | 1995-05-18 | 1995-08-10 | Gottfried Joos Maschinenfabrik GmbH & Co, 72285 Pfalzgrafenweiler | Press, especially veneer press |
| JP2957139B2 (en) * | 1997-02-10 | 1999-10-04 | クリナップ株式会社 | Mold temperature controller |
| DE29808569U1 (en) | 1998-04-30 | 1998-11-05 | Wittmann Kunststoffgeräte Ges.m.b.H., Wien | Temperature control circuit for injection molds |
| AT506978A1 (en) | 2008-07-02 | 2010-01-15 | Engel Austria Gmbh | INJECTION MOLDING MACHINE WITH ENERGY RECOVERY |
| CN109130299A (en) * | 2018-09-26 | 2019-01-04 | 活跃科技股份有限公司 | Energy-saving type trigger squeeze |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3109486A (en) * | 1960-07-11 | 1963-11-05 | Midland Ross Corp | Heating and cooling system |
| DE2425589C3 (en) * | 1974-05-27 | 1980-01-10 | Otmar Dipl.-Ing. 8000 Muenchen Schaefer | Method and device for alternating heating and cooling of a heat exchanger of a heating-cooling system |
-
1977
- 1977-05-05 CA CA277,753A patent/CA1070669A/en not_active Expired
- 1977-05-12 GB GB1996777A patent/GB1526388A/en not_active Expired
- 1977-05-21 DE DE19772723088 patent/DE2723088C2/en not_active Expired
- 1977-05-23 BR BR7703296A patent/BR7703296A/en unknown
- 1977-05-26 JP JP6206377A patent/JPS52144371A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS618359B2 (en) | 1986-03-13 |
| BR7703296A (en) | 1978-03-14 |
| GB1526388A (en) | 1978-09-27 |
| DE2723088C2 (en) | 1986-12-18 |
| DE2723088A1 (en) | 1977-12-08 |
| JPS52144371A (en) | 1977-12-01 |
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