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EP2209631B1 - Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température - Google Patents

Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température Download PDF

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Publication number
EP2209631B1
EP2209631B1 EP08847011A EP08847011A EP2209631B1 EP 2209631 B1 EP2209631 B1 EP 2209631B1 EP 08847011 A EP08847011 A EP 08847011A EP 08847011 A EP08847011 A EP 08847011A EP 2209631 B1 EP2209631 B1 EP 2209631B1
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EP
European Patent Office
Prior art keywords
temperature
heat exchange
heat
temperature control
central
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EP08847011A
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German (de)
English (en)
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EP2209631A2 (fr
Inventor
Andreas Harig
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Technotrans SE
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Technotrans SE
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Priority to EP12004875.6A priority Critical patent/EP2527147B1/fr
Publication of EP2209631A2 publication Critical patent/EP2209631A2/fr
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Publication of EP2209631B1 publication Critical patent/EP2209631B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/22—Means for cooling or heating forme or impression cylinders

Definitions

  • the invention relates to an arrangement on a printing machine for temperature control of operating points of the printing press with different operating temperatures.
  • the DE 10316860 and the WO 2006072558 publish system with a heat recovery.
  • the DE 44 29 520 A1 describes a method and a device for temperature control of temperature control in printing presses, by which temperature fluctuations due to hysteresis switching operations of a thermostat, which controls a temperature control of a Temperier remplikeitsniklaufs a printing press, are reduced.
  • An embodiment using such a device is described as including three color press rollers for three colors of a multi-color press temper. For each of the three colors, a separate branch is provided, each branch containing a paint distributor roller, a bypass line, a supply line, a return line, a thermostatic valve, a temperature sensor and an injector. At each of the three Farbverreiberwalzen a different temperature can be generated, so that thereby a so-called zone regulation is possible.
  • the US 5,471,927 describes a printing machine with a cooling system for lubricating oil.
  • the lubricating oil comes in contact with the major heat-generating components of the printing press. Described are three towers, each of which has an oil sump with a heat exchanger. For all three towers together, one source of coolant and one heating source are provided, but individual controls are provided for each of the towers.
  • the DE 10 2007 003619 A1 describes a printing machine with several printing units, are integrated in the temperature-controlled devices.
  • the various devices to be tempered can be inking units.
  • the devices to be tempered can be temperature-controlled independently of each other via a central tempering device.
  • the printing press has a single central primary supply line extending between the printing machine and the central temperature control device and a single primary return line.
  • the DE 10 2005 005 303 A1 describes that different circuits K1, K2 and K3 can be provided with different temperature levels on a printing press.
  • the temperature level of the circuit K2 can be between 5 ° C and 30 ° C.
  • the temperature level of the circuit K3 can be between 20 ° C and 35 ° C.
  • the circuits K2 and K3 can be connected via heat exchangers with a common, independent circuit.
  • the circuit K3 can be supplied purely for heating purposes with temperature control above the ambient temperature T1.
  • the temperature control in the circuit K3 can, for example, in be heated in a water heater.
  • the temperature control of the circuit K1 can be mixed with the temperature control of the circuit K2 to temper different pressure rollers.
  • a first aspect of the invention relates to an arrangement on a printing machine comprising at least one low-temperature tempering point (NT tempering point), at least one middle temperature tempering point (MT tempering point) and at least one high-temperature tempering point (HT tempering point), which are at a low temperature range ( NT range), a medium temperature range (MT range) and at least one high temperature range (HT range) of a printing press are arranged and designed such that by means of the NT temperature control of the NT range to a low temperature, by means of the MT temperature of the MT Can be temperature-controlled to a middle temperature and by means of the HT tempering point of the HT range to a high temperature, wherein the low temperature is lower than the middle temperature and the middle temperature is lower than the high temperature, wherein the arrangement has a central heat exchange system, which is designed such that the NT tempering point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central heat exchange system can be flow
  • each of the temperature control can be formed as a separate primary circuit, which is designed so that the heat flow through a heat exchanger to a secondary circuit can be discharged.
  • a secondary circuit is preferably part of the central heat exchange system or another closed circuit which is in heat exchanging relationship with the central heat exchange system.
  • each of the temperature control can be designed as a directly through a process means, in particular the heat exchange fluid in the central heat exchange system, flowed through circuit, such that the heat flow is transmitted together with the circulating in the circuit processing means, so that the heat flow coupled to the flowing carrier mass of the process medium flow is.
  • Process fluids are any fluids that are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution, gear oil and / or other fluids which are used for cooling certain components. Also conceivable is a design of tempering, in which the two Designs are combined.
  • a separate primary circuit in the sense described may be formed as an open primary circuit, in which the fluid is consumed at the tempering partially used, such as dampening, or as a closed primary circuit in which in each point of the primary circuit, the inflow is equal to the effluent.
  • Fountain solution is used on printing machines, inter alia, to wet the non-printing areas of a printing plate, so as to prevent ink acceptance in these areas. Excess fountain solution is collected and returned to the circulation. Since fountain solution often contains volatiles, fountain solution is usually cooled to low temperatures before it is applied to the printing plates. As a result, evaporation of the volatile components is significantly reduced, although not completely prevented.
  • This area of a printing press will generally be an NT area within the meaning of the invention, which is tempered by the NT tempering point. Since at this point, as just described, dampening water is only partially recycled, as far as it was not consumed, this cycle is referred to as "open".
  • NT range can also be tempered by a preferably closed circuit, for example by a circuit in the interior of a printing cylinder .. This preferred closed circuit would be part of the NT tempering point and could in the case described preferably also with fountain solution but also with a tempered other process agents.
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy.
  • the difference between the NT region and the MT region is preferably at least 5 ° C.
  • the difference between the MT range and the HT range is at least 10 ° C.
  • the operating temperature of the NT range is between 5 ° C and 15 ° C, more preferably in the range of about 10 ° C. Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature between 15 ° C and 30 ° C is more preferably in the range of about 20 ° C and 25 ° C.
  • Such a range of possible operating temperatures is used in printing presses, for example in the printing area of a printing machine, in particular on the distributor rollers and / or the ductor rollers.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range is used, for example, in UV dryers (operating temperature about 60 ° C), on sheet baffles (operating temperature about 50 ° C) and in the cooling of blown air or compressed air used (operating temperature between 60 ° C and 90 ° C).
  • the arrangement further comprises a cold generator, which is arranged and arranged such that by means of the cold generator, the NT tempering is temperature controlled.
  • a cold generator preferably has a chiller, more preferably a compressor-driven chiller with a condenser.
  • a further advantageous embodiment relates to an arrangement in which both the NT temperature control point and the MT temperature control point can be tempered by means of the cold generator.
  • such an arrangement has a design in which the Refrigerant generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system.
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may for example be a free cooler.
  • free-cooler temperature control meant is a device that uses about the temperature of the ambient air to cool the heat exchange fluid.
  • the heat exchange fluid may for example flow directly through the cooling device or be connected via an additional heat exchanger with this.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied controlled by parameters, for example if a greater cooling capacity is required and / or if a reduction of the cooling temperature is required, for example if the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, which is cooled, for example, with groundwater or the like; Etc.
  • a further advantageous embodiment relates to such an arrangement in which both the HT tempering point and the MT tempering point can be tempered by means of the cooling device.
  • such an arrangement preferably has a design in which the cooling device in the operating state of the printing press is in permanently cooling relationship with the HT tempering point.
  • the cooling relationship is preferably such that a waste heat flow of the MT temperature control point to the refrigerator and / or the cooling device can be discharged.
  • a further advantageous embodiment relates to such an arrangement in which a heat flow from the MT tempering point and / or the HT tempering point to the cooling device via the heat exchange fluid in the central heat exchange system is transferable.
  • the arrangement further comprises a cold producer, which is arranged and arranged such that by means of the cold generator of the MT temperature control point is temperature controlled.
  • the refrigeration producer preferably comprises a refrigerator, more preferably a compressor driven refrigerator with an evaporator and a condenser and more preferably an air cooled refrigerator.
  • a further advantageous embodiment relates to an arrangement in which both the MT tempering point and the NT tempering point can be tempered by means of the cold producer.
  • such an arrangement has a design in which the cold producer is arranged such that the waste heat flow generated by the cold producer is directly transferable to the heat exchange fluid in the central heat exchange system.
  • the cold generator and the cold producer are operated with refrigerants having different evaporation temperatures and / or different condensation temperatures.
  • a further advantageous embodiment relates to such an arrangement in which the central heat exchange system has a heat exchange circuit with a central inlet and a central outlet, wherein extending between the central inlet and the central outlet a plurality of parallel partial branches, wherein a partial feed of a partial branch to one of Tempering points runs, wherein a partial flow of a partial branch coming from the tempering to such that a central heat exchange fluid stream in the central inlet can be divided into different heat exchange fluid partial streams, wherein the different heat exchange fluid partial streams can be supplied to different temperature control points and wherein the different heat exchange fluid partial streams coming from the different temperature control points can be recombined in the central flow to the central heat exchange fluid flow.
  • the central heat exchange fluid flow in the central inlet and in the partial feeds has the same temperature.
  • the temperatures in the sub-sequences differ depending on the operating temperature of the operating points.
  • the partial fluid flows in the partial drains are mixed in the respective sections of the central drain, so that a different temperature prevails in these sections, until finally merge in the flow direction behind the last partial flow all heat exchange fluid partial streams in the last section of the central process.
  • valve is actuatable depending on the operating temperature at the point of operation and the temperature of the incoming central heat exchange fluid stream and / or the incoming heat exchange fluid sub-stream, preferably closing the valve when the temperature of the incoming central heat exchange fluid stream and / or the incoming heat exchange fluid sub-stream is higher as the (actual or desired) operating temperature at the site.
  • such an arrangement preferably has a design in which at least part of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • heat consumers can be, for example, a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermal air, which can be used for drying the printed substrate, for example. Also conceivable are any other heat consumers.
  • the part of the heat flow in the partial sequence of a sub-branch can be removed.
  • the part of the heat flow is taken in a partial branch, which has a suitable temperature level for the respective heat consumer.
  • the part of the heat flow is preferably taken in a partial branch with a high temperature level, in particular in the partial outlet behind the HT tempering point since at this point of the central heat exchange system i.d.R. the highest temperature level prevails.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers at different points of the central heat exchange system with different temperature levels can be dissipated.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device is flowed through directly by the heat exchange fluid flow, wherein the heat exchange fluid flow can be conducted past the cooling device via a bypass line which can be controlled by a bypass valve.
  • cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit can be controlled via a cooling circuit valve.
  • a further advantageous embodiment relates to an arrangement in which the bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central Heat exchange system is higher than the actual temperature of the respective tempering.
  • such an arrangement has a design in which the central Heat exchange system with individual from the central heat exchange system hydraulically separated temperature control circuits in heat exchanging relationship stands. Hydraulically separated in the sense used here meant, without flow connection, via which a heat flow together with a fluid flow would be transferable.
  • the fluid circuits remain separate and can therefore be operated, for example, with different tempering fluids. Accordingly, only the respective heat flows are transmitted to the central heat exchange system by the temperature control circuit circuits provided separately in the hydraulic system.
  • a central heat exchanger in the central heat exchange system preferably a central heat exchanger can be provided, which is in heat exchanging relationship with several or all of the temperature control circuits, wherein the heat flows of the relevant temperature control circuits are transferred to a provided in the central heat exchanger heat exchange fluid.
  • the different temperature levels in the temperature control loop are standardized to a temperature of the heat exchange fluid in the central heat exchanger.
  • a separation of one of the tempering point circuits can preferably be configured via a respective bypass line that can be activated via a valve.
  • the valve is preferably designed as a function of the operating temperature at the respective operating point and the temperature of the heat exchange fluid in the central heat exchange system, wherein the valve is preferably closed when the temperature of the heat exchange fluid is higher than the (actual or desired) operating temperature at the operating point ,
  • a further advantageous embodiment relates to such an arrangement in which at least part of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • a heat consumer for example, have a heater for a Farbreibertemperier réelle and / or preheating, which can be used, for example, for preheating of thermal air, which can be used for example for drying the printed substrate.
  • a configuration of an arrangement in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer is preferred, wherein the arrangement is designed such that this waste heat flow can be dissipated from a point of the respective tempering point circuit which differs from the one Operating point downstream of the central heat exchange system is arranged.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer.
  • heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since da i.d.R. has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated.
  • such an arrangement preferably has a design in which the cooling device is flowed through directly by the heat exchange fluid flow, wherein the heat exchange fluid flow can be conducted past the cooling device via a bypass line that can be controlled by a bypass valve.
  • cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit can be controlled via a cooling circuit valve.
  • a further advantageous embodiment relates to such an arrangement in which the bypass valve or the cooling circuit valve can be blocked in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher than the actual temperature of the respective tempering.
  • the arrangement further comprises a buffer memory in which heat is temporarily stored in a heat storage material.
  • a further advantageous embodiment relates to an arrangement in which the heat storage material has a larger amount of heat exchange fluid.
  • such an arrangement has a design in which two central heat exchange systems are provided, one of the two central heat exchange systems is provided for supplying heat consumers with heat, as described in the claims A17 to A21 and A24 to A29 and wherein the other of the having two central heat exchange systems, the cooling device.
  • a second aspect of the invention relates to an arrangement on a printing press, comprising at least one low-temperature tempering point (NT tempering point), at least one middle temperature tempering point (MT tempering point) and at least one high-temperature tempering point (HT tempering point), which at a low temperature range (NT area), a middle temperature range (MT range) and at least one high temperature range (HT range) of a printing press are arranged and designed such that means of the NT temperature control of the NT range to a low temperature, by means of the MT temperature MT range can be tempered to a middle temperature and by means of the HT tempering point of the HT range to a high temperature, wherein the low temperature is lower than the middle temperature and the middle temperature is lower than the high temperature, wherein the arrangement further comprises a low-temperature temperature control device (NT temperature control device) and a high-temperature temperature control device (HT temperature control device), wherein the MT tempering point can be tempered both via the NT tempering device and via the HT tempering device
  • the NT temperature control device can be designed, for example, to a low temperature which, depending on the embodiment, for example, an NT tempering point on the printing press anyway, whereas the HT tempering device can be designed so that they energy saving the Ambient temperature can be used for temperature control. Therefore, depending on the ambient temperature and the desired operating temperature, an embodiment according to the invention can advantageously be designed in such a way that the desired operating temperature is achieved under a combination of the two temperature control devices which is optimized with regard to desired power and optimum energy utilization.
  • an essential component of the HT temperature control device is preferably a free cooler.
  • the various temperature levels herein are referred to by the terms “high”, “medium” and “low” only for the purpose of indicating a not insignificant difference between the operating temperatures. Moreover, the terms have no quantitative significance.
  • the difference between the NT region and the MT region is preferably at least 5 ° C.
  • the difference between the MT range and the HT range is at least 10 ° C.
  • the operating temperature of the NT range is between 5 ° C and 15 ° C, more preferably in the range of about 10 ° C. Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature between 15 ° C and 30 ° C is more preferably in the range of about 20 ° C and 25 ° C.
  • Such a range of possible operating temperatures is used in printing presses, for example in the printing area of a printing machine, in particular on the distributor rollers and / or the ductor rollers.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range is used, for example, in UV dryers (operating temperature about 60 ° C), on sheet baffles (operating temperature about 50 ° C) and in the cooling of blown air or compressed air used (operating temperature between 60 ° C and 90 ° C).
  • NT temperature control device and the HT temperature control device are connected to the MT temperature control point such that the MT temperature control point can be temperature controlled simultaneously by the NT temperature control device and the HT temperature control device.
  • a further advantageous embodiment relates to an arrangement in which the NT tempering device and the HT tempering device are connected to the MT tempering point such that the MT tempering point depends on certain parameters at a certain time either by the NT tempering device or the HT tempering device is temperature controlled.
  • Such parameters may be, for example, the actual and / or desired temperature of the MT operating point and / or the temperature range achievable by the HT temperature control device. This temperature range may in turn depend on the temperature of a heat exchange fluid. It is also conceivable that when the HT tempering is a free cooler, as described above, a such parameter is the ambient temperature around the free cooler.
  • such an arrangement has a design in which the NT temperature control device has a cold generator.
  • a cold generator preferably has a chiller, more preferably a compressor-driven chiller with a condenser.
  • the arrangement further comprises a central heat exchange system, which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the NT tempering and the heat exchange fluid, as well as between the MT tempering and the heat exchange fluid as well as between the HT tempering point and the heat exchange fluid are transferable.
  • a central heat exchange system which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy.
  • This also applies to the interposition of a chiller.
  • the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression (mechanical energy) and then passes through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid.
  • mechanical energy mechanical energy
  • only “additional" heat is generated by the mechanical energy in the compressor. Even when using a chiller, therefore, the already absorbed heat is not converted but is still present in the refrigerant and is discharged from this as part of the waste heat to the heat exchange system.
  • a further advantageous embodiment relates to an arrangement in which the cold generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system.
  • such an arrangement has a design in which the HT tempering device has a cooling device.
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may e.g. to be a free cooler.
  • free-cooler temperature control device is meant a device which exploits approximately the temperature of the ambient air in order to cool the heat exchange fluid.
  • the heat exchange fluid may be e.g. to be a process agent. Process fluids are any fluids that are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution, gear oil and / or other fluids which are used for cooling certain components.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied under the control of parameters, e.g. if greater cooling capacity is required and / or if a reduction in the cooling temperature is required, e.g. when the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, e.g. is cooled with groundwater or the like; Etc.
  • the cold generator is in a permanently cooling relationship to the NT temperature control point in the operating state of the printing machine.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device in the operating condition of the printing press in permanently cooling Relationship with the HT tempering point stands.
  • the arrangement further comprises a central heat exchange system, which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the NT tempering and the heat exchange fluid, as well as between the MT tempering and the heat exchange fluid as well as between the HT tempering point and the heat exchange fluid are transferable.
  • a central heat exchange system which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the
  • a further advantageous embodiment relates to an arrangement in which the arrangement is designed such that a heat flow from the MT tempering point and / or the HT tempering point to the cooling device via the heat exchange fluid in the central heat exchange system is transferable.
  • such an arrangement has a design in which the arrangement further comprises a refrigeration producer, which is arranged and arranged such that the MT temperature control point can be tempered by means of the cold generator.
  • the refrigeration producer preferably comprises a refrigerator, more preferably a compressor driven refrigerator with an evaporator and a condenser and more preferably an air cooled refrigerator.
  • both the MT tempering point and the NT tempering point can be tempered by means of the cold producer.
  • a further advantageous embodiment relates to such an arrangement in which the cold producer is arranged such that the waste heat flow generated by the cold producer directly to the heat exchange fluid in the central Heat exchange system is transferable.
  • such an arrangement preferably has a configuration in which the central heat exchange system has a heat exchange circuit with a central inlet and a central outlet, wherein extending between the central inlet and the central outlet a plurality of parallel partial branches, wherein a partial feed of a partial branch to a the temperature control points, wherein a partial flow of a partial branch of the tempering leads to the central drain, such that a central heat exchange fluid flow in the central inlet into different heat exchange fluid partial streams can be divided, wherein the different heat exchange fluid partial streams different Temperierstellen zuleitbar and wherein the different heat exchange fluid partial streams of the different tempering coming in the central process again to the central heat exchange fluid flow are merge.
  • the central heat exchange fluid flow in the central inlet and in the partial feeds has the same temperature.
  • the temperatures in the sub-sequences differ depending on the operating temperature of the operating points.
  • the partial fluid flows in the partial drains are mixed in the respective sections of the central drain, so that a different temperature prevails in these sections, until finally merge in the flow direction behind the last partial flow all heat exchange fluid partial streams in the last section of the central process.
  • valve is preferably a function of the operating temperature at the operating point and the temperature of the incoming central heat exchange fluid flow and / or the incoming Heat exchange fluid partial flow is controllable, wherein the valve is preferably closed when the temperature of the incoming central heat exchange fluid flow and / or the incoming heat exchange fluid partial flow is higher than the (actual or desired) operating temperature at the operating point.
  • a further advantageous embodiment relates to such an arrangement in which at least a portion of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • heat consumers may e.g. a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermo air, which, e.g. can be used for drying the printed substrate. Also conceivable are any other heat consumers.
  • a further advantageous embodiment relates to such an arrangement in which the dissipatable part of the heat flow in the partial sequence of a sub-branch can be removed.
  • the part of the heat flow is taken in a partial branch, which has a suitable temperature level for the respective heat consumer.
  • the part of the heat flow is preferably taken in a partial branch with a high temperature level, in particular in the partial outlet behind the HT tempering point since at this point of the central heat exchange system i.d.R. the highest temperature level prevails.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers at different points of the central heat exchange system with different temperature levels can be dissipated.
  • cooling device is flowed through directly by the heat exchange fluid flow and in which the heat exchange fluid flow can be conducted past the cooling device via a bypass line that can be activated by means of a bypass valve is preferred.
  • a further advantageous embodiment relates to an arrangement in which the cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit is controllable via a cooling circuit valve.
  • such an arrangement has a design in which the bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher than the actual temperature of the respective tempering point.
  • central heat exchange system is in heat exchanging relationship with individual temperature control loop circuits hydraulically separated from the central heat exchange system.
  • Hydraulically separated in the sense used here meant, without flow connection, via which a heat flow together with a fluid flow would be transferable.
  • the fluid circuits remain separate and can therefore be operated, for example, with different tempering fluids. Accordingly, only the respective heat flows are transmitted to the central heat exchange system by the temperature control circuit circuits provided separately in the hydraulic system.
  • a central heat exchanger in the central heat exchange system preferably a central heat exchanger can be provided, which is in heat exchanging relationship with several or all of the temperature control circuits, wherein the heat flows of the relevant temperature control circuits are transferred to a provided in the central heat exchanger heat exchange fluid.
  • the different temperature levels in the temperature control loop are standardized to a temperature of the heat exchange fluid in the central heat exchanger.
  • a further advantageous embodiment relates to such an arrangement in which the heat exchanging relationship between one of the separate Temperierstellen circuits and the central heat exchange system is designed separable, such that from the Temperierstellen cycle to the central heat exchange system no heat flow is more transferable.
  • a separation of one of the tempering point circuits can preferably be configured via a respective bypass line that can be activated via a valve.
  • the valve is preferably designed as a function of the operating temperature at the respective operating point and the temperature of the heat exchange fluid in the central heat exchange system, wherein the valve is preferably closed when the temperature of the heat exchange fluid is higher than the (actual or desired) operating temperature at the operating point ,
  • heat consumers may e.g. a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermo air, which, e.g. can be used for drying the printed substrate. Also conceivable are any other heat consumers.
  • such an arrangement preferably has a design in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer, the arrangement being designed such that this waste heat flow can be dissipated from a point of the respective temperature control circuit which from the operating point downstream of the central heat exchange system is arranged.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer. It can heat is advantageously taken from the temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since this usually has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated.
  • cooling device is flowed through directly by the heat exchange fluid flow
  • heat exchange fluid flow can be conducted past the cooling device via a bypass line that can be controlled by a bypass valve.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit can be controlled via a cooling circuit valve.
  • bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher is the actual temperature of the respective temperature control point.
  • a further advantageous embodiment relates to an arrangement in which the arrangement further comprises a buffer memory in which heat is temporarily stored in a heat storage material.
  • such an arrangement has a configuration in which the heat storage material has a larger amount of heat exchange fluid.
  • a third aspect of the invention relates to an arrangement on a printing press comprising at least one low-temperature tempering point (NT tempering point) and at least one middle temperature tempering point (MT tempering point), which are connected to a low-temperature region (NT region) and a medium-temperature region (MT).
  • NT tempering point low-temperature tempering point
  • MT tempering point middle temperature tempering point
  • NT tempering of the NT range to a low temperature and by means of the MT tempering the MT range is temperature-controlled to a middle temperature, wherein the low temperature is lower than the average temperature, wherein the NT tempering point and the MT tempering point via a central heat exchange system, which is traversed by a heat exchange fluid, are connected to a heat consumer system such that the waste heat flows incurred in the temperature control at the NT tempering and MT tempering, at least partially transferable to the heat consumer system.
  • At least partially transferable in the sense means preferably that of each of the two tempering at least a sectionab Anlagenstrom to the Heat consumer system is transferable.
  • the temperature levels herein are referred to by the terms “low” and “medium” only for the purpose of indicating a not insubstantial difference between the operating temperatures. Moreover, the terms have no quantitative significance. Therefore, as long as only two temperature levels are described, the terms described in relation to this aspect of the invention are also replaceable by the terms “medium” and “high” or “low” and “high” described with respect to the other aspects of the invention.
  • the arrangement further has a high-temperature tempering point (HT tempering point) which is arranged on a high-temperature region (HT region) of the printing press and designed such that the HT tempering point of the HT Temperature is tempered to a high temperature, wherein high temperature is higher than the low temperature and higher than the middle temperature.
  • HT tempering point high-temperature tempering point
  • the difference between the NT region and the MT region preferably at least 5 ° C.
  • the difference between the MT range and the HT range is at least 10 ° C.
  • the operating temperature of the NT range is between 5 ° C and 15 ° C, more preferably in the range of about 10 ° C. Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature between 15 ° C and 30 ° C is more preferably in the range of about 20 ° C and 25 ° C.
  • Such a range of possible operating temperatures occurs in printing machines, e.g. in the printing area of a printing press, in particular on the distributor rollers and / or the ductor rollers used.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range comes e.g. 60 ° C), sheet baffles (operating temperature approx. 50 ° C) and cooling of blown air or compressed air (operating temperature between 60 ° C and 90 ° C).
  • a further advantageous embodiment relates to an arrangement in which the arrangement further comprises a central heat reservoir, wherein heat consumers are connected to the central heat reservoir, to which the heat from the central heat reservoir can be dissipated.
  • such an arrangement has a design in which the arrangement is designed such that coming from the tempering, heat-dissipating fluid streams are supplied via Temperierstellen Oberen the central heat exchange system, wherein the fluid streams in the central heat exchange system unite.
  • Temperierstellen Gustaven the central heat exchange system, wherein the fluid streams in the central heat exchange system unite.
  • such an arrangement is preferred in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer, the arrangement being designed such that this waste heat flow or partial waste heat flow can be dissipated from a point of the respective temperature control line, which differs from the one Operating point is arranged downstream of the central heat reservoir.
  • a further advantageous embodiment relates to such an arrangement in which the arrangement is designed such that for at least one of the temperature control points coming, heat-dissipating fluid flows a temperature control circuit is provided which is formed hydraulically separated from the central heat reservoir, so that only a heat flow is transferred from the heat-dissipating fluid flow to the central heat reservoir. Only fluid flow is transferred to the central heat reservoir - but not a fluid flow.
  • the tempering circuit is hydraulically separated from the heat reservoir. As a result, different fluids can preferably be used. Individual temperature control circuits can be hydraulically connected with each other and hydraulically separated from other temperature control circuits.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer.
  • heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since this usually has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated.
  • such an arrangement preferably has a configuration in which the heat exchange system communicates with at least two tempering points in such a way that a heat flow from one of the at least two tempering points to the other of the at least two tempering points can be transferred via the heat exchange fluid.
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy. This also applies to the interposition of a chiller. In the chiller, the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression (mechanical energy) and then passes all the heat surplus through a heat exchanger to the environment or to the Heat exchange fluid from.
  • the arrangement further comprises a cold generator, which is arranged and arranged such that by means of the cold generator, the NT tempering is temperature controlled.
  • a refrigerator preferably comprises a refrigerator and more preferably a compressor-driven refrigerator with a condenser.
  • both the NT temperature control point and the MT temperature control point can be tempered by means of the cold generator.
  • a further advantageous embodiment relates to an arrangement in which the cold generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system. Waste heat flow in the sense is to be understood in such a way that the term includes both the heat absorbed by the chiller - ie the "generated" cold - and the heat loss produced by the chiller.
  • such an arrangement has a configuration in which the arrangement further comprises a cooling device .
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may for example be a free cooler.
  • free-cooler temperature control device is meant a device which exploits approximately the temperature of the ambient air in order to cool the heat exchange fluid.
  • the heat exchange fluid may be, for example, a processing agent.
  • process means any fluids are called, which are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution cleaning agent, gear oil and / or other fluids which are used for cooling certain components.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied controlled by parameters, for example if a greater cooling capacity is required and / or if a reduction of the cooling temperature is required, for example if the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, which is cooled, for example, with groundwater or the like; Etc.
  • both the HT tempering point and the MT tempering point can be tempered by means of the cooling device.
  • a further advantageous embodiment relates to such an arrangement in which the cold generator is in the operating condition of the printing press in a permanently cooling relationship with the NT tempering.
  • cooling device is in the operating state of the printing press in a permanently cooling relationship with the HT tempering.
  • such an arrangement preferably has a design in which the cold generator and the cooling device can be brought into cooling relationship with the MT tempering point in the operating state of the printing press depending on an ambient temperature around the cooling device.
  • the cooling relationship is preferably such that a waste heat flow of the MT temperature control point to the refrigerator and / or the cooling device can be discharged.
  • a further advantageous embodiment relates to such an arrangement in which the arrangement further comprises a cold producer , which is arranged and arranged such that by means of the cold generator of the MT temperature control point is temperature controlled.
  • a refrigerating producer preferably has a refrigerating machine, more preferably a compressor-driven refrigerating machine with an evaporator and a condenser, more preferably such an air-cooled refrigerating machine.
  • a further advantageous embodiment relates to such an arrangement in which both the MT tempering point and the NT tempering point can be tempered by means of the cold producer.
  • the cold producer is arranged such that the waste heat flow generated by the cold producer is directly transferable to the heat exchange fluid in the central heat exchange system.
  • a further advantageous embodiment relates to an arrangement in which the cold generator and the cold producer are operated with refrigerants having different evaporation temperatures and / or different condensation temperatures.
  • such an arrangement has a configuration in which the heat exchange system as described in claims A15 to A28 is described with respect to the heat exchange system.
  • the arrangement further comprises a Buffer memory, in which heat is temporarily stored in a heat storage material.
  • a further advantageous embodiment relates to such an arrangement in which the heat storage material has a larger amount of heat exchange fluid and wherein the heat exchange fluid is hydraulically in communication with the heat exchange fluid in the heat exchange system.
  • such an arrangement preferably has a design in which further preferred is a design of an arrangement in which two central heat exchange systems are provided, wherein one of the two central heat exchange systems is connected to at least one of the heat consumers, as has been set out in the heat exchange system described above , and wherein the other of the two central heat exchange systems comprises the cooling device.
  • the central heat exchange system having the cooling device can also have the same structural features, in particular with regard to the connection to the temperature control points, as the central heat exchange system, which is connected to the heat consumer.
  • FIGS. 1 to 3 which are particularly suitable to describe ways of fluid cooling, as well as on the FIGS. 4 and 5 which are particularly suitable to describe ways of supplying heat to consumers.
  • the illustrated embodiments of the FIGS. 1 to 3 are almost arbitrary with the embodiments of FIGS. 4 and 5 to combine.
  • FIG. 1a shows an overview of an inventive arrangement on a printing machine 1 and thus a system with a cold generator, which is preferably designed as a chiller, and a cooling device 3, which is presently designed as a free cooler.
  • the cooling device 3 is preferably an adiabatic free-cooling device, ie a spraying device 31 makes it possible to improve the cooling capacity by means of evaporative cooling.
  • the spraying device can preferably be supplied with water via a water pipe, for example, and is preferably only switched on if an improvement in the cooling capacity is required.
  • FIG. 1 a the illustrated printing machine on three different areas 11, 12, 13 with three different temperature levels, which are tempered via an NT temperature control point 51, an MT temperature control point 52 and an HT temperature control point 53.
  • the NT tempering point 51 and the MT tempering point 52 are in Fig. 1c shown enlarged example.
  • each of the temperature control points 51, 52, 53 have a separate primary circuit 81, which is designed so that the heat flow via a heat exchanger 681, 682 to a secondary circuit 82 can be discharged.
  • a separate primary circuit in the sense described may be designed as an open primary circuit in which the fluid is partially consumed at the temperature control point, such as e.g. in fountain solution, or as a closed primary circuit, in which at each point of the primary circuit, the inflow is equal to the outflow.
  • each or some of the temperature control points to have a circuit through which a process fluid flows, such that the heat flow is transmitted together with the circulating process agent, so that the heat flow is coupled to the flowing carrier mass of the process fluid flow.
  • Fig. 1c is exemplified by the lines which reach up to the respective tempering 51, 52 and are shown between the primary circuits 81.
  • Fig. 1c is exemplified by the lines which reach up to the respective tempering 51, 52 and are shown between the primary circuits 81.
  • these lines are components of sub-branches 65 of a central heat exchange system 6, which communicate directly with the heat exchange circuit 62, so that via a central inlet 631 of the heat exchange circuit 62 heat exchange fluid can flow into the partial inlet 651 of the partial branch 65, can reach the tempering and from there via a partial outlet 652 of the partial branch 65 can get back to a central sequence of the heat exchange circuit 62.
  • This design can be formed at the tempering "open" and / or closed.
  • the temperature-controlled heat exchange fluid can via the heat exchange circuit 62 are directed to other tempering, which may be useful, for example, in the warm-up phase of a printing press to provide the still cold other tempering the waste heat of another temperature control available.
  • This can be done directly via cross connections 653, 654 between the partial branches of the temperature control, as in FIGS. 1a and 1b is represented by the horizontally illustrated lines, which is exemplified an exchange of heat exchange fluid between the sub-branch of the NT temperature control point and the sub-branch of the MT temperature control point.
  • the transverse connection 653 leads back from the NT temperature control point to the MT temperature control point and the transverse connection 654.
  • valves 661, 664 are provided.
  • a fluid flow could also flow from the central inlet 63 via a section of the cross connection 653 to the heat exchanger 681 of the NT temperature control point in order to cool the NT temperature control point.
  • This can be especially true at low outdoor temperatures, e.g. be useful in winter, when the heat exchange circuit 62 is used for cooling and as shown with a cooling device 3 is in heat exchanging connection.
  • the heat exchange circuit 62 can be connected via the bypass line 67 and the bypass valve 671 for this purpose with the cooling device 3 or shut off from this.
  • the cold generator 2 may be preferable for the cold generator 2 to permanently cool the NT temperature control point, that is, whenever waste heat has to be dissipated.
  • the cold generator 2 is preferably designed to be so powerful that additionally at least part of the heat load of the MT cooling points can be dissipated, eg if the free cooler does not rise when the ambient temperature rises more is sufficient.
  • the intermediate circuit supplies via the cross connections 653, 654 the MT temperature control point to the cooling side of the cold generator 2.
  • the waste heat of the cold generator is preferably dissipated to the heat exchange fluid in the heat exchange circuit 62.
  • a corresponding circulation in the circuits which can change depending on the valve positions their course is preferably generated by circulation pumps, which can be switched on as needed.
  • 3-2 directional valves and associated bypasses ensure a constant temperature at the tempering points, as is illustrated by way of example with respect to the MT tempering point 52 above the heat exchanger 682.
  • the HT tempering point (s) which are to be cooled to a temperature of generally above 50 ° C. are preferably cooled all year round by means of a cooling device 3 designed as a free cooler.
  • a cooling device 3 designed as a free cooler.
  • the other temperature control points which regularly have operating temperatures which can not be cooled or uneconomically cooled all year round via a free cooler, can be shut off in the heat exchange circuit 62 in such a way that too hot a heat exchange fluid does not reach them.
  • tempering is therefore particularly advantageous that all three temperature control with each other either from the cooling capacity and / or participate in the waste heat and / or temperature over an ambient temperature without or with only a little foreign energy.
  • a printing operation can only be started when all circuits have reached the desired temperature. This is usually achieved by cooling in the NT circuit and in the MT or possibly in the HT circuit usually by heating.
  • bypass valve 671 is a 3-2 way valve (46) and only so much heat energy passes on to the free cooler that generated for the temperature of the MT and HT circuits no additional heat energy by means of electric heaters must become.
  • the potential for savings here depends inter alia on the ambient conditions and the actually required temperature levels, especially of the MT cooling points, since the operating temperature of e.g. 20-25 ° C only partially or completely can be generated via the free cooler.
  • FIG. 2 shows a comparable system as in the FIGS. 1a to 1d , So that duplicate descriptions are avoided.
  • a cold producer 4 is additionally provided, which are both designed as chillers in the illustrated embodiment.
  • Two separate chillers can further optimize the system, since the chillers can be operated at different evaporation temperatures.
  • FIG. 2 it is the chillers to water-cooled systems that deliver their waste heat to the central heat exchange system 6, for example, for further use and / or to the free cooler.
  • FIG. 3 again shows a comparable system as in the FIGS. 1a to 1d and 2 , Again, duplicate descriptions are avoided. Also in the FIG. 3 is in addition to the cold generator 2 in addition a cold producer 4 is provided, which is executed in the illustrated embodiment, however, as air-cooled chillers. Preferably, the air-cooled chiller for the average temperature level is not placed in the same room as the printing press. Again, a free cooler is also provided.
  • the MT and the HT tempering can be connected to the heat exchange circuit 62 via a - with open valve further - partial branch 65 of the heat exchange circuit 62.
  • the air-cooled chiller completely and / or partially connected to it.
  • FIG. 4 shows the arrangement with a common heat recovery through a heat consumer system 9 is supplied with heat.
  • the heat consumer 9 has a common heat exchanger 91, which is housed in the illustrated preferred embodiment in a storage tank which is at least partially filled by a heat storage material, which caches the heat emitted from the heat exchanger.
  • the heat exchanger 91 is therefore designed as a heat reservoir 92 at the same time.
  • the illustrated arrangement may preferably have a cooling system, as in relation to the central heat exchange system 6 in FIGS. 1a to 3 has been described.
  • the heat consumer system 9 shown can also be regarded as a cooling system, since heat is also removed from the printing press via the consumers.
  • the illustrated manner of the line system of the heat consumer 9 and the arrangement of the elements of the leads to the heat consumer 9 can therefore be carried out in the same way in a heat exchange system 6 according to the invention, as well as vice versa.
  • the temperature control with the heat consumer 9 preferably via mutually hydraulically separate temperature control circuits in heat exchanging relationship.
  • the individual hydraulically separated Temperierstellen circuits are preferably exemplified circulation valves 653, 654 the heat exchanger 91 can be switched.
  • a blown air cooling 7 is provided here, which is also connected to the heat exchanger 91.
  • waste heat sources e.g. the water-cooled chiller, a UV dryer, sheet baffles and the blast or compressed air supply 7 connected, since comparatively high temperature levels are generated for a meaningful use.
  • Other waste heat sources are also conceivable.
  • the heat absorbed in the heat reservoir 92 is given off to heat consumers 93 as needed.
  • the different temperature levels in the heat exchanger 91 are combined to a mixing temperature which is higher than the lowest temperature level but lower than the highest temperature level.
  • FIG. 5 shows a similar arrangement with a depending on the temperature level separately usable heat recovery.
  • FIG. 5 As shown embodiment, an example is shown how different temperature levels can be tapped and used separately by means of upstream heat exchangers. Furthermore, after the separate use of the residual heat can be summarized in a waste heat cycle and possibly stored in a downstream heat exchanger and / or buffer tank.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Control Of Temperature (AREA)
  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)

Abstract

Dispositif monté sur une machine à imprimer, présentant au moins un emplacement de thermorégulation basse température (emplacement de thermorégulation NT), au moins un emplacement de thermorégulation température moyenne (emplacement de thermorégulation MT) et au moins un emplacement de thermorégulation haute température (emplacement de thermorégulation HT), ces emplacements étant conçus et disposés respectivement dans une zone de basse température (zone NT), dans une zone de température moyenne (zone MT) et dans au moins une zone de haute température (zone HT) d'une machine à imprimer, de manière que la zone NT soit thermorégulée à basse température au moyen de l'emplacement de thermorégulation NT, la zone MT est thermorégulée à température moyenne au moyen de l'emplacement de thermorégulation MT et la zone HT est thermorégulée à haute température au moyen de l'emplacement de thermorégulation HT. Selon l'invention, la température basse est inférieure à la température moyenne, la température moyenne est inférieure à la haute température, le dispositif comporte en outre un appareil de thermorégulation basse température (appareil de thermorégulation NT) et un appareil de thermorégulation haute température (appareil de thermorégulation HT), l'emplacement de thermorégulation MT est réglable à la fois au moyen de l'appareil de thermorégulation NT et de l'appareil de thermorégulation HT.

Claims (15)

  1. Ensemble sur une machine à imprimer (1) comportant au moins une station de thermorégulation basse température (51), au moins une station de thermorégulation moyenne température (52) et au moins une station de thermorégulation haute température (53) qui sont disposées contre une zone basse température (11), une zone moyenne température (12) et au moins une zone haute température (13) d'une machine à imprimer (1) et sont conçues de telle sorte que la température de service de la zone basse température (11) peut être thermorégulée au moyen de la station de thermorégulation basse température (51) à une basse température comprise entre 5 °C et 15 °C, la température de service de la zone moyenne température (12) peut être thermorégulée au moyen de la station de thermorégulation moyenne température (52) à une température moyenne comprise entre 15 °C et 30 °C, et la température de service de la zone haute température (13) peut être thermorégulée à une haute température au moyen de la station de thermorégulation haute température (53), la basse température étant inférieure à la température moyenne,
    caractérisé en ce que la température moyenne de la zone moyenne température (12) est inférieure d'au moins 10 °C à la haute température de la zone haute température (13),
    l'ensemble comportant un système d'échange thermique central (6) qui est conçu de manière à ce que la station de thermorégulation basse température (51), la station de thermorégulation moyenne température (52) et la station de thermorégulation haute température (53) soient thermorégulables via le système d'échange thermique central (6), un système de conduites (61) du système d'échange thermique central (6) pouvant être parcouru par un fluide d'échange thermique et
    le système d'échange thermique (6) étant relié à la station de thermorégulation basse température (51), à la station de thermorégulation moyenne température (52) et à la station de thermorégulation haute température (53) de telle sorte que des flux de chaleur peuvent être transférés entre la station de thermorégulation basse température (51) et le fluide d'échange thermique, entre la station de thermorégulation moyenne température (52) et le fluide d'échange thermique et entre la station de thermorégulation haute température (53) et le fluide d'échange thermique.
  2. Ensemble selon la revendication 1, dans lequel l'ensemble comporte également un producteur de froid (2) qui est disposé et structuré de telle sorte que la station de thermorégulation basse température (51) est thermorégulable au moyen du producteur de froid (2).
  3. Ensemble selon la revendication 2, dans lequel la station de thermorégulation basse température (51) ainsi que la station de thermorégulation moyenne température (52) sont thermorégulables au moyen du producteur de froid (2).
  4. Ensemble selon une des revendications précédentes 2 à 3, dans lequel le producteur de froid (2) est disposé de telle sorte que le flux de chaleur dissipée produit par le producteur de froid (2) peut être transmis directement au fluide d'échange thermique dans le système d'échange thermique central (6).
  5. Ensemble selon une des revendications précédentes 1 à 4, dans lequel l'ensemble comporte également un dispositif réfrigérant (3).
  6. Ensemble selon la revendication 5, dans lequel la station de thermorégulation haute température (53) ainsi que la station de thermorégulation moyenne température (52) sont thermorégulables au moyen du dispositif réfrigérant (3).
  7. Ensemble selon une des revendications précédentes 5 à 6, dans lequel le producteur de froid (2) et le dispositif réfrigérant (3) peuvent être amenés à l'état de fonctionnement de la machine à imprimer (1) en fonction d'une température ambiante adjacente au dispositif réfrigérant dans une relation réfrigérante avec la station de thermorégulation moyenne température (52).
  8. Ensemble selon une des revendications précédentes 5 à 7, lequel est conçu de telle sorte qu'un flux de chaleur peut être transmis de la station de thermorégulation moyenne température (52) et/ou de la station de thermorégulation haute température (53) au dispositif réfrigérant (3) via le fluide d'échange thermique dans le système d'échange thermique (6).
  9. Ensemble selon une des revendications précédentes 1 à 8, dans lequel le système d'échange thermique central (6) comporte un circuit d'échange thermique (62) avec une amenée centrale (63) et une sortie centrale (64), plusieurs embranchements partiels positionnés parallèlement (65) s'étendant entre l'amenée centrale (63) et la sortie centrale (64), une amenée partielle (651) d'un embranchement partiel (65) s'étendant vers une des stations de thermorégulation (51, 52, 53), une sortie partielle (652) d'un embranchement partiel (65) étant dirigée de la station de thermorégulation (51, 52, 53) vers la sortie centrale (64), de telle sorte qu'un courant fluidique d'échange thermique central dans l'amenée centrale peut être divisé en différents courants fluidiques d'échange thermique, les différents courants fluidiques d'échange thermique pouvant être amenés à différentes stations de thermorégulation (51, 52, 53) et les différents courants fluidiques d'échange thermique pouvant être ramenés depuis les différentes stations de thermorégulation (51, 52, 53) dans la sortie centrale (64) vers le courant fluidique d'échange thermique central.
  10. Ensemble selon la revendication 9, dans lequel au moins un des embranchements partiels (65) peut être fermé par une soupape (661).
  11. Ensemble selon une des revendications 1 à 10, dans lequel au moins une partie du flux de chaleur transmis au fluide d'échange thermique peut être évacuée vers un dissipateur de chaleur (93), et la partie évacuable du flux de chaleur peut être extraite en particulier dans la sortie partielle d'un embranchement partiel (65).
  12. Ensemble selon une des revendications 5 à 11, dans lequel le dispositif réfrigérant (3) comporte un circuit de refroidissement séparé qui est en relation d'échange thermique via un échangeur thermique avec le courant fluidique d'échange thermique, le circuit de refroidissement séparé pouvant être commandé par une soupape de circuit de refroidissement.
  13. Ensemble selon une des revendications précédentes 1 à 8, dans lequel le système d'échange thermique central (6) est en relation d'échange thermique avec différents circuits de stations de thermorégulation hydrauliquement séparés du système d'échange thermique central (6).
  14. Ensemble selon la revendication 13, dans lequel au moins une partie du flux de chaleur transmis au fluide d'échange thermique peut être évacuée vers un dissipateur de chaleur (93), ou dans lequel au moins une partie d'un flux de chaleur dissipée produit sur une des stations d'exploitation peut être évacuée vers un dissipateur de chaleur (93), l'ensemble étant conçu de telle sorte que ce flux de chaleur dissipée peut être évacué d'une station du circuit respectif de stations de thermorégulation, laquelle est agencée en aval de la station d'exploitation avant le système d'échange thermique central (6).
  15. Ensemble selon une des revendications 1 à 15, dans lequel l'ensemble comporte de plus un réservoir d'accumulation dans lequel la chaleur peut être stockée temporairement dans un matériau d'accumulation de chaleur.
EP08847011A 2007-11-07 2008-11-07 Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température Not-in-force EP2209631B1 (fr)

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DE102007053080A DE102007053080A1 (de) 2007-11-07 2007-11-07 Temperiersystem für Druckmaschinen mit mehreren Temperaturniveaus
PCT/EP2008/009420 WO2009059787A2 (fr) 2007-11-07 2008-11-07 Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température

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CN105799311B (zh) * 2016-03-21 2018-04-13 安徽工程大学 一种印刷机印版温度控制装置及其温度控制方法
DE102018001132A1 (de) * 2018-02-12 2019-08-14 Harburg-Freudenberger Maschinenbau Gmbh Verfahren und Vorrichtung zur Ventilsteuerung
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CN109677103A (zh) * 2019-03-05 2019-04-26 昆山侨通印务有限公司 一种胶印机水箱水温地下降温系统
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Publication number Publication date
EP2527147A1 (fr) 2012-11-28
US20110088879A1 (en) 2011-04-21
EP2209631A2 (fr) 2010-07-28
CN101883679A (zh) 2010-11-10
EP2527147B1 (fr) 2014-06-04
CN101883679B (zh) 2013-06-05
DE102007053080A1 (de) 2009-05-20
WO2009059787A2 (fr) 2009-05-14
WO2009059787A3 (fr) 2009-11-12

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