EP2527147B1 - Tempering system for printers with multiple temperature levels - Google Patents

Description

Field of the invention

The invention relates to an arrangement on a printing machine for temperature control of operating points of the printing press with different operating temperatures.

Background of the invention and prior art

Various systems exist in the prior art which are used to control the temperature of individual fluids used on printing presses or individual areas of printing presses.

So will in the DE 4426077 a system with two refrigerators described.

The DE 10316860 and the WO 2006072558 publish systems with heat recovery.

In view of the increasing environmental awareness and the development of energy prices, however, further improvements are being sought as to how the heat and mass transfer to printing presses can be further optimized.

task

It is therefore an object of the invention to effectively temper the process heat of different operating points on a printing machine and to make reasonable use of the process heat arising at the operating points economically and ecologically.

Solution of the task

The object is solved by the arrangement according to the independent claim 1. Advantageous embodiments are disclosed in the subclaims.

A first example, which is not the subject of the claimed invention, relates to an arrangement on a printing machine having 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 arranged on a low-temperature region (NT region), a middle temperature region (MT region) and at least one high-temperature region (HT region) of a printing press and are designed in such a way that the NT region is cooled to a low temperature by means of the NT tempering point. by means of the MT tempering point the MT range can be tempered to a middle temperature and by means of the HT tempering point 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 flowed through 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 between the NT tempering point and the heat exchange fluid, between the MT tempering point and the heat exchange fluid and between the HT tempering point and the Heat exchange fluid are transferable.

The embodiment has the advantage that heat which has been transferred to the heat exchange fluid can be made available to other temperature control points which are to be heated. This can be advantageous, in particular, during a start-up process in which various areas have not yet been brought to operating temperature.

In such an arrangement, in principle, each of the temperature control as a be formed separate primary circuit, which is designed so that the heat flow via a heat exchanger to a secondary circuit can be discharged. Such 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. However, 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, cleaning agent, gear oil and / or other fluids which are used for cooling certain components.

Also conceivable is a design of the temperature control, in which the two designs are combined. 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.

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 recycled. 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". In addition, such an NT region 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 be tempered in the described case preferably also with fountain solution but also with another process agent.

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 consideration also applies to the interposition of a chiller. In the chiller, the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression and then passes through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid. However, 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.

The 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. However, 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 preferably at least 10 ° C. Particularly preferably, the operating temperature of the NT range between 5 ° C and 15 ° C is particularly 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. With regard to the MT range, the operating temperature is preferably between 15 ° C and 30 ° C, 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).

Also preferred is an embodiment of the arrangement in which 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. Such 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.

Preferably, such an arrangement has a design 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.

Also preferred is such an arrangement, wherein 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. Such a heat exchanger may for example be a free cooler. By free-cooler temperature control device is meant a device that exploits approximately 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 Adiabatfreikühler which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatfreikühlers, 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 in a controlled manner depending on 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.

Further preferred is a design of 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.

Furthermore, 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.

Also preferred is an embodiment of the arrangement in which the cold generator and the cooling device in the operating state of the printing machine in dependence on an ambient temperature around the cooling device with the MT tempering point in cooling relationship can be brought. Here, 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.

Also preferred is an embodiment of the 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. 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 by means of the cold producer both the MT tempering point and the NT tempering point is temperature controlled.

Preferably, 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.

Furthermore, such an arrangement is preferred in which 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 Temperature control points runs, wherein a partial flow of a partial branch of the tempering leads coming to the central outlet, such that a central heat exchange fluid flow in the central inlet into different heat exchange fluid partial streams can be divided, the different heat exchange fluid partial streams different Temperierstellen zuleitbar and wherein the different heat exchange fluid partial streams coming from the different tempering in the central flow are again merge to the central heat exchange fluid flow. In this case, 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 unite in the flow direction behind the last partial flow all heat exchange fluid partial streams in the last section of the central flow.

Further preferred is a design of an arrangement in which at least one of the partial branches can be shut off via a valve. The valve is preferably in Dependent on the operating temperature and the temperature of the incoming central heat exchange fluid flow and / or the incoming heat exchange fluid partial flow, 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.

Furthermore, 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. Such heat consumers may e.g. a heater for a Farbreibertemperiergerät 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.

Also preferred is an embodiment of the arrangement in which the dischargeable part of the heat flow in the partial sequence of a sub-branch can be removed. Preferably, 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. Furthermore, it is preferred that 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.

Also preferred is an embodiment of the arrangement in which the Cooling device has a separate cooling circuit, which is connected via a heat exchanger with the heat exchange fluid flow in heat exchanging relationship, wherein the separate cooling circuit is 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.

Preferably, such an arrangement has a configuration in which the central heat exchange system is in heat exchanging relationship with individual temperature control 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. In this preferred embodiment, the fluid circuits remain separate and can therefore be e.g. be operated 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. In this case, in the central heat exchange system preferably a central heat exchanger may be provided, which is in heat exchanging relationship with several or all of the temperature control circuits, wherein the heat flows of the respective temperature control circuits are transferred to a provided in the central heat exchanger heat exchange fluid. Thus, in this preferred embodiment, the different temperature levels in the temperature control loop are standardized to a temperature of the heat exchange fluid in the central heat exchanger.

Furthermore, such an arrangement is preferred, in which the heat-exchanging relationship between one of the separate temperature control point circuits and the central heat exchange system is designed to be separable, in such a way that no heat flow is transferable from the tempering point circuit to the central heat exchange system. 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. Such a heat consumer may e.g. a heater for a Farbreibertemperiergerät and / or preheating device, the e.g. can be used for preheating of thermo air, which e.g. can be used to dry the printed substrate.

Furthermore, 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. Preferably, 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. In this case, heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer. Preferably, 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. Furthermore, it is preferred that 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.

Furthermore, 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.

Also preferred is an embodiment of the 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.

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.

Also preferred is an embodiment of the arrangement in which 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.

Preferably, such an arrangement has a design in which two central heat exchange systems are provided, one of the two central heat exchange systems being provided for supplying heat consumers with heat, as described above, and the other of the two central ones Heat exchange systems comprising the cooling device.

In the following example and the following aspect according to the present invention, substantially the same terminology is used. The statements made above with regard to individual terms, advantages and embodiments therefore also apply to the following aspects.

A second example, which is not the subject of the claimed 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). Tempering point), which are arranged 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 and designed such that by means of the NT temperature control of the NT range to a low temperature by means of the MT tempering point the MT range can be tempered to a middle temperature and by means of the HT tempering point 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.

This design has the advantage that, for example, 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, while the HT tempering 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 can advantageously be designed such 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 becomes.

In this case, 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. However, 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 preferably at least 10 ° C. Particularly preferably, the operating temperature of the NT range between 5 ° C and 15 ° C is particularly 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. With regard to the MT range, the operating temperature is preferably between 15 ° C and 30 ° C, 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).

Also preferred is an embodiment of the arrangement in which the 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, for example, the actual and / or desired temperature of the MT operating point and / or achievable by the HT tempering device Be tempering. This temperature range may in turn depend on the temperature of a heat exchange fluid. It is also conceivable that if the HT temperature control device is a free-cooling device, as described above, such a parameter is the ambient temperature around the free cooler.

Preferably, such an arrangement has a design in which the NT temperature control device has a cold generator. Such a cold generator preferably has a chiller, more preferably a compressor-driven chiller with a condenser.

Also preferred is an embodiment of the arrangement in which 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. 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 through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid. However, 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.

Preferably, 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. Such a heat exchanger may e.g. to be a free cooler. By 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, cleaning agent, gear oil and / or other fluids which are used for cooling certain components. A freecooler can preferably be designed as Adiabatfreikühler which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatfreikühlers, 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.

Furthermore, such an arrangement is preferred in which 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 state of the printing press is in a permanently cooling relationship with the HT tempering point.

Also preferred is an embodiment of the arrangement in which 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, the MT tempering and the HT tempering point is in communication such that heat flows both between the NT tempering and the heat exchange fluid and 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 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.

Preferably, 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.

Also preferred is such an arrangement in which 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 is directly transferable to the heat exchange fluid in the central heat exchange system.

Further preferred is a design of an arrangement in which the cold generator and the refrigeration producer are operated with refrigerants having different evaporation temperatures and / or different condensation temperatures.

Furthermore, 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. In this case, 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.

Also preferred is an embodiment of the arrangement in which at least one of the sub-branches can be shut off via a valve. Preferably, the 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.

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. Such heat consumers may e.g. a heater for a Farbreibertemperiergerät 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. Preferably, 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. Furthermore, it is preferred that 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.

Furthermore, an embodiment of the arrangement in which the 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.

Preferably, 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 temperature control point.

Also preferred is such an arrangement wherein the 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 means, without flow connection, via which a heat flow together with a fluid flow would be transferable. In this preferred embodiment, the fluid circuits remain separate and can therefore be e.g. be operated 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. In this case, 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. Thus, in this preferred embodiment, 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. In this case, the valve is preferably in dependence on the operating temperature at the respective operating point and the temperature of the heat exchange fluid in the central Heat exchanging system designed controllable, 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.

Further preferred is a design of 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. Such heat consumers may e.g. a heater for a Farbreibertemperiergerät 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.

Furthermore, 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. Preferably, 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. In this case, heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer. Preferably, 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. Furthermore, it is preferred that 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.

Also preferred is an embodiment of the arrangement in which the Cooling device is directly traversed by the heat exchange fluid flow, wherein the heat exchange fluid flow is passed over a controllable with a bypass valve by-pass line to the cooling device.

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.

Also preferred is an embodiment of the 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 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.

Preferably, such an arrangement has a configuration in which the heat storage material has a larger amount of heat exchange fluid.

Also preferred is such an arrangement wherein two central heat exchange systems are provided, one of the two central heat exchange systems being for supplying heat consumers with heat, as described above, and the other of the two central heat exchange systems having the cooling device.

The statements made above with regard to individual terms, advantages and designs Therefore, apply to the following aspect of the invention.

The present invention relates to an arrangement on a printing press having at least one low-temperature tempering point and at least one middle temperature tempering, which are arranged at a low temperature range and a medium temperature range of the printing press and designed such that by means of the low-temperature tempering the operating temperature of the low-temperature range a low temperature between 5 ° C and 15 ° C and by means of the medium temperature control point the operating temperature of the medium temperature range to a mean temperature between 15 ° C and 30 ° C is temperature controlled, the low temperature is lower than the mean temperature,
wherein the low-temperature tempering point and the middle temperature 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 low-temperature temperature control point and the middle temperature control point, at least partly transferable to the heat consumer system,
wherein 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 discharged, and
wherein the arrangement is designed such that for at least one of the heat-conducting fluid streams coming from the tempering a Temperierstellen cycle is provided which is formed hydraulically separated from the central heat reservoir.

"At least partially transferable" in the sense preferably means that at least one partial waste heat flow from each of the two temperature control points can be transmitted to the heat consumption system. 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, insofar 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 examples.

Furthermore, an embodiment of the arrangement is preferred in which 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 temperature controlled to a high temperature, wherein the high temperature is higher than the low temperature and higher than the middle temperature. The difference between the NT range and the MT range is preferably at least 5 ° C. The difference between the MT range and the HT range is preferably at least 10 ° C. Particularly preferably, the operating temperature of the NT range is 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. With regard to the MT range, the operating temperature 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).

Preferably, 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 Temperierstellenleitungen the central heat exchange system, wherein the fluid streams in the central heat exchange system unite. As a result, a large heat buffer, from which the heat consumer system can be fed, can preferably be created in the heat reservoir.

Furthermore, such an arrangement is preferred in which at least part of a waste heat flow occurring at one of the temperature control 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 of the Temperierstelle downstream in front of the central Heat reservoir is arranged.

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. 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.

Also preferred is a design of an arrangement in which at least part of a waste heat flow occurring at one of the temperature control points can be dissipated to a heat consumer without being transmitted to the central heat reservoir, wherein the arrangement is designed such that this waste heat flow or partial waste heat flow from one Location of the respective temperature control circuit can be discharged, which is arranged by the temperature control point downstream of the central heat reservoir. Preferably, 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. In this case, heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer. Preferably, 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. Furthermore, it is preferred that 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 are.

Furthermore, 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 through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid. However, 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.

Also preferred is an embodiment of the arrangement in which 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. Such a refrigerator preferably comprises a refrigerator and more preferably a compressor-driven refrigerator with a condenser.

Also preferred is an embodiment of the arrangement in which 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. The term waste heat stream in the sense is to be understood as meaning that both the term recorded by the cold generator and the term used in the term are to be understood Heat - ie the "generated" cold - as well as the heat loss produced by the refrigerator is included.

Preferably, 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. Such a heat exchanger may for example be a free cooler. By 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 fluids are any fluids that 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 Adiabatfreikühler which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatfreikühlers, 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.

Furthermore, such an arrangement is preferred in which 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.

Further preferred is a design of an arrangement in which the cooling device in the operating condition of the printing press in a permanently cooling relationship to the HT tempering point is.

Furthermore, 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.

Also preferred is an embodiment of the 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.

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. Such 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.

Also preferred is an embodiment of the arrangement 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.

A further advantageous embodiment relates to an arrangement in which the cold producer and the cold producer with refrigerants with different evaporation temperatures and / or different condensation temperatures operate.

Preferably, such an arrangement has a configuration in which the heat exchange system is as described above with respect to the heat exchange system.

Also preferred is such an arrangement, wherein 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.

Further preferred is an arrangement 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 set out with respect to the heat exchange system described above, and wherein the other of the two central heat exchange systems Cooling device has. 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.

The remarks made in relation to the first example are analogous to the separation of consumer circuit and cooling circuit described here by two central heat exchange systems.

Brief description of the drawings

In the following, individual particularly preferred embodiments of the invention and examples are described by way of example. Some of the described embodiments have features that are not necessarily required to practice the present invention or example, but which are generally considered preferred. Thus, embodiments are also considered to be covered by the teaching of the invention, which does not have all the features of the embodiments described below. Similarly, it is conceivable to selectively combine features described with respect to different embodiments.

This applies in particular to the embodiments of 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. 1 a

eine schematische Darstellung einer Anordnung mit einer Fluidkühlung, welche dazu geeignet ist, insbesondere die ersten beiden Beispiele zu beschreiben,

Fig. 1 b bis 1 d

vergrößerte Ausschnitte aus Fig. 1 a

Fig. 2

eine schematische Darstellung einer Anordnung mit einer Fluidkühlung, welche dazu geeignet ist, insbesondere die ersten beiden Beispiele zu beschreiben,

Fig. 3

eine schematische Darstellung einer Anordnung mit einer Fluidkühlung, welche dazu geeignet ist, insbesondere die ersten beiden Beispiele zu beschreiben,

Fig. 4

eine schematische Darstellung einer bevorzugten Ausführungsform einer erfindungsgemäßen Anordnung mit einer Verbraucherversorgung, und

Fig. 5

eine schematische Darstellung einer weiteren bevorzugten Ausführungsform einer erfindungsgemäßen Anordnung mit einer Verbraucherversorgung.

In the figures show:

Fig. 1 a

1 a schematic representation of an arrangement with a fluid cooling, which is suitable for describing in particular the first two examples,

Fig. 1 b to 1 d

enlarged sections Fig. 1 a

Fig. 2

1 a schematic representation of an arrangement with a fluid cooling, which is suitable for describing in particular the first two examples,

Fig. 3

a schematic representation of an arrangement with a Fluid cooling, which is suitable for describing in particular the first two examples,

Fig. 4

a schematic representation of a preferred embodiment of an inventive arrangement with a consumer supply, and

Fig. 5

a schematic representation of another preferred embodiment of an inventive arrangement with a consumer supply.

Detailed description of the drawing

FIG. 1a shows an overview of an arrangement on a printing machine 1 and thus a system with a cold generator, which is preferably designed as a refrigerator, and a cooling device 3, which is presently designed as a free cooler. As in Figure 1d As can be seen more clearly, 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.

In FIG. 1a For example, the illustrated printing machine has three different regions 11, 12, 13 with three different temperature levels, which can be temperature-controlled 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.

In such an arrangement, as in Figure 1c only exemplary in terms of the temperature control points 51, 52 is shown, in principle, each of the temperature control 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.

Furthermore, it is fundamentally conceivable that each or some of the temperature control points 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. This is in Fig. 1c is exemplified by the lines, which extend to the respective temperature control points 51, 52 and are shown between the primary circuits 81. As in Fig. 1a can be seen, 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 sub-inlet 651 of the sub-branch 65, can reach the tempering and from there via a partial outlet 652 of the partial branch 65, it is possible to get back to a central outlet of the heat exchange circuit 62. This design can be formed at the tempering "open" and / or closed.

As shown, therefore, both configurations of the temperature control can be advantageously combined. However, this is not absolutely necessary, so that one of the designs can be sufficient.

The so-tempered heat exchange fluid can be passed through the heat exchange circuit 62 to other temperature control, which may be useful, for example in the warm-up of a printing press to the still cold other tempering the waste heat of another temperature control available put. This can be done directly via cross connections 653, 654 between the partial branches of the temperature control, as in the FIGS. 1 a and 1b is shown 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. In this case, the transverse connection 653 leads back from the NT temperature control point to the MT temperature control point and the transverse connection 654.

In order to redirect the fluid flow accordingly, valves 661, 664 are provided. With a corresponding design of the valve 661 and depending on the valve position, 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. in winter, be useful if the heat exchange circuit 62 is used for cooling and as shown with a cooling device 3 is in heat exchanging connection. As required, 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.

Depending on the minimum outside temperature at the operating times, it 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.

Since an NT temperature control point can generally be cooled to about 10 ° C., 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, e.g. when the free cooler is no longer sufficient when the ambient temperature rises.

In this case, 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 2, in turn, 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.

Preferably, in the individual tempering points, 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. It is also advantageous if the other temperature control, which regularly have operating temperatures that can not be cooled over a free cooler or only uneconomical year-round, in the heat exchange circuit 62 are shut off such that too warm a heat exchange fluid does not reach them.

In such a 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.

Thus, e.g. a printing operation will not start until 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.

In the present circuit, it is now possible to use the accumulating waste heat for temperature control of each higher-lying from the temperature level circuit via the internal recirculation circuit.

In this case, a configuration may be preferred in which the bypass valve 671 is a 3-2 way valve (46) and only passes on so much heat energy to the free cooler that no additional heat energy generated by electric heaters for the temperature of the MT and HT circuits got to.

Once the working temperature of the printing machine 1 is reached and the printing process itself is completed by e.g. Walk-work and / or drive motors generated waste heat, it is desirable for energetic reasons that the free cooler gives off as much heat energy as possible to the environment.

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. In the figure, in addition to the cold generator 2, 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.

Since a chiller typically works more energetically more efficiently the higher the vaporization temperature (possible due to higher water temperatures), it has been found that there are energetic benefits to having fluid temperatures of e.g. 10 ° C and 20-25 ° C with separate chillers produced.

In addition, here too, a heat exchanger 684-by way of example-is provided only in a hydraulically separated circuit of the MT temperature control point in order to be able to deliver heat exclusively or partially via the free cooler. If necessary, this heat exchanger 684 can be switched off by a 2-way valve shown.

As in FIG. 2 can be seen, 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 an air-cooled refrigerating machine. 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.

About a valve, which in Fig. 3 is shown below the air-cooled refrigerator, 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. In this case, both the free cooler and / or depending on the ambient temperature, the air-cooled chiller completely and / or partially connected to it.

FIG. 4 shows the arrangement with a common heat recovery through which a heat consumer system with heat can be supplied. The heat consumer system has a common heat exchanger 91, which in the illustrated preferred embodiment is accommodated in a storage tank which is at least partially filled by a heat storage medium which temporarily stores the heat emitted by the heat exchanger. The heat exchanger 91 is therefore designed as a heat reservoir 92 at the same time. Like in the FIG. 4 is shown, are attached to the heat reservoir 92, for example, above and below lines through which heat consumers can be supplied with thermal fluid.

True, is in FIG. 4 can be seen that 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. However, the heat consumer system 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 system and the arrangement of the elements of the leads to the heat consumer system can therefore be carried out in the same way in a heat exchange system 6 according to the invention, as well as vice versa.

In the presentation of FIG. 4 are the temperature control with the heat consumer system preferably via mutually hydraulically separate Temperierstellen 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.

In addition to the previously described tempering a blown air cooling 7 is provided here, which is also connected to the heat exchanger 91.

As shown, further 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.

In the illustrated heat recovery, 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.

Here are in the in FIG. 5 shown heat recovery individual consumers via their own supply circuits with the respective waste heat source, eg the individual temperature control connected. As a result, the individual consumers, advantageously a waste heat source can be assigned, which, for example, a preferred Temperature level has. A residual heat flow, which was not taken from the respective fluid flow coming from the temperature control point, is fed here via a common fluid circuit to the heat exchanger 91, which is also embodied here as a heat reservoir 92.

To the leading away from the heat reservoir 92 lines preferably further heat consumers and / or a cooling device can be connected.

At the in 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.

LIST OF REFERENCE NUMBERS

1

press

11

Low temperature range (NT range)

12

Mean temperature range (MT range)

13

High temperature range (HT range)

2

cold generator

3

cooler

31

sprayer

4

cold producer

51

Low-temperature tempering point (NT tempering point),

52

Medium temperature tempering point (MT tempering point)

53

High-temperature tempering point (HT tempering point)

6

central heat exchange system

61

Pipe system of the central heat exchange system

62

Heat exchange circuit

63

central inlet

631

Part of the central inlet

64

central process

641

Part of the central process

65

subbranch

651

part feed

652

partial delivery

653

Partial branch valve

654

Partial branch valve

661-669

Valve

67

bypass line

671

bypass valve

681-689

heat exchangers

7

Blast air / compressed air

81

primary circuit

82

secondary circuit

91

Heat consumer heat exchanger in the respective temperature control circuit

92

central heat reservoir

93

heat consumer

94

Feed-in circle of the heat consumer

Claims (12)

1. An arrangement on a printing machine, comprising at least one low-temperature temperature control point (51) and at least one medium-temperature temperature control point (52), which are arranged in a low-temperature zone (11) and a medium-temperature zone (12) of a printing machine (1) and are designed such that the operating temperature of the low-temperature zone (11) can be controlled to a low temperature between 5°C and 15°C by means of the low-temperature temperature control point (51) and the operating temperature of the medium-temperature zone (12) can be controlled to a medium temperature between 15°C and 30°C by means of the medium-temperature temperature control point (52), the low temperature being lower than the medium temperature,
   wherein the low-temperature temperature control point (51) and the medium-temperature temperature control point (52) are connected to a heat-consuming system via a central heat exchange system (6) that can be flown through by a heat exchange fluid such that the exhaust heat streams occurring in the temperature control at the low-temperature temperature control point (51) and the medium-temperature temperature control point (52) can be transferred at least partly to the heat-consuming system,
   wherein the arrangement further comprises a central heat reservoir (92), wherein heat consumers (63, 64, 91; 93) are connected to the central heat reservoir (92), to which the heat from the central heat reservoir (92) can be dissipated
   wherein the arrangement is designed such that for at least one of the heat-dissipating fluid streams from the temperature control points (51, 52) there is provided a temperature control point circuit, which is formed in a hydraulically separated manner from the central heat reservoir (92).
2. The arrangement according to claim 1, wherein the arrangement is designed such that heat-dissipating fluid streams from the temperature control points are supplied to the central heat exchange system (6) via temperature control point pipes, wherein the fluid streams unite in the central heat exchange system (6).
3. The arrangement according to claim 2, in which at least part of an exhaust heat flow occurring at one of the temperature control points (51, 52) can be dissipated to a heat consumer, wherein the arrangement is designed such that this exhaust heat flow or partial exhaust heat flow can be dissipated from a point of the respective temperature control point pipe which is arranged downstream of the temperature control point (51, 52) before the central heat reservoir (92).
4. The arrangement according to one of the preceding claims, in which at least part of an exhaust heat flow occurring at one of the temperature control points (51, 52) can be dissipated to a heat consumer without being transferred to the central heat reservoir (92), wherein the arrangement is designed such that this exhaust heat flow or partial exhaust heat flow can be dissipated from a point of the respective temperature control point circuit which is arranged downstream of the temperature control point (51, 52) before the central heat reservoir (92).
5. The arrangement according to one of the preceding claims, wherein the heat exchange system (6) is connected to at least two temperature control points (51, 52) such that an exhaust heat stream can be transferred from one of the at least two temperature control points (51, 52) to the other of the at least two temperature control points (51, 52) via the heat exchange fluid.
6. The arrangement according to one of claims 1 to 5, wherein the arrangement further comprises a cold generator arranged and designed such that the low-temperature temperature control point (51) can be temperature controlled by means of the cold generator.
7. The arrangement according to claim 6, wherein both the low-temperature temperature control point (51) and the medium-temperature temperature control point (52) can be temperature controlled by means of the cold generator.
8. The arrangement according to one of the preceding claims 6 or 7, wherein the cold generator is arranged such that the exhaust heat flow generated by the cold generator can directly be transferred to the heat exchange fluid in the central heat exchange system (6).
9. The arrangement according to one of the preceding claims, wherein the arrangement further comprises a high-temperature temperature control point (53), which is arranged in a high-temperature zone (13) of the printing machine (1) and is designed such that the operating temperature of the high-temperature zone (13) can be controlled to a high temperature by means of the high-temperature temperature control point (53), the medium temperature of the medium-temperature zone (12) being at least 10°C lower than the high temperature of the high-temperature zone (13), wherein the arrangement further comprises a cooling device (3) and wherein both the high-temperature temperature control point (53) and the medium-temperature temperature control point (52) can be temperature controlled by means of the cooling device (3).
10. The arrangement according to one of the preceding claims, wherein the arrangement further comprises a cold producer arranged and designed such that the medium-temperature temperature control point (52) can be temperature controlled by means of the cold producer, wherein the cold producer is arranged such that the exhaust heat stream generated by the cold producer can be transferred to the heat exchange fluid in the central heat exchange system (6).
11. The arrangement according to one of the preceding claims, as far as dependent on claim 6, wherein the arrangement further comprises a cold producer arranged and designed such that the medium-temperature temperature control point (52) can be temperature controlled by means of the cold producer, wherein the cold generator and the cold producer are operated with coolants having different evaporation temperatures and/or different condensation temperatures.
12. The arrangement according to one of the preceding claims, wherein the arrangement further comprises a buffer storage in which heat can be temporarily stored in a heat storage substance.

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