U.S. patent application number 12/741670 was filed with the patent office on 2011-04-21 for temperature control system for printing machines having several temperature levels.
This patent application is currently assigned to TECHNOTRANS AG. Invention is credited to Andreas Harig.
Application Number | 20110088879 12/741670 |
Document ID | / |
Family ID | 40560545 |
Filed Date | 2011-04-21 |
United States Patent
Application |
20110088879 |
Kind Code |
A1 |
Harig; Andreas |
April 21, 2011 |
Temperature Control System for Printing Machines Having Several
Temperature Levels
Abstract
An arrangement on a printing machine, includes at least one
low-temperature (NT), medium-temperature (MT) and high-temperature
(HT) temperature control point, which are arranged in a
low-temperature (NT), a medium-temperature (MT), and at least one
high-temperature (HT) zone of a printing machine and are designed
such that the NT zone can be controlled to a low temperature by the
NT temperature control point, the MT zone to a medium temperature
by the MT temperature control point, and the HT zone to a high
temperature by the HT temperature control point, the low
temperature being lower than the medium temperature, and the medium
temperature being lower than the high temperature. The arrangement
includes a low-temperature (NT) temperature control device and a
high-temperature (HT) temperature control device. The temperature
at the MT temperature control point can be controlled by both the
NT and the HT temperature control device.
Inventors: |
Harig; Andreas; (Augustdorf,
DE) |
Assignee: |
TECHNOTRANS AG
Sassenberg
DE
|
Family ID: |
40560545 |
Appl. No.: |
12/741670 |
Filed: |
November 7, 2008 |
PCT Filed: |
November 7, 2008 |
PCT NO: |
PCT/EP2008/009420 |
371 Date: |
May 6, 2010 |
Current U.S.
Class: |
165/104.33 |
Current CPC
Class: |
B41F 13/22 20130101 |
Class at
Publication: |
165/104.33 |
International
Class: |
F28D 15/00 20060101
F28D015/00 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 7, 2007 |
DE |
102007053080.5 |
Claims
1. An arrangement on a printing machine, comprising at least one
low-temperature NT temperature control point, at least one
medium-temperature MT temperature control point, and at least one
high-temperature HT temperature control point, which are arranged
in a low-temperature NT zone, a medium-temperature MT zone, and at
least one high-temperature HT zone, respectively, of a printing
machine and are designed such that the NT zone is adapted to be
controlled to a low temperature by the NT temperature control
point, the MT zone to a medium temperature by the MT temperature
control point, and the HT zone to a high temperature by the HT
temperature control point, the low temperature being lower than the
medium temperature and the medium temperature being lower than the
high temperature, wherein the arrangement comprises a central heat
exchange system designed such that the NT temperature control
point, the MT temperature control point, and the HT temperature
control point are adapted to be temperature controlled via the
central heat exchange system, the central heat exchange system
including a pipe system through which a heat exchange fluid passes,
and wherein the heat exchange system is connected with the NT
temperature control point, the MT temperature control point, and
the HT temperature control point such that heat flows are adapted
to be transferred between the NT temperature control point and the
heat exchange fluid, between the MT temperature control point and
the heat exchange fluid, and between the HT temperature control
point and the heat exchange fluid.
2. The arrangement according to claim 1, wherein the arrangement
further comprises a cold generator arranged and designed such that
the NT temperature control point is adapted to be further
temperature controlled by the cold generator.
3. The arrangement according to claim 2, wherein both the NT
temperature control point and the MT temperature control point are
adapted to be further temperature controlled by the cold
generator.
4. The arrangement according to claim 2, wherein the cold generator
is arranged such that exhaust heat flow generated by the cold
generator is adapted to directly be transferred to the heat
exchange fluid in the central heat exchange system.
5. The arrangement according to claim 1, wherein the arrangement
further comprises a cooling device.
6. The arrangement according to claim 5, wherein both the HT
temperature control point and the MT temperature control point are
adapted to be further temperature controlled by the cooling
device.
7. (canceled)
8. (canceled)
9. The arrangement according to claim 2, wherein the arrangement
further comprises a cooling device, and wherein the cold generator
and the cooling device, in an operating state of the printing
machine, are adapted to be brought into a cooling relationship with
the MT temperature control point dependent on an ambient
temperature around the cooling device.
10. The arrangement according to claim 5, wherein the arrangement
is designed such that a heat flow is adapted to be transferred from
at least one of the MT temperature control point and the HT
temperature control point to the cooling device via the heat
exchange fluid in the central heat exchange system.
11. (canceled)
12. (canceled)
13. (canceled)
14. (canceled)
15. The arrangement according to claim 1, wherein the central heat
exchange system comprises a heat exchange circuit with a central
inlet and a central outlet, wherein several, parallel partial
branches extend between the central inlet and the central outlet,
wherein a partial inlet of a partial branch passes to one of the
temperature control points, wherein a partial outlet of a partial
branch, coming from said one of the temperature control points,
leads to the central outlet such that a central heat exchange fluid
flow in the central inlet is adapted to be divided into different
heat exchange fluid partial flows, wherein the different heat
exchange fluid partial flows are adapted to be fed to different
temperature control points, and wherein the different heat exchange
fluid partial flows, coming from the different temperature control
points, are adapted to be brought together again in the central
outlet to form the central heat exchange fluid flow.
16. The arrangement according to claim 15, wherein at least one of
the partial branches is adapted to be cut off via a valve.
17. The arrangement according to claim 15, in which at least part
of the heat flow transferred to the heat exchange fluid is adapted
to be dissipated to a heat consumer.
18. The arrangement according to claim 17, wherein the part of the
heat flow that is adapted to be dissipated is adapted to be removed
from the partial outlet of a partial branch.
19. (canceled)
20. The arrangement according to claim 5, wherein the cooling
device comprises a separate cooling circuit in heat-exchanging
relationship with the heat exchange fluid flow via a heat
exchanger, and wherein the separate cooling circuit is adapted to
be controlled via a cooling circuit valve.
21. (canceled)
22. The arrangement according to claim 1, wherein the central heat
exchange system is in a heat-exchanging relationship with
individual temperature control point circuits, which are
hydraulically separated from the central heat exchange system.
23. (canceled)
24. The arrangement according to claim 22, in which at least part
of the heat flow transferred to the heat exchange fluid is adapted
to be dissipated to a heat consumer.
25. The arrangement according to claim 22, wherein at least part of
an exhaust heat flow arising at an operating point is adapted to be
dissipated to a heat consumer, and wherein the arrangement is
designed such that this exhaust heat flow is adapted to be
dissipated from a point of the respective temperature control point
circuit which is arranged downstream of the temperature control
point before the central heat exchange system.
26. (canceled)
27. (canceled)
28. (canceled)
29. The arrangement according to claim 1, further comprising a
buffer storage in which heat is adapted to be temporarily stored in
a heat storage substance.
30. (canceled)
31. The arrangement according to claim 5, wherein two central heat
exchange systems are provided, wherein one of the two central heat
exchange systems is provided to supply heat consumers with heat,
and wherein the other of the two central heat exchange systems
comprises the cooling device.
32-88. (canceled)
Description
FIELD OF THE INVENTION
[0001] The invention relates to an arrangement on a printing
machine for the temperature control of operating points of the
printing machine having different operating temperatures.
BACKGROUND OF THE INVENTION AND PRIOR ART
[0002] Different systems exist in the prior art, which bring or
keep fluids, which are used on printing machines, or individual
zones of printing machines to or at a specific temperature for the
sake of temperature control.
[0003] For example, DE 4426077 describes a system with two
refrigerating machines.
[0004] DE 10316860 and WO 2006072558 disclose systems with heat
recovery.
[0005] In view of the increasing environmental awareness and the
energy price development, further improvements of how to optimise
the heat and mass transfer on printing machines further are still
being searched for.
OBJECT
[0006] It is therefore an object of the invention to effectively
control the temperature of the process heat, different operating
points on a printing machine and to economically and ecologically
use the process heat produced at the operating points.
SOLUTION TO THE OBJECT
[0007] The object is solved by the devices according to the
independent claims. Advantageous embodiments are disclosed in the
subclaims.
[0008] A first aspect of the invention relates to an arrangement on
a printing machine, comprising at least one low-temperature
temperature control point (NT temperature control point), at least
one medium-temperature temperature control point (MT temperature
control point), and at least one high-temperature temperature
control point (HT temperature control point), which are arranged in
a low-temperature zone (NT zone), a medium-temperature zone (MT
zone), and at least one high-temperature zone (HT zone) of a
printing machine and are designed such that the NT zone can be
controlled to a low temperature by means of the NT temperature
control point, the MT zone to a medium temperature by means of the
MT temperature control point, and the HT zone to a high temperature
by means of the HT temperature control point, the low temperature
being lower than the medium temperature and the medium temperature
being lower than the high temperature,
[0009] wherein the arrangement comprises a central heat exchange
system designed such that the NT temperature control point, the MT
temperature control point, and the HT temperature control point can
be temperature controlled via the central heat exchange system,
wherein a pipe system of the central heat exchange system can be
flown through by a heat exchange fluid, and
[0010] wherein the heat exchange system is connected with the NT
temperature control point, the MT temperature control point, and
the HT temperature control point such that heat flows can be
transferred between the NT temperature control point and the heat
exchange fluid, between the MT temperature control point and the
heat exchange fluid, and between the HT temperature control point
and the heat exchange fluid.
[0011] The embodiment according to the invention has the advantage
that heat transferred to the heat exchange fluid can be made
available to other temperature control points to be preheated. This
may particularly be of advantage during a starting operation in
which different zones have not yet been brought to the operating
temperature.
[0012] In such an arrangement, each of the temperature control
points can be formed as a separate primary circuit in principle,
which is designed such that the heat flow can be dissipated to a
secondary circuit via a heat exchanger. Preferably, such a
secondary circuit is part of the central heat exchange system or is
a further closed circuit in heat-exchanging relationship with the
central heat exchange system. However, each of the temperature
control points can as well be formed as a circuit that is flown
through directly by a process agent, in particular the heat
exchange fluid in the central heat exchange system, such that the
heat flow is transferred together with the process agent
circulating in the circuit, so that the heat flow is coupled to the
flowing carrier mass of the process agent flow. Process agent
refers to arbitrary fluids supplied to printing machines for
operation thereof and/or circulating in the printing machines, in
particular dampening water, cleaning agents, transmission oil
and/or other fluids used for cooling specific components.
[0013] A design of the temperature control points, in which the two
designs are combined, is also conceivable. A separate primary
circuit as described above can be formed as an open primary
circuit, in which the fluid at the temperature control point is
used up in part, e.g. dampening water, or as a closed primary
circuit, in which the inflow is equal to the outflow.
[0014] A dampening agent is used on printing machines, among
others, for wetting the non-printing points of a printing plate in
order to thus prevent trapping in these zones. Excess dampening
water is collected and fed back into the circuit. Since dampening
water often comprises volatile components, dampening water is
usually cooled to low temperatures before being applied to the
printing plates. Thereby, an evaporation of the volatile components
is clearly reduced, though not completely prevented. This zone of a
printing machine will usually be an NT zone in conformity with the
invention, the temperature of which is controlled by the NT
temperature control point. Since at this point, as just described,
dampening water is only partly fed back into the circuit, as far as
it has not been used up, this circuit is referred to as "open". In
addition, such an NT zone can also be temperature controlled by a
preferred closed circuit, e.g. by a circuit in the interior of a
printing cylinder. This preferred closed circuit would also be part
of the NT temperature control point and the temperature thereof
could as well be controlled with dampening water, but also with
another process agent in the described case.
[0015] The heat transfer between the temperature control points and
the central heat exchange system is preferably conducted without
converting the energy form thermal energy into electrical energy or
other energy forms. This applies also in the case of interposition
of a refrigerating machine. In the refrigerating machine, the
refrigerant absorbs heat by evaporation, the refrigerant is heated
further when being compressed and releases the entire excess heat
to the environment or the heat exchange fluid via a heat exchanger.
In doing so, the mechanical energy in the compressor only generates
heat "in addition". Even with the use of a refrigerating machine is
the already absorbed heat not converted, but is still present in
the refrigerant and is dissipated by same to the heat exchange
system as part of the exhaust heat.
[0016] In the present invention, the temperature levels are
referred to as "high", "medium", and "low" only for the purpose of
indicating a not insignificant difference between the operating
temperatures. Apart from that, the terms do not have any
quantitative significance. However, the difference between the NT
zone and the MT zone is preferably at least 5.degree. C. The
difference between the MT zone and the HT zone is preferably at
least 10.degree. C. Particularly preferably, the operating
temperature of the NT zone is between 5.degree. C. and 15.degree.
C., particularly preferably in the range from approx. 10.degree. C.
Such an operating temperature is possible on printing machines
particularly in the area of a dampening unit. With respect to the
MT zone, the operating temperature is preferably between 15.degree.
C. and 30.degree. C., particularly preferably in the range from
approx. 20.degree. C. and 25.degree. C. Such a range of possible
operating temperatures is applied on printing machines e.g. in the
printing zone of a printing machine, in particular to the
distributor rollers and/or the ductor rollers. The operating
temperature of the HT zone is preferably between 45.degree. C. and
75.degree. C., and particularly preferably in the range between
approx. 50.degree. C. and 65.degree. C. Such a temperature range is
e.g. applied in UV dryers (operating temperature approx. 60.degree.
C.), sheet guide plates (operating temperature approx. 50.degree.
C.), and in the cooling of blast air or compressed air (operating
temperature between 60.degree. C. and 90.degree. C.).
[0017] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a cold generator arranged
and designed such that the NT temperature control point can be
temperature controlled by means of the cold generator. Such a cold
generator preferably comprises a refrigerating machine, more
preferably a compressor-operated refrigerating machine with
condenser.
[0018] A further advantageous embodiment relates to an arrangement
in which both the NT temperature control point and the MT
temperature control point can be temperature controlled by means of
the cold generator.
[0019] Preferably, such an arrangement has a design in which 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.
[0020] Further, such an embodiment is preferred in which the
arrangement further comprises a cooling device. A cooling device is
preferably formed by a heat exchanger or comprises a heat exchanger
via which the arising heat flow can be dissipated to the
environment. Such a heat exchanger may be a free cooler. Free
cooler temperature control apparatus means an apparatus utilising
approx. the temperature of the ambient air for cooling the heat
exchange fluid. The heat exchange fluid can e.g. directly flow
through the cooling device or be connected therewith via an
additional heat exchanger. A free cooler can preferably be an
adiabatic free cooler provided with a liquid application device, in
particular a spraying device, wherein liquid can be applied to
areas of the adiabatic free cooler, so that cooling performance can
be increased and/or cooling to lower temperatures is possible by
evaporation of the liquid. Here, it is preferred that the liquid
can be applied in a controlled manner dependent on parameters, e.g.
if a greater cooling performance is required and/or if a reduction
of the cooling temperature is required, e.g. if the outside
temperature is too high. A cooling device may also comprise a
liquid/liquid heat exchanger that is e.g. cooled with ground water;
etc.
[0021] A further advantageous embodiment relates to such an
arrangement in which both the HT temperature control point and the
MT temperature control point can be temperature controlled by means
of the cooling device.
[0022] Further, a design of an arrangement is preferred in which
the cold generator, in the operating state of the printing machine,
is in a permanently cooling relationship with the NT temperature
control point.
[0023] Moreover, such an arrangement preferably has a design in
which the cooling device, in the operating state of the printing
machine, is in a permanently cooling relationship with the HT
temperature control point.
[0024] Further, an embodiment of the arrangement is preferred in
which the cold generator and the cooling device, in the operating
state of the printing machine, can be brought into a cooling
relationship with the MT temperature control point dependent on an
ambient temperature around the cooling device. Here, the cooling
relationship is preferably shown such that an exhaust heat flow of
the MT temperature control point can be dissipated to the cold
generator and/or the cooling device.
[0025] A further advantageous embodiment relates to such an
arrangement in which a heat flow can be transferred from the MT
temperature control point and/or the HT temperature control point
to the cooling device via the heat exchange fluid in the central
heat exchange system.
[0026] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a cold producer arranged
and designed such that the MT temperature control point can be
temperature controlled by means of the cold generator. The cold
producer preferably comprises a refrigerating machine, more
preferably a compressor-operated refrigerating machine with an
evaporator and a condenser, and more preferably an air-cooled
refrigerating machine.
[0027] A further advantageous embodiment relates to an arrangement
in which both the MT temperature control point and the NT
temperature control point can be temperature controlled by means of
the cold producer.
[0028] Preferably, such an arrangement has a design in which the
cold producer is arranged such that the exhaust heat flow generated
by the cold producer can be directly transferred to the heat
exchange fluid in the central heat exchange system.
[0029] Further, such an arrangement is preferred in which the cold
generator and the cold producer are operated with refrigerants
having different evaporating temperatures and/or different
condensation temperatures.
[0030] A further advantageous embodiment relates to an arrangement
in which the central heat exchange system comprises a heat exchange
circuit with a central inlet and a central outlet, wherein several,
parallel partial branches extend between the central inlet and the
central outlet, wherein a partial inlet of a partial branch passes
to one of the temperature control points, wherein a partial outlet
of a partial branch, coming from the temperature control point,
leads to the central outlet such that a central heat exchange fluid
flow in the central inlet can be divided into different heat
exchange fluid partial flows, wherein the different heat exchange
fluid partial flows can be fed to different temperature control
points, and wherein the different heat exchange fluid partial
flows, coming from the different temperature control points, can be
brought together again in the central outlet to form the central
heat exchange fluid flow. Here, the central heat exchange fluid
flow has the same temperature in the central inlet and in the
partial inlets. The temperatures in the partial outlets differ
depending on the operating temperature of the operating points. The
partial fluid flows in the partial outlets are mixed together in
the respective sections of the central outlet, so that these
sections each have a different temperature until finally, in the
flow direction behind the last partial outlet, all heat exchange
fluid partial flows unite in the last section of the central
outlet.
[0031] Further, a design of an arrangement is preferred in which at
least one of the partial branches can be cut off via a valve. The
valve can preferably be controlled dependent on the operating
temperature at the operating point and the temperature of the
inflowing central heat exchange fluid flow and/or the inflowing
heat exchange fluid partial flow, wherein the valve is preferably
closed if the temperature of the inflowing central heat exchange
fluid flow and/or the inflowing heat exchange fluid partial flow is
higher than the (actual or intended) operating temperature at the
operating point.
[0032] Further, 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 a heat
consumer may be a heater for an ink distributor temperature control
device and/or a preheating device for preheating thermo-air, which
is e.g. used for drying the printed printing substance. Arbitrary
other heat consumers are conceivable as well.
[0033] Further, an embodiment of the arrangement is preferred in
which the part of the heat flow that can be dissipated can be
removed from the partial outlet of a partial branch. Preferably,
the part of the heat flow is removed in a partial branch having a
temperature level suitable for the respective heat consumer.
Preferably, the part of the heat flow is removed in a partial
branch having a high temperature level, in particular in the
partial outlet behind the HT temperature control point, since this
point of the central heat exchange system usually has the highest
temperature level. It is further preferred that the arrangement is
designed such that different parts of the entire heat flow can be
dissipated at different points of the central heat exchange system
with different temperature levels for different heat consumers.
[0034] A further advantageous embodiment relates to such an
arrangement in which the cooling device is directly flown through
by the heat exchange fluid flow, wherein the heat exchange fluid
flow can be led past the cooling device via a bypass line
controllable with a bypass valve.
[0035] Further, an embodiment of the arrangement is preferred in
which the cooling device comprises a separate cooling circuit 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.
[0036] A further advantageous embodiment relates to an arrangement
in which the bypass valve or the cooling circuit valve can be cut
off in a controlled manner in the case that the intended 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.
[0037] Preferably, such an arrangement has a design in which the
central heat exchange system is in a heat-exchanging relationship
with individual temperature control point circuits, which are
hydraulically separated from the central heat exchange system.
Hydraulically separated as used herein means without flow
connection, via which a heat flow could be transferred together
with a fluid flow. In this preferred embodiment, the fluid circuits
remain separate and can therefore be operated e.g. with different
temperature control fluids. Accordingly, merely the respective heat
flows are transferred to the central heat exchange system by the
hydraulically separate temperature control point circuits. Here, a
central heat exchanger, which is in a heat-exchanging relationship
with several or all of the temperature control point circuits, can
preferably be provided in the central heat exchange system, wherein
the heat flows of the respective temperature control point circuits
are transferred to a heat exchange fluid provided in the central
heat exchanger. Accordingly, in this preferred embodiment, the
different temperature levels in the temperature control point
circuits are standardised to a temperature of the heat exchange
fluid in the central heat exchanger.
[0038] Further, such an arrangement is preferred in which the
heat-exchanging relationship between one of the mutually separate
temperature control point circuits and the central heat exchange
system is designed in a separable manner such that no heat flow can
be transferred from the temperature control point circuit to the
central heat exchange system any more. A separation of one of the
temperature control point circuits can preferably be established
via a respective bypass line controllable by a valve. The valve is
preferably designed in a controllable manner dependent on 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 if the temperature
of the heat exchange fluid is higher than the (actual or intended)
operating temperature at the operating point.
[0039] 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 be a heater for an ink distributor temperature
control device and/or a preheating device e.g. usable for
preheating thermo-air, which can e.g. be used for drying the
printed printing substance.
[0040] Further, a design of an arrangement is preferred in which at
least part of an exhaust heat flow arising at one of the operating
points can be dissipated to a heat consumer, wherein the
arrangement is designed such that this exhaust heat flow can be
dissipated from a point of the respective temperature control point
circuit which is arranged downstream of the operating point before
the central heat exchange system. For this purpose, a heat consumer
heat exchanger is preferably provided in the respective temperature
control point circuit, which is flown through by the respective
temperature control fluid in the respective temperature control
point circuit, the fluid flowing in the direction of the central
heat exchange system. The fluid transfers the part of the heat flow
to the respective feed circuit of the heat consumer.
Advantageously, heat can be taken from that temperature control
point circuit that has a temperature level suitable for the
respective temperature control point circuit. Preferably, the part
of the heat flow is removed in a temperature control point circuit
having a high temperature level, in particular the temperature
control point circuit of the HT temperature control point, since it
usually has the highest temperature level. Further preferably, the
arrangement is designed such that different parts of the entire
heat flow can be dissipated from different temperature control
point circuits having different temperature levels for different
heat consumers.
[0041] Further, such an arrangement preferably has a design in
which the cooling device is directly flown through by the heat
exchange fluid flow, wherein the heat exchange fluid flow can be
led past the cooling device via a bypass line controllable with a
bypass valve.
[0042] Further, an embodiment of the arrangement is preferred in
which the cooling device comprises a separate cooling circuit 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.
[0043] A further advantageous embodiment relates to an arrangement
in which the bypass valve or the cooling circuit valve can be cut
off in a controlled manner in the case that the intended 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.
[0044] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a buffer storage in which
heat can be temporarily stored in a heat storage substance.
[0045] A further advantageous embodiment relates to an arrangement
in which the heat storage substance comprises a larger amount of
heat exchange fluid.
[0046] Preferably, such an arrangement has a design in which two
central heat exchange systems are provided, wherein one of the two
central heat exchange systems is provided to supply heat consumers
with heat, as is described in claims 17 to 21 and 24 to 29, and
wherein the other of the two central heat exchange systems
comprises the cooling device.
[0047] The following aspects of the invention relate to other
embodiments of the same invention. Therefore, substantially the
same terminology is used. The above explanations regarding
individual terms, advantages and embodiments therefore apply to the
following aspects accordingly.
[0048] A second aspect of the invention relates to an arrangement
on a printing machine, comprising at least one low-temperature
temperature control point (NT temperature control point), at least
one medium-temperature temperature control point (MT temperature
control point), and at least one high-temperature temperature
control point (HT temperature control point), which are arranged in
a low-temperature zone (NT zone), a medium-temperature zone (MT
zone), and at least one high-temperature zone (HT zone) of a
printing machine and are designed such that the NT zone can be
controlled to a low temperature by means of the NT temperature
control point, the MT zone to a medium temperature by means of the
MT temperature control point, and the HT zone to a high temperature
by means of the HT temperature control point, the low temperature
being lower than the medium temperature and the medium temperature
being lower than the high temperature,
[0049] 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),
[0050] wherein the MT temperature control point can be temperature
controlled both via the NT temperature control device and the HT
temperature control device.
[0051] This design has the advantage that e.g. the NT temperature
control device can e.g. be adapted for a low temperature, which is
used anyway on the printing machine depending on the design of e.g.
an NT temperature control point, whereas the HT temperature control
device can be adapted such that it is able to utilize the ambient
temperature for temperature control in an energy-saving manner.
Therefore, depending on the ambient temperature and the desired
operating temperature, an inventive embodiment can advantageously
be designed such that the desired operating temperature can be
obtained by a combination of both temperature control devices,
which is optimised with respect to the desired performance and
optimum energy utilization.
[0052] Here, an essential component of the HT temperature control
device preferably is a free cooler. In the present invention, the
temperature levels are referred to as "high", "medium", and "low"
only for the purpose of indicating a not insignificant difference
between the operating temperatures. Apart from that, the terms do
not have any quantitative significance. However, the difference
between the NT zone and the MT zone is preferably at least
5.degree. C. The difference between the MT zone and the HT zone is
preferably at least 10.degree. C. Particularly preferably, the
operating temperature of the NT zone is between 5.degree. C. and
15.degree. C., particularly preferably in the range from approx.
10.degree. C. Such an operating temperature is possible on printing
machines particularly in the zone of a dampening unit. With respect
to the MT zone, the operating temperature is preferably between
15.degree. C. and 30.degree. C., particularly preferably in the
range from approx. 20.degree. C. and 25.degree. C. Such a range of
possible operating temperatures is applied on printing machines
e.g. in the printing zone of a printing machine, in particular to
the distributor rollers and/or the ductor rollers. The operating
temperature of the HT zone is preferably between 45.degree. C. and
75.degree. C., and particularly preferably in the range between
approx. 50.degree. C. and 65.degree. C. Such a temperature range is
e.g. applied in UV dryers (operating temperature approx. 60.degree.
C.), sheet guide plates (operating temperature approx. 50.degree.
C.), and in the cooling of blast air or compressed air (operating
temperature between 60.degree. C. and 90.degree. C.).
[0053] Further, an embodiment of the arrangement is preferred in
which the NT temperature control device and the HT temperature
control device are connected with the MT temperature control point
such that the MT temperature control point can be temperature
controlled by the NT temperature control device and the HT
temperature control device at the same time.
[0054] A further advantageous embodiment relates to an arrangement
in which the NT temperature control device and the HT temperature
control device are connected with the MT temperature control point
such that the MT temperature control point can be temperature
controlled either by the NT temperature control device or the HT
temperature control device at a specific time dependent on specific
parameters. Such parameters may be the actual and/or intended
temperature of the MT operating point and/or the temperature
control range to be achieved by the HT temperature control device.
This temperature control range can in turn depend on the
temperature of a heat exchange fluid. It is further conceivable
that if the HT temperature control device is a free cooler, as it
is described above, such a parameter is the ambient temperature
around the free cooler.
[0055] Preferably, such an arrangement has a design in which the NT
temperature control device comprises a cold generator. Such a cold
generator preferably comprises a refrigerating machine, more
preferably a compressor-operated refrigerating machine with
condenser.
[0056] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a central heat exchange
system designed such that the NT temperature control point, the MT
temperature control point, and the HT temperature control point can
be temperature controlled via the central heat exchange system,
wherein a pipe system of the central heat exchange system can be
flown through by a heat exchange fluid, and wherein the heat
exchange system is connected with the NT temperature control point,
the MT temperature control point, and the HT temperature control
point such that heat flows can be transferred both between the NT
temperature control point and the heat exchange fluid, and between
the MT temperature control point and the heat exchange fluid, and
between the HT temperature control point and the heat exchange
fluid. The heat transfer between the temperature control points and
the central heat exchange system is preferably conducted without
converting the energy form thermal energy into electrical energy or
other energy forms. This applies also in the case of interposition
of a refrigerating machine. In the refrigerating machine, the
refrigerant absorbs heat by evaporation, the refrigerant is heated
further when being compressed (mechanical energy) and releases the
entire excess heat to the environment or the heat exchange fluid
via a heat exchanger. In doing so, the mechanical energy in the
compressor only generates heat "in addition". Even with the use of
a refrigerating machine is the already absorbed heat not converted,
but is still present in the refrigerant and is dissipated by same
to the heat exchange system as part of the exhaust heat.
[0057] A further advantageous embodiment relates to an arrangement
in which 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.
[0058] Preferably, such an arrangement has a design in which the HT
temperature control device comprises a cooling device. A cooling
device is preferably formed by a heat exchanger or comprises a heat
exchanger via which the arising heat flow can be dissipated to the
environment. Such a heat exchanger may be a free cooler. Free
cooler temperature control apparatus means an apparatus utilising
approx. the temperature of the ambient air for cooling the heat
exchange fluid. The heat exchange fluid may be a process agent.
Process agent refers to arbitrary fluids supplied to printing
machines for operation thereof and/or circulating in the printing
machines, in particular dampening water, cleaning agents,
transmission oil and/or other fluids used for cooling specific
components. A free cooler can preferably be designed as an
adiabatic free cooler provided with a liquid application device, in
particular a spraying device, wherein liquid can be applied to
areas of the adiabatic free cooler, so that cooling performance can
be increased and/or cooling to lower temperatures is possible by
evaporation of the liquid. Here, it is preferred that the liquid
can be applied in a controlled manner dependent on parameters, e.g.
if a greater cooling performance is required and/or if a reduction
of the cooling temperature is required, e.g. if the outside
temperature is too high. A cooling device may also comprise a
liquid/liquid heat exchanger that is e.g. cooled with ground water;
etc.
[0059] Further, a design of an arrangement is preferred in which
the cold generator, in the operating state of the printing machine,
is in a permanently cooling relationship with the NT temperature
control point.
[0060] A further advantageous embodiment relates to an arrangement
in which the cooling device, in the operating state of the printing
machine, is in a permanently cooling relationship with the HT
temperature control point.
[0061] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a central heat exchange
system designed such that the NT temperature control point, the MT
temperature control point, and the HT temperature control point can
be temperature controlled via the central heat exchange system,
wherein a pipe system of the central heat exchange system can be
flown through by a heat exchange fluid, and wherein the heat
exchange system is connected with the NT temperature control point,
the MT temperature control point, and the HT temperature control
point such that heat flows can be transferred both between the NT
temperature control point and the heat exchange fluid, and between
the MT temperature control point and the heat exchange fluid, and
between the HT temperature control point and the heat exchange
fluid.
[0062] A further advantageous embodiment relates to such an
arrangement in which the arrangement is designed such that a heat
flow can be transferred from the MT temperature control point
and/or the HT temperature control point to the cooling device via
the heat exchange fluid in the central heat exchange system.
[0063] Preferably, such an arrangement has a design in which the
arrangement further comprises a cold producer arranged and designed
such that the MT temperature control point can be temperature
controlled by means of the cold generator. The cold producer
preferably comprises a refrigerating machine, more preferably a
compressor-operated refrigerating machine with an evaporator and a
condenser, and more preferably an air-cooled refrigerating
machine.
[0064] Further, such an arrangement is preferred in which both the
MT temperature control point and the NT temperature control point
can be temperature controlled by means of the cold producer.
[0065] A further advantageous embodiment relates to such an
arrangement in which the cold producer is arranged such that the
exhaust heat flow generated by the cold producer can be directly
transferred to the heat exchange fluid in the central heat exchange
system.
[0066] Further, a design of an arrangement is preferred in which
the cold generator and the cold producer are operated with
refrigerants having different evaporating temperatures and/or
different condensation temperatures.
[0067] Further, such an arrangement preferably has a design in
which the central heat exchange system comprises a heat exchange
circuit with a central inlet and a central outlet, wherein several,
parallel partial branches extend between the central inlet and the
central outlet, wherein a partial inlet of a partial branch passes
to one of the temperature control points, wherein a partial outlet
of a partial branch, coming from the temperature control point,
leads to the central outlet such that a central heat exchange fluid
flow in the central inlet can be divided into different heat
exchange fluid partial flows, wherein the different heat exchange
fluid partial flows can be fed to different temperature control
points, and wherein the different heat exchange fluid partial
flows, coming from the different temperature control points, can be
brought together again in the central outlet to form the central
heat exchange fluid flow. Here, the central heat exchange fluid
flow has the same temperature in the central inlet and in the
partial inlets. The temperatures in the partial outlets differ
depending on the operating temperature of the operating points. The
partial fluid flows in the partial outlets are mixed together in
the respective sections of the central outlet, so that these
sections each have a different temperature until finally, in the
flow direction behind the last partial outlet, all heat exchange
fluid partial flows unite in the last section of the central
outlet.
[0068] Further, a design of the arrangement is preferred in which
at least one of the partial branches can be cut off via a valve.
The valve can preferably be controlled dependent on the operating
temperature at the operating point and the temperature of the
inflowing central heat exchange fluid flow and/or the inflowing
heat exchange fluid partial flow, wherein the valve is preferably
closed if the temperature of the inflowing central heat exchange
fluid flow and/or the inflowing heat exchange fluid partial flow is
higher than the (actual or intended) operating temperature at the
operating point.
[0069] 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 be a heater for an ink distributor temperature
control device and/or a preheating device for preheating
thermo-air, which is e.g. used for drying the printed printing
substance. Arbitrary other heat consumers are conceivable as
well.
[0070] A further advantageous embodiment relates to such an
arrangement in which the part of the heat flow that can be
dissipated can be removed from the partial outlet of a partial
branch. Preferably, the part of the heat flow is removed in a
partial branch having a temperature level suitable for the
respective heat consumer. Preferably, the part of the heat flow is
removed in a partial branch having a high temperature level, in
particular in the partial outlet behind the HT temperature control
point, since this point of the central heat exchange system usually
has the highest temperature level. It is further preferred that the
arrangement is designed such that different parts of the entire
heat flow can be dissipated at different points of the central heat
exchange system with different temperature levels for different
heat consumers.
[0071] Further, an embodiment of the arrangement is preferred in
which the cooling device is directly flown through by the heat
exchange fluid flow, and wherein the heat exchange fluid flow can
be led past the cooling device via a bypass line controllable with
a bypass valve.
[0072] A further advantageous embodiment relates to an arrangement
in which the cooling device comprises a separate cooling circuit 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.
[0073] Preferably, such an arrangement has a design in which the
bypass valve or the cooling circuit valve can be cut off in a
controlled manner in the case that the intended 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.
[0074] Further, such an arrangement is preferred in which the
central heat exchange system is in a heat-exchanging relationship
with individual temperature control point circuits, which are
hydraulically separated from the central heat exchange system.
Hydraulically separated as used herein means without flow
connection, via which a heat flow could be transferred together
with a fluid flow. In this preferred embodiment, the fluid circuits
remain separate and can therefore be operated e.g. with different
temperature control fluids. Accordingly, merely the respective heat
flows are transferred to the central heat exchange system by the
hydraulically separate temperature control point circuits. Here, a
central heat exchanger, which is in a heat-exchanging relationship
with several or all of the temperature control point circuits, can
preferably be provided in the central heat exchange system, wherein
the heat flows of the respective temperature control point circuits
are transferred to a heat exchange fluid provided in the central
heat exchanger. Accordingly, in this preferred embodiment, the
different temperature levels in the temperature control point
circuits are standardised to a temperature of the heat exchange
fluid in the central heat exchanger.
[0075] A further advantageous embodiment relates to such an
arrangement in which the heat-exchanging relationship between one
of the mutually separate temperature control point circuits and the
central heat exchange system is designed in a separable manner such
that no heat flow can be transferred from the temperature control
point circuit to the central heat exchange system any more. A
separation of one of the temperature control point circuits can
preferably be established via a respective bypass line controllable
by a valve. The valve is preferably designed in a controllable
manner dependent on 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 if the temperature of the heat exchange fluid is higher than
the (actual or intended) operating temperature at the operating
point.
[0076] Further, a design of an arrangement is preferred 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 be a
heater for an ink distributor temperature control device and/or a
preheating device e.g. usable for preheating thermo-air, which can
e.g. be used for drying the printed printing substance. Arbitrary
other heat consumers are conceivable as well.
[0077] Further, such an arrangement preferably has a design in
which at least part of an exhaust heat flow arising at one of the
operating points can be dissipated to a heat consumer, wherein the
arrangement is designed such that this exhaust heat flow can be
dissipated from a point of the respective temperature control point
circuit which is arranged downstream of the operating point before
the central heat exchange system. For this purpose, a heat consumer
heat exchanger is preferably provided in the respective temperature
control point circuit, which is flown through by the respective
temperature control fluid in the respective temperature control
point circuit, the fluid flowing in the direction of the central
heat exchange system. The fluid transfers the part of the heat flow
to the respective feed circuit of the heat consumer.
Advantageously, heat can be taken from that temperature control
point circuit that has a temperature level suitable for the
respective temperature control point circuit. Preferably, the part
of the heat flow is removed in a temperature control point circuit
having a high temperature level, in particular the temperature
control point circuit of the HT temperature control point, since it
usually has the highest temperature level. Further preferably, the
arrangement is designed such that different parts of the entire
heat flow can be dissipated from different temperature control
point circuits having different temperature levels for different
heat consumers.
[0078] Further, an embodiment of the arrangement is preferred in
which the cooling device is directly flown through by the heat
exchange fluid flow, wherein the heat exchange fluid flow can be
led past the cooling device via a bypass line controllable with a
bypass valve.
[0079] A further advantageous embodiment relates to such an
arrangement in which the cooling device comprises a separate
cooling circuit 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.
[0080] Further, an embodiment of the arrangement is preferred in
which the bypass valve or the cooling circuit valve can be cut off
in a controlled manner in the case that the intended 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.
[0081] A further advantageous embodiment relates to an arrangement
in which the arrangement further comprises a buffer storage in
which heat can be temporarily stored in a heat storage
substance.
[0082] Preferably, such an arrangement has a design in which the
heat storage substance comprises a larger amount of heat exchange
fluid.
[0083] Further, such an arrangement is preferred in which two
central heat exchange systems are provided, wherein one of the two
central heat exchange systems is provided to supply heat consumers
with heat, as is described above, and wherein the other of the two
central heat exchange systems comprises the cooling device.
[0084] The first and third aspects of the invention relate to other
embodiments of the same invention described with respect to the
second aspect of the invention. Therefore, substantially the same
terminology is used. The above explanations regarding individual
terms, advantages and embodiments therefore apply to the other
aspects of the invention accordingly.
[0085] A third aspect of the invention relates to an arrangement on
a printing machine, comprising at least one low-temperature
temperature control point (NT temperature control point) and at
least one medium-temperature temperature control point (MT
temperature control point), which are arranged in a low-temperature
zone (NT zone) and a medium-temperature zone (MT zone) of a
printing machine and are designed such that the NT zone can be
controlled to a low temperature by means of the NT temperature
control point and the MT zone to a medium temperature by means of
the MT temperature control point, the low temperature being lower
than the medium temperature,
[0086] wherein the NT temperature control point and the MT
temperature control point are connected with a heat consumer system
via a central heat exchange system, which can be flown through by a
heat exchange fluid, such that the exhaust heat flows generated at
the NT temperature control point and the MT temperature control
point during controlling the temperature can at least partly be
transferred to the heat consumer system.
[0087] "At least partly transferred" as used herein means
preferably that at least one partial exhaust heat flow can be
transferred from each of the two temperature control points to the
heat consumer system. In the present invention, the temperature
levels are referred to as "low" and "medium" only for the purpose
of indicating a not insignificant difference between the operating
temperatures. Apart from that, the terms do not have any
quantitative significance. Therefore, the terms described with
respect to this aspect of the invention--as far as only two
temperature levels are described--can also be replaced by the terms
"medium" and "high" or "low" and "high" described with respect to
the other aspects of the invention.
[0088] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a high-temperature
temperature control point (HT temperature control point), which is
arranged in a high-temperature zone (HT zone) of the printing
machine and is designed such that the HT zone can be controlled to
a high temperature by means of the HT temperature control point,
the high temperature being higher than the low temperature and
higher than the medium temperature. The difference between the NT
zone and the MT zone is preferably at least 5.degree. C. The
difference between the MT zone and the HT zone is preferably at
least 10.degree. C. Particularly preferably, the operating
temperature of the NT zone is between 5.degree. C. and 15.degree.
C., particularly preferably in the range from approx. 10.degree. C.
Such an operating temperature is possible on printing machines
particularly in the zone of a dampening unit. With respect to the
MT zone, the operating temperature is preferably between 15.degree.
C. and 30.degree. C., particularly preferably in the range from
approx. 20.degree. C. and 25.degree. C. Such a range of possible
operating temperatures is applied on printing machines e.g. in the
printing zone of a printing machine, in particular to the
distributor rollers and/or the ductor rollers. The operating
temperature of the HT zone is preferably between 45.degree. C. and
75.degree. C., and particularly preferably in the range between
approx. 50.degree. C. and 65.degree. C. Such a temperature range is
e.g. applied in UV dryers (operating temperature approx. 60.degree.
C.), sheet guide plates (operating temperature approx. 50.degree.
C.), and in the cooling of blast air or compressed air (operating
temperature between 60.degree. C. and 90.degree. C.).
[0089] 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 can be dissipated from the central
heat reservoir.
[0090] Preferably, such an arrangement has a design in which the
arrangement is designed such that heat-dissipating fluid flows,
coming from the temperature control points, are fed to the central
heat exchange system via temperature control point lines, wherein
the fluid flows unite in the central heat exchange system. Thereby,
preferably a large heat buffer can be created in the heat
reservoir, from which buffer the heat consumer system can be
fed.
[0091] Further, such an arrangement is preferred in which at least
part of an exhaust heat flow arising at one of the operating points
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 line which is arranged downstream of the operating
point before the central heat reservoir.
[0092] A further advantageous embodiment relates to such an
arrangement in which the arrangement is designed such that for at
least one of the heat-dissipating fluid flows, coming from the
temperature control points, a temperature control point circuit is
provided which is formed hydraulically separated from the central
heat reservoir, so that merely a heat flow is transferred to the
central heat reservoir from the heat-dissipating fluid flow. Only
heat flow is transferred to the central heat reservoir--but not a
fluid flow. The temperature control point circuit is hydraulically
separated from the heat reservoir. Thereby, preferably different
fluids can be used. Individual temperature control point circuits
can be hydraulically connected with each other and be hydraulically
separated from other temperature control point circuits.
[0093] Further, a design of an arrangement is preferred in which at
least part of an exhaust heat flow arising at one of the operating
points can be dissipated to a heat consumer without being
transferred to the central heat reservoir, 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 operating point before the central heat reservoir. For this
purpose, a heat consumer heat exchanger is preferably provided in
the respective temperature control point circuit, which is flown
through by the respective temperature control fluid in the
respective temperature control point circuit, the fluid flowing in
the direction of the central heat exchange system. The fluid
transfers the part of the heat flow to the respective feed circuit
of the heat consumer. Advantageously, heat can be taken from that
temperature control point circuit that has a temperature level
suitable for the respective temperature control point circuit.
Preferably, the part of the heat flow is removed in a temperature
control point circuit having a high temperature level, in
particular the temperature control point circuit of the HT
temperature control point, since it usually has the highest
temperature level. Further preferably, the arrangement is designed
such that different parts of the entire heat flow can be dissipated
from different temperature control point circuits having different
temperature levels for different heat consumers.
[0094] Further, such an arrangement preferably has a design in
which the heat exchange system is connected with at least two
temperature control points such that a heat flow can be transferred
from one of the at least two temperature control points to the
other of the at least two temperature control points via the heat
exchange fluid. The heat transfer between the temperature control
points and the central heat exchange system is preferably conducted
without converting the energy form thermal energy into electrical
energy or other energy forms. This applies also in the case of
interposition of a refrigerating machine. In the refrigerating
machine, the refrigerant absorbs heat by evaporation, the
refrigerant is heated further when being compressed (mechanical
energy) and releases the entire excess heat to the environment or
the heat exchange fluid via a heat exchanger. In doing so, the
mechanical energy in the compressor only generates heat "in
addition". Even with the use of a refrigerating machine is the
already absorbed heat not converted, but is still present in the
refrigerant and is dissipated by same to the heat exchange system
as part of the exhaust heat.
[0095] Further, an embodiment of the arrangement is preferred in
which the arrangement further comprises a cold generator arranged
and designed such that the NT temperature control point can be
temperature controlled by means of the cold generator. Such a cold
generator preferably comprises a refrigerating machine, more
preferably a compressor-operated refrigerating machine with
condenser.
[0096] Further, an embodiment of the arrangement is preferred in
which both the NT temperature control point and the MT temperature
control point can be temperature controlled by means of the cold
generator.
[0097] A further advantageous embodiment relates to an arrangement
in which 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. An
exhaust heat flow as defined herein is to be understood such that
the term comprises both the heat absorbed by the cold
generator--i.e. the "generated" cold--and the dissipated heat
produced by the cold generator.
[0098] Preferably, such an arrangement has a design in which the
arrangement further comprises a cooling device. A cooling device is
preferably formed by a heat exchanger or comprises a heat exchanger
via which the arising heat flow can be dissipated to the
environment. Such a heat exchanger may be a free cooler. Free
cooler temperature control apparatus means an apparatus utilising
approx. the temperature of the ambient air for cooling the heat
exchange fluid. The heat exchange fluid may be a process agent.
Process agent refers to arbitrary fluids supplied to printing
machines for operation thereof and/or circulating in the printing
machines, in particular dampening water, cleaning agents,
transmission oil and/or other fluids used for cooling specific
components. A free cooler can preferably be an adiabatic free
cooler provided with a liquid application device, in particular a
spraying device, wherein liquid can be applied to zones of the
adiabatic free cooler, so that cooling performance can be increased
and/or cooling to lower temperatures is possible by evaporation of
the liquid. Here, it is preferred that the liquid can be applied in
a controlled manner dependent on parameters, e.g. if a greater
cooling performance is required and/or if a reduction of the
cooling temperature is required, e.g. if the outside temperature is
too high. A cooling device may also comprise a liquid/liquid heat
exchanger that is e.g. cooled with ground water; etc.
[0099] Further, such an arrangement is preferred in which both the
HT temperature control point and the MT temperature control point
can be temperature controlled by means of the cooling device.
[0100] A further advantageous embodiment relates to such an
arrangement in which the cold generator, in the operating state of
the printing machine, is in a permanently cooling relationship with
the NT temperature control point.
[0101] Moreover, a design of an arrangement is preferred in which
the cooling device, in the operating state of the printing machine,
is in a permanently cooling relationship with the HT temperature
control point.
[0102] Further, such an arrangement preferably has a design in
which the cold generator and the cooling device, in the operating
state of the printing machine, can be brought into a cooling
relationship with the MT temperature control point dependent on an
ambient temperature around the cooling device. Here, the cooling
relationship is preferably such that an exhaust heat flow of the MT
temperature control point can be dissipated to the cold generator
and/or the cooling device.
[0103] Further, an embodiment of the arrangement is preferred in
which a heat flow can be transferred from the MT temperature
control point and/or the HT temperature control point to the
cooling device via the heat exchange fluid in the central heat
exchange system.
[0104] A further advantageous embodiment relates to such an
arrangement in which the arrangement further comprises a cold
producer arranged and designed such that the MT temperature control
point can be temperature controlled by means of the cold generator.
Such a cold producer preferably comprises a refrigerating machine,
more preferably a compressor-operated refrigerating machine with an
evaporator and a condenser, and more preferably an air-cooled
refrigerating machine.
[0105] A further advantageous embodiment relates to an arrangement
in which both the MT temperature control point and the NT
temperature control point can be temperature controlled by means of
the cold producer.
[0106] Further, an embodiment of the arrangement is preferred in
which the cold producer is arranged such that the exhaust heat flow
generated by the cold producer can be directly transferred to the
heat exchange fluid in the central heat exchange system.
[0107] A further advantageous embodiment relates to an arrangement
in which the cold generator and the cold producer are operated with
refrigerants having different evaporating temperatures and/or
different condensation temperatures.
[0108] Preferably, such an arrangement has a design in which the
heat exchange system is formed as described in claims 15 to 28 with
respect to the heat exchange system.
[0109] Further, such an arrangement is preferred in which the
arrangement further comprises a buffer storage in which heat can be
temporarily stored in a heat storage substance.
[0110] A further advantageous embodiment relates to such an
arrangement in which the heat storage substance comprises a larger
amount of heat exchange fluid and wherein the heat exchange fluid
is hydraulically connected with the heat exchange fluid in the heat
exchange system.
[0111] Further, such an arrangement preferably has a design in
which
[0112] Moreover, a design of an arrangement is preferred in which
two central heat exchange systems are provided, wherein one of the
two central heat exchange systems is connected with at least one of
the heat consumers, as has been explained with respect to the
above-described heat exchange system, and wherein the other of the
two central heat exchange systems comprises the cooling device. The
central heat exchange system comprising the cooling device can have
the same structural features, in particular with respect to the
connection with the temperature control points, as the central heat
exchange system connected with the heat consumer.
[0113] As pointed out above, the three different aspects of the
invention are to be understood in a uniform manner, so that the
explanations regarding the first aspect of the invention (e.g. to
support claims 17 to 21 and 24 to 29) analogously apply to the
here-described separation of consumer circuit and cooling circuit
by two central heat exchange systems. Likewise, the explanations
given here can be applied to the other two aspects of the
invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0114] In the following, individual particularly preferred
embodiments of the invention will be described by way of example.
The individual described embodiments partly have features that are
not absolutely imperative for realising the present invention, but
that are generally considered to be preferred. Thus, embodiments,
which do not include all features of the embodiments described in
the following, are to be considered to be disclosed as falling
under the teaching of the invention as well. It is also conceivable
to selectively combine features described with respect to different
embodiments.
[0115] This applies in particular to the embodiments of FIGS. 1 to
3, which are particularly suitable for describing possibilities of
fluid cooling, and to FIGS. 4 and 5, which are particularly
suitable for describing possibilities of a heat supply of
consumers. The shown embodiments of FIGS. 1 to 3 can almost
arbitrarily combined with the embodiments of FIGS. 4 and 5.
[0116] The figures show:
[0117] FIG. 1a a schematic illustration of a preferred embodiment
of an inventive arrangement with fluid cooling, which is suitable
for describing in particular the first two aspects of the invention
by way of example,
[0118] FIGS. 1b to 1d enlarged sections of FIG. 1a,
[0119] FIG. 2 a schematic illustration of a preferred embodiment of
an inventive arrangement with fluid cooling, which is suitable for
describing in particular the first two aspects of the invention by
way of example,
[0120] FIG. 3 a schematic illustration of a further preferred
embodiment of an inventive arrangement with fluid cooling, which is
suitable for describing in particular the first two aspects of the
invention by way of example,
[0121] FIG. 4 a schematic illustration of a preferred embodiment of
an inventive arrangement with consumer supply, which is suitable
for describing in particular the third aspect of the invention by
way of example, and
[0122] FIG. 5 a schematic illustration of a further preferred
embodiment of an inventive arrangement with consumer supply, which
is suitable for describing in particular the third aspect of the
invention by way of example.
DETAILED DESCRIPTION OF THE DRAWINGS
[0123] FIG. 1a gives an overview of the inventive arrangement on a
printing machine 1 and thus a system with a cold generator
preferably formed as a refrigerating machine, and a cooling device
3 formed as a free cooler in the present invention. As can be seen
more clearly in FIG. 1d, the cooling device 3 is preferably an
adiabatic free cooler, i.e. a spraying device 31 enables the
improvement of the cooling performance by evaporative cold. The
spraying device can preferably be supplied with water via a water
pipe and is preferably only turned on if an improvement of the
cooling performance is required.
[0124] In FIG. 1a, the illustrated printing machine has three
different zones 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 temperature control point 51 and the MT
temperature control point 52 are shown exemplarily enlarged in FIG.
1c.
[0125] In such an arrangement, as is shown in FIG. 1c merely
exemplarily with respect to the temperature control points 51, 52,
basically each of the temperature control points 51, 52, 53 can
have a separate primary circuit 81 designed such that the heat flow
can be dissipated to a secondary circuit 82 via a heat exchanger
681, 682.
[0126] A separate primary circuit as described herein can be formed
as an open primary circuit in which the fluid is partly used up at
the temperature control point, such as in the case of dampening
water, or as a closed primary circuit in which the inflow is equal
to the outflow at any point of the primary circuit.
[0127] Further, it is conceivable in principle that each or some of
the temperature control points have a circuit directly flown
through by a process agent such that the heat flow is transferred
together with the process agent circulating in the circuit, so that
the heat flow is coupled to the flowing carrier mass of the process
agent flow. This is exemplarily shown in FIG. 1c by the lines,
which extend up to the respective temperature control points 51, 52
and are illustrated between the primary circuits 81. As can be seen
in FIG. 1a, these lines are part of partial branches 65 of a
central heat exchange system 6, which are directly connected with
the heat exchange circuit 62, so that heat exchange fluid can flow
into the partial inlet 651 of the partial branch 65 via a central
inlet 631 of the heat exchange circuit 62, can reach the
temperature control point, and from there get back to a central
outlet of the heat exchange circuit 62 via a partial outlet 652 of
the partial branch 65. This design can be formed in a manner "open"
or "closed" at the temperature control point.
[0128] As shown, both designs of the temperature control points can
be advantageously combined. However, this is not absolutely
necessary, so that one of the designs can be sufficient.
[0129] The thus temperature controlled heat exchange fluid can be
led to other temperature control points via the heat exchange
circuit 62, which may be practical in the warm-up phase of a
printing machine in order to provide the cold other temperature
control points with exhaust heat from another temperature control
point. This can directly be done via cross connections 653, 654
between the partial branches of the temperature control points, as
is illustrated in FIGS. 1a and 1b by the horizontal lines, which
exemplarily show an exchange of heat exchange fluid between the
partial branch of the NT temperature control point and the partial
branch of the MT temperature control point. Here, the cross
connection 653 leads from the NT temperature control point to the
MT temperature control point, and the cross connection 654 leads
back.
[0130] In order to redirect the fluid flow correspondingly, valves
661, 664 are provided. If the valve 661 is designed accordingly and
depending on the valve position, a fluid flow, coming from the
central inlet 63, could also flow to the heat exchanger 681 of the
NT temperature control point via a section of the cross connection
653 in order to cool the NT temperature control point. This may be
practical in particular at low outside temperatures, such as in
winter, if the heat exchange circuit 62 is used for cooling and, as
shown, is in heat-exchanging connection with a cooling device 3. As
required, the heat exchange circuit 62 can be connected with or cut
off from the cooling device 3 via the bypass line 67 and the bypass
valve 671 for this purpose.
[0131] Depending on the minimum outside temperature at the
operating times, it may be preferred that the NT temperature
control point is permanently cooled by the cold generator 2, i.e.
always when exhaust heat is to be dissipated.
[0132] Since an NT temperature control point can usually be cooled
to approx. 10.degree. C., the cold generator 2 will preferably be
designed so powerful that in addition at least part of the heat
load of the MT cooling points can be dissipated, e.g. if with
rising ambient temperature the free cooler is not sufficient any
more.
[0133] The intermediate circuit supplies the MT temperature control
point with the cooling side of the cold generator 2 via the cross
connections 653, 654. The exhaust heat of the cold generator 2 can
in turn preferably be dissipated to the heat exchange fluid in the
heat exchange circuit 62.
[0134] A corresponding circulation in the circuits, which can
change course depending on the valve position, is preferably
generated by circulation pumps, which can be switched on as
required.
[0135] Preferably, in the individual temperature control points,
3-2 directional valves and associated bypasses can provide for a
constant temperature at the temperature control points, as this is
exemplarily illustrated with respect to the MT temperature control
point 52 above the heat exchanger 682.
[0136] The HT temperature control point(s) to be cooled to a
temperature of usually above 50.degree. C. are cooled preferably
all year round by a cooling device 3 formed as a free cooler. Here,
it is further advantageous if the other temperature control points,
which regularly have operating temperatures that cannot be cooled
by a free cooler or only in an uneconomical manner all year round,
can be cut off in the heat exchange circuit 62 such that a heat
exchange fluid that is too warm does not reach them.
[0137] In such a temperature control system, it is therefore
particularly beneficial that all three temperature control points
participate from the cooling performance and/or from the exhaust
heat among one another and/or can be temperature controlled via an
ambient temperature without or with only little external
energy.
[0138] For example, a printing operation cannot be started until
all circuits have reached the desired temperature. For the NT
circuit, this is usually achieved by cooling, and for the MT or
optionally the HT circuit normally by heating.
[0139] In the inventive circuitry it is now possible to utilise the
arising exhaust heat for the temperature control of the respective
circuit higher with respect to the temperature level via the
internal recooling circuit.
[0140] Here, a design can be preferred in which the bypass valve
671 is a 3-2 directional valve (46) and only transfers that much
thermal energy to the free cooler that no additional thermal energy
has to be generated by means of electric heaters for the
temperature control of the MT and HT circuits.
[0141] As soon as the working temperature of the printing machine 1
is reached and the printing process itself generates exhaust heat
by e.g. fulling and/or drive motors, it is desirable for energetic
reasons that the free cooler dissipates as much thermal energy to
the environment as possible.
[0142] The savings potential is, among others, dependent on the
ambient conditions and the actually needed temperature levels
specially of the MT cooling points, since the working temperature
of e.g. 20-25.degree. C. can be generated only to a limited extent
in full or in part by the free cooler.
[0143] FIG. 2 shows a comparable system as FIGS. 1a to 1d, so that
double descriptions are avoided. In the figures, in addition to the
cold generator 2, a cold producer 4 is provided, which both are
formed as refrigerating machines in the illustrated embodiment.
[0144] Here, two separate refrigerating machines can optimise the
system further, since the refrigerating machines can be operated at
different evaporating temperatures.
[0145] Since a refrigerating machine usually works energetically
more efficiently the higher the evaporating temperature is (which
is possible due to higher water temperatures), it has turned out
that there are energetic advantages if fluid temperatures of e.g.
10.degree. C. and 20-25.degree. C. are generated with separate
refrigerating machines.
[0146] Here as well, a heat exchanger 684 is
additionally--exemplarily--provided only in a hydraulically
separate circuit of the MT temperature control point to exclusively
or partially dissipate heat via the free cooler. This heat
exchanger 684 can be switched off by an illustrated 2 directional
valve as required.
[0147] As can be seen in FIG. 2, the refrigerating machines are
water-cooled facilities, which dissipate their exhaust heat to the
central heat exchange system 6 e.g. for further use and/or to the
free cooler.
[0148] FIG. 3 shows an again comparable system as FIGS. 1a to 1d
and 2. Double descriptions are avoided here as well. In FIG. 3 as
well, in addition to the cold generator 2, a cold producer 4 is
provided which in the illustrated embodiment is formed as
air-cooled refrigerating machines, however. Preferably, the
air-cooled refrigerating machine for the medium temperature level
is not set up in the same room as the printing machine. A free
cooler is additionally provided here as well.
[0149] By means of a valve, which is illustrated in FIG. 3 below
the air-cooled refrigerating machine, the MT and HT temperature
control points can be connected with the heat exchange circuit 62
via a--further (when the valve is open)--partial branch 65 of the
heat exchange circuit 62. Here, both the free cooler and/or,
depending on the ambient temperature, the air-cooled refrigerating
machine can be added completely or partially.
[0150] FIG. 4 shows an arrangement with common heat recovery, via
which a heat consumer system 9 can be supplied with heat. The heat
consumer system 9 has a common heat exchanger 91, which in the
illustrated preferred embodiment is accommodated in a storage tank
at least partly filled with a heat storage substance, which
temporarily stores the heat dissipated from the heat exchanger.
Therefore, the heat exchanger 91 is also formed as a heat reservoir
92. As is shown in FIG. 4, lines are exemplarily attached to the
heat reservoir 92 at the top and at the bottom, via which heat
consumers can be supplied with
[0151] Only the shortened central inlets 63 and central outlets 64
in FIG. 4 reveal that the illustrated arrangement can preferably
comprise a cooling system, as has been described with respect to
the central heat exchange system 6 in FIGS. 1a to 3. However, the
illustrated heat consumer system 9 can also be considered a cooling
system, since heat is dissipated by the printing machine via the
consumers as well. The shown kind of the line system of the heat
consumer system 9 and the arrangement of the elements of the feed
lines to the heat consumer system 9 can therefore be formed in the
same manner in the inventive heat exchange system 6, and vice
versa.
[0152] In the illustration of FIG. 4, the temperature control
points are in a heat-exchanging relationship with the heat consumer
system 9 preferably via hydraulically separated temperature control
point circuits. The individual, hydraulically separated temperature
control point circuits can preferably be added to the heat
exchanger 91 via exemplarily illustrated circuit valves 653,
654.
[0153] In addition to the so-far described temperature control
points, a blast air cooling device 7 is provided which is also
connected to the heat exchanger 91.
[0154] As is shown, further exhaust heat sources, such as the
water-cooled refrigerating machine, an UV dryer, sheet guide
plates, and the blast or compressed air supply 7 are further
connected to the heat exchanger 91, since here comparatively high
temperature levels are generated for a reasonable use. Other
exhaust heat sources are conceivable as well.
[0155] The heat accommodated in the heat reservoir 92 is dissipated
to the heat consumer 93 as required.
[0156] In the illustrated heat recovery, the different temperature
levels are combined to one mixed temperature, which is higher than
the lowest temperature level but lower than the highest temperature
level.
[0157] FIG. 5 shows a similar arrangement with a heat recovery that
can be used separately depending on the temperature level.
[0158] In the heat recovery shown in FIG. 5, individual consumers
are connected with the respective exhaust heat source, i.e. the
individual temperature control points, via their own feed circuit.
Thereby, the individual consumers can advantageously be assigned an
exhaust heat source that e.g. has a preferred temperature level. A
residual heat flow, which has not been removed from the fluid flow
coming from the temperature control point, is fed to the heat
exchanger 91 via a common fluid circuit, the heat exchanger being
formed as a heat reservoir 92 here as well.
[0159] Further heat consumers and/or a cooling device can
preferably be connected to the lines leading away from the heat
reservoir 92.
[0160] In the embodiment shown in FIG. 5, an example of a
possibility is given of how different temperature levels can be
separately tapped and utilised by means of upstream heat
exchangers. Moreover, after separate use, the residual heat can be
combined in an exhaust heat circuit and optionally be stored in a
downstream heat exchanger and/or buffer tank.
LIST OF REFERENCE NUMERALS
[0161] 1 printing machine [0162] 11 low-temperature zone (NT zone)
[0163] 12 medium-temperature zone (MT zone) [0164] 13
high-temperature zone (HT zone) [0165] 2 cold generator [0166] 3
cooling device [0167] 31 spraying device [0168] 4 cold producer
[0169] 51 low-temperature temperature control point (NT temperature
control point) [0170] 52 medium-temperature temperature control
point (MT temperature control point) [0171] 53 high-temperature
temperature control point (HT temperature control point) [0172] 6
central heat exchange system [0173] 61 pipe system of the central
heat exchange system [0174] 62 heat exchange circuit [0175] 63
central inlet [0176] 631 section of the central inlet [0177] 64
central outlet [0178] 641 section of the central outlet [0179] 65
partial branch [0180] 651 partial inlet [0181] 652 partial outlet
[0182] 653 partial branch valve [0183] 654 partial branch valve
[0184] 661-669 valve [0185] 67 bypass line [0186] 671 bypass valve
[0187] 681-689 heat exchanger [0188] 7 blast air/compressed air
[0189] 81 primary circuit [0190] 82 secondary circuit [0191] 9 heat
consumer system [0192] 91 heat consumer heat exchanger in the
respect temperature control point circuit [0193] 92 central heat
reservoir [0194] 93 heat consumer [0195] 94 feed circuit if the
heat consumer
* * * * *