EP0713767B1 - Arrangement for tempering a dampening fluid and/or selected rollers of a printing machine - Google Patents

Arrangement for tempering a dampening fluid and/or selected rollers of a printing machine Download PDF

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Publication number
EP0713767B1
EP0713767B1 EP95117116A EP95117116A EP0713767B1 EP 0713767 B1 EP0713767 B1 EP 0713767B1 EP 95117116 A EP95117116 A EP 95117116A EP 95117116 A EP95117116 A EP 95117116A EP 0713767 B1 EP0713767 B1 EP 0713767B1
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EP
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Prior art keywords
compressor
output
refrigeration
refrigerant
assembly
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EP95117116A
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German (de)
French (fr)
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EP0713767A1 (en
Inventor
Heinz Mertens
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T E C H N O TRANS AG
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Technotrans SE
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F7/00—Rotary lithographic machines
    • B41F7/20—Details
    • B41F7/24—Damping devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/22—Means for cooling or heating forme or impression cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet

Definitions

  • the invention relates to an arrangement for tempering a Fountain solution and / or selected rollers one Printing machine according to the preamble of claim 1.
  • the invention thus relates generally to the field of Printing using the offset printing process.
  • the arrangement stands out by combining one as a closed system trained cooling fluid circulation system with a Refrigeration device from without affecting the Function and lifetime of the compressor arrangement different cooling capacity can be set.
  • the cooling fluid circulation system therefore does not need a buffer memory in the form a storage container for temporary storage of excessive Cooling fluid quantities, but can be used as a closed circulation system be trained.
  • a compressor e.g. a Piston compressor, designated by a maximum Speed can be switched to a reduced speed can, so that the output of the compressor 10 switched accordingly between full load and part load operation can be.
  • the output of the compressor 10 is a Condenser 2 in connection, in which the refrigerant from gaseous is converted into the liquid state.
  • the liquid refrigerant at the outlet of the condenser 2 is in a refrigerant collector 5, which serves as a store, introduced.
  • the output of the refrigerant collector 5 is connected to the inputs of a first and second heat exchange device 3, 4.
  • the first heat exchange device 3 is part of a dampening solution circulation system indicated at U I , which can be an open system with a storage container (not shown) for storing a sufficient amount of dampening solution.
  • the second heat exchange device 4 is part of a closed cooling fluid circulation system indicated at U II for supplying a roller cooling device (likewise not shown).
  • the output of the collector 5 is on the one hand the entrance of the first heat exchange device 3 via a Shut-off valve 8 and an expansion valve 11 and the other with the input of the second heat exchange device 4 via a Shut-off valve 14 and an expansion valve 16 connected.
  • the output of the first heat exchange device 3 protrudes an evaporative pressure control valve 9 and a non-return valve 23, which is a flow towards the Prevents the heat exchange device 3 and in the opposite direction allows with the entrance of the Compressor 10 in connection while the output of the second Heat exchange device 4 in more detail below Flow control valve 15 described with the input of Compressor 10 is connected.
  • the shut-off valves 8 and 14, which can be solenoid valves, and the flow control valve 15 are actuated as a function of a control device 13 which, as an input variable, receives the signals from sensors 114, 207 for detecting the temperature of the circulating systems U I and U II flowing fluid on the inflow side of the heat exchange devices 3 and 4, respectively.
  • the expansion valves 11 and 16 are controlled as a function of the temperature of the refrigerant at the outlet of the heat exchange devices 3 and 4, respectively.
  • an evaporation pressure control valve 9 can be provided, which is a decrease in the evaporation pressure in the Heat exchange device 3 under a certain lower Limit prevented.
  • a bypass arrangement is provided to part of the gaseous refrigerant at the outlet of the compressor 10 back to lead to its entry page.
  • a pressure detection valve 6 in the return line has the task regardless of respective operating state of the compressor 10 (full or Part-load operation) to ensure that a sufficient Refrigerant throughput guaranteed by the compressor 10 is. In particular, at partial load operation without Refrigerant return is too low a refrigerant throughput present by the compressor 10 so that it no longer would be cooled sufficiently and it would damage the Compressor 10 could come.
  • Pressure sensors 19a and 19b detect the pressure of the refrigerant on the inlet and outlet side of the compressor 10 to this at too low pressure on the inlet side or excessive pressure on the outlet side switch off to damage the compressor prevent how they can occur when certain lower and upper pressure limit values are exceeded or fallen below.
  • an injection valve 7 to Injecting liquid refrigerant into the gaseous Output of the pressure detection valve 6 is provided so that the gaseous output of the pressure detection valve 6 to a preventing damage to the compressor 10 Temperature can be reduced.
  • the injector 7 is connected to the output of the collector 5 and receives the Control signals for setting the coolant injection quantity of a temperature sensor at the inlet of the compressor 10.
  • On Pressure switch 18 is on the input side of the compressor 10 provided to 6 before opening the pressure detection valve Switch compressor 10 from full to part load operation.
  • Pressure switches 19c and 19d at the input of capacitor 2 supply control signals to a pair of fans of the condenser, around them individually according to the pressure of the gaseous Switch refrigerant on or off and at different ambient temperatures constant Maintain pressure conditions in the refrigerant circuit.
  • the flow control valve 15 provided at the outlet of the second heat exchange device 4 for the cooling fluid circulation system U II , that is to say for the system with a higher cooling energy requirement than that of the dampening solution circulation system U I , enables the refrigerant throughput through the heat exchanger 4 to be steplessly regulated and thus adjusted the cooling energy supplied to the heat exchanger 4 is between 0% and a maximum value, for example 100%.
  • the flow control valve 15 simultaneously takes over the function of a shut-off valve in the 0% position.
  • the flow control valve 15 can be set via the control device 13 to an upper limit of the cooling energy supplied to the second heat exchange device 4 if further cooling energy is required to supply the first heat exchange device 3 of the dampening solution circulation system U I.
  • the flow control valve 15 can be set to, for example, a limit value of 2/3 of the total cooling output emitted by the compressor 10 when the dampening solution circulation system U I is in operation, so that it is ensured that a third of the total power for supplying the first heat exchange device 3 is available regardless of the need for the cooling fluid circulation system U II .
  • the shut-off valve 14 at the input of the second heat exchange device 4 for the cooling fluid circulation system U II is in the closed position, and the flow control valve 15 is also set to the position 0% refrigerant throughput, so that no refrigerant can flow through the heat exchange device 4 .
  • the lower cooling capacity requirement of the first heat exchange device 3 of the fountain solution circulation system U I is taken into account in that the compressor 10 is switched to part-load operation (for example 50% of the maximum capacity) by reducing the speed of the compressor 10 accordingly.
  • the pressure detection valve 6 in the return line opens therefore, so that part of the gaseous refrigerant on Flow the output of the compressor 10 back to its input can.
  • the injector 7 is controlled to the temperature to a permissible for the compressor 10 To decrease value. If the cooling capacity is the first Heat exchange device 3 of e.g. 1/3 of the maximum Cooling capacity can e.g. 10% of the output from the compressor 10 Power diverted and to the inlet of the compressor to be led back.
  • the shut-off valve 14 at the entrance of the second Heat exchange device 4 is open, and the flow control valve 15 will correspond to the Cooling fluid inlet temperature to the heat exchange device 4 set a refrigerant flow between 0% and 100%.
  • the shut-off valve 8 at the entrance to the first Heat exchange device 3 is closed, so that Refrigerant only of the second heat exchange device 4 is fed.
  • the compressor 10 can accordingly Refrigeration energy requirement of the second heat exchange device 4 below under these circumstances work at full load or part load, depending on the cooling capacity between 0% and 100% on the part of the flow control valve 15 is specified.
  • heat exchange device 3 prevents that refrigerant from the exit of the second Heat exchange device 4 to the exit of the first Heat exchange device 3 can flow.
  • the shut-off valves 14 and 8 at the inputs of Heat exchangers 3 and 4 are open, and that Flow control valve 15 at the outlet of the second
  • the heat exchange device 4 is controlled by the control device 13 to a maximum cooling capacity corresponding to 2/3 of the Total cooling capacity of the refrigeration device set so that that of the second heat exchanger 4 supplyable cooling capacity to one area e.g. between 0% and is limited to approximately 66%.
  • the rest of the total cooling capacity stands for the supply of the first Heat exchange device 3 regardless of the need of the second Heat exchange device 4 always available.
  • the compressor 10 between Switched full and part load operation, whereby in Part-load operation, a refrigerant return similar to that Operating mode "Only dampening solution cooling" can take place.
  • the Shut-off valve 14 switches when the cooling fluid set temperature is reached, which is detected by the sensor 207, the Refrigerant flow through the second heat exchange device 4 or enables such a refrigerant flow as soon as the predetermined cooling fluid temperature is exceeded, wherein according to the prevailing cooling capacity requirement of first heat exchanger 3 of the compressor 10 under partial or Full load works.
  • the invention was previously based on an arrangement with a refrigeration device described that only one contains only power-switchable compressor. Instead of two or more of them could be parallel to each other arranged compressors are provided, each not need to be switchable, but according to that respective energy requirements can be switched on or off, so that at the common output the compressor has a maximum or minimal cooling capacity.
  • the return of the gaseous refrigerant from the common exit to one common input of the compressor connected in parallel in an analogous manner to that described above Refrigeration device take place.
  • Fig. 2 shows the second embodiment of the invention, the differ from the previous one and shown in FIG. 1 Embodiment differs in particular in that a Refrigerant recirculation using a Pressure detection valve 6 containing return line is omitted and the adjustment range of the flow control valve 15 between a maximum value of e.g. 100% and is limited to a minimum value that is much larger than 0%, e.g. 40%.
  • the means that in the recycled refrigerant is a liquid refrigerant Can inject cooling.
  • the embodiment according to FIG. 2 is therefore characterized by a smaller number of components out, reducing the effort for assembly and maintenance is reduced and cost-effective operation can be achieved can.
  • FIG. 2 be designed as that of FIG. 1.
  • two or more compressors 10 ', 10' 'are provided in parallel lie to each other and are designed so that they each a fraction, e.g. 50% of the total required Can deliver cooling capacity.
  • Each compressor is 10 ', 10' '
  • the outputs of the check valves 23 ', 23' ' are connected to the Input of capacitor 2 in connection.
  • the entire of the Cooling device delivered cooling capacity between 20% and 100% continuously by means of the flow control valve 15 can be set.
  • Overheating of the compressors 10 ' 10 '' in the "cooling fluid cooling" mode, i.e. at open shut-off valve 16, is limited by the Adjustment range of the flow control valve 15 to Prevents a minimum value that is significantly greater than 0%, so that there is always a certain amount of refrigerant in the direction will flow to the compressors 10 ', 10' '.
  • the refrigeration device according to both of the above Embodiments of the invention are preferably one separate unit with integrated heat exchange devices 3, 4 and inlet and outlet connections for the ends to be connected Dampening solution or cooling fluid circulation systems.
  • the invention thus enables the cooling power output by the compressor 10 to be specifically adapted to the respective operating conditions. This ensures an energy supply to the second heat exchange device 4, which is matched to the requirements of the cooling fluid circulation system U II in the different operating modes, so that an increased energy supply to the heat exchange device 4 is avoided.
  • the cooling fluid circulation system U II can therefore be designed as a closed system, since an energy buffer store in the form of a cooling fluid storage container can be dispensed with.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Description

Die Erfindung betrifft eine Anordnung zur Temperierung eines Feuchtmittels und/oder ausgewählter Walzen einer Druckmaschine gemäss Oberbegriff des Patentanspruches 1. Die Erfindung bezieht sich damit allgemein auf das Gebiet des Druckens im Offset-Druckverfahren.The invention relates to an arrangement for tempering a Fountain solution and / or selected rollers one Printing machine according to the preamble of claim 1. The The invention thus relates generally to the field of Printing using the offset printing process.

Bei einer bekannten Anordnung (EP-A-0 602 312) sind die Umlaufsysteme für das Feuchtmittel und für ein Kühlfluid zur Versorgung einer Walzenkühlvorrichtung jeweils als offene Systeme ausgebildet, indem jedem Umlaufsystem ein Vorratsbehälter zugeordnet ist, der einen Pufferspeicher für das jeweilige Strömungsmittel des Systems bildet. Bei der bekannten Anordnung ist insbesondere auch der mit dem offenen Umlaufsystem für das Kühlfluid verbundene Vorratsbehälter notwendig, da die die Wärmetauscheinrichtungen der Umlaufsysteme mit dem Kältemittel versorgende Kälteerzeugungseinrichtung auf eine maximal notwendige Leistung ausgelegt ist. Dies bedeutet, dass bei einem Offset-Druckbetrieb ohne Feuchtmittelkühlung die Wärmetauscheinrichtung für das Kühlfluid-Umlaufsystem mit maximaler Kälteleistung arbeitet und dies zu einer übermässigen Kühlung des Kühlfluids führen könnte, wenn, wie es bei einem geschlossenen System der Fall, eine nicht ausreichende Kühlfluidmenge zur Aufnahme der überhöhten Kälteenergie vorhanden ist. M.a.W.: Bei der bekannten Temperierungsanordnung fängt der Vorratsbehälter einen Teil der überschüssigen Kälteenergie ab. Wollte man den Vorratsbehälter weglassen, müsste ein wiederholtes Ein- und Ausschalten des auf maximale Kälteleistung ausgelegten Verdichters vorgenommen werden, um die abgegebene Kälteleistung zu begrenzen. Dies ist bei den dann erforderlich werdenden kurzen Schaltzyklen praktisch nicht durchführbar, da Verdichter eine gewisse minimale kontinuierliche Laufzeit benötigen, anderenfalls die Gefahr von Beschädigungen mit vorzeitigem Ausfall des Verdichters bestünde. Ein weiterer Nachteil der bekannten Anordnung ist der erhöhte Energiebedarf, da die Kälteerzeugungseinrichtung unabhängig von der beim jeweiligen Betrieb geforderten tatsächlichen Kälteleistung stets mit Maximalleistung betrieben werden muss.In a known arrangement (EP-A-0 602 312) they are Circulation systems for the dampening solution and for a cooling fluid Supply of a roller cooling device as an open one Systems formed by each circulation system Storage container is assigned, which is a buffer for forms the respective fluid of the system. In the known arrangement is in particular the one with the open Circulation system for the reservoir connected to the cooling fluid necessary because the the heat exchange facilities of the Circulation systems with the refrigerant supply Refrigeration device to a maximum necessary Performance is designed. This means that in an offset printing operation without dampening solution cooling Heat exchange device for the cooling fluid circulation system with maximum cooling capacity works and this to a could result in excessive cooling of the cooling fluid if, like it is the case with a closed system, one is not sufficient amount of cooling fluid to accommodate the excessive Cooling energy is present. M.a.W .: In the known Temperature control arrangement catches a part of the storage container excess cooling energy. Did you want that If you omit the storage container, you would have to Switching off the designed for maximum cooling capacity Compressor made to the delivered Limit cooling capacity. This is with the then short switching cycles that are practically not required feasible because the compressor has a certain minimum need continuous duration, otherwise the danger damage with premature failure of the compressor exist. Another disadvantage of the known arrangement is the increased energy requirement because the refrigeration device regardless of what is required by the respective company actual cooling capacity always at maximum capacity must be operated.

Es besteht daher Bedarf nach einer Anordnung der gattungsgemässen Art, die wenigstens hinsichtlich einer der Gesichtspunkte "apparativer Aufwand", "Energieverbrauch" oder "Betriebsverhalten" verbessert ist.There is therefore a need for an arrangement of the generic type, at least with regard to one of the Aspects of "expenditure on equipment", "energy consumption" or "Operating behavior" is improved.

Zur Lösung dieser Aufgabe wird auf den Patentanspruch 1 verwiesen. Die Anordnung zeichnet sich durch die Kombination eines als geschlossenes System ausgebildeten Kühlfluid-Umlaufsystems mit einer Kälteerzeugungseinrichtung aus, die ohne Beeinträchtigung der Funktion und Lebenszeit der Verdichteranordnung auf unterschiedliche Kälteleistung eingestellt werden kann. Durch die Umschaltung kann die Kälteleistung auf den jeweiligen Bedarf der Wärmetauscheinrichtung für das eine oder andere Umlaufsystem abgestimmt werden, und insbesondere kann eine übermässige Beaufschlagung einer der Wärmetauscheinrichtungen mit Kälteenergie wirksam vermieden werden. Das Kühlfluid-Umlaufsystem benötigt daher keinen Pufferspeicher in Gestalt eines Vorratsbehälters zur Zwischenspeicherung übermässiger Kühlfluidmengen, sondern kann als geschlossenes Umlaufsystem ausgebildet sein. Dies wir bevorzugt, da dadurch nicht nur das Betriebsverhalten der gesamten Temperierungsanlage wesentlich verbessert wird, indem Verunreinigungen des Kühlfluides naturgemäss nicht auftreten können, sondern gleichzeitig wird auch der apparative Aufwand mit entsprechender Kosteneinsparung herabgesetzt, da auf einen Vorratsbehälter für das Kühlfluid verzichtet werden kann. Der etwas erhöhte Aufwand für die Ausbildung der Kälteerzeugungseinrichtung fällt demgegenüber nicht ins Gewicht, zumal mit der erfindungsgemässen Anordnung auch wesentliche Einsparungen an Primärenergie erzielt werden können.To solve this problem, claim 1 referred. The arrangement stands out by combining one as a closed system trained cooling fluid circulation system with a Refrigeration device from without affecting the Function and lifetime of the compressor arrangement different cooling capacity can be set. By the switching can adjust the cooling capacity to the respective Need the heat exchange device for one or the other Circulatory system can be tuned, and in particular, a excessive exposure to one of the heat exchange devices can be effectively avoided with cooling energy. The cooling fluid circulation system therefore does not need a buffer memory in the form a storage container for temporary storage of excessive Cooling fluid quantities, but can be used as a closed circulation system be trained. This is preferred because it not only the operating behavior of the entire temperature control system is significantly improved by contaminating the Cooling fluids cannot occur naturally, but rather At the same time, the expenditure on equipment is also included corresponding cost savings reduced, because on one Reservoir for the cooling fluid can be dispensed with. Of the somewhat increased effort for training the In contrast, the refrigeration device does not fall into place Weight, especially with the arrangement according to the invention substantial savings in primary energy can be achieved can.

Die Erfindung wird nachfolgend anhand von Ausführungsformen und der Zeichnung näher erläutert. Es zeigen:

  • Fig. 1 den Schaltplan einer Kälteerzeugungseinrichtung gemäss einer ersten Ausführungsform der Erfindung mit angedeuteten Umlaufsystemen für das Feuchtmittel und für ein Kühlfluid, und
  • Fig. 2 in einer Ansicht ähnlich Fig. 1 den Schaltplan einer Kälteerzeugungseinrichtung gemäss einer zweiten Ausführungsform der Erfindung.
    • The invention is explained in more detail below with the aid of embodiments and the drawing. Show it:
  • Fig. 1 shows the circuit diagram of a refrigeration device according to a first embodiment of the invention with indicated circulation systems for the dampening solution and for a cooling fluid, and
  • Fig. 2 in a view similar to Fig. 1, the circuit diagram of a refrigeration device according to a second embodiment of the invention.

    • In der Zeichnung sind die mit dem Feuchtmittel bzw. Kühlfluid versorgten Einrichtungen an der Druckmaschine, d.h. das Feuchtmittel-Walzenauftragssystem sowie die Kühleinrichtung für z.B. die Farbreiberwalzen oder andere ausgewählte Walzen der Druckmaschine weggelassen. Derartige Einrichtungen sind dem Fachmann grundsätzlich bekannt und brauchen daher nicht näher erläutert zu werden.In the drawing are those with the dampening solution or cooling fluid supplied facilities on the printing press, i.e. the Dampening solution roller application system and the cooling device for e.g. the ink roller or other selected rollers omitted from the printing press. Such facilities are basically known to the expert and therefore do not need to be explained in more detail.

    In Fig. 1, die die erste Ausführungsform der Erfindung zeigt, ist mit dem Bezugszeichen 10 ein Verdichter, z.B. ein Kolbenverdichter, bezeichnet, der von einer maximalen Drehzahl auf eine verringerte Drehzahl umgeschaltet werden kann, so dass die Leistungsabgabe des Verdichters 10 entsprechend zwischen Vollast- und Teillastbetrieb geschaltet werden kann. Der Ausgang des Verdichters 10 steht mit einem Kondensator 2 in Verbindung, in dem das Kältemittel vom gasförmigen in den flüssigen Zustand überführt wird. Das flüssige Kältemittel am Ausgang des Kondensators 2 wird in einen Kältemittelsammler 5, der als Speicher dient, eingeführt.1, which shows the first embodiment of the invention, is a compressor, e.g. a Piston compressor, designated by a maximum Speed can be switched to a reduced speed can, so that the output of the compressor 10 switched accordingly between full load and part load operation can be. The output of the compressor 10 is a Condenser 2 in connection, in which the refrigerant from gaseous is converted into the liquid state. The liquid refrigerant at the outlet of the condenser 2 is in a refrigerant collector 5, which serves as a store, introduced.

    Der Ausgang des Kältemittelsammlers 5 ist mit den Eingängen einer ersten und zweiten Wärmetauscheinrichtung 3, 4 verbunden. Die erste Wärmetauscheinrichtung 3 ist Teil eines bei UI angedeuteten Feuchtmittel-Umlaufsystems, welches ein offenes System mit einem Vorratsbehälter (nicht gezeigt) für die Bevorratung einer ausreichenden Feuchtmittelmenge sein kann. Die zweite Wärmetauscheinrichtung 4 ist Teil eines bei UII angedeuteten geschlossenen Kühlfluid-Umlaufsystems zur Versorgung einer Walzenkühleinrichtung (ebenfalls nicht gezeigt).The output of the refrigerant collector 5 is connected to the inputs of a first and second heat exchange device 3, 4. The first heat exchange device 3 is part of a dampening solution circulation system indicated at U I , which can be an open system with a storage container (not shown) for storing a sufficient amount of dampening solution. The second heat exchange device 4 is part of a closed cooling fluid circulation system indicated at U II for supplying a roller cooling device (likewise not shown).

    Insbesondere ist der Ausgang des Sammlers 5 einerseits mit dem Eingang der ersten Wärmetauscheinrichtung 3 über ein Absperrventil 8 und ein Expansionsventil 11 und andererseits mit dem Eingang der zweiten Wärmetauscheinrichtung 4 über ein Absperrventil 14 und ein Expansionsventil 16 verbunden. In particular, the output of the collector 5 is on the one hand the entrance of the first heat exchange device 3 via a Shut-off valve 8 and an expansion valve 11 and the other with the input of the second heat exchange device 4 via a Shut-off valve 14 and an expansion valve 16 connected.

    Der Ausgang der ersten Wärmetauscheinrichtung 3 steht über ein Verdampfungsdruck-Regelventil 9 und ein Rückflusssperrventil 23, welches eine Strömung in Richtung auf den Ausgang der Wärmetauscheinrichtung 3 verhindert und in die entgegengesetzte Richtung ermöglicht, mit dem Eingang des Verdichters 10 in Verbindung, während der Ausgang der zweiten Wärmetauscheinrichtung 4 über ein nachfolgend näher beschriebenes Durchfluss-Stellventil 15 mit dem Eingang des Verdichters 10 verbunden ist.The output of the first heat exchange device 3 protrudes an evaporative pressure control valve 9 and a non-return valve 23, which is a flow towards the Prevents the heat exchange device 3 and in the opposite direction allows with the entrance of the Compressor 10 in connection while the output of the second Heat exchange device 4 in more detail below Flow control valve 15 described with the input of Compressor 10 is connected.

    Die Absperrventile 8 und 14, bei denen es sich um Magnetventile handeln kann, sowie das Durchfluss-Stellventil 15 werden in Abhängigkeit von einer Steuereinrichtung 13 betätigt, die als Eingangsgrösse die Signale von Messfühlern 114, 207 zur Erfassung der Temperatur des in den Umlaufsystemen UI und UII strömenden Strömungsmittels zuflusseitig der Wärmetauscheinrichtungen 3 bzw. 4 erhält. Die Expansionsventile 11 und 16 werden in Abhängigkeit von der Temperatur des Kältemittels am Ausgang der Wärmetauscheinrichtungen 3 bzw. 4 gesteuert.The shut-off valves 8 and 14, which can be solenoid valves, and the flow control valve 15 are actuated as a function of a control device 13 which, as an input variable, receives the signals from sensors 114, 207 for detecting the temperature of the circulating systems U I and U II flowing fluid on the inflow side of the heat exchange devices 3 and 4, respectively. The expansion valves 11 and 16 are controlled as a function of the temperature of the refrigerant at the outlet of the heat exchange devices 3 and 4, respectively.

    In der Verbindung zwischen dem Ausgang der ersten Wärmetauscheinrichtung 3 und dem Eingang des Verdichters 10 kann ein Verdampfungsdruck-Regelventil 9 vorgesehen sein, welches ein Absinken des Verdampfungsdruckes in der Wärmetauscheinrichtung 3 unter einen bestimmten unteren Grenzwert verhindert.In the connection between the exit of the first Heat exchange device 3 and the input of the compressor 10 an evaporation pressure control valve 9 can be provided, which is a decrease in the evaporation pressure in the Heat exchange device 3 under a certain lower Limit prevented.

    Eine Bypassanordnung ist vorgesehen, um einen Teil des gasförmigen Kältemittels am Ausgang des Verdichters 10 zurück zu dessen Eingangsseite zu führen. Ein Druckerfassungsventil 6 in der Rückführleitung hat die Aufgabe, unabhängig vom jeweiligen Betriebszustand des Verdichters 10 (Voll- oder Teillastbetrieb) dafür zu sorgen, dass ein ausreichender Kältemitteldurchsatz durch den Verdichter 10 gewährleistet ist. Insbesondere würde bei Teillastbetrieb ohne Kältemittelrückführung ein zu geringer Kältemitteldurchsatz durch den Verdichter 10 vorliegen, so dass dieser nicht mehr ausreichend gekühlt werden würde und es zu Beschädigungen des Verdichters 10 kommen könnte. Druckfühler 19a und 19b erfassen den Druck des Kältemittels ein- bzw. ausgangsseitig des Verdichters 10, um diesen bei zu geringem Druck eingangsseitig bzw. zu hohem Druck ausgangsseitig abzuschalten, um Beschädigungen des Verdichters zu verhindern, wie sie auftreten können, wenn gewisse untere und obere Druckgrenzwerte unter- bzw. überschritten werden.A bypass arrangement is provided to part of the gaseous refrigerant at the outlet of the compressor 10 back to lead to its entry page. A pressure detection valve 6 in the return line has the task regardless of respective operating state of the compressor 10 (full or Part-load operation) to ensure that a sufficient Refrigerant throughput guaranteed by the compressor 10 is. In particular, at partial load operation without Refrigerant return is too low a refrigerant throughput present by the compressor 10 so that it no longer would be cooled sufficiently and it would damage the Compressor 10 could come. Pressure sensors 19a and 19b detect the pressure of the refrigerant on the inlet and outlet side of the compressor 10 to this at too low pressure on the inlet side or excessive pressure on the outlet side switch off to damage the compressor prevent how they can occur when certain lower and upper pressure limit values are exceeded or fallen below.

    Das heisse zum Eingang des Verdichters 10 rückgeführte gasförmige Kältemittel würde eine Überhitzung des Verdichters hervorrufen. Um dies zu verhindern ist zur Kühlung des rückgeführten Kältemittels ein Einspritzventil 7 zum Einspritzen von flüssigem Kältemittel in den gasförmigen Ausgang des Druckerfassungsventiles 6 vorgesehen, so dass der gasförmige Ausgang des Druckerfassungsventiles 6 auf eine eine Beschädigungen des Verdichters 10 verhindernde Temperatur herabgesetzt werden kann. Das Einspritzventil 7 ist mit dem Ausgang des Sammlers 5 verbunden und erhält die Stellsignale zur Einstellung der Kühlmitteleinspritzmenge von einem Temperaturfühler am Eingang des Verdichters 10. Ein Druckschalter 18 eingangsseitig des Verdichters 10 ist vorgesehen, um vor Öffnen des Druckerfassungsventiles 6 den Verdichter 10 von Voll- auf Teillastbetrieb umzuschalten.That is, returned to the input of the compressor 10 gaseous refrigerant would overheat the compressor cause. To prevent this, the cooling of the recycled refrigerant an injection valve 7 to Injecting liquid refrigerant into the gaseous Output of the pressure detection valve 6 is provided so that the gaseous output of the pressure detection valve 6 to a preventing damage to the compressor 10 Temperature can be reduced. The injector 7 is connected to the output of the collector 5 and receives the Control signals for setting the coolant injection quantity of a temperature sensor at the inlet of the compressor 10. On Pressure switch 18 is on the input side of the compressor 10 provided to 6 before opening the pressure detection valve Switch compressor 10 from full to part load operation.

    Druckschalter 19c und 19d am Eingang des Kondensators 2 liefern Steuersignale an ein Paar Gebläse des Kondensators, um diese einzeln entsprechend dem Druck des gasförmigen Kältemittels ein- bzw. auszuschalten und bei unterschiedlichen Umgebungstemperaturen konstante Druckverhältnisse im Kältemittelkreislauf einzuhalten.Pressure switches 19c and 19d at the input of capacitor 2 supply control signals to a pair of fans of the condenser, around them individually according to the pressure of the gaseous Switch refrigerant on or off and at different ambient temperatures constant Maintain pressure conditions in the refrigerant circuit.

    Das am Ausgang der zweiten Wärmetauscheinrichtung 4 für das Kühlfluid-Umlaufsystem UII, d.h. für das System mit höherem Kälteenergiebedarf als der des Feuchtmittel-Umlaufsystems UI, vorgesehene Durchfluss-Stellventil 15 ermöglicht eine stufenlose Regelung des Kältemitteldurchsatzes durch den Wärmetauscher 4 und damit eine Einstellung der dem Wärmetauscher 4 zugeführten Kälteenergie zwischen 0 % und einem Maximalwert, z.B. 100 %. Das Durchfluss-Stellventil 15 übernimmt gleichzeitig in der Stellung 0 % die Funktion eines Absperrventiles. Darüber hinaus kann das Durchfluss-Stellventil 15 über die Steuereinrichtung 13 auf eine obere Begrenzung der der zweiten Wärmetauscheinrichtung 4 zugeführten Kälteenergie eingestellt werden, wenn weitere Kälteenergie für die Versorgung der ersten Wärmetauscheinrichtung 3 des Feuchtmittel-Umlaufsystems UI benötigt wird. Wegen des höheren Kälteenergiebedarfes des Kühlfluid-Umlaufsystems UII kann das Durchfluss-Stellventil 15 bei gleichzeitig in Betrieb befindlichem Feuchtmittel-Umlaufsystem UI auf z.B. einen Grenzwert von 2/3 der gesamten vom Verdichter 10 abgegebenen Kälteleistung eingestellt werden, so dass gewährleistet ist, dass ein Drittel der Gesamtleistung für die Versorgung der ersten Wärmetauscheinrichtung 3 unabhängig vom Bedarf des Kühlfluid-Uumlaufsystemes UII zur Verfügung steht.The flow control valve 15 provided at the outlet of the second heat exchange device 4 for the cooling fluid circulation system U II , that is to say for the system with a higher cooling energy requirement than that of the dampening solution circulation system U I , enables the refrigerant throughput through the heat exchanger 4 to be steplessly regulated and thus adjusted the cooling energy supplied to the heat exchanger 4 is between 0% and a maximum value, for example 100%. The flow control valve 15 simultaneously takes over the function of a shut-off valve in the 0% position. In addition, the flow control valve 15 can be set via the control device 13 to an upper limit of the cooling energy supplied to the second heat exchange device 4 if further cooling energy is required to supply the first heat exchange device 3 of the dampening solution circulation system U I. Because of the higher cooling energy requirement of the cooling fluid circulation system U II , the flow control valve 15 can be set to, for example, a limit value of 2/3 of the total cooling output emitted by the compressor 10 when the dampening solution circulation system U I is in operation, so that it is ensured that a third of the total power for supplying the first heat exchange device 3 is available regardless of the need for the cooling fluid circulation system U II .

    Mit den Bezugszeichen 12 am Eingang der Wärmetauscheinrichtungen 3 und 4 sind Schaugläser angedeutet, die eine visuelle Kontrolle des den Wärmetauscheinrichtungen 3, 4 zufliessenden Kältemittels ermöglichen. Mit 17 ist ein Filter am Ausgang des Sammlers 5 angedeutet, um wässrige Bestandteile aus dem Kältemittel auszufiltern. With the reference number 12 at the entrance to Heat exchangers 3 and 4 are indicated sight glasses, which is a visual inspection of the heat exchangers 3, 4 allow inflowing refrigerant. At 17 is one Filters indicated at the outlet of the collector 5 to aqueous Filter out components from the refrigerant.

    Die, wie vorbeschrieben, aufgebaute Anordnung arbeitet wie folgt:The arrangement, as described above, works like follows:

    Betriebsart: Nur Kühlung des FeuchtmittelsOperating mode: Cooling of the dampening solution only

    Bei dieser Betriebsart steht das Absperrventil 14 am Eingang der zweiten Wärmetauscheinrichtung 4 für das Kühlfluid-Umlaufsystem UII in Schliesstellung, und ebenfalls ist das Durchfluss-Stellventil 15 auf die Position 0%-Kältemitteldurchsatz eingestellt, so dass kein Kältemittel durch die Wärmetauscheinrichtung 4 strömen kann. Dem geringeren Kälteleistungsbedarf der ersten Wärmetauscheinrichtung 3 des Feuchtwasser-Umlaufsystems UI wird dadurch Rechnung getragen, dass der Verdichter 10 auf Teillastbetrieb (z.B. 50% der Maximalleistung) umgeschaltet wird, indem die Drehzahl des Verdichters 10 entsprechend herabgesetzt wird.In this operating mode, the shut-off valve 14 at the input of the second heat exchange device 4 for the cooling fluid circulation system U II is in the closed position, and the flow control valve 15 is also set to the position 0% refrigerant throughput, so that no refrigerant can flow through the heat exchange device 4 . The lower cooling capacity requirement of the first heat exchange device 3 of the fountain solution circulation system U I is taken into account in that the compressor 10 is switched to part-load operation (for example 50% of the maximum capacity) by reducing the speed of the compressor 10 accordingly.

    Das Druckerfassungsventil 6 in der Rückführleitung öffnet daher, so dass ein Teil des gasförmigen Kältemittels am Ausgang des Verdichters 10 zu seinem Eingang zurückfliessen kann. Entsprechend der Temperatur des Kältemittels am Eingang des Verdichters 10 wird das Einspritzventil 7 gesteuert, um die Temperatur auf einen für den Verdichter 10 zulässigen Wert herabzusetzen. Bei einem Kälteleistungsbedarf der ersten Wärmetauscheinrichtung 3 von z.B. 1/3 der maximalen Kälteleistung kann z.B. 10% der vom Verdichter 10 abgegebenen Leistung abgezweigt und zum Eingang des Verdichters zurückgeführt werden.The pressure detection valve 6 in the return line opens therefore, so that part of the gaseous refrigerant on Flow the output of the compressor 10 back to its input can. According to the temperature of the refrigerant at the entrance of the compressor 10, the injector 7 is controlled to the temperature to a permissible for the compressor 10 To decrease value. If the cooling capacity is the first Heat exchange device 3 of e.g. 1/3 of the maximum Cooling capacity can e.g. 10% of the output from the compressor 10 Power diverted and to the inlet of the compressor to be led back.

    Betriebsart: Nur Kühlung des KühlfluidesOperating mode: Cooling of the cooling fluid only

    Das Absperrventil 14 am Eingang der zweiten Wärmetauscheinrichtung 4 ist geöffnet, und das Durchfluss-Stellventil 15 wird entsprechend der Kühlfluidzulauftemperatur zur Wärmetauscheinrichtung 4 auf einen Kältemitteldurchsatz zwischen 0% und 100% eingestellt.The shut-off valve 14 at the entrance of the second Heat exchange device 4 is open, and the flow control valve 15 will correspond to the Cooling fluid inlet temperature to the heat exchange device 4 set a refrigerant flow between 0% and 100%.

    Das Absperrventil 8 am Eingang der ersten Wärmetauscheinrichtung 3 ist geschlossen, so dass das Kältemittel nur der zweiten Wärmetauscheinrichtung 4 zugeführt wird. Der Verdichter 10 kann entsprechend dem Kälteenergiebedarf der zweiten Wärmetauscheinrichtung 4 unter diesen Umständen bei Vollast- oder Teillastbetrieb arbeiten, je nachdem, welche Kälteleistung zwischen 0% und 100% seitens des Durchfluss-Stellventiles 15 vorgegeben wird.The shut-off valve 8 at the entrance to the first Heat exchange device 3 is closed, so that Refrigerant only of the second heat exchange device 4 is fed. The compressor 10 can accordingly Refrigeration energy requirement of the second heat exchange device 4 below under these circumstances work at full load or part load, depending on the cooling capacity between 0% and 100% on the part of the flow control valve 15 is specified.

    Im Teillastbetrieb des Verdichters 10 erfolgt eine Kältemittelrückführung entsprechend den in Verbindung mit der Betriebsart "Nur Kühlung des Feuchtmittels" beschriebenen Verhältnissen.In the partial load operation of the compressor 10 there is a Refrigerant return according to the in connection with the Operating mode "Cooling of the dampening solution only" described Relationships.

    Das Rückflussperrventil 23 am Ausgang der ersten Wärmetauscheinrichtung 3 verhindert in dieser Betriebsart, dass Kältemittel vom Ausgang der zweiten Wärmetauscheinrichtung 4 zum Ausgang der ersten Wärmetauscheinrichtung 3 strömen kann.The check valve 23 at the outlet of the first In this operating mode, heat exchange device 3 prevents that refrigerant from the exit of the second Heat exchange device 4 to the exit of the first Heat exchange device 3 can flow.

    Betriebsart: Kühlung des Feuchtmittels und KühlfluidesOperating mode: cooling of the dampening solution and cooling fluid

    Die Absperrventile 14 und 8 an den Eingängen der Wärmetauscheinrichtungen 3 bzw. 4 sind geöffnet, und das Durchfluss-Stellventil 15 am Ausgang der zweiten Wärmetauscheinrichtung 4 wird durch die Steuereinrichtung 13 auf eine maximale Kälteleistung entsprechend 2/3 der Gesamtkälteleistung der Kälteerzeugungseinrichtung eingestellt, so dass die der zweiten Wärmetauscheinrichtung 4 zuführbare Kälteleistung auf einen Bereich z.B. zwischen 0% und ca. 66% begrenzt ist. Der Rest der Gesamtkälteleistung steht somit für die Versorgung der ersten Wärmetauscheinrichtung 3 unabhängig vom Bedarf der zweiten Wärmetauscheinrichtung 4 stets zur Verfügung.The shut-off valves 14 and 8 at the inputs of Heat exchangers 3 and 4 are open, and that Flow control valve 15 at the outlet of the second The heat exchange device 4 is controlled by the control device 13 to a maximum cooling capacity corresponding to 2/3 of the Total cooling capacity of the refrigeration device set so that that of the second heat exchanger 4 supplyable cooling capacity to one area e.g. between 0% and is limited to approximately 66%. The rest of the total cooling capacity stands for the supply of the first Heat exchange device 3 regardless of the need of the second Heat exchange device 4 always available.

    Entsprechend dem Kälteleistungsbedarf der Wärmetauscheinrichtungen 3, 4 wird der Verdichter 10 zwischen Voll- und Teillastbetrieb umgeschaltet, wobei im Teillastbetrieb eine Kältemittelrückführung analog zu der Betriebsart "Nur Feuchtmittelkühlung" erfolgen kann. Das Absperrventil 14 schaltet bei Erreichen der Kühlfluid-Solltemperatur, die über den Fühler 207 erfasst wird, den Kältemittelfluss durch die zweite Wärmetauscheinrichtung 4 ab bzw. ermöglicht einen derartigen Kältemittelfluss, sobald die vorgegebene Kühlfluidtemperatur überschritten wird, wobei entsprechend dem dabei herrschenden Kälteleistungsbedarf der ersten Wärmetauscheinrichtung 3 der Verdichter 10 unter Teil- oder Vollast arbeitet.According to the cooling capacity requirement of Heat exchange devices 3, 4, the compressor 10 between Switched full and part load operation, whereby in Part-load operation, a refrigerant return similar to that Operating mode "Only dampening solution cooling" can take place. The Shut-off valve 14 switches when the cooling fluid set temperature is reached, which is detected by the sensor 207, the Refrigerant flow through the second heat exchange device 4 or enables such a refrigerant flow as soon as the predetermined cooling fluid temperature is exceeded, wherein according to the prevailing cooling capacity requirement of first heat exchanger 3 of the compressor 10 under partial or Full load works.

    Die Erfindung wurde vorausgehend anhand einer Anordnung mit einer Kälteerzeugungseinrichtung beschrieben, die nur einen einzigen leistungsumschaltbaren Verdichter enthält. Anstelle davon könnten auch zwei oder mehrere Parallel zueinander angeordnete Verdichter vorgesehen werden, die jeweils nicht leistungsumschaltbar sein brauchen, sondern entsprechend dem jeweiligen Energiebedarf zu- oder abgeschaltet werden können, so dass am gemeinsamen Ausgang der Verdichter eine maximale oder minimale Kälteleistung vorliegt. Die Rückführung des gasförmigen Kältemittels vom gemeinsamen Ausgang zu einem gemeinsamen Eingang der parallel geschalteten Verdichter kann in analoger Weise wie bei der vorbeschriebenen Kälteerzeugungseinrichtung erfolgen. The invention was previously based on an arrangement with a refrigeration device described that only one contains only power-switchable compressor. Instead of two or more of them could be parallel to each other arranged compressors are provided, each not need to be switchable, but according to that respective energy requirements can be switched on or off, so that at the common output the compressor has a maximum or minimal cooling capacity. The return of the gaseous refrigerant from the common exit to one common input of the compressor connected in parallel in an analogous manner to that described above Refrigeration device take place.

    Fig. 2 zeigt die zweite Ausführungsform der Erfindung, die sich von der vorausgehenden und in Fig. 1 gezeigten Ausführungsform insbesondere dadurch unterscheidet, dass eine Kältemittelrückführung mittels einer das Druckerfassungsventil 6 enthaltenden Rückführleitung weggelassen ist und der Stellbereich des Durchfluss-Stellventiles 15 zwischen einem Maximalwert von z.B. 100 % und einem Minimalwert begrenzt ist, der wesentlich grösser als 0 %, z.B. 40 %, beträgt. Bei der Ausführungsform nach Fig. 2 sind ferner die Mittel weggelassen, die in das rückgeführte Kältemittel ein flüssiges Kältemittel zur Kühlung einspritzen können. Die Ausführungsform nach Fig. 2 zeichnet sich daher durch eine geringere Anzahl an Bauteilen aus, wodurch der Aufwand für die Montage und Wartung reduziert ist und ein kostengünstiger Betrieb erreicht werden kann.Fig. 2 shows the second embodiment of the invention, the differ from the previous one and shown in FIG. 1 Embodiment differs in particular in that a Refrigerant recirculation using a Pressure detection valve 6 containing return line is omitted and the adjustment range of the flow control valve 15 between a maximum value of e.g. 100% and is limited to a minimum value that is much larger than 0%, e.g. 40%. In the embodiment according to Fig. 2 are also omitted the means that in the recycled refrigerant is a liquid refrigerant Can inject cooling. The embodiment according to FIG. 2 is therefore characterized by a smaller number of components out, reducing the effort for assembly and maintenance is reduced and cost-effective operation can be achieved can.

    Im übrigen kann die Ausführungsform der Erfindung nach Fig. 2 wie diejenige nach Fig. 1 ausgebildet sein. Vorzugsweise sind jedoch anstelle nur eines leistungsumschaltbaren Verdichters zwei oder mehr Verdichter 10', 10'' vorgesehen, die parallel zueinander liegen und so ausgelegt sind, dass sie jeweils einen Bruchteil, z.B. 50 %, der gesamten erforderlichen Kälteleistung liefern können. Jedem Verdichter 10', 10'' ist ausgangsseitig in Reihe ein Rückflussperrventil 23' bzw. 23'' zugeordnet. Die Ausgänge der Rückflussperrventile 23', 23'' stehen über eine gemeinsame Verbindungsleitung mit dem Eingang des Kondensators 2 in Verbindung.Otherwise, the embodiment of the invention according to FIG. 2 be designed as that of FIG. 1. Are preferred however, instead of just a capacity switchable compressor two or more compressors 10 ', 10' 'are provided in parallel lie to each other and are designed so that they each a fraction, e.g. 50% of the total required Can deliver cooling capacity. Each compressor is 10 ', 10' ' On the output side, a non-return valve 23 'or 23' ' assigned. The outputs of the check valves 23 ', 23' ' are connected to the Input of capacitor 2 in connection.

    Indem einer der Verdichter 10', 10'' abgeschaltet und das Durchfluss-Stellventil 15 auf den Minimalwert von z.B. 40 % eingestellt wird, kann somit die gesamte von der Kälteerzeugungseinrichtung gelieferte Kälteleistung zwischen 20 % und 100 % stufenlos mittels des Durchfluss-Stellventiles 15 eingestellt werden. Eine Überhitzung der Verdichter 10', 10'' in der Betriebssart "Kühlung des Kühlfluid", d.h. bei geöffnetem Absperrventil 16, wird durch die Begrenzung des Stellbereiches des Durchfluss-Stellventiles 15 auf einen Minimalwert, der wesentlich grösser als 0 % ist, verhindert, so dass stets eine gewisse Menge an Kältemittel in Richtung auf die Verdichter 10', 10'' abfliessen wird.By switching off one of the compressors 10 ', 10' 'and that Flow control valve 15 to the minimum value of e.g. 40% is set, the entire of the Cooling device delivered cooling capacity between 20% and 100% continuously by means of the flow control valve 15 can be set. Overheating of the compressors 10 ' 10 '' in the "cooling fluid cooling" mode, i.e. at open shut-off valve 16, is limited by the Adjustment range of the flow control valve 15 to Prevents a minimum value that is significantly greater than 0%, so that there is always a certain amount of refrigerant in the direction will flow to the compressors 10 ', 10' '.

    Die Kälteerzeugungseinrichtung gemäss beider vorbeschriebener Ausführungsformen der Erfindung stellt vorzugsweise eine separate Baueinheit mit integrierten Wärmetauscheinrichtungen 3, 4 und Zu- und Abflussanschlüssen für die anzuschliessenden Feuchtmittel- bzw. Kühlfluid-Umlaufsysteme dar.The refrigeration device according to both of the above Embodiments of the invention are preferably one separate unit with integrated heat exchange devices 3, 4 and inlet and outlet connections for the ends to be connected Dampening solution or cooling fluid circulation systems.

    Die Erfindung ermöglicht somit eine gezielte Anpassung der vom Verdichter 10 abgegebenen Kälteleistung auf die jeweiligen Betriebsverhältnisse. Dies gewährleistet eine Energiezufuhr zur zweiten Wärmetauscheinrichtung 4, die auf den Bedarf des Kühlfluid-Umlaufsystemes UII bei den verschiedenen Betriebsarten abgestimmt ist, so dass eine erhöhte Energiezufuhr zur Wärmetauscheinrichtung 4 vermieden wird. Das Kühlfluid-Umlaufsystem UII kann daher als geschlossenes System ausgebildet werden, da auf einen Energiepufferspeicher in Gestalt eines Kühlfluid-Vorratsbehälters verzichtet werden kann.The invention thus enables the cooling power output by the compressor 10 to be specifically adapted to the respective operating conditions. This ensures an energy supply to the second heat exchange device 4, which is matched to the requirements of the cooling fluid circulation system U II in the different operating modes, so that an increased energy supply to the heat exchange device 4 is avoided. The cooling fluid circulation system U II can therefore be designed as a closed system, since an energy buffer store in the form of a cooling fluid storage container can be dispensed with.

    Claims (9)

    1. An assembly for temperature control of a fountain fluid and/or selected rolls of a printing press, comprising
      a) a fountain fluid circulating system (UI) for supplying a fountain fluid from a fountain fluid reservoir to a fountain fluid application means,
      b) a cooling fluid circulating system (UII) for supplying a cooling fluid to a roller cooling means, in which to each of said circulating systems being assigned a heat exchanging means (3,4) for a heat exchange between the fountain fluid or cooling fluid circulating in the corresponding circulating system, and a refrigerant,
      c) a refrigeration means including a refrigerant circulating system for supplying a refrigerant to said heat exchanging means, said refrigeration means including a compressor means comprising at least one compressor, and
      d) a means of selectively operating one of said circulating systems for the fountain fluid or cooling fluid or both of said circulating systems,
      characterized in that said cooling fluid circulating system (UII) being designed as a closed-circuit system, and that said refrigeration means being switchable between a maximum and a minimum refrigeration output.
    2. The assembly as set forth in claim 1, characterized in that said compressor means comprises a power-switchable compressor (10) output of which being connected to the input thereof via a return conduit including a pressure sensing valve (6).
    3. The assembly as set forth in claim 2, characterized in that said compressor (10) being speed-switchable.
    4. The assembly as set forth in claim 1, characterized in that said compressor means comprising at least two compressors (10) connected in parallel to each other, each of which being switchable ON/OFF, the individual refrigeration outputs of said compressors being smaller than a desired total refrigeration output, and that a common output of said compressors being connected to a common input thereof via a return conduit including a pressure sensing valve (6).
    5. The assembly as set forth in claim 2, 3 or 4, characterized by a means (7) for injecting a quantity of liquid refrigerant into the output of said pressure sensing valve (6) in response to the temperature of the refrigerant at the input of said compressor(s) (10) for reducing the temperature of the refrigerant at the input of the compressor(s).
    6. The assembly as set forth in one of the preceding claims, characterized by a flow control valve (15) between the output of one of said heat exchanging means (3,4) and the input of said compressor(s) for setting and limiting the refrigeration output supplied to the corresponding heat exchanging means.
    7. The assembly as set forth in claim 6, characterized in that said flow control valve (15) being assigned to the heat exchanging means (4) of said cooling fluid circulating system (UII), that the supplied refrigeration output being adjustable by means of said flow control valve between 0% and 100%, and that in a common operation of said cooling fluid and fountain fluid circulating systems (UI,UII) the refrigeration output supplied to said heat exchanging means (4) being limited to a value ≤ two-thirds of the total refrigeration output.
    8. The assembly as set forth in claim 1, characterized in that a flow control valve (1) between the output of one of said heat exchanging means (3,4) and the input of said compressor means has a the control range limited between >> 0% and ≤ 100%, preferably between 40% and 100%.
    9. The assembly as set forth in claim 8, characterized in that at least two compressors (10',10'') connected in parallel to each other being provided, each of which being switchable ON/OFF, the individual refrigeration outputs of said compressors being smaller than a desired total refrigeration output.
    EP95117116A 1994-11-25 1995-10-31 Arrangement for tempering a dampening fluid and/or selected rollers of a printing machine Revoked EP0713767B1 (en)

    Priority Applications (1)

    Application Number Priority Date Filing Date Title
    DE29522412U DE29522412U1 (en) 1994-11-25 1995-10-31 Arrangement for tempering moisturiser and=or selected rolls of printing press - has combination of closed coolant fluid circulating system with freezing mixture switchable between max. and min. settings round at least one compressor

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE4442072 1994-11-25
    DE4442072A DE4442072B4 (en) 1994-11-25 1994-11-25 Arrangement for controlling the temperature of a dampening solution and a cooling fluid for selected rolls of a printing press

    Publications (2)

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    EP0713767A1 EP0713767A1 (en) 1996-05-29
    EP0713767B1 true EP0713767B1 (en) 1998-07-15

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    EP95117116A Revoked EP0713767B1 (en) 1994-11-25 1995-10-31 Arrangement for tempering a dampening fluid and/or selected rollers of a printing machine

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    EP (1) EP0713767B1 (en)
    DE (2) DE4442072B4 (en)

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    Also Published As

    Publication number Publication date
    EP0713767A1 (en) 1996-05-29
    DE4442072A1 (en) 1996-05-30
    DE4442072B4 (en) 2005-11-10
    DE59502819D1 (en) 1998-08-20
    US5657637A (en) 1997-08-19

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