EP1357338B1 - Tieftemperaturgefrieranlage, insbesondere für das Einfrieren, Tieffrieren und Lagern von Lebensmitteln - Google Patents

Tieftemperaturgefrieranlage, insbesondere für das Einfrieren, Tieffrieren und Lagern von Lebensmitteln Download PDF

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Publication number
EP1357338B1
EP1357338B1 EP03290827A EP03290827A EP1357338B1 EP 1357338 B1 EP1357338 B1 EP 1357338B1 EP 03290827 A EP03290827 A EP 03290827A EP 03290827 A EP03290827 A EP 03290827A EP 1357338 B1 EP1357338 B1 EP 1357338B1
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Prior art keywords
circuit
compressor
circuits
evaporator
frigorific
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Expired - Lifetime
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EP03290827A
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English (en)
French (fr)
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EP1357338A1 (de
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Jean-Paul Arpin
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    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators

Definitions

  • Low temperatures especially between -20 ° C and -60 ° C are particularly interesting in the field of food. Indeed, it has long been observed that maintaining products at such temperatures allows better preservation of the organoleptic qualities of these products. Such low temperatures are also useful, particularly in the field of chemistry or metallurgy. Although their use is still limited, it is due to the fact that refrigeration plants, which cover wide temperature ranges, that is to say ambient temperature at -60 ° C, remain expensive, complex and generally particularly bulky.
  • the first family of refrigeration plants consists of double-stage installations with an intermediate bottle. These installations, also called “booster”, consist of a low-pressure single-stage compressor and a single-stage high pressure compressor separate or double-stage compressors called “compound” screw or piston.
  • boost consist of a low-pressure single-stage compressor and a single-stage high pressure compressor separate or double-stage compressors called “compound” screw or piston.
  • the fluid mass flow rate displaced by the low pressure compressor is sub-cooled under the condensation pressure in an exchanger immersed in the liquid of the intermediate bottle. It is only the difference between the high pressure and low pressure masses which undergoes the relaxation of the high pressure at the intermediate pressure, hence its partial injection name.
  • the system operates at low suction pressures, the result is the use of a large volume of gas that requires particularly large compressors.
  • FIG. 1 Another family of refrigeration plants has therefore supplanted this first family of installations.
  • This is refrigeration installations called “cascade”.
  • the cascade system has two or more different refrigerants flowing in individual circuits. These individual circuits are arranged side by side so that the condenser installed in the low temperature circuit is cooled by the evaporative refrigerant of the other circuit where the temperature is higher.
  • Such an installation is more particularly described in US-A-2,434,221.
  • FIG. 1 it clearly appears a first circuit consisting of a compressor, represented in FIGS. 1, of a condenser, of a pressure reducer 6 and of an evaporator represented at 7.
  • Another object of the present invention is to provide a refrigeration plant whose design allows to obtain a reliable installation, high performance, small footprint with attractive yields.
  • the subject of the invention is a low temperature refrigeration plant, in particular for freezing, freezing and storage of products, in particular food products, according to claim 1.
  • the evaporator passes successively and automatically from a fluid supply by means of a first so-called conventional freezing or cooling circuit to a supply by means of a so-called deep freezing or low temperature subcooling circuit. Since the cooling capacity of phase 2 is lower than the cooling capacity of phase 1, the delta T, the temperature difference between the evaporation temperature and the air temperature at the inlet of the evaporator, is lowered. therefore clearly in phase 2, which ensures excellent performance of the installation. Moreover, such an installation is versatile since it can operate permanently in the form of a conventional cooling installation if the second circuit is never activated.
  • the two refrigerant circulation circuits which, in the examples shown, are compression-type circuits, each comprise, arranged in series, at least one compressor 2, a condenser 3, a pressure reducer 6 and an evaporator 1.
  • the pressure reducer 6, serving to supply the evaporator 1 could have been equivalently replaced by a pump or a thermosiphon system (flood).
  • these circuits are common over part of their length and are powered by the same refrigerant capable of supplying the first circuit and / or the second circuit.
  • These first and second circuits comprise, on their common section extending between the letters X and Z, taken in the flow direction of the fluid in Figure 1, at least the evaporator 1 for the production of cold. This evaporator 1 common to both circuits is thus able to be supplied with fluid by one or the other of the circuits as a function of the desired reference temperature.
  • these first and second refrigerant circuits are of the compression type and comprise at least one evaporator 1, a compressor 2, a condenser 3 and a pressure reducer 6 common to both circuits.
  • the second circuit is constituted between evaporator 1 and compressor 2, taken in the fluid flow direction, by a bypass of the first circuit.
  • the XZ section common to the two circuits implies that the fluid of the first and second circuits flows at the outlet of compressor 2 through a condenser 3 associated with a tank 4 and then through an economizer 5 or intermediate bottle before reaching the regulator 6 and then at the evaporator 1 for the production of cold.
  • the design of this connection differs from one circuit to another.
  • the second circuit is constituted between evaporator 1 and compressor 2 by a derivation of the first circuit, this branch corresponding to the ZY section.
  • This second circuit is equipped, on its bypass, with a piston compressor 7 connected at the output to an intermediate bottle 5, itself closably connected to the inlet of the suction channel of the compressor 2 common to the first and second circuits.
  • the compressor 2 common to the first and second circuits is constituted of a screw compressor and economizer 5.
  • the economizer 5 serving the first circuit and the intermediate bottle of the second circuit are preferably constituted by one and the same capacity.
  • the screw compressor 2 is also equipped with a medium pressure low pressure suction suction channel 10 'to which is connected the first economizer output circuit 5 (section WY').
  • This suction channel WY ' is connected to the economizer 5 so as to form in the first circuit a recirculation loop of at least a portion of the fluid from the condenser 3 towards the compressor 2.
  • these circuits are selectively activatable depending on the desired cooling temperature. The activation is preferably obtained by actuating at least one shutter member 8, 9 positioned on at least one of the circuits.
  • the refrigerant flows at the first circuit between the compressor 2, the condenser 3, the tank 4, the economizer 5, the expander 6 and the evaporator 1. At the evaporator outlet 1, the fluid returns directly to the inlet of the compressor 2 by borrowing the section ZY in Figure 1.
  • Part of the vapors contained in the economizer 5 is reintroduced into the circuit and feeds the channel 10 ' suction medium pressure compressor.
  • a part of the fluid of this first circuit is brought to recirculate in the compressor part 2, condenser 3, tank 4, economizer 5 thanks to the connection WY 'between economizer 5 and compressor 2.
  • This connection is of the shutter type and is equipped of a closure member 8.
  • This first circuit therefore corresponds to the circuit portions equipped with valves 8 of white color which are represented in the open position.
  • the compressor part 2 screw and bottle saver 5 serves high pressure booster stage whose low pressure part is no longer calculated for the entire deep freeze but only to ensure the subcooling products.
  • the valves 8, shown in white in Figure 1 are closed while the black valves 9 are open.
  • the fluid then follows a path in accordance with that shown with a solid train and a dotted line and a point in FIG. 1.
  • the fluid at the evaporator outlet 1 is passed through a piston compressor 7 after having passed through a valve 9 closed when the first circuit is activated and open when the second circuit is activated.
  • the fluid at the outlet of this piston compressor 7 is fed into an intermediate bottle. This fluid, at the outlet of the intermediate bottle, is returned to the inlet of the compressor 2 to screw.
  • This portion WY between the bottle 5 and the inlet of the compressor 2 is also equipped with a shutter member 9 to prevent a reflux of the first circuit in the second circuit when the first circuit is activated.
  • the fluid follows the same path as in the case of the first circuit, namely, it passes through the condenser 3 and then the tank 4 before to reach the intermediate or economizer bottle 5 then pass through the expander 6 and supply the evaporator 1.
  • a circuit portion WY in the case of the second circuit, brings the refrigerant back to the inlet of the screw compressor 2 at the level of the suction channel, while in the In the case of the first circuit, this same outlet of the bottle 5 or of the economiser 5 brings the fluid entering the compressor 2 via a so-called medium pressure suction channel 10 'which also equips the compressor 2 with a screw.
  • This circuit portion is represented in WY '.
  • the portion WY of the second circuit allows the screw compressor 2 to operate without economizer by becoming the high pressure compressor of a double-stage installation, the first stage is constituted by the compressor 7.
  • the portion WY 'of the first circuit allows a suction of gas contained in the economizer 5 and their injection into the compressor 2 at the channel 10 'suction medium pressure.
  • the refrigerant used common to the first and second circuits is R 404 A.
  • the physical properties of this fluid are described in particular in the book “Ashrae fundamentals Handbook” of 1997. This fluid allows operation with moderate pressures (18.5 bar absolute for a condensing temperature of -40 ° C), which is compatible with all refrigeration equipment standards.
  • the switching of the first circuit to the second circuit and vice versa takes place beyond a predetermined temperature measured and / or calculated.
  • the operating time of the first circuit may be taken into account, the activation of the second circuit occurring beyond a predetermined duration which is assumed to have attained an evaporation temperature of within a predetermined range.
  • FIGS. 2A to 2E show the refrigeration scheme for the execution of a refrigeration system of a long liner tuna boat.
  • Such boats go fishing for a period of about 15 days. From the port, the holds C1, C2 in which the fish will be stored are at room temperature. These shims must therefore reach a temperature close to -60 ° C.
  • each tunnel is loaded with fresh tuna, the fresh tuna being at room temperature.
  • the freezing step is started by activating the first circuit of the installation and then the freezing step by activating the second circuit of the installation. Once the freezing and freezing cycles are complete, the tuna is then transported to a storage hold at -60 ° C.
  • the two tunnels are for example designed to have a freezing capacity of 2 tons per cycle at -45 ° C heart.
  • the shims represented here in the form of cleat C1 and C2 wedge, have meanwhile volumes of the order of 100 m 3 at -60 ° C.
  • the C3 bait block has a volume of 10 m 3 at -20 ° C.
  • the outside temperature is 35 ° C and the external humidity is 80%.
  • the thermal insulation coefficient of the refrigerated rooms K is equal to 0.2 kcal / hr.
  • the installation is still equipped with two low-pressure piston-motor compressors (see FIG. 2c), for example of the Mycom brand, type F8WA.
  • the speed of rotation can be of the order of 1450 rpm, the operating speed of -65 ° C / -20 ° C with cooling capacities of 16.7 kW and an absorbed power of 16.5 kW.
  • the power regulation of such compressors can be 50, 75, 100% and the power of the electric drive motor is 22 kW.
  • the installation is still equipped with three motorcycle compressors 2 high pressure screw, one of them in relief or extra.
  • These motorcycle compressors 2 can be branded Bitzer Type OSN5361-K with a rotation speed of 2900 rpm.
  • These compressors 2 operate economizer on the first circuit, they have a cooling capacity of 34.7 kW and an absorbed power of 23.5 kW.
  • Each of the tunnels shown in T1, T2, is equipped with a ventilated battery or evaporator 1, supplied with direct expansion and with air defrosting. Electrical valves placed on the liquid and suction lines make it possible to automatically switch from the first conventional freezing or cooling circuit to the second intense subcooling circuit. In order to avoid pressure drops, the electric suction valves are motorized full-flow valves.
  • Each evaporator 1 is equipped with a liquid-vapor exchanger 18, so that the The temperature of the gases sucked by the low-pressure piston compressors shall be not less than -50 ° C.
  • Each of the shims is equipped with a ventilated battery 1 ', supplied with direct expansion and with electric defrosting. As a result, these batteries are each equipped with a safety thermostat which cuts off the supply of the resistors when the evaporator is at a high temperature. Electrical valves placed on the liquid and suction lines also make it possible to start lowering the temperature of the evaporators. shim at -25 ° C before the fishing trip using the screw compressor 2 with economizer 5, before using the low pressure circuit of the booster to reach the temperature of -60 ° C. As for the tunnels and for the same reasons, each evaporator of the holds C1, C2 is equipped with a liquid-vapor exchanger 18.
  • the C3 shim is equipped with a ventilated battery 1 'supplied with direct expansion and electric defrosting. This battery is of course only connected to the screw compressor with economizer circuit. Each of these stations is equipped with a thermostameter 12 (thermostat + temperature indication). Shims at -60 ° C are also equipped with a temperature recorder allowing control by the buyer of the cargo.
  • the engine room comprises a series of low pressure compressors corresponding to the piston compressors 7 of the general scheme.
  • These reciprocating compressors are provided with a liquid-stripping bottle 14 with a liquid subcooler coil and are each equipped with a direct-expansion oil cooler 15, an oil level controller 16 in the crankcase, the possible surplus of oil in the crankcase compressors will be injected at the suction of the priority screw compressor, an oil separator 17.
  • compressors 7 operate in cooperation with an economizer intermediate bottle 5.
  • the latter is provided with a cooling pot for the gases discharged by the low-pressure compressors 7, a high-pressure liquid supply with a liquid level controlled by a switch 19.
  • a second float switch 20 ensures the safety of the compressors when the level is too high.
  • This economizer intermediate bottle 5 is again equipped with a constant pressure valve 21 in order to limit the pressure to -20 ° C. in the present case. We also find the classic elements such as safety valve, liquid indicator ...
  • the installation comprises three motorcycles 2 identical screw compressors that can work both during the conventional freezing regime adopted in the first phase, ie + 40 ° C to -34 ° C with economizer, or single stage without economizer at -20 ° C -40 ° C when operating the high pressure stage of the booster, during phase 2 of tunnels, phase of intense subcooling or when cooling chocks to -60 ° C is necessary.
  • This unit is equipped with a common oil separator 23, which facilitates the automatic oil returns and a single oil cooler 24.
  • the compressors are also equipped with a 25 anti-liquid bottle with coil subcooler liquid.
  • An oil decocenter 26 placed on the general discharge allows an automatic recovery of the oil dissolved in the freon of the intermediate bottle by means of an ejector system 27.
  • the installation also comprises a condenser 3 of the multitubular condenser type forming a reservoir. Condensation of high pressure discharge gases is provided by this seawater condenser. This condenser acts as a reservoir and also allows the thermosiphon supply of the oil cooler.
  • the refrigeration system allows the simultaneous operation of all stations in all cases, such as tuna storage chutes at -60 ° C, a bait wedge in service, a tunnel N ° 1 in phase intense subcooling (Phase 2) and tunnel No. 2 in the conventional freezing phase (Phase 1).
  • valves 32 and 33 can also operate in a high-pressure stage of the booster system, electric valve 31 (corresponding to the member 9 of FIG. 1) open, valves 32 and 33 (corresponding to the members 8 of Figure 1) closed, that in system with economizer (circuit No. 1), electric valves 32 and 33 (corresponding to the members 8 of Figure 1) open, electric valve 31 (corresponding to the member 9 of Figure 1) closed.

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

Claims (5)

  1. Tieftemperaturkälteanlage, insbesondere für das Einfrieren, Tieffrieren und Lagern von insbesondere Lebensmitteln, die oben genannte Anlage hat wenigstens zwei Kühlkreisläufe um die Zirkulation des Kältemittels zu gewährleisten, wobei der erste, sog. erster Kreislauf, als erster Kühlvorgang fungiert, um eine Temperatur vorzugsweise in der Nähe von -18°C zu erreichen, der weitere, sog. zweiter Kreislauf, dient zur Unterkühlung vorzugsweise von -18°C bis ungefähr -45°C, jeder Kühlkreislauf des Verdichtungstyps beinhaltet, in Reihe geschaltet, wenigstens einen Verdichter (2), einen Kondensator (3) und einen Verdampfer (1) durch die das Kältemittel durchfließt, wobei der Verdampfer (1) durch ein Expansionsventil (6), durch eine Pumpe oder durch Schwerkraft (Thermosiphon) versorgt wird, wobei diese Kühlkreisläufe eine gemeinsame Strecke auf einem Teil (XZ) ihrer Gesamtlänge haben und werden mit demselben Kältemittel versorgt, der abwechselnd in dem einen oder in dem anderen der oben genannten Kreisläufe, wobei diese Kreisläufe auf ihrer gemeinsamen Strecke (XZ) wenigstens einen Kondensator (3), vorzugsweise ein Expansionsventil (6), und den zur Kälteerzeugung dienenden Verdampfer (1) haben, dieser Verdampfer (1) wird durch den einen oder anderen oben genannten Kreisläufe mit Flüssigkeit versorgt, je nach gewünschter Abkühltemperatur, charakterisiert bei der Tatsache, dass der erste und der zweite Kreislauf insbesondere einen gemeinsamen Kompressor beinhalten (2), der von einem Schraubenverdichter und einem Economiser (5) zusammengesetzt wird, wobei dieser Schraubenverdichter (2) an der Saugseite mit einem absperrbaren Kanal (WY') bei mittlerem Druck ausgestattet ist, der bei dem aktivierten Zustand des zweiten Kreislaufes abgesperrt ist, dieser Saugkanal (WY') ist mit dem Economiser (5) verbunden, so dass in dem ersten Kreislauf einen Rückfluss wenigstens eines Teiles der von dem Kondensator (3) kommenden Flüssigkeit in Richtung des Verdichters (2), und in dem der zweite Kreislauf, zwischen dem Verdampfer (1) und dem Verdichter (2), in Fliessrichtung der Flüssigkeit betrachtet, durch eine Abzweigung des ersten Kreislaufes dargestellt wird, dieser zweiten Kreislauf ist, auf seiner Abzweigung, mit einem Kolbenverdichter (7) ausgestattet, dessen Druckseite an einem Zwischenbehälter (5) angeschlossen ist, der auf absperrbare Weise an dem Eintritt einer Saugleitung (WY) des Verdichters angeschlossen ist, die dem ersten und dem zweiten Kreislauf gemeinsam ist.
  2. Kälteanlage gemäß Forderung Nr. 1,
    charakterisiert bei der Tatsache, dass der erste und der zweite Kreislauf je nach gewünschter Abkühltemperatur selektiv aktiviert werden können, wobei die Aktivierung vorzugsweise durch Betätigung wenigstens eines in wenigstens einem Kreislauf sich befindenden Absperrteiles (8, 9) erfolgt.
  3. Kälteanlage gemäß einer der Forderungen 1 und 2,
    charakterisiert bei der Tatsache, dass der Economiser (5) und der Zwischenbehälter (5) des zweiten Kreislaufes aus einer und selben Kapazität bestehen.
  4. Kälteanlage gemäß einer der Forderungen 1 bis 3,
    charakterisiert bei der Tatsache, dass der erste Kreislauf in dem Bereich zwischen dem Verdampfer (1) und dem Verdichter (2), flussabwärts der Abzweigung, die den zweiten Kreislauf darstellen soll, mit einem Absperrteil (8) ausgestattet ist, so ein Ventil, das in Sperrrichtung bei Überschreitung einer vorher bestimmten gemessenen und/oder insbesondere in Abhängigkeit der Betriebszeit des ersten Kreislaufes berechneten Temperatur betätigt wird.
  5. Kälteanlage gemäß einer der Forderungen 1 bis 4,
    charakterisiert bei der Tatsache, dass das dem ersten und dem zweiten Kreislauf gemeinsame benutzte Kältemittel R 404A ist.
EP03290827A 2002-04-03 2003-04-02 Tieftemperaturgefrieranlage, insbesondere für das Einfrieren, Tieffrieren und Lagern von Lebensmitteln Expired - Lifetime EP1357338B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0204164A FR2838180B1 (fr) 2002-04-03 2002-04-03 Installations frigorifiques basse temperature de surgelation et de stockage
FR0204164 2002-04-03

Publications (2)

Publication Number Publication Date
EP1357338A1 EP1357338A1 (de) 2003-10-29
EP1357338B1 true EP1357338B1 (de) 2006-12-27

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EP03290827A Expired - Lifetime EP1357338B1 (de) 2002-04-03 2003-04-02 Tieftemperaturgefrieranlage, insbesondere für das Einfrieren, Tieffrieren und Lagern von Lebensmitteln

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EP (1) EP1357338B1 (de)
AT (1) ATE349660T1 (de)
DE (1) DE60310636D1 (de)
ES (1) ES2279076T3 (de)
FR (1) FR2838180B1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005009173A1 (de) 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
CN101413738A (zh) * 2007-10-17 2009-04-22 开利公司 一种中低温集成式冷藏/冷冻系统
CN114674090A (zh) * 2022-04-12 2022-06-28 新科环保科技有限公司 一种低环境温度采暖空调系统

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US2024323A (en) * 1932-07-01 1935-12-17 Baldwin Southwark Corp Apparatus for compressing gaseous fluids
US2434221A (en) * 1943-07-02 1948-01-06 Honeywell Regulator Co Control means for plural stage refrigerating systems
CH234315A (de) * 1943-07-13 1944-09-30 Escher Wyss Maschf Ag Wärmepumpe.
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JPS6054025B2 (ja) * 1983-08-04 1985-11-28 日新興業株式会社 食品の凍結方法並びに其の装置
US4594858A (en) * 1984-01-11 1986-06-17 Copeland Corporation Highly efficient flexible two-stage refrigeration system
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US5729993A (en) * 1996-04-16 1998-03-24 Apd Cryogenics Inc. Precooled vapor-liquid refrigeration cycle
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DE29906359U1 (de) * 1999-04-09 1999-08-05 Fuhrmann & Schreiner GmbH, 08491 Netzschkau Anlage zur Erzeugung von Kälte auf einem hohen und einem niedrigen Temperaturniveau

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FR2838180A1 (fr) 2003-10-10
FR2838180B1 (fr) 2006-10-27
ES2279076T3 (es) 2007-08-16
DE60310636D1 (de) 2007-02-08
ATE349660T1 (de) 2007-01-15
EP1357338A1 (de) 2003-10-29

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