EP3479903B1 - Centrifugeuse - Google Patents

Centrifugeuse Download PDF

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Publication number
EP3479903B1
EP3479903B1 EP17200209.9A EP17200209A EP3479903B1 EP 3479903 B1 EP3479903 B1 EP 3479903B1 EP 17200209 A EP17200209 A EP 17200209A EP 3479903 B1 EP3479903 B1 EP 3479903B1
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EP
European Patent Office
Prior art keywords
cooling circuit
centrifuge
circuit
primary
refrigeration circuit
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EP17200209.9A
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German (de)
English (en)
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EP3479903A1 (fr
Inventor
Christian Riese
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Sigma Laborzentrifugen GmbH
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Sigma Laborzentrifugen GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B15/00—Other accessories for centrifuges
    • B04B15/02—Other accessories for centrifuges for cooling, heating, or heat insulating
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation

Definitions

  • the invention relates to a centrifuge, in particular a laboratory centrifuge.
  • Centrifuges of the type presented here are used, for example, in biotechnology, the pharmaceutical industry, medical technology and environmental analysis.
  • Such a centrifuge is used to centrifuge a product, in particular a container or vessel with a sample or substance arranged therein, or a large number of such products at speeds which can be more than 3,000 rpm, for example more than 15,000 rpm.
  • accelerations acting on the product are to be generated which, for example, can be more than 15,000 x g (in particular more than 16,000 x g, more than 20,000 x g up to more than 60,000 x g).
  • Centrifugation is intended to break down a mixture of substances formed by the sample or the substance into components of different densities. Depending on the chemical and / or physical properties of the substance mixture, specific control of the pressure and / or temperature conditions can also take place during centrifugation. To name just a few examples, the use of a laboratory centrifuge in connection with a polymerase chain reaction (PCR), a determination of the hematocrit, cytological examinations or the centrifugation of microtiter, blood bags, petroleum vessels or blood vessels, etc. the like.
  • PCR polymerase chain reaction
  • the centrifuges generate very high kinetic energies during operation, which are generated in the immediate vicinity of the refrigeration circuit and can destroy the inner workings of the centrifuge including the refrigeration circuit in the event of a crash of the centrifuge.
  • the coolant can escape and catch fire, and in the event of a crash a spark causing the fire can also occur.
  • special requirements regarding the flammability of the refrigerant must be observed.
  • a refrigerant that ensures the special requirements in terms of flammability must also be powerful enough to ensure the cooling required when the centrifuge is in operation.
  • the pamphlet EP 3 015 791 A1 suggests using a CO 2 (R744) -based refrigerant or at least a hydrocarbon refrigerant in a centrifuge instead of a refrigerant R-134a, with mixtures also being used. This is intended to achieve a higher degree of efficiency of the refrigeration circuit, so that the refrigeration circuit can have a lower power consumption or, with the same power consumption, can bring about a stronger cooling effect.
  • Possible refrigerants are, for example, propane (R-290), propene (R-1270), butane (R-600) and isobutane (R-600a), which can be easily recycled since they are naturally occurring Substances that do not lead to the undesirable greenhouse effect when the refrigerant is released.
  • EP 3 015 791 A1 further suggests arranging an injection system in the evaporator of the refrigeration circuit, the pressure in the compressor being limited by controlling the injection. It is also proposed that the refrigeration circuit have at least one bypass to bypass an internal heat exchanger. In contrast to a refrigeration circuit in which a refrigerant R-134a is used, a greater pressure difference is required here in the refrigeration circuit between the low-pressure side and the high-pressure side, which in EP 3 015 791 A1 with a pressure of 1 bar on the low pressure side and 8 bar on the high pressure side. As a result, a changed safety design of the centrifuge, which must be designed for three times the working pressure, and / or a restriction of the compressor pressure is required.
  • a hot gas bypass must also ensure that warm refrigerant is fed to the evaporator, so that ice formation, for example at the triple point of CO 2 in the evaporator, must be avoided.
  • the compressor can be regulated or the injection system mentioned can be controlled.
  • the pamphlet DE 10 2014 110 467 A1 suggests that a centrifuge not just use a refrigeration cycle. Rather, the cold should be generated by a primary cooling circuit, which is then thermally coupled via a heat exchanger to a secondary cooling circuit in which a refrigerant is circulated by a pump.
  • the secondary cooling circuit arranged downstream of the primary cooling circuit thus only serves to transport the cold that has been generated by the primary cooling circuit from the heat exchanger to the centrifuge chamber.
  • a conventional flammable refrigerant can then be used in the primary refrigeration circuit, which under certain circumstances has low costs, but can have a large specific enthalpy of vaporization.
  • a non-flammable heat transfer medium such as, for example, cooling water with additives (for example salt or alcohol) that lower the freezing point
  • a non-flammable heat transfer medium such as, for example, cooling water with additives (for example salt or alcohol) that lower the freezing point
  • the primary cooling circuit and the secondary cooling circuit are then separated from one another by a safety wall, the combustible primary cooling circuit can be protected by the safety wall in the event of a crash, while the crash can at most have effects on the non-combustible secondary cooling circuit.
  • the primary cooling circuit can extend below the secondary cooling circuit or a safety boiler or laterally offset to this in the housing of the centrifuge.
  • a safety vessel can be fastened to the housing of the centrifuge via a clamp connection in such a way that in the event of a crash a relative movement of the safety vessel with respect to the housing of the centrifuge is possible. It is also proposed that lines of the primary cooling circuit are made from a mechanically stronger material than lines of the secondary cooling circuit, it also being possible for lines of the secondary cooling circuit to be specifically equipped with predetermined breaking points.
  • the mechanical connection between the secondary cooling circuit and the primary cooling circuit can be separated due to the weaker design of the lines of the secondary cooling circuit, which is intended to prevent this that the energy as a result of the crash via the lines of the secondary cooling circuit to the primary cooling circuit is transferred, which could lead to damage, leakage of the refrigerant of the primary refrigeration circuit and thus a fire.
  • DE 10 2014 110 467 A1 discloses a laboratory centrifuge with a primary refrigeration circuit which has a compressor, a condenser, a fan, a filter dryer and a heat exchanger with an integrated evaporator.
  • a flammable refrigerant is used in the primary refrigeration circuit.
  • the cold generated in the primary cooling circuit is transferred to a secondary cooling circuit in which a non-combustible heat transfer medium is circulated by means of a pump.
  • a cooling coil of the secondary cooling circuit extends for cooling a safety boiler in secondary pipelines around the safety boiler.
  • a conventional flammable refrigerant can thus be used in the primary refrigeration circuit, which can have a large specific enthalpy of vaporization at comparatively low procurement costs.
  • the use of a non-combustible heat transfer medium in the secondary circuit can reduce the occurrence of a fire in the event of a rotor crash and the breakdown of the safety boiler.
  • EP 2 910 870 A1 discloses a general freezing or refrigeration device which has a primary refrigeration circuit with a compressor, a condenser and a throttle and a first evaporator, and a secondary refrigeration circuit with a compressor, a condenser, a consumer, a throttle and a second evaporator .
  • a cascade condenser has the evaporator of the primary refrigeration circuit and the condenser of the primary refrigeration circuit, forming a heat exchanger between the refrigerants of the two refrigeration circuits. The generated cold is released to an object such as a freezer or cooling room via the evaporator of the secondary cooling circuit.
  • the refrigeration device should be designed and operated in such a way that there is the possibility of freezing in the area of the evaporator of the secondary refrigeration circuit, which is why a defrosting function must be necessary. Furthermore, the dimensioning of the refrigeration device is carried out in such a way that when it is operated in an environment with a temperature that is higher than the critical temperature of the refrigerant, the refrigerant in the secondary refrigeration circuit passes through the Ambient air is heated, so that a gaseous phase results when the circulation of the refrigerant is stopped in the secondary refrigeration circuit, whereby a pressure increase in the secondary refrigeration circuit is established.
  • EP 2 910 870 A1 is dedicated to the problem of at least reducing such a pressure increase in the secondary refrigeration circuit when the circulation of the refrigerant in the secondary refrigeration circuit is interrupted.
  • EP 2 910 970 A1 proposes for this purpose to provide an expansion tank in the secondary refrigeration circuit, which ensures the interruption of the circulation of the refrigerant in the secondary refrigeration circuit in order to limit the pressure increase.
  • the expansion tank is arranged below the cascade condenser. If the circulation of the refrigerant in the secondary refrigeration circuit is stopped, the condensed and liquefied refrigerant in the primary refrigeration circuit is quickly collected in the expansion tank, whereby a pressure increase in the secondary refrigeration circuit can be avoided.
  • the present description speaks of “generation of cold” and “transfer of cold”, although if the physical approach is correct, only a temperature sink can be generated to which heat is then transferred.
  • the centrifuge according to the invention which is in particular a laboratory centrifuge, has a housing and a centrifuge chamber arranged in the housing.
  • a rotatably mounted rotor (and driven by a motor) can be arranged in the centrifuge chamber.
  • the centrifuge chamber usually surrounds a safety element at least in a partial circumferential area, which can also be a safety vessel extending completely in the circumferential direction (for example single-walled or double-walled).
  • the centrifuge has both a primary refrigeration circuit and a secondary refrigeration circuit.
  • the secondary cooling circuit is thermally coupled to the primary cooling circuit (in particular via a heat exchanger), so that cold generated in the primary cooling circuit can be transferred to the secondary cooling circuit.
  • the secondary refrigeration circuit is thermally coupled to the centrifuge chamber so that both the cold generated in the primary refrigeration circuit and transferred via the heat exchanger and the cold generated in the secondary refrigeration circuit can be cumulatively transferred to the centrifuge chamber.
  • the centrifuge has a control unit.
  • the control unit has control logic that controls the primary refrigeration circuit and the secondary refrigeration circuit. The control is carried out in such a way that while the centrifuge is operating with a rotation of the rotor, cold is generated by means of the primary cooling circuit and / or the primary cooling circuit and the secondary cooling circuit are operated simultaneously.
  • the two refrigeration circuits can be individually adapted (for example with regard to the changes in state, the pressure changes and the enthalpy difference and / or to the refrigerant used in the refrigeration circuits), which results in increased efficiency and / or an improved ratio with regard to the structural volume and the Costs compared to the refrigeration capacity that can be generated.
  • the configuration according to the invention enables any choice of refrigerants in the two refrigeration circuits, which means that the scope for design in terms of efficiency, environmental compatibility, security against the occurrence of a fire and / or costs can be expanded. Under certain circumstances, the configuration according to the invention also enables new control options for controlling the temperature in the centrifuge chamber, depending on the configuration and coordination of the control and operation of the two refrigeration circuits.
  • a “refrigeration cycle” is understood to mean a cycle with a refrigerant, in which cold is generated using electrical power. It is possible here that a compression of the refrigerant and / or a change in the aggregate state of the refrigerant is generated in a refrigeration circuit, the refrigeration circuit uses a magnetocaloric effect, the refrigeration circuit has electrical Peltier cooling, the refrigeration circuit generates cold using a vortex tube or in in which the refrigeration cycle generates cold using an absorption refrigeration cycle or a compression refrigeration cycle.
  • a refrigeration circuit does not include a "cooling circuit" in which only a refrigerant is conveyed, in particular by means of a pump, and by means of which a transport of cold from a transfer location (such as a heat exchanger, in which a transfer of cold that has been generated externally by the cooling circuit takes place to the refrigerant of the cooling circuit) to the centrifuge chamber.
  • a transfer location such as a heat exchanger, in which a transfer of cold that has been generated externally by the cooling circuit takes place to the refrigerant of the cooling circuit
  • control unit in the sense of the invention can be a control unit in the form of a singular structural unit, several interconnected or flanged control unit modules or several interconnected or networked control subunits.
  • the primary refrigeration circuit and / or the secondary refrigeration circuit have a suggestion of the invention a compressor, a condenser, an expansion device and an evaporator.
  • This choice of the design of the refrigeration circuit has proven to be advantageous in terms of installation space, costs, energy efficiency and the refrigerants that can be used.
  • the primary refrigeration circuit can be designed as a high-pressure circuit, while the secondary refrigeration circuit can be designed as a low-pressure circuit. This enables the different design of the different refrigeration circuits with a potential for optimizing the generation of the required cold.
  • a further proposal of the invention in the centrifuge can also A flammable refrigerant (in particular a flame-retardant refrigerant, a flammable refrigerant or a highly flammable refrigerant) can be used, especially if this is (only) used for the primary cooling circuit.
  • This proposal is based on the knowledge that the lines and components of the primary refrigeration circuit u. U. can also be arranged outside a safety vessel of the centrifuge, so that even in the event of a centrifuge crash, the flammable refrigerant in the primary refrigeration circuit cannot escape from the lines and / or cannot be ignited.
  • the invention further proposes that a non-flammable or hardly flammable refrigerant is used in the secondary refrigeration circuit.
  • This configuration takes into account the fact that u. U. the refrigerant of the secondary refrigeration circuit is also arranged in the area of the safety boiler of the centrifuge or even inside the same, so that it is basically exposed to the risk of a fire in the event of a centrifuge crash.
  • the non-flammable or hardly flammable refrigerant By using the non-flammable or hardly flammable refrigerant, however, the fundamental risk of a fire occurring can at least be reduced.
  • the invention proposes that the primary refrigeration circuit has a flammable refrigerant (in particular a hardly inflammable refrigerant, a flammable refrigerant or a highly flammable refrigerant), while the secondary refrigeration circuit has a non-flammable or hardly inflammable refrigerant. Also it is possible that the primary refrigeration circuit has a non-flammable or hardly inflammable refrigerant and the secondary refrigeration circuit has a non-flammable or hardly inflammable refrigerant. In these cases, the two refrigeration circuits can have the same or different refrigerants.
  • a "non-flammable refrigerant” is a refrigerant which, according to SN DIN EN 378-1, has no flame spread and is assigned to group A1 (low toxicity) or B1 (higher toxicity). This requires that when the test is carried out in air at 60 ° C and at a pressure of 1.013 bar, this refrigerant does not spread flame if it is a single-substance refrigerant.
  • Flame-resistant refrigerants are category A2L refrigerants in accordance with ISO 817 (Section 6.1.3.3) which, when tested at 60 ° C and a pressure of 1.013 bar, lead to flame spread, a lower explosion limit (LFL)> 3.5 vol. -%, have a heat of combustion that is ⁇ 19,000 kJ / kg, and have a maximum flame propagation speed that is ⁇ 10 cm / s when tested at 23 ° C and a pressure of 1.013 bar.
  • a refrigerant R1234yf is preferably used as the flame-retardant refrigerant in this A2L category.
  • “Flammable refrigerants” are assigned to groups A2 (low toxicity) or B2 (higher toxicity) of the SN DIN EN 378-1 standard and, for a single-substance refrigerant and for a mixed refrigerant, meet the conditions that a When tested at 60 ° C and a pressure of 1.013 bar, the flame spreads, the lower explosion limit (LFL) being> 3.5% by volume and the heat of combustion being ⁇ 19,000 kJ / kg.
  • refrigerants are regarded as "highly flammable refrigerants" which, according to the SN DIN EN 378-1 standard, are classified in groups A3 (low toxicity) and B3 (higher toxicity) get ranked. Single-substance refrigerants and mixed refrigerant use are assigned to these groups if a test at 60 ° C and a pressure of 1.013 bar results in flame spread and the lower explosion limit (LFL) ⁇ 3.5% by volume or the heat of combustion is ⁇ 19,000 kJ / kg.
  • LFL lower explosion limit
  • single-substance or mixture refrigerants are regarded as "flammable refrigerants" if they are assigned to one of the flammability classes A2, B2, A2L, B2L, A3, B3 according to SN DIN EN 378-1 and are hardly inflammable , are flammable or highly flammable, while the single-substance or mixture refrigerants, which are assigned to groups A1 or B1 and are not flammable, are referred to as “non-flammable refrigerants” .
  • a heat exchanger can be arranged in the area of the condenser of the primary refrigeration circuit and / or in the transfer area between the two refrigeration circuits, i.e. the evaporator of the primary refrigeration circuit and the condenser of the secondary refrigeration circuit.
  • heat exchangers of any type can be used within the scope of the invention.
  • a plate heat exchanger or a tube bundle heat exchanger can be used.
  • a microchannel heat exchanger is used for a heat exchanger, in particular for the heat exchanger in the area of the condenser of the primary refrigeration circuit.
  • This is understood to mean a heat exchanger in which a body or block (for example made of metal, in particular aluminum, consisting of one or more parts) has a plurality of small channels with a transverse extension of the channels or a diameter of the same of, for example, less than 2 mm or 1 mm from the Refrigerant is flowed through, with which a high degree of efficiency, a small filling volume of the refrigerant, a low weight and a compact design can be achieved.
  • the refrigerant is therefore not routed in pipes here.
  • the channels of bores in the body or block are formed in the microchannel heat exchanger or the body or block is formed from several parts, for example welded or soldered together, which can have grooves and delimit the channels when connected to one another.
  • ambient air can then be conducted past the body or block directly and / or through cooling fins attached thereto by means of a fan.
  • heat exchangers of this type are distributed, for example, by Danfoss or on the Internet site www.kka-online.info/ obviously/kka_Neue_Trends_bei_Komplettverfluess, toleratessaetzen_1406699 are described.
  • the components of the refrigeration circuits and the heat exchangers used can be arranged at any point in the centrifuge.
  • the primary refrigeration circuit, a heat exchanger which couples the primary refrigeration circuit with the secondary refrigeration circuit, and at least part of the secondary refrigeration circuit are arranged on a side of a safety element, in particular a safety boiler, facing away from the centrifuge chamber.
  • the rotor of the centrifuge on the one hand and the primary refrigeration circuit on the other hand are on different sides of the safety element, which means for the design of the safety element as a safety boiler that the rotor is located inside the safety boiler, while the primary refrigeration circuit is arranged outside the safety boiler is.
  • the housing of the centrifuge can have an approximately rectangular horizontal section.
  • the security element is a security kettle with a circular horizontal section.
  • an intermediate space between a corner of the housing and the safety boiler with a circular horizontal section there is an intermediate space in which, within the scope of the invention, a compressor of the primary refrigeration circuit can be arranged particularly advantageously.
  • a corresponding other gap results between another corner of the housing and the safety boiler.
  • the compressor of the secondary refrigeration circuit can then be arranged in this other intermediate space.
  • the heat exchanger which thermally couples the primary refrigeration circuit and the secondary refrigeration circuit to one another, can in this case be arranged in an intermediate space which is between a Side wall of the housing and the safety boiler results, which is preferably an intermediate space between the compressor of the primary refrigeration circuit, the compressor of the secondary refrigeration circuit, the side wall of the housing and the safety boiler.
  • the line connections (in particular from and to the heat exchanger) in the two refrigeration circuits can be kept relatively short as a result.
  • the heat exchanger protected by the safety boiler
  • control logic of the control unit is designed in such a way that a compressor of the primary refrigeration circuit and / or a compressor of the secondary refrigeration circuit are / is controlled in ON operating states and OFF operating states.
  • non-speed-regulated compressors can also be used, which thus only have an active and an inactive operating state.
  • the regulation of the compression output and thus the cold generated can be controlled via the duration of the ON operating states and the ratio of the duration of the ON operating states to the duration of the OFF operating states taking place in between.
  • the two compressors of the refrigeration circuits can be switched to the ON operating state at the same time. If, on the other hand, an undesired increased peak current due to the simultaneous switching on of the compressors is to be avoided, the compressor of the primary refrigeration circuit and the compressor of the secondary refrigeration circuit are controlled to the ON operating state with a time delay for a proposal by the inventors. In contrast, the change to the OFF operating state can take place simultaneously or also with a time offset.
  • control logic of the control unit of the centrifuge is designed in such a way that the primary refrigeration circuit is independent of a required refrigeration capacity for cooling the centrifuge chamber (and thus independent of the deviation of the actual temperature inside the centrifuge chamber from the setpoint temperature) is operated in an ON operating state.
  • the temperature fluctuations in the evaporator of the primary refrigeration circuit are not as pronounced as would be the case for an alternating change between an ON operating state and an OFF operating state in the primary refrigeration circuit.
  • only the secondary refrigeration circuit is switched back and forth between an ON operating state and an OFF operating state, depending on the refrigeration capacity required to cool the centrifuge chamber.
  • the background to this embodiment is that the possible amount of heat to be dissipated from the primary refrigeration circuit depends on the condensation temperature, this being increased according to the invention, which can result in a reduction in output. A more precise regulation of the temperature in the centrifuge chamber can possibly take place by means of such a different control of the two refrigeration circuits.
  • Fig. 1 shows a centrifuge 1 according to the prior art.
  • the centrifuge 1 has a refrigeration system 2.
  • the refrigeration system 2 here has a single refrigeration circuit 3.
  • a compressor 5 which is driven by a motor 4 operated with electrical energy, a liquefier or condenser 6, an expansion element 7 (in particular an expansion valve or a throttle) and an evaporator 8 in this order via lines 9a, 9b , 9c, 9d connected to one another in a closed circuit.
  • Fig. 1 the circled numbers identify the states (I), (II), (III) and (IV) of the coolant used in the refrigeration circuit 3.
  • the condenser 6 with the lines 9a, 9b forms a high-pressure circuit part 10
  • the evaporator 8 with the lines 9c, 9d forms a low-pressure circuit part 11.
  • the cold generated in the cooling circuit 3 is transferred to the centrifuge chamber 12, which is only shown schematically here.
  • An energetic exchange of the refrigeration circuit 3 takes place via the provision of cold for the centrifuge chamber 12 by the evaporator 8, on the one hand, by applying electrical power to the motor 4 and compressing the refrigerant in the area of the compressor 5.
  • a heat exchange with the ambient air whereby a fan can be driven with electrical power.
  • the condenser 6 thus forms a heat exchanger 13.
  • Fig. 2 shows the counter-clockwise cycle, like this with steps a) to d) and the changes of state (I) - (II), (II) - (III), (III) - (IV) and (IV) - (I) in the introductory part of the description under the heading "Technical Field of the Invention" has been described.
  • Fig. 3 schematically shows a centrifuge 1 according to the invention, in which the refrigeration system 2 has a primary refrigeration circuit 14 and a secondary refrigeration circuit 15.
  • the primary refrigeration circuit 14 is coupled to the secondary refrigeration circuit 15 via a heat exchanger 16.
  • the secondary refrigeration circuit 15 basically corresponds to the refrigeration circuit 3 according to FIG Fig. 1 , this also having corresponding states (I), (II), (III) and (IV).
  • components which are contained in the refrigeration circuit 3 are identified by the same reference symbols, and these are referred to below with the same designations.
  • the evaporator 6 communicates differently in the secondary refrigeration circuit 15 Fig. 1 not with the ambient air. Rather, the evaporator 6 is part of the heat exchanger 16.
  • a compressor 17 which is driven by a motor 18 driven by means of electrical energy
  • a condenser 19 which is designed here as a heat exchanger 20 and is thermally coupled to the ambient air via a fan
  • an expansion element 21 and a Evaporator 22 which together with condenser 6 forms heat exchanger 16, connected to one another in a closed circuit via lines 23a, 23b, 23c, 23d.
  • the states (V), (VI), (VII) and (VIII) identify the states of the refrigerant between the evaporator 22 and the compressor 17 (state V), between the compressor 17 and the condenser 19 ( State VI), between the condenser 19 and the expansion element 21 (state VII) and between the expansion element 21 and the evaporator 22 (state VIII).
  • the refrigerant also circulates between a high-pressure circuit part and a low-pressure circuit part, as has been explained above for the refrigeration circuit 3.
  • the primary refrigeration circuit 14 forms a high-pressure circuit 24, while the secondary refrigeration circuit 15 forms a low-pressure circuit 25.
  • An energetic exchange of the primary refrigeration circuit 14 takes place via the provision of cold for the heat exchanger 16 by the evaporator 22, on the one hand, by applying electrical power to the motor 18 and compressing the refrigerant in the area of the compressor 17.
  • An energetic exchange of the secondary refrigeration circuit 15 takes place via the provision of cold by the heat exchanger 16 to the condenser on the one hand by applying electrical power to the motor 4 and compressing the refrigerant in the area of the compressor 5, on the other hand in the area of the evaporator 8 cooling of the centrifuge chamber 12.
  • the refrigeration circuits 14, 15 can be operated simultaneously. On the basis of the introduction of electrical energy via the motor 18 and the compressor 17 driven by it, cold is generated in the primary refrigeration circuit 14, which is transferred via the heat exchanger 16 to the secondary refrigeration circuit 15 in that the evaporator 22 releases cold to the condenser 6 and in that the transferred cold is used in the condenser 6 to liquefy the refrigerant of the secondary refrigeration circuit 15.
  • additional refrigeration is generated with the introduction of electrical energy via the motor 4 and the compressor 5 driven by it. The refrigeration generated in this way by the primary refrigeration circuit 14 and the secondary refrigeration circuit 15 is then accumulated by the evaporator 8 of the secondary refrigeration circuit 15 are transferred to the centrifuge chamber 12. It is possible that the mass flows, the refrigerants and / or the pressures in the two refrigeration circuits 14, 15 are different.
  • Fig. 4 shows the two counterclockwise cycle processes of the two refrigeration circuits 14, 15 in a diagram in which the logarithm of the pressure p is shown over the enthalpy h.
  • the coupling of the two refrigeration circuits 14, 15 via the heat exchanger 16 is based on the principle that the coolant in the secondary refrigeration circuit 15 can be cooled more deeply as a result of the supply of cold via the heat exchanger 16 from the primary refrigeration circuit 14 than this This is the case when the coolant cooling the centrifuge chamber 12 is thermally coupled to the environment via a condenser 6 in the form of a heat exchanger 13.
  • the secondary cooling circuit 15 absorbs heat from the centrifuge chamber 12 and transfers it in the heat exchanger 16 via the condenser 6 of the secondary cooling circuit 15 to the primary cooling circuit 14, here the evaporator 22 of the heat exchanger 16.
  • Fig. 4 correspond to the respective cycle processes (I) - (II), (II) - (III), (III) - (IV), (IV) - (I) for the secondary refrigeration circuit 15 and (V) - (VI), (VI) - (VII), (VII) - (VIII), (VIII) - (V) for the primary refrigeration circuit 14 basically the in Fig. 2 cycle process shown and described in the introduction to the description, but these cycle processes then take place at different pressures, temperatures and specific enthalpies.
  • the heat transfer between the refrigeration circuits 14, 15 takes place in the area of the heat exchanger 16, which is shown in the cycle processes according to FIG Fig. 4 in the changes of state (II) - (III) of the secondary refrigeration circuit 15 and (VIII) - (V) of the primary refrigeration circuit 14 is shown.
  • the evaporation temperature of the primary refrigeration circuit 14 must be slightly lower than the condensation temperature of the secondary refrigeration circuit 15 in order to enable the required heat transfer through an artificial temperature sink.
  • the significant reduction in the final temperature of the liquefaction in the area of the condenser 6 of the secondary refrigeration circuit 15 increases the enthalpy difference required for the evaporation of the refrigerant.
  • the achievable injection temperature in the evaporator 8 of the primary refrigeration circuit 15 is reduced.
  • the lower injection temperature creates a greater temperature gradient between the refrigerant and the centrifuge chamber 12, which improves the dissipation of heat.
  • Fig. 4 With the diagram according to Fig. 4 the operation of the refrigeration system 2 formed with the primary refrigeration circuit 14 and the secondary refrigeration circuit 15 is only intended to be shown qualitatively.
  • the cycle processes are shown by way of example for a refrigerant in the refrigeration circuits 14, 15, which is each designed as a refrigerant R1234yf.
  • the injection temperatures in the evaporator 8 of the secondary cooling circuit 15 can be reduced to a minimum by using the two refrigeration circuits 14, 15 connected in series.
  • the reduced inlet temperature of the refrigerant in the area of the condenser 6 increases the specific internal energy to be absorbed by the refrigerant, which is necessary in order to completely evaporate it.
  • the refrigeration system 2 according to the invention it is possible, due to the respective vapor pressure curve, to use a refrigerant which has less enthalpy of vaporization and a higher injection temperature at the same pressure levels.
  • the refrigeration system 2 according to the invention can u. U. are operated at significantly higher ambient temperatures than a refrigeration system 2 according to Fig. 1 with only one refrigeration circuit 3. This does indeed result in a loss of performance. However, this loss of performance does not affect the refrigeration system as much as a single-stage refrigeration system 3.
  • FIGS 5 to 8 show an exemplary structural design of a centrifuge 1 with the integration of the components required for the refrigeration system 2.
  • the centrifuge 1 has a housing 28, which is basically angular in horizontal section and can be closed by means of a cover 29.
  • the safety element 26 in the form of the safety vessel 27, in which the rotor rotates, is arranged in a sub-space 30 which is accessible via the cover 29.
  • essential components of the refrigeration system 2 in particular the compressors 5, 17, the heat exchanger 16 and the condenser 19 or heat exchanger 20 are in an adjacent subspace 31, which is not accessible via the cover 29, so that the housing 28 is closed here and associated lines 9, 23 are arranged.
  • the compressor 17 of the primary refrigeration circuit 14 is arranged in an intermediate space 32 between a corner 33 and the safety boiler 27.
  • the compressor 5 of the secondary refrigeration circuit 15 is arranged in an intermediate space 34 between an adjacent corner 35 and the safety boiler 27.
  • the heat exchanger 16 is in turn arranged in an intermediate space 36 between a side wall 37 connecting the two corners 33, 35 and the safety boiler 27.
  • Fig. 8 it can be seen that the two expansion elements 7, 21 are arranged in a plane below the safety boiler 27 (laterally offset to this in the subspace 31 or even below the safety boiler 27 in the subspace 30), which results in a compact design and / or lines from the expansion elements 7, 21 to the evaporator 8 can be kept short.
  • FIG. 3 Schematic is in Fig. 3 outlines that the two refrigeration circuits 14, 15 are controlled via an electronic control unit 39 having control logic 38.
  • the control unit 39 controls the power of the compressors 5, 17 via control lines 40, 41, which is done by directly controlling the electrical application of the motors 4, 18 or by transmitting a control signal to the motors 4, 18, in which, u. U.
  • the suitable electrical application of the motors 4, 18 is controlled.
  • the invention also includes the following possibilities: In Fig. 9 the operating state 43 of the compressors 5, 17 or the motors 4, 18 is shown over the time 42, which results from the activation of the same by the control unit 39.
  • Fig. 9 shows the control for ensuring permanent cooling with maximum cooling capacity.
  • the controlled operating behavior of the secondary refrigeration circuit 15, that is to say of the compressor 5 is shown with a solid operating curve 47, while the operating curve 48 for the operating behavior of the primary refrigeration circuit 14 and thus of the compressor 17 is shown with a broken line.
  • the operating states are permanently switched to the ON operating state 45.
  • Fig. 9 shows Fig. 9 that the switchover to the ON operating state 45 for the operating curves 47, 48 takes place with a time offset 49, whereby a reduction in the peak currents is brought about by a temporal separation of the two peaks as a result of the switchover of the motors 4, 18 to the ON operating state 45 can.
  • the activation of the secondary cooling circuit 15 takes place before the activation of the primary circuit 14, while a reverse time offset 49 is also possible.
  • Fig. 10 shows the corresponding relationships for a control (which also includes a regulation) of a predetermined temperature in the centrifuge chamber 12, which does not require the provision of the maximum cooling capacity.
  • the operating states of the refrigeration circuits 14, 15 are alternately switched between the ON operating state 45 and the OFF operating state 46, with the frequency of the switching back and forth and / or the ratio of the time periods for the ON operating state 45 and the OFF operating state 46 correlates with the provided cooling capacity, so that, depending on the required cooling capacity, the control unit can be used for suitable control by influencing the frequency of switching back and forth and the ratios of the time periods.
  • a time offset 49 for switching from the OFF operating state 46 to the ON operating state 45 can also be used for this switching back and forth, the switching back from the ON operating state 45 to the OFF operating state 46 preferably then taking place without a time offset 49 .
  • the two refrigeration circuits 14, 15 are switched over at the same frequency to provide a constant refrigeration capacity, but in the illustrated embodiment, given the time offset 49, the ON operating state 45 for the secondary refrigeration circuit 15 is longer than for the primary refrigeration circuit 14 (without this necessarily being the case).
  • Fig. 11 shows a modified temperature control, in which the primary cooling circuit 14 is permanently switched to the ON operating state 45, so that it provides a permanent heat sink.
  • the control of the cold supplied to the centrifuge chamber 12 is controlled only by the decrease of the cold from the primary refrigeration circuit 14 by the secondary refrigeration circuit 15 by switching the secondary refrigeration circuit 15 back and forth between the ON operating state 45 and the OFF operating state 46 takes place, whereby here to control or regulate the temperature in the centrifuge chamber 12 and thus the cold supplied to the centrifuge chamber 12, the ratio of the time periods of the ON operating states and the OFF operating states is influenced.
  • HD denotes the high-pressure circuit 24
  • ND denotes the low-pressure circuit 25.
  • an evaporator 8 (and a heat exchanger formed with it) can extend inside a security element 26 or security vessel 27, in a wall of the security element 26 or security vessel 27 itself, or outside of the security element 26 or security vessel 27.
  • a line forming the evaporator 8 can extend in the circumferential direction of a safety boiler 27 or be integrated in this way into the safety boiler 27 itself.
  • the primary refrigeration circuit 14 and the secondary refrigeration circuit 15 can both be arranged inside or outside a safety boiler 27.
  • the secondary cooling circuit 15 can be arranged in an intermediate space between the safety boiler 27 and the safety wall, while the primary cooling circuit 14 is then arranged on the side of the safety wall facing away from the safety boiler 27. It is also possible that the safety boiler 27 is double-walled and the secondary cooling circuit 15 extends at least partially and in the area of the evaporator 8 in an intermediate space between the double walls of the safety boiler 27.
  • the primary refrigeration circuit 14 and the secondary refrigeration circuit 15 are sometimes referred to in abbreviated form in the form of “the refrigeration circuits 14, 15”.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Centrifugal Separators (AREA)

Claims (12)

  1. Centrifugeuse (1), avec
    a) un carter (28),
    b) une chambre de centrifugeuse (12) dans laquelle un rotor est ou peut être disposé supporté en rotation,
    c) un circuit de réfrigération primaire (14),
    caractérisée par
    d) un circuit de réfrigération secondaire (15), qui est couplé thermiquement au circuit de réfrigération primaire (14) et à la chambre de centrifugeuse (12),
    e) une unité de commande (39) dotée d'une logique de commande (38) étant présente, laquelle commande le circuit de réfrigération primaire (14) et le circuit de réfrigération secondaire (15) de telle sorte que
    ea) pendant un fonctionnement de la centrifugeuse (1) avec une rotation du rotor, il se produit une production de froid au moyen du circuit de réfrigération primaire (14), et/ou
    eb) un fonctionnement simultané du circuit de réfrigération primaire (14) et du circuit de réfrigération secondaire (15) est effectué.
  2. Centrifugeuse (1) selon la revendication 1, caractérisée en ce que le circuit de réfrigération primaire (14) et/ou le circuit de réfrigération secondaire (15) comporte/comportent un compresseur (5 ; 17), un condenseur (6; 19), un équipement d'expansion (7 ; 21) et un évaporateur (8 ; 22).
  3. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que le circuit de réfrigération primaire (14) est un circuit haute pression (24), et le circuit de réfrigération secondaire (15) est un circuit basse pression (25).
  4. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que le circuit de réfrigération primaire (14) comporte un réfrigérant combustible.
  5. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que le circuit de réfrigération secondaire (15) comporte un réfrigérant non inflammable ou difficilement inflammable.
  6. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que
    a) le circuit de réfrigération primaire (14) comporte un réfrigérant combustible, et le circuit de réfrigération secondaire (15) comporte un réfrigérant non inflammable ou difficilement inflammable, ou
    b) le circuit de réfrigération primaire (14) comporte un réfrigérant non inflammable ou difficilement inflammable, et le circuit de réfrigération secondaire (15) comporte un réfrigérant non inflammable ou difficilement inflammable.
  7. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce qu'au moins un échangeur de chaleur (16 ; 20) est constitué en tant qu'échangeur de chaleur à microcanaux.
  8. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que
    a) le circuit de réfrigération primaire (14),
    b) un échangeur de chaleur (16) qui couple thermiquement le circuit de réfrigération primaire (14) au circuit de réfrigération secondaire (15), et
    c) au moins une partie du circuit de réfrigération secondaire (15)
    sont disposés sur un côté d'un élément de sécurité (26) qui est éloigné de la chambre de centrifugeuse (12).
  9. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que
    a) un carter (28) de la centrifugeuse (1) comporte une coupe horizontale à peu près rectangulaire,
    b) l'élément de sécurité (26) est une chaudière de sécurité (27) ayant une coupe horizontale circulaire,
    c) un compresseur (17) du circuit de réfrigération primaire (14) est disposé dans un espace intermédiaire (32) entre un coin (33) du carter (28) et la chaudière de sécurité (27),
    d) un compresseur (5) du circuit de réfrigération secondaire (15) est disposé dans un espace intermédiaire (34) entre un coin (35) du carter (28) et la chaudière de sécurité (27),
    e) le ou un échangeur de chaleur (16), qui couple thermiquement le circuit de réfrigération primaire (14) au circuit de réfrigération secondaire (15), est disposé dans un espace intermédiaire (36) entre une paroi latérale (37) du carter (28) et la chaudière de sécurité (27).
  10. Centrifugeuse (1) selon l'une des revendications précédentes, caractérisée en ce que la logique de commande (38) de l'unité de commande (39) est constituée de telle sorte qu'un compresseur (17) du circuit de réfrigération primaire (14) et/ou un compresseur (5) du circuit de réfrigération secondaire (15) est/sont commandés pour adopter des états de fonctionnement ON (45) et des états de fonctionnement OFF (46).
  11. Centrifugeuse (1) selon la revendication 10, caractérisée en ce que la logique de commande (38) de l'unité de commande (39) est constituée de telle sorte que le compresseur (17) du circuit de réfrigération primaire (14) et le compresseur (5) du circuit de réfrigération secondaire (15) sont commandés pour adopter l'état de fonctionnement ON (45) de façon décalée avec un décalage temporel (49).
  12. Centrifugeuse (1) selon la revendication 10 ou 11, caractérisée en ce que la logique de commande (38) de l'unité de commande (39) est constituée de telle sorte que
    a) le circuit de réfrigération primaire (14) est mis en fonctionnement dans un état de fonctionnement ON (45) de façon durable indépendamment d'une performance de réfrigération nécessaire pour le refroidissement de la chambre de centrifugeuse (12), et
    b) le circuit de réfrigération secondaire (15) est commuté dans un sens et dans l'autre entre un état de fonctionnement ON (45) et un état de fonctionnement OFF (46) en fonction d'une performance de réfrigération nécessaire pour le refroidissement de la chambre de centrifugeuse (12).
EP17200209.9A 2017-11-06 2017-11-06 Centrifugeuse Active EP3479903B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP17200209.9A EP3479903B1 (fr) 2017-11-06 2017-11-06 Centrifugeuse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17200209.9A EP3479903B1 (fr) 2017-11-06 2017-11-06 Centrifugeuse

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EP3479903B1 true EP3479903B1 (fr) 2020-09-16

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Cited By (3)

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DE102022116777B3 (de) 2022-07-05 2023-10-26 Rittal Gmbh & Co. Kg Kühlgerät für die Schaltschrankklimatisierung sowie eine entsprechende Schaltschrankanordnung
EP4434636A1 (fr) 2023-03-23 2024-09-25 Sigma Laborzentrifugen GmbH Ensemble de produit de fermentation de centrifugeuse de laboratoire, produit de fermentation de mesure et centrifugeuse de laboratoire
EP4434637A1 (fr) 2023-03-23 2024-09-25 Sigma Laborzentrifugen GmbH Dispositif de fixation de centrifugeuse de laboratoire, ensemble capteur de centrifugeuse de laboratoire, unité de rotor de centrifugeuse de laboratoire, procédé de montage d'une unité de rotor de centrifugeuse de laboratoire et procédé de fonctionnement d'une centrifugeuse de laboratoire

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CN110332728A (zh) * 2019-07-04 2019-10-15 深圳市瑞沃德生命科技有限公司 一种制冷系统
DE102021125446A1 (de) * 2021-09-30 2023-03-30 Thermo Electron Led Gmbh Kühlsystem und Laborgerät mit Kühlsystem
DE102021126963A1 (de) 2021-10-18 2023-04-20 Thermo Electron Led Gmbh Kühlsystem
CN114226074B (zh) * 2021-11-30 2023-03-31 浙江大学 基于热源分析的超重力离心装置的温控系统和温控方法

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DE102012002593A1 (de) 2012-02-13 2013-08-14 Eppendorf Ag Zentrifuge mit Kompressorkühleinrichtung und Verfahren zur Steuerung einer Kompressorkühleinrichtung einer Zentrifuge
JP5800994B2 (ja) * 2012-09-21 2015-10-28 三菱電機株式会社 冷凍装置及びその制御方法
DE102014107294B4 (de) 2014-05-23 2017-02-09 Andreas Hettich Gmbh & Co. Kg Zentrifuge
DE102014110467A1 (de) 2014-07-24 2016-01-28 Andreas Hettich Gmbh & Co. Kg Zentrifuge
EP3015791A1 (fr) 2014-10-29 2016-05-04 Eppendorf Ag Centrifugeuse dotée d'un circuit de refroidissement de compresseur et procédé de fonctionnement d'une centrifugeuse dotée d'un circuit de refroidissement de compresseur

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022116777B3 (de) 2022-07-05 2023-10-26 Rittal Gmbh & Co. Kg Kühlgerät für die Schaltschrankklimatisierung sowie eine entsprechende Schaltschrankanordnung
EP4434636A1 (fr) 2023-03-23 2024-09-25 Sigma Laborzentrifugen GmbH Ensemble de produit de fermentation de centrifugeuse de laboratoire, produit de fermentation de mesure et centrifugeuse de laboratoire
EP4434637A1 (fr) 2023-03-23 2024-09-25 Sigma Laborzentrifugen GmbH Dispositif de fixation de centrifugeuse de laboratoire, ensemble capteur de centrifugeuse de laboratoire, unité de rotor de centrifugeuse de laboratoire, procédé de montage d'une unité de rotor de centrifugeuse de laboratoire et procédé de fonctionnement d'une centrifugeuse de laboratoire
WO2024194313A1 (fr) 2023-03-23 2024-09-26 Sigma Laborzentrifugen Gmbh Utilisation d'un produit factice de mesure
WO2024194312A1 (fr) 2023-03-23 2024-09-26 Sigma Laborzentrifugen Gmbh Dispositif de fixation de centrifugeuse de laboratoire, ensemble capteur de centrifugeuse de laboratoire, unité rotor de centrifugeuse de laboratoire, procédé de montage d'une unité rotor de centrifugeuse de laboratoire et procédé de fonctionnement d'une centrifugeuse de laboratoire

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