EP3479903A1 - Centrifugeuse - Google Patents

Centrifugeuse Download PDF

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Publication number
EP3479903A1
EP3479903A1 EP17200209.9A EP17200209A EP3479903A1 EP 3479903 A1 EP3479903 A1 EP 3479903A1 EP 17200209 A EP17200209 A EP 17200209A EP 3479903 A1 EP3479903 A1 EP 3479903A1
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EP
European Patent Office
Prior art keywords
refrigeration cycle
centrifuge
primary
refrigerant
compressor
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EP17200209.9A
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German (de)
English (en)
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EP3479903B1 (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 present type are used, for example, in biotechnology, the pharmaceutical industry, medical technology and environmental analysis.
  • a centrifuge is carried out a centrifugation of a product, in particular a container or vessel with sample or substance arranged therein, or a plurality of such products at speeds which may be more than 3,000 U / min, for example. More than 15,000 U / min.
  • accelerations acting on the product are to be produced, which may be, for example, more than 15,000 ⁇ g (in particular more than 16,000 ⁇ g, more than 20,000 ⁇ g up to more than 60,000 ⁇ g).
  • the centrifugation is intended to break down a mixture of substances formed by the sample or the substance into components of different densities.
  • a targeted control of the pressure and / or temperature conditions can additionally take place during the centrifugation.
  • PCR polymerase chain reaction
  • the F-Gas Regulation (Regulation EU No. 517/2014 of the European Parliament and of the Council of 16.04.2014, which is valid from 01.01.2015), is aimed at emissions of fluorinated greenhouse gases (F-gases) by the year 2030 be reduced to 21% in several steps specified in the F-Gas Regulation.
  • conventionally used refrigerants such as 1,1,1,2-tetrafluoroethane (R-134a) or R404a need to be replaced with alternative refrigerants, which is a challenge for centrifuges of the present type.
  • centrifuges in operation generate very high kinetic energies, which are generated in close proximity to the refrigeration cycle and in the event of a crash of the centrifuge can destroy the inner workings of the centrifuge including the refrigeration cycle. This can escape the coolant in a crash and catch fire, which can also cause a fire in a crash spark.
  • special requirements with regard to the flammability of the refrigerant must be observed.
  • a refrigerant which ensures the particular requirements with regard to combustibility must also be powerful enough to ensure the cooling required during operation of the centrifuge.
  • EP 3 015 791 A1 further proposes to arrange an injection system in the evaporator of the refrigeration cycle, wherein the pressure in the compressor is to be limited by controlling the injection. Furthermore, it is proposed that the refrigeration cycle has at least one bypass for bridging an internal heat exchanger. In contrast to a refrigeration cycle in which a refrigerant R-134a is used, here in the refrigeration cycle between the low pressure side and the high pressure side, a larger pressure difference is required 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, an altered safety design of the centrifuge, which must be designed for a triple working pressure, and / or a restriction of the compressor pressure conditional.
  • a hot gas bypass By means of a hot gas bypass must also be ensured that hot refrigerant is supplied to the evaporator, whereby an ice formation, for example. Must be avoided at the triple point of CO 2 in the evaporator.
  • a control of the hot gas bypass in dependence on the temperature in the suction line of the compressor is required, wherein suitably the hot gas bypass is used in a partial load operation.
  • a control of the compressor can take place to avoid the formation of ice or a control of said injection system can take place.
  • the publication DE 10 2014 110 467 A1 Proposes that not only a refrigeration cycle be used in a centrifuge. Rather, the generation of the cold should be done by a primary refrigeration cycle, which is then thermally coupled via a heat exchanger with a secondary cooling circuit in which a refrigerant is circulated via a pump.
  • the primary refrigeration circuit downstream secondary cooling circuit thus serves only to transport the cold, which has been generated by the primary refrigeration cycle, from the heat exchanger to the centrifuge chamber.
  • a conventional combustible refrigerant can be used, which may have low costs, but may have a high specific enthalpy of vaporization.
  • a non-combustible heat transfer medium such as, for example, a cooling water with additives (for example, salt or alcohol) which reduce the freezing point
  • a non-combustible heat transfer medium such as, for example, a cooling water with additives (for example, salt or alcohol) which reduce the freezing point
  • the primary refrigeration cycle and the secondary refrigeration cycle are then separated from one another via a safety wall, the combustible primary refrigeration cycle can be protected by the safety wall in the event of a crash, while the crash can possibly have effects on the non-combustible secondary refrigeration cycle.
  • the primary refrigeration cycle may extend below the secondary refrigeration cycle or a safety boiler or laterally offset thereto in the housing of the centrifuge.
  • a safety boiler can be fastened to the housing of the centrifuge via a clamping connection such that in the event of a crash a relative movement of the safety boiler relative to the housing of the centrifuge is possible. It is also proposed that lines of the primary refrigeration cycle are made of a mechanically stronger material than lines of the secondary cooling circuit, whereby it is also possible that lines of the secondary cooling circuit are specifically equipped with predetermined breaking points.
  • 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 (and driven by a motor) rotor can be arranged in the centrifuge chamber.
  • the centrifuge chamber surrounds at least in a partial circumferential area a security element, which may also be a safety vessel extending completely in the circumferential direction (for example, a single or double-walled).
  • the centrifuge has both a primary refrigeration cycle and a secondary refrigeration cycle.
  • the secondary refrigeration cycle is thermally coupled (in particular via a heat exchanger) to the primary refrigeration cycle, so that cold generated in the primary refrigeration cycle can be transferred to the secondary refrigeration cycle.
  • the secondary refrigeration cycle is thermally coupled to the centrifuge chamber, so that both the generated in the primary refrigeration cycle and transferred through the heat exchanger cold and the cold generated in the secondary refrigeration cycle can be transferred cumulatively to the centrifuge chamber.
  • the centrifuge has a control unit.
  • the control unit has control logic that controls the primary refrigeration cycle and the secondary refrigeration cycle.
  • the control takes place such that during operation of the centrifuge with a rotation of the rotor, a generation of cold by means of the primary refrigeration cycle takes place and / or a simultaneous operation of the primary refrigeration cycle and the secondary refrigeration cycle takes place.
  • the invention proposes for the first time to operate simultaneously the primary refrigeration cycle and the secondary refrigeration cycle, so that both mentioned refrigeration circuits used to produce the used for cooling the centrifuge chamber Cold can provide a contribution.
  • the two refrigeration circuits can be adjusted individually (for example, with regard to the state changes, the pressure changes and the enthalpy difference and / or to the respectively used in the refrigeration circuits refrigerant), resulting in an increased efficiency and / or an improved ratio in terms of construction volume and Cost over the producible cooling capacity can result.
  • the inventive design allows any choice of refrigerant in the two refrigeration circuits, with which the Design scope in terms of efficiency, environmental compatibility, the security against the development of a fire and / or increase the cost.
  • the inventive design also allows new control options for the control of the temperature in the centrifuge chamber depending on the design 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 refrigeration is produced by using electrical power. It is possible here that in a refrigeration cycle, a compression of the refrigerant and / or a change in an aggregate state of the refrigerant is generated, the refrigeration circuit uses a magnetocaloric effect, the refrigeration cycle has an electric Peltier cooling, the refrigeration circuit generates cold using a vortex tube or in the refrigeration cycle is a generation of cold using an absorption refrigeration cycle or a compression refrigeration cycle.
  • a refrigeration cycle does not include a "cooling circuit" in which only a refrigerant is conveyed by means of a pump and by means of a transport of cold from a transfer point (such as a heat exchanger, in which a transmission of cold, which was generated externally from the cooling circuit is done, to the refrigerant of the refrigeration cycle) takes place to the centrifuge chamber.
  • a transfer point such as a heat exchanger, in which a transmission of cold, which was generated externally from the cooling circuit is done, to the refrigerant of the refrigeration cycle
  • control unit in the sense of the invention may be a control unit in the form of a singular unit, a plurality of interconnected or flanged control unit modules, or a plurality of interconnected or networked control subunits.
  • the primary refrigeration cycle and / or the secondary refrigeration cycle for a proposal of the invention comprises a compressor, a condenser, an expansion device and an evaporator on.
  • This choice of embodiment of the refrigeration cycle has been found to be advantageous in terms of space, cost, energy efficiency and usable refrigerant.
  • the primary refrigeration cycle may be formed as a high pressure circuit, while the secondary refrigeration cycle may be formed as a low pressure circuit. This allows the different design of different refrigerant circuits with a potential for optimizing the generation of the required cold.
  • a combustible refrigerant in particular, a flame retardant refrigerant, a flammable refrigerant, or a highly flammable refrigerant
  • a combustible refrigerant in particular, a flame retardant refrigerant, a flammable refrigerant, or a highly flammable refrigerant
  • This proposal is based on the finding that the lines and components of the primary refrigeration cycle u. U. also outside a safety boiler of the centrifuge can be arranged so that even in the case of a centrifuge crash the combustible refrigerant in the primary refrigeration circuit can not escape from the lines and / or can not be ignited.
  • the invention further proposes that in the secondary refrigeration cycle, a non-flammable or flame-retardant refrigerant is used.
  • a non-flammable or flame-retardant refrigerant is used in the secondary refrigeration cycle.
  • This embodiment takes into account the fact that u. U. the refrigerant of the secondary refrigeration circuit is also located in the same area of the safety boiler of the centrifuge or even inside, so that this is basically exposed in a centrifuge crash the risk of the formation of a fire.
  • the use of the non-flammable or flame-retardant refrigerant can at least reduce the inherent risk of the occurrence of a fire.
  • the invention proposes that the primary refrigeration cycle comprises a combustible refrigerant (especially a low flammable refrigerant, a flammable refrigerant or a highly flammable refrigerant), while the secondary refrigeration cycle has a nonflammable or low flammable refrigerant. It is also possible that the primary refrigeration cycle, a non-flammable or flame retardant refrigerant and the secondary refrigeration cycle has a non-flammable or flame retardant refrigerant. In these cases, the two refrigeration circuits may have the same or different refrigerants.
  • Flammable 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, cause flame propagation, 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 velocity that is ⁇ 10 cm / s when tested at 23 ° C and a pressure of 1.013 bar.
  • “Flammable refrigerants” are assigned to the groups A2 (low toxicity) or B2 (higher toxicity) of the standard SN DIN EN 378-1 and meet for a one-substance refrigerant and for a mixture refrigerant employment the conditions that it with a Test at 60 ° C and a pressure of 1.013 bar to a flame propagation comes, the lower explosion limit (LFL)> 3.5 vol .-% and the heat of combustion is ⁇ 19,000 kJ / kg.
  • highly flammable refrigerants are considered to be refrigerants which are classified according to the standard SN DIN EN 378-1 in the groups A3 (low toxicity) and B3 (higher toxicity).
  • one-substance-refrigerant and mixture-refrigerant use are assigned to these groups, if it comes with a test with 60 ° C and a pressure of 1.013 bar to a flame propagation and the lower explosion limit (LFL) ⁇ 3.5 vol .-% or the heat of combustion is ⁇ 19,000 kJ / kg.
  • one-substance or mixture refrigerants are regarded as "combustible 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 one-component or mixture refrigerants associated with groups A1 or B1 and which are not flammable are referred to as “non-flammable refrigerants” .
  • a heat exchanger in the region of the condenser of the primary refrigeration cycle and / or in the region of the transfer between the two refrigeration circuits, ie the evaporator of the primary refrigeration circuit and the condenser of the secondary refrigeration cycle can be arranged.
  • This heat exchangers of any type can be used in the invention.
  • a plate heat exchanger or a shell and tube heat exchanger may be used.
  • a microchannel heat exchanger is used for a heat exchanger, in particular for the heat exchanger in the region of the condenser of the primary refrigeration cycle.
  • 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 extent of the channels or a diameter thereof of, for example, less than 2 mm or 1 mm of the Refrigerant is flowed through, whereby a high efficiency, a small filling volume of the refrigerant, a low weight and a compact design can be achieved.
  • the refrigerant is thus not routed here in pipes.
  • the channels are formed by bores of the body or block or the body or block of several, for example, welded together or soldered parts is formed, which may have grooves and limit the channels when connected to each other.
  • ambient air can then be conducted past the body or block directly and / or to cooling fins attached thereto by means of a blower.
  • heat exchangers of this type as are sold, for example, by the company Danfoss or on the Internet site www.kka-online.info/ obviously/kka_New Trends_bei_ Komplettverfless whyssaetzen_1406699 are described.
  • the components of the refrigeration circuits and the heat exchangers used can be arranged at any point in the centrifuge.
  • the rotor of the centrifuge on the one hand and the primary refrigeration circuit on the other hand are on different sides of the security element, which means for the formation of the security element as a safety boiler, that the rotor is located inside the safety boiler, while the primary refrigeration circuit outside the safety boiler is.
  • the centrifuge housing may have an approximately rectangular horizontal section.
  • the security element is a safety vessel with a circular horizontal section. Between a corner of the housing and the safety vessel with a circular horizontal section results in a gap in which in the context of the invention, a compressor of the primary refrigeration cycle can be arranged particularly advantageous. A corresponding other space results between another corner of the housing and the safety boiler. In this other space then the compressor of the secondary refrigeration cycle can be arranged.
  • the heat exchanger which thermally couples the primary refrigeration cycle and the secondary refrigeration cycle together, may in this case be arranged in a space which results between a side wall of the housing and the safety vessel, which is preferably a 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 safety vessel which is preferably a 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.
  • control or regulation in the following also briefly only “control” of the compressors of the refrigeration circuits
  • variable speed compressors can be used.
  • these require a converter, other components and / or increased sensor complexity and regulatory effort, which can increase the cost.
  • the control logic of the control unit is designed such that a compressor of the primary refrigeration cycle and / or a compressor of the secondary refrigeration cycle is / are activated in ON operating states and OFF operating states.
  • non-speed-controlled compressor can be used, which thus have only an active and a non-active operating state.
  • the control of the compression power and hence the generated cold can be controlled over the duration of the ON operating conditions and the ratio of the duration of the ON operating conditions to the duration of the intermediate OFF operating conditions.
  • the two compressors of the refrigeration circuits are simultaneously controlled in the ON operating state. If, however, an undesirable increased peak current due to the simultaneous switching of the compressor can be avoided, are controlled for a proposal by the inventor of the compressor of the primary refrigeration cycle and the compressor of the secondary refrigeration circuit with a time delay in the ON operating state. On the other hand, the change to the OFF operating state can take place simultaneously or likewise with a time offset.
  • control logic of the control unit of the centrifuge is designed such that the primary refrigeration circuit regardless of a required cooling 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 that occur in the evaporator of the primary refrigeration circuit are not as great as would be the case for an alternating changeover between an ON operating state and an OFF operating state in the primary refrigeration cycle.
  • only the secondary refrigeration cycle is switched between an ON operation state and an OFF operation state depending on a required refrigerating capacity for cooling the centrifuge chamber.
  • 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 cycle 3.
  • a compressor 5 driven by an electric power motor 4
  • a condenser or condenser 6 an expansion element 7 (specifically, an expansion valve or a throttle), and an evaporator 8 are connected in this order via lines 9a, 9b , 9c, 9d connected in a closed circuit.
  • Fig. 1 the circled numerals indicate the states (I), (II), (III) and (IV) of the coolant used in the refrigeration cycle 3.
  • the condenser 6 forms a high pressure circuit part 10 with the lines 9a, 9b
  • the evaporator 8 with the lines 9c, 9d forms a low pressure circuit part 11.
  • the cold generated in the refrigeration cycle 3 is transferred to the centrifuge chamber 12, which is shown here only schematically.
  • An energetic exchange of the refrigeration cycle 3 takes place via the provision of refrigeration for the centrifuge chamber 12 through the evaporator 8 on the one hand by the application of electrical power to the motor 4 and the compression of the refrigerant in the region of the compressor 5. On the other hand takes place in the region of the condenser 6 a Heat exchange with the ambient air, in which case a fan with electric power can be driven.
  • the condenser 6 thus forms a heat exchanger 13.
  • Fig. 2 shows the left-handed cyclic process, such as this with the steps a) to d) and the state changes (I) - (II), (II) - (III), (III) - (IV) and (IV) - (I) in of the introduction to 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 comprises a primary refrigeration cycle 14 and a secondary refrigeration cycle 15.
  • the primary refrigeration cycle 14 is coupled via a heat exchanger 16 to the secondary refrigeration cycle 15.
  • the secondary refrigeration cycle 15 basically corresponds to the refrigeration cycle 3 according to Fig. 1 which also has corresponding states (I), (II), (III) and (IV).
  • components included in the refrigeration cycle 3 are identified with the same reference numerals and will be referred to hereinafter by the same designations.
  • the evaporator 6 differing from Fig. 1 not with the ambient air. Rather, the evaporator 6 is part of the heat exchanger 16.
  • the states (V), (VI), (VII) and (VIII) indicate the states of the refrigerant between the evaporator 22 and the compressor 17 (state V), between the compressor 17 and the condenser 19 (FIG.
  • the refrigerant also circulates between a high pressure circuit part and a low pressure circuit part, as previously explained for the refrigeration cycle 3.
  • the primary refrigeration cycle 14 forms a high pressure circuit 24, while the secondary refrigeration cycle 15 forms a low pressure circuit 25.
  • An energetic exchange of the primary refrigeration cycle 14 takes place via the provision of cold for the heat exchanger 16 through the evaporator 22 on the one hand by the application of electric motor 18 and the compression of the refrigerant in the region of the compressor 17. On the other hand, takes place in the region of the condenser 19 a heat exchange with the ambient air, in which case a fan with electric power can be driven.
  • An energetic exchange of the secondary refrigeration cycle 15 via the provision of cold through the heat exchanger 16 to the condenser on the one hand by the application of the motor 4 with electrical power and the compression of the Refrigerant in the region of the compressor 5.
  • the refrigeration circuits 14, 15 can be operated simultaneously. Based on the introduction of electrical energy through the motor 18 and the compressor 17 driven therefrom, refrigeration is generated in the primary refrigeration cycle 14, which is transmitted via the heat exchanger 16 to the secondary refrigeration circuit 15 by the evaporator 22 gives off cold to the condenser 6 and by the transferred cold is used in the condenser 6 for liquefying the refrigerant of the secondary refrigeration circuit 15.
  • the secondary refrigeration cycle 15 supplementary refrigeration is generated with the introduction of electrical energy via the motor 4 and the compressor 5 driven therefrom. The refrigeration generated in this way by the primary refrigeration circuit 14 and the secondary refrigeration circuit 15 is then cumulated by the evaporator 8 of the secondary refrigeration cycle 15 is transmitted to the centrifuge chamber 12. It is possible that the mass flows, the refrigerant and / or the pressures in the two refrigeration circuits 14, 15 are different.
  • Fig. 4 shows the two left-handed cycles of the two refrigeration circuits 14, 15 in a diagram in which the logarithm of the pressure p over the enthalpy h is shown.
  • the coupling of the two refrigeration circuits 14, 15 via the heat exchanger 16, which takes place here, is based on the principle that the coolant can be cooled down more deeply in the secondary refrigeration circuit 15 as a result of the supply of cold via the heat exchanger 16 from the primary refrigeration circuit 14 than the latter Case is when the refrigerant cooling the centrifuge chamber 12 is thermally coupled via a condenser 6 in the form of a heat exchanger 13 with the environment.
  • the secondary refrigeration cycle 15 absorbs heat from the centrifuge chamber 12 and outputs it in the heat exchanger 16 via the condenser 6 of the secondary refrigeration cycle 15 to the primary refrigeration cycle 14, here the evaporator 22 of the heat exchanger 16, from.
  • the heat transfer between the refrigeration circuits 14, 15 takes place in the region of the heat exchanger 16, which in the cycle according to Fig. 4 in the state changes (II) - (III) of the secondary refrigeration cycle 15 and (VIII) - (V) of the primary refrigeration cycle 14 is shown.
  • the evaporation temperature of the primary refrigeration cycle 14 must be slightly lower than the condensation temperature of the secondary refrigeration cycle 15 in order to allow the necessary heat transfer through an artificial temperature sink.
  • the achievable injection temperature in the evaporator 8 of the primary refrigeration circuit 15 is lowered.
  • the lower injection temperature creates a greater temperature gradient between the refrigerant and the centrifuge chamber 12, thus improving the dissipation of heat.
  • Fig. 4 With the diagram according to Fig. 4 should only the quality of the operation of the refrigeration system 2 formed with the primary refrigeration cycle 14 and the secondary refrigeration cycle 15 are shown.
  • the cycle processes are exemplified for a refrigerant in the refrigeration circuits 14, 15, which is in each case designed as a refrigerant R1234yf.
  • the injection temperatures in the evaporator 8 of the secondary refrigeration cycle 15 are lowered to a minimum. Due to the reduced inlet temperature of the refrigerant in the region of the condenser 6, the internal specific energy of the refrigerant to be absorbed increases, which is necessary in order to evaporate it completely. Thus, the amount of heat that can be transferred from the centrifuge chamber 12 to the refrigerant increases.
  • 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 has a higher injection temperature at the same pressure positions.
  • the refrigeration system 2 according to the invention can u. U. operated at much higher ambient temperatures than one Refrigeration system 2 according to Fig. 1 with only one refrigeration cycle 3. This occurs while a loss of power. However, this power loss does not affect the refrigeration system as much as a single-stage refrigeration system 3.
  • Fig. 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 generally rectangular in horizontal section and can be closed by means of a cover 29.
  • the security element 26 in the form of the safety boiler 27, in which the rotor rotates is arranged in a subspace 30, which is accessible via the cover 29.
  • essential components of the refrigeration system 2 in particular the compressor 5, 17, the heat exchanger 16 and the condenser 19 or heat exchanger 20th and associated lines 9, 23 arranged.
  • a control panel and displays of the centrifuge 1 are arranged in the subspace 31 and the closed housing part connected thereto.
  • Fig. 5 are the subspaces 30, 31, which are not separated by a wall here, separated by the dashed fictitious curved separation plane shown.
  • the compressor 17 of the primary refrigeration cycle 14 is disposed in a gap 32 between a corner 33 and the safety boiler 27.
  • the compressor 5 of the secondary refrigeration cycle 15 is arranged in a gap 34 between an adjacent corner 35 and the safety boiler 27.
  • the heat exchanger 16 is in turn arranged in a gap 36 between the two corners 33, 35 connecting side wall 37 and the safety boiler 27.
  • Fig. 8 It can be seen that the two expansion elements 7, 21 in a plane below the safety vessel 27 (laterally offset to this in the subspace 31 or even below the safety vessel 27 in the subspace 30) are arranged, whereby a compact design results and / or lines from the expansion elements 7, 21 to the evaporator 8 can be kept short.
  • Fig. 10 shows the corresponding conditions for a control (which also includes a regulation) of a predetermined temperature in the centrifuge chamber 12, which is not the Provision of the maximum cooling capacity required.
  • a control which also includes a regulation
  • a time offset 49 can be used for switching from the OFF operating state 46 in the ON operating state 45, wherein preferably then the downshift from the ON operating state 45 to the OFF operating state 46 takes place without time offset 49 ,
  • the switching of the two refrigeration circuits 14, 15 with the same frequency, but for the illustrated embodiment in view of the time offset 49 of the ON operating state 45 for the secondary refrigeration circuit 15 is longer than for the primary refrigeration cycle fourteenth (without this being absolutely necessary).
  • Fig. 11 shows a modified temperature control in which the primary refrigeration cycle 14 is permanently switched to the ON operating state 45, so that this provides a permanent heat sink.
  • the control of the centrifuge chamber 12 supplied cold is controlled only via the decrease in the cold of the primary refrigeration cycle 14 through the secondary refrigeration circuit 15 by switching on and off the secondary refrigeration circuit 15 between the ON operating state 45 and as needed OFF operating state 46 takes place, in which case for controlling or regulating the temperature in the centrifuge chamber 12 and thus the centrifugal chamber 12 supplied cold influence is taken on the ratio of the periods of the ON operating states and the OFF operating states.
  • the indices refer to the states (I) to (VIII) of the refrigerants in the refrigeration circuits 14, 15, as in the Fig. 3 and 4 be used.
  • HD denotes the high-pressure circuit 24
  • ND denotes the low-pressure circuit 25.
  • an evaporator 8 (and a heat exchanger formed therewith) may extend inside a security element 26 or safety boiler 27, in a wall of the security element 26 or safety boiler 27 itself or outside the security element 26 or safety boiler 27.
  • a line forming the evaporator 8 may extend in the circumferential direction of a safety boiler 27 or be integrated into the safety boiler 27 itself.
  • the primary refrigeration cycle 14 and the secondary refrigeration cycle 15 can both be arranged inside or outside a safety boiler 27.
  • a safety wall is used, which at least partially the subspaces 30, 31 can separate from each other.
  • the secondary refrigeration cycle 15 may be arranged in a space between the safety boiler 27 and the safety wall, while the primary refrigeration cycle 14 is then arranged on the side facing away from the safety boiler 27 of the safety wall.
  • the safety boiler 27 is double-walled and the secondary refrigeration circuit 15 extends at least partially and in the region of the evaporator 8 in a space between the double walls of the safety boiler 27.

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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)
EP17200209.9A 2017-11-06 2017-11-06 Centrifugeuse Active EP3479903B1 (fr)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021000600A1 (fr) * 2019-07-04 2021-01-07 深圳市瑞沃德生命科技有限公司 Système de réfrigération
CN114226074A (zh) * 2021-11-30 2022-03-25 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
EP4160109A1 (fr) * 2021-09-30 2023-04-05 Thermo Electron LED GmbH Système de refroidissement et appareil de laboratoire doté d'un système de refroidissement
DE102021126963A1 (de) 2021-10-18 2023-04-20 Thermo Electron Led Gmbh Kühlsystem
WO2024008230A1 (fr) * 2022-07-05 2024-01-11 Rittal Gmbh & Co. Kg Dispositif de refroidissement pour commande de température d'armoire de commande et ensemble armoire de commande correspondant

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012002593A1 (de) 2012-02-13 2013-08-14 Eppendorf Ag Zentrifuge mit Kompressorkühleinrichtung und Verfahren zur Steuerung einer Kompressorkühleinrichtung einer Zentrifuge
EP2910870A1 (fr) * 2012-09-21 2015-08-26 Mitsubishi Electric Corporation Dispositif de réfrigération et son procédé de commande
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
DE102014107294B4 (de) 2014-05-23 2017-02-09 Andreas Hettich Gmbh & Co. Kg Zentrifuge

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012002593A1 (de) 2012-02-13 2013-08-14 Eppendorf Ag Zentrifuge mit Kompressorkühleinrichtung und Verfahren zur Steuerung einer Kompressorkühleinrichtung einer Zentrifuge
EP2910870A1 (fr) * 2012-09-21 2015-08-26 Mitsubishi Electric Corporation Dispositif de réfrigération et son procédé de commande
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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021000600A1 (fr) * 2019-07-04 2021-01-07 深圳市瑞沃德生命科技有限公司 Système de réfrigération
EP4160109A1 (fr) * 2021-09-30 2023-04-05 Thermo Electron LED GmbH Système de refroidissement et appareil de laboratoire doté d'un système de refroidissement
DE102021126963A1 (de) 2021-10-18 2023-04-20 Thermo Electron Led Gmbh Kühlsystem
CN114226074A (zh) * 2021-11-30 2022-03-25 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
WO2024008230A1 (fr) * 2022-07-05 2024-01-11 Rittal Gmbh & Co. Kg Dispositif de refroidissement pour commande de température d'armoire de commande et ensemble armoire de commande correspondant

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