EP2814617B1 - Laborzentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer laborzentrifuge - Google Patents

Laborzentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer laborzentrifuge Download PDF

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Publication number
EP2814617B1
EP2814617B1 EP13705913.5A EP13705913A EP2814617B1 EP 2814617 B1 EP2814617 B1 EP 2814617B1 EP 13705913 A EP13705913 A EP 13705913A EP 2814617 B1 EP2814617 B1 EP 2814617B1
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EP
European Patent Office
Prior art keywords
compressor
temperature
actual temperature
centrifuge
controllable
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Active
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EP13705913.5A
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German (de)
English (en)
French (fr)
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EP2814617A2 (de
Inventor
Heiko Müller
Sven Fischer
Dieter Wolf
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Eppendorf SE
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Eppendorf SE
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Priority to PL13705913T priority Critical patent/PL2814617T3/pl
Publication of EP2814617A2 publication Critical patent/EP2814617A2/de
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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to a laboratory centrifuge according to claim 1 and a method for controlling and regulating the compressor cooling device of a centrifuge according to claim 9.
  • centrifugation especially in very fast rotating laboratory centrifuges, heat is generated during the rotation of the centrifuge rotor in the centrifuge bowl by air friction and the introduction of electrical power loss. Since the centrifuge bowl is closed with a lid to prevent the centrifuging material from escaping, this heat input cannot be dissipated easily and leads to an increase in the temperature of the centrifuging material.
  • a compressor cooling device with pipes and heat exchangers is often provided, by means of which a special refrigerant (in contrast to "coolants", such as those used for the cooling water circuit of cars, for example), a refrigerant undergoes phase changes during the passage through the refrigeration cycle, namely usually of liquid after gaseous, and with such a refrigerant it is also possible to temper a refrigerated product which has a temperature below the ambient temperature) via pipes (which form the refrigeration cycle), which, for example, are in a spiral shape against the centrifuge bowl, i.e. the side walls and the bottom of the bowl , is led past the boiler to remove heat.
  • a special refrigerant in contrast to "coolants”, such as those used for the cooling water circuit of cars, for example
  • a refrigerant undergoes phase changes during the passage through the refrigeration cycle, namely usually of liquid after gaseous, and with such a refrigerant it is also possible to temper a refrigerated product which has a temperature below the ambient
  • compressor cooling device cooling of the sample to a temperature below the temperature of the ambient air is also possible.
  • Such laboratory centrifuges are for example DE 38 18 584 A1 or JP 2011 255330 A known.
  • Compressor cooling devices 1 of this type have an evaporator 3, which is usually guided around the centrifuge bowl 5 in a tubular manner, a compressor 7, a condenser 9 and a expansion element 11 (cf. Fig. 1 ).
  • the expansion element 11 is designed for the greatest possible load case, i.e. the maximum speed of the centrifuge rotor (not shown), it being known that the expansion device (pressure compensation element between the high and low pressure sides of the refrigeration circuit when the compressor is at a standstill) as a capillary tube or thermostatic injection valve 11 is trained.
  • this thermostatic injection valve (TEV) 11 is used to independently increase or reduce the inflow of refrigerant in the refrigeration circuit 15 depending on the temperature determined at the evaporator inlet VE.
  • this thermostatic injection valve (TEV) 11 is used to independently increase or reduce the inflow of refrigerant in the refrigeration circuit 15 depending on the temperature determined at the evaporator inlet VE.
  • an overheating of the refrigerant at the evaporator outlet VA is necessary, so that an overpressure arises which is passed directly to a spring 17 of the thermostatic injection valve 11 in order to actuate it.
  • the sensor 13 of the TEV 11 in which a refrigerant is contained, is attached to the evaporator outlet VA. Due to the temperature at the evaporator outlet VA, the refrigerant has a corresponding pressure, which then affects the TEV 11 and the counterforce of the spring and thus opens or closes the TEV 11.
  • Another load element which is a frequency-controlled compressor 7, for example, can be used to control other load cases partially, but mostly only inaccurately.
  • compressors 7 usually have a minimum runtime in order to ensure the internal oil circuit.
  • compressors 7 usually have a minimum runtime in order to ensure the internal oil circuit.
  • Another disadvantage is that vibrations occur when the compressor 7 of a compressor cooling device 1 starts or stops. These vibrations influence the operating behavior of the centrifuge, increase the backmixing rate in the rotor after the centrifuge has come to a standstill and have effects on laboratory equipment and the like placed in the vicinity.
  • the compressor 7 is shortened by frequently switching the compressor on and off.
  • the object of the present invention is to remedy or alleviate these disadvantages mentioned.
  • the centrifuge with the compressor cooling device should be simple and cost-effective, have a high control quality and cause less vibrations.
  • the centrifuge according to the invention in particular a laboratory centrifuge, has a centrifuge bowl and a compressor cooling device with a refrigeration circuit, an evaporator, a compressor and a condenser and is characterized in that at least one controllable throttle device for regulating the refrigerant flow is provided in the refrigeration circuit, which is preferably used as electronic injection valve is formed. It can expediently be provided that the controllable throttle device also acts as a pressure compensation element between the high and low pressure side of the refrigeration circuit when the compressor is at a standstill.
  • an externally controllable throttle device is understood to be a throttle device in which there is a direct external control option for regulating the refrigerant flow, that is to say an actuator that can be influenced from outside the refrigeration circuit.
  • a direct external control option for regulating the refrigerant flow that is to say an actuator that can be influenced from outside the refrigeration circuit.
  • the control option according to the invention is preferably electrical, but hydraulic and / or pneumatic control options or the like are also possible.
  • Thermostatic injection valves are therefore not controllable throttle devices in the sense of the present invention, since they cannot be directly influenced externally, but rather these elements react passively to a temperature-related pressure increase with respect to a spring.
  • the compressor cooling device of the centrifuge has a controllable throttle device in the refrigeration circuit, the compressor cooling device can be controlled directly for many load cases without having to regulate the compressor itself.
  • the compressor cooling device is therefore much less a source of vibrations and also has a longer service life.
  • the heat transfer area of the evaporator is increased, as a result of which a higher cooling capacity is achieved and the overall efficiency of the cooling device is improved. In this way, lower cooling temperatures can be achieved in the centrifuge bowl and / or the desired lower cooling temperatures can also be set for higher centrifuge outputs.
  • the desired temperature in the centrifuge bowl can be reached more quickly.
  • a compressor with a lower capacity can be used, which reduces the installation space required, or a frequency-controllable compressor can be operated at a lower frequency, i.e. with a lower capacity, as a result of which the overall energy requirement for the same cooling capacity can be reduced ,
  • the accuracy of the control is increased, which is why smaller deviations from a desired setpoint can be achieved.
  • At least one means for detecting the temperature of the refrigerant in the refrigeration cycle is provided.
  • a means for detecting the temperature in the centrifuge bowl is provided.
  • a means for detecting the temperature of the refrigerant in the refrigeration circuit upstream of the evaporator, preferably at the evaporator inlet, and a means for Detection of the temperature after the evaporator are provided.
  • the location for the latter means is preferably the evaporator outlet, because otherwise the temperature can possibly only be measured imprecisely due to overheating at a point further in the direction of the compressor, and therefore optimal utilization of the evaporator would not be guaranteed. This enables a much more precise control.
  • “Means for detecting the temperature” are all means which determine a physical parameter by means of which the temperature can be determined. For example, they are pressure or temperature sensors, temperature sensors being less expensive and therefore being used with preference.
  • the compressor for controlling its delivery rate is designed to be controllable, preferably power-controllable, in particular frequency-controllable, so that, particularly for starting up the compressor cooling device with a frequency that is higher than the mains frequency, the settling time is substantially reduced until the desired temperature is reached.
  • a bypass can be provided in the refrigeration circuit to bypass the condenser, which is in particular designed to be controllable.
  • a controllable throttle device can also be used for this regulation.
  • Controllable throttle devices according to the present invention can be designed both as continuously adjustable throttle valves and as discretely adjustable throttle valves.
  • the possible actuators are designed as continuously adjustable throttle devices, compressors with continuously adjustable flow rates, continuously adjustable bypass valves, coverage of the entire load spectrum can be ensured very efficiently and quickly in an appealing manner without leaps in performance.
  • control means which are designed in particular as programmable electronics (e.g. microcontrollers), which use at least one of the recorded temperatures as an input variable and which control and regulate at least one of the elements controllable throttle device, controllable bypass and controllable compressor, because then particularly effective Control routines can be used.
  • programmable electronics e.g. microcontrollers
  • independent protection is claimed for the method according to the invention for controlling and / or regulating the compressor cooling device of a centrifuge with a centrifuge bowl, the compressor cooling device having a refrigeration cycle, an evaporator, a compressor and a condenser and being characterized in that a controllable throttle device for regulating the refrigerant flow is used in the refrigeration circuit of the compressor cooling device.
  • the centrifuge according to the invention is preferably used here.
  • a target temperature of the centrifuge bowl of the centrifuge is specified and the actual temperature of the centrifuge bowl of the centrifuge is determined.
  • the trend of the actual temperature is preferably determined for a predetermined trend period in order to be able to react more quickly to temperature changes and to minimize fluctuations around the setpoint value.
  • the trend period is preferably at least 2 s, preferably at least 5 s, in particular at least 10 s.
  • a tolerance range is defined around the predetermined target temperature, which is at most +/- 5 K, preferably at most +/- 3 K and in particular +/- 1.5 K. Then the regulation can be significantly improved if the actual temperature is only regulated by means of the controllable throttle device if it is within the defined tolerance range. This regulation is particularly sensitive. "Within” the tolerance range means here that the temperatures of the edges of the tolerance range are also recorded. In addition, the control is improved if the actual temperature is only controlled by the compressor if the actual temperature is not within the tolerance range.
  • a controllable compressor is used for the regulation outside the tolerance range (rough regulation).
  • the compressor is controlled by the actual temperature measured in the centrifuge bowl when the tolerance range is exited so that the actual temperature is again within the tolerance range.
  • the combination of coarse and fine control (see below), the performance of the compressor is used particularly advantageously and at the same time switching the compressor off and on again in the low-load range, especially at high internal boiler temperatures, largely prevented because the compressor is mainly used only for regulating the actual temperature up to the tolerance range.
  • the controllable throttle device when the compressor cooling device is started, the controllable throttle device is set to an empirically determined refrigerant flow and the actual temperature is reduced to the predetermined tolerance range by means of the compressor.
  • a position of the controllable throttle device that is determined as optimal for the respective centrifuge should be used for maximum cooling and, if necessary, adjusted later to a position corresponding to the optimal evaporator charge.
  • the compressor is only adjusted over such a period until the actual temperature is within the tolerance range for an empirically determined period, advantageously a multiple, preferably 40 times, most preferably 26 times and in particular 12 times, for example for at least 2 minutes , according to which it is then provided according to the invention that the compressor output is kept constant, for as long as the actual temperature is in the tolerance range and is regulated to the target temperature via the controllable throttle device. This ensures that when starting the refrigeration compressor device in a first step, only a coarse control takes place via the compressor and then a fine control via the controllable throttle device with constant compressor output.
  • the performance of the compressor and / or the refrigerant flow can also be regulated accordingly by the controllable throttle device.
  • a pre-switch-off value can be provided above the target temperature or the tolerance range. This takes into account the effect that, in such a control process, the actual temperature value is currently very rapidly striving for the target temperature value from the positive temperature range.
  • the pre-switch-off value is introduced, i.e. before the actual target temperature value, preferably in the middle of the tolerance range, is reached by the actual temperature value, for example the compressor already turned down or switched off or the controllable throttle device is actuated in the direction of closing. So this is a counter rule against the inertia of the system.
  • the temperature of the refrigerant in the refrigeration cycle is determined firstly upstream of the evaporator, preferably at the evaporator inlet, and secondly downstream of the evaporator, preferably at the evaporator outlet, and the controllable throttle device is controlled so that the difference in the temperature of the refrigerant in the refrigeration cycle before the evaporator and the temperature of the refrigerant in the refrigeration cycle after the evaporator is between 0 K and 5 K, preferably between 0 K and 3 K, in particular between 0 K and 1 K. (The specified range limits are permitted values.) This means that the evaporator is used particularly effectively since the temperature difference of approx.
  • the temperature of the refrigerant in the refrigeration circuit upstream of the evaporator is determined and if the temperature falls below a predetermined temperature at least by one of the following measures, this predetermined temperature is at least reached again: i) lowering the delivery rate of the compressor, ii) switching on and Regulating a bypass with which the condenser in the refrigeration circuit is bypassed and iii) controlling the controllable throttle device to increase the refrigerant flow in the refrigeration circuit of the compressor cooling device.
  • the predetermined temperature depends on the refrigerant used and the geometric relationships between the evaporator inlet and the compressor inlet and is, for example, -18 ° C. This effectively prevents the compressor from entering the vacuum area and the oil return failing. In variant iii), therefore, the throttle device must be opened again when the temperature falls below a predetermined value.
  • Fig. 2 the centrifuge 20 according to the invention is shown purely schematically in a perspective top view.
  • the centrifuge is designed as a laboratory centrifuge 20 and has a housing 21 with a cover (not shown) for the compressor cooling device 25 with the compressor 27, a cover 23 for the centrifuge bowl 37 and rotor 28 and a base plate 29.
  • the compressor cooling device 30 also has a frequency-controllable compressor 31, a condenser 33, an evaporator 35, which is arranged for indirect cooling around a centrifuge bowl 37, and a relaxation element 39.
  • the previously known compressor cooling device 1 has, as the expansion device 11, a thermostatic injection valve (TEV) which has a pressure inlet 17 which is connected to a sensor 13 at the outlet VA of the evaporator 3.
  • TEV thermostatic injection valve
  • the TEV 11 is therefore only an element of a passive control, since there is no external controllability, for example via electronics, and it is not possible to fully utilize the evaporator due to the overheating to be produced.
  • the in Fig. 3 shown compressor cooling device 30 instead of the TEV a controllable throttle device 39 in the form of an electronic injection valve (EEV) 39.
  • the refrigeration circuit 41 has a bypass 43 for bridging the condenser 33.
  • This bypass 43 is also provided with an electronic injection valve 45.
  • discrete actuators can alternatively also be provided.
  • three means 47, 49, 51 are provided for detecting the temperature T VE upstream of the evaporator 35, for detecting the temperature T VA at the outlet VA of the evaporator 35 and for detecting the temperature T in the centrifuge bowl 37.
  • a control means 60 which takes into account the target temperature T K for the centrifuge bowl set by an operator.
  • the temperature T VE at the inlet VE and the temperature T VA at the outlet VA are recorded on the evaporator 35 and fed to the control means 60.
  • the actual temperature T is taken from the boiler 37 and fed to the control means 60.
  • the tendency of the temperature development of the actual temperature T is determined over a trend period td of 10 s empirically determined for the centrifuge 20 constructed according to the invention, both longer and shorter periods being possible.
  • a tolerance range of +/- 1.5 K is established for the centrifuge bowl 37.
  • the control means 60 controls the EEV 39, the compressor 31 and possibly the bypass 45.
  • the EEV 39 is set to an empirically determined refrigerant flow and the actual temperature T is reduced to the predetermined tolerance range by controlling the speed of the compressor 31.
  • the speed of the compressor 31 is either kept at a maximum or, if a specific cooling time to the target temperature T K is desired, is kept at a corresponding value.
  • a pre-switch-off time can be used to take into account the inertia of the compressor cooling device 30 and / or the speed of the compressor 31 is reduced by means of an empirically determined function during the rough control.
  • a position of the controllable throttle device 39 which is determined as optimal for the respective centrifuge 20, should be used for maximum cooling and, if necessary, be subsequently adjusted to a position corresponding to the optimal evaporator charge.
  • the coarse control by means of the compressor speed is carried out until the actual temperature T in the boiler 37 remains in the tolerance range for a fixed period (for example 1 min). If the actual temperature T falls below the target temperature T K , the power of the compressor 31 is reduced by reducing the frequency until the actual temperature T reaches or exceeds the target temperature T K again. If the target temperature T K is exceeded, the frequency of the compressor 31 is raised again. This iterative process is continued until the actual temperature T is within the tolerance range of the target temperature T K for a period of at least 1 min, ie 6 tendency periods td.
  • the compressor speed is then kept constant, for as long as the actual temperature is within the tolerance range and the setpoint temperature is regulated via the controllable throttle device 39.
  • controllable throttle device 39 is set to a middle position and the speed of the compressor 31 is adjusted accordingly in order to be able to optimally utilize the control capacity of the throttle device 39 during the fine control. It is essential, however, that during the fine control, ie the time in which the actual temperature T is within the tolerance range, there is no change in the output of the compressor 31.
  • the cooling capacity is only controlled via the EEV 39 alone. Regulation is based on the tendency, i. H. If the tendency of the actual temperature T decreases in the trend period td, the EEV 39 is reduced, that is to say the refrigerant flow is reduced. In the event that the tendency increases, the electronic injection valve 39 is regulated upward, so that more refrigerant is supplied to the evaporator 35.
  • a defined lower limit T VEmin of the temperature T VE at the input VE of the evaporator 35 is monitored and if this temperature T VEmin is undershot , the EEV 39 is opened further until the temperature T VE determined is again greater than the temperature T VEmin specified therefor . This prevents the compressor 31 from getting into the vacuum range.
  • T VA - T VE the difference in temperatures T VA - T VE is constantly monitored. This should be in the range between 0 K and 1 K, on the one hand to keep the utilization of the evaporator 35 to a maximum, and on the other hand to prevent liquid refrigerant from getting into the compressor 31. If this difference falls below T VA - T VE , the EEV 39 is closed further and / or the compressor frequency is reduced.
  • the evaporator can be used to the maximum with the method according to the invention.
  • the cooling capacity of the evaporator can thus be increased and, in the case of the centrifuge 20 according to the invention, approximately 5% more heat can be dissipated compared to previously known compressor cooling devices, as a result of which the capacity of the rotor of the centrifuge can be increased accordingly. In extreme cases, a 5% higher heat generation by the rotor is permissible and it can be operated in a higher speed range, which increases the centrifuging performance.
  • Fig. 5 The advantageous effect of the centrifuge 20 according to the invention can be clearly seen in connection with the method according to the invention, it being provided for simplification that the compressor frequency was kept constant (maximum) over the entire running time and was regulated with the throttle device. It is very clear from the graphical representation of the courses of the actual temperature T that the control of the temperature of the boiler air according to the present invention takes place much more steadily and that a lower final temperature can be reached.
  • the samples can thus be kept much more precisely at a certain temperature, which is of great advantage particularly in the case of sensitive samples or problematic temperature influences.

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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)
EP13705913.5A 2012-02-13 2013-02-13 Laborzentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer laborzentrifuge Active EP2814617B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13705913T PL2814617T3 (pl) 2012-02-13 2013-02-13 Wirówka laboratoryjna ze sprężarkowym urządzeniem chłodniczym i sposób sterowania sprężarkowym urządzeniem chłodniczym wirówki laboratoryjnej

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US201261597916P 2012-02-13 2012-02-13
DE102012002593A DE102012002593A1 (de) 2012-02-13 2012-02-13 Zentrifuge mit Kompressorkühleinrichtung und Verfahren zur Steuerung einer Kompressorkühleinrichtung einer Zentrifuge
PCT/EP2013/000415 WO2013120604A2 (de) 2012-02-13 2013-02-13 Zentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer zentrifuge

Publications (2)

Publication Number Publication Date
EP2814617A2 EP2814617A2 (de) 2014-12-24
EP2814617B1 true EP2814617B1 (de) 2020-01-22

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EP13705913.5A Active EP2814617B1 (de) 2012-02-13 2013-02-13 Laborzentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer laborzentrifuge

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Country Link
US (1) US10449556B2 (ja)
EP (1) EP2814617B1 (ja)
JP (1) JP6329910B2 (ja)
CN (1) CN104203422B (ja)
DE (1) DE102012002593A1 (ja)
PL (1) PL2814617T3 (ja)
WO (1) WO2013120604A2 (ja)

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DE102018114450A1 (de) * 2018-06-15 2019-12-19 Eppendorf Ag Temperierte Zentrifuge mit Crashschutz
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WO2024002794A1 (de) 2022-06-30 2024-01-04 Sigma Laborzentrifugen Gmbh Zentrifuge, verfahren zum betrieb einer zentrifuge und computerlesbares medium

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EP2814617A2 (de) 2014-12-24
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WO2013120604A3 (de) 2013-12-19
WO2013120604A2 (de) 2013-08-22
CN104203422B (zh) 2017-12-29
DE102012002593A1 (de) 2013-08-14
JP6329910B2 (ja) 2018-05-23
US10449556B2 (en) 2019-10-22
PL2814617T3 (pl) 2020-07-27
US20150080202A1 (en) 2015-03-19

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