EP2814617A2 - Zentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer zentrifuge - Google Patents
Zentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer zentrifugeInfo
- Publication number
- EP2814617A2 EP2814617A2 EP13705913.5A EP13705913A EP2814617A2 EP 2814617 A2 EP2814617 A2 EP 2814617A2 EP 13705913 A EP13705913 A EP 13705913A EP 2814617 A2 EP2814617 A2 EP 2814617A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- centrifuge
- temperature
- evaporator
- controllable
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 66
- 238000000034 method Methods 0.000 title claims abstract description 21
- 238000005057 refrigeration Methods 0.000 claims abstract description 36
- 239000003507 refrigerant Substances 0.000 claims description 38
- 230000001276 controlling effect Effects 0.000 claims description 14
- 230000033228 biological regulation Effects 0.000 claims description 10
- 238000002347 injection Methods 0.000 claims description 9
- 239000007924 injection Substances 0.000 claims description 9
- 230000001105 regulatory effect Effects 0.000 claims description 8
- 238000013021 overheating Methods 0.000 description 9
- 230000008901 benefit Effects 0.000 description 5
- 238000011161 development Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000003570 air Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- ONPGOSVDVDPBCY-CQSZACIVSA-N 6-amino-5-[(1r)-1-(2,6-dichloro-3-fluorophenyl)ethoxy]-n-[4-(4-methylpiperazine-1-carbonyl)phenyl]pyridazine-3-carboxamide Chemical compound O([C@H](C)C=1C(=C(F)C=CC=1Cl)Cl)C(C(=NN=1)N)=CC=1C(=O)NC(C=C1)=CC=C1C(=O)N1CCN(C)CC1 ONPGOSVDVDPBCY-CQSZACIVSA-N 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000005119 centrifugation Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000012804 iterative process Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000004622 sleep time Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- 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 centrifuge according to the preamble of claim 1 and a method for controlling and regulating the compressor cooling device of a centrifuge according to the preamble of claim 5.
- a compressor cooling device with pipes and heat exchangers is often provided, by means of which a special refrigerant (in contrast to "coolants", as used for example for the cooling water circuit of cars, a refrigerant passes through during the passage through the refrigeration cycle phase changes, namely usually of liquid After gaseous, and with such a refrigerant is also a temperature of a chilled goods, which has a temperature below the ambient temperature, possible) via pipes (form the refrigeration cycle), for example, spirally against the centrifuge, ie the side walls and the bottom of the boiler in which the boiler is passed to carry off heat, by means of such a compressor cooling device Also, a cooling of the sample to a temperature below the temperature of the ambient air possible.
- a special refrigerant in contrast to "coolants", as used for example for the cooling water circuit of cars, a refrigerant passes through during the passage through the refrigeration cycle phase changes, namely usually of liquid After gaseous, and with such a refrigerant is also a temperature of a chilled goods
- Such compressor cooling devices 1 have an evaporator 3, which is generally guided around the centrifuge vessel 5 in a tubular manner, a compressor 7, a condenser 9 and an expansion element 11 (see FIG. 1).
- the expansion element 1 1 is on the largest possible load case, so the maximum speed of the centrifuge rotor (not shown), designed, it is already known that the expander (pressure compensation element between high and low pressure side of the refrigeration cycle at standstill of the compressor) as a capillary tube or thermostatic injector 1 1 is formed.
- this thermostatic injection valve (TEV) 11 is used to independently increase or restrict the refrigerant inflow in the refrigeration circuit 15 as a function of the determined temperature at the evaporator inlet VE.
- this thermostatic injection valve (TEV) 11 is used to independently increase or restrict the refrigerant inflow in the refrigeration circuit 15 as a function of the determined temperature at the evaporator inlet VE.
- an overheating of the refrigerant at the evaporator outlet VA is required, so that an overpressure is formed, which is passed directly to a spring 17 of the thermostatic injector 1 1 to actuate this.
- the sensor 13 of the TEV 1 1 is fixed, in which a refrigerant is contained. Due to the temperature at the evaporator outlet VA, the refrigerant has a corresponding pressure, which then affects the TEV 1 1 and the counterforce of the spring and thus the TEV 1 1 opens or closes.
- the evaporator output can not be fully utilized, with only about 95% of the evaporator surface being usable. Due to the required overheating, there is a temperature difference of approximately 7 K between the evaporator inlet VE and the evaporator outlet VA.
- a further disadvantage is that shocks occur when the compressor 7 starts or stops. These vibrations influence the operating behavior of the centrifuge, increase the backmixing rate in the rotor after standstill of the centrifuge and have effects on adjacently placed laboratory equipment and the like.
- the object of the present invention is to remedy or mitigate these disadvantages.
- the centrifuge should be constructed with the compressor cooling device simple and inexpensive, have a high control quality and cause less vibration.
- the centrifuge according to the invention in particular laboratory centrifuge, has a centrifuge vessel and a compressor cooling device with a refrigeration cycle, an evaporator, a compressor and a condenser and is characterized in that at least one controllable throttle device for controlling the refrigerant flow is provided in the refrigeration cycle, preferably as electronic injection valve is formed.
- the controllable throttle device also acts as a pressure compensation element between the high and low pressure side of the refrigeration cycle at standstill of the compressor.
- a controllable, ie externally controllable throttle device in the context of the present invention is understood to mean a throttle device in which a direct external control possibility exists to regulate the refrigerant flow, that is to say an actuator that can be influenced outside of the refrigeration circuit.
- the control option according to the invention is electrically, but also hydraulic and / or pneumatic control options or the like. Possible.
- Thermostatic injection valves are therefore not controllable throttle devices in the context of the present invention, since in them no direct external influence can be made, but react passively these elements to a temperature-related increase in pressure against a spring.
- the compressor cooling device of the centrifuge has a controllable throttle device in the refrigeration cycle
- the compressor cooling device can be controlled directly for many load cases without having to regulate the compressor itself.
- the compressor cooling device is much less source of vibration and also has a longer life.
- it is no longer necessary to allow overheating of the refrigerant which is why the full evaporator length can be exploited.
- the heat transfer surface of the evaporator is increased, whereby a higher cooling capacity is achieved and overall the efficiency of the cooling device is improved.
- This makes it possible to achieve lower cooling temperatures in the centrifuge vessel and / or to set the desired lower cooling temperatures even for higher centrifuge capacities.
- the desired temperature in the centrifuge vessel can be reached faster.
- Deviations from a desired setpoint can be achieved.
- At least one means for detecting the temperature of the refrigerant in the refrigeration cycle and / or for detecting the temperature in the centrifuge vessel is provided.
- means for detecting the temperature in the centrifuge vessel means for detecting the temperature of the refrigerant in the refrigeration cycle upstream of the evaporator, preferably at the evaporator inlet, and a means for Detecting the temperature after the evaporator are provided.
- the arrangement location for the latter agent is preferably the evaporator outlet, because otherwise the temperature may possibly only be measured inaccurately due to overheating at a point further in the direction of the compressor and thus no optimal utilization of the evaporator would be ensured. This allows a much more precise control.
- means for recording the temperature are all means which determine a physical parameter by means of which the temperature can be determined, for example pressure or temperature sensors, whereby temperature sensors are more cost-effective and are therefore preferred.
- the compressor for controlling its delivery rate is controllable, preferably power controlled, in particular designed frequency controllable, which in particular for the start of the compressor cooling device with a relation to the mains frequency increased frequency, the settling time is significantly shortened until reaching the desired temperature.
- a bypass can be provided in the refrigeration cycle for bridging the condenser, which is designed in particular controllable.
- a controllable throttle device for this regulation can also be used.
- Controllable throttle devices according to the present invention can be designed both as continuously variable throttle valves and as discretely adjustable throttle valves.
- the possible actuators are designed as a continuously adjustable throttle device, compressor with continuously adjustable flow rate, continuously adjustable bypass valve, the coverage of the entire load spectrum can be ensured very efficient and fast response without performance leaps.
- control means which are designed in particular as programmable electronics (eg microcontrollers), which use at least one of the detected temperatures as an input variable and control and regulate at least one of the elements controllable throttle device, controllable bypass and controllable compressor, because then particularly effective Control and regulation routines can be used.
- programmable electronics eg microcontrollers
- Independent protection is claimed for the inventive method for controlling and / or regulating the compressor cooling device of a centrifuge with a centrifuge vessel, wherein the compressor cooling device comprises a refrigeration cycle, an evaporator, a compressor and a condenser and is characterized in that a controllable throttle device for controlling the flow of refrigerant is used in the refrigeration cycle of the compressor cooling device.
- the centrifuge according to the invention is used.
- a setpoint temperature of the centrifuge tank of the centrifuge is specified and the actual temperature of the centrifuge tank of the centrifuge is determined.
- the tendency of the actual temperature for a predetermined tendency period is preferably determined in order to be able to react faster to temperature changes and to minimize fluctuations around the desired value.
- the tendency period is preferably at least 2 s, preferably at least 5 s, in particular at least 10 s.
- this can also be appropriate deviations, which are derived from the size and performance of the overall system centrifuge.
- a tolerance range is set around the predetermined desired temperature, which is at most +/- 5 K, preferably at most +/- 3 K and in particular +/- 1.5 K. Then, the control can be significantly improved if the actual temperature is controlled by the controllable throttle device only if it is within the specified tolerance range. "Within” the tolerance range here means that the temperatures of the edges of the tolerance range are also detected, and the control is improved if the actual temperature is only controlled via the compressor when the actual temperature is higher. Temperature is not within the tolerance range.
- a controllable compressor is used for the control outside the tolerance range (coarse regulation).
- the compressor is controlled by the actual temperature measured in the centrifuge tank in such a way that the actual temperature returns to the tolerance range.
- the combination of coarse and fine control (see below), the efficiency of the compressor is used particularly advantageously and at the same time a switching off and on again of the compressor in the low load range, especially at high Kesselin nentemperaturen, largely prevented because the compressor is used essentially only for the regulation of the actual temperature up to the tolerance range.
- the controllable throttle device is particularly preferably adjusted to an empirically determined refrigerant flow, and the actual temperature is lowered to the predetermined tolerance range by means of the compressor.
- a position of the controllable throttle device determined to be optimal for the respective centrifuge should be used for maximum cooling and, if appropriate, adjusted later to a position corresponding to the optimum evaporator filling.
- the compressor is adjusted only over such a period until the actual temperature for an empirically determined period, advantageously a multiple, preferably 40 times, most preferably 26 times and especially 12 times the trend period, for example for at least 2 min , is within the tolerance range, according to which it is then provided in particular that the compressor power is kept constant, and as long as the actual temperature is within the tolerance range and is controlled to the target temperature via the controllable throttle device.
- the power of the compressor and / or the flow of refrigerant can be controlled by the controllable throttle device accordingly.
- a Vorabschaltwert 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 currently very rapidly strives for the desired temperature value from the positive temperature range.
- the Vorabschaltwert is introduced, that is, before the actual target temperature value, preferably located in the middle of the tolerance range, is reached by the actual temperature value, for example, the compressor already down or shut down or the controllable throttle device is pressed in the direction of closing. It is therefore a counter-regulation against the inertia of the system.
- the temperature of the refrigerant in the refrigeration cycle is determined firstly before the evaporator, preferably at the evaporator inlet, and secondly after 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 between 0 K and 5 K, preferably between 0 K and 3 K, in particular between 0 K and 1 K.
- the temperature of the refrigerant is determined in the refrigeration cycle before the evaporator and falls below a predetermined temperature, at least by one of the following measures, this predetermined temperature is at least achieved again: i) lowering the flow rate of the compressor, ii) switching on and Controlling a bypass bypassing the condenser in the refrigeration cycle; and iii) controlling the variable throttle device to increase the refrigerant flow in the refrigeration cycle of the compressor cooler.
- the predetermined temperature is dependent 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 causing oil return to fail. Therefore, in variant iii) when a temperature falls below a predetermined temperature, the throttle device must be opened again.
- FIG. 1 shows the block diagram of a compressor cooling device according to the prior art
- FIG. 2 shows the centrifuge according to the invention in a top view
- FIG 3 shows the block diagram of the compressor cooling device of the centrifuge according to the invention
- FIG. 4 shows the block diagram of the control according to the method according to the invention
- FIG. 5 shows the comparison of the maximum cooling power of two centrifuges with compressor cooling device according to the prior art with TEV and the compressor cooling device with EEV used according to the invention.
- the centrifuge 20 according to the invention is shown purely schematically in a perspective plan 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 lid 23 for the centrifuge vessel 37 and rotor 28 and a bottom plate 29.
- the inventive compressor cooling device 30 has a frequency-controllable compressor 3 1, a condenser 33, an evaporator 35, which is arranged for indirect cooling around a centrifuge vessel 37, and a relaxation element 39.
- TEV 1 has a thermostatic injection valve (TEV), which has a pressure input 17, which communicates with a sensor 13 at the output VA of the evaporator 3.
- TEV thermostatic injection valve
- a pressure input 17 which communicates with a sensor 13 at the output VA of the evaporator 3.
- an overpressure which acts against the pressure of a spring of the TEV 1 1 and this opens.
- the TEV 1 1 is therefore only element of a passive control, since there is no external controllability, for example via an electronics, and it is not possible due to the overheating to fully exploit the evaporator.
- the compressor cooling device 30 shown in FIG. 3 has a controllable throttle device 39 in the form of an electronic injection valve (EEV) 39 instead of the TEV.
- 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.
- continuously adjustable actuators 39, 45 may alternatively be provided discrete actuators.
- three means 47, 49, 51 for detecting the temperature T V E before the evaporator 35, for detecting the temperature T VA at the output VA of the evaporator 35 and for detecting the temperature T in the centrifuge vessel 37 are provided.
- a control means 60 which takes into account the setpoint temperature T K set by the operator for the centrifuge vessel.
- the temperature T V E at the input VE and the temperature T V A at the output VA are detected at the evaporator 35 and fed to the control means 60.
- the actual temperature T is removed from the boiler 37 and fed to the control means 60.
- td the average temperature of 10 s, both longer and shorter periods are possible.
- the tendency of the temperature development of the actual temperature T is determined.
- a tolerance range of +/- 1.5 K set for the target temperature T K for the centrifuge vessel 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 lowered to the predetermined tolerance range by controlling the rotational speed of the compressor 31.
- the speed of the compressor 31 is either kept maximum or, if a certain cooling time is desired to the target temperature T K , be kept at a corresponding value.
- a pre-shift time may be used to account for the inertia of the compressor cooler 30, and / or the speed of the compressor 31 may be lowered by an empirically determined function during coarse control.
- an optimal position of the controllable throttle device 39 for the respective centrifuge 20 should be used for maximum cooling and, if appropriate, adjusted later to a position corresponding to the optimum evaporator filling.
- the coarse control by means of compressor speed is carried out until the actual temperature T in the boiler 37 lingers in the tolerance range for a defined period of time (eg 1 min).
- a defined period of time eg 1 min.
- the power of the compressor 31 is reduced by reducing the frequency, and that until the actual temperature T reaches or exceeds the target temperature T K again.
- the frequency of the compressor 31 is raised again. This iterative process is continued until the actual temperature T for a period of, for example, at least 1 min, ie 6 tendency periods td within the tolerance range of the target temperature T K moves.
- the compressor speed is then kept constant, as long as the actual temperature is within the tolerance range and the desired temperature is controlled by 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 to optimally utilize the control capacity of the throttle device 39 during the fine control can. It is essential, however, that during the fine control, ie the time in which the actual temperature T is within the tolerance range, no change in the power of the compressor 31 takes place.
- the cooling capacity is controlled only via the EEV 39 alone.
- the present invention is not limited to that the coarse control (control via the compressor alone) and the fine control (control by the throttle device alone) are performed separately from each other. It can also be provided that an overlap takes place, that is, a simultaneous control of compressor and throttle device.
- a fixed lower limit T V Emin the temperature T VE at the input VE of the evaporator 35 is monitored and falls below this temperature T V Emin the EEV 39 is further opened until the determined temperature T VE is again greater than the predetermined temperature T V Emin- This prevents the compressor 31 is in the vacuum range.
- the difference between the 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 maximum, and on the other hand to prevent liquid refrigerant from entering the compressor 31, If this difference T VA - T VE is exceeded , the EEV 39 is further closed or / and the compressor frequency is reduced.
- the evaporator can be utilized to the maximum.
- the cooling capacity of the evaporator can be increased and thus in the case of the centrifuge 20 according to the invention about 5% more heat compared to previously known compressor cooling devices are removed, whereby the power of the rotor of the centrifuge can be raised accordingly. In extreme cases, therefore, a 5% higher heat generation by the rotor is allowed and this can thus be operated in a higher speed range, whereby the centrifuging power is increased.
- the samples can thus be kept substantially more accurately at a specific temperature, which is of great advantage, in particular, in the case of sensitive samples or problematic temperature influences.
- Compressor starts less, minimizing the number of load peaks in the grid and consumption
- Compressor can be operated at the optimum operating point, more often at low speed, which reduces working noise
- Low pressure side reduces the starting currents of the compressor. It is possible to selectively open the EEV when the compressor is at a standstill in order to and low-pressure side to accelerate and thus to achieve a higher control quality in the low load range
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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)
Abstract
Description
Claims
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 true EP2814617A2 (de) | 2014-12-24 |
EP2814617B1 EP2814617B1 (de) | 2020-01-22 |
Family
ID=48868130
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13705913.5A Active EP2814617B1 (de) | 2012-02-13 | 2013-02-13 | Laborzentrifuge mit kompressorkühleinrichtung und verfahren zur steuerung einer kompressorkühleinrichtung einer laborzentrifuge |
Country Status (7)
Country | Link |
---|---|
US (1) | US10449556B2 (de) |
EP (1) | EP2814617B1 (de) |
JP (1) | JP6329910B2 (de) |
CN (1) | CN104203422B (de) |
DE (1) | DE102012002593A1 (de) |
PL (1) | PL2814617T3 (de) |
WO (1) | WO2013120604A2 (de) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 (de) * | 2014-10-29 | 2016-05-04 | Eppendorf Ag | Zentrifuge mit einem Kompressorkühlkreislauf und Verfahren zum Betrieb einer Zentrifuge mit einem Kompressorkühlkreislauf |
US10415891B2 (en) * | 2016-02-22 | 2019-09-17 | Kabushiki Kaisha Toyota Chuo Kenkyusho | Heat exchanger and heat storage system |
CN107752587A (zh) * | 2016-08-16 | 2018-03-06 | 开利公司 | 制冷展示柜、制冷系统及恒温控制方法 |
EP3479903B1 (de) | 2017-11-06 | 2020-09-16 | Sigma Laborzentrifugen GmbH | Zentrifuge |
DE102017130785A1 (de) * | 2017-12-20 | 2019-06-27 | Eppendorf Ag | Temperierte Zentrifuge |
CN108981969B (zh) * | 2018-06-07 | 2023-07-25 | 浙江大学 | 真空环境下土工离心机空气摩擦产热量测试装置及方法 |
DE102018114450A1 (de) * | 2018-06-15 | 2019-12-19 | Eppendorf Ag | Temperierte Zentrifuge mit Crashschutz |
CN110565317B (zh) * | 2019-08-27 | 2022-03-15 | 亳州樰骏纺织有限公司 | 一种化纤面料熨烫装置 |
CN111832189B (zh) * | 2020-07-24 | 2021-09-14 | 重庆通用工业(集团)有限责任公司 | 一种离心式蒸汽压缩机选型方法 |
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-
2012
- 2012-02-13 DE DE102012002593A patent/DE102012002593A1/de not_active Withdrawn
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2013
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- 2013-02-13 WO PCT/EP2013/000415 patent/WO2013120604A2/de active Application Filing
- 2013-02-13 CN CN201380018633.9A patent/CN104203422B/zh active Active
- 2013-02-13 JP JP2014555980A patent/JP6329910B2/ja active Active
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2014
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Non-Patent Citations (1)
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WO2013120604A2 (de) | 2013-08-22 |
EP2814617B1 (de) | 2020-01-22 |
CN104203422A (zh) | 2014-12-10 |
PL2814617T3 (pl) | 2020-07-27 |
WO2013120604A3 (de) | 2013-12-19 |
CN104203422B (zh) | 2017-12-29 |
US20150080202A1 (en) | 2015-03-19 |
US10449556B2 (en) | 2019-10-22 |
DE102012002593A1 (de) | 2013-08-14 |
JP6329910B2 (ja) | 2018-05-23 |
JP2015513447A (ja) | 2015-05-14 |
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