EP2828589B1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
EP2828589B1
EP2828589B1 EP13711051.6A EP13711051A EP2828589B1 EP 2828589 B1 EP2828589 B1 EP 2828589B1 EP 13711051 A EP13711051 A EP 13711051A EP 2828589 B1 EP2828589 B1 EP 2828589B1
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EP
European Patent Office
Prior art keywords
refrigerant
control
refrigerant compressor
refrigeration system
heat sink
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.)
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Application number
EP13711051.6A
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German (de)
English (en)
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EP2828589A1 (fr
Inventor
Birte MARGOTTI
Stephan Rölke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication of EP2828589A1 publication Critical patent/EP2828589A1/fr
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Classifications

    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B31/00—Compressor 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • 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
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • 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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor

Definitions

  • the invention relates to a refrigeration system comprising a refrigeration cycle in which a refrigerant compressor, a condenser following the refrigerant compressor, an expansion device following the condenser and an evaporator following the expansion device are arranged, which in turn is connected to the refrigerant compressor, wherein the refrigerant compressor by a an electronic engine control speed-controlled drive motor, and a refrigerant flow-through control cooling branch, which branches off from the refrigeration circuit between the condenser and the expansion device and is guided to a connection of the refrigerant compressor and in which a thermally conductive with electronic power components of the engine control heat sink is arranged, wherein a minimum evaporation temperature of the Heatsink is below a liquefaction temperature of the refrigerant in the condenser.
  • the invention is therefore based on the object to improve a refrigeration system of the generic type such that malfunctions of the engine control are avoided as possible.
  • the solution according to the invention provides that the temperature of the heat sink is at least at a settable by an evaporation pressure of the refrigerant in the heat sink minimum evaporation temperature or higher.
  • the minimum flow of refrigerant through the heat sink ensures that a cooling capacity control for the heat sink is functional even in the start-up phase and starts as soon as possible after switching on the refrigerant compressor.
  • control in the start-up phase allows a minimal flow of refrigerant through the control cooling branch, so that the entire control cooling branch is traversed by the minimum flow of refrigerant and thus, the temperature control provided for this in the cooling body receives the control activity.
  • the solution according to the invention provides that the setting of the evaporation pressure in the heat sink is effected by an evaporation pressure regulator.
  • control has an evaporation pressure regulator, which regulates an evaporation pressure in the cooling element so that it lies above a pressure at the connection of the refrigerant compressor to which the control cooling branch is connected.
  • Such an evaporation pressure regulator may be a mechanical evaporation pressure regulator.
  • the evaporation pressure regulator is an electrically or electronically operating evaporation pressure regulator which, for example, controls a control valve with pulse-width modulation in order to regulate the evaporation pressure.
  • the evaporation pressure regulator allows for the minimum refrigerant flow when switching on the refrigerant compressor in the start-up phase, that is, that the evaporation pressure regulator operates so that this allows in any case, the minimum refrigerant flow regardless of the intended control.
  • the evaporation pressure regulator is ineffective or limited in effect during the startup of the refrigerant compressor in the start-up phase.
  • Evaporative pressure control is of minor importance when starting up the refrigerant compressor in the start-up phase, as opposed to the minimum refrigerant flow required to assure power control of the heat sink.
  • Such a control inefficiency of the evaporation pressure regulator can be achieved, for example, in a mechanical evaporation pressure regulator or an electrically or electronically controlled evaporation pressure regulator, that the evaporation pressure regulator is assigned a bypass line with a throttle, wherein the throttle defines the minimum refrigerant flow, so that regardless of whether the evaporation pressure regulator works or not, the minimum refrigerant flow is ensured by the control cooling branch.
  • the evaporation pressure regulator comprises a control valve and a pressure control and that the pressure control in the start-up phase of the refrigerant compressor, the control valve so controls that it allows the minimum refrigerant flow primarily before the evaporation pressure control.
  • connection of the refrigerant compressor for the control cooling branch is not the connection of the refrigerant compressor, which is connected to the evaporator, but a connection of the refrigerant compressor, on a relative to the associated with the evaporator port higher pressure, for example an intermediate pressure of the refrigerant compressor is located.
  • the connection of the refrigerant compressor which is connected to the control cooling branch, leads into a closed compressor chamber of the screw compressor.
  • this solution has the advantage that a pressure level is thus already predetermined by the connection of the refrigerant compressor, which ensures a pressure level and thus a temperature in the heat sink, which is above the lowest possible temperature of the evaporator even with no existing control function of the evaporation pressure regulator.
  • control cooling branch comprises a thermostatic expansion valve upstream of the heat sink, which is controlled by a temperature sensor on the heat sink.
  • the temperature sensor could be provided centrally or in the course of a cooling channel in the heat sink.
  • the temperature sensor is arranged at an output terminal of the heat sink.
  • the expansion valve is associated with a bypass line with a throttle.
  • Such a bypass line for the expansion valve makes it possible to flow a minimal refrigerant flow through the heat sink even with the expansion valve closed in the start-up phase and thus, for example, build up an evaporation pressure, which causes the evaporation pressure regulator comes into action and thus also the minimum flow of refrigerant in the start-up phase, regardless of whether the expansion valve already regulates or not.
  • This minimum refrigerant flow through the heat sink ensures that when the heat sink heats up, the expansion valve can react quickly to prevent overheating of the heat sink and thus overheating of the electronic power components.
  • An exemplary embodiment of a refrigerant compressor 10 used according to the invention is designed as a screw compressor, as described, for example, in the German patent applications DE 198 45 991 A1 or DE 103 59 032 A1 is described.
  • Such a screw compressor comprises, for example, a first screw rotor 12 and a second screw rotor 14, which are each rotatably arranged in screw rotor bores 16 and 18 of a screw compressor housing 20 and engage with their peripheral screw contours 22 and 24, wherein the screw contours 22 and 24 in the region of a suction side arranged inlet window 26 form at least partially open compression chambers and subsequent to the inlet window 26 closed and increasingly reduced volume compressor chambers form, which in turn in the region of an outlet window 28, the pressure side of the screw rotors 16 and 18 is arranged to open in this.
  • inlet connection AE to which refrigerant with the suction pressure is supplied
  • intermediate pressure connection AZ1 to which refrigerant with the intermediate pressure PZ1 can be supplied
  • intermediate pressure connection AZ2 to which refrigerant with the intermediate pressure PZ2 can be supplied
  • outlet port AA at which refrigerant at the outlet pressure PA exits.
  • one of the screw rotors can be driven by a drive motor 30, which can be controlled by a motor controller 32 in a speed-controlled manner, the motor controller 32 being driven as in FIG Fig. 2 an electronic speed control 34 includes, for example, an inverter, which has highly temperature-loaded electronic power components 36 which have a high heat development in the operation of the drive motor 30 with the motor controller 32, and show a shortened life in excess of heating during operation of the drive motor 30 ,
  • the heat sink 40 is provided with an input port 42 and an outlet port 44 for a refrigerant, and between the input port 42 and the output port 44 extends in the heat sink 40, a refrigerant flow-through cooling channel 46, such extends in the heat sink 40 that the cooling body 40 can be cooled substantially uniformly with the refrigerant, in particular, the cooling channel 46 is such that optimal heat dissipation of thermally coupled to the heat sink 40 electronic power components 36 via the flowing through the cooling channel 46 refrigerant possible is.
  • FIG Fig. 3 shown in FIG Fig. 3 is the refrigerant compressor according to Fig. 1 arranged in a designated as a whole with 50 refrigeration cycle, wherein an output terminal AA of the refrigerant compressor 10 is connected via a first connecting line 52 with a condenser 54, in which a liquefaction of the exiting from the output port AA of the refrigerant compressor 10 refrigerant takes place.
  • the condenser 54 is connected via a connecting line 56 with an expansion device 58, which is followed by an evaporator 62, which in turn is connected via a connecting line 64 to the input terminal AE of the refrigerant compressor 10.
  • the refrigeration cycle 50 is thus a conventional refrigeration cycle, as it is usually present in refrigeration systems.
  • a control cooling branch 70 for cooling the heat sink 40 From the refrigeration circuit 50 branches a control cooling branch 70 for cooling the heat sink 40 from, for example, the connecting line 56 between the condenser 54 and the expansion device 58, wherein a first connecting line 72 of the control cooling branch 70 leads to a switch-on valve 74 of the control cooling branch 70, to which a thermostatic Expansion valve 76 follows, which is connected to the input terminal 42 of the heat sink 40, which is arranged in the control cooling branch 70.
  • connection line 78 which leads to an evaporation pressure regulator 80, which in turn is in turn connected via a connection line 82 to an intermediate pressure connection, for example the intermediate pressure connection AZ1 of the refrigerant compressor 10.
  • the fact that the connecting line 82 is led to the intermediate pressure port AZ1 has the consequence that the evaporating pressure VD in the heat sink 40 is higher than the suction pressure PS of the refrigerant compressor 10 without regulation of the evaporating pressure regulator 80.
  • the evaporation pressure VD is in the heat sink 40 at least on the pressure PZ1 of the refrigerant compressor 10, without the evaporation pressure regulator 80 is effective.
  • the evaporation pressure VD can be further raised above the intermediate pressure PZ1 of the refrigerant compressor 10.
  • Such an increase in the evaporation pressure VD in the heat sink 40 has the purpose of ensuring that the evaporator temperature of the control cooling arm 70 flowing through the heat sink 40 is above the freezing point temperature of water in order to prevent icing of the heat sink 40.
  • the evaporation pressure VD is set so high that the evaporation temperature is above a dew point temperature of the environment to prevent condensation of water on the heat sink 40.
  • the evaporation pressure regulator 80 opens up the possibility of establishing a minimum evaporation temperature in the heat sink 40 via the evaporation pressure VD in the heat sink 40, which temperature does not fall below this even at full cooling capacity of the control cooling branch 70.
  • the control of the cooling capacity in the heat sink 40 is carried out by the expansion valve 76, which has a temperature at the output terminal 44 of the heat sink 40 detected temperature sensor 86 which transmits the temperature at the output terminal 44 of the heat sink 40 in the expansion valve 76.
  • the expansion valve 76 is a thermostatic expansion valve that controls according to a differential pressure resulting from the difference of a first pressure generated by a heated in the temperature sensor 86 and a capillary tube 88 the expansion valve 76 supplied Medium, and a second pressure D2 of the refrigerant which is present at the input terminal 42 of the heat sink 40 or at the output terminal 44 of the heat sink 40 results.
  • Such a thermostatic, working with a pressure difference expansion valve 76 is both a cost, on the other hand maintenance-free and has a long life.
  • thermostatic or mechanical expansion valve 76 is not controllable by a controller 90 of the control cooling branch 70, so that the following problem occurs when switching on the refrigerant compressor 10.
  • the switch-on valve 74 When switching off the refrigerant compressor 10, the switch-on valve 74 is closed by the controller 90, so that the pressure in the heat sink corresponds to the maximum set by the evaporation pressure regulator 80 evaporation pressure VD.
  • the evaporation pressure regulator 80 is also a mechanical pressure regulator, which regulates to a fixed set reference pressure.
  • the pressure in the heat sink 40 may also fall below the vaporization pressure VD predetermined by the evaporation pressure regulator 80.
  • the switch-on valve 74 is also opened by the controller 90 at the same time.
  • the evaporation pressure regulator 80 Since the pressure in the heat sink 40 is equal to or below the evaporation pressure VD, the evaporation pressure regulator 80 remains closed, that is, no refrigerant can flow through the expansion valve 76 and the heat sink 40.
  • the expansion valve 76 also remains closed because the temperature measured by the temperature sensor 86 of the expansion valve 76 does not indicate any increase.
  • This heating leads to undesired heating of the electronic power components 16, so that in many cases the drive motor 30 has to be switched off in order to protect the electronic power components 36, but in any case such heating of the electronic power components 36 reduces their life.
  • a bypass line 92 with a built-in throttle 94 is connected in parallel to the expansion valve 76, the throttle 94 may be formed as a nozzle, capillary or as a diaphragm.
  • the bypass line 92 may be provided with the throttle 94 external or internal.
  • the bypass line 92 with the built-in throttle 94 now leads to the fact that when starting the refrigerant compressor 10 and opening the on-off valve 74 by the controller 90 despite closed expansion valve 76 due to this bridging parallel bypass line 92, the pressure of the refrigerant in the heat sink 40 through the evaporating pressure 80 set evaporation pressure VD increases, so that due to this pressure increase, the evaporation pressure regulator 80 will open and thus allows a refrigerant flow through the heat sink 40, the leads to the fact that the temperature sensor 86 can detect a heating of the heat sink flowing through the heat sink 40 of the electronic power components very quickly and leads to an opening of the expansion valve 76, so that this assumes the intended control function for the cooling capacity of the heat sink 40.
  • FIG Fig. 4 A second embodiment of a refrigeration system according to the invention, shown in FIG Fig. 4 is insofar as it has the same elements as the first embodiment, provided with the same reference numerals, so that reference may be made in full to the description of the first embodiment with regard to the description of these elements.
  • bypass line 92 with a throttle 94 is provided in parallel to the expansion valve 76 in this embodiment, but a bypass line 102 with a throttle 104 in parallel to the evaporation pressure regulator 80, which may be provided externally or internally.
  • the throttle 94 may be formed as a nozzle, capillary or aperture.
  • opening of the on-off valve 74 by the controller 90 and the bypass line 102 and the throttle 104 will also result in a limited minimum refrigerant flow even if the evaporative pressure regulator 80 did not open due to too low a pressure in the heat sink 40 through the heat sink 40, which in turn has the consequence that the temperature sensor 86 through the Contact with the exiting at the output terminal 44 of the heat sink refrigerant can react very quickly to a heating of this refrigerant and thus the thermostatic expansion valve 76 receives the control of the cooling capacity in the heat sink 40.
  • the pressure in the heat sink 40 then increases at least to the evaporation pressure VD predetermined by the evaporation pressure regulator 80, and when this evaporation pressure VD is exceeded, the evaporation pressure regulator 80 begins to regulate again.
  • the second embodiment works in the same way as the above-described embodiment, so that this can be fully incorporated by reference.
  • FIG Fig. 5 In a third embodiment of a refrigeration system according to the invention, shown in FIG Fig. 5 , those parts that are identical to those of the preceding embodiments are provided with the same reference numerals, so that with regard to the description of the same can be made in full to the comments on the above embodiments.
  • neither the thermostatic expansion valve nor the mechanical evaporation pressure regulator 80 is associated with a bypass line with a throttle line.
  • the mechanical evaporation pressure regulator 80 is replaced by an electrically controlled evaporation pressure regulator 80 ', a through a pressure control 110 having a pulse width modulated control signal controlled control valve 112 which is arranged between the connecting line 78 and the connecting line 82 in order to regulate the evaporation pressure VD in the heat sink 40 to the intended value.
  • This electrically controlled evaporation pressure regulator 80 ' is controllable via the controller 90, which cooperates with the pressure controller 110, that the pressure controller 110 controls the control valve 112 by a corresponding pulse width modulated control signal at starting refrigerant compressor 10 so that this a minimum refrigerant flow through the control cooling branch 70th allows, which ensures that the mechanical expansion valve 76 detects very quickly with its temperature sensor 86, a temperature increase of the heat sink 40 flowing through the refrigerant and thus receives the control of the cooling capacity of the heat sink.
  • the third embodiment works in the same way as the above-described embodiments, so that this can be fully incorporated by reference.
  • FIG Fig. 6 In a fourth embodiment, shown in FIG Fig. 6 , those elements which are identical to those of the preceding embodiment are provided with the same reference numerals, so that with regard to the description of the same reference may be made in full to the comments on the preceding embodiments.
  • an electrically controlled evaporation pressure regulator 80 "with the control valve 112 is also provided, however, the pressure control 110 'is designed such that on the one hand the evaporation pressure VD in the heat sink 40, for example in the connecting line 78, and on the other hand, the pressure in the Connected line 82 and controls the evaporation pressure VD to a minimum pressure according to this pressure difference.
  • This pressure control 110 ' can also be controlled by the controller 90, so that a minimal refrigerant flow through the heat sink 40 can be allowed even with a starting refrigerant compressor independently of the pressure in the heat sink 40 by a suitable pulse width modulated control signal for the control valve 112, which ensures that the thermostatic expansion valve 76 with the temperature sensor 86 receives the control for the heat sink 40 and only after a certain start-up time of the evaporation pressure regulator 80 "adjusts the evaporation pressure VD in the heat sink 40 to the intended evaporation pressure VD.
  • the fourth embodiment operates in the same manner as described in connection with the above embodiments, so that the statements in connection with these embodiments can be fully incorporated by reference.
  • FIG Fig. 7 a fifth embodiment, shown in FIG Fig. 7 , Those parts which are identical to the above embodiments are also provided with the same reference numerals, so that with regard to the description thereof reference may be made in full to the comments on these embodiments.
  • an evaporation pressure regulator 80 which has a three-way control valve 122 controlled by a pressure controller 120, which connects either the connection line 78 directly to the connection line 82 or via a throttle 124 to the connection line 82 combines.
  • This evaporation pressure regulator 80 "'controls, with the pressure controller 120, the three-way control valve 122 corresponding to the pressure in the connection line 82 leading to the connection AZ1 of the refrigerant compressor 10.
  • the activation of the control valve 122 takes place in such a way that already during the Switching off the refrigerant compressor 10, the pressure control 120, the control valve 122 is set so that it connects via the throttle 124, the connecting line 78 to the connecting line 82.
  • the pressure PZ1 is established at the port AZ1, which, however, is lower than the desired vapor pressure VD in the heat sink 40, and the pressure in the heat sink 40 is first reduced to the pressure PZ1 by the throttle 124 lowered.
  • the three-way control valve 122 is then switched to a pulse-width-modulated operation with regulation of the evaporation pressure in the heat sink 40 to the specified value VD.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Claims (12)

  1. Installation frigorifique comprenant un circuit frigorifique (50) dans lequel sont agencés un compresseur frigorifique (10), un condenseur (54) suivant le compresseur frigorifique (10), un dispositif de détente (58) suivant le condenseur (54) et un évaporateur suivant le dispositif de détente (58), lequel évaporateur est à son tour raccordé au compresseur frigorifique (10), dans laquelle le compresseur frigorifique (10) présente un moteur d'entraînement (30) dont la vitesse de rotation est régulée via une commande de moteur (32) électronique et une branche de refroidissement de commande (70) traversée par un réfrigérant, laquelle bifurque à partir du circuit frigorifique (50) entre le condenseur (54) et le dispositif de détente (58) et est amené jusqu'à un branchement (AZ) du compresseur frigorifique (10) et dans laquelle est agencé un dissipateur thermique (40) raccordé avec conduction thermique à des composants de puissance (36) électroniques de la commande de moteur (32), dans laquelle une température d'évaporation minimale du dissipateur thermique se situe en-dessous d'une température de fluidification du réfrigérant dans le condenseur (54),
    caractérisée en ce qu'est prévue une unité de régulation pour la branche de refroidissement de commande (70), laquelle unité est conçue de telle sorte que lors de l'exploitation du compresseur frigorifique (10), elle régule une température du dissipateur thermique (40) de manière à ce qu'une température d'évaporation minimale du dissipateur thermique (40) se situe au-dessus d'une température de point de congélation de l'eau et au-dessus d'une température de point de condensation d'un environnement de la commande de moteur (32), en ce que la température du dissipateur thermique (40) se situe à une température d'évaporation minimale réglable par une pression d'évaporation (VD) du réfrigérant dans le dissipateur thermique (40) ou plus haut et en ce que la régulation de la pression d'évaporation (VD) dans le dissipateur thermique (40) s'effectue via un régulateur de pression d'évaporation (80).
  2. Installation frigorifique selon la revendication 1, caractérisée en ce que dans une phase de lancement du compresseur frigorifique (10) un flux minimal de réfrigérant circule à travers le dissipateur thermique (40).
  3. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que la régulation dans la phase de lancement du compresseur frigorifique (10) autorise un flux minimal de réfrigérant à travers la branche de refroidissement de commande (70).
  4. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que le régulateur de pression d'évaporation (80) régule la pression d'évaporation (VD) dans le dissipateur thermique (40) de telle manière que celle-ci se situe au-dessus d'une pression (PZ) au niveau du branchement (AZ) du compresseur frigorifique (10) avec lequel la branche de refroidissement de commande (70) est raccordée.
  5. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que dans la phase de lancement lors de l'enclenchement du compresseur frigorifique (10), le régulateur de pression d'évaporation (80) laisse passer le flux minimal de réfrigérant à travers la branche de refroidissement de commande (70).
  6. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que le régulateur de pression d'évaporation (80) est inopérant à la régulation lors de l'enclenchement du compresseur frigorifique (10) dans la phase de lancement.
  7. Installation frigorifique selon l'une des revendications 5 ou 6, caractérisée en ce qu'un tuyau de dérivation (102) avec un étranglement (104) est affecté au régulateur de pression d'évaporation (80).
  8. Installation frigorifique selon la revendication 5 ou 6, caractérisée en ce que le régulateur de pression d'évaporation (80) comprend une vanne de commande (112, 122) et une commande de pression (110, 120) pour la vanne de commande (112, 122) et en ce que la commande de pression (110, 120) dans la phase de lancement du compresseur frigorifique (10) travaille de telle manière qu'elle autorise le flux minimal de réfrigérant.
  9. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que le branchement (AZ) du compresseur frigorifique (10) avec lequel la branche de refroidissement de commande (70) est raccordée se situe sur un niveau de pression qui se situe au-dessus du niveau de pression (PS) du branchement (AE) du compresseur frigorifique (10), lequel est raccordé à l'évaporateur (62).
  10. Installation frigorifique selon l'une des revendications précédentes, caractérisée en ce que la branche de refroidissement de commande (70) comprend une vanne de détente (76) thermostatique disposée en amont du dissipateur thermique (40), laquelle est commandée par un détecteur thermique (86) sur le dissipateur thermique (40).
  11. Installation frigorifique selon la revendication 10, caractérisée en ce que le détecteur thermique (86) est agencé contre un branchement de sortie (44) du dissipateur thermique (40).
  12. Installation frigorifique selon la revendication 10 ou 11, caractérisée en ce qu'un tuyau de dérivation (92) avec un étranglement (94) est affecté à la vanne de détente (76) thermostatique.
EP13711051.6A 2012-03-21 2013-03-21 Réfrigérateur Active EP2828589B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210102404 DE102012102404A1 (de) 2012-03-21 2012-03-21 Kälteanlage
PCT/EP2013/055931 WO2013139909A1 (fr) 2012-03-21 2013-03-21 Installation frigorifique

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EP2828589A1 EP2828589A1 (fr) 2015-01-28
EP2828589B1 true EP2828589B1 (fr) 2019-11-06

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DE (1) DE102012102404A1 (fr)
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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8428778B2 (en) 2002-09-13 2013-04-23 Irobot Corporation Navigational control system for a robotic device
JP6320731B2 (ja) * 2013-11-26 2018-05-09 三菱重工サーマルシステムズ株式会社 空気調和機
CN107816823B (zh) 2016-09-14 2021-11-23 开利公司 制冷系统及其润滑方法
EP3361192B1 (fr) * 2017-02-10 2019-09-04 Daikin Europe N.V. Unité source de chaleur et climatiseur équipé de ladite source de chaleur
EP3361191B1 (fr) * 2017-02-10 2022-04-06 Daikin Europe N.V. Unité de source de chaleur et climatiseur comportant l'unité de source de chaleur
JP6436196B1 (ja) * 2017-07-20 2018-12-12 ダイキン工業株式会社 冷凍装置
EP3692309A1 (fr) * 2017-10-04 2020-08-12 BITZER Kühlmaschinenbau GmbH Système de compresseur frigorifique
US11156231B2 (en) 2018-03-23 2021-10-26 Honeywell International Inc. Multistage compressor having interstage refrigerant path split between first portion flowing to end of shaft and second portion following around thrust bearing disc
DE102019001632A1 (de) * 2019-03-08 2020-09-10 Stiebel Eltron Gmbh & Co. Kg Wärmepumpeneinrichtung, Heizungs- und/oder Warmwasserbereitungssystem und Verfaheren

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0933603A1 (fr) * 1998-01-30 1999-08-04 RC Group S.p.A. Système de réfrigération comportant un onduleur refroidi par un fluide du système et commandant un compresseur, et procédé associé

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913346A (en) 1974-05-30 1975-10-21 Dunham Bush Inc Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor
CA1022425A (fr) 1974-11-01 1977-12-13 Singer Company (The) Pressostat d'evaporateur
SU964379A1 (ru) * 1980-07-04 1982-10-07 за вители Герметичный холодильный компрессор
SU1357660A1 (ru) * 1985-05-27 1987-12-07 Предприятие П/Я А-3304 Холодильна установка дл охлаждени жидких хладоносителей
IL109967A (en) * 1993-06-15 1997-07-13 Multistack Int Ltd Compressor
EP0730128B1 (fr) 1995-02-06 1999-06-23 Carrier Corporation ContrÔle en logique floue de l'injection du liquide pour le refroidissement d'un moteur
CA2248525A1 (fr) 1998-09-30 2000-03-30 Chih-Shiu Hung Methode de fabrication de plaques comportant une structure en nid d'abeilles
DE19845993A1 (de) 1998-10-06 2000-04-20 Bitzer Kuehlmaschinenbau Gmbh Schraubenverdichter
DE19925744A1 (de) * 1999-06-05 2000-12-07 Mannesmann Vdo Ag Elektrisch angetriebenes Kompressionskältesystem mit überkritischem Prozeßverlauf
US6357242B1 (en) 2000-07-20 2002-03-19 Delphi Technologies, Inc. Control system and method for suppressing head pressure spikes in a vehicle air conditioning system
US6651451B2 (en) * 2002-04-23 2003-11-25 Vai Holdings, Llc Variable capacity refrigeration system with a single-frequency compressor
EP1549517B1 (fr) 2002-10-02 2008-01-09 Behr GmbH & Co. KG Procede de reglage d'une installation de climatisation
DE10359032A1 (de) 2003-12-15 2005-07-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
JP4479275B2 (ja) * 2004-02-25 2010-06-09 株式会社デンソー 空調装置
DE102006048821A1 (de) * 2006-10-09 2008-04-10 Bitzer Kühlmaschinenbau Gmbh Kühlsystem
WO2011077720A1 (fr) * 2009-12-22 2011-06-30 ダイキン工業株式会社 Dispositif de refrigeration

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0933603A1 (fr) * 1998-01-30 1999-08-04 RC Group S.p.A. Système de réfrigération comportant un onduleur refroidi par un fluide du système et commandant un compresseur, et procédé associé

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US9194619B2 (en) 2015-11-24
CN103322739A (zh) 2013-09-25
WO2013139909A1 (fr) 2013-09-26
US20130247603A1 (en) 2013-09-26
RU2615864C2 (ru) 2017-04-11
EP2828589A1 (fr) 2015-01-28
CN103322739B (zh) 2016-04-20
DE102012102404A1 (de) 2013-09-26
RU2014142091A (ru) 2016-05-20

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