EP2828589A1 - Installation frigorifique - Google Patents

Installation frigorifique

Info

Publication number
EP2828589A1
EP2828589A1 EP13711051.6A EP13711051A EP2828589A1 EP 2828589 A1 EP2828589 A1 EP 2828589A1 EP 13711051 A EP13711051 A EP 13711051A EP 2828589 A1 EP2828589 A1 EP 2828589A1
Authority
EP
European Patent Office
Prior art keywords
heat sink
refrigerant
refrigerant compressor
refrigeration system
control
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
Application number
EP13711051.6A
Other languages
German (de)
English (en)
Other versions
EP2828589B1 (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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP2828589A1 publication Critical patent/EP2828589A1/fr
Application granted granted Critical
Publication of EP2828589B1 publication Critical patent/EP2828589B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 has, and a refrigerant flow through Steuerungskühlungszweig 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 heat-conductively connected to electronic power components of the engine control heat sink is arranged.
  • 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. - -
  • a control for the control cooling branch is provided which controls a temperature of the heat sink during operation of the refrigerant compressor so that a mecanical freezing point and below a Condensing temperature of the refrigerant in the condenser is.
  • a particularly favorable solution 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.
  • 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 a vapor pressure regulator can be a mechanical
  • 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 flow of refrigerant 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.
  • a pressure level is specified, 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 evaporating 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 expediently arranged at an output connection 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.
  • Fig. 1 is a schematic representation of a refrigerant compressor
  • Fig. 2 is a schematic representation of a motor control of
  • FIG. 3 is a schematic representation of a first embodiment of a refrigeration system according to the invention.
  • FIG. 4 is a schematic representation of a second embodiment of a refrigeration system according to the invention.
  • FIG. 5 is a schematic representation of a third embodiment of a refrigeration system according to the invention.
  • Fig. 6 is a schematic representation of a fourth embodiment of a refrigeration system according to the invention.
  • Fig. 7 is a schematic representation of a fifth embodiment of a refrigeration system according to the invention.
  • An embodiment of a refrigerant compressor 10 used in the invention is designed as a screw compressor, as described for example in German patent applications DE 198 45 991 AI or DE 103 59 032 AI. - -
  • Such a screw compressor includes, for example, a first
  • Screw rotor 12 and a second screw rotor 14, which are each rotatably disposed 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 at least partially open compression chambers form 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, open in this.
  • inlet connection AE to which refrigerant with the suction pressure is supplied
  • intermediate pressure connection AZ1 to which intermediate pressure refrigerant PZ1 can be supplied
  • intermediate pressure connection AZ2 to which refrigerant with the intermediate pressure PZ2 can be supplied
  • output 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, wherein the motor controller 32, as shown in FIG. 2, an electronic speed control 34 comprises, for example, an inverter which has highly temperature-stressed electronic power components 36, which have a high heat development during operation of the drive motor 30 with the motor control 32, and too large
  • Heating during operation of the drive motor 30 show a shortened life.
  • the heat sink 40 is provided with an input port 42 and an outlet port 44 for a refrigerant and between the
  • the inlet port 42 and the outlet port 44 extends in the heat sink 40, a cooling channel 46 which can be flowed through in the cooling body 40 in such a way that the cooling body 40 can be cooled substantially uniformly with the coolant; in particular, the cooling channel 46 runs such that a optimum heat dissipation of the thermally coupled to the heat sink 40 electronic power components 36 via the flowing through the cooling channel 46 refrigerant is possible.
  • FIG. 3 the refrigerant compressor according to FIG. 1 arranged in a designated as a whole by 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 pressure exiting from the outlet port AA of the refrigerant compressor 10 refrigerant occurs.
  • the condenser 54 is connected via a connecting line 56 with an expansion device 58, on which an evaporator 62 follows, 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.
  • An outlet connection 44 of the heat sink 40 is then followed by a connecting line 78 which leads to an evaporation pressure regulator 80, which in turn via a connecting line 82 with an intermediate pressure port, for example the intermediate pressure port AZ1 of
  • Refrigerant compressor 10 is connected.
  • 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 PZl 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 of the evaporation pressure VD in the heat sink 40 has the purpose of ensuring that the self-adjusting in the heat sink 40
  • Evaporating temperature of the control cooling branch 70 flowing through the refrigerant is above the freezing point temperature of water 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 regulation of the cooling capacity in the heat sink 40 is performed by the
  • Expansion valve 76 which has a temperature at the output terminal 44 of the heat sink 40 detecting temperature sensor 86, the
  • Expansion valve 76 the temperature at the output terminal 44 of the heat sink 40 transmitted.
  • the expansion valve 76 is a thermostatic
  • Expansion valve which controls in accordance with 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 to the expansion valve 76 supplied - -
  • Expansion valve 76 is on the one hand inexpensive, on the other hand maintenance-free and has a long service 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 on-valve 74 is closed by the controller 90, so that the pressure in the heat sink maximally set by the evaporating pressure regulator 80
  • 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. It can the
  • Bypass line 92 may be provided with the throttle 94 external or internal.
  • 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 by the heat of the electronic power components very quickly and to open the
  • Expansion valve 76 leads, so that this assumes the intended control function for the cooling capacity of the heat sink 40.
  • the first embodiment of the in Fig. 3 already leads shortly after the start of the refrigerant compressor 10 to an at least minimum flow of refrigerant through the heat sink 40, which causes the thermostatic expansion valve 76 receives its control function and in good time before excessive heating of the heat sink 40 to a sufficient cooling of the same the coolant flowing through the heat sink 40 and evaporates in this refrigerant.
  • a second embodiment of a refrigeration system according to the invention shown in Fig. 4, insofar as it has the same elements as the first embodiment, provided with the same reference numerals, so that with respect to the description of these elements in full reference may be made to the statements on the first embodiment.
  • Expansion valve 76 is provided, but a bypass line 102 with a throttle 104 in parallel to the evaporation pressure regulator 80, which may be provided externally or internally. Furthermore, the throttle 94 as a nozzle,
  • Capillary line or aperture be formed.
  • 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 - -
  • 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.
  • 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 to regulate the evaporation pressure VD in the heat sink 40 to the intended value.
  • Control 90 which cooperates with the pressure control 110, controllable so that the pressure control 110 controls the control valve 112 by a corresponding pulse width modulated control signal at starting refrigerant compressor 10 so that this a minimum flow of refrigerant through the
  • Control cooling branch 70 allows, which ensures that the mechanical expansion valve 76 with its temperature sensor 86 detects a temperature increase of the heat sink 40 flowing through the refrigerant very quickly 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 they can be fully incorporated by reference.
  • 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.
  • the fourth embodiment works in the same way as in connection with the above embodiments
  • a fifth embodiment shown in Fig. 7, are also those parts which are identical to the preceding embodiments, provided with the same reference numerals, so that in terms of
  • Embodiments can be referenced.
  • 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 port AZ1 of the refrigerant compressor 10.
  • Control of the control valve 122 takes place so that already at - -
  • 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 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)

Abstract

L'invention concerne une installation frigorifique comprenant un circuit frigorifique dans lequel sont disposés un compresseur de réfrigérant, un liquéfacteur faisant suite au compresseur de réfrigérant, un dispositif de détente faisant suite au liquéfacteur et un évaporateur faisant suite au dispositif de détente et relié d'autre part au compresseur de réfrigérant. Le compresseur de réfrigérant présente un moteur d'entraînement à vitesse régulée par une commande de moteur électronique et une branche de refroidissement de commande parcourue par du réfrigérant, laquelle se sépare du circuit frigorifique entre le liquéfacteur et le dispositif de détente et est guidée jusqu'à un raccord du compresseur de réfrigérant et dans laquelle est disposé un dissipateur de chaleur relié de manière thermoconductrice à des éléments de puissance électroniques de la commande de moteur. Pour améliorer une installation frigorifique de telle manière que des dysfonctionnements de la commande de moteur puissent être évités dans toute la mesure du possible, une régulation pour la branche de refroidissement de commande, laquelle règle, lors du fonctionnement du compresseur de réfrigérant, une température du dissipateur de chaleur de telle manière qu'une température d'évaporation minimale du dissipateur de chaleur se situe au-dessus d'une température du point de congélation et en dessous d'une température de liquéfaction du réfrigérant dans le liquéfacteur.
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

Publications (2)

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

Family

ID=47913442

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13711051.6A Active EP2828589B1 (fr) 2012-03-21 2013-03-21 Réfrigérateur

Country Status (6)

Country Link
US (1) US9194619B2 (fr)
EP (1) EP2828589B1 (fr)
CN (1) CN103322739B (fr)
DE (1) DE102012102404A1 (fr)
RU (1) RU2615864C2 (fr)
WO (1) WO2013139909A1 (fr)

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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
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
EP3361192B1 (fr) * 2017-02-10 2019-09-04 Daikin Europe N.V. Unité source de chaleur et climatiseur équipé de ladite source de chaleur
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Also Published As

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US20130247603A1 (en) 2013-09-26
US9194619B2 (en) 2015-11-24
WO2013139909A1 (fr) 2013-09-26
RU2615864C2 (ru) 2017-04-11
RU2014142091A (ru) 2016-05-20
CN103322739B (zh) 2016-04-20
EP2828589B1 (fr) 2019-11-06
DE102012102404A1 (de) 2013-09-26
CN103322739A (zh) 2013-09-25

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