EP2221559A1 - Thermodynamische Anlage mit verbesserter Schmierung - Google Patents

Thermodynamische Anlage mit verbesserter Schmierung Download PDF

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Publication number
EP2221559A1
EP2221559A1 EP09153255A EP09153255A EP2221559A1 EP 2221559 A1 EP2221559 A1 EP 2221559A1 EP 09153255 A EP09153255 A EP 09153255A EP 09153255 A EP09153255 A EP 09153255A EP 2221559 A1 EP2221559 A1 EP 2221559A1
Authority
EP
European Patent Office
Prior art keywords
compressor
compressors
lubricant
circulation
refrigerant
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
EP09153255A
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English (en)
French (fr)
Other versions
EP2221559B1 (de
Inventor
Mario Borras
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.)
Systemair Ac SAS
Original Assignee
Airwell Industrie France Sas
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Filing date
Publication date
Application filed by Airwell Industrie France Sas filed Critical Airwell Industrie France Sas
Priority to ES09153255.6T priority Critical patent/ES2600474T3/es
Priority to EP09153255.6A priority patent/EP2221559B1/de
Publication of EP2221559A1 publication Critical patent/EP2221559A1/de
Application granted granted Critical
Publication of EP2221559B1 publication Critical patent/EP2221559B1/de
Not-in-force legal-status Critical Current
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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B2400/0401—Refrigeration circuit bypassing means for 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication

Definitions

  • the present invention relates to a thermodynamic refrigerant plant and its method of operation.
  • lubricant such as lubricating oil
  • refrigerant for the compressors is often driven by the refrigerant.
  • An object of the invention is to avoid this.
  • a corollary problem also arises as to how to ensure the type of valve means to be used so that the lubricant balancing can be achieved effectively and simply at least in the second and third aforementioned configurations.
  • the architecture of the system will preferably make it possible to use a simple 4-way valve (favorably with a non-return valve) to go from the two-stage operation cycle to the single-stage cycle, depending on the needs of the system. building heating in such an application.
  • the fat indicates a circulation of the refrigerant in the blackened pipe.
  • the figure 1 shows such a two-stage operation.
  • the low pressure (LP) compressor 1 draws in the refrigerant which has evaporated in the evaporator 9 thus recovering the heat generally from the outside air.
  • the cold source may be soil or water. However, it is best to use outside air.
  • the compressor 1 compresses the refrigerant, for example a mixture of HFCs such as R-407C, at the medium pressure of the system which is fixed by the high pressure compressor (HP) 2.
  • This intermediate pressure is set by the ratio of the volumes swept compressors 1 and 2.
  • the four-way valve 3 then relates its input 31 to its output 34, as figure 2 . It will be understood that this valve is mounted to operate the installation according to one of said three possible configurations, being arranged between the two compressors 1, 2 when they operate in series.
  • the low-pressure delivery pipe 5 is in direct connection with the suction pipe 6 of the compressor 2.
  • the non-return valve 4 prevents the high-pressure refrigerant leaving the compressor 2 by the pipe 21 to iron at low system pressure by the pipes 8 and 7.
  • the water of the heating circuit of the habitat here to be heated is heated by the refrigerant which gives in heat there.
  • the water enters the condenser 10 after cooling in the heating system (radiators, convectors ...) by the pipe 19 and out, at a temperature typically higher than 4 to 5 ° C, through the pipe 20.
  • the tapping 17 on the high-pressure pipe 18 of the condenser outlet makes it possible to take a certain flow rate d3 of fluid which is evaporated in the subcooling exchanger 11, after expansion by the expander 12, in order to sub-cool the flow rate d2.
  • the flow d2 is equal to d1 - d3.
  • the flow d1 is then the total flow compressed by the compressor 2 and condensed in the condenser 10.
  • the flow d3 is much lower than d2.
  • the point 25 is the outlet point of the flow d2 of the subcooling exchanger 11.
  • the enthalpies at the respective points 13, 17 and 25 are shown in FIG. figure 4 on a so-called Mollier diagram, pressure - enthalpy, where is represented the two-stage cycle corresponding to the functioning presented figure 1 .
  • the quilting 16 of the pipework 26 on the pipe 6 allows the high-pressure compressor 2 to suck also the flow rate d3 evaporated in the subcooling heat exchanger 11.
  • the flow d2 is then brought by the pipe 14 to the evaporator 9, the refrigerant being expanded in the expander 15.
  • the four-way valve 3, according to its position, then allows either the first compressor 1 to operate alone, or the second compressor 2 to operate alone.
  • the operation of one or the other of the compressors depends on the heat output required, since the first compressor 1 has a swept volume greater than the HP compressor 2 and therefore a higher power, given their size for the two-stage operation.
  • the figure 2 presents the operation with the first compressor 1 in operation and the second compressor 2 stopped.
  • the inlet 31 of the four-way valve 3 is in connection with the outlet 32, thereby directly connecting the discharge pipe 5 of the first compressor 1 with the pipe 8 which bypasses the second compressor 2 and joins the ducting 21 before entering the condenser 10 via the quilting 22.
  • the figure 3 shows the operation of the second compressor 2 alone, the first compressor 1 being stopped.
  • the second compressor 2 sucks up the refrigerant which has evaporated in the evaporator 9 via the piping 7 and the tap 23 of the outlet pipe 24 of the evaporator 9.
  • the four-way valve 3 then communicates this piping. 7 with the suction pipe 6 of the second compressor 2 via the second inlet 33 and the first outlet 34 of the four-way valve 3.
  • the rest of the circulation of the refrigerant is identical. Again the sub-cooling exchanger 11 is not in operation. It is therefore crossed by the total flow d1.
  • the four-way valve 3 is electrically controlled to move an inner piston, thereby communicating the first input 31 with either the first output 34 or the second output 32. In the latter case, the four-way valve 3 in communication the second input 33 with the first output 34.
  • This single four-way valve 3 associated favorably with the non-return valve 4 then allows to develop a simple regulation according to the external temperature of the environment.
  • the regulator 40 of the installation which controls its configuration receives, via the input channel 41, an electrical signal corresponding to the analog value of the outside temperature, measured for example by a probe, shown schematically in FIG. figure 5 .
  • this outside temperature is below a threshold temperature T1, for example 0 ° C.
  • T1 a threshold temperature
  • the four-way valve 3 is in position 1 of Table A below corresponding to the operation presented.
  • FIG 1 where the tubing 5 is in communication with the tubing 6, via the first inlet 31 and the first output 34 of the four-way valve.
  • the regulator 40 then sends an electrical signal via the channel 42 to put the four-way valve 3 in position 1.
  • the controller has also operated the compressors 1 and 2 via the channels 44 and 45 of the regulator 40.
  • the heating capacity of the heat pump is set by two thresholds, low and high, from the water inlet temperature to the condenser.
  • This water temperature is measured on the pipe 19 by a probe, schematized at 47, and its value is received analogically by the regulator 40, via the channel 43.
  • the regulator 40 puts into operation either the compressors 1 and 2 together in two-stage operation, or the one of the compressors 1, 2, this as a function of the outside temperature, as indicated below in Table A.
  • the regulator 40 sends, via the channel 42, the setpoint position 2 to the four-way valve 3 as defined in the table below.
  • the regulator 40 controls in parallel the operation of the first compressor 1 alone, as shown figure 2 .
  • the first input 31 is then put into communication with the second output 32.
  • the regulator 40 sends, via the channel 42, the instruction of the same position 2 to the four-way valve 3, as again defined in the table below.
  • the regulator 40 controls the operation of the second compressor 2 alone, as shown figure 3 .
  • the second input 33 is thus placed in communication with the first output 34.
  • the four-way valve 3 is in its position 2 unchanged. It is the compressor, 1 or 2, in operation that circulates the refrigerant as indicated in FIG. figure 2 or 3 corresponding.
  • the second regulator 12 may conventionally be a capillary tube. In this case, it is necessary to provide on the bypass circuit 26 a solenoid valve, shown diagrammatically in Figures 1 to 3 , to close the circuit 26, in particular in the operating mode shown schematically in FIG. figure 3 .
  • the capillary tube could be replaced by another type of regulator.
  • the four-way valve 3 could be replaced by equivalent means fulfilling the same functions (selection means).
  • the first valve 50 is mounted, upstream of the tapping 16, between the pipes 5 and 6 connected together.
  • the second valve 51 is mounted on the second bypass 8 then connected between the tapping 54 situated upstream of the first valve inlet 50 and the tapping 22.
  • the third valve 52 is mounted on first bypass 7 then connected between the tap 23 located upstream of the inlet of the compressor BP 1 and the tap 53 connected between the tap 16 and the inlet of the compressor HP 2.
  • the figure 6 shows the two-stage configuration, with the two compressors in series.
  • the valves 51, 52 are closed, the one 50 is open.
  • the figure 7 shows the single-stage configuration with the HP 2 compressor running, while the other 1 is stopped.
  • the valves 50, 51 are closed, that 52 is open.
  • the figure 8 shows the other single-stage configuration with the BP 1 compressor in operation, the other 2 being stopped.
  • the valves 50, 52 are closed, the 51 is open.
  • the selective circulation means comprise a dedicated conduit 56 with two pipes 57, 59 interconnecting the lubricant receptacles of the compressors, and a valve means 55 interposed at a location of this selectively to open and close the circulation of the lubricant between the compressors.
  • Figure 9 on each of the two compressors, the tubing concerned is connected to the casing at the level of the oil level (used here as a lubricating fluid), thus in connection with the lubricant receptacles 100, 200.
  • the valve means 55 that is recommended to use is of the two-way solenoid valve type which, when under direct control (“directly actuated"), operates in such a way that the magnetic field of the solenoid then forces a movement of the plunger and thus causes the opening of the valve means 550 that it contains, this without requiring any pressure difference.
  • this preferred valve means will be adapted to open on command (direct) and remain open regardless of the difference in lubricant pressures established between the compressors 1, 2.
  • valve means 55 This will impose a mounting direction of the valve means 55, as shown more clearly figure 9 where the arrow 551, directed from the compressor HP 2 to the compressor BP 1, therefore indicates this closing tightness all the stronger the valve 550 that P2 will be higher compared to P1.
  • a two-way valve solenoid valve from "ALCO CONTROLS" type 110RB, without pressure differential, will be suitable.
  • the start of the installation is carried out here from the compressor 2 (C2) with the four-way valve 3 in single-stage configuration ( figure 3 ).
  • the suction pressure of the C2 (C2 housing pressure) is equal to the suction pressure of the compressor 1 (C1) minus the pressure drop of the valve 3.
  • the management of the opening time of the valve 55 and the frequency of this operation are defined by the regulator 40.
  • the regulator 40 will intervene so that a correct amount of oil is stored in each compressor for reliable operation.
  • valve 3 could be replaced by that of the valves 50 or 52, for the pressure drop, and that of the three valves 50, 51, 52 for the circulation of the refrigerant.
  • the duration of the balancing may be a few seconds.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP09153255.6A 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung Not-in-force EP2221559B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ES09153255.6T ES2600474T3 (es) 2009-02-19 2009-02-19 Instalación termodinámica con lubricación mejorada
EP09153255.6A EP2221559B1 (de) 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09153255.6A EP2221559B1 (de) 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung

Publications (2)

Publication Number Publication Date
EP2221559A1 true EP2221559A1 (de) 2010-08-25
EP2221559B1 EP2221559B1 (de) 2016-08-10

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EP09153255.6A Not-in-force EP2221559B1 (de) 2009-02-19 2009-02-19 Thermodynamische Anlage mit verbesserter Schmierung

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EP (1) EP2221559B1 (de)
ES (1) ES2600474T3 (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2487437A1 (de) * 2011-02-11 2012-08-15 STIEBEL ELTRON GmbH & Co. KG Wärmepumpenvorrichtung
WO2013004974A1 (fr) 2011-07-06 2013-01-10 Electricite De France Procede d'equilibrage des niveaux de lubrifiant dans une unite de compression multi-etagee d'un systeme d'echange thermique et systeme d'echange thermique mettant en oeuvre un tel procede
DE102013014543A1 (de) * 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
EP2846112A1 (de) * 2013-09-03 2015-03-11 Stiebel Eltron GmbH & Co. KG Wärmepumpenvorrichtung
EP3040643A4 (de) * 2013-09-30 2016-12-14 Mitsubishi Heavy Ind Ltd Wärmepumpensystem und wärmepumpenwassererhitzer
US10801757B2 (en) 2014-07-09 2020-10-13 Carrier Corporation Refrigeration system
CN113167519A (zh) * 2018-10-31 2021-07-23 艾默生环境优化技术有限公司 用于气候控制系统的油控制
CN113513856A (zh) * 2021-07-15 2021-10-19 广东纽恩泰新能源科技发展有限公司 一种热泵系统及控制方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3621670A (en) * 1970-01-12 1971-11-23 Vilter Manufacturing Corp Lubricating oil equalizing system
EP0961091A2 (de) * 1998-05-26 1999-12-01 Linde Aktiengesellschaft Verbund(kälte)anlage und Verfahren zum Betreiben einer Verbund(kälte)anlage
JP2001147047A (ja) * 1999-11-19 2001-05-29 Fujitsu General Ltd 空気調和機
DE102005019795A1 (de) * 2004-05-07 2005-12-01 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Klimakompressor
FR2889733A1 (fr) 2005-08-12 2007-02-16 A C E Ind Soc Par Actions Simp Systeme de pompe a chaleur avec deux compresseurs
WO2008111712A2 (en) * 2007-03-13 2008-09-18 Lg Electronics Inc. Compression system and air conditioning system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3621670A (en) * 1970-01-12 1971-11-23 Vilter Manufacturing Corp Lubricating oil equalizing system
EP0961091A2 (de) * 1998-05-26 1999-12-01 Linde Aktiengesellschaft Verbund(kälte)anlage und Verfahren zum Betreiben einer Verbund(kälte)anlage
JP2001147047A (ja) * 1999-11-19 2001-05-29 Fujitsu General Ltd 空気調和機
DE102005019795A1 (de) * 2004-05-07 2005-12-01 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Klimakompressor
FR2889733A1 (fr) 2005-08-12 2007-02-16 A C E Ind Soc Par Actions Simp Systeme de pompe a chaleur avec deux compresseurs
WO2008111712A2 (en) * 2007-03-13 2008-09-18 Lg Electronics Inc. Compression system and air conditioning system

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2487437A1 (de) * 2011-02-11 2012-08-15 STIEBEL ELTRON GmbH & Co. KG Wärmepumpenvorrichtung
WO2013004974A1 (fr) 2011-07-06 2013-01-10 Electricite De France Procede d'equilibrage des niveaux de lubrifiant dans une unite de compression multi-etagee d'un systeme d'echange thermique et systeme d'echange thermique mettant en oeuvre un tel procede
FR2977657A1 (fr) * 2011-07-06 2013-01-11 Electricite De France Procede d'equilibrage des niveaux de lubrifiant dans une unite de compression multi-etagee d'un systeme d'echange thermique et systeme d'echange thermique mettant en oeuvre un tel procede
DE102013014543A1 (de) * 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
EP2846112A1 (de) * 2013-09-03 2015-03-11 Stiebel Eltron GmbH & Co. KG Wärmepumpenvorrichtung
EP3040643A4 (de) * 2013-09-30 2016-12-14 Mitsubishi Heavy Ind Ltd Wärmepumpensystem und wärmepumpenwassererhitzer
US10801757B2 (en) 2014-07-09 2020-10-13 Carrier Corporation Refrigeration system
CN113167519A (zh) * 2018-10-31 2021-07-23 艾默生环境优化技术有限公司 用于气候控制系统的油控制
US11460224B2 (en) 2018-10-31 2022-10-04 Emerson Climate Technologies, Inc. Oil control for climate-control system
CN113167519B (zh) * 2018-10-31 2023-05-26 艾默生环境优化技术有限公司 用于气候控制系统的油控制
CN113513856A (zh) * 2021-07-15 2021-10-19 广东纽恩泰新能源科技发展有限公司 一种热泵系统及控制方法

Also Published As

Publication number Publication date
EP2221559B1 (de) 2016-08-10
ES2600474T3 (es) 2017-02-09

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