EP1105647B9 - Kältemittelverdichteranlage - Google Patents

Kältemittelverdichteranlage Download PDF

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Publication number
EP1105647B9
EP1105647B9 EP00927008A EP00927008A EP1105647B9 EP 1105647 B9 EP1105647 B9 EP 1105647B9 EP 00927008 A EP00927008 A EP 00927008A EP 00927008 A EP00927008 A EP 00927008A EP 1105647 B9 EP1105647 B9 EP 1105647B9
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigerant compressor
drive motor
compressor apparatus
pressure stage
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.)
Expired - Lifetime
Application number
EP00927008A
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German (de)
English (en)
French (fr)
Other versions
EP1105647B1 (de
EP1105647A2 (de
Inventor
Volker Pollrich
Günter DITTRICH
Helmut Barowsky
Wolfgang SANDKÖTTER
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
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Publication of EP1105647A2 publication Critical patent/EP1105647A2/de
Application granted granted Critical
Publication of EP1105647B1 publication Critical patent/EP1105647B1/de
Publication of EP1105647B9 publication Critical patent/EP1105647B9/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0414—Cams
    • 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
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston 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
    • 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

Definitions

  • the invention relates to a refrigerant compressor system comprising a drive motor, a compressor driven by the drive motor with a plurality of cylinders arranged in a V-shape and a compressor shaft carrying an eccentric for driving pistons operating in the respective cylinders.
  • Such refrigerant compressor systems are known from the prior art (see US 2,454,600) In these, the eccentrics are usually formed so that an eccentric for driving a plurality of cylinders is used to obtain a compact and cost-effective solution on the one hand.
  • the invention has for its object to improve a refrigerant compressor plant of the generic type such that the greatest possible smoothness at any desired V-angle can be achieved.
  • the advantage of the invention is that by the single arrangement of the eccentric whose rotational position relative to each other is arbitrarily adjustable and thus independent of the desired V-angle a great smoothness by free selectability of the angular position of the individual eccentric is relatively achievable.
  • the compressor shaft between two successive eccentrics intermediate pieces having a cross-sectional shape which extends in the radial direction to the axis of rotation maximum to the nearest two lateral surfaces, one of which is the lateral surface one eccentric and the other is the lateral surface of the other eccentric of the two successive eccentric.
  • the compressor shaft has a lubricant channel which is coaxial with the axis of rotation, wherein transverse channels for the lubrication of running surfaces of the eccentric preferably branch off from the lubricant channel in the region of each eccentric.
  • the lubricant bore is also formed so that branch off from these transverse channels for lubricating the bearing sections thereof.
  • the cylinders arranged in a V-shape enclose a V angle of less than 70 ° with one another.
  • a particularly narrow design is achievable when the V-shaped cylinders enclose a V angle of about 60 ° or less.
  • each of the eccentrics is arranged rotated relative to the other eccentrics with respect to a rotational axis of the compressor shaft at an angle.
  • a particularly favorable solution provides that the eccentric form successively arranged pairs in the direction of the axis of rotation of the compressor shaft, wherein the eccentric forming a pair are arranged rotated by an angle of 360 ° by the number of cylinders plus the V-angle against each other and in particular each the eccentric of a pair is associated with one of two cylinders arranged at a V angle to each other.
  • first eccentric of each of the pairs and the second eccentric of each of the pairs are each rotated against each other by 180 °, so that they work in opposite directions to each other.
  • each eccentric of the compressor shaft in each case two successive eccentric each two V-shaped cylinders are arranged to each other, so that successively arranged eccentric are arranged alternately arranged on different sides of cylinders.
  • a particularly advantageous solution provides that the compressor comprises at least four cylinders and that the compressor shaft comprises at least four spaced-apart individual eccentric.
  • a particularly favorable embodiment of a refrigerant compressor installation according to the invention provides that the compressor has a low pressure stage comprising at least one cylinder and a high pressure stage comprising at least one cylinder.
  • the high pressure stage and the low pressure stage are divided so that one row of the V-shaped cylinders forms the low pressure stage and the other row of cylinders forms the high pressure stage.
  • the cylinder volumes of the low-pressure stage and the high-pressure stage no details have yet been given.
  • the cylinder volumes could be the same size and it would be possible to adjust the volumes of high-pressure stage and low-pressure stage due to the different eccentricity.
  • a particularly favorable embodiment of the solution according to the invention provides that the low-pressure stage can be switched off, in particular with regard to its compressor action. This is especially true advantageous if a power control of the refrigerant compressor plant according to the invention is desired and in particular at low cooling capacity, the not necessary itself low-pressure stage either reduced in power or can be switched off in terms of their compressor action to reduce the power consumption of the compressor.
  • Such shutdown of the low-pressure stage can be realized in a variety of ways. For example, it would be conceivable to let the low pressure stage work without compression, that is, so that no compression of the refrigerant takes place more.
  • Another possibility would be to open a detour line to the low pressure stage.
  • a particularly favorable solution provides that the suction side of the low-pressure stage, a power control valve is arranged and that between a low pressure port of the compressor and a suction side of the high-pressure stage, a valve is arranged, which opens with active power control valve.
  • Such a valve can for example be activated actively.
  • valve between the low-pressure port of the compressor and the suction side of the high-pressure stage is a check valve, which opens automatically with active power control valve depending on the pressure difference occurring, so that a targeted control of this valve between the low pressure side of the compressor and the suction side of the high pressure stage is not necessary and can be omitted.
  • a check valve has the advantage that it opens automatically when the pressure on the suction side of the high pressure stage is equal to or lower than the pressure at the low pressure exclusion, so that no additional measures for the exact control of this valve is required at such pressure ratios.
  • a particularly advantageous embodiment provides that the drive motor of the compressor flows through the refrigerant flowing from the low-pressure stage to the high-pressure stage and is thereby cooled.
  • a particularly favorable solution that ensures sufficient cooling of the drive motor in any case provides that the drive motor of the compressor of the in the High-pressure stage entering refrigerant is flowed through, that is, essentially that the refrigerant that enters the high-pressure stage, also flows through the drive motor and thus always ensures adequate cooling of the drive motor.
  • a converter is arranged on the drive motor, the converter preferably being arranged on the drive motor such that its power components are thermally coupled to a housing of the drive motor.
  • Such a coupling with the housing of the drive motor can be achieved in a simple manner in that the power components are either coupled with an intermediate piece or arranged directly on the housing of the drive motor.
  • a housing part thermally coupled to the power components of the converter is in thermal contact with the refrigerant, preferably with the refrigerant flow flowing through the drive motor.
  • a particularly advantageous arrangement of the converter in particular with regard to a compact and narrow design of the refrigerant compressor system according to the invention provides that the inverter is arranged on a side opposite the compressor side of the housing of the drive motor.
  • a refrigerant compressor system operating according to the invention in particular with regard to energy consumption, can be operated when the drive motor is speed-controlled, with preferably a speed control of the drive motor taking into account the required cooling capacity.
  • a controller is provided for speed control of the drive motor, which controls the speed of the drive motor according to the required cooling capacity.
  • control according to the invention which controls the rotational speed of the drive motor, can be used to control the temperature of a medium to be cooled by the refrigerant compressor system according to the invention, wherein the controller detects the temperature of the medium to be cooled and controls the speed accordingly.
  • a particularly precise control of the temperature of the medium to be cooled takes place when the controller operates the drive motor running interruption-free and the entire temperature control is done exclusively on the speed and, if necessary, shutdown of the low pressure stage.
  • controller controls the speed of the drive motor according to an ambient temperature.
  • a further advantageous development of the refrigerant compressor installation according to the invention provides that a controller is provided which shuts off the low-pressure stage when the temperature falls below a definable cooling capacity. This is particularly created in a simple way, the possibility to additionally reduce the power to be provided by the drive motor for the operation of the compressor in cases where such a low cooling capacity is required that it can be provided alone with the high pressure stage of the compressor.
  • this also takes place as a function of the ambient temperature.
  • a particularly favorable solution provides that the control for the speed of the drive motor and the switching off of the low-pressure stage is the same.
  • an advantageous embodiment provides that the refrigerant compressor plant is associated with a liquid subcooler.
  • the liquid subcooler is arranged on a side opposite the drive motor side of the compressor.
  • the liquid subcooler is preferably configured to evaporate liquid refrigerant for liquid subcooling, and this vaporized refrigerant enters the refrigerant flowing to the high pressure stage.
  • the refrigerant vaporized by the liquid subcooler flows through the drive motor on its way to the high-pressure stage.
  • the vaporized refrigerant is supplied to the medium-pressure channel before flowing through the drive motor.
  • a particularly advantageous with regard to the sufficient cooling of the drive motor solution provides that the liquid subcooler is controlled according to a temperature of the drive motor.
  • the detection of the temperature of the drive motor via a detection of the temperature of the housing of the drive motor.
  • a particularly favorable solution in particular for the efficient cooling of the converter, provides that the liquid subcooler can be controlled in accordance with the temperature of the part of the housing of the drive motor carrying the converter.
  • the liquid subcooler is controlled to maintain a minimum temperature of the converter-carrying portion of the housing, the minimum temperature of the converter-carrying portion of the housing should be chosen so that no condensation of moisture from the ambient air can take place.
  • control of the liquid subcooler takes place in such a way that the converter-carrying part of the housing remains at a temperature of at least 10 ° Celsius, preferably at least 20 ° Celsius.
  • the liquid subcooler is controlled so that the maximum temperature of the converter carrying part of the housing does not exceed a predetermined temperature.
  • This predetermined temperature is about 60 ° Celsius, preferably about 50 ° Celsius.
  • FIG. 1 An exemplary embodiment of a refrigerant compressor system according to the invention, shown in FIG. 1, comprises a plant housing designated as a whole by 10, which extends in a longitudinal direction 12 and carries an inverter 16 on a first end face 14 extending transversely to the longitudinal direction 12, while on one of the front side 14 opposite end face 18 a designated as a whole with 20 liquid subcooler is arranged.
  • a motor housing portion 22 designated as a whole with 24 drive motor is arranged, which has a motor housing portion 22 arranged in the stator 26 and a stator 26 enclosed by the rotor 28 which is rotatable about a rotation axis 30 ,
  • the rotor 28 is seated on a shaft portion 32 of a designated as a whole with 34 compressor shaft.
  • the plant housing 10 further comprises a compressor housing portion 38 of a designated as a whole with 40 compressor for the refrigerant.
  • the compressor housing section 38 extends from the end face 18 of the plant housing 10 to a partition wall 42 which separates the compressor housing section 38 from the motor housing section 22.
  • a compressor shaft bearing designated as a whole by 44, which supports the shaft 34 in a first bearing section 46 which is arranged on a shaft section 32 carrying the rotor 28 on a side facing the compressor 40.
  • a second compressor shaft bearing 50 is arranged, in which the shaft 34 is rotatably mounted with a second bearing portion 52.
  • the compressor shaft 34 carries the rotor 28 on its over the first bearing portion 46 on a second bearing portion 52 opposite side freely projecting shaft portion 32, so that the compressor shaft 34 is mounted in a simple manner with only two bearing portions 46, 52.
  • first bearing portion 46 and the second bearing portion 52 is a designated as a whole with 54 eccentric portion of the compressor shaft 34 which extends through the compressor housing portion 38 and four eccentric 60 1 , 60 2 , 60 3 and 60 4 carries, starting from the second Bearing portion 52 in the direction of the first bearing portion 46 along the axis of rotation 30 are arranged successively and at intervals to each other.
  • the eccentric 60 1 to 60 4 are formed as approximately disc-shaped body with a circular cylindrical surface 62 1 to 62 4 , which are arranged eccentrically to the axis of rotation 30 of the compressor shaft and each form the tread for this enclosing connecting rod 64 1 to 64 4 .
  • the cylinder jacket surfaces 62 1 to 62 4 of the eccentric 60 1 to 60 4 are arranged so that a central axis 66 1 of the cylinder jacket surface 62 1 in a plane 68 1 , which extends through the central axis 66 1 and the axis of rotation 30.
  • a plane 68 2 in which a central axis 66 2 of the cylinder jacket surface 62 2 lies and which also extends through the axis of rotation 30, is rotated relative to the plane 68 1 at an angle of 150 °.
  • the central axis 66 3 of the cylinder jacket surface 62 3 of the eccentric 60 3 in a plane 68 3 which is rotated relative to the plane 68 1 by 180 °, that is, the central axes 66 1 and 68 3 of the eccentric 60 1 and 60 3rd are arranged on exactly opposite sides of the axis of rotation 30.
  • a central axis 66 4 of the cylinder jacket surface 62 4 of the eccentric 60 4 lies in a plane 68 4 , which is rotated relative to the plane 68 1 by 330 °, that is to the plane 68 2 by 180 ° and with respect to the plane 68 3 by 150 ° is turned.
  • center axes 66 4 and 66 2 are exactly opposite each other with respect to the rotation axis 30.
  • the eccentric 60 1 and 60 2 and the eccentric 60 3 and 60 4 are each a pair in which the two eccentrics are arranged relative to each other rotated by an angle of 150 ° with respect to the axis of rotation 30 and also the respective first eccentric 60 first and 60 3 of the two pairs and the respective second eccentric 60 2 and 60 4 of the two pairs each arranged opposite each other with respect to the axis of rotation 30.
  • the compressor shaft 34 also includes, as shown in Fig. 2 and Fig. 4, a passing through this lubricant passage 70 which extends from one of the end face 18 facing inlet opening 72 coaxial with the axis of rotation 30 through the entire compressor shaft 34 and is completed in the region of the first bearing portion 46 , Furthermore, a transverse channel 74 branches off from this lubricant channel in the area of the first bearing section 52, which exits in the region of the first bearing section 52 in order to lubricate it.
  • transverse channels 76 1 to 76 4 are provided, which open respectively in the corresponding lateral surface 62 1 to 62 4 in one of the axis of rotation closest area 78 1 to 78 4 and lube oil leak.
  • transverse channels 80 and 82 are provided in the region of the first bearing portion, which contribute to the lubrication thereof.
  • an intermediate region 90 is provided between the bearing section 52 and the eccentric 60 1 , which, as shown in FIG. 5, has a cross section. whose first outer contour region 92 1 extends in the radial direction to the axis of rotation 30 maximally up to the cylinder jacket surface 96 of the second bearing portion 52, while a second outer contour region 94 1 of the cross section in the radial direction to the axis of rotation 30 maximum up to the cylinder jacket surface 62 1 of the first eccentric 60th 1 extends.
  • the intermediate piece 98 (FIGS. 4 and 6) which extends in the direction of the axis of rotation 30 over a length which corresponds to at least one width of the connecting rod 64 in this direction. Furthermore, the intermediate piece 98 has a cross section whose first outer contour region 92 2 extends in the radial direction to the axis of rotation 30 maximum to the cylinder jacket surface 62 1 of the first eccentric 60 1 and the second outer contour region 94 2 in the radial direction to the axis of rotation 30 maximum up to the cylinder jacket surface 62 2 of the second eccentric 60 2 extends.
  • an intermediate piece 100 is provided between the second eccentric 60 2 and the third eccentric 60 3 (FIGS. 4 and 7) whose first outer contour region 92 3 extends in the radial direction to the axis of rotation 30 up to the cylinder jacket surface 62 2 of the second eccentric 60 2 extends and the second outer contour portion 94 3 extends in the radial direction to the axis of rotation 30 maximum to the cylinder surface 62 3 of the third eccentric. Furthermore, the intermediate piece 100 still has a third outer contour region 95 3 , which has, for example, a radial extent to the axis of rotation 30 to the lateral surface 96.
  • a further intermediate piece 102 is provided (FIG. 4 and 8), which has a first outer contour region 92 4 , which in the radial direction to the axis of rotation 30 maximum to the cylinder surface 62 3 of the third eccentric 60 3 extends and a second outer contour region 94 4 , which extends in the radial direction to the axis of rotation 30 a maximum to the cylindrical surface 62 4 of the fourth eccentric 60 4 .
  • an intermediate portion 104 is provided, which is in the radial Direction to the rotation axis 30 in a first outer contour region 92 5 maximally extends to the cylinder jacket surface 60 4 and with a second outer contour region 94 5 maximum up to a cylinder jacket surface 106 of the first bearing portion 46th
  • the first row 110 with the cylinders 112 and 114 forms a high-pressure stage of the multistage compressor 40 and the second row 120 with the cylinders 122 and 124 forms a low-pressure stage of the multistage compressor 40.
  • the cylinders 112 and 114 of the high pressure stage have a smaller cross section than the cylinders 122 and 124 of the low pressure stage, while the stroke is the same due to the use of identical shaped eccentrics 60 1 to 60 4 in all cylinders 112 and 114 and 122 and 124.
  • the first row 110 of the cylinders 112 and 114 is arranged symmetrically with respect to a passing through the axis of rotation 30 level 130, while the second row 120 with the cylinders 122 and 124 symmetrical to a through the rotation axis 30th lying through plane 132 and both levels 130 and 132 include a V-angle a of 60 ° with each other.
  • the eccentric 60 1 and 60 3 are arranged so that the pistons 116 and 118 with an angular displacement of exactly 180 move each other and also the eccentric 60 2 and 60 4 are arranged that the piston 126 and 128 are also offset by an angle of 180 ° to each other, wherein in Fig. 11, the piston 126 is at bottom dead center and in Fig. 13, the piston 128 at top dead center, while on the other hand, the two pistons 116 and 118th exactly between the top dead center and the bottom dead center. That is, the pistons 116 and 118 of the row 110 move at exactly 90 ° angularly offset from the pistons 126 and 128 of the row 120.
  • the plant housing 10 is formed so that at this as the refrigerant inlet, a low-pressure port 140 is arranged, through which refrigerant flows into a provided in the plant housing low-pressure channel 142, which forms the low-pressure stage to the two cylinders 122 and 124 Row 120 leads, which can be entered via a common cylinder head cover 144 shown in FIGS. 11 and 13, the low-pressure refrigerant in the cylinder 122 and 124.
  • refrigerant released from the cylinders 122 and 124 exhausts refrigerant at medium pressure into a medium pressure passage 146 which transits from the cylinder head cover 144 to the plant housing 10 in the area near the partition 42, wherein
  • the medium-pressure channel 146 then the refrigerant compressed to medium pressure flows into an interior 148 of the drive motor 24 and flows there against the end face 14 forming end wall 150 and tempered.
  • the end wall 150 is in thermal contact with the inverter 16 and thus serves to cool the inverter 16, in particular of the electrical power components of the same.
  • the medium pressure refrigerant continues to flow in an inflow channel 152, which leads to the cylinders 112 and 114 of the high-pressure stage forming row 110. In this, the refrigerant is compressed to high pressure, which then enters a high pressure passage 154 of the system housing 10 and flows through this to a high pressure port 160.
  • the refrigerant compressor plant according to the invention is used in a refrigeration system constructed in a known manner, as shown in FIG. 15.
  • a line 162 leads from the high pressure port 160, a line 162 to a designated as a whole 164 capacitor.
  • From this liquid refrigerant flows in a line 176 to a collector 168 for the liquid refrigerant.
  • From the accumulator 168 flows liquid refrigerant via a line 170 to the liquid cooler 120, wherein the main part of the liquid refrigerant flows through the liquid subcooler 20 and flows via a line 172 to an expansion valve 174 for an evaporator 176.
  • the vaporized refrigerant flows via a line 178 to the low pressure port 140 of the refrigerant compressor plant according to the invention.
  • a small part of the liquid refrigerant is branched off from the line 170 and passed via a line 180 to an injection valve 182, wherein before the injection valve 182 a controllable by a controller 186 solenoid valve 184 is arranged.
  • the injection valve 182 constitutes an expansion valve for the liquid cooler 120, which feeds liquid refrigerant via a line 188 to the liquid subcooler 20, which evaporates therein and undercuts the flow of the liquid refrigerant from the line 170 into the line 172, so that in the line 172 supercooled liquid refrigerant flows to the expansion valve 174.
  • the vaporized refrigerant from the liquid subcooler 20 is passed via a line 190 to a shown in FIGS. 14 and 15 medium pressure port 192, via which it enters the medium pressure passage 146 and with the coming of the low pressure stage 120 and compressed to medium pressure refrigerant together through the interior 148 of the drive motor 24 flows and then enters the high-pressure stage 110.
  • the controller 186 further detects its temperature via a temperature sensor 194 disposed on the motor housing portion 22 of the plant housing 10 and controls the solenoid valve 184 so that the motor housing portion 22, in particular the end wall 150, for example, at a temperature in the range of about 30 ° to about 50 ° Celsius is maintained and thus prevents moisture is condensed in the range of the inverter 16.
  • This temperature range is also chosen so that the respective refrigerant has a suitable overheating before entering the high pressure stage 110.
  • a controller 200 which controls the drive motor 24 with respect to its speed via the inverter 16 and controls the power of the drive motor 24 according to a measured temperature sensor at the evaporator 176 so that the evaporator 176, the desired cooling capacity is available ,
  • a particularly advantageous embodiment of the controller 200 provides that this serves to regulate the temperature of the air flow 206, which is forcibly circulated, for example, in a space to be cooled by means of the blower 204, very precisely to a certain temperature, for example with a control accuracy of 0 , 5 °.
  • the controller 200 operates the refrigeration compressor according to the invention in the control range above a minimum cooling power without interruption, that is not as in the prior art, after sufficiently strong cooling off the refrigerant compressor system and wait until the temperature rises again to turn on again but by changing the rotational speed of the drive motor increases or reduces the cooling capacity according to the temperature of the air flow 206.
  • the controller 200 is additionally coupled to the controller 186.
  • the possibility of switching off the low-pressure stage 120 with the cylinders 122 and 124 is provided with regard to its compressor action.
  • a branch 210 is provided in the low-pressure channel 142, with the branch 210, a check valve 212 is connected, which is able to connect the low-pressure channel 142 with the medium-pressure channel 146 when the pressure in the medium-pressure channel 146 under the pressure in the low pressure channel 142 is located.
  • a power control valve 214 is still provided, which is capable of the influx of gaseous Refrigerant via the low pressure passage 142 in the low-pressure stage 120 to throttle or block.
  • the possibility is given to lower the compressor power of the low-pressure stage 120 so far that the pressure in the medium-pressure passage 146 drops so far that refrigerant flows via the branch 210 from the low-pressure passage 142 via the check valve 112 into the medium-pressure passage 146, the interior 148th flows through the drive motor 24 and then enters the high pressure stage 110 with the cylinders 112 and 114 to be compressed in this to high pressure, wherein the high pressure refrigerant flows through the high pressure passage 154 to the high pressure port 160.
  • the controller 200 by switching off the low-pressure stage 120 by the drive motor 24 required power consumption thereby reduce that only the high-pressure stage 110 operates and compresses the refrigerant to a lower pressure, for the necessary cooling capacity is sufficient in this case.
  • the drive motor 24 is loaded at the same time less and thus absorbs less power.
  • the shutdown of the low-pressure stage 120 by the controller 186 in communication with the controller 200 allows a particularly advantageous exact control of the temperature of the air stream 206, since in the case of a reduction of the cooling capacity first when the low-pressure stage 120 is operating, the speed of the drive motor 24 is reduced by the controller 200 ,
  • the shutdown of the low pressure stage 120 has now the advantage that the speed of the drive motor 24 by the controller 200 must not be driven arbitrarily low, but that after switching off the low pressure stage 120, the drive motor 24 can be operated again at a higher speed to the by switching off to compensate for the drop in compressor power entering the low pressure stage 120. In a further reduction then the speed of the drive motor 24 can be lowered again from the higher level.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP00927008A 1999-04-22 2000-04-20 Kältemittelverdichteranlage Expired - Lifetime EP1105647B9 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19918161A DE19918161A1 (de) 1999-04-22 1999-04-22 Kältemittelverdichteranlage
DE19918161 1999-04-22
PCT/EP2000/003606 WO2000065232A2 (de) 1999-04-22 2000-04-20 Kältemittelverdichteranlage

Publications (3)

Publication Number Publication Date
EP1105647A2 EP1105647A2 (de) 2001-06-13
EP1105647B1 EP1105647B1 (de) 2005-10-19
EP1105647B9 true EP1105647B9 (de) 2006-03-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP00927008A Expired - Lifetime EP1105647B9 (de) 1999-04-22 2000-04-20 Kältemittelverdichteranlage

Country Status (7)

Country Link
US (1) US6401472B2 (da)
EP (1) EP1105647B9 (da)
AT (1) ATE307290T1 (da)
DE (2) DE19918161A1 (da)
DK (1) DK1105647T3 (da)
ES (1) ES2250129T3 (da)
WO (1) WO2000065232A2 (da)

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US20010011463A1 (en) 2001-08-09
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ATE307290T1 (de) 2005-11-15
EP1105647B1 (de) 2005-10-19
WO2000065232A3 (de) 2001-03-22
DK1105647T3 (da) 2006-02-13
EP1105647A2 (de) 2001-06-13
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US6401472B2 (en) 2002-06-11
WO2000065232A2 (de) 2000-11-02

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