EP2372158B1 - Frequenzvariabler verdichter und steuerverfahren dafür - Google Patents

Frequenzvariabler verdichter und steuerverfahren dafür Download PDF

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Publication number
EP2372158B1
EP2372158B1 EP09826234.8A EP09826234A EP2372158B1 EP 2372158 B1 EP2372158 B1 EP 2372158B1 EP 09826234 A EP09826234 A EP 09826234A EP 2372158 B1 EP2372158 B1 EP 2372158B1
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EP
European Patent Office
Prior art keywords
refrigerant
compression
frequency variable
frequency
passage
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Active
Application number
EP09826234.8A
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English (en)
French (fr)
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EP2372158A4 (de
EP2372158A1 (de
Inventor
Seung-Jun Lee
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LG Electronics Inc
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LG Electronics Inc
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Publication of EP2372158A4 publication Critical patent/EP2372158A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/804—Accumulators for refrigerant circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable

Definitions

  • the present invention relates to a frequency variable compressor.
  • a compressor is a mechanical apparatus receiving power from a power generation apparatus such as an electric motor, a turbine or the like, and compressing the air, refrigerant or various operating gases to raise a pressure.
  • the compressor has been widely used for electric home appliances such as refrigerators and air conditioners, and the application thereof has been expanded to the whole industry.
  • the compressors are roughly classified into a reciprocating compressor in which a compression space into/from which an operating gas is sucked and discharged is defined between a piston and a cylinder and the piston is linearly reciprocated in the cylinder to compress refrigerant, a rotary compressor in which a compression space into/from which an operating gas is sucked and discharged is defined between an eccentrically-rotated roller and a cylinder and the roller is eccentrically rotated along an inside wall of the cylinder to compress refrigerant, and a scroll compressor in which a compression space into/from which an operating gas is sucked and discharged is defined between an orbiting scroll and a fixed scroll and the orbiting scroll is rotated along the fixed scroll to compress refrigerant.
  • the rotary compressor has been developed into a twin rotary compressor including two rollers and two cylinders at its upper and lower portions, in which the upper and lower roller and cylinder pairs compress some and the rest of the total compression capacity, and a 2-stage rotary compressor including two rollers and two cylinders at its upper and lower portions, in which the two cylinders communicate with each other, one pair compresses relatively low-pressure refrigerant, and the other pair compresses relatively high-pressure refrigerant undergoing the low-pressure compression stage.
  • Document D1 ( EP 1 655 492 A1 ) relates to a rotary-type enclosed compressor and refrigeration cycle apparatus wherein a vane of a first cylinder is compressed and urged by a spring member and a vane of a second cylinder is compressed and urged corresponding to a differential pressure between an intra-casing pressure guided into a vane chamber and a suction pressure or discharge pressure guided to the cylinder chamber.
  • a pressure shift mechanism which guides the suction pressure or discharge pressure has a branch pipe having one end connected to a high pressure side of the refrigeration cycle, another end connected to a suction pipe, a first on-off valve in a midway portion and a second on-off valve or a check valve, which is provided in the suction pipe on a side upstream of a connection portion of the branch pipe and on a side downstream of an oil returning opening in an accumulator.
  • KR 940001355 B1 discloses a rotary compressor.
  • a motor is positioned in a shell and a rotating shaft is installed to penetrate through the motor.
  • a cylinder is positioned below the motor, and an eccentric portion fitted around the rotating shaft and a roller fitted into the eccentric portion are positioned in the cylinder.
  • a refrigerant outlet hole and a refrigerant inlet hole are formed in the cylinder, and a vane preventing low-pressure non-compressed refrigerant from being mixed with high-pressure compressed refrigerant is installed between the refrigerant outlet hole and the refrigerant inlet hole.
  • a spring is installed at one end of the vane to maintain the eccentrically-rotated roller and the vane to be in contact with each other.
  • KR 20050062995 A discloses a twin rotary compressor.
  • the twin rotary compressor includes two cylinders 1035 and 1045 compressing the same capacity and a middle plate 1030, and thus doubles a compression capacity as compared with a 1-stage compressor.
  • KR 20070009958 A discloses a 2-stage rotary compressor.
  • a motor unit 2014 having a stator 2007 and a rotor 2008 is provided at an inside upper portion of a hermetic container 2013 of a compressor 2001, and a rotating shaft 2002 connected to the motor unit 2014 is provided with two eccentric portions.
  • a main bearing 2009, a high-pressure compression element 2020b, a middle plate 2015, a low-pressure compression element 2020a and a sub bearing 2019 are successively stacked from the motor unit side 2014 with respect to the rotating shaft 2002.
  • a middle pipe 2040 is provided to introduce refrigerant compressed in the low-pressure compression element 2020a into the high-pressure compression element 2020b.
  • the rotary compressor includes a frequency variable motor with a variable operating frequency as the motor unit.
  • the operating frequency of the frequency variable motor is varied according to changes in the cooling capacity required of the compressor, thereby varying the compression capacity of the compressor.
  • a control unit controlling the compressor receives an input of the cooling capacity required of the compressor or senses the cooling capacity and controls an output frequency through a converter and an inverter.
  • the converter receives an input of commercial power AC and converts the AC into DC to rectify a commercial frequency into the DC, and the inverter re-converts the DC into a desired AC voltage/frequency.
  • the frequency variable motor which is the motor unit, drives a compression mechanism unit of the compressor at a frequency controlled by the control unit using the AC frequency-converted by the inverter.
  • FIG. 3 is a graph of efficiency and yearly operating time of a compressor including a conventional DC frequency variable motor as a motor unit by cooling and heating loads (operating frequencies).
  • a variable speed DC inverter compressor generally used for heating and cooling operations has the maximum efficiency during the mid to high speed operation.
  • the variable speed DC inverter compressor has the longest yearly operating time in the low to mid speed range. Therefore, it is necessary to improve the performance of the variable speed DC inverter compressor during the low to mid speed operation of a large air-conditioning load and high using frequency.
  • the present invention has been made in an effort to solve the above-described problems of the prior art, and an object of the present invention is to prevent reduction of energy efficiency of a frequency variable motor, when an inverter compressor using a DC frequency variable motor as a motor unit operates the frequency variable motor at a low speed to generate a low compression capacity as required.
  • Another object of the present invention is to provide a frequency variable compressor and a control method thereof which can control the total compression capacity of a compression mechanism unit by controlling two compression mechanism units driven by an inverter compressor to selectively compress refrigerant by either a twin compression method or a 2-stage compression method according to a cooling capacity required of the compressor, aside from controlling an operating frequency of a frequency variable motor.
  • a further object of the present invention is to provide a frequency variable compressor and a control method thereof which can improve energy efficiency in a small compression capacity by controlling two compression mechanism units to compress refrigerant by a 2-stage compression method, instead of decelerating the speed of a DC frequency variable motor, when a small compression capacity is required of the compressor.
  • a further object of the present invention is to provide a frequency variable compressor and a control method thereof which can improve efficiency of the compressor by controlling a compression mechanism unit to compress refrigerant by a 2-stage compression method, when a small compression capacity is required of the compressor and a DC frequency variable motor is operated at a low speed.
  • a frequency variable compressor including: a shell defining a hermetic space; an accumulator temporarily storing refrigerant before introducing the refrigerant into the shell; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a frequency variable motor positioned in the shell and transferring power to the rolling pistons of the first and second compression mechanism units through a rotating shaft; and a valve controlling the flow of the refrigerant such that the first and second compression mechanism units compress the refrigerant in a twin rotary compressor type or a 2-stage rotary compressor type.
  • the frequency variable compressor further includes a passage through which the refrigerant is sucked into or discharged from the first and second compression mechanism units, wherein the valve changes the refrigerant suction or discharge direction in the passage.
  • the passages through which the refrigerant discharged from the first compression mechanism unit flows includes an inner passage through which the compressed refrigerant is discharged into the shell and a mid-pressure passage through which the compressed refrigerant is discharged to the valve.
  • the passage through which the refrigerant introduced from the second compression mechanism unit flows is selectively connected by the valve to either a passage connecting the accumulator to the valve or a mid-pressure passage through which the compressed refrigerant is discharged from the first compression mechanism unit to the valve.
  • the passages through which the refrigerant to be sucked into the second compression mechanism unit flows includes a passage into which the refrigerant is sucked from the accumulator and a passage into which the refrigerant compressed in the first compression mechanism unit is sucked.
  • the frequency variable compressor further includes a control unit controlling the opening and closing of the valve, wherein the control unit controls the valve to compress the refrigerant in the 2-stage rotary compressor type when a small cooling capacity is required of the compressor and in the twin rotary compressor type when a large cooling capacity is required of the compressor.
  • control unit controls the speed of the frequency variable motor according to a cooling capacity required of the compressor.
  • control unit controls the valve such that the first and second compression mechanism units compress the refrigerant in the 2-stage rotary compressor type.
  • a frequency variable compressor including: a shell defining a hermetic space; an accumulator temporarily storing refrigerant before introducing the refrigerant into the shell; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a frequency variable motor positioned in the shell and transferring power to the rolling pistons of the first and second compression mechanism units through a rotating shaft; a first suction passage through which the refrigerant is sucked into the first compression mechanism unit; a first discharge passage through which the refrigerant is discharged from the first compression mechanism unit; a second suction passage through which the
  • valve closes the rest of the second suction passage when some part of the second suction passage is connected to the mid-pressure passage, and opens the rest of the second suction passage when some part of the second suction passage is disconnected from the mid-pressure passage.
  • the frequency variable compressor further includes a first discharge valve provided at one end of the first discharge passage and opening the first discharge passage over a determined pressure to discharge the refrigerant into the shell.
  • the opening pressure of the first discharge valve is determined not to open the first discharge valve when the mid-pressure passage is connected to some part of the second suction passage, such that the refrigerant discharged from the first compression mechanism unit is sucked into the second suction passage.
  • the frequency variable compressor further includes a lower bearing positioned below the first compression mechanism unit and temporarily storing the refrigerant discharged from the first compression mechanism unit, the first discharge passage being connected to the lower bearing.
  • the frequency variable compressor further includes a mid-pressure discharge valve installed at the lower bearing and opened when the refrigerant compressed in the first compression mechanism unit has a pressure over a determined value.
  • the mid-pressure passage is connected to the lower bearing.
  • first discharge passage penetrates through the first compression mechanism unit and the second compression mechanism unit.
  • the mid-pressure passage is defined by a pipe having both ends positioned on the first discharge passage and the valve, respectively.
  • the pipe defining the mid-pressure passage has one end inserted into the second compression mechanism unit and is connected to the first discharge passage defined in the second compression mechanism unit.
  • the pipe defining the mid-pressure passage is upwardly extended from the second compression mechanism unit and connected to the valve.
  • a frequency variable compressor including: a shell defining a hermetic space; an accumulator temporarily storing refrigerant before introducing the refrigerant into the shell; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a frequency variable motor positioned in the shell and transferring power to the rolling pistons of the first and second compression mechanism units through a rotating shaft; a first suction passage through which the refrigerant is sucked into the first compression mechanism unit; a first discharge passage through which the refrigerant is discharged from the first compression mechanism unit into the shell; a second suction passage
  • the frequency variable compressor further includes a check valve positioned on the first discharge passage.
  • the frequency variable compressor further includes a check valve positioned on the second suction passage.
  • a frequency variable compressor including: a shell defining a hermetic space; a plurality of compression mechanism units positioned in the shell and compressing refrigerant; a frequency variable motor positioned in the shell and transferring power to the plurality of compression mechanism units through a rotating shaft; and a valve controlling the suction and discharge directions with respect to the plurality of compression mechanism units such that the plurality of compression mechanism units compress the refrigerant in a twin rotary compressor type or a 2-stage rotary compressor type.
  • a frequency variable compressor including: a shell defining a hermetic space; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a lower bearing positioned below the first compression mechanism unit and temporarily storing the refrigerant discharged from the first compression mechanism unit; an upper bearing positioned over the second compression mechanism unit; a first discharge port positioned in the upper bearing and opened when the refrigerant discharged from the first compression mechanism unit has a pressure over a determined value; a second discharge port positioned in the upper bearing and opened when the refrigerant discharged from the second compression mechanism unit has a pressure over
  • a frequency variable compressor including: a shell defining a hermetic space; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; an inner passage formed such that the refrigerant compressed in the first compression mechanism unit is discharged into the shell through the first compression mechanism unit and the second compression mechanism unit; an accumulator temporarily storing the refrigerant before introducing the refrigerant into the shell; a 4-way valve selecting a refrigerant discharge passage of the first compression mechanism unit and a refrigerant suction passage of the second compression mechanism unit such that the first compression mechanism unit and the second compression mechanism unit
  • the mid-pressure suction pipe penetrates through an upper portion of the shell and is fixed by the shell.
  • a frequency variable compressor including: a shell defining a hermetic space; a first compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a second compression mechanism unit positioned in the shell, including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole and a vane, and compressing refrigerant; a lower bearing positioned below the first compression mechanism unit and temporarily storing the refrigerant discharged from the first compression mechanism unit; an upper bearing positioned over the second compression mechanism unit; a discharge port positioned in the upper bearing and opened when the refrigerant discharged from the second compression mechanism unit has a pressure over a determined value; an accumulator temporarily storing the refrigerant before introducing the refrigerant into the shell; a first suction pipe providing a
  • a counter-flow prevention valve is installed at a portion of the first discharge pipe connecting the 4-way valve to the shell.
  • a counter-flow prevention valve is installed at a portion of the second suction pipe connecting the 4-way valve to the accumulator.
  • a control method of a frequency variable compressor including: a first step of receiving, at a control unit, an input of a required cooling capacity; a second step of controlling a valve to select either a twin compression method or a 2-stage compression method as a driving method of a compression mechanism unit; and a third step of controlling a driving speed of a frequency variable motor.
  • a control method of a frequency variable compressor including: a first step of receiving, at a control unit, an input of a required cooling capacity; a second step of comparing the required cooling capacity with a compression capacity obtained by a twin compression method at a speed in which a frequency variable motor has the maximum efficiency; and a third step of selecting either the twin compression method or a 2-stage compression method as a driving method of a compression mechanism unit according to the result of the second step.
  • control method further includes a fourth step of controlling a driving speed of the frequency variable motor.
  • the third step controls a 4-way valve to select the driving method of the compression mechanism unit.
  • the compressor can be operated in the mid to high speed operation range in which the frequency variable motor has relatively high efficiency, unlike the conventional twin compressor.
  • the compressor compresses the refrigerant by the 2-stage compression method at a low operating frequency in which efficiency of the frequency variable motor is degraded, and thus reduces an over-compression loss more than by a one-stage compression method or a twin compression method.
  • the compressor when a cooling capacity required for compression increases, the compressor converts the compression method into the twin compression method and raises the operating frequency of the frequency variable motor to increase the compression capacity. Accordingly, it is possible to increase the compressible capacity range of the compressor and considerably improve energy efficiency of the compressor.
  • FIG. 4 is a graph of changes in an operating frequency of a general frequency variable compressor by the time elapsed.
  • the compressor is a part of a freezing cycle of cooling apparatuses including air conditioners and refrigerators or heating apparatuses using heat pumps.
  • the cooling apparatus or the heating apparatus is initially operated in a power mode until the ambient temperature reaches a desired temperature and in a saving mode after the ambient temperature reaches the desired temperature.
  • the power mode is an operating mode which increases a compression capacity of the compressor to raise the cooling or heating capability of the cooling apparatus or the heating apparatus
  • the saving mode is an operating mode which decreases the compression capacity of the compressor to lower the cooling or heating capability of the cooling apparatus or the heating apparatus.
  • an operating frequency of the motor is set at a high to mid frequency (about 120 Hz to 60 Hz) in the power mode and at a mid to low frequency (about 60 Hz to 20 Hz) in the saving mode.
  • the general cooling apparatus or heating apparatus is initially operated in the power mode to cause a change in temperature until the ambient temperature reaches the desired temperature, and normally operated in the saving mode to maintain the desired temperature after the ambient temperature reaches the desired temperature. Accordingly, the operating time is much longer in the saving mode than in the power mode.
  • the frequency variable compressor has the maximum efficiency in mid-frequencies (about 50 Hz to 70 Hz), generally maintains high efficiency in high frequencies (over 70 Hz), and has low efficiency in low frequencies (below 50 Hz). Therefore, it is necessary to improve efficiency of the frequency variable compressor in the low-frequency (below 50 Hz) region.
  • the low-frequency region, the mid-frequency region and the high-frequency region may be dependent upon detailed specifications of the frequency variable motor.
  • the region in which the frequency variable motor has the maximum efficiency is set as the mid-frequency region
  • the region in which frequencies are lower than the mid-frequencies and efficiency of the frequency variable motor is sharply reduced is set as the low-frequency region
  • the region in which frequencies are higher than the mid-frequencies and efficiency of the frequency variable motor is gradually reduced is set as the high-frequency region.
  • the mid-frequency region is a frequency region of efficiency which is not different from the maximum efficiency of the frequency variable motor by over 5 %.
  • the frequency variable compressor includes a plurality of compression chambers.
  • the compression chamber is a space in which the sucked refrigerant is compressed.
  • the compression chamber is a space defined in a compression mechanism unit including a cylinder and a rolling piston.
  • One compression chamber may be defined in one compression mechanism unit, or two or more compression chambers may be defined in one compression mechanism unit.
  • a plurality of compression chambers may be defined in one compression mechanism unit, compression chambers as many as compression mechanism units may be defined in the plurality of compression mechanism units, and compression chambers more than compression mechanism units may be defined in the plurality of compression mechanism units.
  • the process in which the refrigerant is sucked into the plurality of compression chambers, compressed therein and discharged therefrom may be performed in parallel.
  • the representative examples of compressing the refrigerant in parallel in the plurality of compression chambers are a twin (double) compressor, a triple compressor, and so on.
  • the refrigerant may be sucked into one of the plurality of compression chambers, compressed therein, sucked again into another compression chamber, compressed therein and discharged therefrom.
  • the representative examples of sequentially compressing the refrigerant in the plurality of compression chambers are a 2-stage compressor, a 3-stage compressor, and so on.
  • the frequency variable compressor compresses the refrigerant in parallel in the plurality of compression chambers when it is operated over a mid-frequency and sequentially compresses the refrigerant in the plurality of compression chambers when it is operated at a low frequency.
  • an over-compression loss occurs in the compressor.
  • the compression loss occurs merely in the final-stage compression.
  • the volume of the refrigerant to be compressed is smaller in the final stage of the multi-stage compression than the 1-stage compression or the parallel compression, and thus the compression loss is also smaller.
  • the frequency variable compressor compresses the refrigerant by the multi-stage compression method for sequentially compressing the refrigerant in the plurality of compression chambers.
  • the frequency variable compressor includes a plurality of compression chambers in a shell which are unit spaces for refrigerant compression, and a frequency variable motor supplying a driving force to a compression mechanism unit to compress the refrigerant in the compression chamber.
  • the compression chamber is provided in the compression mechanism unit.
  • One or plural compression chambers may be defined in one compression mechanism unit.
  • a refrigerant suction passage through which the refrigerant is introduced into the compression chamber and a refrigerant discharge passage through which the refrigerant is discharged from the compression chamber to the shell must be provided to compress the refrigerant in the compression chamber and discharge the refrigerant therefrom.
  • At least one (hereinafter, referred to as 'first compression chamber') of the plurality of compression chambers includes a first discharge passage through which the compressed refrigerant is discharged into the shell and a mid-pressure passage through which the compressed refrigerant is sucked into at least another one (hereinafter, referred to as 'second compression chamber') of the plurality of compression chambers.
  • the mid-pressure passage connected to the first compression chamber is selectively connected to a second suction passage connected to the second compression chamber. That is, the mid-pressure passage and the second suction passage can be connected or disconnected to/from each other by a valve.
  • the second suction passage is divided into two parts at the valve-connected section.
  • the second suction passage can be divided into a part (first part) connected directly to the second compression chamber and allowing the refrigerant to be sucked into the second compression chamber and a part (second part) connected to the first part and introducing low-pressure refrigerant.
  • the valve disconnects the mid-pressure passage from the second suction passage, the refrigerant discharged from the first compression chamber cannot be sucked into the second suction passage through the mid-pressure passage, and thus is discharged into the shell through the first discharge passage. Moreover, in parallel to this, the low-pressure refrigerant is sucked into the second suction passage, compressed in the second compression chamber, and discharged into the shell.
  • the valve connects the mid-pressure passage to the first part of the second suction passage, the valve prevents the low-pressure refrigerant from being sucked into the second part of the second suction passage and allows the refrigerant compressed in the first compression chamber to be sucked into the first part of the second suction passage through the mid-pressure passage.
  • the refrigerant compressed in the first compression chamber is not discharged into the shell through the first discharge passage but sucked into the second compression chamber through the mid-pressure passage due to the suction pressure in the second compression chamber.
  • the refrigerant sucked into the second compression chamber may be recompressed and discharged into the shell. Further, the refrigerant compressed in the second compression chamber may be sucked into another one (third compression chamber) of the plurality of compression chambers, compressed as the third stage, and then discharged into the shell.
  • FIG. 5 is a graph of efficiency of a frequency variable compressor according to the present invention.
  • the frequency variable compressor includes two compression mechanism units, in which one compression chamber is defined in each compression mechanism unit.
  • the 2-stage compression method improved efficiency more than the twin compression method by about 10 to 15 %.
  • the twin compression method was more efficient than the 2-stage compression method.
  • the 2-stage compression method became less efficient than the twin compression method due to a loss caused by a valve. Accordingly, in order to improve efficiency of the compressor in the low-frequency region, when the operating frequency of the frequency variable compressor exists in the low-frequency region, it is preferable to control the valve to compress the refrigerant by the 2-stage compression method. That is, when the operating frequency of the frequency variable compressor exists in the low-frequency region, it is preferable to perform the multi-stage compression in the plurality of compression chambers.
  • FIGS. 6 and 7 are views of a frequency variable compressor according to a first embodiment of the present invention.
  • the frequency variable compressor according to the first embodiment of the present invention includes two compression mechanism units and compresses refrigerant by a twin compression method in a power mode and by a 2-stage compression method in a saving mode.
  • the frequency variable compressor includes a shell 100 forming the external appearance of the compressor, a DC variable speed frequency variable motor 200 (hereinafter, referred to as 'frequency variable motor') is installed in the shell 100 as a motor unit, and a rotating shaft 300 transferring a rotational force of the frequency variable motor 200 is connected to the frequency variable motor 200.
  • 'frequency variable motor' DC variable speed frequency variable motor 200
  • the frequency variable motor 200 is positioned on the upper side in the shell 100, and the rotating shaft 300 is downwardly extended from the frequency variable motor 200.
  • a compression mechanism unit 400 is installed below the frequency variable motor 200, receives power from the frequency variable motor 200 through the rotating shaft 300, and compresses the refrigerant.
  • the compression mechanism unit 400 includes a first compression mechanism unit 410 and a second compression mechanism unit 420 which are rotary compression mechanisms.
  • the first compression mechanism unit 410 and the second compression mechanism unit 420 include cylinders 411 and 421 providing spaces for refrigerant compression, rolling pistons 412 and 422, refrigerant suction holes 410h and 420h, refrigerant discharge holes 410d and 420d, and vanes (not shown), respectively.
  • the first compression mechanism unit 410 and the second compression mechanism unit 420 can compress a determined amount of refrigerant, respectively.
  • a lower bearing 500 is installed below the first compression mechanism unit 410, and an upper bearing 600 is installed over the second compression mechanism unit 420.
  • a mid-pressure discharge valve 510 opened when the refrigerant compressed in the first compression mechanism unit 410 has a pressure over a determined value is installed at the lower bearing 500.
  • the mid-pressure refrigerant discharged through the mid-pressure discharge valve 510 temporarily stays in the lower bearing 500.
  • a first discharge port 610 discharging the refrigerant temporarily stored in the lower bearing 500 into the shell 100 over a determined pressure and a second discharge port 620 discharging the refrigerant compressed in the second compression mechanism unit 420 into the shell 100 are formed in the upper bearing 600.
  • the first discharge port 610 is connected to an inner space of the lower bearing 500 through a discharge passage 820, and the discharge passage 820 provides a refrigerant movement path from the lower bearing 500 to the first discharge port 610.
  • the discharge passage 820 may be formed as an inner passage penetrating through the cylinder 411 of the first compression mechanism unit 410 and the cylinder 421 of the second compression mechanism unit 420 and connecting the lower bearing 500 to the first discharge port 610.
  • the refrigerant is sucked from an accumulator 900 into the first compression mechanism unit 410 and the second compression mechanism unit 420 through suction passages 810, 840 and 850.
  • the refrigerant is introduced from another apparatus constituting the freezing cycle with the frequency variable compressor into the accumulator 900 and temporarily stored therein.
  • the first suction passage 810 and the second suction passage 840 and 850 are connected to the accumulator 900.
  • the refrigerant is divided into liquid refrigerant and gas refrigerant in the accumulator 900 and only the gas-phase refrigerant is sucked into the first suction passage 810 and the second suction passage 840 and 850.
  • a mid-pressure passage 830 connects a part 850 of the second suction passage 840 and 850 to the lower bearing 500 such that the refrigerant compressed first in the first compression mechanism unit 410 is sucked into the second compression mechanism unit 420 through the part 850 of the second suction passage 840 and 850.
  • the double capacity variable inverter compressor includes a 4-way valve 700 connected to the mid-pressure passage 830 and also connected to the middle of the second suction passage 840 and 850 to divide the second suction passage 840 and 850 into two parts 840 and 850.
  • the 4-way valve 700 serves to selectively connect either the other part 840 of the second suction passage 840 and 850 or the mid-pressure passage 830 to the part 850 of the second suction passage 840 and 850 connected to the second mechanism unit 420. Irrespective of the control of the valve 700, the refrigerant is always sucked into the first compression mechanism unit 410 through the first suction passage 810 which is not connected to the valve 700.
  • a control unit controls the valve 700 such that the compression mechanism unit 400 compresses the refrigerant by the twin compression method or the 2-stage compression method. Additionally, the control unit (not shown) not only controls the valve 700 but also controls the speed of the frequency variable motor 200.
  • the control unit receives an input of a cooling capacity required of an indoor unit or the like of the freezing/heating cycle including the double capacity variable inverter compressor or receives information on the cooling capacity and controls the speed of the frequency variable motor 200 or controls the compression method of the compression mechanism unit 400 using the valve 700.
  • the first compression mechanism unit 410 and the second compression mechanism unit 420 may adopt the twin rotary compressor type in which each of the first compression mechanism unit 410 and the second compression mechanism unit 420 compresses a determined amount of refrigerant and discharges the compressed refrigerant into the shell 100, or the 2-stage rotary compressor type in which the first compression mechanism unit 410 compresses the refrigerant and the second compression mechanism unit 420 re-compresses the refrigerant and discharges the 2-stage compressed refrigerant into the shell 100.
  • FIG. 6 illustrates a state where the compression mechanism unit 400 compresses the refrigerant in the twin rotary compressor type, one part 850 of the second suction passage 840 and 850 being connected to the other part 840, the mid-pressure passage 830 being closed.
  • the refrigerant is sucked from the accumulator 900 into the first compression mechanism unit 410 through the first suction passage 810 and into the second compression mechanism unit 420 through the second suction passage 840 and 850 at the same time.
  • the refrigerant sucked into the cylinders 411 and 421 is compressed by the rolling pistons 412 and 422 rotated by power of the frequency variable motor 200 transferred through the rotating shaft 300.
  • the refrigerant compressed over a determined pressure in the first compression mechanism unit 410 opens the mid-pressure discharge valve 510 and is discharged to the lower bearing 500 through the refrigerant discharge hole 410d. Since the mid-pressure passage 830 has been closed by the valve 700, the refrigerant cannot be introduced into the part of the second suction passage 840 and 850. Therefore, the refrigerant temporarily stored in the lower bearing 500 is discharged into the shell 100 through the first discharge port 610 along the discharge passage 820.
  • a first discharge valve 610v is installed on the first discharge port 610 to discharge the refrigerant into the shell 100 through the first discharge port 610 when the refrigerant has a pressure over a determined value.
  • the second compression mechanism unit 420 compresses the refrigerant sucked through the second suction passage 840 and 850 and discharges the refrigerant into the shell 100 through the second discharge port 620.
  • a second discharge valve 620v is installed on the second discharge port 620 to discharge the refrigerant into the shell 100 when the refrigerant has a pressure over a determined value.
  • each of the first compression mechanism unit 410 and the second compression mechanism unit 420 compresses the determined amount of refrigerant and discharges the refrigerant into the shell 100.
  • the total compression capacity of the refrigerant is equal to the sum of the compression capacity of the first compression mechanism unit 410 and the compression capacity of the second compression mechanism unit 420.
  • the total compression capacity of the compressor can be controlled according to the speed (frequency) of the frequency variable motor 200.
  • FIG. 7 illustrates a state where the compression mechanism unit 400 compresses the refrigerant in the 2-stage compressor type, one part 850 of the second suction passage 840 and 850 being disconnected from the other part 840 and connected to the mid-pressure passage 830.
  • the refrigerant stored in the accumulator 900 is sucked into the first compression mechanism unit 410 through the first suction passage 810, compressed therein, and discharged to the lower bearing 500.
  • the refrigerant discharged to the lower bearing 500 is sucked into the second compression mechanism unit 420 through the mid-pressure passage 830 and the part 850 of the second suction passage 840 and 850.
  • a sound pressure is generated in the cylinder 421 due to the rolling piston 422 fitted onto the rotating shaft 300 and rotated in the cylinder 421, and operated as a refrigerant suction pressure. Accordingly, the refrigerant discharged to the lower bearing 500 is not discharged into the shell 100 through the discharge passage 820 as shown in FIG.
  • the second compression mechanism unit 420 re-compresses the refrigerant compressed in the first compression mechanism unit 410 and discharges the 2-stage compressed refrigerant into the shell 100 through the second discharge port 620 of the upper bearing 600.
  • the first discharge valve 610v installed on the first discharge port 610 is preferably a counter-flow prevention valve such that the refrigerant in the shell 100 is not sucked into the second compression mechanism unit 420 again through the first discharge port 610-the discharge passage 820-the lower bearing 500-the mid-pressure passage 830 due to the suction pressure of the second compression mechanism unit 420.
  • FIGS. 8 and 9 are views of a frequency variable compressor according to a second embodiment of the present invention.
  • a shell 100, a frequency variable motor 200, a rotating shaft 300, a compression mechanism unit 400, a lower bearing 500, an upper bearing 600, a valve 700 and an accumulator 900 are the same as those of the first embodiment of the present invention, and thus detailed description thereof will be omitted.
  • a mid-pressure passage 830' penetrates an upper portion of the shell 100. This can significantly reduce piping vibration generated in the mid-pressure passage 830'.
  • a discharge passage 820 and a first discharge port 610 are formed in the opposite direction to a mid-pressure discharge valve 510 and a second discharge port 620 such that the discharge passage 820 and the first discharge port 610 do not overlap with the mid-pressure discharge valve 510 and the second discharge port 620.
  • the discharge passage 820 and the first discharge port 610 are very close to the mid-pressure discharge valve 510 and the second discharge port 620.
  • the discharge passage 820 is distant from the mid-pressure discharge valve 510, i.e., if the discharge passage 820 is distant from a discharge hole 410d of a first compression mechanism unit 410, when the refrigerant flows, its pressure loss is generated in the lower bearing 500. Therefore, if the mid-pressure passage 830' is connected to the discharge passage 820, i.e., inserted into a cylinder 421 of a second compression mechanism unit 420, the length of the mid-pressure passage 830' can be considerably reduced. Thus, when the refrigerant flows through the mid-pressure passage 830', its pressure loss can be reduced.
  • FIG. 8 illustrates a state where the compressor is operated as a twin rotary compressor
  • FIG. 9 illustrates a state where the compressor is operated as a 2-stage rotary compressor.
  • the construction of the second embodiment is the same as that of the first embodiment except the position of the mid-pressure passage 830', and thus the operation methods of the twin compressor and the 2-stage compressor are the same as those of the first embodiment.
  • FIGS. 10 and 11 are views of a frequency variable compressor according to a third embodiment of the present invention.
  • FIG. 10 illustrates a state where the compressor compresses refrigerant by a twin compression method
  • FIG. 11 illustrates a state where the compressor compresses refrigerant by a 2-stage compression method.
  • the frequency variable compressor according to the third embodiment of the present invention includes a shell 100, a frequency variable motor 200, a rotating shaft 300, a compression mechanism unit 400, a lower bearing 500, an upper bearing 600, a valve 700 and an accumulator 900.
  • the third embodiment is the same as the first and second embodiments except the construction of suction passages and discharge passages.
  • the refrigerant is sucked into a first compression mechanism unit 410 through a first suction passage 810, compressed therein, and discharged to the lower bearing 500.
  • the compressed refrigerant flows to the valve 700 through a mid-pressure passage 830" connected to the lower bearing 500.
  • the mid-pressure passage 830" is disconnected from a part 850 of a second suction passage 840 and 850 by the valve 700, and the other part 840 of the second suction passage 840 and 850 communicates with the part 850 of the second suction passage 840 and 850.
  • the refrigerant of the mid-pressure passage 830" is discharged into the shell 100 through a first discharge passage 820' connected to the valve 700.
  • a check valve 800v is installed on the first discharge passage 820' to prevent the refrigerant from being introduced from the shell 100 to the first discharge passage side 820'.
  • the refrigerant is sucked from the accumulator 900 to a second compression mechanism unit 420 through the second suction passage 840 and 850, compressed therein, and discharged into the shell 100.
  • the driving by the 2-stage compression method will be described with reference to FIG. 11 .
  • the refrigerant is sucked into the first compression mechanism unit 410 through the first suction passage 810, compressed therein, and discharged to the lower bearing 500.
  • the compressed refrigerant flows to the valve 700 through the mid-pressure passage 830" connected to the lower bearing 500.
  • the valve 700 is controlled to allow the part 850 of the second suction passage 840 and 850 and the mid-pressure passage 830" to communicate with each other and to close the other part 840 of the second suction passage 840 and 850.
  • the mid-pressure refrigerant sucked into the second compression mechanism unit 420 through the mid-pressure passage 830" and the part 850 of the second suction passage 840 and 850 is compressed into a high pressure and discharged into the shell 100 through a second discharge port 620.
  • a first discharge port is not specially formed.
  • the check valve 800v allows the refrigerant to flow from the valve 700 into the shell 100 but disallows the refrigerant to flow from the shell 100 into the valve side 700. Therefore, it is possible to prevent the refrigerant from flowing backward from the shell 100 having a higher pressure than the mid-pressure passage 830" or the discharge passage 820 to the discharge passage 820.
  • the frequency variable motor 200 has the maximum efficiency in the middle of its speed (operating frequency) range. In addition, the frequency variable motor 200 has much higher efficiency in the mid to high speed operation than the low to mid-speed operation. Accordingly, a control unit (not shown) preferably controls the frequency variable motor 200 to perform the mid to high speed operation.
  • FIG. 12 is a graph of the comparison of efficiency between a frequency variable compressor according to an embodiment of the present invention and a conventional inverter compressor.
  • first and second compression mechanism units 410 and 420 have the same compression capacity
  • the 2-stage compression method can reduce the compression capacity by about 50 % as compared with the twin compression method. Therefore, when a capacity compressed by operating the conventional compressor in the low to mid speed section by a frequency variable motor 200 is compressed by the 2-stage compression method, it can be compressed in the mid to high speed section.
  • a capacity compressed by the twin compression method at a speed in which the frequency variable motor 200 has maximum efficiency is '100' and a compression capacity of the first and second compression mechanism units 410 and 420 is '50', respectively.
  • a required cooling capacity is '70'
  • the compression capacity of the compression mechanism unit 400 is about '50'. Accordingly, when the speed of the frequency variable motor 200 is raised to 140 %, the compressor can perform the high-speed operation. As a result, the compressor can be operated in the mid to high speed operation range in which the frequency variable motor 200 has relatively high efficiency.
  • the frequency variable compressor according to the present invention can increase the compressible capacity range and considerably improve energy efficiency.
  • the 2-stage compression method has a smaller over-compression loss than the 1-stage compression method or the twin compression method.
  • the control unit controls the operating frequency of the frequency variable motor to adjust the capacity of the refrigerant compressed in the compressor to the compression capacity required of the compressor.
  • the control unit controls the valve to compress the refrigerant in the plurality of compression chambers by multiple steps. It is more effective to improve efficiency of the compressor at an operating frequency of the low-frequency region having relatively long operating time than the other operating frequency regions.
  • a control method of a frequency variable compressor will be described.
  • a refrigerant compression capacity per unit time required of the compressor is large at an initial stage but small after the ambient temperature reaches a desired temperature. Therefore, as illustrated in FIG. 4 , an operating frequency of the conventional frequency variable compressor is gradually reduced with the passage of time. After the ambient temperature reaches a desired temperature, the compressor is operated at a low frequency of 30 Hz to 40 Hz.
  • the frequency variable compressor according to the present invention starts to be operated by the multiple compression method such as the twin compression method because a required compression capacity is large at an initial stage of the operation.
  • an operating frequency of the frequency variable compressor of the present invention is controlled similarly to the operating frequency of the conventional frequency variable compressor of FIG. 4 until the ambient temperature reaches a desired temperature.
  • a control unit controlling a frequency variable motor adjusts the operating frequency of the motor to a low frequency.
  • the control unit controls the connection of a suction passage, a discharge passage and a mid-pressure passage connected to a plurality of compression chambers and changes the flow of the refrigerant, thereby compressing the refrigerant by the multi-stage compression method.
  • a control unit receives an input of a required cooling capacity from another apparatus of a cycle including the frequency variable compressor or receives information on the input required cooling capacity.
  • the control unit compares the required cooling capacity with a compression capacity obtained by the twin compression method at a mid speed (a speed in which a frequency variable motor has the maximum efficiency). If the required cooling capacity is equal to or greater than the compression capacity obtained by the twin compression method at the mid speed, the control unit controls a valve to operate a compression mechanism unit by the twin compression method. If the required cooling capacity is smaller than the compression capacity obtained by the twin compression method at the mid speed, the control unit controls the valve to operate the compression mechanism unit by the 2-stage compression method. After determining either the twin compression method or the 2-stage compression method as the compression method, the control unit controls the speed of the frequency variable motor to generate the compression capacity equivalent to the required cooling capacity.

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Claims (13)

  1. Frequenzvariabler Verdichter, der aufweist:
    ein Gehäuse (100), das einen hermetischen Raum definiert;
    mehrere Verdichtungskammern (410, 420), die in dem Gehäuse bereitgestellt sind und Kältemittel darin verdichten; und
    einen frequenzvariablen Motor (200), der Leistung erzeugt, um das Kältemittel in der Verdichtungskammer zu verdichten, wobei der Bereich, in dem der frequenzvariable Motor (200) den maximalen Wirkungsgrad hat, als ein Mittelfrequenzbereich festgelegt wird, wobei der Bereich, in dem Frequenzen niedriger als die mittleren Frequenzen sind und der Wirkungsgrad des frequenzvariablen Motors (200) stark verringert ist, als ein Niederfrequenzbereich festgelegt wird, und der Bereich, in dem Frequenzen höher als die mittleren Frequenzen sind und der Wirkungsgrad des frequenzvariablen Motors (200) allmählich verringert wird, als der Hochfrequenzbereich festgelegt wird,
    gekennzeichnet durch:
    ein Ventil (700), das die Strömung des Kältemittels, das in die mehreren Verdichturigskammern (410, 420) eingesaugt und von ihnen abgegeben wird, steuert, um das Kältemittel in den mehreren Verdichtungskammern (410, 420) sequentiell zu verdichten, wenn der frequenzvariable Motor (200) in dem Niederfrequenzbereich betrieben wird, und um das Kältemittel in den mehreren Verdichtungskammern (410, 420) gleichzeitig zu verdichten, wenn der frequenzvariable Motor (200) in dem Mittelfrequenzbereich und dem Hochfrequenzbereich betrieben wird.
  2. Frequenzvariabler Verdichter nach Anspruch 1, wobei die mehreren Verdichtungskammern (410, 420) in einer Verdichtungsmechanismuseinheit mit einem Wälzkolben (412, 422) und einem Zylinder (411, 421) ausgebildet sind.
  3. Frequenzvariabler Verdichter nach Anspruch 1 oder 2, wobei zwei oder mehr der mehreren Verdichtungskammern (410, 420) zwei Räume sind, die in einer Verdichtungsmechanismuseinheit durch eine Barriere getrennt sind.
  4. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 3, wobei die mehreren Verdichtungskammern (410, 420) in zwei oder mehr Verdichtungsmechanismuseinheiten ausgebildet sind.
  5. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 4, der ferner mehrere Durchgänge (810, 820, 820', 840, 850) aufweist, durch die Kältemittel in die mehreren Verdichtungskammern gesaugt oder von ihnen abgegeben wird,
    wobei das Ventil (700) die Kältemittelansaug- oder Abgaberichtung in den Durchgängen ändert.
  6. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 5, der ferner mehrere Durchgänge (810, 820, 820', 840, 850) aufweist, durch die Kältemittel in die mehreren Verdichtungskammern gesaugt oder von ihnen abgegeben wird,
    wobei das Ventil (700) die mehreren Durchgänge miteinander verbindet oder voneinander trennt.
  7. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 6, wobei eine oder mehrere der mehreren Verdichtungskammern (410, 420) mit einem inneren Durchgang (820), durch den das verdichtete Kältemittel in das Gehäuse abgegeben wird, und einem Mitteldruckdurchgang (830, 830', 830"), durch den das verdichtete Kältemittel zu der Ventilseite abgegeben wird, verbunden ist/sind, und das Ventil (700) den Mitteldruckdurchgang mit einem Durchgang, durch den das Kältemittel in eine andere der mehreren Verdichtungskammern (410, 420) gesaugt wird, verbindet oder von ihm trennt.
  8. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 7, wobei die mehreren Verdichtungskammern umfassen:
    eine erste Verdichtungsmechanismuseinheit (410) mit einem Wälzkolben (412), einem Zylinder (411), einem Kältemittelansaugloch (410h), einem Kältemittelabgabeloch (410d) und einem Schieber; und
    eine zweite Verdichtungsmechanismuseinheit (420) mit einem Wälzkolben (422), einem Zylinder (421), einem Kältemittelansaugloch (420h), einem Kältemittelabgabeloch (420d) und einem Schieber; und
    wobei der frequenzvariable Motor (200) in dem Gehäuse (100) positioniert ist und Leistung der ersten und zweiten Verdichtungsmechanismuseinheiten (410, 420) durch eine Drehwelle (300) auf die Wälzkolben (412, 422) überträgt, und ferner aufweist:
    einen ersten Ansaugdurchgang (810), durch den das Kältemittel in die erste Verdichtungsmechanismuseinheit (410) gesaugt wird;
    einen ersten Abgabedurchgang, durch den das Kältemittel von der ersten Verdichtungsmechanismuseinheit (410) abgegeben wird;
    einen zweiten Ansaugdurchgang (840, 850), durch den das Kältemittel in die zweite Verdichtungsmechanismuseinheit (420) gesaugt wird;
    einen Mitteldruckdurchgang (830), der den zweiten Ansaugdurchgang (840, 850) mit dem ersten Abgabedurchgang verbindet,
    wobei das Ventil (700) auf dem Mitteldruckdurchgang (830) und dem zweiten Ansaugdurchgang (840, 850) bereitgestellt ist, einen Teil des zweiten Ansaugdurchgangs (840, 850) mit dem Mitteldruckdurchgang (830) verbindet/davon trennt und den Rest des zweiten Ansaugdurchgangs (840, 850) schließt und öffnet.
  9. Frequenzvariabler Verdichter nach einem der Ansprüche 1 bis 8, der ferner aufweist:
    einen Sammler (900), der vor dem Einleiten des Kältemittels in das Gehäuse (100) vorübergehend Kältemittel lagert, wobei die mehreren Verdichtungskammern (410, 420) umfassen:
    eine erste Verdichtungsmechanismuseinheit (410) mit einem Wälzkolben (412), einem Zylinder (411), einem Kältemittelansaugloch (410h), einem Kältemittelabgabeloch (410d) und einem Schieber; und
    eine zweite Verdichtungsmechanismuseinheit (420) mit einem Wälzkolben (422), einem Zylinder (421), einem Kältemittelansaugloch (420h), einem Kältemittelabgabeloch (420d) und einem Schieber; und
    wobei der frequenzvariable Motor (200) in dem Gehäuse positioniert ist und Leistung durch eine Drehwelle (300) auf die Wälzkolben (412, 422) der ersten und zweiten Verdichtungsmechanismuseinheiten (410, 420) überträgt, und ferner aufweist:
    einen ersten Ansaugdurchgang (810), durch den das Kältemittel in die erste Verdichtungsmechanismuseinheit (410) gesaugt wird;
    einen ersten Abgabedurchgang (820', 830"), durch den das Kältemittel von der ersten Verdichtungsmechanismuseinheit (410) in das Gehäuse (100) abgegeben wird;
    einen zweiten Ansaugdurchgang (840, 850), durch den das Kältemittel in die zweite Verdichtungsmechanismuseinheit (420) gesaugt wird; und
    ein 4-Wegeventil (700), das derart gesteuert wird, dass das zu dem ersten Abgabedurchgang (820', 830") abgegebene Kältemittel wahlweise in den zweiten Ansaugdurchgang (840, 850) gesaugt oder in das Gehäuse (100) abgegeben wird, wobei zwei Ventillöcher auf dem zweiten Ansaugdurchgang (840, 850) positioniert sind, wobei die anderen zwei Ventillöcher auf dem ersten Abgabedurchgang (820', 830") positioniert sind.
  10. Frequenzvariabler Verdichter nach Anspruch 9, der ferner ein Rückschlagventil (800v) aufweist, das auf dem ersten Abgabedurchgang (820') und dem zweiten Ansaugdurchgang (840, 850) positioniert ist.
  11. Steuerverfahren eines frequenzvariablen Verdichters, der umfasst:
    mehrere Verdichtungskammern (410, 420);
    einen frequenzvariablen Motor (200), wobei der Bereich, in dem der frequenzvariable Motor (200) den maximalen Wirkungsgrad hat, als ein Mittelfrequenzbereich festgelegt wird, wobei der Bereich, in dem Frequenzen niedriger als die mittleren Frequenzen sind und der Wirkungsgrad des frequenzvariablen Motors (200) stark verringert ist, als ein Niederfrequenzbereich festgelegt wird, und der Bereich, in dem Frequenzen höher als die mittleren Frequenzen sind und der Wirkungsgrad des frequenzvariablen Motors (200) allmählich verringert wird, als der Hochfrequenzbereich festgelegt wird,
    ein Ventil (700), das die Strömung von Kältemittel steuert, das in die mehreren Verdichtungskammern (410, 420) eingesaugt und von ihnen abgegeben wird, und
    eine Steuereinheit, die das Ventil (700) steuert,
    dadurch gekennzeichnet, dass das Steuerverfahren aufweist:
    wenn eine Betriebsfrequenz des frequenzvariablen Motors (200) in dem Niederfrequenzbereich ist, Steuern des Ventils (700), um das Kältemittel in den mehreren Verdichtungskammern (410, 420) in mehreren Stufen zu verdichten;
    wenn eine Betriebsfrequenz des frequenzvariablen Motors (200) in dem Mittelfrequenzbereich und dem Hochfrequenzbereich ist, Steuern des Ventils (700), um das Kältemittel in den mehreren Verdichtungskammern (410, 420) gleichzeitig zu verdichten.
  12. Steuerverfahren nach Anspruch 11, das, wenn eine kleine Verdichtungskapazität des Verdichters benötigt wird, die Betriebsfrequenz des frequenzvariablen Motors (200) auf den Niederfrequenzbereich steuert.
  13. Steuerverfahren nach Anspruch 11 oder 12, wobei die Steuerung der Betriebsfrequenz des frequenzvariablen Motors (200) gemäß Änderungen in der benötigten Verdichtungskapazität und des Verdichtungsverfahrens fortlaufend wiederholt wird.
EP09826234.8A 2008-11-17 2009-10-29 Frequenzvariabler verdichter und steuerverfahren dafür Active EP2372158B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020080114279A KR101268612B1 (ko) 2008-11-17 2008-11-17 주파수 가변 압축기 및 그 제어 방법
PCT/KR2009/006299 WO2010056002A1 (ko) 2008-11-17 2009-10-29 주파수 가변 압축기 및 그 제어 방법

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EP2372158A1 EP2372158A1 (de) 2011-10-05
EP2372158A4 EP2372158A4 (de) 2014-10-29
EP2372158B1 true EP2372158B1 (de) 2017-07-26

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EP (1) EP2372158B1 (de)
KR (1) KR101268612B1 (de)
CN (1) CN102203425A (de)
ES (1) ES2643564T3 (de)
WO (1) WO2010056002A1 (de)

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KR101983049B1 (ko) * 2012-12-28 2019-09-03 엘지전자 주식회사 압축기
KR101973623B1 (ko) * 2012-12-28 2019-04-29 엘지전자 주식회사 압축기
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CN103953544B (zh) * 2014-04-10 2016-01-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机和空调器
KR101667724B1 (ko) * 2014-04-11 2016-10-19 엘지전자 주식회사 원격 관리 서버, 이를 포함하는 원격 통합 관리 시스템 및 원격 관리 방법
CN106232991B (zh) 2014-06-02 2018-11-09 开利公司 螺旋式压缩机
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CN106704189A (zh) * 2015-08-10 2017-05-24 珠海格力节能环保制冷技术研究中心有限公司 压缩机和换热系统
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CN106221839A (zh) * 2016-08-31 2016-12-14 武汉格瑞拓机械有限公司 一种高效节能沼气纯化与增压一体化装置
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KR101268612B1 (ko) 2013-05-29
EP2372158A4 (de) 2014-10-29
WO2010056002A1 (ko) 2010-05-20
EP2372158A1 (de) 2011-10-05
CN102203425A (zh) 2011-09-28
ES2643564T3 (es) 2017-11-23
KR20100055282A (ko) 2010-05-26
US20110271699A1 (en) 2011-11-10

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