WO2010056002A1 - Compresseur à fréquence variable et procédé de commande de celui-ci - Google Patents

Compresseur à fréquence variable et procédé de commande de celui-ci Download PDF

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Publication number
WO2010056002A1
WO2010056002A1 PCT/KR2009/006299 KR2009006299W WO2010056002A1 WO 2010056002 A1 WO2010056002 A1 WO 2010056002A1 KR 2009006299 W KR2009006299 W KR 2009006299W WO 2010056002 A1 WO2010056002 A1 WO 2010056002A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compression
frequency
compressor
shell
Prior art date
Application number
PCT/KR2009/006299
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English (en)
Korean (ko)
Inventor
이승준
Original Assignee
엘지전자 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to ES09826234.8T priority Critical patent/ES2643564T3/es
Priority to US13/127,016 priority patent/US20110271699A1/en
Priority to EP09826234.8A priority patent/EP2372158B1/fr
Priority to CN2009801442618A priority patent/CN102203425A/zh
Publication of WO2010056002A1 publication Critical patent/WO2010056002A1/fr

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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 device that increases pressure by receiving power from a power generator such as an electric motor or a turbine to compress air, refrigerant, or various other working gases. It is widely used throughout.
  • These compressors can be classified into reciprocating compressors for compressing refrigerant while linearly reciprocating inside the cylinders by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder.
  • a rotary compressor for compressing the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder to form a compression space in which the working gas is sucked and discharged between the roller and the cylinder which are eccentrically rotated.
  • a scroll compressor for compressing the refrigerant while the turning scroll is rotated along the fixed scroll to form a compressed space in which the working gas is sucked and discharged between the orbiting scroll and the fixed scroll.
  • the rotary compressor has two rollers and two cylinders at the top and the bottom, and a pair of roller and cylinders at the top and the bottom, and a rotary twin compressor for compressing the part and the rest at the top and the bottom.
  • Two-stage compressor with two rollers and two cylinders in communication one pair compresses relatively low pressure refrigerant and the other compresses relatively high pressure refrigerant after low pressure compression stage Further development.
  • a rotary compressor In the Republic of Korea Patent Publication No. 1994-001001 a rotary compressor is disclosed.
  • the motor is located inside the shell, and a rotating shaft is installed to penetrate the motor.
  • a cylinder is located under the electric motor, and an eccentric portion fitted to the rotating shaft and a roller fitted to the eccentric portion are located inside the cylinder.
  • the cylinder has a coolant discharge hole and a coolant inlet hole, and a vane is provided between the coolant discharge hole and the coolant inlet hole to prevent the uncompressed low pressure refrigerant from mixing with the compressed high pressure refrigerant.
  • a spring is installed at one end of the vane to maintain the eccentric and rotating roller and the vane in contact.
  • Republic of Korea Patent Publication No. 10-2005-0062995 discloses a rotary twin compressor. Referring to FIG. 1, two cylinders 1035 and 1045 and an intermediate plate 1030 which compress the same capacity are provided, and the compression capacity is improved by twice compared to the first stage compressor.
  • Republic of Korea Patent Publication No. 10-2007-0009958 discloses a rotary two-stage compressor.
  • the compressor 2001 includes an electric motor 2014 having a stator 2007 and a rotor 2008 above the inside of the sealed container 2013, and the rotating shaft 2002 connected to the electric mechanism part is 2.
  • the main bearing 2009, the high pressure compression element 2020b, the intermediate plate 2015, the low pressure compression element 2020a and the sub bearing 2019 are stacked in this order from the power mechanism part 2014 side with respect to the rotary shaft 2002. have.
  • an intermediate tube 2040 for introducing refrigerant compressed in the low pressure compression element 2020a into the high pressure compression element 2020b.
  • the rotary compressor may include a frequency variable motor capable of varying the operating frequency as the electric mechanism unit, and may vary the compression capacity of the compressor by varying the operating frequency of the frequency variable motor according to a change in the cooling force required for the compressor.
  • the control unit for controlling the compressor receives or detects the cold power required by the compressor, receives the commercial power (AC), converts it to direct current, and rectifies it to direct current (DC) at a commercial frequency.
  • the output frequency is controlled by controlling the inverter to convert back to frequency.
  • the frequency variable motor which is an electric mechanism unit, drives the compression mechanism unit of the compressor at a frequency regulated by the control unit by using an alternating current frequency converted by the inverter.
  • Figure 3 is a graph showing the efficiency and the annual operating time according to the heating and cooling load (operation frequency) of the compressor having a conventional DC frequency variable motor as the electric mechanism unit.
  • the efficiency of the variable seat DC inverter compressor is the highest in medium to high speed operation.
  • the annual operating time is longest in the range of low speed to medium speed. Therefore, it is required to improve the performance of the variable speed DC inverter compressor during low to medium speed operation, which has a high actual air conditioning load and a high frequency of use.
  • An object of the present invention is to improve the energy efficiency of a frequency variable motor when the inverter compressor adopting a DC frequency variable motor as a transmission mechanism requires a low capacity compression capacity to operate the frequency variable motor at a low speed to adjust the compression capacity. It is done.
  • an object of the present invention is to provide a variable frequency compressor and a control method thereof in which the overall compression capacity of the compression mechanism unit can be adjusted.
  • the present invention when the compression capacity required for the compressor is small, instead of the DC frequency variable motor to reduce the speed to low speed control two compression mechanisms to compress the refrigerant in a two-stage compression method to reduce the energy efficiency when the compression capacity is small
  • An object of the present invention is to provide an improved frequency variable compressor and a control method thereof.
  • the present invention is a variable frequency compressor and its control method that can improve the efficiency of the compressor by compressing the refrigerant in a two-stage compression method when the DC frequency variable motor is operated at a low speed because the compression capacity required for the compressor is small
  • the purpose is to provide.
  • the present invention provides a shell forming a closed space; A plurality of compression chambers provided in the shell and into which the refrigerant is compressed; A frequency variable motor generating power for compressing the refrigerant in the compression chamber; And a valve controlling a flow of the refrigerant sucked and discharged into the plurality of compression chambers so as to sequentially or simultaneously compress the refrigerants in the plurality of compression chambers.
  • a plurality of compression chambers are provided in a compression mechanism including a rolling piston and a cylinder.
  • At least two of the plurality of compression chambers provide a variable frequency compressor, characterized in that the two spaces partitioned by a partition in one compression mechanism.
  • a plurality of compression chambers are provided in at least two compression mechanism units.
  • a plurality of flow paths in which the refrigerant is sucked into the plurality of compression chambers or the refrigerant is discharged from the plurality of compression chambers; further comprising a valve connecting or blocking the plurality of flow paths to each other Provide a variable frequency compressor.
  • At least one of the plurality of compression chambers is connected to an internal flow path for discharging the compressed refrigerant into the hermetic container and an intermediate pressure flow path for discharging the compressed refrigerant to the valve side
  • the present invention provides a variable frequency compressor comprising connecting or blocking a flow path for sucking a refrigerant to another one of the compression chambers and a medium pressure flow path.
  • the present invention also provides a shell forming a closed space;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a frequency variable motor positioned in the shell and transmitting power to the rolling pistons of the first and second compression mechanism units through the rotating shaft;
  • a valve
  • the present invention also provides a shell forming a closed space; An accumulator for temporarily storing a refrigerant before entering the shell; A first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant; A second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant; A frequency variable motor positioned in the shell and transmitting power to the rolling pistons of the first and second compression mechanism units through the 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 through which the refrigerant is sucked into the second compression mechanism unit; And two valve holes are positioned on the second suction
  • variable frequency compressor further comprises a check valve located on the first discharge passage and the second suction passage.
  • the present invention provides a control method of a variable frequency compressor comprising a plurality of compression chambers, a frequency variable motor, a valve for controlling the flow of refrigerant to be discharged to the plurality of compression chambers and a control unit for controlling the valve.
  • a control method of a variable frequency compressor characterized in that the valve is controlled such that the refrigerant is compressed in multiple stages in a plurality of compression chambers when the frequency is less than the middle frequency.
  • a control method of a variable frequency compressor characterized in that when the compression capacity required by the compressor is small, the operating frequency of the variable frequency motor is controlled at a low frequency.
  • the present invention comprises the steps of adjusting the operating frequency of the frequency variable motor according to the required compression capacity; And a refrigerant by any one of a parallel compression method of simultaneously compressing refrigerants in a plurality of compression chambers and a multistage compression method of sequentially compressing refrigerants in a plurality of compression chambers when an operating frequency of the frequency variable motor is less than or equal to a predetermined frequency. And controlling the valve so that the compressor is compressed.
  • the present invention also provides a shell forming a closed space;
  • An accumulator for temporarily storing a refrigerant before entering the shell;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a frequency variable motor positioned in the shell and transmitting power to the rolling pistons of the first and second compression mechanism units through the rotating shaft;
  • a valve for controlling the flow of the refrigerant to compress the refrigerant in a twin rotary compressor type or a two-stage rotary compressor type in the first and second compression mechanism units.
  • the first and second compression mechanism further comprises a flow path for the refrigerant is sucked or discharged, the valve is variable frequency, characterized in that for changing the suction or discharge direction of the refrigerant in the flow path Provide a compressor.
  • the flow path through which the refrigerant discharged from the first compression mechanism portion flows includes an internal flow path for discharging the compressed refrigerant into the sealed container and an intermediate pressure flow path for discharging the refrigerant compressed by the valve.
  • a variable frequency compressor is provided.
  • any one of a flow path through which the refrigerant flowing from the second compression mechanism portion flows may include one of a flow path connecting the accumulator and the valve and an intermediate pressure flow passage discharging the refrigerant compressed into the valve from the first compression mechanism portion.
  • a variable frequency compressor is provided which is selectively connected by a valve.
  • the flow path through which the refrigerant sucked into the second compression mechanism unit includes a glass into which the refrigerant is sucked from the accumulator and a flow path through which the refrigerant compressed by the first compression mechanism unit is sucked.
  • control unit for controlling the opening and closing of the valve; further comprising a control unit, and adjusts the valve to compress the refrigerant in the form of a two-stage rotary compressor when the cooling force required for the compressor is small
  • a frequency variable compressor characterized in that the valve is adjusted to compress the refrigerant into the twin rotary compressor fluorspar when the required cold power is large.
  • control unit provides a variable frequency compressor, characterized in that for controlling the speed of the frequency variable motor according to the cooling power required by the compressor.
  • control unit may be configured to control the valve to compress the refrigerant in the form of a two-stage rotary compressor when the frequency variable motor is operated at a speed lower than the maximum efficiency. It provides a variable displacement inverter compressor characterized in that the adjustment.
  • the present invention also provides a shell forming a closed space; An accumulator for temporarily storing a refrigerant before entering the shell; A first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant; A second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant; A frequency variable motor positioned in the shell and transmitting power to the rolling pistons of the first and second compression mechanism units through the 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 refrigerant is sucked into the second compression mechanism unit; An intermediate pressure flow path connecting the second suction flow path and the first
  • the valve closes the remaining part of the second suction flow path when the portion of the second suction flow path and the intermediate pressure flow path is connected, and the portion of the second suction flow path and the intermediate pressure flow path are blocked from each other.
  • a variable frequency compressor is provided, wherein the remaining part of the second suction channel is opened.
  • variable frequency characterized in that it further comprises; a first discharge valve for opening the first discharge flow path to the end of the first discharge flow path at a predetermined pressure or more, the refrigerant is discharged into the shell; Provide a compressor.
  • the opening pressure of the first discharge valve is such that the refrigerant discharged from the first compression mechanism is sucked into the second suction flow path when the intermediate pressure flow path and a part of the second suction flow path are connected to each other.
  • a frequency variable compressor characterized in that the discharge valve is determined not to open.
  • the lower bearing is located in the lower portion of the first compression mechanism, the refrigerant discharged from the first compression mechanism is temporarily stored, the lower bearing connected to the first discharge passage; It provides a frequency variable compressor.
  • variable frequency compressor further comprising an intermediate pressure discharge valve is installed in the lower bearing, and opened when the refrigerant compressed in the first compression mechanism is a predetermined pressure or more.
  • variable frequency compressor characterized in that the intermediate pressure flow path is connected to the lower bearing.
  • variable frequency compressor wherein the first discharge passage passes through the first compression mechanism portion and the second compression mechanism portion.
  • the intermediate pressure flow path provides a variable frequency compressor, characterized in that formed by a pipe located at both ends of the first discharge flow path and the valve, respectively.
  • the pipe forming the intermediate pressure flow path is provided with a variable frequency compressor, one end of which is inserted into the second compression mechanism portion and connected to the first discharge passage formed in the second compression mechanism portion. do.
  • variable frequency compressor wherein the pipe forming the intermediate pressure flow passage extends upward from the second compression mechanism and is connected to the valve.
  • the present invention also provides a shell forming a closed space;
  • An accumulator for temporarily storing a refrigerant before entering the shell;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a frequency variable motor positioned in the shell and transmitting power to the rolling pistons of the first and second compression mechanism units through the 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;
  • variable frequency compressor further comprising a check valve located on the first discharge passage.
  • variable frequency compressor further comprises a check valve located on the second suction flow path.
  • the present invention also provides a shell forming a closed space; Located in the shell, a plurality of compression mechanism portion for compressing the refrigerant; Located in the shell, the frequency variable motor for transmitting power to the plurality of compression mechanism through the rotating shaft; It provides a variable frequency compressor comprising a; a plurality of compression mechanism to control the suction and discharge direction to the plurality of compression mechanism to compress the refrigerant in the twin rotary compressor type or two-stage rotary compressor type.
  • the present invention also provides a shell forming a closed space;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the 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 above the second compression mechanism;
  • a first discharge port positioned in the upper bearing and opened when the refrigerant discharged from the first compression mechanism is greater than or equal to a predetermined pressure;
  • a second discharge port positioned in the upper bearing and opened when the refrigerant discharged from the second compression mechanism unit is greater than or equal to a predetermined pressure;
  • a first suction pipe configured to provide a refrigerant passage between the accumulator and the refrigerant suction hole of the first compression mechanism unit;
  • An intermediate pressure suction pipe providing a refrigerant flow path between the lower bearing and the four-way valve;
  • a second suction pipe providing a refrigerant flow path between the accumulator and the four-way valve path;
  • a third suction pipe configured to provide a refrigerant flow path between the four-way valve and the refrigerant suction hole of the second compression mechanism unit.
  • the present invention also provides a shell forming a closed space;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • An internal flow path providing a flow path such that the refrigerant compressed in the first compression mechanism part is discharged into the shell through the first compression mechanism part and the second compression mechanism part;
  • An accumulator for temporarily storing a refrigerant before entering the shell;
  • a four-way valve that selects the refrigerant discharge passage of the first compression mechanism portion and the refrigerant suction passage of the second compression mechanism portion to control the first compression mechanism portion and the second compression mechanism portion to compress the refrigerant in a twin
  • a first suction pipe configured to provide a refrigerant passage between the accumulator and the refrigerant suction hole of the first compression mechanism unit;
  • An intermediate pressure suction pipe providing a refrigerant flow path between the inner flow path and the four-way valve;
  • a second suction pipe providing a refrigerant flow path between the accumulator and the four-way valve path;
  • a third suction pipe configured to provide a refrigerant flow path between the four-way valve and the refrigerant suction hole of the second compression mechanism unit.
  • variable frequency compressor characterized in that the medium pressure suction pipe passes through the top of the shell and is fixed by the shell.
  • the present invention also provides a shell forming a closed space;
  • a first compression mechanism unit positioned in the shell and having a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the refrigerant;
  • a second compressor mechanism positioned in the shell and including a rolling piston, a cylinder, a refrigerant suction hole, a refrigerant discharge hole, and a vane to compress the 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 above the second compression mechanism;
  • a discharge port positioned in the upper bearing and opened when the refrigerant discharged from the second compression mechanism unit is greater than or equal to a predetermined pressure;
  • An accumulator for temporarily storing a refrigerant before entering the shell;
  • a first suction pipe configured to provide a refrigerant passage between the accumulator and the
  • variable frequency compressor characterized in that the non-return valve is installed in the portion connecting the four-way valve and the shell in the first discharge pipe.
  • a frequency variable compressor characterized in that a non-return valve is installed at a portion connecting the four-way valve and the accumulator in the second suction pipe.
  • the present invention is the first step of receiving the required cooling power from the control unit; Adjusting a valve to select one of a twin compression method and a two-stage compression method as the driving method of the compression mechanism unit; And a third step of adjusting a driving speed of the frequency variable motor.
  • the present invention is the first step of receiving the required cooling power from the control unit; A second step of comparing the compression capacity during compression in a twin compression scheme at a speed at which the required cooling power and the frequency variable motor can achieve maximum efficiency; And a third step of selecting one of a twin compression method and a two-stage compression method as the driving method of the compression mechanism unit according to the result of the second step.
  • a control method of a variable frequency compressor further comprising; a fourth step of adjusting the drive speed of the variable frequency motor.
  • a third step provides a control method of a variable frequency compressor, wherein the driving mechanism of the compression mechanism is selected by adjusting a four-way valve.
  • the frequency variable compressor and its control method provided by the present invention can be operated in a medium to high speed operating range in which the frequency variable motor exhibits relatively high efficiency even in a situation where a small compression capacity is required, compared to a conventional twin compressor.
  • variable frequency compressor and the control method provided by the present invention reduce the overcompression loss compared to the single stage or twin compression by compressing the refrigerant in a two-stage compression method at a low frequency operating frequency of the efficiency of the frequency variable motor. It is possible to improve the compressor efficiency in the low capacity compression operation that is used relatively frequently.
  • the frequency variable compressor and the control method provided by the present invention can increase the compression capacity by switching the compression method to a twin compression method and increasing the operating frequency of the frequency variable motor when the cooling power required for compression is increased.
  • the variable frequency compressor according to the present invention not only widens the compressible capacity, but also can significantly improve the energy efficiency of the compressor itself.
  • FIG. 3 is a graph showing the efficiency and the annual operating time according to the heating and cooling load (operating frequency) of the compressor having a conventional DC frequency variable motor as the electric mechanism unit;
  • FIG. 6 and 7 show a frequency variable compressor according to a first embodiment of the present invention
  • FIG. 12 is a graph comparing the compressor efficiency of the variable frequency compressor and the conventional inverter compressor according to an embodiment of the present invention.
  • the compressor forms part of a refrigeration cycle, such as a cooling device such as an air conditioner or a refrigerator, or a heating device using a heat pump.
  • the cooling device or the heating device is operated in the power mode until the environmental temperature reaches the desired temperature at the first time of operation, and is operated in the saving mode after the desired temperature is reached.
  • the power mode is an operation mode in which the compression capacity of the compressor is increased to increase the cooling or heating capability of the air conditioner or heating device.
  • the saving mode is the operation mode in which the compression capacity of the compressor is reduced by reducing the cooling or heating capacity of the air conditioner or heating device. to be.
  • the motor In the case of a frequency variable compressor using a variable frequency motor as a driving device for refrigerant compression, the motor is operated with the operating frequency of the motor at high frequency to medium frequency (approximately 120 Hz to 60 Hz) in the power mode, and medium frequency to low frequency in the saving mode. (Approximately 60 Hz to 20 Hz).
  • the cooling and heating devices are generally operated in power mode to cause a temperature change only until the desired temperature is reached from the environmental temperature, and the saving temperature is generally maintained since the desired temperature is maintained after the desired temperature is reached. Is operated. Therefore, the running time in the saving mode is much longer than the running time in the power mode.
  • the frequency variable motor (frequency variable motor) has the highest efficiency at medium frequency (approximately 50 to 70 Hz), and generally high efficiency at high frequency (70 Hz or more), but low frequency (50 Hz). In the following), the efficiency is greatly reduced. Therefore, it is necessary to improve the efficiency of the frequency variable compressor in the low frequency (50 Hz or less) region.
  • the low frequency region, the middle frequency region and the high frequency region may vary according to the specific specifications of the frequency variable motor, but in general, the region in which the frequency variable motor shows the best efficiency is the middle frequency region and the frequency region lower than the middle frequency.
  • the high frequency region is where the efficiency of the frequency variable motor gradually decreases in the low frequency region and the higher frequency region than the middle frequency region.
  • the middle frequency region is regarded as a frequency region showing an efficiency of about 5% of the maximum efficiency of the frequency motor.
  • the frequency variable compressor according to the present invention includes a plurality of compression chambers.
  • the compression chamber is a space in which refrigerant is sucked in and is compressed.
  • the compression chamber is a space formed in a compression mechanism including a cylinder and a rolling piston.
  • Each of the plurality of compression chambers may be formed in one compression mechanism unit, but two or more compression chambers may be formed in one compression mechanism unit.
  • a plurality of compression chambers when a plurality of compression chambers are formed in one compression mechanism unit, when the same number of compression chambers is formed in a plurality of compression mechanism units, a plurality of compression chambers may be provided in a plurality of compression mechanisms. It means all cases formed.
  • the refrigerant may be sucked into the plurality of compression chambers, compressed and discharged in parallel.
  • Representative examples of compressing the refrigerant in parallel in a plurality of compression chambers include twin (double) compressor, triple compressor and the like.
  • the refrigerant may be sucked into one of the plurality of compression chambers, compressed, and then resorbed into another compression chamber to be compressed and discharged.
  • Representative examples of sequentially compressing the refrigerant in the plurality of compression chambers include a two-stage compressor, a three-stage compressor, and the like.
  • variable frequency compressor compresses the refrigerant in parallel in a plurality of compression chambers when operated above a medium frequency, and sequentially compresses the refrigerant in the plurality of compression chambers when operated at a low frequency.
  • overcompression losses occur when a part of the refrigerant is compressed above the required pressure when the refrigerant is compressed.
  • the refrigerant is compressed in multiple stages, there is a compression loss only when the refrigerant is compressed in the final stage.
  • the variable frequency compressor according to the present invention compresses the refrigerant in a multi-stage compression method in which the refrigerant is sequentially compressed in the plurality of compression chambers when operated at a low frequency.
  • the variable frequency compressor includes a plurality of unit chambers in which a refrigerant is compressed in the shell, and a plurality of unit chambers, and a variable frequency motor that provides a driving force to the compressor mechanism so that the refrigerant is compressed in the compression chamber.
  • the compression chamber is provided in the compression mechanism unit, one compression chamber may be formed in a single compression mechanism unit or a plurality of compression chambers may be formed.
  • a refrigerant suction passage for introducing the refrigerant into the compression chamber and a refrigerant discharge passage for discharging the refrigerant from the compression chamber to the shell should be provided.
  • At least one of the plurality of compression chambers may include a refrigerant compressed into at least one of the plurality of compression chambers (hereinafter referred to as a second compression chamber) and a first discharge passage for discharging the compressed refrigerant into the shell.
  • a medium pressure flow path for suctioning is provided together.
  • the intermediate pressure flow path and the first discharge flow path are connected to the first compression chamber, and the intermediate pressure discharge flow path is selectively connected to the second suction flow path connected to the second compression chamber. That is, the intermediate pressure flow path and the second suction flow path may be connected to each other or blocked by the valve.
  • the second suction passage may be divided into two parts based on where the valve is connected.
  • the second suction passage is directly connected to the second compression chamber based on the place where the valve is connected, and a portion (first portion) that sucks the refrigerant into the second compression chamber and a portion that is connected to the first portion and introduces a low pressure refrigerant Can be divided into (second part).
  • the valve blocks the intermediate pressure flow path and the second suction flow path from each other, the refrigerant discharged from the first compression chamber cannot be sucked into the second suction flow path through the intermediate pressure flow path, and thus is discharged into the shell through the first discharge flow path.
  • the second suction flow path sucks the low pressure refrigerant, compresses it in the second compression chamber, and discharges it into the shell.
  • the valve connects the first portion of the intermediate pressure passage and the second suction passage to each other, the valve prevents the suction of the low pressure refrigerant from the second portion of the second suction passage and compresses the first compression through the intermediate pressure passage.
  • the refrigerant compressed in the chamber is sucked through the second portion of the second suction passage.
  • the refrigerant compressed in the first compression chamber due to the suction pressure in the second compression chamber is not discharged into the shell through the first discharge passage but is sucked into the second compression chamber through the intermediate pressure passage.
  • the refrigerant sucked into the second compression chamber may be discharged into the shell through compression again.
  • the refrigerant compressed in the second compression chamber may be sucked into another one of the plurality of compression chambers (third compression chamber), compressed in three stages, and then discharged into the shell.
  • the configuration of the plurality of compression chambers, the suction discharge flow paths, the intermediate pressure flow paths, and the valve may be any configuration as long as the multi-stage compression and the multiple compression can selectively occur by the valves in the plurality of compression chambers.
  • two-stage compression occurs in the first compression chamber and the second compression chamber
  • two-stage compression occurs in the third compression chamber and the fourth compression chamber
  • each two-stage compression is performed in parallel.
  • various types of compression may be possible, such as a form in which single stage compression is performed in parallel.
  • Figure 5 is a graph showing the efficiency of the variable frequency compressor according to the present invention. Efficiency is compared by using the compressor of the embodiment is provided with two compression mechanism and one compression chamber of each of the variable frequency compressor. .
  • the two-stage compression method improves the efficiency by about 10 to 15% compared to the twin compression method. there was.
  • the twin compression scheme is more efficient than the two-stage compression scheme. This is because when the compressor is operated at a high frequency, the loss caused by the valve in the two-stage compression method is increased, which is less efficient than the twin compression method.
  • the operating frequency of the variable frequency compressor when the operating frequency of the variable frequency compressor is in the low frequency region, it is preferable to compress the refrigerant by a two-stage compression method by adjusting the valve. That is, when the operating frequency of the variable frequency compressor is in the low frequency region, it is preferable that multistage compression occurs in the plurality of compression chambers.
  • the frequency variable compressor according to the first embodiment of the present invention includes two compression mechanism units, and is configured to compress the refrigerant by a twin compression method in a power mode and a two-stage compression method in a saving mode.
  • the frequency variable compressor has a shell 100 constituting the appearance of the compressor, and a DC variable speed frequency variable motor 200 (hereinafter referred to as a frequency variable motor) is installed as an electric mechanism part in the shell 100, and the frequency variable motor 200 has a frequency.
  • the rotating shaft 300 for transmitting the rotating force of the variable motor 200 is connected.
  • the frequency variable motor 200 is located above the shell 100, and the rotation shaft 300 extends downward from the frequency variable motor 200.
  • the compressor sphere 400 is installed below the frequency variable motor 200, and the compressor sphere 400 receives power from the frequency variable motor 200 through the rotating shaft 300 to compress the refrigerant.
  • the compression mechanism 400 includes a first compression mechanism 410 and a second compression mechanism 420, and both the first compression mechanism 410 and the second compression mechanism 420 are rotary compression mechanisms. That is, the first compression mechanism 410 and the second compression mechanism 420 are cylinders 411 and 421, rolling pistons 412 and 422, and refrigerant suction holes 410h and 420h, respectively, which provide a space in which the refrigerant is compressed. And refrigerant discharge holes 410d and 420d and vanes (not shown).
  • the first compression mechanism 410 and the second compression mechanism 420 may each compress a refrigerant having a predetermined capacity.
  • a lower bearing 500 is installed below the first compression mechanism 410, and an upper bearing 600 is installed above the second compression mechanism 420.
  • the lower bearing 500 is provided with an intermediate pressure discharge valve 510 which is opened when the refrigerant compressed in the first compression mechanism is greater than or equal to a predetermined pressure.
  • the medium pressure refrigerant discharged through the intermediate pressure discharge valve 510 temporarily stays in the lower bearing 500.
  • the upper bearing 600 includes refrigerant compressed by the first discharge port 610 and the second compression mechanism 420 that discharge the refrigerant temporarily stored in the lower bearing 500 into the shell 100 at a predetermined pressure or more.
  • a second discharge port 620 is formed to discharge into the shell.
  • the first discharge port 610 is connected to the space inside the lower bearing 500 through the discharge flow path 820, and the discharge flow path 820 moves the refrigerant from the lower bearing 500 to the first discharge port 610.
  • Provide a path to The discharge passage 820 penetrates the cylinder 411 of the first compression mechanism 410 and the cylinder 421 of the second compression mechanism 420 and connects the lower bearing 500 to the first discharge port 610. It may be formed as an internal flow path.
  • the refrigerant is sucked from the accumulator 900 through the suction passages 810, 840, and 850 in the first compression mechanism unit 410 and the second compression mechanism unit 420.
  • the accumulator 900 is temporarily stored with the refrigerant flowing from the other device forming the refrigeration cycle with the variable frequency compressor.
  • the first suction passage 810 and the second suction passages 840 and 850 are connected to the accumulator 900, and the liquid refrigerant and the gas refrigerant are separated from the accumulator 900 so that only the refrigerant in the gas state is the first suction passage ( 810 and the second suction passages 840 and 850.
  • the refrigerant compressed in the first compression mechanism 410 may be sucked into the second compression mechanism 420 through portions 850 of the second suction flow paths 840 and 850.
  • the intermediate pressure flow path 830 may be provided to connect a portion 850 of the second suction flow paths 840 and 850 to the lower bearing 500.
  • the dual displacement variable inverter compressor is connected to the intermediate pressure flow path 830, and is connected to the middle of the second suction flow paths 840 and 850 so that the second suction flow paths 840 and 850 are divided into two parts 840. 850, divided into four-way valve 700.
  • the four-way valve 700 has a portion 850 connected to the second compression mechanism 420 among the second suction passages 840 and 850, and the other portion 840 and the intermediate pressure passage of the second suction passages 840 and 850. 830 selectively connects any one of them. Regardless of the adjustment of the valve 700, the refrigerant is always sucked into the first compression mechanism 410 through the first suction channel 810 not connected to the valve 700.
  • the valve 700 controls the compression mechanism 400 to compress the refrigerant by a twin compression method or a two-stage compression method by a control unit (not shown).
  • the controller controls the speed of the variable frequency motor 200 as well as the control of the valve 700.
  • the control unit receives or receives a cooling force required by an indoor unit of a cooling / heating cycle including a dual displacement variable inverter compressor, or adjusts the speed of the frequency variable motor 200 or adjusts the valve 700 to provide a compression mechanism.
  • the compression method of 400 is controlled.
  • the first compression mechanism 410 and the second compression mechanism 420, the first compression mechanism 410 and the second compression mechanism 420 separately compresses the refrigerant having a predetermined capacity to the refrigerant compressed into the shell
  • the refrigerant may be compressed in the form of a rotary twin compressor to discharge, and the refrigerant compressed in the first compression mechanism unit 410 is sucked into the second compression mechanism unit 420 to discharge the refrigerant compressed in two stages into the shell after recompression.
  • the refrigerant can be compressed in the form of a rotary two stage compressor.
  • valve 700 connects a portion 850 of the second suction passages 840 and 850 and the other portion 840 to each other, and closes the intermediate pressure passage 830 so that the compression mechanism 400 is rotary.
  • Compressing the refrigerant in the form of a twin compressor is shown.
  • the refrigerant is sucked into the first compression mechanism 410 through the first suction passage 810, and at the same time, the refrigerant is sucked into the second compression mechanism 420 through the second suction passages 840 and 850. do.
  • the refrigerant sucked into the cylinders 411 and 421 is compressed by the rolling pistons 412 and 422 which receive the power of the frequency variable motor 200 through the rotating shaft 300 and rotate.
  • the refrigerant compressed by the first compression mechanism 410 above the predetermined pressure opens the intermediate pressure discharge valve 510 and is discharged to the lower bearing 500 through the refrigerant discharge hole 410d. Since the intermediate pressure flow path 830 is closed by the valve 700, and refrigerant cannot flow into a portion of the second suction flow paths 840 and 850, the refrigerant temporarily stored in the lower bearing 500 may discharge the flow path 820. It is discharged into the shell 100 through the first discharge port 610 through. At this time, the first discharge valve 610v is installed on the first discharge port 610 so that the refrigerant can be discharged into the shell 100 through the first discharge port 610 only when the refrigerant is above a predetermined pressure.
  • the second compressor mechanism 420 compresses the refrigerant sucked through the second suction passages 840 and 850 and discharges the refrigerant into the shell 100 through the second discharge port 620.
  • the second discharge valve 620v is also provided on the second discharge port 620 so that the refrigerant can be discharged into the shell 100 only at a predetermined pressure or more.
  • each of the first compression mechanism 410 and the second compression mechanism 420 compresses a refrigerant having a predetermined capacity and discharges it into the shell 400, respectively, and the total compression capacity of the refrigerant is the compression capacity of the first compression mechanism 410.
  • the compression capacities of the second compression mechanism 420 are added together. In this case, the total compression capacity of the compressor may be adjusted according to the speed (frequency) of the frequency variable motor 200.
  • valve 700 blocks the part 850 of the second suction flow paths 840 and 850 from the other part 840, and instead allows the intermediate pressure flow path 830 to communicate so that the compression mechanism 400 is 2. It is shown that the control to compress the refrigerant in the form of a compressor. The refrigerant stored in the accumulator 900 through the first suction channel 810 is sucked into the first compression mechanism 410, compressed, and then discharged to the lower bearing 500.
  • the intermediate pressure flow path 830 is connected to the portion 850 of the second suction flow paths 840 and 850 by the valve 700, the refrigerant discharged to the lower bearing 500 is transferred to the intermediate pressure flow path ( 830 and a portion 850 of the second suction passages 840 and 850 are sucked into the second compression mechanism unit 420.
  • a negative pressure is generated in the cylinder 421 due to the rolling piston 422 fitted to the rotating shaft 300 to rotate in the cylinder 421, which acts as a suction pressure for sucking the refrigerant. Therefore, 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 refrigerant in the shell 100 is regenerated through the first discharge port 610, the discharge passage 820, the lower bearing 500, and the intermediate pressure passage 830 by the suction pressure of the second compression mechanism 420.
  • the 1st discharge valve 610v provided in the 1st discharge port 610 not be suctioned into the 2nd compression mechanism part 420 is a backflow prevention valve.
  • variable frequency compressor illustrates a variable frequency compressor according to a second embodiment of the present invention.
  • the configuration of the shell 100, the variable frequency motor 200, the rotating shaft 300, the compression mechanism 400, the lower bearing 500, the upper bearing 600, the valve 700, the accumulator 900 is Since it is the same as that of the first embodiment, the repeated description is omitted here.
  • the intermediate pressure passage 830 ′ is configured to penetrate the upper portion of the shell 100. Due to this structure, the pipe vibration generated in the intermediate pressure flow path 830 'can be considerably reduced.
  • the discharge passage 820 and the first discharge port 610 are not shown. Although shown as being formed in the opposite direction to the intermediate pressure discharge valve 510 and the second discharge port 620, the actual discharge flow path 820 and the first discharge port 610 is the intermediate pressure discharge valve 510 and the second The discharge port 620 is installed at a fairly close position.
  • FIG. 8 is a view showing the operation of the rotary twin compressor
  • Figure 7 is a view showing the operation of the rotary two-stage compressor.
  • the operation method of operating a twin compressor and a two-stage compressor is the same as in the first embodiment.
  • FIG. 10 and 11 illustrate a variable frequency compressor according to a third embodiment of the present invention.
  • FIG. 10 illustrates compressing a refrigerant by a twin compressor method
  • FIG. 11 illustrates compressing a refrigerant by a two-stage compressor method.
  • the frequency variable compressor according to the third embodiment of the present invention is also the shell 100, the frequency variable motor 200, the rotating shaft 300, the compression mechanism 400, the lower bearing 500, as in the first and second embodiments ), An upper bearing 600, a valve 700, and an accumulator 900, and only the configuration of the suction flow path and the discharge flow path is different from those of the first and second embodiments.
  • the twin compressor type driving will be described with reference to FIG. 10.
  • the refrigerant is sucked into the first compression mechanism 410 through the first suction channel 810, compressed, and then discharged to the lower bearing 500.
  • the compressed refrigerant flows to the valve 700 through an intermediate pressure flow path 830 "connected to the lower bearing 500.
  • the intermediate pressure flow path 830" is connected to the second suction flow path 840 by the valve 700. Flow to the part 850 of the 850 is blocked, and the other part 840 of the second suction paths 840 and 850 communicates with a part of the second suction paths 840 and 850. Therefore, the intermediate pressure flow path 830 ′′ is discharged into the shell 100 through the first discharge flow path 820 ′ connected to the valve 700.
  • the check valve 800v is disposed on the first discharge flow path 820 ′. It is installed to prevent the refrigerant from flowing into the first discharge flow path 820 ′ from the shell 100. Meanwhile, the second compression mechanism 420 from the accumulator 900 through the second suction flow path (840, 850). The refrigerant is sucked in, compressed, and then discharged into the shell 100.
  • the refrigerant is sucked into the first compression mechanism 410 through the first suction channel 810, compressed, and then discharged to the lower bearing 500.
  • the compressed refrigerant then flows through the intermediate pressure flow path 830 ′′ connected to the lower bearing 500.
  • the valve 700 is intermediate with a portion 850 of the second suction flow paths 840, 850.
  • the pressure flow path 830 ′′ is adjusted to communicate, and closes the other part 840 of the second suction flow paths 840 and 850.
  • the medium pressure refrigerant sucked into the second compression mechanism unit 420 through the middle pressure passage 830 "and the portions 850 of the second suction passages 840 and 850 is compressed to a high pressure, and then the second discharge port 620 is pressed. Is discharged into the shell 100.
  • the first discharge port is not formed separately, while the check valve 800v flows from the valve 700 into the shell 100. Only and does not allow the refrigerant to flow from the shell 100 to the valve 700.
  • the efficiency of the frequency variable motor 200 is highest in the middle of the range of speed (operating frequency) that the frequency variable motor 200 can produce.
  • the efficiency of the frequency variable motor 200 in the medium speed to high speed operation is significantly higher than the efficiency of the frequency variable motor 200 in the low speed to medium speed operation. Therefore, it is preferable that the controller (not shown) controls the frequency variable motor 200 to perform the medium to high speed operation as much as possible.
  • FIG. 12 is a graph comparing the compressor efficiency of the variable frequency compressor and the conventional inverter compressor according to an embodiment of the present invention.
  • the compression capacity can be reduced by about 50% compared to when the refrigerant is compressed by the twin compression method under the assumption that the compression capacities of the first and second compression mechanisms are the same. Therefore, in the case of a capacity that had to be compressed by operating in a low speed to medium speed section with a frequency variable motor 200 in the conventional compressor, when compressed in a two-stage compression method, it can be compressed into a medium speed to high speed section.
  • the compression capacity of the first and second compression mechanism units 410 and 420 may be 50, respectively.
  • the compression capacity in the compression mechanism unit 420 becomes approximately 50 when the compression is performed by the two-stage compression method. Therefore, when the speed of the frequency variable motor 200 is increased by 140%, high speed operation can be performed. It becomes possible. Therefore, the frequency variable motor 200 may be operated in a medium speed to high speed operating range having a relatively high efficiency.
  • variable frequency compressor not only widens the compressible capacity, but also can significantly improve the energy efficiency of the compressor itself.
  • the two-stage compression scheme has the advantage of less overcompression loss than the one-stage or twin compression scheme. Therefore, when the variable frequency compressor is operated at a low speed, that is, when operated in the low frequency region by adjusting the valve, it is possible to reduce the overcompression loss by allowing the refrigerant to be compressed in multiple stages in a plurality of compression chambers.
  • the control unit adjusts the operating frequency of the variable frequency motor to adjust the capacity of the refrigerant compressed by the compressor to the compression capacity required by the compressor, and when the operating frequency becomes a low frequency region, the refrigerant is controlled in multiple compression chambers by adjusting the valve. To be compressed. Therefore, improving the efficiency of the compressor in the operating frequency of the low frequency region, which has the longest operating time, can achieve a greater efficiency improvement than that of the compressor in the other operating frequency region.
  • the conventional frequency variable compressor as shown in Figure 4, the operating frequency gradually decreases over time, and after reaching the desired temperature is operated at a low frequency of 30 ⁇ 40Hz.
  • the frequency variable compressor of the present invention also starts to operate in multiple compression schemes, such as twin compression schemes, since the compression capacity required at the beginning of operation will be large.
  • the operating frequency of the frequency variable compressor of the present invention will be controlled in a similar manner to the operating frequency of the conventional frequency variable compressor shown in FIG. Then, as the compression capacity required for the variable frequency compressor of the present invention becomes smaller, the control unit for controlling the variable frequency motor adjusts the operating frequency of the motor to a low frequency.
  • the control unit controls the connection of the suction flow path, the discharge flow path and the intermediate pressure flow path connected to the plurality of compression chambers, and changes the flow of the refrigerant so that the refrigerant is compressed in a multi-stage compression method. .
  • control unit receives the required cooling power from another mechanism of the cycle including the variable frequency compressor, or receives information about the received required cooling power.
  • This cooling capacity is compared with the compression capacity when operating at medium speed (speed at which the variable frequency motor can achieve maximum efficiency) using twin compression. If the required cooling power is greater than or equal to the compression capacity when operating at medium speed with twin compression method, adjust the valve to operate with twin compression method, and if the required cooling force is smaller than the compression capacity when operating at medium speed with twin compression method, 2 steps Adjust the valve to operate the compression mechanism by the compression method.
  • the compression method is set to either the twin compression method or the two-stage compression method, the speed of the variable frequency motor is controlled to achieve a compression capacity equal to the required cooling power.

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Abstract

La présente invention porte sur un compresseur à fréquence variable, qui comprend une coque (100) définissant un espace étanche à l'air, un accumulateur (900) stockant temporairement un réfrigérant avant l'introduction du réfrigérant dans la coque (100), une première unité de mécanisme de compression (410) positionnée dans la coque (100), comprenant un piston roulant (412), un cylindre (411), un trou d'aspiration de réfrigérant (410h), un trou de décharge de réfrigérant (410d), et une soupape, et comprimant le réfrigérant, une seconde unité de mécanisme de compression (420) positionnée dans la coque (100), comprenant un piston roulant (422), un cylindre (421), un trou d'aspiration de réfrigérant (420h), un trou de décharge de réfrigérant (420d) et une soupape, et comprimant le réfrigérant, un moteur à fréquence variable (200) positionné dans la coque (100) et transférant de la puissance aux pistons roulants (412, 422) des première et seconde unités de mécanisme de compression (410, 420) par l'intermédiaire d'un arbre tournant (300), et une soupape (700) commandant l'écoulement du réfrigérant de telle sorte que les première et seconde unités de mécanisme de compression (410, 420) compriment le réfrigérant par un compresseur de type rotatif double ou un compresseur de type rotatif à deux étages.
PCT/KR2009/006299 2008-11-17 2009-10-29 Compresseur à fréquence variable et procédé de commande de celui-ci WO2010056002A1 (fr)

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ES09826234.8T ES2643564T3 (es) 2008-11-17 2009-10-29 Compresor de frecuencia variable y método de control del mismo
US13/127,016 US20110271699A1 (en) 2008-11-17 2009-10-29 Frequency variable compressor and control method thereof
EP09826234.8A EP2372158B1 (fr) 2008-11-17 2009-10-29 Compresseur à fréquence variable et procédé de commande de celui-ci
CN2009801442618A CN102203425A (zh) 2008-11-17 2009-10-29 变频压缩机及其控制方法

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KR1020080114279A KR101268612B1 (ko) 2008-11-17 2008-11-17 주파수 가변 압축기 및 그 제어 방법

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CN108035880B (zh) * 2017-12-15 2019-11-05 同济大学 一种变转速变排量多转子压缩机及其变排量控制方法
GB201805409D0 (en) * 2018-04-02 2018-05-16 Bolwell Michael Robin A Hybrid Heat Pump
CN108843573B (zh) * 2018-07-26 2023-08-11 珠海格力节能环保制冷技术研究中心有限公司 一种三缸双级变容压缩机
CN111219880B (zh) * 2019-12-02 2020-12-18 珠海格力电器股份有限公司 三缸压缩机模式切换方法和装置

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ES2643564T3 (es) 2017-11-23
EP2372158A1 (fr) 2011-10-05
KR101268612B1 (ko) 2013-05-29
US20110271699A1 (en) 2011-11-10
EP2372158B1 (fr) 2017-07-26
CN102203425A (zh) 2011-09-28
EP2372158A4 (fr) 2014-10-29
KR20100055282A (ko) 2010-05-26

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