WO2011062427A2 - 리니어 압축기 - Google Patents
리니어 압축기 Download PDFInfo
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- WO2011062427A2 WO2011062427A2 PCT/KR2010/008159 KR2010008159W WO2011062427A2 WO 2011062427 A2 WO2011062427 A2 WO 2011062427A2 KR 2010008159 W KR2010008159 W KR 2010008159W WO 2011062427 A2 WO2011062427 A2 WO 2011062427A2
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- WIPO (PCT)
- Prior art keywords
- voltage
- motor
- unit
- movable member
- current
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/04—Motor parameters of linear electric motors
- F04B2203/0401—Current
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/04—Motor parameters of linear electric motors
- F04B2203/0402—Voltage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/04—Motor parameters of linear electric motors
- F04B2203/0404—Frequency of the electric current
Definitions
- the present invention relates to a linear compressor of the present invention, and more particularly, to a linear compressor capable of providing greater power and cooling power by varying a frequency at high loads.
- a motor is also provided in a compressor, a mechanical device that increases power by compressing air, refrigerant, or various working gases by receiving power from a power generator such as an electric motor or a turbine. Or widely used throughout the industry.
- a reciprocating compressor for compressing the refrigerant while linearly reciprocating the piston inside the cylinder is formed by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder.
- Rotary compressor that compresses the refrigerant while the roller is eccentrically rotated along the inner wall of the cylinder so that a compression space for absorbing and discharging the working gas is formed between the reciprocating compressor and the eccentrically rotating roller and the cylinder.
- Scroll compressor that compresses the refrigerant while the rotating scroll rotates along the fixed scroll by forming a compression space for absorbing and discharging the working gas between the orbiting scroll and the fixed scroll.
- the piston is directly connected to the reciprocating linear motion drive motor, so that there is no mechanical loss due to the motion conversion to improve the compression efficiency as well as a simple linear compressor has been developed a lot.
- FIG. 1 is a block diagram of a motor control device applied to a linear compressor according to the prior art.
- the motor control apparatus applies a diode bridge 11 for receiving and rectifying an AC power, which is a commercial power source, and outputting the rectified part, a rectifying unit including a capacitor C1 smoothing the rectified voltage, and applying a DC voltage.
- a motor including an inverter unit 12, a motor 13, and a capacitor C2 connected in series with the motor 13, which are converted into an AC voltage according to a control signal from the controller 17 and provided to the motor unit.
- a voltage detector 14 that detects the voltage across the capacitor C1
- a current detector 15 that detects a current flowing in the motor unit, a sense voltage from the voltage detector 14, and a current detector 15
- a calculation unit 16 for calculating the counter electromotive force (EMF) from the sense current from the control unit 16, and a control unit 17 for generating a control signal by reflecting the deferred power from the calculation unit 16 and the sense current from the current detection unit 15.
- the linear compressor according to the prior art of FIG. 1 requires a cost and space for providing the capacitor C2 in the linear compressor due to the capacitor C2 connected in series with the motor 13.
- the capacity of the capacitor C2 determines the variable cooling power according to the load, but in the prior art, it is not easy to change the capacity of the capacitor C2, and a plurality of capacitors are provided to selectively connect the capacitors.
- cost and space also come with design difficulties.
- FIG. 2 is a graph showing changes in the input voltage and the stroke of the motor in FIG. 1.
- simply removing the capacitor C2 reduces the voltage applied to the motor at a larger stroke, that is, in the region close to the top dead center (TDC), as shown in FIG. A phenomenon (jumping phenomenon) occurs, and the cold stroke variable operation (under stroke operation) becomes impossible.
- TDC top dead center
- An object of the present invention is to provide a linear compressor capable of variable cooling control while removing a capacitor connected to a motor of the linear compressor.
- the linear compressor according to the present invention includes a fixed member including a compression space therein, a movable member for compressing refrigerant sucked into the compression space while reciprocating linearly moving inside the fixed member, and installed to elastically support the movable member in the direction of movement of the movable member.
- a mechanical unit comprising at least one spring and a motor installed to be connected to the movable member to reciprocate linearly the movable member in the axial direction, a rectifier for receiving an AC power and outputting the DC voltage, and a control signal applied to the DC voltage.
- the inverter unit converts into an AC voltage and provides the motor to the motor, a voltage sensing unit sensing a DC voltage by the rectifier unit, a current sensing unit sensing a current flowing between the motor and the inverter unit, and a current from the current sensing unit
- the required voltage of the motor is calculated from the
- the control unit generates a control signal for controlling the frequency of the AC voltage converted by the inverter unit and comprises an electric control unit including a control unit for applying to the inverter unit.
- the degree of change of the frequency of the AC voltage is proportional to the voltage difference between the required voltage and the DC voltage.
- a required voltage becomes small according to the frequency change of an alternating voltage.
- the controller integrates the current from the current sensing unit, calculates the attenuation voltage by multiplying the integrated value by a constant (1 / Cr), and calculates the required voltage by the difference between the set voltage and the attenuation voltage.
- the controller when the required voltage is less than or equal to the DC voltage of the voltage sensing unit, the controller preferably generates and applies a control signal to the inverter so that an AC voltage according to the currently set frequency is applied to the motor.
- the linear compressor of the present invention is a fixed member including a compression space therein, a movable member for compressing the refrigerant sucked into the compression space while reciprocating linear motion inside the fixed member, and the movable member elastically supports in the movement direction of the movable member
- a mechanical unit comprising at least one spring installed to be connected to the movable member and a motor installed to be connected to the movable member to reciprocate linearly the movable member in the axial direction, a rectifier for receiving an AC power and outputting the DC voltage, and receiving a DC voltage
- the inverter unit converts into an AC voltage according to the control signal and provides the motor to the motor, and controls the controller so that the frequency of the AC voltage converted by the inverter unit is changed when the load is high.
- control method of the linear compressor of the present invention includes the steps of applying a DC voltage to the inverter unit; Converting the inverter unit into an AC voltage according to a control signal and applying the same to a motor; Sensing a current flowing between the motor and the inverter unit; Calculating a required voltage of the motor from the sensed current; If the calculated required voltage is greater than the DC voltage applied to the inverter unit, generating a control signal for changing the frequency of the AC voltage applied to the motor unit and applying to the inverter unit.
- the present invention has the effect of allowing variable cooling control while removing the capacitor connected to the motor of the linear compressor.
- the present invention has the effect of allowing greater power to be applied to the motor at a lower voltage under high load conditions.
- the present invention has the effect that the cooling force corresponding to the high load is generated by reducing the required voltage to the motor, without additional circuit connection.
- FIG. 1 is a block diagram of a motor control device applied to a linear compressor according to the prior art.
- FIG. 2 is a graph showing changes in the input voltage and the stroke of the motor in FIG. 1.
- FIG. 3 is a control block diagram of the linear compressor according to the present invention.
- FIG. 4 is a control embodiment of the control unit of FIG. 3.
- FIG. 5 is a configuration diagram of a linear compressor according to the present invention.
- FIG. 6 is a vector diagram of a linear compressor according to the present invention.
- FIG. 7 is a graph showing a relationship between a frequency and a required voltage in the linear compressor according to the present invention.
- FIG. 3 is a control configuration diagram of the linear compressor according to the present invention
- FIG. 4 is a control embodiment of the control unit of FIG. 3.
- the control configuration of the linear compressor includes a rectifier 21 for rectifying and smoothing and outputting an AC power, which is a commercial power source, and an AC according to a control signal from the controller 25 under a DC voltage.
- Inverter section 22, which is converted into voltage and provided to motor 23, motor 23 including coil L, and coil 23 in motor 23 and inverter section 22 or motor 23 Calculate a motor applied voltage (Vmotor) to be applied to the motor 23 on the basis of the current sensing unit 24 for detecting the current flowing through the current and the sensed current from the current sensing unit 24, the load condition
- the control unit 25 and the voltage sensing the magnitude of the DC voltage from the rectifier 21 to generate and apply a control signal corresponding to the inverter unit 22 to vary the frequency of the motor applied voltage (Vmotor) according to the
- the sensing unit 26 is made.
- the configuration for supplying the voltage required for the control unit 25, the current sensing unit 24, the voltage sensing unit 26, and the like corresponds to a technical configuration that is natural to
- the rectifier 21 includes a diode bridge for performing a general rectification function, a capacitor for smoothing the rectified voltage, and the like.
- the inverter unit 22 is a means for receiving a DC voltage, generating an alternating voltage, and applying the alternating voltage to the motor 23.
- the inverter unit 22 turns on / off the IGBT element according to the control signal from the IGBT element and the control unit 25. It is provided with the gate control part etc. which turn off.
- the inverter unit 22 is only a degree that is naturally recognized by those familiar with the technical field to which the present invention belongs, and the description thereof is omitted.
- the motor 23 has the coil L in the same way as a general motor in other mechanical configurations, but unlike the prior art, it does not include a capacitor.
- the current sensing unit 24 is an element that senses a current flowing in the conductive line between the inverter unit 22 and the motor 23 or senses a current flowing in the coil L of the motor 23.
- the voltage detector 26 is a device that detects a DC voltage output from the rectifier 21. In this case, the voltage detector 26 may detect the total DC voltage, or may detect the DC voltage reduced at a predetermined ratio.
- the controller 25 receives a start command of the linear compressor from the outside, or generates a control signal for applying a predetermined applied voltage Vin to the motor 23 when AC commercial power is applied, thereby generating an inverter unit ( 22). Accordingly, the inverter unit 22 generates an AC voltage corresponding to the applied voltage Vin and applies it to the motor 23.
- the current sensing unit 24 detects the current i from the inverter unit 22 to the motor 23 or the current i flowing through the coil L of the motor 23.
- the controller 25 receives the current i from the current detector 24 and performs a process as shown in FIG. 4.
- the applied voltage Vin in this embodiment will correspond to the voltage applied by the inverter unit in the conventional compressor, and is fixed or variable according to the control algorithm of the nia compressor.
- the integrator 25a and the attenuator 25b correspond to the attenuation calculation unit that attenuates the influence of inductance by the coil L of the motor by using the current i flowing in the motor 23. That is, in this embodiment, since there is no capacitor connected to the coil L of the motor 23, the inductance effect by the coil L is controlled by controlling the motor applied voltage Vmotor applied to the motor 23 to reduce it. will be.
- the constant 1 / Cr in the attenuator 25b may be fixed or variably set according to the size of the coil L of the motor 23.
- the constant 1 / Cr may be determined accordingly.
- the constant 1 / Cr may be determined accordingly.
- the control unit 25 After the motor application voltage Vmotor is calculated, the control unit 25 generates a control signal for causing the inverter unit 22 to apply the calculated motor application voltage Vmotor to the motor 23, thereby inverting the inverter. It applies to the part 22. That is, the controller 25 allows the sensed current i to be fed back to the motor applied voltage Vmotor, thereby controlling the operation of the motor 23 even when the capacitor is not connected to the motor 23. . In the present invention, since the counter electromotive force is reflected and fed back to the current i, it does not need to be considered separately.
- the motor applied voltage Vmotor which is a required voltage
- the motor applied voltage Vmotor that is, the maximum value
- the direct current voltage Vdc direct current voltage
- the control unit 25 changes the frequency of the AC voltage applied from the inverter unit 22 to the motor 23, so as to reduce the motor applied voltage Vmotor, which is a necessary voltage, but maintain the required cooling force.
- FIG. 5 is a configuration diagram of a linear compressor according to the present invention.
- an inlet pipe 32a and an outlet pipe 32b through which refrigerant is flowed in and out of one side of the sealed container 32 are installed, and a cylinder is formed inside the sealed container 32.
- the piston 34 is installed to be fixed, and the piston 36 is installed inside the cylinder 34 so as to reciprocate linear movement so as to compress the refrigerant sucked into the compression space P inside the cylinder 34.
- an intake valve 52 is installed at one end of the piston 36 in contact with the compression space P
- a discharge valve assembly 54 is installed at one end of the cylinder 34 in contact with the compression space P. The intake valve 52 and the discharge valve assembly 54 are automatically adjusted to open and close according to the pressure in the compression space P, respectively.
- the airtight container 32 is installed so that the upper and lower shells are coupled to each other so that the inside is sealed, and an inlet tube 32a through which the refrigerant is introduced and an outlet tube 32b through which the refrigerant is discharged are installed, and a cylinder ( 34, the piston 36 is installed so as to be elastically supported in the movement direction for reciprocating linear motion, and the linear motors 40 are assembled to each other by the frame 48 outside the cylinder 34 to form an assembly.
- the assembly is installed to be elastically supported by the support spring 59 on the bottom surface of the sealed container (32).
- a predetermined oil is contained in the bottom surface of the airtight container 32, and an oil supply device 60 for pumping oil is installed at the bottom of the assembly, and oil is supplied to the inside of the lower frame 48 of the assembly.
- An oil supply pipe 48a is formed to be supplied between the cylinders 34, so that the oil supply device 60 is operated by the vibration generated by the reciprocating linear movement of the piston 36 to pump oil, and The oil is supplied to the gap between the piston 36 and the cylinder 34 along the oil supply pipe 48a to cool and lubricate.
- the cylinder 34 is formed in a hollow shape so that the piston 36 can reciprocate linearly, and a compression space P is formed at one side, and one end is located close to the inside of the inlet pipe 32a. It is preferable to be provided on the same straight line as the inflow pipe 32a.
- the cylinder 34 has a piston 36 installed in one end close to the inlet pipe 32a so as to reciprocate linearly, and a discharge valve assembly 54 is installed at one end opposite to the inlet pipe 32a. .
- the discharge valve assembly 54 is a discharge cover 54a is installed to form a predetermined discharge space on one end of the cylinder 34, and the discharge valve is installed to open and close one end of the compression space (P) side of the cylinder ( 54b) and a valve spring 54c, which is a kind of coil spring that imparts an elastic force in the axial direction between the discharge cover 54a and the discharge valve 54b, and has an O-ring R around one end of the cylinder 34. It is installed so that the discharge valve 54a is in close contact with one end of the cylinder (34).
- a curved loop pipe 58 is installed between one side of the discharge cover 54a and the outlet pipe 32b.
- the loop pipe 58 not only guides the compressed refrigerant to be discharged to the outside. Vibration caused by the interaction of the cylinder 34, the piston 36, and the linear motor 40 buffers the transmission of the entire sealed container 32.
- valve spring 54c is compressed to open the discharge valve 54b.
- the refrigerant is discharged from the compressed space P, and then completely discharged along the loop pipe 58 and the outlet pipe 32b.
- the piston 36 has a refrigerant passage 36a formed at the center so that the refrigerant flowing from the inlet pipe 32a flows, and one end of the piston 36 adjacent to the inlet pipe 32a is connected by the linear motor. 40 is installed to be directly connected, and the suction valve 52 is installed at one end of the inflow pipe 32a in the opposite direction, and is installed to be elastically supported by various springs in the movement direction of the piston 36.
- the suction valve 52 is formed in a thin plate shape so that the center portion is partially cut to open and close the refrigerant passage 36a of the piston 36, and one side is fixed by a screw to one end of the piston 36a. It is installed as possible.
- the suction valve 52 is opened to compress the refrigerant.
- the suction in the space P and the pressure in the compression space P becomes equal to or greater than a predetermined suction pressure, the refrigerant in the compression space P is compressed while the suction valve 52 is closed.
- the piston 36 is installed so as to be elastically supported in the movement direction.
- a piston flange 36b protruding in a radial direction at one end of the piston 36 proximate to the inflow pipe 32a includes a mechanical spring such as a coil spring or the like.
- the refrigerant is elastically supported in the movement direction of the piston 36 by 38a, 38b, and the refrigerant contained in the compression space P on the opposite side to the inflow pipe 32a acts as a gas spring by its elastic force, thereby causing the piston 36 It will elastically support.
- the mechanical springs 38a and 38b have a constant mechanical spring constant K m regardless of the load, and the mechanical springs 38a and 38b are fixed to the linear motor 40 based on the piston flange 36b.
- the predetermined support frame 56 and the cylinder 34 are installed side by side in the axial direction, respectively, the mechanical spring 38a supported by the support frame 56 and the mechanical spring 38a installed in the cylinder 34.
- the gas spring has a variable gas spring constant (K g ) depending on the load, the gas contained in the compression space (P) is the elastic force increases as the pressure of the refrigerant increases as the ambient temperature increases.
- K g variable gas spring constant
- the gas spring has a larger gas spring constant K g as the load increases.
- the mechanical spring constant (K m ) is constant, while the gas spring constant (K g ) is variable depending on the load, so the overall spring constant is also variable depending on the load, and the natural frequency (f n ) of the piston is also the gas It depends on the spring constant K g .
- this load can be measured in various ways, but since such a linear compressor is configured to be included in a refrigeration / air conditioning cycle in which the refrigerant is compressed, condensed, evaporated, and expanded, the load is the condensing pressure which is the pressure at which the refrigerant is condensed. It can be defined as the difference in the evaporation pressure, which is the pressure at which the refrigerant is evaporated, and further determined in consideration of the average pressure obtained by averaging the condensation pressure and the evaporation pressure in order to increase the accuracy.
- the load is calculated to be proportional to the difference between the condensation pressure and the evaporation pressure and the average pressure, and as the load increases, the gas spring constant K g increases.
- the load between the condensation pressure and the evaporation pressure increases. Even if the difference between the condensation pressure and the evaporation pressure is the same, the larger the average pressure is, the greater the load is, and the larger the gas spring constant K g is calculated corresponding to the load.
- the linear compressor may be provided with a sensor (pressure sensor, temperature sensor, etc.) for calculating the load.
- the load is measured so as to measure the condensation temperature which is substantially proportional to the condensation pressure and the evaporation temperature which is proportional to the evaporation pressure, and is proportional to the difference between the condensation temperature and the evaporation temperature and the average temperature.
- the mechanical spring constant (K m ) and the gas spring constant (K g ) can be determined through various experiments, and the resonance frequency of the piston is increased according to the load by increasing the ratio of the gas spring constant to the total spring constant. It can be varied in a relatively wide range.
- the linear motor 40 is configured such that a plurality of laminations 42a are stacked in the circumferential direction, and an inner stator 42 installed to be fixed to the outside of the cylinder 34 by the frame 48 and a coil wound configured to wind the coils.
- the outer stator 44 is configured such that a plurality of laminations 44b are laminated in the circumferential direction around the hull 44a and is provided with a predetermined gap with the inner stator 42 outside the cylinder 34 by the frame 48.
- a permanent magnet 46 positioned in the gap between the inner stator 42 and the outer stator 44 and installed to be connected by the piston 36 and the connecting member 47, wherein the coil winding body 44a is provided. May be installed to be fixed to the outer side of the inner stator 42.
- the linear motor 40 corresponds to one embodiment of the motor 23 described above.
- Equation 1 The electrical equivalent circuit in the motor of the linear compressor of the present invention is represented by Equation 1:
- Vmotor is the motor applied voltage
- R is the resistance value of the motor coil
- L is the inductance value of the coil
- i is the current flowing through the coil of the motor
- the counter electromotive force e (Ref) has a larger phase difference with Vprime than the counter electromotive force e (cecomaf), and its size is also reduced. This means that the condition of the counter electromotive force e (cecomaf) is higher than the condition of e (Ref). When such a high load occurs, the frequency is changed to reduce the required motor voltage.
- the controller 25 increases the frequency of the motor applied voltage Vmorotr so that the phase angles of the counter electromotive voltages e and Vprime are made larger, or by decreasing the frequency, the phase angles of the counter electromotive voltages e and Vprime are increased. Can be made smaller.
- FIG. 7 is a graph showing a relationship between a frequency and a required voltage in the linear compressor according to the present invention. As shown in FIG. 7, the magnitude of the motor applied voltage Vmotor, which is a necessary voltage, and the frequency have an inverse relationship with each other.
- the point A corresponds to a voltage having an operating frequency (60 Hz).
- the point B has an operating frequency (61 Hz).
- the degree of the frequency that varies according to the magnitude (difference between the maximum value) Vin-Vc between the applied voltage Vin and the attenuation voltage Vc also increases.
- the difference c between the applied voltage Vin and the attenuation voltage Vc at the point C is not the difference b between the applied voltage Vin at the point B and the attenuation voltage Vc. Larger case.
- the controller 25 sets the operating frequency to 62 Hz.
- the motor 23 is operated. That is, according to the difference between the applied voltage Vin and the attenuation voltage Vc, the controller 25 selects among the pre-stored operating frequencies so that a voltage corresponding to the selected operating frequency is applied to the motor 23.
- the frequency varies depending on the degree to which the motor applied voltage Vmotor, which is the difference between the applied voltage Vin and the attenuation voltage Vc, is greater than the direct current voltage Vdc. That is, if the degree is large, the variable width of the frequency also increases, and if the degree is small, the variable width of the frequency also decreases.
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Abstract
Description
Claims (12)
- 내부에 압축공간을 포함하는 고정부재와, 고정부재 내부에서 왕복 직선운동하면서 압축공간으로 흡입된 냉매를 압축시키는 가동부재와, 가동부재를 가동부재의 운동방향으로 탄성 지지하도록 설치된 적어도 하나 이상의 스프링과, 가동부재와 연결되도록 설치되어 가동부재를 축방향으로 왕복 직선운동시키는 모터로 이루어지는 기계 유닛과;교류전원을 입력받아 직류 전압으로 출력하는 정류부와, 직류전압을 인가받아 제어 신호에 따라 교류전압으로 변환하여 모터에 제공하는 인버터부와, 정류부에 의한 직류 전압을 감지하는 전압 감지부와, 모터와 인버터부 사이에 흐르는 전류를 감지하는 전류 감지부와, 전류 감지부로부터의 전류로부터 모터의 필요 전압을 산정하고, 필요 전압이 전압 감지부의 직류 전압보다 큰 경우, 인버터부가 변환하는 교류전압의 주파수가 변경되도록 제어하는 제어 신호를 생성하여 인버터부에 인가하는 제어부를 포함하는 전기 제어 유닛으로 구성된 것을 특징으로 하는 리니어 압축기.
- 제1항에 있어서,교류전압의 주파수의 변경 정도는 필요 전압과 직류 전압 간의 전압차에 비례하는 것을 특징으로 하는 리니어 압축기.
- 제1항 또는 제2항에 있어서,필요 전압은 교류 전압의 주파수 변경에 따라, 작아지는 것을 특징으로 하는 리니어 압축기.
- 제1항에 있어서,제어부는 전류 감지부로부터의 전류를 적분하되, 적분된 값에 상수(1/Cr)를 곱하여 감쇄 전압을 연산하고, 설정 전압과, 감쇄 전압 간의 차로 필요 전압을 연산하는 것을 특징으로 하는 리니어 압축기.
- 제1항에 있어서,필요 전압이 전압 감지부의 직류 전압과 같거나 작은 경우, 제어부는 현재 설정된 주파수에 따른 교류 전압이 모터에 인가되도록, 인버터부에 제어 신호를 생성하여 인가하는 것을 특징으로 하는 리니어 압축기.
- 내부에 압축공간을 포함하는 고정부재와, 고정부재 내부에서 왕복 직선운동하면서 압축공간으로 흡입된 냉매를 압축시키는 가동부재와, 가동부재를 가동부재의 운동방향으로 탄성 지지하도록 설치된 적어도 하나 이상의 스프링과, 가동부재와 연결되도록 설치되어 가동부재를 축방향으로 왕복 직선운동시키는 모터로 이루어지는 기계 유닛과;교류전원을 입력받아 직류 전압으로 출력하는 정류부와, 직류전압을 인가받아 제어 신호에 따라 교류전압으로 변환하여 모터에 제공하는 인버터부와, 고부하인경우, 인버터부가 변환하는 교류전압의 주파수가 변경되도록 제어하는 제어 신호를 생성하여 인버터부에 인가하는 제어부를 포함하는 전기 제어 유닛으로 구성된 것을 특징으로 하는 리니어 압축기.
- 제6항에 있어서,상기 전기 제어 유닛은 정류부에 의한 직류 전압을 감지하는 전압 감지부와, 모터와 인버터부 사이에 흐르는 전류를 감지하는 전류 감지부를 구비하고, 제어부는 전류 감지부로부터의 전류로부터 모터의 필요 전압을 산정하고, 필요 전압이 전압 감지부의 직류 전압보다 큰 경우, 고부하로 판단하는 것을 특징으로 하는 리니어 압축기.
- 직류전압을 인버터부에 인가하는 단계와;인버터부가 제어 신호에 따라 교류 전압으로 변환하여 모터에 인가하는 단계와;모터와 인버터부 사이에 흐르는 전류를 감지하는 단계와;감지된 전류로부터 모터의 필요 전압을 산정하는 단계와;산정된 필요 전압이 인버터부에 인가되는 직류 전압보다 큰 경우, 인버터부가 모터에 인가하는 교류전압의 주파수를 변경하도록 하는 제어 신호를 생성하여 인버터부에 인가하는 단계를 포함하는 리니어 압축기의 제어 방법.
- 제8항에 있어서,교류전압의 주파수를 변경하는 정도는 필요 전압과 직류 전압 간의 전압차에 비례하는 것을 특징으로 하는 리니어 압축기의 제어 방법.
- 제8항 또는 제9항에 있어서,산정되는 필요 전압은 교류 전압의 주파수 변경에 따라, 작아지는 것을 특징으로 하는 리니어 압축기의 제어 방법.
- 제8항에 있어서,필요 전압을 산정하는 단계를 감지된 전류를 적분하되, 적분된 값에 상수(1/Cr)를 곱하여 감쇄 전압을 연산하고, 설정 전압과, 감쇄 전압 간의 차로 필요 전압을 연산하는 것을 특징으로 하는 리니어 압축기의 제어 방법.
- 제8항에 있어서,제어 방법은 필요 전압이 전압 감지부의 직류 전압과 같거나 작은 경우, 현재 설정된 주파수에 따른 교류 전압이 모터에 인가되도록, 인버터부에 제어 신호를 생성하여 인가하는 단계를 포함하는 것을 특징으로 하는 리니어 압축기의 제어 방법.
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Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150226210A1 (en) * | 2014-02-10 | 2015-08-13 | General Electric Company | Linear compressor |
KR102355136B1 (ko) * | 2014-06-25 | 2022-01-26 | 엘지전자 주식회사 | 리니어 압축기, 리니어 압축기의 쉘, 리니어 압축기의 쉘 제작방법 |
CN104410347B (zh) * | 2014-09-29 | 2017-10-17 | 四川长虹电器股份有限公司 | 一种驱动压缩机的方法及驱动压缩机的装置 |
WO2017088141A1 (zh) * | 2015-11-26 | 2017-06-01 | 深圳市英威腾电气股份有限公司 | 直线电机的变频控制方法、装置和系统 |
US10784809B2 (en) * | 2016-05-27 | 2020-09-22 | Hitachi, Ltd. | Linear motor system and compressor |
CN111425383B (zh) * | 2018-12-21 | 2023-04-14 | 海信冰箱有限公司 | 一种线性压缩机驱动方法及装置、线性压缩机、冰箱 |
CN111089042B (zh) * | 2019-12-04 | 2021-07-09 | 杭州电子科技大学 | 一种采用双线圈结构的动圈式线性压缩机 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001090659A (ja) * | 1999-09-24 | 2001-04-03 | Sanyo Electric Co Ltd | リニアコンプレッサ |
KR100764277B1 (ko) * | 2006-03-08 | 2007-10-05 | 엘지전자 주식회사 | 리니어 압축기의 제어장치 |
KR100801373B1 (ko) * | 2006-08-04 | 2008-02-05 | 엘지전자 주식회사 | 리니어 압축기의 오일 급유 장치 |
KR100845943B1 (ko) * | 2001-04-05 | 2008-07-11 | 월풀 에쎄.아. | 밀폐형 왕복동 압축기용 오일 펌핑 시스템 |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5032772A (en) * | 1989-12-04 | 1991-07-16 | Gully Wilfred J | Motor driver circuit for resonant linear cooler |
US5272429A (en) * | 1990-10-01 | 1993-12-21 | Wisconsin Alumni Research Foundation | Air gap flux measurement using stator third harmonic voltage and uses |
KR0176909B1 (ko) * | 1996-05-08 | 1999-10-01 | 구자홍 | 선형 압축기 구동장치 |
JP2001095294A (ja) * | 1999-09-20 | 2001-04-06 | Mitsubishi Electric Corp | 空気調和機のインバータ制御装置 |
KR100317301B1 (ko) * | 2000-01-21 | 2001-12-22 | 구자홍 | 선형 압축기의 피스톤 위치 제어장치 및 방법 |
US6537034B2 (en) | 2000-11-29 | 2003-03-25 | Lg Electronics Inc. | Apparatus and method for controlling operation of linear compressor |
BRPI0113565B1 (pt) * | 2001-06-21 | 2016-07-26 | Lg Electronics Inc | aparelho e método para controlar a posição de pistão em compressor de movimento alternativo |
JP2003176788A (ja) * | 2001-12-10 | 2003-06-27 | Matsushita Electric Ind Co Ltd | リニアコンプレッサの駆動装置 |
US20030161735A1 (en) | 2002-02-28 | 2003-08-28 | Samsung Electronics Co., Ltd. | Apparatus and method of controlling linear compressor |
US6877326B2 (en) * | 2002-03-20 | 2005-04-12 | Lg Electronics Inc. | Operation control apparatus and method of linear compressor |
KR100941422B1 (ko) * | 2003-08-04 | 2010-02-10 | 삼성전자주식회사 | 리니어 압축기 및 그 제어 장치 |
KR100500528B1 (ko) | 2003-10-10 | 2005-07-18 | 삼성전자주식회사 | 리니어 압축기 및 그 제어방법 |
KR100633155B1 (ko) | 2004-07-29 | 2006-10-11 | 삼성전자주식회사 | 리니어 압축기 및 그 제어방법 |
CN101305512B (zh) * | 2004-08-30 | 2012-03-28 | Lg电子株式会社 | 直线压缩机 |
KR100652590B1 (ko) * | 2004-12-10 | 2006-12-01 | 엘지전자 주식회사 | 왕복동식 압축기의 모터 구동장치 및 방법 |
KR100690663B1 (ko) * | 2005-05-06 | 2007-03-09 | 엘지전자 주식회사 | 용량 가변형 왕복동식 압축기의 운전 제어장치 및 방법 |
KR100774470B1 (ko) * | 2006-01-16 | 2007-11-08 | 엘지전자 주식회사 | 왕복동식 압축기의 운전제어장치 및 방법 |
US8079825B2 (en) * | 2006-02-21 | 2011-12-20 | International Rectifier Corporation | Sensor-less control method for linear compressors |
KR100806100B1 (ko) * | 2006-04-20 | 2008-02-21 | 엘지전자 주식회사 | 리니어 압축기의 운전제어장치 및 방법 |
KR101415058B1 (ko) * | 2007-12-11 | 2014-07-04 | 엘지전자 주식회사 | 인버터 리니어 압축기 제어 장치 및 방법 |
KR20100008307A (ko) | 2008-07-15 | 2010-01-25 | 엘지전자 주식회사 | 리니어 압축기 |
KR101681324B1 (ko) * | 2010-02-24 | 2016-12-13 | 엘지전자 주식회사 | 리니어 압축기 |
-
2009
- 2009-11-18 KR KR1020090111585A patent/KR101619524B1/ko active IP Right Grant
-
2010
- 2010-11-18 WO PCT/KR2010/008159 patent/WO2011062427A2/ko active Application Filing
- 2010-11-18 CN CN201080044190.7A patent/CN102575657B/zh active Active
- 2010-11-18 US US13/510,294 patent/US9194386B2/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001090659A (ja) * | 1999-09-24 | 2001-04-03 | Sanyo Electric Co Ltd | リニアコンプレッサ |
KR100845943B1 (ko) * | 2001-04-05 | 2008-07-11 | 월풀 에쎄.아. | 밀폐형 왕복동 압축기용 오일 펌핑 시스템 |
KR100764277B1 (ko) * | 2006-03-08 | 2007-10-05 | 엘지전자 주식회사 | 리니어 압축기의 제어장치 |
KR100801373B1 (ko) * | 2006-08-04 | 2008-02-05 | 엘지전자 주식회사 | 리니어 압축기의 오일 급유 장치 |
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US9194386B2 (en) | 2015-11-24 |
US20120230842A1 (en) | 2012-09-13 |
KR20110054802A (ko) | 2011-05-25 |
CN102575657A (zh) | 2012-07-11 |
WO2011062427A3 (ko) | 2011-11-03 |
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