KR100588717B1 - Linear compressor - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a linear compressor, and more particularly, to a linear compressor for adjusting inductance so that an operating frequency varies depending on a load.

The linear compressor according to the present invention includes a fixed member including a compression space therein, a movable member for compressing the refrigerant sucked into the compression space while reciprocating linearly in the axial direction within the fixed member, and the movable member is connected to the movable member. At least one or more springs installed to elastically support in the movement direction and having a spring constant variable depending on the load, and connected to the movable member to reciprocate linearly the movable member in the axial direction, and operate frequency according to the load (fc ) Is made of a linear motor that adjusts the inductance to vary.

Description

Linear Compressor {LINEAR COMPRESSOR}             

1a and 1b is a graph showing the stroke and efficiency according to the load in the linear compressor according to the prior art,

2 is a configuration diagram of a power supply circuit of a linear compressor according to the prior art;

3 is a sectional view showing a linear compressor according to the present invention;

4a and 4b is a graph showing the stroke and efficiency according to the load in the linear compressor according to the present invention,

6 is a cross-sectional view of a coil according to the present invention;

7A and 7B are configuration diagrams of the first and second embodiments of the linear compressor control device composed of the coil of FIG.

<Explanation of symbols on main parts of the drawings>

2: airtight container 4: cylinder

6: piston 7: muffler

8a, 8b: 1st, 2nd mechanical spring 10: linear motor

12: inner stator 14: outer stator

16: permanent magnet 15, 15: branch means

18: control means 22: suction valve

24: discharge valve assembly

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a linear compressor, and more particularly, to a linear compressor for adjusting inductance so that an operating frequency varies depending on a load.

In general, 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 are classified into a reciprocating compressor which compresses the refrigerant while linearly reciprocating the inside of the cylinder by forming a compression space in which the working gas is absorbed and discharged between the piston and the cylinder. And 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 eccentrically rotating roller and the cylinder. As a scroll compressor that compresses the refrigerant while the rotating scroll rotates along the fixed scroll to form a compression space in which the working gas is absorbed and discharged between the orbiting scroll and the fixed scroll. Divided.

Recently, among the reciprocating compressors, in particular, 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.

In general, a linear compressor sucks, compresses, and discharges a refrigerant by using a linear driving force of a motor. A compression unit including a cylinder and a piston for compressing a refrigerant gas is large, and a linear motor supplying driving force to the compression unit. It is divided into included driving parts.

Specifically, the linear compressor is installed so that the cylinder is fixed inside the sealed container, the piston is installed in the cylinder to reciprocate linear movement, the compression space in the cylinder as the piston reciprocating linear movement in the cylinder It is configured to compress and then discharge the refrigerant into the inlet, the inlet and outlet valve assembly is installed in the compression space to adjust the inflow and discharge of the refrigerant in accordance with the pressure in the compression space.

In addition, the linear motor for generating a linear motion force to the piston is installed so as to be connected to each other, the linear motor is provided with an inner stator and an outer stator configured to be laminated in a circumferential direction around the cylinder with a predetermined gap, A coil (or coil winding) is installed inside the inner stator or the outer stator, and a permanent magnet is installed in the gap between the inner stator and the outer stator so as to be connected to the piston.

At this time, the permanent magnet is installed to be movable in the direction of movement of the piston, and the reciprocating linear motion in the direction of movement of the piston by the electromagnetic force generated as the current flows in the coil, the linear motor is a constant operation Not only is it operated at frequency f _c , but it also causes the piston to reciprocate linearly with a predetermined stroke S.

On the other hand, the piston is provided with a variety of springs to be elastically supported in the direction of movement even if the linear motor reciprocating linear movement, specifically, a coil spring which is a kind of mechanical spring to the closed container and the cylinder in the direction of movement of the piston It is installed to be elastically supported, and the refrigerant sucked into the compression space also acts as a gas spring.

At this time, the coil spring has a constant mechanical spring constant (K _m ), the gas spring has a gas spring constant (K _g ) that is variable according to the load, the mechanical spring constant (K _m ) and gas spring constant (K Taking into account _g ), the natural frequency f _n of the piston (or linear compressor) is calculated.

The calculated natural frequency f _n of the piston determines the operating frequency f _{c of} the linear motor, and the linear motor matches the operating frequency f _c with the natural frequency f _n of the piston. The efficiency can be increased by operating in the resonance state.

Therefore, in the linear compressor configured as described above, when a current is applied to the linear motor, an electromagnetic force is generated by interacting with the outer stator and the inner stator as a current flows in the coil, and the permanent magnet and The piston connected to this causes the reciprocating linear motion.

At this time, the linear motor operates at a constant operating frequency f _c , and the operating frequency f _n of the linear motor coincides with the natural frequency f _n of the piston to operate in a resonance state to maximize efficiency. Can be.

As such, the pressure inside the compression space is changed as the piston reciprocates linearly in the cylinder, and the refrigerant is sucked into the compression space according to the pressure change of the compression space, and then compressed and discharged.

The linear compressor configured as described above has a natural frequency f _n of the piston which is calculated by the mechanical spring constant K _m of the coil spring and the gas spring constant K _g of the gas spring under the load considered by the linear motor in design. Since the linear motor is configured to operate at an operating frequency f _c corresponding to the linear motor operates in a resonance state only under the load considered in the design, the efficiency can be increased.

However, in the linear compressor as described above, as the actual load is changed, the gas spring constant K _g of the gas spring and the natural frequency f _n calculated by considering the gas spring constant are changed.

Specifically, in the linear motor, as shown in FIG. 1A, the operating frequency f _c is determined to match the natural frequency f _n of the piston in the intermediate load region during design, and the constant constant determined as described above even if the load is variable. Although operated at an operating frequency f _c , the natural frequency f _n of the piston increases as the load increases.

Where f _n is the natural frequency of the piston, K _m and K _g are the mechanical spring constant and the gas spring constant, and M is the mass of the piston.

In general, the gas spring constant (K _g ) is small because the ratio of the gas spring constant (K _g ) to the total spring constant (K _T ) at the time of design is not considered or the gas spring constant (K _g ) is set to a constant value. In addition, since the mass (M) and the mechanical spring constant (K _m ) of the piston also has a constant value, the natural frequency (f _n ) of the piston is also calculated as a constant value depending on Equation (1).

In practice, however, the more the load increases, the pressure and temperature of the coolant increases in a limited space, which results the elastic force of the gas spring itself increases the gas spring constant (K _g) is large, and yield to be proportional to such a gas spring constant (K _g) The natural frequency f _n of the piston is also increased.

FIG. 2 is a configuration diagram of a power supply circuit of a linear compressor according to the prior art, and includes a coil L having a constant inductance, a capacitor C having a constant conductance, and a power source. As shown, the voltage or current applied from the power source has a constant operating frequency f _c due to LC resonance in the power supply circuit. This operating frequency f _c is set by selection of appropriate L and C to match the natural frequency f _n in the middle load region of FIGS. 1A and 1B. Therefore, as shown in FIGS. 1A and 1B, the driving frequency f _c of the linear motor and the natural frequency f _n of the piston coincide with each other in the intermediate load region, thereby driving the piston to reach a top dead center. The compression operation is performed, and the operation is performed in the resonance state to maximize the efficiency of the compressor.

However, in the low load region, the piston's natural frequency (f _n ) is smaller than the operating frequency (f _c ) of the linear motor, so that the piston is excessively moved above the top dead center, so that the excessive compression force is applied as well as the piston and the cylinder. Friction and abrasion occurs, and the compressor efficiency is lowered because it is not operated in a resonance state.

Similarly, in the high load region, the piston's natural frequency f _n is greater than the operating frequency f _c of the linear motor, so that the piston is operated to fall below the top dead center, so that the compression force is lowered and the compressor is not operated in a resonance state. Inefficient

As a result, in the conventional linear compressor, the natural frequency f _n of the piston is variable as the load is varied, whereas the linear motor is not operated in a resonance state because the operating frequency f _{c of} the linear motor is constant. There is a problem in that the efficiency is lowered and the load cannot be released quickly due to the failure to actively respond to the load.

Accordingly, an object of the present invention is to provide a linear compressor that efficiently performs compression in response to a load by adjusting the operating frequency (f _c ) of the linear motor even if the natural frequency f _n of the piston varies depending on the load. do.

The linear compressor according to the present invention includes a fixed member including a compression space therein, a movable member for compressing the refrigerant sucked into the compression space while reciprocating linearly in the axial direction within the fixed member, and the movable member is connected to the movable member. At least one or more springs installed to elastically support in the movement direction and having a spring constant variable depending on the load, and connected to the movable member to reciprocate linearly the movable member in the axial direction, and operate frequency according to the load (fc ) Is made of a linear motor that adjusts the inductance to vary.

In addition, the linear compressor is installed in a refrigeration / air conditioning cycle, and the load differs between a pressure (condensation pressure) at which the refrigerant condenses in the refrigeration / air conditioning cycle and a pressure (evaporation pressure) at which the refrigerant evaporates in the evaporator. It is preferable to calculate in proportion.

In addition, the load is preferably further calculated in proportion to the pressure (average pressure) which is the average of the condensation pressure and the evaporation pressure.

In addition, the linear motor preferably synchronizes the driving frequency fc to the resonance frequency f n of the movable member, which varies in proportion to the load.

In addition, the linear motor is preferably operated to reciprocate linear motion to the top dead center.

In addition, the linear motor includes an inner stator configured to stack a plurality of laminations in a circumferential direction so as to surround the fixing member, and an outer stator configured to stack a plurality of laminations in a circumferential direction with a predetermined distance outside the inner stator. A coil winding in which a coil is wound so as to generate an electromagnetic force between the inner stator and the outer stator, and a coil winding body wound around the inner stator and the outer stator, and installed to be connected to the movable member so as to be connected to the movable member. A permanent magnet that linearly reciprocates by interaction, wherein the coil winding is composed of two or more coil winding layers stacked radially, and the linear motor selects at least one coil winding layer to apply an input current Basin End, it is desirable to include the further coil volume control means for varying the total inductance for controlling the branching unit in accordance with the capacitor and the load connected in series with the hull.

In addition, the coil winding layer preferably has different inductances.

In addition, the coil winding layer preferably has a different number of windings of the coil.

In addition, the coil winding layer preferably has a different coil thickness.

Further, the control means preferably controls the branching means such that a small inductance is selected at high loads and a large inductance is selected at low loads.

In addition, the coil winding layers are preferably separated from each other.

In addition, the branching means may apply the current to at least one individual terminal among the common terminals commonly connected to one end of each coil winding layer and two or more individual terminals respectively connected to the other end of the coil winding layer.

In addition, the coil winding layer is preferably connected to each other.

In addition, it is preferable that the branching means selects two points from both ends of the coil winding body and a connection point between each coil winding layer to apply the input current.

In addition, the linear compressor control device of the present invention is a coil winding body consisting of two or more coil winding layers in the circumferential direction of the linear compressor, branching means for selecting at least one coil winding layer to apply an input current, and the coil winding body and Capacitors connected in series and control means for adjusting the inductance to control the branching means in accordance with the load to vary the operating frequency (fc).

In addition, the coil winding of the linear compressor of the present invention is laminated in coils in the circumferential direction, and consists of two or more coil winding layers having different inductances.

Hereinafter, the present invention is a linear compressor for operating a moving magnet type linear motor based on the embodiments of the present invention and the accompanying drawings, and the piston connected thereto reciprocates linearly in the cylinder to suck, compress and discharge the refrigerant. It is explained in detail by way of example. However, the scope of the present invention is not limited by the above embodiments and drawings, and the scope of the present invention will be limited only by the contents described in the claims below.

In the linear compressor according to the present invention, as shown in FIG. 3, an inlet tube 2a and an outlet tube 2b through which a refrigerant flows in and out are installed at one side of the sealed container 2, and the inside of the sealed container 2 is provided. The cylinder 4 is installed to be fixed, and the piston 6 is installed in the cylinder 4 so as to reciprocate linear movement so as to compress the refrigerant sucked into the compression space P inside the cylinder 4. At the same time, a variety of springs are installed to elastically support the movement direction of the piston (6), the piston (6) is installed to be connected to the linear motor 10 for generating a linear reciprocating drive force, the natural frequency of the piston (f) Even though _n ) varies depending on the load, the linear motor 10 controls its operating frequency f _c to be synchronized with the natural frequency f _n of the piston as shown in FIGS. 4A and 4B.

In addition, a suction valve 22 is installed at one end of the piston 6 in contact with the compression space P, and a discharge valve assembly 24 is provided at one end of the cylinder 4 in contact with the compression space P. ) Is installed, and the suction valve 22 and the discharge valve assembly 24 are automatically adjusted to open and close according to the pressure inside the compression space P, respectively.

Here, the airtight container (2) is installed so that the upper and lower shells are coupled to each other so that the inside is sealed, the inlet pipe (2a) and the outlet pipe (2b) for the coolant flow in one side is installed, the The piston 6 is installed inside the cylinder 4 so as to be elastically supported in the movement direction for reciprocating linear motion, and the linear motor 10 is assembled to each other by the frame 18 outside the cylinder 4. The assembly is installed to be elastically supported by a support spring 29 on the inner bottom surface of the sealed container (2).

In addition, a predetermined oil is contained in the bottom surface of the airtight container (2), and an oil supply device (30) for pumping oil is installed at the bottom of the assembly, and oil is provided in the lower frame (18) of the assembly. An oil supply pipe 18a is formed to be supplied between the 6 and the cylinder 4, so that the oil supply device 30 is operated by vibration generated by the reciprocating linear motion of the piston 6. The oil is pumped, and this oil is supplied along the oil supply pipe 18a to the gap between the piston 6 and the cylinder 4 for cooling and lubrication.

Next, the cylinder 4 is formed in a hollow shape so that the piston 6 can reciprocate linearly, and a compression space P is formed at one side, and one end is close to the inside of the inlet pipe 2a. It is preferable to be installed on the same straight line as the inlet pipe (2a) in the position.

Of course, the cylinder (4) is installed in one end close to the inlet pipe (2a) so as to reciprocate linear movement, the discharge valve assembly ( 24) is installed.

At this time, the discharge valve assembly 24 is provided to open and close the discharge cover 24a which is installed to form a predetermined discharge space on one end side of the cylinder 4, and one end of the compression space P side of the cylinder. And a discharge valve 24b and a valve spring 24c, which is a kind of coil spring that imparts an elastic force in the axial direction between the discharge cover 24a and the discharge valve 24b, and at one end of the cylinder 4 The O-ring (R) is installed in the fitting so that the discharge valve 24a is in close contact with one end of the cylinder (4).

In addition, a bent loop pipe 28 is installed between one side of the discharge cover 24a and the outlet pipe 2b. The loop pipe 28 guides the compressed refrigerant to be discharged to the outside. In addition, the vibration caused by the interaction of the cylinder 4, the piston 6, and the linear motor 10 buffers the transmission of the entire sealed container 2.

Therefore, when the pressure of the compression space P becomes equal to or greater than a predetermined discharge pressure as the piston 6 reciprocates linearly in the cylinder 4, the valve spring 24c is compressed and the discharge valve ( 24b) is opened, and the refrigerant is discharged from the compression space P, and then completely discharged along the loop pipe 28 and the outlet pipe 2b.

Next, the piston 6 has a coolant flow path 6a formed at the center thereof so that the coolant flowing from the inlet pipe 2a flows, and one end close to the inlet pipe 2a is connected to the connection member 17. In addition, the linear motor 10 is installed to be directly connected to each other, and the suction valve 22 is installed at one end of the inflow pipe 2a opposite to the inflow pipe 2a, and is elastically formed by various springs in the movement direction of the piston 6. It is installed to be supported.

At this time, the suction valve 22 is formed in a thin plate shape so that the center portion is partially cut to open and close the refrigerant passage 6a of the piston, and one side is fixed by a screw to one end of the piston 6a. It is installed as possible.

Therefore, as the piston 6 reciprocates linearly in the cylinder 4, when the pressure of the compression space P becomes lower than or equal to a predetermined suction pressure lower than the discharge pressure, the suction valve 22 is When the refrigerant is opened and sucked into the compression 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 closed while the suction valve 22 is closed. Is compressed.

In particular, the piston 6 is installed so as to be elastically supported in the movement direction, specifically, the piston flange 6b protruding radially at one end of the piston 6 proximate to the inlet pipe 2a is a machine such as a coil spring or the like. Resiliently supported in the movement direction of the piston (6) by the spring (8a, 8b), the refrigerant contained in the compression space (P) on the opposite side to the inlet pipe (2a) acts as a gas spring by its elastic force The piston 6 is elastically supported.

Here, the mechanical springs (8a, 8b) has a constant mechanical spring constant (K _m ) irrespective of the load, the mechanical spring (8a, 8b) is the linear motor (10) relative to the piston flange (6b) It is preferable that the predetermined support frame 26 and the cylinder 4 are fixed to the cylinder 4 side by side in the axial direction, respectively, the mechanical spring (8a) and the cylinder (4) supported by the support frame 26 It is preferable that the mechanical spring 8a to be installed in is configured to have the same mechanical spring constant K _m .

However, the gas spring has a variable gas spring constant (K _g ) depending on the load, but the gas contained in the compression space (P) increases its elastic force as the pressure of the refrigerant increases as the ambient temperature increases As the gas spring loads, the gas spring constant K _g increases.

At this time, the mechanical spring constant (K _m ) is constant, while the gas spring constant (K _g ) is variable depending on the load, so the total spring constant is also variable depending on the load, piston according to the above equation (1) The natural frequency f _n of also varies depending on the gas spring constant K _g .

Therefore, even if the load is variable, the mechanical spring constant (K _m ) and the mass (M) of the piston are constant, while the natural frequency (f _n ) of the piston depends on the load because the gas spring constant (K _g ) is variable. It is greatly influenced by the gas spring constant (K _g ), which is determined using a frequency estimation algorithm in which the natural frequency (f _n ) of the piston is variable according to the load, and accordingly the operating frequency (f _c) of the linear motor. ) Can be synchronized with the natural frequency (f _n ) of the piston to increase the compressor efficiency as well as to quickly release the load.

Of course, the load can be measured in various ways, but such a linear compressor is configured to be included in the refrigeration / air conditioning cycle in which the refrigerant is compressed, condensed, evaporated, and expanded, so that 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 to increase accuracy.

That is, 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. For example, as the difference between the condensation pressure and the evaporation pressure increases, Even if the load is large and the difference between the condensation pressure and the evaporation pressure is the same, the larger the average pressure is, the larger the load is. The corresponding gas spring constant K _g is calculated to correspond to the load.

At this time, the load is actually calculated as measured in proportion to the condensation temperature proportional to the condensation pressure and the evaporation temperature proportional to the evaporation pressure as shown in Figure 5, and proportional to the difference between the condensation temperature and the evaporation temperature and the average temperature.

Specifically, the mechanical spring constant K _m and the gas spring constant K _g can be determined through various experiments. By applying a mechanical spring with a smaller mechanical spring constant than a conventional linear compressor, By increasing the ratio of the gas spring constant for the control so that the resonant frequency of the piston fluctuates in a relatively wide range according to the load, it is controlled to easily synchronize the operating frequency of the linear motor to the natural frequency of the piston that is variable according to the load can do.

6 is a cross-sectional view of the coil according to the present invention, in which the coils according to the present invention are stacked in a radial direction and consist of two or more coil winding layers L1 and L2. The number of coil winding layers L1 and L2 is determined by the number of operating frequencies f _c selected by the manufacturer.

As shown, the coil winding layer (L1, L2) has a different number of windings of the coil, or have a different coil thickness, and have different inductance. In detail, the inductance of the coil winding layer L1 becomes larger than the inductance of the coil winding layer L2.

The coil winding layers L1 and L2 having such different inductances may be connected to each other in series or separated from each other in parallel.

7A and 7B are configuration diagrams of the first and second embodiments of the linear compressor control device composed of the coil of FIG.

As shown, the linear motor 10 is composed of a plurality of laminations (12a) are laminated in the circumferential direction and the inner stator 12 is installed to be fixed to the outside of the cylinder (4) by the frame 18 and And a plurality of laminations 14b are laminated in the circumferential direction around the coil winding body 14a configured to wind the coils so that the inner stator 12 and the inner stator 12 are disposed outside the cylinder 4 by the frame 18. Permanent magnet installed in the gap between the outer stator (14) and the inner stator (12) and the outer stator (14) installed with a gap of the piston 6 and the connecting member (17) 16, the coil winding 14a may be installed to be fixed to the outer side of the inner stator 12.

In particular, the linear motor 10 may vary inductance. Specifically, the linear motor 10 is divided into two or more coil winding layers L1 and L2 in which the coil winding 14a is radially stacked, and the linear The motor 10 is preferably configured to generate an electromagnetic force by applying a current to at least one coil winding layer (L1, L2).
Here, the linear motor 10 is a branching means (15, 15) for applying at least one coil winding layer (L1, L2) to apply a current input from the outside, and the branching means (15) by determining the load And control means 18 for controlling 15).

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At this time, each coil winding layer (L1, L2) may be configured to have a different inductance (L), for example, the number of windings of the coil and / or the thickness of the coil (wire diameter) in each winding layer (L1, L2) ) Can be different.

FIG. 7A illustrates a case where the coil winding layers L1 and L2 of the coil winding body 14a are separated from each other and have a parallel structure. FIG. 7B illustrates the coil winding layers L1 and L2 of the coil winding body 14a connected to each other. This is the case of a serial structure. According to the connection state of the coil winding layers L1 and L2, the branching means 15 and 15 may cause a combination of various inductances.

First, in FIG. 7A, the connection terminal 15a is commonly connected to one end of the coil winding layers L1 and L2, and the connection terminal 15b is connected to the other end of the coil winding layer L1 and the connection terminal 15c. Is connected to the other end of the coil winding layer L2, the branching means 15 always selects the connecting terminal 15a, and selects at least one of the connecting terminals 15b and 15c by the switch 15d and inputs it. Apply a current. Accordingly, the inductances that can be selected and combined by the branching means 15 are the two cases when the coil winding layers L1 and L2 are respectively selected, and when the coil winding layers L1 and L2 are selected together. In case 1 (an additional switch is required due to the parallel connection of L1 and L2).

In addition, in FIG. 7B, the connecting terminal 15a is connected to one end of the coil winding layer L1, the connecting terminal 15b is connected to one end of the coil winding layer L2, and the connecting terminal 15c is coil winding. It is connected to the connection point between the layers L1 and L2, and the branching means 15 selects two of the connection terminals 15a, 15b, and 15c by the switches 15d and 15e to apply an input current. Therefore, the inductance that can be selected and combined by the branching means 15 is the coil winding layer L1 when the connection terminals 15a and 15c are selected and the coil when the connection terminals 15b and 15c are selected. The winding layer L2 and the coil winding layers L1 and L2 are connected in series when the connection terminals 15a and 15b are selected.

Then, the control unit 18 receives the condensation temperature and the evaporation temperature of the refrigerant to determine the load (for example, by using the data on the graph of FIG. 5 through temperature information input according to a predetermined frequency estimation algorithm). After estimating the natural frequency f _n ), the operation of the branching means 15, 15 is controlled according to the magnitude of the load. The control means 18 allows a small inductance to be selected in case of high load (or high cooling power) to increase the operating frequency f _c and a large inductance to be selected in case of low load (or low cooling power) operating frequency f _c ) controlling the branching means 15, 15 to lower. The control by the control means 18 of the branching means 15, 15 allows the operating compressor f _c to be synchronized with the natural frequency f _n which varies according to the above-described load so that the linear compressor is in a resonant state. Control to combine the appropriate inductance among the various inductances for operation.

According to the present invention configured as described above, the gas spring constant and the natural frequency are varied by a predetermined frequency estimation algorithm according to the load, and the operation is performed in a resonance state by synchronizing the operating frequency of the linear motor with the estimated natural frequency. And, consequently, the compression efficiency can be maximized.

Claims (28)

A fixing member including a compression space therein; A movable member compressing the refrigerant sucked into the compression space while reciprocating linearly in the fixed member in the axial direction; At least one spring installed to elastically support the movable member in a direction of movement of the movable member and varying a spring constant depending on a load; And a linear motor installed to be connected to the movable member to reciprocate linearly the movable member in the axial direction and to adjust the inductance so that the driving frequency (fc) varies according to the load. The method of claim 1, The linear compressor is installed in a refrigeration / air conditioning cycle, and the load is proportional to a difference between a pressure (condensation pressure) at which the refrigerant condenses in the refrigeration / air conditioning cycle and a pressure (evaporation pressure) at which the refrigerant evaporates in the evaporator. Linear compressor, characterized in that calculated. The method of claim 2, And the load is further calculated in proportion to the pressure (average pressure) which is the average of the condensation pressure and the evaporation pressure. The method of claim 1, And the linear motor synchronizes the operation frequency fc to a resonance frequency f n of the movable member which is changed in proportion to the load. The method of claim 4, wherein And the linear motor operates the reciprocating linear motion to the top dead center. The method of claim 1, The linear motor may include an inner stator surrounding the fixing member, an outer stator positioned at a predetermined interval outside the inner stator, and a coil winding body in which a coil located between the inner stator or the outer stator is wound; A permanent magnet located in the gap between the inner stator and the outer stator and installed to be connected to the movable member, wherein the coil winding body is composed of two or more coil winding layers radially stacked, and the linear motor includes at least one Branching means for selecting the coil winding layer to apply an input current, a capacitor connected in series with the coil winding body, and control means for varying the overall inductance for controlling the branching means in accordance with the load Linear compressor made. The method of claim 6, And the coil winding layer has different inductances. The method of claim 7, wherein The coil winding layer is a linear compressor, characterized in that the number of turns of the coil is different. The method of claim 7, wherein The coil winding layer is a linear compressor, characterized in that having a different coil thickness. The method according to any one of claims 6 to 9, And said control means controls said branching means such that a small inductance is selected at high loads and a large inductance is selected at low loads. The method according to claim 6 or 7, The coil winding layer is a linear compressor, characterized in that separated from each other. The method of claim 11, The branching means may apply the current to a common terminal commonly connected to one end of each coil winding layer, and at least one individual terminal among two or more individual terminals respectively connected to the other end of the coil winding layer. . The method according to claim 6 or 7, And the coil winding layer is connected to each other. The method of claim 13, And the branching means selects two points from both ends of the coil winding and a connection point between each coil winding layer to apply the input current. A coil winding body comprising two or more coil winding layers in a radial direction; Branching means for selecting at least one coil winding layer to apply an input current; A capacitor connected in series with the coil winding; And a control means for controlling the inductance so as to control the branching means according to the load so that an operating frequency fc is variable. The method of claim 15, And the coil winding layer has different inductances. The method of claim 16, The coil winding layer is a linear compressor control device, characterized in that the number of turns of the coil is different. The method of claim 16, The coil winding layer is a linear compressor control device, characterized in that having a different coil thickness. The method according to any one of claims 15 to 18, And the control means controls the branching means such that a small inductance is selected at high loads and a large inductance is selected at low loads. The method according to claim 15 or 16, And the coil winding layer is separated from each other. The method of claim 20, The branching means may be configured to apply the input current to at least one individual terminal of the common terminal commonly connected to one end of each coil winding layer, and at least two individual terminals respectively connected to the other end of the coil winding layer. Compressor Control. The method according to claim 15 or 16, And the coil winding layers are connected to each other. The method of claim 22, And the branching means selects two points from both ends of the coil winding body and a connection point between each coil winding layer to apply an input current. Coil winding body of a linear compressor having a different inductance, consisting of two or more coil winding layers stacked in a radial direction. The method of claim 24, The coil winding layer is a coil winding of the linear compressor, characterized in that the number of turns of the coil is different. The method of claim 24, The coil winding layer of the linear compressor, characterized in that the coil winding layer has a different coil thickness. The method according to any one of claims 24 to 26, The coil winding layer of the linear compressor, characterized in that the coil winding layer is separated from each other. The method according to any one of claims 24 to 26, The coil winding of the linear compressor, characterized in that the coil winding layer is connected to each other.

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