JPH11324912A - Linear compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To control the capacity by comprising a stopper for stopping a slide seat which is movable in the reciprocating direction with a constant resonance frequency by a linear motor, at a predetermined position against the reaction force of an elastic member, and a stopper for stopping the slide seat at a predetermined position against the pressing force. SOLUTION: A linear compressor comprises a member for elastically supporting a piston 4 inserted into a cylinder 7, a first stopper portion 45a for stopping a slide seat 14 supporting the member and movable in the reciprocating direction at a predetermined position against the reaction force of the elastic member with a pressing means in the opposite direction of more than the reaction force generated on the elastic member, and a second stopper portion 45b for stopping the slide seat 14 at a predetermined position againt the pressing force of the pressing means. Thereby a neutral point movement can be surely performed without coupling a resonance system as a gas spring by the back pressure space of the slide seat 14, and a capacity controllable linear compressor of high efficiency can be provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a capacity control mechanism for a linear compressor used for refrigeration and air conditioning.

[0002]

2. Description of the Related Art FIG. 7 is a sectional view of a conventional linear compressor disclosed in Japanese Patent No. 2687689. In a closed container 5, a stator composed of iron cores 11a and 11b and a permanent magnet 1 and a cylinder 7 are fixed. A mover including a piston 4 and a coil 2 is disposed on the fixed portion so as to be supported by the resonance spring 3. Coil 2 has iron cores 11a and 11
b, and is placed in the magnetic field of the magnetic circuit formed by the permanent magnet 1 via the iron cores 11a and 11b, so that when a current flows through the coil, the magnetic field generated by the coil and the stator Due to the interaction with the magnetic field, the mover receives an axial force (thrust).

When an alternating current is passed through the coil 2, the direction of the thrust acting on the mover is alternately switched, and the mover reciprocates. Piston 4 configured as part of mover
Reciprocating in the cylinder 7, the volume of the compression chamber 12 periodically increases and decreases, so that the gas sucked from the suction pipe 6 into the compression chamber via the suction valve 8 is compressed, and then discharged through the discharge valve 9 to the discharge pipe. It is discharged from 10 to the outside of the closed container.

The power for inhaling, compressing, and discharging gas is generated by a linear motor unit including a permanent magnet 1, a coil 2, and iron cores 11a and 11b. However, in order to perform the entire process directly with only the thrust generated by the motor, It is necessary to generate a thrust exceeding the compression reaction force of the gas over the entire stroke area, and it is difficult to construct a compressor having a large size and a realistic size due to a large motor portion. Then, the mover is connected to the resonance spring 3
A resonance system consisting of a spring and a mass is constructed by supporting it, and the frequency of the alternating current to be applied matches the resonance frequency determined from the mass of the movable part and the spring constant of the resonance spring, and the mechanical resonance phenomenon is used. I have. The amplitude at this time is determined depending on the voltage of the power supply up to the maximum stroke determined by the size of the motor unit.

In the above-described example, a compression section composed of a piston / cylinder is arranged outside the motor section. However, a configuration in which the compression section is incorporated in the motor section for miniaturization is schematically illustrated. Is shown in FIG. In FIG. 8A, the resonance spring 3 is assumed to be a leaf spring, and is an example in which a stator is constituted by a so-called moving coil (MC) type linear motor including an iron core 11 and a magnet 1, and a mover including a coil 2. However, when the motor is a moving magnet (MM) type, the configuration becomes as shown in FIG. 8B. In the motor section, the magnet 1 forms a mover, and the coil 2 and the iron cores 11a and 11b form a stator. FIG. 8C is a schematic diagram of a case in which a moving iron (MI) motor is used as a motor and a piston is fixed and a cylinder is driven. The same or corresponding portions as those in FIG. 7 are denoted by the same reference numerals, and description thereof will be omitted.

In the motor section, the stator is a magnet 1, a coil 2,
The movable element is composed of an iron core 11a, and the mover is composed of an iron core 11b, and drives the cylinder 7 integrated with the movable iron core.

[0007] In the above configuration, the movable element and the spring-mass system of the resonance spring are resonated by the thrust generated in the motor section, regardless of the type of the motor and the difference between the piston drive and the cylinder drive. The operating principle of reciprocating the piston 4 and the cylinder 7 relatively is the same.

[0008]

The conventional linear compressor as described above utilizes resonance so that the operating frequency cannot be freely changed. Therefore, when using the compressor for refrigeration and air conditioning, it is necessary to perform capacity control. The stroke volume is changed by changing the amplitude by voltage control. At this time, simply reducing the amplitude increases the compression chamber volume at the time of completion of compression / discharge at the top dead center, that is, the so-called dead volume, leading to a decrease in efficiency.
It is necessary to take measures to reduce the dead volume when operating with small amplitude.

As a method of reducing the dead volume, there are two methods, that is, a head movement for moving the top dead center position on the fixed side and a neutral point movement for moving the center position of the amplitude. FIG. 9 is a schematic diagram showing a comparison between the movement of the head and the movement of the neutral point. For simplicity, the motor section is omitted and only the piston drive type is shown. In contrast to the full stroke shown in FIG.
In (a), the dead volume at the time of a small stroke is reduced by moving the head part of the cylinder 7 as a slide head 13 movable in the axial direction by a pressing force FH.
As shown in FIG. 9 (c), the neutral point is moved by moving the slide seat 14 capable of moving the fixed side mounting portion of the resonance spring 3 in the axial direction by the pressing force FN to move the neutral point, thereby reducing the dead volume. cut back. In addition, since the piston is driven, the head moves by moving the cylinder head. However, in the case of the cylinder drive, the fixed piston is moved.

The movement of the head shown in FIG.
9C, the pressing force FN is applied to the piston via a resonance spring, and the piston is driven by a motor. Since a force is also acting, FN can be set to a gas pressure or less. When no pressing force is applied, the slide seat 14 is pushed back to the original position by the reaction force of the resonance spring 3, whereas the slide head 13 may become unstable and the position may not be determined. It is necessary to provide means for returning, such as 15. From these points, the neutral point movement is more advantageous than the head movement.

FIG. 10 shows a linear compressor disclosed in JP-A-9-151843, in which a piston is driven by an MC type motor. The capacity control by moving the neutral point is performed by changing the volume of the back pressure chamber 20,
Since the gas in the back pressure chamber has compressibility and acts as a gas spring, in the configuration shown in the figure, the position of the slide seat 14 is a position where the spring force of the resonance spring at that time and the pressure in the back pressure chamber are balanced, and the spring force is reduced. The position changes every moment with the change. That is, a spring system in which the resonance spring 3 and the gas spring are coupled with each other with the slide seat 14 interposed therebetween is formed, and the intended neutral point cannot be moved.

SUMMARY OF THE INVENTION In view of the above, an object of the present invention is to provide a linear compressor having a neutral point moving means which can function as a capacity control mechanism.

[0013]

According to the present invention, there is provided a linear compressor, comprising: a cylinder reciprocally driven at a constant resonance frequency by a linear motor; or an elastic member for elastically supporting a piston inserted in the cylinder; A slide seat that supports an elastic member and is movable in the reciprocating drive direction; a pressing unit that presses the slide seat in a direction opposite to the reaction force with a force greater than a reaction force generated in the elastic member; A first stopper for stopping at a predetermined position against the reaction force of the elastic member, and a second stopper for stopping the slide seat at a predetermined position against the pressing force of the pressing means. , Is provided.

The amplitude of the reciprocating drive is maximized when the position of the slide seat is determined by the first stopper portion, and is minimized when determined by the second stopper portion.

The amplitude of the reciprocating drive is minimized when the position of the slide seat is determined by the first stopper portion, and is maximized when determined by the second stopper portion.

The pressing by the pressing means acting on the slide seat and the seat stopper is turned ON / OFF by an external operation.
It can be turned off.

The pressing means switches between high pressure and low pressure.

Further, the initial deformation amount of the elastic member when the elastic member is stopped is
At this time, the amplitude of the reciprocating drive is set to １ ／ or more.

Further, a coil spring is used as the elastic member.

The elastic members are arranged separately on both sides of the mover, and a slide seat is attached to one of the elastic members and pressed.

The two elastic members have the same elastic coefficient.

Further, the two elastic members have different elastic coefficients.

Further, when the position of the slide seat is determined by the second stopper portion, the amount of deformation of the elastic member having the larger elastic coefficient at the time of stop becomes equal to or more than の of the stroke at that time. It is.

Further, an elastic member for elastically supporting a cylinder or a piston fitted in the cylinder reciprocally driven at a constant resonance frequency by the linear motor, and an elastic member for supporting the elastic member and movable in the reciprocating driving direction. A slide seat, a first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force equal to or greater than the pressing force of the first pressing means for the slide seat. Second pressing means for pressing the slide seat in a direction opposite to the pressing direction of the first pressing means, and a first stopper for stopping the slide seat at a predetermined position against the reaction force of the elastic member. Part, a second stopper part for stopping the slide seat at a predetermined position against the pressing force of the first pressing means, and a second stopper part for pressing the slide seat against the pressing force of the second pressing means. hand, Serial first comprises a third stopper part stopping at a predetermined position between the second stopper portion.

Further, an elastic member for elastically supporting a cylinder or a piston inserted in the cylinder reciprocally driven at a constant resonance frequency by a linear motor, and an elastic member for supporting the elastic member and movable in the reciprocating driving direction. A slide seat, a first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force equal to or greater than the pressing force of the first pressing means for the slide seat. A second pressing means for pressing in a direction opposite to a pressing direction of the first pressing means with a force of the first pressing means, and a first for stopping the slide seat at a predetermined position against a reaction force of the elastic member. A stopper portion, and a third stopper portion for stopping the slide seat at a predetermined position between the first and second stopper portions against a reaction force of the elastic member.

Further, by arranging a plurality of seat stoppers, a stopper portion for determining the position of the slide seat is firstly provided.
A plurality is provided between the second stopper portions.

[0027]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. 1 is a cross-sectional view showing a linear compressor according to Embodiment 1 of the present invention, and FIG. 2 is a schematic view for explaining the operation. FIG. 1 shows a cylinder drive system using an MI type linear motor. In FIG. 1, a stator 41 comprising a magnet 1, a coil 2, and an iron core 11b is shown.
And an iron core 11a, which is a mover, form an MI type linear motor.
The cylinder is driven by being fastened by the push nut 31 through the “0”. On both sides of the stator 41, the lower frame 23a and the upper frame 23
The slide guide 22 is attached to the lower frame 23a, and the stay holder 25 is attached to the upper frame 23b in the radial direction of the cylinder 7 and the plate springs 24a and 24b elastically support the axial direction. It is fastened with bolts.

The inner circumference of the leaf spring 24a is fastened to the cylinder head 33b by a lock nut 34, and the inner circumference of the leaf spring 24b is fastened to the cylinder 7 and the push nut 31 by a lock nut 32. The cylinder head 33b is attached to the cylinder 7 with the head plate 33 therebetween.
a and a screw 33 with a suction valve 8 interposed therebetween, and a port 33a1 provided in the head plate and a cylinder head center hole 33b1 form a gas suction path to the compression chamber 12, and a The gas is led to the compression chamber 12 through the suction pipe 6.

In the compression chamber 12, the piston 4 is fixedly arranged at a predetermined position inside the cylinder 7 which reciprocates integrally with the iron core 11a, the suction valve 8, the head plate 33a, and the cylinder head 33b. Formed by The piston 4 is fixed to the piston stay 27 by a push bolt 28, and the piston 4 is fixed to the stay holder 25 attached to the iron core 11b by the stay fixing screw 26. Stationary arrangement.

The piston 4 is provided with a discharge port 401, and the discharge valve 9 held by the discharge valve holder 29 is disposed at the outlet thereof. After the gas compressed in the compression chamber 12 is discharged by pushing the discharge valve 9 open, the gas is guided to the discharge pipe 10 through the hole at the center of the stay holder 25 and discharged out of the closed vessel 5.

The movable part 4 including the iron core 11a, the cylinder 7, the head plate 33a, the cylinder head 33b, etc.
2 has a resonance spring 3a, 3b which is an elastic member at both ends.
The other end of the resonance spring 3b is supported by the stay holder 25, and the resonance spring 3a
Is supported on the slide seat 14. The resonance frequency of the system consisting of the two resonance springs 3a, 3b and the movable part 42 is
It is determined by the spring constant of the resonance springs 3a and 3b and the mass of the movable part. Each spring is pre-assembled in a contracted state by a length equal to or longer than the extension allowance so that the resonance spring does not become longer than its natural length when it is stretched most along with the reciprocating motion of the movable portion 42. The resonance springs 3a and 3b use coil springs.

Next, the operation will be described with reference to FIGS. FIG. 1A shows the case where the slide seat 14 is supported by the first stopper portion of the guide member 22 during the full stroke, and FIG. 1B shows the case where the slide seat 14 is supported by the second stopper portion of the seat stopper 22b during the capacity control. In this case, FIG. 1C is a cross-sectional view of main parts when the seat stopper 22b is supported by the third stopper portion during capacity control. FIG. 2 (a),
FIGS. 1 (b) and 1 (c) show these FIGS. 1 (a), 1 (b) and 1 (c).
FIG.

First, when an alternating current having a frequency corresponding to the resonance frequency of the spring-mass system, which is the mass of the springs of the resonance springs 3a and 3b and the movable part 42, is passed through the coil 2, the movable part will reciprocate at the same frequency. The suction force, the compression and the discharge of the gas utilizing the resonance phenomenon are performed, and the amplitude of the reciprocation is adjusted by the power supply voltage. The highest compression efficiency is obtained when the volume of the compression chamber 12 is extremely small when the movable-side head plate 33a comes closest to the fixed-side piston 4. When the slide seat 14 of the resonance spring 3a on the head side is at a position far from the piston as shown in the figure, when the displacement is controlled by reducing the amplitude by operating at a lower power supply voltage than at the full stroke, the compression is completely completed. As the compression chamber volume at the time of compression, that is, the so-called dead volume increases, the efficiency decreases.

Therefore, when controlling the capacity, the slide seat 1
A path (not shown) for guiding high-pressure gas, which is the first pressing means, is provided in the back pressure space on the back surface of the slide 4. The point is moved in the direction in which the volume of the compression chamber is reduced, and the dead volume when the amplitude is small is reduced to prevent a decrease in efficiency. However, the pressing force acting on the back surface of the slide seat 14 and the reaction force of the resonance spring 3a are reduced. In order to balance, the position of the slide seat is not determined because the reaction force of the spring changes every moment, and a spring-mass system is formed in which the mass of the slide seat 14 and the gas spring of the back pressure chamber are coupled. .

In order to avoid such a situation, in the present embodiment, a high pressure acts on the back surface of the slide seat 14 so that a force greater than the maximum value of the reaction force from the resonance spring 3a in one cycle of the reciprocating motion acts. The cross-sectional area is set. The remaining part of the pressing force, which is offset by the spring reaction force, is used as the guide member 2.
When the slide seat 14 is received by the first stopper portion 2a, the slide seat 14 is stopped at a position where it comes into contact with the first stopper portion.

A seat stopper 22b having an end surface functioning as a stopper is movable in the axial direction by being guided by the guide member 22, and is provided in the back pressure space formed on the surface opposite to the slide seat 14. By providing a path (not shown) for guiding the gas as the second pressing means, by switching between high pressure and low pressure, the position of the stopper part can be set at two places of the second stopper part and the third stopper part. Has become.

With the above-described configuration, the position of the slide seat 14 is adjusted by the guide member 22a as shown in FIGS. 1 (a) and 2 (a) according to the normal operation and the capacity control operation. When supported by one stopper, (2) FIG.
2 (b), as shown in FIG. 2 (b), when supported by the second stopper portion by the seat stopper 22b abutted against the guide member 22, (3) FIGS. 1 (c) and 2 (c) As shown in (3), three positions are set when the seat is supported by the third stopper portion by the seat stopper 22b abutted against the guide member 22a.

At this time, in each of the above cases, the back pressure of the slide seat 14 / back pressure of the seat stopper 22b is (1) low pressure /
High-pressure or low-pressure, (2) high-pressure / low-pressure, (3) high-pressure / high-pressure, and the relationship of the forces related to position determination is (1) spring minimum reaction force> slide seat back pressure, (2) slide seat back pressure-spring maximum. Reaction force> Seat stopper back pressure = 0, (3) Slide seat back pressure−Spring maximum reaction force <Seat stopper back pressure, the pressure receiving area of each back pressure is determined.

Although the two resonance springs 3a and 3b have different spring constants due to space restrictions, both of them have different spring constants when the slide seats are in the first, second and third displacement positions. The amount of initial deformation is set so that it does not exceed the natural length even when stretched most during one cycle, so that the spring constant constituting the system does not change discontinuously during one cycle.

The above operation will be described with reference to FIG. At the time of full stroke, as shown in FIG. 2A, the slide seat 14 is supported by the first stopper portion of the guide member 22a by the spring force of the resonance spring 3a to determine the position of the neutral point. As shown in (b), the position of the neutral point is determined by being supported by the second stopper portion of the seat stopper 22b. At this time, the volume of the compression chamber 12 is minimized. Further, as shown in FIG. 2C, the position of the neutral point is determined by being supported by the third stopper portion of the seat stopper 22b, and the volume of the compression chamber 12 is between the full stroke and the minimum.

As described above, the back pressure space of the slide seat is
The neutral point can be reliably moved without coupling the resonance system as the gas spring, and the capacity control can be performed with high efficiency.

In this embodiment, the case of cylinder drive is shown, but the neutral point can be similarly moved in the case of piston drive, and will be described with reference to FIG. In the schematic diagram of FIG. 3, the piston 4 is radially supported by a leaf spring 23 and is configured to resonate by the resonance spring 3. The fixed portion of the resonance spring 3 on the fixed side is a slide seat 14 movable in the axial direction.
2 moves against the spring force of the resonance spring 3 by a pressing means such as guiding high-pressure gas to the back pressure chamber 22c formed between the back pressure chamber 22 and the pressure spring 22. As a result, the position of the piston 4 at the neutral point moves in the direction in which the volume of the compression chamber 12 decreases with respect to the cylinder 7, and the dead volume can be reduced when the amplitude is small.

The slide seat 14 is pressed against the first stopper portion 22a by a spring force at the time of a full stroke, and its position is determined. At the time of capacity control, the pressing force is set to be larger than the maximum value in one cycle of the spring force. Since the position is determined by being pressed against the stopper portion 22b, the position does not change every moment.

Further, by providing an external pressure introduction path so that the pressing force against the slide seat and the seat stopper is applied by the pressure of the slide seat back pressure chamber, the neutral point can be moved from the outside.

When the coil spring of the spring is used, especially in the case of a compression spring, the spring exerts an elastic force proportional to the position on the slide seat 14 based on a constant spring constant. In order to make it work, the entire length of the stroke needs to fall within a range where the length of the spring is equal to or less than the natural length and equal to or more than the close contact height. For this reason, since the stroke is displaced by １ ／ of the stroke from the neutral position, it is necessary that the spring is deformed by ２ of the stroke when stopped. Therefore, by setting the amount of deformation of the elastic member (spring) at the time of stop to 1/2 stroke or more at that time, when the elastic member is a coil spring, it is possible to prevent the spring constant from changing discontinuously in the middle of the stroke, It is possible to prevent the maximum stress of the elastic member from becoming excessive.

When the position of the slide seat is determined by the second stopper portion, the amount of deformation of the elastic member having the larger elastic coefficient at the time of stop is set to be equal to or more than 1/2 of the stroke at that time. It is possible to prevent the spring constant from changing discontinuously in the middle, and to prevent the maximum stress of the elastic member from becoming excessive.

In addition, when the resonance springs are provided on both sides of the mover, when the spring constants of the two resonance springs are equal, when the slide seat is supported by the first stopper (the state where the springs are most extended), Spring is half of stroke at neutral position
If it is deformed as described above, even when the neutral point is moved, it is deformed by half or more of the stroke at the neutral point. When the spring constants of the two resonance springs are different, it is generally better to initialize the stress generated in the spring so that the maximum deformation amount of the spring having the larger spring constant is the smallest. Since the amount of deformation of the smaller spring is larger than the amount of deformation of the other spring, the larger spring constant is deformed by half or more of the stroke. The amount of deformation may be determined.

As described above, when the position of the slide seat is determined by the second stopper portion, the amount of deformation of the elastic member having the larger elastic coefficient at the time of stop is equal to or more than の of the stroke at that time. In addition, the spring constant can be prevented from changing discontinuously in the middle of the stroke, and the maximum stress of the elastic member can be prevented from becoming excessive.

Further, it is possible to dispose coil springs having different spring constants on both sides of the movable portion as elastic members, or to arrange coil springs having the same spring constant. Can be reduced, and a peripheral space can be effectively used by using springs having different spring constants as necessary.

Embodiment 2 FIG. 4 is a cross-sectional view showing a linear compressor according to Embodiment 2 of the present invention, and FIG. 5 is a schematic view for explaining the operation. FIG. 4 is of a cylinder drive type using an MI type linear motor similarly to FIG. 1 of the first embodiment. A cylinder integrated with the movable iron core 11a of the motor is supported by the resonance springs 3a and 3b to form a resonance system, and is movable by passing an alternating current to the coil 2 forming the stator 41 together with the magnet 1 and the iron core 11b. The piston stay 27 and the stay holder 2
The basic function of compressing the gas in the compression chamber 12 formed between the piston 4 and the piston 4 fixed to the stator 41 through 5 is the same as that in FIG.

The two resonance springs 3a and 3b have the same spring constant, and the slide seat 14 for moving the neutral point of the resonance amplitude is mounted on the side of the resonance spring 3b. Stay holder 2
A part of 5 serves as a first stopper of the slide seat 14, and a stopper member 25a fixed to the stay holder 25 serves as a second stopper. The third stopper portion is formed when the seat stopper 25b abuts against the stopper member 25a by back pressure.

In the first embodiment shown in FIG. 1, the position of the first stopper portion corresponds to a full stroke, whereas in the second embodiment, the position of the second stopper portion corresponds to a full stroke. doing. In the first embodiment, the seat stopper 22b of FIG. 1 forms a second stopper portion facing the back pressure of the slide seat 14, whereas in the second embodiment, the seat stopper 25b
The direction of the back pressure acting on b is the direction facing the spring reaction force acting on the slide seat 14.

Next, the operation will be described with reference to FIGS. FIG. 4A shows the stopper member 2 at full stroke.
4a when supported by the second stopper portion according to FIG.
4B shows a case where the first stopper portion is supported by the stay holder 25 during the capacity control. FIG. 4C shows a case where the third stopper portion is supported by the seat stopper 25b abutted against the stopper member 25a during the capacity control. It is principal part sectional drawing in the case of being performed. FIGS. 5A, 5B, and 5C show FIGS.
It is a schematic diagram respectively corresponding to (a), (b), (c).

In each of the above cases, the back pressure of the slide seat 14 / back pressure of the seat stopper 25b is (1) low pressure / low pressure, (2) high pressure / high pressure or low pressure, and (3) low pressure / high pressure. The relationship is (1) spring minimum reaction force> slide seat back pressure, spring minimum reaction force> seat stopper back pressure, (2) slide seat back pressure-spring maximum reaction force> 0, (3) seat stopper back pressure-spring Set the maximum reaction force> 0.

The operation will be described with reference to FIG. At the time of a full stroke, as shown in FIG.
As shown in FIG. 5B, the position of the neutral point is determined by being supported by the second stopper portion by the stopper member 25a. During the capacity control, as shown in FIG. 5B, the neutral point is supported by the first stopper portion of the stay holder 25. Determine the position of At this time, the volume of the compression chamber 12 is minimized. FIG.
As shown in (c), the position of the neutral point is determined by being supported by the third stopper portion by the seat stopper 25b abutted against the stopper member 25a, and the volume of the compression chamber 12 is set between the full stroke and the minimum. I do.

As described above, the neutral point can be reliably moved and the capacity control with high efficiency can be performed.

When the position of the second stopper portion when the slide seat is pressed corresponds to the minimum capacity as described in the first embodiment, the slide seat is moved to the fixed portion side (the guide member The slide seat can be arranged on the fixed part side (the side with the stay holder) with respect to the movable part when the second stopper position corresponds to the full stroke as shown in the first embodiment. , And the capacity control mechanism can be arranged on either side, so that the degree of freedom of design can be expanded.

Embodiment 3 FIG. Although the first and second embodiments have one seat stopper and correspond to three neutral points, the present embodiment has a plurality of seat stoppers. FIG. 6 is an explanatory diagram in the case of performing multi-stage displacement control of the linear compressor according to the third embodiment. FIG. 6A shows the case where the slide seat 14 is supported by the first stopper 46a, and FIG. 6B shows that the second seat stopper 45b is pressed against the second stopper 46b so that the second seat stopper 45b is pressed against the slide seat 14. FIG. 6C shows a case where the third stopper is formed, and FIG. 6C shows a case where the fourth stopper is formed on the slide seat 14 by pressing the first seat stopper 45a against the second stopper 46b. (d) is a view showing a case where the slide seat 14 is supported by the second stopper 46b. 1 in the figure
4a is a recess formed in the slide seat 14 to support a spring, 45a is a first seat stopper, 45b is a second seat stopper, 46 is a holder, 46a is a first stopper, 46b is a second stopper, and 3 is It is a resonance spring.

With this configuration, the backing pressure of the slide seat 14 in the first stopper portion is low as shown in FIG. 6A, and the first stopper portion is moved through the first and second seat stoppers 45a and 45b. The second stopper portion is supported by one stopper 46a, and the slide seat 14 is pressed against the second stopper 46b by receiving a high pressing force, as shown in FIG. 6D. At this time, the elastic force of the resonance spring 3 <the pressing force.

As shown in FIG. 6 (b), the third stopper portion applies a high pressure to the back surface of the second seat stopper 45b to cause the slide seat 14 to move through the first seat stopper 45a. Against the elastic force of the resonant spring 3 transmitted
It is formed by pressing the second seat stopper 45b against the second stopper 46b. As shown in FIG. 6C, the fourth stopper portion is provided with a first seat stopper 45.
The first seat stopper 45a is pressed against the second stopper 46b against the elastic force of the resonance spring 3 transmitted from the slide seat 14 by applying a high pressing force to the rear surface of the first seat a.

In this manner, a plurality of stopper portions are formed between the first and second stopper portions, so that a neutral point can be set corresponding to four or more levels of capacity control.

[0062]

As described above, according to the present invention, an elastic member for elastically supporting a cylinder reciprocatingly driven by a linear motor at a constant resonance frequency or a piston inserted in the cylinder, A slide seat that is supported and movable in the reciprocating drive direction, pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member; and A first stopper for stopping at a predetermined position against a reaction force, and a second stopper for stopping the slide seat at a predetermined position against the pressing force of the pressing means. Because the back pressure space of the slide seat does not couple with the resonance system as a gas spring, the neutral point can be reliably moved and a highly efficient linear compressor with capacity control can be configured. Rukoto can. Also, if the position of the second stopper portion when pressing the slide seat corresponds to the minimum capacity, the slide seat can be arranged on the side opposite to the fixed portion side with respect to the movable portion, and the second stopper position is set at the time of full stroke. When corresponding, the slide seat can be arranged on the fixed part side with respect to the movable part, and the capacity control mechanism part can be arranged on either side, so that the degree of freedom of design can be expanded.

Further, the amplitude of the reciprocating drive is maximized when the position of the slide seat is determined by the first stopper, and the amplitude (stroke) is minimized when determined by the second stopper. The slide seat can be arranged on the side opposite to the fixed section with respect to the movable section.

Further, the amplitude of the reciprocating drive is minimized when the position of the slide seat is determined by the first stopper portion, and the amplitude is maximized when determined by the second stopper portion. Can be arranged on the fixed part side with respect to the movable part.

The pressing by the pressing means acting on the slide seat and the seat stopper is turned ON / OFF by an external operation.
Since it can be turned off, the operation is easy.

Further, the pressing means switches between high pressure and low pressure, so that the structure can be simplified.

The amount of initial deformation of the elastic member when stopped is
Since the stroke is set to be の or more of the stroke at that time, if the elastic member is a coil spring, it is possible to prevent the spring constant from changing discontinuously in the middle of the stroke or to prevent the maximum stress of the elastic member from becoming excessive. Can be avoided.

Since the coil spring is used for the elastic member, the structure can be simplified and the size can be reduced.

Further, since the elastic members are separately arranged on both sides of the movable element and a slide seat is attached to one elastic member and pressed, the coil springs having different spring constants are arranged on both sides of the movable part. It is possible to arrange even coil springs with spring constants, so if the spring constants are the same, the amount of deformation of each spring can be reduced, and if necessary, the surrounding space can be effectively used by using springs with different spring constants Available.

Since the two elastic members have the same elastic modulus, the amount of deformation of the spring can be reduced, and the peripheral space can be used effectively.

Since the two elastic members have different elastic coefficients, the surrounding space can be effectively used.

Further, when the position of the slide seat is determined by the second stopper portion, the amount of deformation of the elastic member having the larger elastic coefficient at the time of stop is set to be not less than 1/2 of the stroke at that time. When the elastic member is a coil spring, the spring constant can be prevented from changing discontinuously in the middle of the stroke, and the maximum stress of the elastic member can be prevented from becoming excessive.

Further, an elastic member for elastically supporting a cylinder reciprocally driven at a constant resonance frequency by a linear motor or a piston fitted in the cylinder, and an elastic member for supporting the elastic member and movable in the reciprocating driving direction. A slide seat, a first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force equal to or greater than the pressing force of the first pressing means for the slide seat. Second pressing means for pressing the slide seat in a direction opposite to the pressing direction of the first pressing means, and a first stopper for stopping the slide seat at a predetermined position against the reaction force of the elastic member. Part, a second stopper part for stopping the slide seat at a predetermined position against the pressing force of the first pressing means, and a second stopper part for pressing the slide seat against the pressing force of the second pressing means. hand, Serial first, the third stopper part stopping at a predetermined position between the second stopper portion, since with a may correspond to the capacity control of the three stages.

Further, an elastic member for elastically supporting a cylinder reciprocatingly driven at a constant resonance frequency by a linear motor or a piston fitted in the cylinder, an elastic member for supporting the elastic member and being movable in the reciprocating driving direction. A slide seat, a first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force equal to or greater than the pressing force of the first pressing means for the slide seat. A second pressing means for pressing in a direction opposite to a pressing direction of the first pressing means with a force of the first pressing means, and a first for stopping the slide seat at a predetermined position against a reaction force of the elastic member. A stopper portion, and a second portion for stopping the slide seat at a predetermined position against the pressing force of the first and the first pressing means, with the slide seat against the reaction force of the elastic member. Stopper part A third stopper portion for stopping the slide seat at a predetermined position between the first and second stopper portions against the reaction force of the elastic member. It can respond to capacity control.

Further, by arranging a plurality of seat stoppers, a stopper portion for determining the position of the slide seat is firstly provided.
Since a plurality of components are provided between the second stopper portions, it is possible to cope with multi-stage capacity control.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a linear compressor according to a first embodiment of the present invention.

FIG. 2 is a schematic diagram showing an operation of the first embodiment of the present invention.

FIG. 3 is a schematic diagram showing the operation of the first embodiment of the present invention.

FIG. 4 is a longitudinal sectional view of a linear compressor according to a second embodiment of the present invention.

FIG. 5 is a schematic diagram showing the operation of the second embodiment of the present invention.

FIG. 6 is an explanatory diagram when performing multi-stage control of a linear compressor according to a third embodiment of the present invention.

FIG. 7 is a longitudinal sectional view showing a conventional linear compressor.

FIG. 8 is a schematic diagram showing the configuration of a conventional linear compressor according to the type of motor.

FIG. 9 is a schematic diagram for explaining capacity control based on head movement and neutral point movement.

FIG. 10 is a sectional view showing a capacity control mechanism of a conventional linear compressor.

[Explanation of symbols]

1 magnet, 2 coils, 3, 3a, 3b resonance spring,
4 pistons, 7 cylinders, 14 slide seats, 2
2, 22a guide member, 22b seat stopper, 24
a, 24b leaf spring, 25 stay holder, 25a
Stopper member, 25b Seat stopper, 45a First seat stopper, 45b Second seat stopper.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yoshiaki Yamazaki 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Masaya Inoue 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Rishi Electric Co., Ltd.

Claims (14)

[Claims] An elastic member for elastically supporting a cylinder or a piston fitted in the cylinder, which is reciprocally driven at a constant resonance frequency by a linear motor; and an elastic member which supports the elastic member and is movable in the reciprocating drive direction. A slide seat, pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and the slide seat being determined in advance against the reaction force of the elastic member. A linear compressor comprising: a first stopper that stops at a position; and a second stopper that stops the slide seat at a predetermined position against the pressing force of the pressing means. 2. When the position of the slide seat is determined by the first stopper portion, the amplitude of the reciprocating drive becomes maximum,
2. The linear compressor according to claim 1, wherein the amplitude is minimized when determined by the second stopper portion. 3. When the position of the slide seat is determined by the first stopper portion, the amplitude of the reciprocating drive is minimized,
2. The linear compressor according to claim 1, wherein the amplitude is maximized when determined by the second stopper portion. 4. The pressing by the pressing means acting on the slide seat and the seat stopper is turned on / off by an external operation.
2. The linear compressor according to claim 1, wherein the linear compressor is capable of performing F. 5. The linear compressor according to claim 4, wherein the pressing means switches between high pressure and low pressure. 6. The linear compressor according to claim 1, wherein the amount of initial deformation of the elastic member when the elastic member stops is equal to or more than １ ／ of the stroke at that time. 7. The linear compressor according to claim 1, wherein a coil spring is used as the elastic member. 8. The linear compressor according to claim 1, wherein the elastic members are arranged separately on both sides of the mover, and a slide seat is attached to one of the elastic members and pressed. 9. The linear compressor according to claim 8, wherein the two elastic members have the same elastic modulus. 10. The linear compressor according to claim 8, wherein the two elastic members have different elastic coefficients. 11. When the position of the slide seat is determined by the second stopper portion, the amount of deformation of the elastic member having the larger elastic coefficient at the time of stopping is equal to or more than の of the stroke at that time. The linear compressor according to claim 10, wherein: 12. A cylinder reciprocatingly driven at a constant resonance frequency by a linear motor or an elastic member elastically supporting a piston inserted in the cylinder, and supporting the elastic member and movable in the reciprocating driving direction. A slide seat, first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force of the slide seat equal to or greater than the pressing force of the first pressing means. A second pressing means for pressing the slide seat in a direction opposite to the pressing direction of the first pressing means, and a first stopper for stopping the slide seat at a predetermined position against a reaction force of the elastic member. A second stopper portion for stopping the slide seat at a predetermined position against the pressing force of the first pressing means; and a second stopper portion for stopping the sliding seat against the pressing force of the second pressing means. hand, A linear compressor, comprising: a third stopper portion that stops at a predetermined position between the first and second stopper portions. 13. A reciprocating cylinder driven by a linear motor at a constant resonance frequency or an elastic member for elastically supporting a piston inserted in the cylinder; and an elastic member for supporting the elastic member and movable in the reciprocating driving direction. A slide seat, first pressing means for pressing the slide seat in a direction opposite to the reaction force with a force equal to or greater than a reaction force generated in the elastic member, and a pressing force of the slide seat equal to or greater than the pressing force of the first pressing means. A second pressing means for pressing the slide seat in a direction opposite to the pressing direction of the first pressing means, and a first stopper for stopping the slide seat at a predetermined position against a reaction force of the elastic member. A second stopper portion that stops the slide seat at a predetermined position against the pressing force of the first pressing means, and the slide seat against a reaction force of the elastic member. The above 1. A linear compressor, comprising: a third stopper portion which stops at a predetermined position between the second stopper portions. 14. The seat stopper according to claim 12, wherein a plurality of seat stoppers are disposed between the first and second stopper portions to determine a position of the slide seat. The described linear compressor.