JPH11173688A - Linear compressor and refrigeration equipment - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To sufficiently reduce whirling of a piston of a linear compressor. SOLUTION: A piston 4 is reciprocated with respect to a cylinder 3 by connecting a piston shaft 4a of a piston 4 to a mover 2a of a linear motor 2 via a flange 4b. , And flexure springs 5 and 6.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a linear compressor and a refrigerating apparatus, and more particularly, to a cylinder, a piston, a linear motor for reciprocating the piston, a cylinder and a piston in a compressor casing. The present invention relates to a linear compressor including a refrigerant flow path for introducing a refrigerant into a compression chamber and discharging a refrigerant from the compression chamber, and a refrigeration apparatus using the linear compressor.

[0002]

2. Description of the Related Art Various types of compressors such as a reciprocating compressor, a rotary compressor, and a scroll compressor have been proposed or provided. Among these, reciprocating compressors can be broadly classified into those using a rotary motor as a drive source and those using a linear motor as a drive source. The latter configuration is called a linear compressor.

[0003] In this linear compressor, the seal portion and the sliding portion are basically only the outer periphery of the piston, and the leakage of the refrigerant is small and the friction loss is small. Therefore, the efficiency of the linear motor is the same as that of the rotary motor. If it is on the order, there is an advantage that the volume efficiency and the mechanical efficiency are high as compared with a ratio-pro compressor using a rotary motor as a drive source. FIG.
3 is a longitudinal sectional view showing the configuration of a conventional linear compressor.

In this linear compressor, a linear motor is provided at a predetermined position inside a compressor casing, and a cylinder is provided at a predetermined position remote from the linear motor. Then, the piston is reciprocated by connecting the piston located inside the cylinder to the mover of the linear motor. Further, a spring is provided between the mover of the linear motor and the compressor casing. Furthermore, a suction pipe for sucking refrigerant is provided at a predetermined position of the compressor casing, and a discharge pipe for discharging high-pressure refrigerant from a compression chamber formed by a cylinder and a piston is provided. A valve for discharging the refrigerant is provided between the compression chamber and the discharge pipe, a valve for suctioning the refrigerant is provided at a predetermined position of the piston, and a valve for suctioning the refrigerant passing through the wall of the cylinder and the piston. A coolant channel is provided.

The operation of the linear compressor having the above configuration is as follows. By operating the linear motor to retract the piston (by moving the piston in a direction to increase the volume of the compression chamber), the internal pressure of the compression chamber decreases,
Refrigerant is sucked into the compression chamber through the suction pipe and the refrigerant flow path.
During this time, the valve for discharging the refrigerant is closed.

Next, when the piston is moved in the reverse direction, the volume of the compression chamber is reduced, and the refrigerant is compressed accordingly. Then, at the end of the movement of the piston in this direction, the high pressure refrigerant is discharged through the discharge pipe by opening the valve for discharging the refrigerant. The valve for sucking the refrigerant does not need to be specially controlled, and the open state and the closed state are automatically controlled by the refrigerant pressure in the compression chamber.

[0007]

In the linear compressor shown in FIG. 13, when whirling occurs in the circumferential direction when the piston reciprocates, leakage of the refrigerant increases,
There is a disadvantage that the compression efficiency of the refrigerant is reduced. In addition, the piston and the cylinder come into contact with each other due to the whirling, so that the mechanical loss increases and the reliability decreases.

Therefore, in the linear compressor, it is required that the whirling of the piston be as small as possible, and in order to satisfy this requirement, the rigidity in the circumferential direction is high.
It is conceivable to use two flexure springs to support the piston. However, even when this configuration is adopted, the whirling of the piston cannot be sufficiently reduced, and therefore, the disadvantage that the compression efficiency of the refrigerant decreases, the mechanical loss increases, and the reliability increases. However, the inconvenience of the decrease in the temperature cannot be sufficiently solved.

[0009]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and it is possible to sufficiently reduce the whirling of a piston, and to maintain a high compression efficiency of a refrigerant. An object of the present invention is to provide a linear compressor capable of reducing loss and improving reliability, and a refrigeration apparatus using the linear compressor.

[0010]

According to a first aspect of the present invention, there is provided a linear compressor in which flexure springs for supporting a piston in a reciprocating manner are provided at a plurality of predetermined positions of the piston. In the linear compressor according to claim 2, a part of the flexure spring is provided at a predetermined position on a side away from the cylinder with respect to a connecting portion between the linear motor and the piston, and the rest of the flexure spring is connected to the linear motor. It is provided at a predetermined position on the side closer to the cylinder with respect to the connection portion with the piston.

According to a third aspect of the present invention, the part of the flexure spring is provided between the compressor casing and the piston, and the remaining flexure spring is also provided between the compressor casing and the piston. It is a thing. According to a fourth aspect of the present invention, the part of the flexure spring is provided between the compressor casing and the piston, and the remaining flexure spring is provided between the cylinder and the piston.

According to a fifth aspect of the present invention, in the linear compressor, all of the flexure springs are provided at predetermined positions on the side closer to the cylinder with respect to a connecting portion between the linear motor and the piston. In the linear compressor according to a sixth aspect, the flexure spring is provided between a compressor casing and a piston. In the linear compressor according to a seventh aspect, the flexure spring is provided between a cylinder and a piston.

In the linear compressor according to the present invention, all of the flexure springs are provided at predetermined positions on the side away from the cylinder with respect to the connection between the linear motor and the piston. In a linear compressor according to a ninth aspect, the flexure spring is provided to assist a compression stroke of the piston.

According to a tenth aspect of the present invention, a plurality of throttle elements are formed on at least one of an outer peripheral surface of the piston and an inner peripheral surface of the cylinder. The linear compressor according to the eleventh aspect is configured such that the inside of the casing excluding the compression chamber has a suction pressure, and the refrigerant passes through the linear motor and is sucked into the compression chamber.

According to a twelfth aspect of the present invention, the refrigerant is sucked into the compression chamber through the interior of the piston. A refrigeration apparatus according to a thirteenth aspect includes the linear compressor according to the tenth aspect, which employs at least one of a gas containing no carbon atom, carbon dioxide, nitrogen oxide, a hydrocarbon, ethylene, and ethane as a refrigerant.

[0016]

According to the linear compressor of the first aspect, the piston is reciprocated by the linear motor so that the refrigerant is introduced into the compression chamber formed by the cylinder and the piston, and the refrigerant is discharged from the compression chamber. In this case, since the flexure springs for supporting the piston so as to be able to reciprocate are provided at a plurality of preset positions of the piston, the whirling of the piston can be sufficiently reduced, and the compression efficiency of the refrigerant can be maintained high. And mechanical loss can be reduced, and reliability can be improved.

In the linear compressor according to the present invention, a part of the flexure spring is provided at a predetermined position on a side away from the cylinder with respect to a connecting portion between the linear motor and the piston, and a remaining portion of the flexure spring is provided. Is provided at a predetermined position close to the cylinder with respect to the connecting portion between the linear motor and the piston, so that the distance between the mounting position of a part of the flexure spring and the rest of the flexure spring should be sufficiently large. Thus, the whirling of the piston can be further reduced.

According to a third aspect of the present invention, the part of the flexure spring is provided between the compressor casing and the piston, and the remaining flexure spring is also provided between the compressor casing and the piston. Since it is provided, the same operation as the second aspect can be achieved. Claim 4
In the case of a linear compressor, the part of the flexure spring is provided between the compressor casing and the piston, and the remaining flexure spring is provided between the cylinder and the piston. The same operation as that of No. 2 can be achieved.

In the linear compressor according to the fifth aspect, since all of the flexure springs are provided at predetermined positions on the side closer to the cylinder with respect to the connecting portion between the linear motor and the piston, This is suitable when the shaft is sufficiently long, and the same operation as in claim 1 can be achieved. According to the linear compressor of claim 6, since the flexure spring is provided between the compressor casing and the piston, it is suitable when the cylinder is not too long. Can be achieved.

According to the linear compressor of claim 7, since the flexure spring is provided between the cylinder and the piston, it is suitable when the cylinder is long.
The same operation as the fifth aspect can be achieved. In the case of the linear compressor according to claim 8, since all of the flexure springs are provided at predetermined positions on the side away from the cylinder with reference to the connection between the linear motor and the piston, on the side remote from the cylinder. This is suitable when the piston shaft is sufficiently long, and the same operation as that of claim 1 can be achieved.

According to the ninth aspect of the present invention, since the flexure spring is provided to assist the compression stroke of the piston, the maximum work of the linear motor can be reduced and the efficiency can be further increased. In addition to achieving cost reduction, the same operation as any one of claims 1 to 8 can be achieved. According to the linear compressor of the tenth aspect, since a plurality of throttle elements are formed on at least one of the outer peripheral surface of the piston and the inner peripheral surface of the cylinder, the whirling of the piston is significantly reduced. In addition to being able to respond to oilless with a simple configuration, the same operation as any one of claims 1 to 9 can be achieved.

In the linear compressor according to the eleventh aspect, since the inside of the casing excluding the compression chamber is at the suction pressure, and the refrigerant is sucked into the compression chamber through the linear motor, the linear motor A permanent magnet having a low heat-resistant temperature can be adopted as a permanent magnet incorporated in the linear compressor, so that the cost of the entire linear compressor can be reduced, and the same operation as any one of the first to tenth aspects can be achieved.

According to the twelfth aspect of the present invention, since the refrigerant is sucked into the compression chamber through the interior of the piston, the refrigerant suction pressure loss can be reduced and the efficiency can be further improved. Claims 1 to 10
The same operation as any of the above can be achieved. According to the refrigeration apparatus of claim 13, a gas containing no carbon atom, carbon dioxide,
Since the linear compressor according to the tenth aspect employs at least one of nitrogen oxide, hydrocarbon, ethylene, and ethane as the refrigerant, the degree of freedom in selecting the refrigerant can be increased.

[0024]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a linear compressor according to the present invention will be described in detail with reference to the accompanying drawings. FIG. 1 is a longitudinal sectional view showing one embodiment of the linear compressor of the present invention. In this linear compressor, a linear motor 2 is provided at a predetermined position inside a casing 1, and a cylinder 3 is provided concentrically with the linear motor 2. A piston 4 is provided in the cylinder 3 so as to be able to reciprocate, and a large-diameter flange 4b provided at the center of the piston shaft 4a is connected to the movable element 2a of the linear motor 2. In the piston shaft 4a, a first flexure spring 5 is provided on the piston 4 side with respect to the flange 4b, and a second flexure spring 6 is provided on a side away from the piston 4 with respect to the flange 4b. Also, the piston shaft 4
a and the piston 4 have through holes 4c penetrating in the axial direction.
A suction valve 4d for closing the through hole 4c and a spring 4e for urging the suction valve 4d to open the through hole 4c are provided at the tip of the piston 4. Further, on a support member 3a for supporting the cylinder 3 with respect to the casing 1, there is provided a discharge spare space 3b communicating with the internal space of the cylinder 3, and the discharge spare space 3b is provided with the internal space of the cylinder 3 and And a spring 3d for urging the discharge valve 3c to maintain the communication state. Furthermore, a discharge pipe 7 for discharging the refrigerant from the preliminary discharge space 3b is provided, and the refrigerant is sucked into a predetermined position on a surface of the casing 1 where the discharge pipe 7 is provided in a penetrating state. Suction pipe 8 is provided. Reference numeral 4f is a seal member for maintaining airtightness between the cylinder 3 and the piston 4. The space surrounded by the cylinder 3, the piston 4, and the support member 3a is a compression chamber 9 for compressing the refrigerant.

The linear motor 2 reciprocates the mover 2a in the direction of the central axis, and its structure and control device are well known in the art. FIG. 3 is a plan view showing the configuration of the flexure spring 5. The flexure spring 5 is mounted between a predetermined position of the piston shaft 4a and an end face of the cylinder 3, and is disposed at a predetermined position of a disk made of stainless steel (for example, SUS301) from the center to the outer periphery. A plurality of elongated holes 5a are formed in a substantially spiral shape toward the portion. In addition, both ends of each long hole 5a are made to extend substantially in the radial direction in order to reduce stress concentration. And
A hole 5b for inserting the piston shaft 4a is formed in the center, and a bolt hole 5c for achieving connection to the piston shaft 4a via a mounting member (not shown).
Is formed. Further, a bolt hole 5d for achieving connection to the end face of the cylinder 3 is also formed in the outer peripheral portion.

The flexure spring 6 is connected to the piston shaft 4.
It is mounted between a predetermined position of a and a predetermined position of the casing 1. Therefore, although the size (outer diameter) is different from that of the flexure spring 5, the basic configuration is the same, and detailed description is omitted. Furthermore, the two flexure springs 5 and 6 are deformed when the piston 4 is separated from the support member 3a (non-compressed state of the refrigerant) and deformed when the piston 4 is closest to the support member 3a (compressed state of the refrigerant). Is applied so as to assist the movement of the piston 4 in the process of compressing the refrigerant. The mounting positions of the two flexure springs 5 and 6 are as follows, assuming that the distance between the top dead center and the flexure spring 5 is 11 and the distance between the top dead center and the flexure spring 6 is 12
It is preferable to set l1 / l2 <1/2.

The operation of the linear compressor having the above configuration is as follows. FIG. 1 shows a state where the piston 4 is at the bottom dead center, and the volume of the compression chamber 9 is the largest. In this state, the refrigerant in the non-compressed state is stored in the compression chamber 9 and the discharge valve 3c is set in the preliminary discharge space 3b.
And the compression chamber 9 are disconnected from each other.

In this state, by operating the linear motor 2 to move the piston 4 toward the top dead center, the pressure of the refrigerant in the compression chamber 9 increases, and the suction valve 4d
Closes the through hole 4c and makes the compression chamber 9 a closed space. Thereafter, the refrigerant is compressed by moving the piston 4 toward the top dead center. In this process, since the restoring force of the flexure springs 5 and 6 acts on the piston shaft 4a, the refrigerant can be compressed with a larger force than the driving force of the linear motor 2.

When the piston 4 reaches the top dead center, the pressure of the refrigerant in the compression chamber 9 reaches a maximum value, and the discharge valve 3c is moved against the spring 3d by this pressure (see FIG. 2). The refrigerant having the maximum pressure can be discharged through the preliminary discharge space 3b and the discharge pipe 7. After the refrigerant is discharged through the discharge pipe 7, the linear motor 2 is operated to move the piston 4 toward the bottom dead center. In this case, first, the discharge valve 3c is moved backward by the spring 3d, so that the communication between the preliminary discharge space 3b and the compression chamber 9 is cut off, and the spring 4e
The suction valve 4d opens the through hole 4c, and thereafter, as the volume of the compression chamber 9 increases, the refrigerant passes through the suction pipe 8, the gap between the linear motor 2 and the like, and through the through hole 4c of the piston 4 and the piston shaft 4a. Inhalation. And piston 4
Reaches the bottom dead center, the refrigerant suction stroke ends. In this refrigerant suction stroke, a low-pressure, low-temperature refrigerant is introduced into the compression chamber 9 through a gap or the like in the linear motor 2, so that the linear motor 2 can be cooled. Further, since the linear motor 2 can be cooled by the refrigerant, a permanent magnet having a low heat-resistant temperature can be used as the permanent magnet incorporated in the linear motor 2. Since the cost of the permanent magnet having a low heat-resistant temperature is low, the cost of the linear compressor as a whole can be reduced.

Thereafter, by repeating the above series of operations, the suction stroke of the refrigerant, the compression stroke of the sucked refrigerant, and the discharge stroke of the high-pressure refrigerant can be repeated. When repeating the above-described series of operations, the piston shaft 4
Since a is elastically supported by the flexure springs 5 and 6, and the flexure springs 5 and 6 have a remarkably high circumferential elastic coefficient, the whirling of the piston 4 can be greatly reduced. As a result, the compression efficiency of the refrigerant can be kept high, the mechanical loss can be reduced, and the reliability can be improved. In particular, when l1 / l2 <1/2, the interval between the mounting positions of the flexure springs 5 and 6 can be made sufficiently large, so that a sufficient whirling effect can be achieved. Further, although the flexure springs 5 and 6 have a low elastic modulus in the axial direction, since the thickness is thin, a plurality of flexure springs can be stacked without being excessively large. The elastic modulus can be increased.

FIG. 4 is a longitudinal sectional view showing another embodiment of the linear compressor of the present invention. This linear compressor is shown in FIG.
The difference from the linear compressor of FIG. 2 is that instead of providing the flexure spring 5 between the piston shaft 4a and the cylinder 3,
It is only a point provided between the piston shaft 4a and the casing 1. When this embodiment is adopted, the length of the flexure spring 5 that can be displaced in the axial direction can be increased due to the large diameter of the flexure spring 5.
The same operation as the linear compressor of FIGS. 1 and 2 can be achieved.

FIG. 5 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention. This linear compressor differs from the linear compressors of FIGS. 1 and 2 in that the flexure spring 6 is provided between the piston shaft 4a and the cylinder 3 instead of being provided between the piston shaft 4a and the casing 1. , And the springs 5, 6 are provided between the piston shaft 4 a and the cylinder 3 so that the cylinder 3 is
Side and the piston 4 rather than the flange 4b
The only difference is that the piston shaft 4a on the side away from the piston shaft is omitted.

When this embodiment is adopted, both the flexure springs 5 and 6 may be provided on the piston shaft 4a closer to the piston 4 than the flange 4b.
Can be shortened, the size of the linear compressor can be reduced as a whole, and the same operation as the linear compressor of FIGS. 1 and 2 can be achieved. FIG. 6 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

This linear compressor differs from the linear compressor of FIG. 5 in that the flexure springs 5, 6 are provided between the piston shaft 4a and the casing 1 instead of being provided between the piston shaft 4a and the cylinder 3. It is only a point. In the case of adopting this embodiment, the axial distance between the cylinder 3 and the linear motor 2 must be set large so as to allow the mounting of the flexure springs 5 and 6, and therefore, compared with the linear compressor of FIG. In addition, the same operation as the linear compressor of FIG. 5 can be achieved.

FIG. 7 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention. This linear compressor is different from the linear compressor of FIG.
6 is a piston shaft 4a closer to the piston 4 than the flange 4b.
Is provided only on the piston shaft 4a on the side farther from the piston 4 than the flange 4b. When this embodiment is adopted, the axial distance between the cylinder 3 and the linear motor 2 does not need to be set large enough to allow the mounting of the flexure springs 5 and 6, but the piston 3 is farther from the piston 4 than the flange 4b. Since the side piston shaft 4a needs to be set to a certain length, the size can be substantially the same as that of the linear compressor of FIG. 6, and the same operation as that of the linear compressor of FIG. 6 can be achieved.

FIG. 8 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention. This linear compressor differs from the linear compressor of FIG. 5 in that the piston shaft 4a is extended to a side farther from the piston 4 than the flange 4b, and that the piston shaft 4a and the casing are further away from the piston 4 than the flange 4b. 1 only in that a flexure spring 6 is provided.

When this embodiment is adopted, the number of locations supported by the flexure spring is increased, so that the whirling of the piston 4 can be further reduced, and the same operation as the linear compressor of FIG. 5 is achieved. be able to. In addition, in the embodiment of FIG. 8, the number of mounting locations of the flexure springs can be four or more, and in the other embodiments, the number of mounting locations of the flexure springs can be three or more.

FIG. 9 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention. The difference between this linear compressor and the linear compressor shown in FIGS.
The only difference is that instead of providing the through hole 4c for a refrigerant suction in a, the refrigerant suction passages 3e and 4g penetrating the wall of the cylinder 3 and the predetermined position of the piston 4 are provided. In addition, the formation positions of the refrigerant suction passages 3e and 4g may be any predetermined positions closer to the flange 4b than the seal member 4f.

When this embodiment is adopted, it is not necessary to form the through-hole 4c in the long piston shaft 4a, so that the structure can be simplified, and the refrigerant is supplied to the refrigerant suction passages 3e, 4g. The suction pressure loss of the refrigerant can be reduced as compared with the case where the refrigerant is sucked through the gap of the linear motor 2, the piston 4, and the through hole 4c of the piston shaft 4a. 1, Fig. 2
The same operation as that of the linear compressor can be achieved.

FIG. 10 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention. This linear compressor differs from the linear compressor of FIGS. 1 and 2 in that a plurality of throttle elements 4 are provided on the outer peripheral surface of the piston 4 instead of the seal member 4f.
Only the point where h was formed. When this embodiment is adopted, it is possible to cope with oil-less operation with a simple structure, in combination with a remarkable reduction in whirling of the piston 4 (any refrigerant such as natural refrigerant can be adopted). In addition, the same operation as the linear compressor of FIGS. 1 and 2 can be achieved. Specifically, refrigerants that do not contain carbon atoms, carbon dioxide, nitric oxide,
Examples thereof include hydrocarbon, ethylene, and ethane.

As shown in FIG. 11, the stop element 4h
Is provided on the outer peripheral surface of the piston 4 instead of the throttle element 3f.
Can be provided on the inner surface of the cylinder 3, and the throttle element 4 h can be provided on the outer peripheral surface of the piston 4, and the throttle element 3 f can be provided on the inner surface of the cylinder 3, as shown in FIG.

[0042]

According to the first aspect of the present invention, the whirling of the piston can be sufficiently reduced, the compression efficiency of the refrigerant can be maintained high, and the mechanical loss can be reduced. This has a specific effect that the reliability can be improved.

According to the second aspect of the present invention, the distance between the mounting position of a part of the flexure spring and the rest of the flexure spring can be made sufficiently large, and the whirling of the piston can be further reduced. It works. The third aspect of the invention has the same effect as the second aspect. The invention of claim 4 has the same effect as that of claim 2.

The invention of claim 5 is suitable when the piston shaft on the cylinder side is sufficiently long, and has the same effect as that of claim 1. The invention of claim 6 is suitable when the cylinder is not too long, and has the same effect as that of claim 5. The invention of claim 7 is suitable when the cylinder is long, and has the same effect as that of claim 5.

The invention of claim 8 is suitable when the piston shaft on the side remote from the cylinder is sufficiently long, and has the same effect as that of claim 1. According to the ninth aspect of the present invention, the maximum work of the linear motor can be reduced, the efficiency can be increased, the cost can be reduced, and the same effects as those of the first to eighth aspects can be obtained.

According to the tenth aspect of the present invention, in addition to the remarkable reduction of the whirling of the piston, it is possible to cope with the oilless operation with a simple structure. It works. According to the eleventh aspect of the present invention, a permanent magnet incorporated in a linear motor having a low heat-resistant temperature can be adopted, so that the cost of the entire linear compressor can be reduced. The same effect as any one is obtained.

According to the twelfth aspect, the refrigerant suction pressure loss can be reduced, the efficiency can be further improved, and the same effect as any one of the first to tenth aspects can be obtained. The invention of claim 13 has a unique effect that the degree of freedom in selecting a refrigerant can be increased.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a refrigerant uncompressed state of an embodiment of a linear compressor according to the present invention.

FIG. 2 is a vertical cross-sectional view showing a compressed state of the refrigerant of the linear compressor of FIG.

FIG. 3 is a plan view showing a configuration of a flexure spring.

FIG. 4 is a longitudinal sectional view showing another embodiment of the linear compressor of the present invention.

FIG. 5 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 6 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 7 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 8 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 9 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 10 is a longitudinal sectional view showing still another embodiment of the linear compressor of the present invention.

FIG. 11 is a longitudinal sectional view showing another example of the relationship between the piston and the cylinder.

FIG. 12 is a vertical sectional view showing still another example of the relationship between the piston and the cylinder.

FIG. 13 is a longitudinal sectional view showing a conventional linear compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing 2 Linear motor 3 Cylinder 3f, 4h Throttle element 4 Piston 4a Piston shaft 4b Flange 5, 6 Flexure spring 7 Discharge pipe 8 Suction pipe 9 Compression chamber

Claims (13)

[Claims] 1. A cylinder (3), a piston (4), a linear motor (2) for reciprocating the piston (4), a cylinder (3) and a piston (4) in a compressor casing (1). A refrigerant flow path (7) for introducing refrigerant into the compression chamber (9) formed by the above and discharging refrigerant from the compression chamber (9)
(8), the flexure springs (5) and (6) for reciprocatingly supporting the pistons (4) and (4a) are provided at predetermined positions of the pistons (4) and (4a). A linear compressor characterized by being provided. 2. A part of the flexure springs (5) and (6) that is apart from the cylinder (3) with respect to a connection (4b) between the linear motor (2) and the pistons (4) and (4a). And said flexure spring (5)
The rest of (6) is the linear motor (2) and piston (4)
2. The linear compressor according to claim 1, wherein the linear compressor is provided at a predetermined position close to the cylinder (3) with respect to a connection portion (4 b) with the (4 a). 3. The partial flexure spring (6) is provided between the compressor casing (1) and the piston (4a), and the remaining flexure spring (5) is also provided on the compressor casing (1). The linear compressor according to claim 2, which is provided between the piston and the piston (4a). 4. A part of the flexure spring (6) is provided between a compressor casing (1) and a piston (4a), and the remaining part of the flexure spring (5) is a cylinder (3) and a piston (4). The linear compressor according to claim 2, wherein the linear compressor is provided between the linear compressor and (4a). 5. All the flexure springs (5) (6)
2. The linear compressor according to claim 1, wherein the first compressor is provided at a predetermined position on the side closer to the cylinder (3) with respect to a connection portion (4 b) between the linear motor (2) and the pistons (4), (4 a). 6. The linear compressor according to claim 5, wherein the flexure springs (5) (6) are provided between the compressor casing (1) and the piston (4a). 7. The linear compressor according to claim 5, wherein the flexure springs (5) and (6) are provided between the cylinder (3) and the piston (4a). 8. All the flexure springs (5) (6).
2. The linear compressor according to claim 1, wherein the compressor is provided at a predetermined position on a side away from the cylinder (3) with respect to a connection portion (4 b) between the linear motor (2) and the pistons (4) (4 a). . 9. The linear compressor according to claim 1, wherein the flexure springs (5) and (6) are provided to assist a compression stroke of the pistons (4) and (4a). . 10. The throttle element according to claim 1, wherein a plurality of throttle elements (3f) (4h) are formed on at least one of an outer peripheral surface of the piston (4) and an inner peripheral surface of the cylinder (3). The linear compressor according to any one of the above. 11. A casing (1) excluding a compression chamber (9).
Inside is suction pressure and refrigerant is linear motor (2)
The linear compressor according to any one of claims 1 to 10, wherein the linear compressor is configured to be sucked into the compression chamber (9) through the compressor. 12. The system according to claim 1, wherein the refrigerant is drawn into the compression chamber through the interior of the piston.
The linear compressor according to any one of claims 1 to 10. 13. A refrigerating apparatus comprising the linear compressor according to claim 10, wherein at least one of a gas containing no carbon atom, carbon dioxide, nitric oxide, hydrocarbon, ethylene, and ethane is used as a refrigerant.