KR100814595B1 - Rotary compressor - Google Patents

Abstract

The piston 22 is disposed inside the cylinder chambers C1 and C2 of the cylinder 21, and the cylinder 21 and the piston 22 are configured to perform relatively eccentric rotational movement. In a rotary compressor having a compression mechanism 20 in which C1 and C2 are divided into a high pressure chamber and a low pressure chamber by a blade 23, in order to prevent vibration or noise from occurring due to pressure pulsations generated in a suction stroke. In the casing 10, a low pressure space S1 communicating with the suction side of the compression mechanism 20 and a high pressure space S2 communicating with the discharge side of the compression mechanism 20 are formed. And a suction pipe 14 communicating with the low pressure space S1 and a discharge tube 15 communicating with the high pressure space S2.

Cylinder, cylinder chamber, piston, compression mechanism, casing, high pressure space, low pressure space

Description

Rotary compressors {ROTARY COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly, to a rotary compressor having a compression mechanism configured to allow the piston and the piston to be relatively eccentrically rotated, while the piston is eccentrically housed in the annular cylinder chamber of the cylinder. .

BACKGROUND ART Conventionally, as a rotary compressor of this kind, there is a compressor configured to compress a refrigerant by changing a cylinder chamber volume when an annular piston makes an eccentric rotational movement in an annular cylinder chamber (see Patent Document 1, for example). . As shown to FIG. 11 and FIG. 12 (XII-XII sectional drawing of FIG. 11: hatching is abbreviate | omitted), in this compressor 100, in the hermetic casing 110, the compression mechanism 120 and this compression mechanism 120 are shown. An electric motor (not shown) for driving the engine is housed.

The compression mechanism 120 includes a cylinder 121 having annular cylinder chambers C1 and C2, and an annular piston 122 disposed in the cylinder chambers C1 and C2. The cylinder 121 includes an outer cylinder 124 and an inner cylinder 125 disposed on concentric circles with each other, and the cylinder chambers C1 and C2 are disposed between the outer cylinder 124 and the inner cylinder 125. Is formed.

The cylinder 121 is fixed to the casing 110. In addition, the annular piston 122 is connected to the eccentric portion 133a of the drive shaft 133 connected to the motor via a circular piston base 160 so as to perform an eccentric rotational movement about the center of the drive shaft 133. It is composed.

In the annular piston 122, one point of the outer circumferential surface is substantially in contact with the inner circumferential surface of the outer cylinder 124 ("substantially abuts", strictly speaking, there is a minute gap such that an oil film is formed, but in the gap) At the same time, it is configured to perform an eccentric rotational movement while maintaining a state where one point of the inner circumferential surface is substantially in contact with the outer circumferential surface of the inner cylinder 125 at a position different from that of the refrigerant. . As a result, the outer cylinder chamber C1 is formed outside the annular piston 122, and the inner cylinder chamber C2 is formed inside.

An outer blade 123A is disposed outside the annular piston 122, and an inner blade 123B is disposed on an extension line of the outer blade 123A inside. The outer blade 123A is pushed inward in the radial direction of the annular piston 122, and the inner circumferential end thereof is pressed against the outer circumferential surface of the annular piston 122. In addition, the inner blade 123B is pushed outward in the radial direction of the annular piston 122, and the outer peripheral end thereof is pressed against the inner peripheral surface of the annular piston 122.

The outer blade 123A partitions the outer cylinder chamber C1 into two, and the inner blade 123B partitions the inner cylinder chamber C2 into two. Specifically, the outer blade 123A partitions the outer cylinder chamber C1 into a low pressure chamber C1-Lp and a high pressure chamber C1-Hp, and the inner blade 123B defines the inner cylinder chamber C2. It is divided into low pressure chamber (C2-Lp) and high pressure chamber (C2-Hp). In the outer cylinder 124, a suction port 141 communicating with the outer cylinder chamber C1 from the suction pipe 114 provided in the casing 110 is formed near the outer blade 123A. In addition, a through hole 143 is formed in the annular piston 122 in the vicinity of the suction port 141, and the low pressure chamber of the outer cylinder chamber C1 and the inner cylinder chamber C2 is formed by the through hole 143. (C1-Lp, C2-Lp) are in communication with each other. In addition, the compressor port 120, the discharge port (not shown) for communicating the high pressure chamber (C1-Hp, C2-Hp) of the two cylinder chamber (C1, C2) to the high pressure space (S) in the casing 110 Is formed.

In this example, since only the eccentric rotational movement (orbital movement) is allowed while preventing the rotational movement of the annular piston 122, the Oldham mechanism 161 is mounted as the rotational movement blocking mechanism.

In the compression mechanism 120, when the annular piston 122 eccentrically rotates as the drive shaft 133 rotates, the volume of the volume is increased in the outer cylinder chamber C1 and the inner cylinder chamber C2, respectively. The reduction is repeated alternately. And when the volume of each cylinder chamber C1, C2 expands, the suction stroke which sucks a refrigerant from the inlet port 141 into cylinder chamber C1, C2 is made, and when a volume is reduced, a refrigerant | coolant is carried out in each cylinder chamber. A compression stroke for compressing in (C1, C2) and a discharge stroke for discharging the refrigerant from each cylinder chamber (C1, C2) through the discharge port into the high pressure space (S) in the casing (110). The high pressure refrigerant discharged into the high pressure space S of the casing 110 flows out to the condenser of the refrigerant circuit through the discharge pipe 115 provided in the casing 110.

On the other hand, the said patent document 1 also discloses the example which changed part of the structure of FIG. 12 as shown in FIG. In this compression mechanism 120, the annular piston 122 is partly divided into a C-shape, and one blade 123 intersects this part and the inner circumferential surface of the outer cylinder 124 and the inner cylinder 125 are formed. Abuts the outer circumference of the As for the inner peripheral surface of the outer cylinder 124, the part which the said blade 123 contacts is formed with the same radius of curvature as the outer peripheral surface of the inner cylinder 125. As shown in FIG. Moreover, the Oldham mechanism (not shown) is attached so that the annular piston 122 may have an eccentric rotational movement (orbital movement) around the inner cylinder 125 but does not rotate. By the eccentric rotation of the annular piston 122, the suction stroke, the compression stroke, and the discharge stroke of the refrigerant are made in the same manner as in the examples of FIGS. 11 and 12.

Patent Document 1 Japanese Patent Application Laid-Open No. 6-288358

[Initiation of invention]

[Problem to Solve Invention]

However, in the conventional structure shown in FIGS. 11-13, since the suction pipe is directly connected to the low pressure chambers C1-Lp and C2-Lp of the cylinder chambers C1 and C2, in each cylinder chamber C1 and C2, Pressure pulsation occurring in the suction stroke is propagated through the suction pipe into the refrigerant circuit system. As a result, there is a problem that the equipment and piping of the refrigerant circuit vibrate or noise occurs.

The present invention was devised in view of the above problems, and an object thereof is that the annular piston is disposed inside the annular cylinder chamber of the cylinder, and the cylinder and the annular piston are configured to perform relatively eccentric rotational movement. In addition, in the rotary compressor having a compression mechanism in which the cylinder chamber is divided into a high pressure chamber and a low pressure chamber by a blade, vibration and noise are prevented from occurring due to pressure pulsations generated in the suction stroke.

[Means for solving the problem]

According to the present invention, the pressure pulsation generated in the suction stroke is disposed through the suction pipe by arranging the low pressure space S1 in the casing 10, which is a buffer space when suction gas is sucked into the compression mechanism 20. It is to prevent propagation in the system of the refrigerant circuit.

Specifically, the first invention includes a cylinder 21 having cylinder chambers C1 and C2 and C, and a piston 22 which is eccentric with respect to the cylinder 21 and stored in the cylinder chambers C1 and C2 and C. ) And the cylinder chambers C1 and C2 and C, and the cylinder chambers C1 and C2 and C are replaced by the high pressure chambers C1-Hp and C2-Hp (C-Hp) and the low pressure chamber ( Compressor 20 having a blade 23 partitioned into C1-Lp, C2-Lp) (C-Lp), in which cylinder 21 and piston 22 perform relatively eccentric rotational movement, It assumes the rotary compressor provided with the electric motor 30 which drives the 20, and the casing 10 which accommodates this compression mechanism 20 and the electric motor 30.

The rotary compressor has a low pressure space S1 communicating with the suction side of the compression mechanism 20 and a high pressure space S2 communicating with the discharge side of the compression mechanism 20 in the casing 10. The casing 10 is characterized in that the suction pipe 14 connected to the low pressure space S1 side and the discharge pipe 15 connected to the high pressure space S2 side are provided.

In this first invention, the suction gas flows from the suction pipe 14 into the low pressure space S1 in the casing 10 and is then sucked into the compression mechanism 20. The gas sucked into the compression mechanism 20 is compressed by this compression mechanism 20, becomes a high pressure, flows out into the high pressure space S2 in the casing 10, and is discharged from the discharge pipe 15.
Moreover, in the 1st invention, the outer periphery of the compression mechanism 20 is surrounded by the low pressure space S1, and the said compression mechanism 20 has the housings 16 and 17 and the cover plate 18 of this compression mechanism 20. Discharge spaces 49 and 49A formed between the plurality of discharge spaces, discharge ports 45 and 46 which communicate with the discharge spaces 49 and 49A through the housings 16 and 17 of the compression mechanism 20, A discharge passage 49a for communicating the discharge spaces 49 and 49A to the high pressure spaces S2, 49B and S2 is formed, and the entire discharge passage 49a penetrates the housings 16 and 17. Characterized in that.
In the first invention, since the outer periphery of the compression mechanism 20 is surrounded by the low pressure space S1, the ambient temperature of the compression mechanism 20 is low, and the suction gas is contained in the high pressure space S2. It can be prevented from being influenced by the discharge gas.
According to a second aspect of the invention, in the rotary compressor of the first aspect, two spaces are formed in the casing (10) via the compression mechanism (20), one of which is a low pressure space (S1) and the other of a high pressure space ( S2).

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In this second invention, the suction gas passing through the suction pipe 14 flows into the low pressure space S1 partitioned in the casing 10 by the compression mechanism 20, and then is sucked into the compression mechanism 20. High pressure. Further, the high pressure gas flows out into the high pressure space S2 formed on the opposite side to the low pressure space S1 with the compression mechanism 20 interposed therebetween, and then discharged from the discharge tube 15.

According to a third aspect of the invention, in the rotary compressor of the first aspect of the invention, the electric motor 30 is disposed in the high pressure space S2.

In this third invention, the discharge gas discharged from the compression mechanism 20 flows around the electric motor 30 when passing through the high pressure space S2, and is discharged from the discharge tube 15.

In the fourth invention, in the rotary compressor of the first invention, a high pressure space S2 is formed below the compression mechanism 30, and an oil pan 19 for storing lubricating oil is formed in the high pressure space S2. It is characterized by.

In this fourth invention, the lubricating oil is stored in the high pressure space S2 filled with the discharge gas from the compression mechanism 20, so that the high pressure pressure of the discharge gas acts on the lubricating oil.

According to a sixth aspect of the invention, in the rotary compressor of the first aspect of the invention, the axially perpendicular cross-sectional shapes of the cylinder chambers C1 and C2 are formed in an annular shape, and the piston 22 is disposed in the cylinder chambers C1 and C2. It is characterized by consisting of the annular piston 22 which divides the cylinder chambers C1 and C2 into the outer cylinder chamber C1 and the inner cylinder chamber C2. The "axis right angle cross section" here means the cross section perpendicular | vertical to a drive shaft (rotation center).

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In this sixth invention, the compression mechanism 20 in which the annular piston 22 is eccentrically stored in the annular cylinder chambers C1 and C2, and the outer cylinder chamber C1 and the inner cylinder chamber C2 are partitioned. In the rotary compressor provided with the suction gas, the suction gas flows into the low pressure space S1 in the casing 10 from the suction pipe 14, and then is sucked into the compression mechanism 20. The gas sucked into the compression mechanism 20 is compressed by this compression mechanism 20, becomes a high pressure, flows out into the high pressure space S2 in the casing 10, and is discharged from the discharge pipe 15.

According to a seventh aspect of the present invention, in the rotary compressor of the sixth invention, the blade (23) is integrally formed with the cylinder (21), and the connecting member for connecting the annular piston (22) and the blade (23) to each other in a movable manner ( 27, wherein the connecting member 27 has a first sliding surface P1 for the annular piston 22 and a second sliding surface P2 for the blade 23. do.

In this seventh invention, when the compression mechanism 20 is driven, the cylinder 21 and the annular piston 22 perform relatively eccentric rotation. In the eccentric rotational movement, the annular piston 22 and the blade 23 are relatively rocked at a predetermined swing center and relatively advanced in the plane direction of the blade 23. The gas is sucked into the cylinder chambers C1 and C2 when the volumes of the cylinder chambers C1 and C2 expand, and the gas is compressed when the volume of the cylinder chambers C1 and C2 decreases.

Here, in the conventional configuration shown in FIGS. 11 and 12, the blades 123A and 123B and the annular piston 122 make line contact, and in the configuration shown in FIG. 13, the blade 123 and the cylinders 124 and 125 are in line contact. Since the linear contact makes a linear contact, the load received by the contact portion is large when the annular piston 122 performs the eccentric rotation movement during operation, and the contact portion may be worn or a scissor may be generated.

Moreover, in the structure of FIGS. 11-13, since the member makes linear contact with each other in this way, the sealing property of a contact part is low, and the high pressure chamber C1-Hp, in each of the outer cylinder chamber C1 and the inner cylinder chamber C2 is carried out. The gas may leak from C2-Hp) into the low pressure chambers C1-Lp and C2-Lp, which may lower the compression efficiency.

However, in the present invention, when the blade 23 and the annular piston 22 perform the operation (relative rocking motion and the forward and backward motion) via the heat connecting member 27, the connecting member 27 is an annular piston ( Since both surface 22 and the blade 23 are substantially in surface contact with the sliding surfaces P1 and P2, the load acting on the contact portion is small, and wear and contact of the contact portion are less likely to occur. Moreover, since the members make surface contact with each other on the sliding surfaces P1 and P2 in this way, gas leakage from the contact portion can be prevented as compared with a compressor having a line contact structure as in Patent Document 1.

8th invention is the rotary compressor of 7th invention WHEREIN: The annular piston 22 is formed in C shape which the part of circular ring was divided, and the blade 23 has the annular cylinder chambers C1 and C2. From the inner circumferential wall surface to the outer circumferential wall surface of the annular piston (22), the dividing portion of the annular piston (22) is inserted and extended, and the connecting member (27) holds the blade (23) in advance and retreat. ) And an oscillating bush 27 having an arcuate outer circumferential surface which is freely swingable at a divided portion in the annular piston 22.

In this eighth invention, when the compression mechanism 20 is driven, the blade 23 retreats while making surface contact with the blade groove 28 of the swing bush 27, and the swing bush 27 is an annular piston 22. Rotate while making surface contact with the divided part of). In this way, the connecting member 27 can reliably contact the ring-shaped piston 22 and the blade 23 with each other, and can reliably prevent gas leakage from the contact portion.

In the rotary compressor of the sixth invention, the rotary compressor of the sixth invention includes a drive shaft (33) for driving the compression mechanism (20), and the drive shaft (33) is provided with an eccentric portion (33a) eccentrically at the center of rotation, The eccentric part 33a is connected to the cylinder 21 or the annular piston 22, and both axial side parts of the eccentric part 33a of the drive shaft 33 are provided through the casing part 16a, 17a. It is characterized in that it is maintained in 10).

In this ninth invention, the drive shaft 33 for driving the compression mechanism 20 is held in the casing 10 via the bearing portions 16a, 17a at both axial sides of the eccentric portion 33a. As it rotates, the operation of the compression mechanism 20 is stabilized.

10th invention is the rotary compressor of 1st invention WHEREIN: The cylinder right angle cross section shape of the cylinder chamber C is formed circularly, and the piston 22 is the circular piston 22 arrange | positioned in the said cylinder chamber C. It is characterized in that the configuration.

In the tenth aspect of the present invention, in the rotary compressor including the compression mechanism (20) in which the circular piston (22) is eccentrically stored in the circular cylinder chamber (C), the suction gas is supplied from the suction pipe (14) to the casing (10). After flowing into the low pressure space (S1) therein, it is sucked into the compression mechanism (20). The gas sucked into the compression mechanism 20 is compressed by this compression mechanism 20, becomes a high pressure, flows out into the high pressure space S2 in the casing 10, and is discharged from the discharge pipe 15.

[Effects of the Invention]

According to the first invention, in the casing 10, a low pressure space S1 communicating with the suction side of the compression mechanism 20 and a high pressure space S2 communicating with the discharge side of the compression mechanism 20 are formed. In the casing 10, a suction pipe 14 connected to the low pressure space S1 side and a discharge pipe 15 connected to the high pressure space S2 side are provided. As a result, the suction pipe 14 is opened to the low pressure space S1 without directly connecting the suction pipe 14 to the suction side of the compression mechanism 20. Therefore, the low pressure space S1 receives the suction gas from the compression mechanism ( 20) becomes a buffer space for inhalation. Therefore, since the pressure pulsation generated in the suction stroke in the cylinder chambers C1, C2 and C of the compression mechanism 20 does not propagate in the refrigerant circuit system through the suction pipe 14, the equipment of the refrigerant circuit or It is possible to prevent the pipe from vibrating or generating noise.

Further, the discharge gas passes through the high pressure space S2 and is discharged from the discharge tube 15. Therefore, since the heat of the discharge gas is not transmitted to the suction side, it is possible to prevent performance degradation due to suction overheat loss. In addition, since the discharge gas is discharged from the discharge pipe 15 after the discharge gas is filled in the high pressure space S2, the pulsation of the discharge pressure can also be avoided affecting the discharge pipe.

Even if the liquid refrigerant is mixed with the low pressure gas sucked into the compressor, the liquid refrigerant and the gas can be separated from the low pressure space, so that only the gas can be sucked into the compression mechanism 20. Therefore, the liquid compression can be prevented depending on the suction structure. In this way, damage to the compression mechanism 20 can be avoided.
In addition, since the outer circumference of the compression mechanism 20 is surrounded by the low pressure space S1, the ambient temperature of the compression mechanism 20 is low, and the suction gas is discharged from the hot discharge gas contained in the high pressure space S2. It can be affected to prevent overheating.

According to the second invention, two spaces are formed in the casing 10 with the compression mechanism 20 interposed therebetween, so that one side is a low pressure space S1 and the other is a high pressure space S2. As a result, the low pressure space S1 and the high pressure space S2 can be formed. Therefore, the structure of the compressor 1 is not complicated, and enlargement can also be prevented.

According to the third invention, the electric motor 30 is disposed in the high pressure space S2. As a result, since the discharge gas from the compression mechanism 20 flows around the electric motor 30, the suction gas to the compression mechanism 20 does not flow around the electric motor 30. Therefore, since the suction gas is not heated by the electric motor 30, performance deterioration due to suction overheat loss can be reliably prevented.

According to the fourth aspect of the present invention, the high pressure space S2 is formed below the compression mechanism 30, and the oil pan 19 is formed in the high pressure space S2, so that the lubricating oil is compressed using the high pressure pressure of the discharge gas. It can supply to the sliding part of 20. Therefore, the oil supply structure can be simplified.

According to the sixth invention, the compression mechanism (20) in which the annular piston (22) is eccentrically stored in the annular cylinder chambers (C1, C2), and the outer cylinder chamber (C1) and the inner cylinder chamber (C2) are partitioned. In the rotary compressor provided with), it is possible to prevent pressure pulsation on the suction side and pressure pulsation on the discharge side, and to prevent performance deterioration due to suction overheat loss.

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According to the seventh aspect of the invention, when the compression mechanism 20 is operated, the connecting member 27 makes substantial surface contact with the annular piston 22 and the blade 23 at the sliding surfaces P1 and P2. As compared with the structure of linear contact as in Patent Document 1, the load per unit area acting on the contact portion can be reduced. Therefore, when the blade 23 and the annular piston 22 slides through the connecting member 27 during operation, the contact portion wears out, or it is difficult to cause scissor generation. In addition, the connecting member 27 is in surface contact with the annular piston 22 and the blade 23 at the sliding surfaces P1 and P2, whereby the first chamber C1-Hp and C2-Hp and the second chamber C1 It is also possible to prevent gas leakage between -Lp and C2-Lp).

According to the eighth aspect of the present invention, as the connecting member 27, a blade groove 28 for holding the blade 23 in a retractable manner, and an arc-shaped outer circumference that is freely held at the divided portion by the annular piston 22 By using the swinging bushing 27 having a surface, it is possible to reliably prevent gas leakage during operation, wear of members and scissor generation, and also to prevent the structure of the connecting portion from becoming complicated. As a result, the enlargement of the mechanism and the increase of atoms can be prevented.

According to the ninth aspect of the invention, the drive shaft 33 for driving the compression mechanism 20 is held in the casing 10 via the bearing portions 16a, 17a at both axial sides of the eccentric portion 33a. By rotating at, the operation of the compression mechanism 20 is stabilized, so that the reliability of the mechanism 20 is improved.

According to the tenth aspect of the present invention, in the rotary compressor including the compression mechanism (20) in which the circular piston (22) is eccentrically housed in the circular cylinder chamber (C), it is possible to prevent the pressure pulsation on the suction side and the pressure pulsation on the discharge side. At the same time, it is possible to prevent performance degradation due to suction overheating loss.

1 is a longitudinal cross-sectional view of a rotary compressor according to the prior art of the present invention.

2 is a cross-sectional view showing the operation of the compression mechanism.

3 is a longitudinal sectional view of a rotary compressor according to a modification of the prior art.

4 is a longitudinal sectional view of the rotary compressor according to the first embodiment of the present invention.

5 is a longitudinal sectional view of a rotary compressor according to a modification of the first embodiment.

7 is a longitudinal sectional view of the rotary compressor according to the third embodiment.

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8 is a longitudinal sectional view of the rotary compressor according to the fourth embodiment.

9 is a cross-sectional view showing the operation of the rotary compression mechanism of FIG.

10 is a longitudinal sectional view of the rotary compressor according to the fifth embodiment.

11 is a partial longitudinal sectional view of a rotary compressor according to the prior art.

FIG. 12 is a sectional view taken along the line II-XIII of FIG. 11.

13 is a cross-sectional view illustrating a modification of FIG. 12.

[Description of the code]

1: compressor 10: casing

14: suction pipe 15: discharge pipe

16: upper housing 16a, 17a: bearing portion

17: lower housing 19: oil pan

20: compression mechanism 21: cylinder

22: annular piston (piston) 23: blade

24: outer cylinder 25: inner cylinder

26: mirror plate 27: connecting member (swinging bush)

28: blade groove 30: electric motor

33: drive shaft 33a: eccentric portion

C1: Cylinder chamber (outer cylinder chamber) C2: Cylinder chamber (inner cylinder chamber)

C1-Hp, C2-Hp: High pressure chamber (compression chamber) C1-Lp, C2-Lp: Low pressure chamber (suction chamber)

P1: 1st sliding surface P2: 2nd sliding surface

S1: low pressure space S2: high pressure space

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described in detail based on drawing.

[Prerequisites]

As shown in FIG. 1, in the compressor 1 of the present prior art, the compression mechanism 20 and the electric motor (drive mechanism) 30 are housed in the casing 10, and are configured in a fully sealed type. The compressor 1 is used, for example, in the refrigerant circuit of the air conditioner to compress the refrigerant sucked from the evaporator and discharge it to the condenser.

The casing 10 includes a cylindrical body portion 11, an upper mirror plate 12 fixed to an upper end portion of the body portion 11, and a lower mirror plate 13 fixed to a lower end portion of the body portion 11. It consists of. The suction tube 14 which penetrates this mirror plate 12 is provided in the upper mirror plate 12, and the discharge part 15 which penetrates this body part 11 is provided in the body part 11.

The compression mechanism 20 is configured between the upper housing 16 and the lower housing 17 fixed to the casing 10. The compression mechanism 20 includes a cylinder 21 having cylinder chambers C1 and C2 having an annular rectangular cross-sectional shape, an annular piston 22 disposed in the cylinder chambers C1 and C2, and FIG. Blade 23 dividing cylinder chambers C1 and C2 into high pressure chambers (compression chambers) (C1-Hp, C2-Hp) and low pressure chambers (suction chambers) (C1-Lp, C2-Lp), as shown in FIG. ). The cylinder 21 and the annular piston 22 are configured to have a relatively eccentric rotational movement. In this preliminary technique, the cylinder 21 having the cylinder chambers C1 and C2 is the movable side, and the annular piston 22 disposed in the cylinder chambers C1 and C2 is the fixed side.

The electric motor 30 includes a stator 31 and a rotor 32. The stator 31 is disposed below the compression mechanism 20 and is fixed to the body portion 11 of the casing 10. A drive shaft 33 is connected to the rotor 32, and the drive shaft 33 is configured to rotate together with the rotor 32. The drive shaft 33 penetrates the cylinder chambers C1 and C2 in the vertical direction.

An oil supply passage (not shown) in which the inside of the drive shaft 33 extends in the axial direction is formed in the drive shaft 33. In addition, an oil supply pump 34 is disposed at the lower end of the drive shaft 33. The oil supply passage extends upward from the oil supply pump 34 to the compression mechanism 20. By this structure, the lubricating oil which accumulates in the oil pan 19 of the high pressure space S2 mentioned later in the casing 10 is moved to this oil supply pump 34 through the oil supply passage, and the sliding part of the compression mechanism 20 is carried out. Supply until.

The eccentric part 33a is formed in the drive shaft 33 in the part located in the middle of cylinder chamber C1, C2. The eccentric part 33a is formed with a diameter larger than the upper and lower parts of this eccentric part 33a, and is eccentrically by a predetermined amount in the axial center of the drive shaft 33. As shown in FIG.

The cylinder 21 includes an outer cylinder 24 and an inner cylinder 25. The outer cylinder 24 and the inner cylinder 25 are integrated by connecting the lower end part with the mirror plate 26. The inner cylinder 25 slides freely on the eccentric portion 33a of the drive shaft 33.

The annular piston 22 is formed integrally with the upper housing 16. In addition, bearing portions 16a and 17a for supporting the drive shaft 33 are formed in the upper housing 16 and the lower housing 17, respectively. As described above, in the compressor 1 of the prior art, the drive shaft 33 penetrates the cylinder chambers C1 and C2 in the up and down direction, and both axial side portions of the eccentric portion 33a are bearing parts 16a and 17a. It is composed of a through shaft structure that is held in the casing (10) through.

The compression mechanism 20 has a swinging bush 27 as a connecting member for connecting the annular piston 22 and the blade 23 to each other in a movable manner. The annular piston 22 is formed in a C shape in which a portion of the circular ring is divided. The blade 23 is on the radial line of the cylinder chambers C1 and C2, and the outer circumferential wall surface (outer cylinder (from the outer circumferential surface of the inner cylinder 25)) of the cylinder chambers C1 and C2. 24), the dividing portion of the annular piston 22 is inserted and extended through the inner peripheral surface thereof, and is fixed to the outer cylinder 24 and the inner cylinder 25. The swing bush 27 connects the annular piston 22 and the blade 23 at the divided portion of the annular piston 22. Here, the blade 23 may be formed integrally with the outer cylinder 24 and the inner cylinder 25 as shown in FIG. 2, and may be formed integrally with the other cylinders 24 and 25.

The inner circumferential surface of the outer cylinder 24 and the outer circumferential surface of the inner cylinder 25 are cylindrical surfaces disposed on the same center, and the cylinder chambers C1 and C2 are formed therebetween. The annular piston 22 has a diameter whose outer peripheral surface is smaller than the inner peripheral surface of the outer cylinder 24 and whose inner peripheral surface is larger than the outer peripheral surface of the inner cylinder 25. As a result, an outer cylinder chamber C1 is formed between the outer circumferential surface of the annular piston 22 and the inner circumferential surface of the outer cylinder 24, and the inner circumferential surface of the annular piston 22 and the outer circumferential surface of the inner cylinder 25 are formed. The inner cylinder chamber C2 is formed between and.

In addition, the annular piston 22 and the cylinder 21 are in a state where the outer circumferential surface of the annular piston 22 and the inner circumferential surface of the outer cylinder 24 are substantially in contact with each other (strictly there are micron order gaps, In a state where the leakage of refrigerant in the gap is not a problem), the inner circumferential surface of the annular piston 22 and the outer circumferential surface of the inner cylinder 25 are substantially positioned at one point at a position where the contact and the phase are different from each other by 180 °. It is formed to contact with.

The swinging bush 27 has a discharge side bush 27A positioned at the high pressure chambers C1-Hp and C2-Hp with respect to the blade 23, and low pressure chambers C1-Lp and C2- with respect to the blade 23. It consists of the suction side bush 27B located in the Lp) side. The discharge-side bush 27A and the suction-side bush 27B are almost semicircular in cross-sectional shape, are formed in the same shape, and are disposed so that the flat surfaces face each other. The space between the opposing surfaces of both bushes 27A and 27B constitutes the blade groove 28.

The blade 23 is inserted into the blade groove 28 so that the flat surfaces of the swing bushes 27A and 27B (second sliding surface P2: see FIG. 2C) are substantially the same as the blade 23. In surface contact, an arcuate outer circumferential surface (first sliding surface) P1 is substantially in surface contact with the annular piston 22. The swinging bushes 27A and 27B are configured such that the blade 23 advances and retreats in the blade groove 28 in the plane direction while the blade 23 is fitted into the blade groove 28. At the same time, the oscillating bushes 27A and 27B are configured to oscillate integrally with the blade 23 with respect to the annular piston 22. Therefore, the swinging bush 27 has the center point of the swinging bush 27 as the swinging center so that the blade 23 and the annular piston 22 are relatively swingable, and the blade 23 is the annular piston. It is comprised so that it may be made to advance and retreat in the surface direction of this blade 23 with respect to (22).

In this preliminary technology, an example in which both bushes 27A and 27B are separately described has been described. However, both bushes 27A and 27B may be integrally formed by connecting them in part.

In the above configuration, when the drive shaft 33 rotates, the outer cylinder 24 and the inner cylinder 25 move around the center point of the swing bush 27 while the blade 23 moves in and out of the blade groove 28. Rocking. By this swinging motion, the contact point between the annular piston 22 and the cylinder 21 moves sequentially from (A) to (D) in FIG. 2. At this time, the outer cylinder 24 and the inner cylinder 25 is orbital movement around the center of rotation of the drive shaft 33, but does not rotate.

In the upper housing 16, a suction port 41 is formed at a position below the suction pipe 14. The suction port 41 is formed in a long hole shape from the inner cylinder chamber C2 to the suction space 42 formed in the outer circumference of the outer cylinder 24. The suction port 41 penetrates the upper housing 16 in the axial direction, and the low pressure chambers C1-Lp and C2-Lp and the suction space 42 and the upper housing 16 of the cylinder chambers C1 and C2. The upper space (low pressure space (S1)) of the () is communicated. In the outer cylinder 24, a light through hole 43 for communicating the suction space 42 and the low pressure chamber C1-Lp of the outer cylinder chamber C1 is formed, and the annular piston 22 has an outer side. An optical through hole 44 for communicating the low pressure chamber C1-Lp of the cylinder chamber C1 and the low pressure chamber C2-Lp of the inner cylinder chamber C2 is formed.

The outer cylinder 24 and the annular piston 22 are formed in a wedge shape by chamfering the upper end portion of the portion corresponding to the suction port 41. In this way, the refrigerant suction into the low pressure chambers C1-Lp and C2-Lp can be efficiently performed.

Discharge ports 45 and 46 are formed in the upper housing 16. These discharge ports 45 and 46 penetrate the upper housing 16 in the axial direction, respectively. The lower end of the discharge port 45 is opened to face the high pressure chamber C1-Hp of the outer cylinder chamber C1, and the lower end of the discharge hole 46 is located in the high pressure chamber C2-Hp of the inner cylinder chamber C2. Opening so as to. On the other hand, the upper ends of these discharge ports 45 and 46 communicate with the discharge space 49 via discharge valves (lead valves) 47 and 48 which open and close these discharge ports 45 and 46.

This discharge space 49 is formed between the upper housing 16 and the cover plate 18. In the upper housing 16 and the lower housing 17, a discharge passage 49a is formed which communicates from the discharge space 49 to the space (high pressure space) S2 below the lower housing 17.

Meanwhile, a seal ring 29 is formed in the lower housing 17. The seal ring 29 is loaded into the annular groove 17b of the lower housing 17 and pressed against the lower surface of the mirror plate 26 of the cylinder 21. Moreover, the high pressure lubricating oil is introduce | transduced into the radially inner part of the seal ring 29 at the contact surface of the cylinder 21 and the lower housing 17. As shown in FIG. In view of the above, the seal ring 29 uses the pressure of the lubricant to reduce the axial clearance between the lower end surface of the annular piston 22 and the mirror plate 26 of the cylinder 21. ) Configure the appliance.

[Operation operation]

Next, the operation of the compressor 1 will be described.

When the electric motor 30 is started, the rotation of the rotor 32 is transmitted to the outer cylinder 24 and the inner cylinder 25 of the compression mechanism 20 through the drive shaft 33. Then, the blade 23 reciprocates between the swinging bushes 27A and 27B (retraction), and the blade 23 and the swinging bushes 27A and 27B are integrated to form an annular piston 22. Oscillate motion At this time, the swing bushes 27A and 27B are substantially in surface contact with the annular piston 22 and the blade 23 at the sliding surfaces P1 and P2. And the outer cylinder 24 and the inner cylinder 25 oscillate with respect to the annular piston 22, and the compression mechanism 20 performs a predetermined | prescribed compression operation.

Specifically, in the outer cylinder chamber C1, the volume of the low pressure chamber C1-Lp is almost the minimum in the state of FIG. 2D. From here, the drive shaft 33 rotates in the right direction of the drawing, When the volume of this low pressure chamber C1-Lp increases as it changes to the state of (A), (B), (C), a refrigerant | coolant carries out the suction pipe 14, the low pressure space S1, and the suction port 41. Through the low pressure chamber (C1-Lp). At this time, the coolant is not only directly sucked from the suction port 41 into the low pressure chamber C1-Lp, but part of the refrigerant flows from the suction port 41 into the suction space 42 and therefrom, through the through hole 43. Inhaled at (C1-Lp).

When the drive shaft 33 is rotated once and is in the state of FIG. 2D again, the suction of the refrigerant into the low pressure chambers C1-Lp is completed. The low pressure chamber C1-Lp is then a high pressure chamber C1-Hp to which the refrigerant is compressed, and a new low pressure chamber C1-Lp is formed with the blade 23 interposed therebetween. When the drive shaft 33 rotates again, suction of the refrigerant is repeated in the low pressure chamber C1-Lp, while the volume of the high pressure chamber C1-Hp is reduced, so that the refrigerant is discharged in the high pressure chamber C1-Hp. Is compressed. When the pressure in the high pressure chamber C1-Hp reaches a predetermined value and the pressure difference between the discharge space 49 reaches the set value, the discharge valve 47 opens by the high pressure refrigerant in the high pressure chamber C1-Hp, The refrigerant flows out of the discharge space 49 through the discharge passage 49a into the high pressure space S2.

In the inner cylinder chamber C2, the volume of the low pressure chamber C2-Lp is almost the minimum in the state of FIG. 2B, from which the drive shaft 33 rotates in the right direction of the drawing, and When the volume of the low pressure chamber C2-Lp increases as the state changes to the state of (), (D), (A), the refrigerant passes through the suction pipe 14, the low pressure space S1 and the suction port 41. Inhaled into the low pressure chamber (C2-Lp). At this time, the refrigerant is not only directly sucked from the suction port 41 into the low pressure chamber C2-Lp, but part of the refrigerant flows from the suction port 41 into the suction space 42, from which the through hole 43 and the outer cylinder are located. The low pressure chamber C1-Lp of the yarn and the through hole 44 are sucked into the low pressure chamber C2-Lp of the inner cylinder chamber C2.

When the drive shaft 33 is rotated once and is brought into the state of FIG. 2B again, the suction of the refrigerant into the low pressure chamber C2-Lp is completed. The low pressure chamber C2-Lp next becomes a high pressure chamber C2-Hp in which the refrigerant is compressed, and a new low pressure chamber C2-Lp is formed with the blade 23 interposed therebetween. When the drive shaft 33 rotates again, suction of the refrigerant is repeated in the low pressure chamber C2-Lp, while the volume of the high pressure chamber C2-Hp is reduced, so that the refrigerant is discharged in the high pressure chamber C2-Hp. Is compressed. When the pressure in the high pressure chamber C2-Hp reaches a predetermined value and the differential pressure with the discharge space 49 reaches a set value, the discharge valve 48 opens by the high pressure refrigerant in the high pressure chamber C2-Hp, The refrigerant flows out of the discharge space 49 through the discharge passage 49a into the high pressure space S2.

In this way, the high pressure refrigerant compressed in the outer cylinder chamber C1 and the inner cylinder chamber C2 and discharged into the high pressure space S2 is discharged from the discharge tube 15, and the condensation stroke, expansion stroke, and evaporation in the refrigerant circuit are performed. After the stroke, it is sucked back into the compressor 1.

[Effect of premise technology]

In this preliminary technique, the suction pipe 14 is not directly connected to the low pressure chambers (suction chambers) C1-Lp and C2-Lp of the compression mechanism 20, but inside the suction pipe 14 in the low pressure space S1. Open the end. As a result, the low pressure space S1 becomes a buffer space when suction gas is sucked into the compression mechanism 20. Therefore, the pressure pulsation generated in the suction stroke in each of the cylinder chambers C1 and C2 does not propagate into the system of the refrigerant circuit through the suction pipe 14, so that the device or the pipe to the refrigerant 진동 vibrates or generates noise. Can be prevented. Also on the discharge side, since the discharge gas is discharged from the discharge tube 15 after filling the high pressure space S2, it is also possible to avoid the pressure pulsation on the discharge side affecting the discharge pipe.

In addition, since two spaces are formed in the casing 10 via the compression mechanism 20, one side is a low pressure space S1 and the other is a high pressure space S2. The high pressure space S2 may be formed. Therefore, the structure of the compressor 1 is not complicated, and enlargement can also be prevented.

Moreover, since the electric motor 30 is arrange | positioned in the high pressure space S2, what flows around the electric motor 30 is discharge gas from the compression mechanism 20, and the suction gas to the compression mechanism 20 is the periphery of the electric motor 30. Do not flow. As a result, since the suction gas is not heated by the electric motor 30, performance deterioration due to suction overheat loss does not occur. In addition, since the low pressure space S1 and the high pressure space S2 are separated with the compression mechanism 20 therebetween, the low pressure gas passage and the high pressure gas passage in the casing 10 are completely separated. Therefore, also in this respect, the performance degradation by suction overheating loss can be prevented.

In addition, the high pressure space S2 is formed below the compression mechanism 30, and the oil pan 19 is formed in this high pressure space S2, so that the lubricating oil is discharged using the high pressure pressure of the discharge gas. It can supply to a sliding part. Therefore, the oil supply structure can be simplified.

In addition, the drive shaft 33 for driving the compression mechanism 20 is rotated in the state held in the casing 10 via the bearing portions 16a, 17a at both axial sides of the eccentric portion 33a. Since the operation of the compression mechanism 20 is stabilized, the reliability of the mechanism 20 is improved.

In this preliminary technique, the swinging bush 27 is provided as a connecting member for connecting the annular piston 22 and the blade 23, and the swinging bush 27 is the annular piston 22 and the blade 23. In the case of the line contact, the annular piston 22 or the blade 23 is worn during operation, or a scissor is formed at the contact portion. It is possible to prevent such a problem, although it is thought that the occurrence or the like.

Further, by using the swinging bush 27 as the connecting member, the structure of the connecting portion can be prevented from being complicated, and therefore, the enlargement of the mechanism and the increase in cost can be prevented.

In addition, since the swing bush 27 is provided in this manner, the swing bush 27 and the annular piston 22 and the blade 23 are in surface contact with each other, so that the sealing portion of the contact portion is also excellent. As a result, in each of the outer cylinder chamber C1 and the inner cylinder chamber C2, the refrigerant leaks from the high pressure chambers C1-Hp and C2-Hp to the low pressure chambers C1-Lp and C2-Lp, thereby reducing the compression efficiency. It can also be prevented.

Moreover, according to the compressor 1 of this preliminary art, the phase difference between the torque fluctuation accompanying the compression operation in the outer cylinder chamber C1 and the torque fluctuation accompanying the compression operation in the inner cylinder chamber C2 is shifted by 180 degrees. The total torque curve amplitude is smaller than that of the single cylinder compressor. If the amplitude is large, vibration or noise of the compressor 1 becomes a problem, but this problem can also be prevented in the present prerequisite technique. In addition, since the structure is low in noise, no sound insulation material is required, and the cost reduction effect is also possible.

In addition, in the conventional two-cylinder type compressor (for example, see Japanese Patent Application Laid-Open No. 2000-161276) in which a compression mechanism is superimposed in two stages, for example, the configuration is complicated and the cost increases, but the compressor of this preliminary technique ( In 1), the two cylinder chambers C1 and C2 formed in one compression mechanism 20 can achieve the same capability as the two-cylinder type compressor, and can simplify the structure and reduce the cost. Can be.

According to the structure of this premise technique, when the liquid back occurs from the evaporator of the refrigerant circuit to the compressor 1 due to the change in the operating conditions, the high pressure chambers C1-Hp and C2-Hp of the cylinder chambers C1 and C2 When the high pressure rises abnormally, the cylinder 21 is displaced downward by deforming the seal ring 29. In this way, the liquid refrigerant can leak from the high pressure chambers C1-Hp and C2-Hp into the low pressure chambers C1-Lp and C2-Lp, and liquid compression can also be prevented. As a result, there is little possibility of the failure of the compression mechanism 20, and reliability improves.

According to this premise technique, since the blade 23 is formed integrally with the cylinder 21 and is held by the cylinder 21 at both ends thereof, abnormal concentrated load is applied to the blade 23 during operation, or stress concentration is performed. This is hard to happen. As a result, the sliding part is hardly lost, and in this respect, the reliability of the mechanism can be improved.

In addition, in the conventional compressors shown in Figs. 11 to 13, the Oldham mechanism is used as a rotation preventing mechanism for only rotating the eccentric rotation without rotating the annular piston 22. Connecting the annular piston 22 and the blade 23 via the through itself becomes the rotational movement blocking mechanism of the annular piston, and thus does not require a dedicated rotational movement blocking mechanism, thereby enabling a compact design.

[Variation of Premise Technology]

The modification of the said prior art is shown in FIG.

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This modification is an example in which the cylinder 21 is configured without using the mirror plate 26. Specifically, the cylinder 21 is the structure in which the outer cylinder 24, the inner cylinder 25, and the blade 23 were integrated. In this example, the seal ring 29 shown in FIG. 1 is not loaded.

In such a configuration, the configuration of the cylinder 21 can be further simplified, and the compression mechanism 20 can be downsized.

Since the other configurations, operations, and effects are the same as those of the premise technology, detailed description thereof will be omitted.

[First embodiment]

The 1st Embodiment of this invention is shown in FIG.

This 1st Embodiment is the example which changed the bonding structure of the trunk | drum 11 and the upper mirror plate 12 in the casing 10 from the example of FIG. In this example, the body portion 11 is formed to have a length at which the upper portion protrudes slightly above the lower housing 17 so that the lower housing 17 is welded to the body portion 11 by welding. In addition, the upper housing 16 is formed with a diameter smaller than the inner diameter of the upper mirror plate 12, it is fixed to the lower housing 17. The upper mirror plate 12 is welded to the upper end of the body portion 11 with respect to the body portion 11.

In this configuration, the joining portion of the body portion 11 and the lower housing 17 becomes a seal point. Therefore, the low pressure space S1 above the lower housing 17 becomes a space completely blocked from the high pressure space S2. In contrast, in the configuration of FIG. 1, since the lower housing 17 and the upper housing 16 are fitted into the body portion 11, the upper housing 16 is formed through a minute gap between the body portion 11 and the lower housing 17. There is a possibility of high pressure gas leaking around).

On the other hand, in the present embodiment, the junction between the body portion 11 and the lower housing 17 is a sealing point, and a space is formed between the upper mirror plate 12 and the upper housing 16. The outer circumference of the compression mechanism 20 is surrounded by the low pressure space S1. Therefore, since the hot discharge gas in the high pressure space S2 does not leak around the upper housing 16, it is possible to reliably prevent the suction gas from being overheated by the discharge gas.

[Modification]

5 shows a modification of the first embodiment.

This modification is an example in which the bonding structure of the body portion 11 and the upper mirror plate 12 in the casing 10 is changed from the example of FIG. 3. In this example, as in the modification of the above-described prior art, the body portion 11 has a length at which the upper end protrudes slightly above the lower housing 17, so that the lower housing 17 is welded to the body portion 11 by welding. Are bonded. In addition, the upper housing 16 is formed with a diameter smaller than the inner diameter of the upper mirror plate 12, it is fixed to the lower housing 17. The upper mirror plate 12 is welded to the body portion 11 at the upper end of the body portion 11.

In this configuration, the junction between the body portion 11 and the lower housing 17 is a sealing point. Therefore, the low pressure space S1 above the lower housing 17 becomes a space completely blocked from the high pressure space S2. In contrast, in the configuration of FIG. 3, since the lower housing 17 and the upper housing 16 are fitted into the body portion 11, the upper housing 16 is formed through a minute gap between the body portion 11 and the lower housing 17. There is a possibility of high pressure gas leaking around).

On the other hand, in the present modification, the junction between the body portion 11 and the lower housing 17 is a sealing point, and a space is formed between the upper mirror plate 12 and the upper housing 16. The outer circumference of the compression mechanism 20 is surrounded by the low pressure space S1. Therefore, since the hot discharge gas in the high pressure space S2 does not leak around the upper housing 16, it is possible to reliably prevent the suction gas from being overheated by the discharge gas.

[Third Embodiment]

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In the third embodiment of the present invention, the first and second embodiments have the annular piston 22 on the fixed side and the cylinder 21 on the movable side, whereas the cylinder 21 is on the fixed side. This is an example in which the piston 22 is set to the movable side.

In this 3rd Embodiment, as shown in FIG. 7, the compression mechanism 20 is comprised between the upper housing 16 and the lower housing 17 in the upper part in the casing 10 similarly to the said embodiment.

On the other hand, unlike the above embodiment, the outer cylinder 24 and the inner cylinder 25 are disposed in the upper housing 16. These outer cylinders 24 and inner cylinders 25 are integrated into the upper housing 16 to constitute the cylinder 21.

Between the upper housing 16 and the lower housing 17, an annular piston 22 is held. This annular piston 22 is integrated with the mirror plate 26. The mirror plate 26 is provided with a hub 26a which is freely fitted to the eccentric portion 33a of the drive shaft 33. Therefore, in this structure, when the drive shaft 33 rotates, the annular piston 22 performs eccentric rotation movement in the cylinder chambers C1 and C2. Moreover, the blade 23 is integrated in the cylinder 21 similarly to the said embodiment.

The upper housing 16 has a suction port 41 communicating with the outer cylinder chamber C1 and the inner cylinder chamber C2 from the low pressure space S1 above the compression mechanism 20 in the casing 10, and the outer cylinder chamber. The discharge port 45 of (C1) and the discharge port 46 of the inner cylinder chamber C2 are formed. In addition, a suction space 42 communicating with the suction port 41 is formed between the hub 26a and the inner cylinder 25. A through hole 44 is formed in the inner cylinder 25, and the annular piston 22 is formed. The through hole 43 is formed in the. Moreover, the fillet process is given to the upper end part of the annular piston 22 and the inner cylinder 25 at the part corresponding to the suction port 41. FIG.

A cover plate 18 is installed above the compression mechanism 20, and a discharge space 49 is formed between the upper housing 16 and the cover plate 18. The discharge space communicates with the high pressure space S2 below the compressor 20 through the discharge passage 49a formed in the upper housing 16 and the lower housing 17.

 In this third embodiment, as in the examples of FIGS. 4 and 5, the body portion 11 is formed to have a length at which the upper end protrudes slightly higher than the lower housing 17, so that the lower housing 17 is attached to the body portion 11. ) Is joined by welding. In addition, the upper housing 16 is formed with a diameter smaller than the inner diameter of the upper mirror plate 12, it is fixed to the lower housing 17. The upper mirror plate 12 is welded to the body portion 11 at the upper end of the body portion 11.

Also in this configuration, the joint portion between the body portion 11 and the lower housing 17 becomes a sealing point, so that the low pressure space S1 above the lower housing 17 is completely blocked from the high pressure space S2. And since the outer periphery of the compression mechanism 20 is surrounded by the low pressure space S1, the suction gas is not overheated by the high temperature discharge gas in the high pressure space S2.

Also in this 3rd Embodiment, like the said 1st Embodiment, the low pressure space S1 is not connected directly to the low pressure chamber (suction chamber) C1-Lp, C2-Lp of the compression mechanism 20. ) Is a buffer space when suction gas is sucked into the compression mechanism 20. Therefore, the pressure pulsation generated in the suction stroke in each of the cylinder chambers C1 and C2 does not propagate in the system of the refrigerant circuit through the suction pipe 14, so that the equipment or piping of the refrigerant circuit vibrates or generates noise. Can be prevented. Similarly, the pressure pulsation on the discharge side can be prevented in the same manner, and the performance deterioration due to suction overheat loss can also be prevented.

In addition, a swinging bush 27 is provided as a connecting member for connecting the annular piston 22 and the blade 23, so that the swinging bush 27 slides against the annular piston 22 and the blade 23. It is the same as that of the said embodiment comprised so that surface contact may be made in P1 and P2 substantially. Therefore, it is possible to prevent the annular piston 22 or the blade 23 from being worn during operation, or the occurrence of a scissor at the contact portion thereof.

Moreover, since the rocking bush 27, the annular piston 22, and the blade 23 make surface contact, the point which is excellent in the sealing property of a contact part is the same as that of the said embodiment. As a result, in each of the outer cylinder chamber C1 and the inner cylinder chamber C2, the refrigerant leaks from the high pressure chambers C1-Hp and C2-Hp to the low pressure chambers C1-Lp and C2-Lp, thereby reducing the compression efficiency. It can also be prevented.

In addition, the same effects as those of the above-described embodiments can be achieved, such as low vibration, low noise, and cost reduction due to a smaller total torque curve amplitude, and a structure simplification and prevention of liquid compression as compared with conventional two-cylinder compressors. Can be.

Fourth Embodiment

As shown in FIG. 8, the 4th Embodiment of this invention changes the compression mechanism 20 of the said 1st Embodiment, its modified example (FIG. 4, FIG. 5), and 3rd Embodiment (FIG. 7). to be.

Specifically, the examples of FIGS. 4, 5 and 7 accommodate the annular piston 22 in the eccentric state in the annular cylinder chambers C1 and C2, thereby storing the cylinder chambers C1 and C2 in the outer cylinder. In contrast to an example in which the chamber C1 and the inner cylinder chamber C2 are divided into two, the fourth embodiment of the present invention forms a circular cross-sectional shape of the cylinder chamber C in a circular shape, and the piston 22 ) Is composed of a circular piston 22 eccentrically housed in the cylinder chamber C, so that the cylinder chamber C is not divided into two inside and outside.

The compression mechanism 20 is configured between the lower housing 17 fixed to the casing 10 and the upper housing 16 fixed to the lower housing 17. The compression mechanism 20 includes a cylinder 21 having a cylinder chamber C having a circular axial right-angle cross-sectional shape, a circular piston 22 disposed in the cylinder chamber C, and a cylinder chamber C. A blade 23 partitioned into a high pressure chamber (compression chamber) (C-Hp) and a low pressure chamber (suction chamber) (C-Lp) is provided. In this fourth embodiment, the cylinder 21 having the cylinder chamber C is the fixed side, the piston 22 disposed in the cylinder chamber C is the movable side, and the piston 22 with respect to the cylinder 21. It is configured to make an eccentric rotational movement.

The eccentric part 33a is formed in the drive shaft 33 of the electric motor 30 in the part located in the cylinder chamber C. As shown in FIG. The eccentric part 33a is formed with a diameter larger than the upper and lower parts of this eccentric part 33a, and is eccentrically by a predetermined amount in the axial center of the drive shaft 33. As shown in FIG. The piston 22 is fitted to this eccentric portion 33a.

The cylinder 21 having the cylinder chamber C is formed in the upper housing 16. In the upper housing 16 and the lower housing 17, bearing portions 16a and 17a for supporting the drive shaft 33 are formed, respectively. Therefore, in the compressor 1 of this embodiment, the said drive shaft 33 penetrates the said cylinder chamber C in an up-down direction, and the axial direction both sides of the eccentric part 33a interpose through bearing parts 16a and 17a. And a through shaft structure held in the casing 10.

As shown in FIG. 9, in the compression mechanism 20 of this embodiment, the blade 23 is integrally formed in the piston 22, and this blade is hold | maintained via the swinging bush 27 in the cylinder 21. So-called swing type compression mechanism (20).

In the upper housing 16, a suction port 41 is formed at a position below the suction pipe 14. This suction port 41 penetrates through the upper housing 16 in the axial direction, and communicates the low pressure chamber C-Lp of the cylinder chamber C with the space above the upper housing 16 (low pressure space S1). Let's do it.

The discharge hole 45 is formed in the upper housing 16. This discharge port 45 penetrates the upper housing 16 in the axial direction. The lower end of the discharge port 45 is opened to face the high pressure chamber C-Hp of the cylinder chamber C. On the other hand, the upper end of this discharge port 45 is communicated with the discharge space 49 via the discharge valve (lead valve) 47 which opens and closes this discharge port 45. As shown in FIG.

This discharge space 49 is formed between the upper housing 16 and the cover plate 18. In the upper housing 16 and the lower housing 17, a discharge passage 49a is formed which communicates from the discharge space 49 to the space (high pressure space) S2 below the lower housing 17.

In this fourth embodiment, similarly to the examples of FIGS. 4, 5, and 7, the upper end of the body portion 11 is formed to have a length slightly projecting upwardly from the lower housing 17, so that the body portion 11 The lower housing 17 is joined by welding. In addition, the upper housing 16 is formed with a diameter smaller than the inner diameter of the upper mirror plate 12, it is fixed to the lower housing 17. The upper mirror plate 12 is welded to the body portion 11 at the upper end of the body portion 11.

Also in this configuration, the junction between the body portion 11 and the lower housing 17 becomes a sealing point, so that the low pressure space S1 above the lower housing 17 is completely blocked from the high pressure space S2. And since the outer periphery of the compression mechanism 20 is surrounded by the low pressure space S1, the suction gas is not overheated by the high temperature discharge gas in the high pressure space S2.

Also in this 4th embodiment, like the said 1st, 3rd embodiment, the low pressure space S1 is not connected directly to the low pressure chamber (suction chamber) C-Lp of the compression mechanism 20. Since the inner end of the suction pipe 14 is opened in the cavity), the low pressure space S1 serves as a buffer space when suction gas is sucked into the compression mechanism 20. Therefore, since the pressure pulsation generated in the suction stroke in the cylinder chamber C does not propagate in the refrigerant circuit system through the suction pipe 14, the equipment and piping of the refrigerant circuit are prevented from vibrating or generating noise. can do. Similarly, the pressure pulsation on the discharge side can be prevented in the same manner, and the performance deterioration due to suction overheat loss can also be prevented.

[Fifth Embodiment]

As shown in FIG. 10, 5th Embodiment of this invention is the example which comprised the compression mechanism of 4th Embodiment by superimposing in two stages.

In the figure, the lower housing 17 is welded to the body portion 11 of the casing 10. In the lower housing 17, the second cylinder 21B, the intermediate plate 21C, the first cylinder 21A, and the upper housing 16 are stacked in order from the bottom, and these members are fastened by bolts or the like. It is integrated by a member (not shown).

The first cylinder 21A and the second cylinder 21B each have a circular first cylinder chamber C1 and a second cylinder chamber C2. In the drive shaft 33, a first eccentric portion 33a is formed in a portion located in the first cylinder chamber C1, and a second eccentric portion 33b is formed in a portion located in the second cylinder chamber C2. do. The 2nd eccentric part 33b is eccentrically in the direction of 180 degrees with respect to the eccentric direction of the 1st eccentric part 33a.

The first piston 22A is fitted to the first eccentric part 33a, and the second piston 22B is fitted to the second eccentric part 33b. The 1st piston 22A is eccentrically accommodated in the 1st cylinder chamber C1, and the 2nd piston 22B is eccentrically accommodated in the 2nd cylinder chamber C2. The first cylinder chamber C1 is partitioned into a high pressure chamber and a low pressure chamber by a first blade (not shown), and the second cylinder chamber C2 is partitioned into a high pressure chamber and a low pressure chamber by a second blade (not shown). And when the drive shaft 33 rotates, the 1st piston 22A will make an eccentric rotation movement substantially contacting the inner peripheral surface of the 1st cylinder chamber C1 at one point, and the 2nd piston 22B will be a 1st cylinder The eccentric rotation is made while substantially contacting the inner peripheral surface of the seal C2 at one point.

The upper housing 16 is provided with a first suction port 41A communicating with the low pressure chamber of the first cylinder chamber C1, and the middle plate 21C has a second suction port communicating with the low pressure chamber of the second cylinder chamber C2. 41B is formed. The first suction port 41A and the second suction port 41B are communicated with each other by the first suction passage 41a formed in the second cylinder 21B. The first suction passage 41a communicates from the side surface to the low pressure chamber of the first cylinder chamber C1. In addition, a second suction passage 41b is formed in the second cylinder 21B so as to communicate from the side surface to the low pressure chamber of the second cylinder chamber C2 from the second suction port 41B.

The first discharge hole 45 is formed in the upper housing 16. This first discharge port 45 penetrates the upper housing 16 in the axial direction thereof. The lower end of the first discharge port 45 is opened to face the high pressure chamber of the first cylinder chamber C1. On the other hand, the upper end of the first discharge port 45 communicates with the first discharge space 49A via the first discharge valve (lead valve) 47 that opens and closes the first discharge port 45. The first discharge space 49A is formed between the upper housing 16 and the first cover plate 18A.

The second discharge hole 46 is formed in the lower housing 17. This second discharge port 46 penetrates through the lower housing 17 in the axial direction thereof. The upper end of the second discharge port 46 is opened to face the high pressure chamber of the second cylinder chamber C2. On the other hand, the lower end of the second discharge port 46 communicates with the second discharge space 49B via a second discharge valve (lead valve 48) that opens and closes the second discharge port 46. The second discharge space 49B is formed between the lower housing 17 and the second cover plate 18B.

In the upper housing 16, the first cylinder 21A, the intermediate plate 21C, the second cylinder 21B, and the lower housing 17, from the first discharge space 49A to the second discharge space 49B. The discharge passage 49a in communication is formed. The second discharge space 49B is a space continuous in the circumferential direction between the lower housing 17 and the second cover plate 18B, and through the opening 18a of the second cover plate 18B, the second discharge space 49B is provided. It communicates with the high pressure space below the cover plate 18B.

In this fifth embodiment, similarly to the examples of FIGS. 4, 5, 7, and 8, the upper end of the body portion 11 is formed to have a length that protrudes slightly higher than the lower housing 17, so that the body portion ( The lower housing 17 is welded to 11. In addition, the upper housing 16, the first cylinder 21A, the intermediate plate 21C, and the second cylinder 21B are formed to have a diameter smaller than the inner diameter of the upper mirror plate 12. Therefore, also in this structure, the junction part of the body part 11 and the lower housing 17 becomes a sealing point, and the low pressure space S1 above the lower housing 17 is completely interrupted from the high pressure space S2. And since the outer periphery of the compression mechanism 20 is surrounded by the low pressure space S1, the suction gas is not overheated by the high temperature discharge gas in the high pressure space S2.

Also in this fifth embodiment, the suction pipe 14 is not connected directly to the low pressure chamber (suction chamber) C-Lp of the compression mechanism 20 in the same manner as in the first, third, and fourth embodiments. Since the inner end of the suction pipe 14 is opened in the space S1, the low pressure space S1 serves as a buffer space when the suction gas is sucked into the compression mechanism 20. Therefore, since the pressure pulsation generated in the suction stroke in the cylinder chamber C does not propagate in the refrigerant circuit system through the suction pipe 14, the equipment and piping of the refrigerant circuit are prevented from vibrating or generating noise. can do. Similarly, the pressure pulsation on the discharge side can be prevented in the same manner, and the performance deterioration due to suction overheat loss can also be prevented.

Other Embodiments

This invention may be set as the following structures about the said embodiment.

In the first and third embodiments, the annular piston 22 is a C-shape in which a portion of the circular ring is divided, and the blade 23 inserts the divided portion through the annular piston 22. And the blade 23 are connected via the swinging bush 27, but the swinging bush 27 does not necessarily need to be installed.

That is, according to the present invention, the cylinder 21, the piston 22 disposed eccentrically and arranged in the cylinder chambers C1 and C2 of the cylinder 21, and the cylinder chambers C1 and C2 are the high pressure chambers C1-Hp. Compressor 20 having a blade 23 partitioned into a C2-Hp and a low pressure chamber (C1-Lp, C2-Lp), the cylinder 21 and the piston 22 is relatively eccentric rotational movement In the rotary compressor provided with a low pressure space S1 in the casing 10, and the low pressure space S1 is used as a buffer space for suction into the compression mechanism 20, other specific structures may be changed as appropriate. You may also

For example, in each said embodiment, although the blade 23 is arrange | positioned so that it may exist on the radial line of the cylinder chambers C1 and C2, the blade 23 will be arranged in the radial line segment of the cylinder chambers C1 and C2. It may be a slightly inclined arrangement.

And the above embodiments are essentially preferred examples and are not intended to limit the scope of the invention, its application, or its use.

As described above, in the present invention, the annular piston 22 is disposed inside the annular cylinder chambers C1 and C2 of the cylinder 21, and the cylinder 21 and the annular piston 22 are provided. The cylinder chambers C1 and C2 are configured to perform relatively eccentric rotational movements, and the cylinder chambers C1 and C2 are connected to the high pressure chambers C1-Hp and C2-Hp and the low pressure chambers C1-Lp and C2-Lp by the blades 23. It is useful for rotary compressors with compartmentalized compression mechanisms.

Claims (10)

A cylinder 21 having cylinder chambers C1, C2 and C, a piston 22 which is eccentric with respect to the cylinder 21 and housed in the cylinder chambers C1 and C2 and C, and the cylinder chamber ( It is arranged in C1, C2) and (C), and the cylinder chambers C1 and C2 and C are replaced with high pressure chambers C1-Hp and C2-Hp (C-Hp) and low pressure chambers C1-Lp and C2-Lp. Compressor 20 having a blade 23 partitioned by C-Lp, the cylinder 21 and the piston 22 is relatively eccentric rotational movement, An electric motor 30 for driving the compression mechanism 20; A rotary compressor provided with a casing 10 for storing the compression mechanism 20 and the electric motor 30, In the casing 10, a low pressure space S1 communicating with the suction side of the compression mechanism 20 and a high pressure space S2 communicating with the discharge side of the compression mechanism 20 are formed. The casing 10 is provided with a suction pipe 14 connected to the low pressure space S1 and a discharge pipe 15 connected to the high pressure space S2. The outer circumference of the compression mechanism 20 is surrounded by the low pressure space (S1), The compression mechanism 20 includes discharge spaces 49 and 49A formed between the housings 16 and 17 and the cover plate 18 of the compression mechanism 20 and the housing 16 of the compression mechanism 20. , The outlets 45 and 46 communicating with the discharge spaces 49 and 49A, and the discharge spaces 49 and 49A communicate with the high pressure spaces S2, 49B and S2. And a discharge passage (49a) is formed, and the entire discharge passage (49a) passes through the housing (16, 17). The casing (10) according to claim 1, wherein two casings are formed in the casing (10) via the compression mechanism (20), one of which is a low pressure space (S1) and the other of which is a high pressure space (S2). compressor. The rotary compressor according to claim 1, wherein the electric motor (30) is disposed in the high pressure space (S2). The rotary compressor according to claim 1, wherein a high pressure space (S2) is formed below the compression mechanism (30), and an oil pan (19) for storing lubricating oil is formed in the high pressure space (S2). delete The cylinder chambers C1 and C2 have an annular cross-sectional shape at right angles, and have an annular shape. The piston 22 is composed of an annular piston 22 disposed in the cylinder chambers C1 and C2 and partitioning the cylinder chambers C1 and C2 into an outer cylinder chamber C1 and an inner cylinder chamber C2. Rotary compressor, characterized in that. The method of claim 6, wherein the blade 23 is formed integrally with the cylinder 21, And a connecting member 27 for connecting the annular piston 22 and the blade 23 to each other in a movable manner, The connecting member (27) is a rotary compressor, characterized in that it comprises a first sliding surface (P1) for the annular piston (22), and a second sliding surface (P2) for the blade (23). 8. The annular piston (22) according to claim 7, wherein the annular piston (22) is formed in a C shape with a portion of a circular ring segmented, The blade 23 is configured to extend through the dividing portion of the annular piston 22 from the inner circumferential wall surface of the annular cylinder chambers C1 and C2 to the outer circumferential wall surface. The connecting member 27 is a swing bush 27 having a blade groove 28 for holding the blade 23 in a retractable manner, and an arcuate outer circumferential surface that is freely swingable at a divided portion in the annular piston 22. Rotary compressor characterized in that)). 7. A driving shaft (33) for driving the compression mechanism (20) according to claim 6, The drive shaft 33 has an eccentric portion 33a eccentric at the center of rotation, which eccentric portion 33a is connected to the cylinder 21 or the annular piston 22, The drive shaft (33) is a rotary compressor, characterized in that the axially opposite sides of the eccentric portion (33a) are held in the casing (10) via the bearing portions (16a, 17a). The cylinder chamber (C) is formed in a circular axis cross-sectional shape is circular, The piston (22) is a rotary compressor, characterized in that consisting of a circular piston (22) disposed in the cylinder chamber (C).

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