JP2014034940A - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of preventing separation of a coil spring even when a split vane is displaced in a sliding direction, by reducing a surface pressure of a sliding portion of a tip of the split vane and a roller, and suppressing increase in costs, and to provide a refrigeration cycle device including the rotary compressor.SOLUTION: A motor portion and a compressing mechanism portion connected with the motor portion through a rotating shaft, are accommodated in a sealed case, the compressing mechanism portion includes: a cylinder having a cylinder chamber; a roller eccentrically moved in the cylinder chamber; a vane kept into contact with the roller and dividing the cylinder chamber into a compression side and a suction side; and a coil spring elastically pressing the vane so that it is brought into contact with the roller. The vane is configured by stacking two sheets of split vanes in a height direction of the cylinder, two sheets of split vanes are pressed by one coil spring, the coil spring has two turns or more of close contact parts with the split vanes, and each of the split vanes includes: a coil spring mounting groove composed of a tapered portion longitudinally disposed from an end edge; and a parallel portion in parallel with a close contact portion of the coil spring.

Description

  Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle apparatus including the rotary compressor and constituting a refrigeration cycle circuit.

  A refrigeration cycle apparatus equipped with a rotary compressor is frequently used. In this type of rotary compressor, an electric motor part and a compression mechanism part are connected via a rotating shaft. The compression mechanism section includes a cylinder that forms a cylinder chamber in the inner diameter portion, a roller that moves eccentrically in the cylinder chamber, and a vane that abuts against the roller and divides the cylinder chamber into a compression side and a suction side.

  Conventionally, as shown in FIG. 8A, one vane is provided for one roller, and the tip of the vane is in sliding contact with the roller peripheral wall. The pressing force (load) F of the vane against the roller is expressed by the following equation (1).

F = {Pd * (L1 + L2)-(Pm * L1 + Ps * L2)} * H (1)
Pd: Pressure inside the sealed case (= discharge pressure), L1: Projection length on the suction side of the vane tip, L2: Projection length on the compression side of the vane tip, Ps: Suction side pressure, Pm: High pressure (compression) side pressure , H = cylinder thickness (= vane height).

Japanese Patent No. 4488104

In such a conventional structure, there are few problems when the thickness of the cylinder (length in the axial direction) is relatively small, but there are the following disadvantages when the thickness of the cylinder is large.
1) The effect of component accuracy on the uniformity of surface pressure at the sliding portion between the vane tip and the roller peripheral wall increases. The perpendicularity of the rotating shaft, the (main) bearing, and the cylinder end face deteriorates, and local contact (circle) as shown in FIG.

The load applied to the vane increases in proportion to the cylinder thickness. Therefore, the true surface pressure (contact force or pressing force) of the portion per local part is expressed by the following equation (2).
Pt = Pa * H / Lt (2)
Pt: true surface pressure per part, Pa: average surface pressure, Lt: true contact length.
In other words, the load Pt applied to the vanes becomes very high in proportion to the cylinder thickness H, thereby causing seizure and abnormal wear on the sliding portion between the roller and the vane.

2) Since the gas load applied to the rotating shaft increases, the bending of the rotating shaft increases. As a result, similar to 1) above, local contact is generated at the sliding portion, the surface pressure of the sliding portion is increased, and seizure or abnormal wear occurs.
In order to prevent these problems, a special surface treatment is applied to the sliding portion between the vane and the roller, or a structure in which the vane and the roller are integrated is used.

  For this reason, the vane is divided into two pieces to reduce the surface pressure of the sliding portion between the tip of the divided vane and the roller, and the single vane is used to press the divided vane. Rotating compressor that prevents the coil spring from coming off even if it deviates in the sliding direction, eliminates the need for a special sliding material, and suppresses cost increase, and a refrigeration cycle apparatus equipped with the rotating compressor Was desired.

  In the rotary compressor of the present embodiment, an electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft are accommodated in a sealed case, and the compression mechanism part includes a cylinder having a cylinder chamber, a cylinder A roller that moves eccentrically in the chamber, a reciprocating motion in contact with the roller, a vane that divides the cylinder chamber into a compression side and a suction side, and a rear end side of the vane so that the tip of the vane contacts the roller A coil spring for urging the vane in the roller direction. The vane is arranged by stacking two divided vanes in the height direction of the cylinder, which is the axial direction of the rotating shaft. The coil spring is configured to press the split vane, and the coil spring is provided with a close contact portion at a contact portion with the split vane, and the split vane is a tapered portion provided in the direction of the tip from the rear end edge of the split vane, Coil spring mounting groove provided continuously in the further distal direction from the tapered portion consisting of a reciprocating direction and parallel parallel portion of the vane is provided.

The longitudinal cross-sectional view of the rotary compressor based on this embodiment, and the schematic refrigeration cycle block diagram of a refrigeration cycle apparatus. The top view of the cylinder of the compression mechanism part based on the embodiment. The figure explaining the vane and coil spring structure of a compression mechanism part based on the embodiment. The figure explaining the spring attachment groove | channel provided in a vane, and a coil spring structure based on the embodiment. The figure explaining the spring attachment groove | channel based on the modification of the embodiment. The figure explaining the spring attachment groove | channel which concerns on the further modification of the embodiment. The longitudinal cross-sectional view of the compression mechanism part based on the further modification of the embodiment. The figure explaining the conventional structure, the figure explaining the sliding structure of the vane with respect to a roller, and the figure explaining the local contact | win of a vane.

Hereinafter, the present embodiment will be described with reference to the drawings.
FIG. 1 is a schematic longitudinal sectional view of a two-cylinder type rotary compressor K and a configuration diagram of a refrigeration cycle circuit R of a refrigeration cycle apparatus provided with the rotary compressor K.
First, the two-cylinder type rotary compressor K will be described.

In the figure, reference numeral 1 denotes a sealed case, in which the motor part 2 is accommodated in the upper part of the sealed case 1 and the compression mechanism part 3 is accommodated in the lower part. Furthermore, the compression mechanism 3 is immersed in an oil reservoir (not shown) of lubricating oil collected at the inner bottom of the sealed case 1.
The electric motor unit 2 and the compression mechanism unit 3 are connected to each other via a rotating shaft 4. When the electric motor unit 2 rotationally drives the rotating shaft 4, the compression mechanism unit 3 sucks and compresses a gas refrigerant as described later. And can be discharged.

The compression mechanism unit 3 includes a first cylinder 5A in the upper portion and a second cylinder 5B in the lower portion, and an intermediate partition plate is provided between the first cylinder 5A and the second cylinder 5B. 6 is interposed.
A main bearing 7 is superimposed on the upper surface of the first cylinder 5A, and the main bearing 7 is attached to the inner peripheral wall of the sealed case 1. A sub bearing 8 is stacked on the lower surface of the second cylinder 5B, and is attached to the main bearing 7 together with the second cylinder 5B, the intermediate partition plate 6 and the first cylinder 5A.

  The rotary shaft 4 is pivotally supported at the intermediate portion thereof by the main bearing 7 and is pivotally supported at the lower end portion by the auxiliary bearing 8. Further, the first cylinder 5A, the intermediate partition plate 6 and the inner diameter of the second cylinder 5B are penetrated, and the first and second cylinders 5A and 5B have the same diameter with a phase difference of about 180 ° in the inner diameter. The first eccentric portion and the second eccentric portion are integrally provided.

  The first roller 9a is fitted to the first eccentric portion circumferential surface, and the second roller 9b is fitted to the second eccentric portion circumferential surface. The first and second rollers 9a and 9b are eccentrically moved while the rotation shaft 4 is rotated, while part of the peripheral wall is in contact with the inner peripheral wall of the first cylinder 5A and the second cylinder 5B. To be accommodated.

The inner diameter portion of the first cylinder 5A is closed by the main bearing 7 and the intermediate partition plate 6 to form a first cylinder chamber 10A. The inner diameter portion of the second cylinder 5B is closed by the intermediate partition plate 6 and the auxiliary bearing 8, and a second cylinder chamber 10B is formed.
The diameters of the first cylinder chamber 10A and the second cylinder chamber 10B and the height dimension that is the axial length of the rotating shaft 4 are set to be the same. The first roller 9a is accommodated in the first cylinder chamber 10A, and the second roller 9b is accommodated in the second cylinder chamber 10B.

  The main bearing 7 is provided with a discharge muffler 11 which is doubled and provided with a discharge hole, and covers the discharge valve mechanism 12 a provided in the main bearing 7. A single discharge muffler 13 is attached to the auxiliary bearing 8 and covers the discharge valve mechanism 12 b provided in the auxiliary bearing 8. The discharge muffler 13 is not provided with a discharge hole.

  The discharge valve mechanism 12a of the main bearing 7 communicates with the first cylinder chamber 10A and opens when the inside of the cylinder chamber 10A rises to a predetermined pressure due to the compression action, and discharges the compressed gas refrigerant into the discharge muffler 11. To do. The discharge valve mechanism 12b of the auxiliary bearing 8 communicates with the second cylinder chamber 10B and opens when the inside of the cylinder chamber 10B rises to a predetermined pressure due to the compression action, and discharges the compressed gas refrigerant to the discharge muffler 13. To do.

  A discharge gas guide path is provided across the auxiliary bearing 8, the second cylinder 5 </ b> B, the intermediate partition plate 6, the first cylinder 5 </ b> A and the main bearing 7. This discharge gas guide path guides the gas refrigerant compressed in the second cylinder chamber 10B and discharged to the lower discharge muffler 13 through the discharge valve mechanism 12b into the upper double discharge muffler 11.

  On the other hand, the first vane 15A is provided in the first cylinder 5A, and the second vane 15B is provided in the second cylinder 5B. Each of the first vane 15A and the second vane 15B is divided into an upper side and a lower side along the height direction of the first cylinder 5A and the second cylinder 5B, which is the axial direction of the rotating shaft 4. It consists of two divided vanes a and b.

  As will be described later, one end of one coil spring (elastic member) 16 is elastically formed at the rear end of each of the two divided vanes a and b constituting the first and second vanes 15A and 15B. Abut. Accordingly, the coil spring 16 is biased in the direction of the rollers a and 9b so that the tip ends of the divided vanes a and b abut against the rollers 9a and 9b.

FIG. 2 is a plan view of the first cylinder 5A, and the second cylinder 5B (not shown) has a similar planar structure. Therefore, the names “first” and “second” and the symbols “A” and “B” are omitted. (Hereinafter the same)
In the cylinder 5, a vane groove 17 that opens to the cylinder chamber 10, which is an inner diameter portion, is provided continuously, and a vane back chamber 18 is provided continuously at the rear end portion of the vane groove 17. In the vane groove 17, a vane 15 that is divided into two upper and lower divided vanes a and b is accommodated in the height direction of the cylinder 5 so as to reciprocate. The front end portions of the upper side divided vane a and the lower side divided vane b can project and retract into the cylinder chamber 10, and the rear end portion can project and retract into the vane back chamber 18.

The tip ends of the divided vanes a and b are formed in a substantially arc shape in a plan view, and in a state where the tip portions protrude into the opposing cylinder chamber 10, the circular roller 9 circumferential wall in a plan view has this rotational angle. Regardless of the line contact.
Furthermore, one spring accommodating hole 19 is provided from the substantially central portion in the thickness (axis) direction of the cylinder 10, which is the outer peripheral wall of the cylinder 10, to the front of the cylinder chamber 10 which is the inner diameter portion via the vane back chamber 18. It is done.

  In a state where the coil spring 16 is accommodated in the spring accommodating hole 19 and assembled as the compression mechanism portion 3, one end portion of the coil spring 16 abuts against the inner peripheral wall of the sealed case 1. The other end portion is interposed so as to contact both the upper divided vane a and the lower divided vane b constituting the vane 15, and simultaneously presses and urges the divided vanes a and b.

As shown in FIG. 1 again, a discharge refrigerant pipe P is connected to the upper end of the sealed case. The refrigerant pipe P is provided with a condenser 20, an expansion device 21, an evaporator 22, and an accumulator 23 in order to communicate with each other.
And it connects to the 1st cylinder 5A and the 2nd cylinder 5B via the airtight case 1 in the rotary compressor K from the accumulator 23 via the two refrigerant | coolant pipes P and P for suction. In this way, the refrigeration cycle circuit R of the refrigeration cycle apparatus is configured.

  As shown in FIG. 2, a suction hole 25 is provided from the outer peripheral wall of the sealed case 1 and the cylinder 5 to the cylinder chamber 10, and a suction refrigerant pipe P branched from the accumulator 23 is inserted and fixed therein. The A suction hole 25 is provided on one side in the circumferential direction of the cylinder 5 across the vane 15 and the vane groove 17, and a discharge hole 26 communicating with the discharge valve mechanism 12 is provided on the other side.

  In the rotary compressor K configured as described above, when the electric motor unit 2 is energized and the rotary shaft 4 is rotationally driven, the roller 9 makes an eccentric motion in the cylinder chamber 10. Both the upper-side divided vane a and the lower-side divided vane b constituting the vane 15 are urged by one coil spring 16, and the tip ends of these divided vanes a and b elastically contact the peripheral wall of the roller 9.

  As each roller 9 moves eccentrically, the gas refrigerant is sucked from the suction refrigerant pipe P to the suction side of the cylinder chamber 10 defined by the vanes 15. Further, the gas refrigerant moves to the compression side of the partitioned cylinder chamber 10 and is compressed. When the compression-side volume decreases and the pressure of the gas refrigerant rises to a predetermined pressure, the gas refrigerant is discharged from the discharge hole 26 to the discharge valve mechanism 12.

  In the upper double-discharge muffler 11, the gas refrigerant discharged from the first cylinder chamber 10A and the gas refrigerant discharged from the second cylinder chamber 10B merge and are further discharged into the sealed case 1. . Then, the upper end portion of the sealed case 1 is filled through a gas guide path provided between the components constituting the motor unit 2 and discharged from the discharge refrigerant pipe P to the outside of the compressor K.

  The high-pressure gas refrigerant is led to the condenser 20 to be condensed and converted into a liquid refrigerant. This liquid refrigerant is led to the expansion device 21 and adiabatically expands, and is led to the evaporator 22 to evaporate and change into a gas refrigerant. The evaporator 22 takes away latent heat of evaporation from the surrounding air and performs a freezing action.

  If the rotary compressor K is mounted on the air conditioner, it performs a cooling action. Further, a heat pump refrigeration cycle circuit may be configured by providing a four-way switching valve on the discharge side of the compressor K in the refrigeration cycle. If the four-way switching valve is switched to reversely change the flow of the refrigerant so that the gas refrigerant discharged from the compressor K is directly led to the indoor heat exchanger, a heating operation is performed.

  Here, a mounting structure of a vane 15 composed of two divided vanes a and b that are vertically stacked in the height direction of the cylinder 5 and one coil spring 16 that urges the divided vanes a and b. Detailed description.

  As shown in FIG. 3, the coil spring 16 is wound so as to form a contact portion 16a composed of a close winding portion at a contact portion with the divided vanes a and b. The close contact portion 16a of the coil spring 16 is desirably two turns (two turns) or more. However, it may be less than 2 turns.

  In contrast, a coil spring mounting groove 30 is provided in each of the divided vanes a and b. The coil spring mounting groove 30 is provided with a tapered portion 30a provided from the rear end edge of the divided vanes a and b toward the tip portion, and is further provided continuously from the tapered portion 30a in the tip portion direction. The parallel portion 30b is parallel to the reciprocating direction.

  The opening ends of the divided vanes a and b of the tapered portion 30a have a width dimension larger than the wire diameter of the coil spring 16, and the final end of the tapered portion 30a (the processed end portion of the parallel portion 30b) is the coil spring 16. It is formed in the width dimension substantially the same as the wire diameter. The longitudinal dimension of the parallel portion 30b is less than the length of the contact portion 16a in the coil spring 16.

Since the close contact portions 16a of the coil springs 16 are fitted into the parallel portions 30b of the coil spring mounting grooves 30 provided in the respective divided vanes a and b, the postures of the divided vanes a and b are always stable and prevent falling.
In particular, when the contact portion 16a has two or more turns, the action of posture stability and fall prevention is great. Even if the coil spring 16 moves away from the coil spring mounting groove 30, since the tapered portion 30a is provided, it is easy to return to the original state.

  Even if the rotating shaft 4 is deformed due to the influence of parts accuracy or excessive gas load, and the leading edges of the divided vanes a and b contact the outer peripheral wall of the roller 9 unevenly, the height per one divided vane (shaft Since the direction length) dimension H becomes 1/2 when the vane 15 is divided into two pieces, the true (actual) surface pressure Pt of the portion per local part becomes 1/2.

  On the other hand, by limiting the shape of the coil spring mounting groove 30, for example, when liquid compression occurs, the vane 15 is separated from the roller 9 and the two divided vanes a and b are temporarily displaced in the sliding direction. However, the coil spring 16 does not fall down or come off. If it returns to the state of normal operation from this state, it will return to a regular attachment state again.

In this way, since the true surface pressure of the portion per portion can be reduced, seizure and abnormal wear of the portion can be prevented, and a highly reliable rotary compressor K can be obtained. Separately, no special sliding lubricant or surface treatment is required, and costs can be reduced.
Each split vane a. Since b slides independently on the outer peripheral wall of the roller 9, it can follow the roller 9 well even if the component accuracy is not so high. The gap between the tip edges of the divided vanes a and b and the outer peripheral wall of the roller 9 is reduced, and the leakage of the compressed gas refrigerant is reduced so that the compression performance is improved.

In particular, when a structure in which a ring groove is provided in the main bearing 7 and the sub-bearing 8 in order to relieve the extreme pressure of the bearing and the bending of the rotating shaft 4 is adopted, the effect becomes remarkable.
For example, if the number of coil springs is two in accordance with the number of the divided vanes a and b, the average diameter of each coil spring must be reduced, and design restrictions become large. Here, since there is one coil spring 16, there is no design restriction.

If the structure of the coil spring 16 and the divided vanes a and b described above are further limited, they may be set so as to satisfy the following expression (1).
As shown in FIG. 4A, the length dimension of the parallel part 30b constituting the coil spring mounting groove 30 provided in the divided vanes a and b is D, and the length dimension of the contact part 16a of the coil spring 16 is T. When
D <T (1)
The width dimension Sa of the parallel portion 30 b of the coil spring mounting groove 30 is substantially the same as the wire diameter S of the coil spring 16.

  Due to the above limitation, even if the leading edges of the divided vanes a and b abut against the outer peripheral wall of the roller 9 unevenly, the height (axial length) dimension H per divided vane is halved. For this reason, the true (actual) surface pressure Pt at the local portion is ½.

By limiting the shape of the coil spring mounting groove 30, even if the vane 15 is separated from the roller 9 and the two divided vanes a and b are temporarily displaced in the sliding direction, the coil spring 16 falls or falls off. There is nothing. If it returns to the state of normal operation from this state, it will return to a regular attachment state again.
Since the operating portion of the coil spring 16 does not come inside the parallel portion 30b of the mounting groove 30, the operating portion and the parallel portion 30b of the mounting groove 30 do not come into contact (sliding contact), and the coil spring 16 is broken. Etc. can be prevented.

5 to 7 show different modifications of this embodiment.
5A is a front view of the vane 40, and FIG. 5B is a side view of the vane 40 to which the coil spring 50 is attached.
Each of the divided vanes a and b constituting the vane 40 is provided with a spring mounting groove 60 including a deformed tapered portion 60a and a parallel portion 60b, and the coil spring 50 is fitted therein.

The shape in the width direction of the divided vanes a and b perpendicular to the longitudinal direction of the parallel portion 60 b constituting the coil spring mounting groove 60 is formed to form an arc shape equal to the inner diameter and the outer diameter of the coil spring 50.
That is, as the coil spring 50 has a circular shape in a side view, both the tapered portion 60a and the parallel portion 60b are formed in an arc shape in the side view. With the coil spring 50 fitted into the parallel portion 60b via the tapered portion 60a, the inner and outer diameters of the parallel portion 60b coincide with the inner and outer diameters of the coil spring 50.

Therefore, smooth operation is sufficient to fit the coil spring 50 into the parallel portion 60b through the tapered portion 60a. Actually, when machining the spring mounting groove 60 in the vane 40, it can be performed while rotating in a state where the machining tools or the divided vanes a and b are combined, so that the machining efficiency can be improved.
Here, the arc shape that is equal to the inner diameter and the outer diameter of the coil spring 50 means that a gap that can prevent the coil spring 50 from being largely collapsed is between the parallel portion 60 b that constitutes the mounting groove 60 and the coil spring 50. Including the case where it is formed.

6A is a front view of the vane 70, and FIG. 6A is a side view of the vane 70 to which the coil spring 80 is attached.
The shape in the width direction of the divided vanes a and b perpendicular to the longitudinal direction of the parallel portion 90b constituting the coil spring mounting groove 90 is a straight line, and the width dimension in which the inner diameter and the outer diameter of the coil spring 80 are in contact with each other. .

  That is, with the coil spring 80 fitted in the parallel portion 90b of the spring mounting groove 90, the inner diameter of the coil spring 80 contacts the inner corner of the parallel portion 90b of each of the divided vanes a and b. A diameter contacts the outer center part of the parallel part 90b of each division | segmentation vane a and b. Eventually, the coil spring 80 comes into contact with the parallel portions 90b, 90b having four inner diameters and two outer diameters.

With such a configuration, the positional deviation and disengagement of the coil spring 80 with respect to the coil spring mounting groove 90 parallel part 90b can be prevented to improve reliability, and a plurality of vanes 70 can be arranged at a time. It can be processed, and the processing efficiency can be improved.
In this case as well, the width dimension where the inner diameter and the outer diameter of the coil spring 80 are in contact with each other is such that a gap that can prevent the coil spring 50 from falling down is between the parallel portion 90b of the mounting groove 90 and the coil spring 80. Including the case where it is formed.

FIG. 7 shows only the compression mechanism unit 3 of the rotary compressor Ka of the modification.
Although it is not changed that it is a two-cylinder type rotary compressor Ka, on the other hand, for example, a vane 15A attached to the first cylinder 5A includes two divided vanes a and b and one coil spring. The fact that it is energized at 16 remains unchanged.

  There is no change in that the vane 15B attached to the second cylinder 5B is also composed of two divided vanes a and b, but here there is no coil spring. Instead, the vane back chamber 18 is exposed in the sealed case 1 and is affected by the pressure in the sealed case 1.

  The rotary shaft 4 is driven to rotate, and in the first cylinder chamber 10A, the first vane 15A is urged by the coil spring 16 and reciprocates as the roller 9a moves eccentrically. In the second cylinder chamber 10B, the roller 9b moves eccentrically, but since the inside of the sealed case 1 is still at a low pressure and is not subjected to back pressure, the second vane 15B is kicked by the roller 9b to ensure a retracted position. .

  The compression action is performed only in the first cylinder chamber 10A, and the high-pressure gas refrigerant compressed in the sealed case 1 is released. Therefore, after the pressure in the sealed case 1 gradually increases and fills up, it is discharged from the discharge refrigerant pipe P to the refrigeration cycle circuit. The gas refrigerant led to the refrigeration cycle circuit changes as described above, and the refrigeration action is performed.

  On the other hand, the gas refrigerant released from the first cylinder chamber 10 </ b> A raises the pressure in the sealed case 1 to a predetermined high pressure and fills the vane back chamber 18 exposed in the sealed case 1. Accordingly, the second vane 15B reciprocates following the roller 9b by pressing the tip portion against the roller 9b using the high-pressure gas refrigerant filling the vane back chamber 18 as the back pressure.

  As described above, in the first cylinder chamber 10A, the compression action is performed at the start of operation, whereas in the second cylinder chamber 10B, the compression action is performed in a state where the gas refrigerant compressed in the sealed case 1 is filled. Start.

  Although the compression action of the second cylinder chamber 10B is started with a time difference from the first cylinder chamber 10A, one coil spring is less than the rotary compressor K of the present embodiment described above. Therefore, it is not necessary to provide a spring accommodation hole, which contributes to cost reduction.

  As mentioned above, although this embodiment was described, the above-mentioned embodiment is shown as an example and does not intend limiting the range of embodiment. The novel embodiment can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  DESCRIPTION OF SYMBOLS 1 ... Sealing case, 2 ... Electric motor part, 4 ... Rotary shaft, 3 ... Compression mechanism part, K ... Rotary compressor, 10 ... Cylinder chamber, 5 ... Cylinder, 9 ... Roller, 15 ... Vane, a, b ... Division Vane, 16 ... Coil spring, 16a ... Adhering part, 30a ... Tapered part, 30b ... Parallel part, 30 ... Coil spring mounting groove, 20 ... Condenser, 21 ... Expansion device, 22 ... Evaporator, R ... Refrigeration Cycle circuit.

Claims (6)

In a rotary compressor that houses an electric motor unit and a compression mechanism unit connected to the electric motor unit via a rotating shaft in a sealed case,
The compression mechanism includes: a cylinder having a cylinder chamber; a roller that moves eccentrically in the cylinder chamber; a vane that reciprocates in contact with the roller and divides the cylinder chamber into a compression side and a suction side; and A coil spring that abuts on the rear end side and urges the vane in the roller direction so that the tip of the vane abuts on the roller, and
The vane is disposed by stacking two divided vanes in the height direction of the cylinder, which is the axial direction of the rotating shaft,
The coil spring is configured to press the two divided vanes by one, and a contact portion is provided at a contact portion with the divided vanes,
The split vane includes a tapered portion provided from the rear end edge of the split vane toward the tip portion, a parallel portion that is further provided in the tip direction from the tapered portion, and is parallel to the reciprocating direction of the vane. A rotary compressor having a coil spring mounting groove. When the length dimension of the parallel portion of the coil spring mounting groove provided in the split vane is D and the length dimension of the close contact portion of the coil spring is T, the following formula (1) is satisfied. The rotary compressor according to claim 1.
D <T (1) The shape of the width direction of the said division | segmentation vane orthogonal to the longitudinal direction of the parallel part which comprises the said coil spring attachment groove | channel makes the circular arc shape equal to the internal diameter and outer diameter of the said coil spring. Rotary compressor. The shape of the divided vane in the width direction perpendicular to the longitudinal direction of the parallel portion constituting the coil spring mounting groove is a straight line, and has a width dimension in which the inner diameter and the outer diameter of the coil spring are in contact with each other. The rotary compressor according to claim 1. 2. The rotary compressor according to claim 1, wherein the coil spring that biases the split vane is provided in only one cylinder of the plurality of cylinders, and is provided in another cylinder. A rotary compressor characterized in that the atmospheric pressure in the sealed case is a back pressure instead of a coil spring in the divided vanes. A refrigeration cycle comprising a rotary compressor according to any one of claims 1 to 5, a condenser, an expansion device, and a refrigeration cycle circuit communicating the evaporator via a refrigerant pipe. apparatus.

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