JP7218195B2 - rotary compressor - Google Patents

Description

The present invention relates to rotary compressors.

Rotary compressors are used in air conditioners, refrigerators, and the like. A rotary compressor has a structure in which rollers and vanes are in sliding contact, and in order to improve efficiency, it is important to reduce the frictional resistance between the rollers and vanes.

As a conventional technique, for example, as in Patent Document 1, the center of the arc of the vane tip is offset from the center line in the thickness direction of the vane to the suction chamber side, and the compression chamber side arc radius of the vane tip is changed to the suction chamber side arc radius Larger techniques have been proposed.

Further, as in Patent Document 2, a technique is disclosed in which the arc radius on the high-pressure chamber side of the tip of the vane is made smaller than the arc radius on the low-pressure chamber side.

JP 2011-231663 A JP-A-2003-293971

The rotary compressor is partitioned into a compression chamber side (high-pressure chamber side) and a suction chamber side (low-pressure chamber side) by contact of vanes with rollers. The vanes are pressed against the rollers by spring bias and back pressure. If the pressing force of the vane against the roller is large, the frictional resistance becomes large, resulting in mechanical loss. For this reason, it is important that the tip of the vane receives pressure on the compression chamber side (high pressure chamber side) in order to obtain a reaction force against the pressing force. Further, it is preferable that the vane contacts the roller with a large curvature radius R in order to reduce the surface pressure of the vane against the roller.

In the technique described in Patent Document 1, since the radius of the arc on the compression chamber side of the tip of the vane is larger than the radius of the arc on the suction chamber side, the area on the compression chamber side that receives the high pressure becomes smaller, and the vane presses. There was a problem that the reaction force against the force could not be received sufficiently, and mechanical loss due to frictional resistance occurred.

In the technique described in Patent Document 2, since the radius of the arc on the high-pressure chamber side of the tip of the vane is smaller than the radius of the arc on the low-pressure chamber side, the area on the compression chamber side that receives the high pressure can be increased. , when the rotation angle of the crankshaft of the rotary compressor is around 0 degrees, the vanes and rollers come into contact with each other on the side of the high-pressure chamber where the arc radius is small, and mechanical loss occurs due to frictional resistance due to increased surface pressure.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above problems and to provide a rotary compressor capable of suppressing mechanical loss due to frictional resistance and improving efficiency.

In order to achieve the above object, the present invention provides a crankshaft having an eccentric portion, an electric motor portion that rotationally drives the crankshaft to eccentrically drive the eccentric portion, and a compression mechanism portion that is driven by the eccentric portion. a closed container housing the crankshaft, the electric motor section, and the compression mechanism section, the compression mechanism section containing a roller eccentrically driven by the eccentric section; A rotary compressor comprising: a cylinder having a groove formed thereon; and a vane fitted in the vane insertion groove and in contact with the outer circumference of the roller to separate the cylinder into a suction chamber and a compression chamber, wherein the vane is formed with arcuate surfaces having two different curvatures, the radius of curvature R1 on the suction chamber side is larger than the radius of curvature R2 on the compression chamber side, and the center point C1 of the radius of curvature R1 on the suction chamber side is is a tangent line drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the trajectory of the center point of the roller, which is shifted toward the suction chamber side with respect to the center line CL in the thickness direction of the vane, When the rotation angle of the crankshaft is at a position where the intersection of the tangential line TL1 on the compression chamber side and the trajectory of the center point of the roller coincides with the center point C3 of the roller, the radius of curvature R2 on the compression chamber side is The center point C2 is on the suction chamber side with respect to the tangent line TL1 on the compression chamber side, and when the rotation angle of the crankshaft is 0 degrees, the center point C2 of the compression chamber side curvature radius R2 is , on the compression chamber side with respect to a straight line CCL drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the center point C3 of the roller, and from the center point C1 of the curvature radius R1 on the suction chamber side to the above Among the tangent lines drawn on the trajectory of the center point of the roller, the position where the intersection of the tangent line TL1 on the compression chamber side and the trajectory of the center point of the roller coincides with the center point C3 of the roller is the position of the crankshaft. The rotation angle is 270 degrees.

ADVANTAGE OF THE INVENTION According to this invention, the rotary compressor which can suppress a friction loss and can aim at an efficiency improvement can be provided.

1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the invention; FIG. FIG. 2 is a cross-sectional view taken along the line II-II of the compression mechanism shown in FIG. 1; FIG. 2 is an explanatory view of one rotation of the compression mechanism shown in FIG. 1; FIG. 4 is a partially enlarged view showing a contact state between rollers and vanes (the rotation angle of the crankshaft is 270 degrees) according to the first embodiment of the present invention; 5 is a partially enlarged view showing a contact state between rollers and vanes in FIG. 4; FIG. FIG. 3 is a partially enlarged view showing a contact state between rollers and vanes (the rotation angle of the crankshaft is 0 degrees) according to the first embodiment of the present invention; 7 is a partially enlarged view showing a contact state between rollers and vanes in FIG. 6. FIG. FIG. 3 is a partially enlarged view showing a contact state between rollers and vanes (the rotation angle of the crankshaft is 90 degrees) according to the first embodiment of the present invention; FIG. 9 is a partially enlarged view showing a contact state between rollers and vanes in FIG. 8 ; FIG. 11 is a partially enlarged view showing a contact state between rollers and vanes (the rotation angle of the crankshaft is 270 degrees) according to the second embodiment of the present invention; FIG. 7 is a partial enlarged view showing a contact state between rollers and vanes (the rotation angle of the crankshaft is 90 degrees) according to the second embodiment of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a rotary compressor according to the present invention will be described below with reference to the drawings. The present invention is not limited to the following examples, but includes various modifications and applications within the technical concept of the present invention.

First, the overall configuration of a rotary compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 and 2. FIG. FIG. 1 is a vertical cross-sectional view of a rotary compressor according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view of the compression mechanism shown in FIG. 1 taken along the line II--II.

A rotary compressor 20 shown in FIG. 1 has an electric motor section 21 composed of a stator 2 and a rotor 3 in the upper part of a sealed container 1 in which lubricating oil 15 is stored, and a crankshaft 4 is attached to the electric motor section 21 in the lower part. The compression mechanism part 22 connected with is accommodated. This rotary compressor 20 is used to form a part of a refrigeration cycle in refrigerators such as air conditioners and cold air applications. Such a refrigeration cycle uses an HFC refrigerant.

The crankshaft 4 has an upper portion fixed to the rotor 3 and a lower portion formed with an eccentric portion 4a. The electric motor portion 21 rotationally drives the crankshaft 4 to eccentrically drive the eccentric portion 4a.

Compression mechanism 22 has crankshaft 4 , main bearing 5 , cylinder 6 , auxiliary bearing 7 , roller 8 , and vane 9 as main components, and is driven by eccentric portion 4 a of crankshaft 4 .

Lubricating oil 15 for lubricating the compression mechanism is stored in the lower part of the sealed container 1 . The lubricating oil 15 is sucked up from an oil supply passage 4 b provided in the axial direction of the crankshaft 4 . An oil supply passage 4c that supplies oil from the oil supply passage 4b to the radial bearing portion 7b of the auxiliary bearing 7, an oil supply passage 4d that supplies oil from the oil supply passage 4b to the eccentric portion 4a of the crankshaft 4, the roller inner wall surface 8b, and the thrust bearing portion, The lubricating oil 15 is supplied to each sliding portion through an oil supply passage 4e that supplies oil from the oil supply passage 4b to the radial bearing portion 5b of the main bearing 5. As shown in FIG. Incidentally, since the oil supply passages 4c to 4e extend in the radial direction of the rotating crankshaft 4, the lubricating oil 15 is sucked up from the oil supply passage 4b by the principle of a centrifugal pump.

The main bearing 5 is fixed to the closed container 1 by welding or the like. A crankshaft 4 is rotatably supported by the main bearing 5 . A roller 8 is rotatably fitted on the eccentric portion 4a of the crankshaft 4. As shown in FIG. The roller 8 is eccentrically driven by the eccentric portion 4a of the crankshaft 4, and rotates eccentrically within the inner cylindrical surface 6a of the cylinder 6 as the eccentric portion 4a moves eccentrically.

The cylinder 6 is bolted to and supported by the main bearing 5 . The cylinder 6 is formed with an inner peripheral cylindrical surface 6a (see FIG. 2), which constitutes a working chamber. The main bearing 5 also serves as a shielding member that closes the end surface of the cylinder 6 .

Vane insertion grooves 6b (see FIG. 2) are formed through the cylinder 6 vertically. A vane 9 is horizontally slidably fitted in the vane insertion groove 6b. The vane 9 is pressed against the outer circumference of the roller 8 by a spring (not shown). The pressing force of this vane 9 is set according to the reciprocating motion of the vane 9 . The vane 9 contacts the outer circumference of the roller 8 and separates the inside of the cylinder 6 (working chamber) into a suction chamber 18 and a compression chamber 19 . The suction chamber 18 becomes a low pressure chamber and the compression chamber 19 becomes a high pressure chamber.

The secondary bearing 7 is fastened to the cylinder 6 . The sub-bearing 7 also serves as a shielding member that closes the end surface of the cylinder 6 . A space surrounded by the inner cylindrical surface 6a, the main bearing 5, the sub-bearing 7 and the roller 8 constitutes a working chamber.

The suction pipe 11 is connected to the low pressure line of the external cycle. Refrigerant gas that has flowed from the suction pipe 11 flows into the cylinder 6 through a suction port 14 provided in the cylinder 6, and flows into the working chamber (suction chamber 18) of the cylinder 6. As shown in FIG. The discharge pipe 12 communicates with the high-pressure space in the closed container 1 and is connected to the high-pressure piping of the external cycle.

As the crankshaft 4 rotates, the roller 8 rotates eccentrically within the working chamber of the cylinder 6 . As a result, the refrigerant gas is sucked into the suction chamber 18 through the suction pipe 11 in a state of low temperature and low pressure, is compressed in the compression chamber 19 switched from the suction pipe 11, and is then transferred into the sealed container 1 in a state of high temperature and high pressure. Dispensed. Refrigerant gas in the closed container 1 is discharged to the external cycle through the discharge pipe 12 . Since the inside of the sealed container 1 is in a high temperature and high pressure state, a high back pressure acts on the vanes 9 . The tip of the vane 9 presses the roller 8 with a spring force plus a back pressure.

Next, the state of contact between the vane 9 and the roller 8 will be described with reference to FIG. 3A and 3B are diagrams for explaining the operation of one rotation of the compression mechanism shown in FIG.
When the crankshaft 4 rotates, the contact state between the vane 9 and the roller 8 changes as shown in FIGS. 3(a) to 3(d). In the first embodiment, the crankshaft 4 rotates counterclockwise. When the rotation angle of the crankshaft 4 is 0 degrees, the vanes 9 are farthest from the center of the rotation axis of the crankshaft 4, as shown in FIG. 3(a). In this state, the central portion of the vane 9 contacts the roller 8 and contacts the roller 8 symmetrically about the center of the contact portion. Further, when the rotation angle of the crankshaft 4 reaches 90 degrees, as shown in FIG. . In other words, the contact position of the vane 9 with respect to the roller 8 within one rotation is the contact state at the position farthest to one side from the contact center of the vane 9 . Further, when the rotation angle of the crankshaft 4 reaches 180 degrees, the vanes 9 come closest to the center of the rotation axis of the crankshaft 4 as shown in FIG. 3(c). In this state, the central portion of the vane 9 contacts the roller 8 and contacts the roller 8 symmetrically about the center of the contact portion. Further, when the rotation angle of the crankshaft 4 reaches 270 degrees, as shown in FIG. . In other words, the contact position of the vane 9 with respect to the roller 8 within one rotation is the contact state at the position farthest from the contact center of the vane 9 to the other side. The state shown in FIG. 3(d) returns to the state shown in FIG. 3(a), and this is repeated thereafter.

As described above, the contact position of the vanes 9 with respect to the roller 8 changes as the roller 8 rotates. In the rotary compressor, reducing the frictional resistance between the vanes 9 and the rollers 8 reduces mechanical loss, leading to improved efficiency of the rotary compressor. Since the tip of the vane 9 presses the roller 8 with a spring force plus back pressure, there are two ways to reduce the frictional resistance at the tip of the vane 9 . The first means is to increase the surface area of the tip portion of the vane 9 exposed to the compression chamber 19 (high pressure chamber). If the surface area of the tip of the vane 9 is increased, the area that receives the high pressure is increased, so that the reaction force can be increased. A second means is to increase the radius of curvature R of the tip of the vane 9 that contacts the roller 8 . By increasing the curvature radius R of the tip of the vane 9, the surface pressure at the tip of the vane 9 in contact with the roller 8 can be dispersed, so the frictional resistance between the roller 8 and the vane 9 can be reduced.

Means for reducing the frictional resistance between the vanes 9 and the rollers 8 will be described below with reference to FIGS. 4 to 9. FIG. FIG. 4 is a partial enlarged view showing the contact state between the roller and the vane according to the first embodiment of the present invention. FIG. 4 shows the state (FIG. 3(d)) when the rotation angle of the crankshaft 4 has advanced to 270 degrees. FIG. 5 is a partial enlarged view showing the contact state between the roller and the vane in FIG. FIG. 6 is a partial enlarged view showing the contact state between the rollers and the vanes according to the first embodiment of the present invention. FIG. 6 shows the state (FIG. 3(a)) when the rotation angle of the crankshaft 4 is 0 degrees. FIG. 7 is a partial enlarged view showing the contact state between the roller and the vane in FIG. FIG. 8 is a partial enlarged view showing the contact state between the roller and the vane according to the first embodiment of the present invention. FIG. 8 shows the state (FIG. 3(b)) when the rotation angle of the crankshaft 4 is 90 degrees. 9 is a partially enlarged view showing a contact state between the roller and the vane in FIG. 8. FIG.

4 to 9, the tip portion of the vane 9 in the first embodiment is formed with arc surfaces having two different curvatures. In the first embodiment, the radius of curvature R1 on the side of the suction chamber 18 (low pressure chamber) is made larger than the radius of curvature R2 on the side of the compression chamber 19 (high pressure chamber).

4 and 5, the center point C1 of the radius of curvature R1 of the tip of the vane 9 on the suction chamber 18 side is set to be shifted toward the suction chamber 18 with respect to the center line CL in the thickness direction of the vane 9 (offset ). FIG. 4 shows the state when the rotation angle of the crankshaft 4 has advanced to 270 degrees. The position of the intersection of the locus of the tangential line TL1 on the 19 side and the center point of the roller 8 coincides with the center point C3 of the roller 8 at a rotation angle of the crankshaft. With this configuration, in the first embodiment, the radius of curvature from the suction chamber 18 to a portion of the compression chamber 19 can be formed to have a radius of curvature R1 that is larger than the radius of curvature R2 on the compression chamber 19 side. .

Further, the center point C2 of the curvature radius R2 of the tip of the vane 9 in the compression chamber 19 is defined by a tangent line TL1 extending toward the compression chamber 19, a parallel line PL1 passing through the center point C1 to the thickness direction center line of the vane 9, and the vane 9 The vane 9 is provided in a region on the side of the suction chamber 18 from the center line CL in the thickness direction of the vane 9 (the hatched region in FIG. 5). With this configuration, in the first embodiment, the position where the radius of curvature R1 and the radius of curvature R2 intersect can be positioned closer to the compression chamber 19 than the center line CL in the thickness direction of the vane 9. In FIG. 5, the position where the radius of curvature R1 and the radius of curvature R2 intersect substantially coincides with the contact portion CP between the vane 9 and the roller 8. As shown in FIG. Furthermore, in the first embodiment, the curvature radius R2 on the compression chamber 19 side can be formed with a smaller curvature radius than the curvature radius R1 on the suction chamber 18 side. In particular, the center point C2 of the radius of curvature R2 is located on the suction chamber 18 side with respect to the center line CL in the thickness direction of the vane 9. , the area of the radius of curvature R2 can be made larger. Further, since the area on the compression chamber side that receives the high pressure can be increased, the reaction force against the pressing force of the vanes can be increased.

The contact position of the tip of the vane 9 with the roller 8 changes according to the rotation of the compression mechanism. Next, the state when the rotation angle of the crankshaft 4 is 0 degrees will be described with reference to FIGS. 6 and 7. FIG. 6 and 7, in the first embodiment, when a straight line CCL connecting the center point C1 of the radius of curvature R1 on the side of the suction chamber 18 (low pressure chamber) and the center point C3 of the roller 8, the compression chamber 19 (high pressure chamber ) side of the curvature radius R2 is positioned on the compression chamber 19 (high pressure chamber) side with respect to the straight line CCL. With this configuration, in the first embodiment, the position where the radius of curvature R1 and the radius of curvature R2 intersect can be located closer to the compression chamber 19 than the center line CL in the thickness direction of the vane 9. A contact portion CP between the vane 9 and the roller 8 has a radius of curvature R1.

When the rotation angle of the crankshaft 4 is 0 degrees, the compression is completed and the compression chamber 19 is closed, so the differential pressure between the tip of the vane 9 and the back pressure becomes the largest. In the first embodiment, when the rotation angle of the crankshaft 4 is 0 degrees, the tip of the vane 9 contacts the roller 8 at a position with a radius of curvature R1 larger than the radius of curvature R2. surface pressure can be reduced, and mechanical loss due to frictional resistance can be reduced.

Next, the state when the rotation angle of the crankshaft 4 is 90 degrees will be described with reference to FIGS. 8 and 9. FIG. 8 and 9, the rotation angle of the crankshaft 4 is the tangent line TL2 on the side of the suction chamber 18 among the tangent lines drawn from the center point C1 of the radius of curvature R1 on the side of the suction chamber 18 to the trajectory of the center point of the roller 8. The point of intersection with the trajectory of the center point of the roller 8 coincides with the center point C3 of the roller 8 . 8 and 9, the rotation angle of the crankshaft 4 is 90 degrees. In this state, the tangent line TL2 on the side of the suction chamber 18 (low pressure side) has a center point C1 that intersects with the radius of curvature R1. In FIG. 9, the contact portion CP between the vane 9 and the roller 8 is near the intersection of the tangent line TL2 on the suction chamber 18 side (low pressure side) and the radius of curvature R1. According to the first embodiment, since the leftmost corner of the tip of the vane 9 does not come into contact with the outer diameter of the roller 8, the compression operation can be performed smoothly.

Next, a second embodiment of the invention will be described with reference to FIGS. 10A and 10B. FIG. 10A is a partially enlarged view showing the contact state between the roller and the vane (the rotation angle of the crankshaft is 270 degrees) according to the second embodiment of the present invention. FIG. 10B is a partially enlarged view showing the contact state between the roller and the vane (the rotation angle of the crankshaft is 90 degrees) according to the second embodiment of the present invention. In the second embodiment, the same reference numerals are given to the same configurations as in the first embodiment, and detailed description thereof will be omitted.

The second embodiment differs from the first embodiment in that the center line CL in the thickness direction of the vane 9 is shifted from the center point of the rotation locus of the center point of the roller 8 .

In FIG. 10A where the rotation angle of the crankshaft is 270 degrees, when a line passing through the center point of the locus of the center point of the roller 8 and parallel to the thickness direction center line CL of the vane 9 is a parallel line PL2, the vane 9 The thickness direction center line CL is positioned on the compression chamber 19 side. In other words, the center line CL in the thickness direction of the vane 9 is shifted toward the compression chamber 19 with respect to the center point of the rotation locus of the center point of the roller 8 .

10B in which the rotation angle of the crankshaft is 90 degrees, when a line passing through the center point of the trajectory of the center point of the roller 8 and parallel to the thickness direction center line CL of the vane 9 is a parallel line PL3, the vane A center line CL in the thickness direction of 9 is positioned on the suction chamber 18 side. In other words, the center line CL in the thickness direction of the vane 9 is shifted toward the suction chamber 18 with respect to the center point of the rotation locus of the center point of the roller 8 .

As described above, in the second embodiment, the center line CL in the thickness direction of the vane 9 is located on the compression chamber 19 side (high pressure chamber side) or the suction chamber 18 side with respect to the center point of the rotation trajectory of the center point of the roller 8. (low pressure chamber side). When the center line CL in the thickness direction of the vane 9 is on the compression chamber 19 side (high pressure chamber side), the curvature radius R2 at the tip of the vane 9 can be exposed to the compression chamber 19 side (high pressure chamber side) to increase the friction loss. and wear can be reduced.

Further, when the center line CL in the thickness direction of the vane 9 is on the suction chamber 18 side (low pressure chamber side), the trajectory from the center point C1 of the curvature radius R1 on the suction chamber 18 side (low pressure chamber side) to the center point of the roller 8 is The drawn tangent line TL2 on the side of the suction chamber 18 and the radius of curvature R1 on the side of the suction chamber 18 at the tip of the vane 9 tend to intersect. Alternatively, a tangent line TL2 on the side of the suction chamber drawn from the center point C1 of the radius of curvature R1 on the side of the suction chamber 18 (low pressure chamber side) to the rotation locus of the center point of the roller 8 and the tip of the vane 9 on the side of the suction chamber 18 ( low pressure chamber side) is formed on the compression chamber 19 side (high pressure chamber side) with respect to the leftmost end of the tip of the vane 9, the leftmost corner of the tip of the vane 9 is outside the roller 8. Compression can be performed smoothly without contact with the diameter.

Furthermore, by arranging the thickness direction center line CL of the vane 9 on the compression chamber 19 side (high pressure chamber side) or the suction chamber 18 side (low pressure chamber side) with respect to the center point of the rotation locus of the roller 8, , various compression chamber specifications can be met without changing the multi-arc shape of the tip of the vane 9.

In addition, the present invention is not limited to the above-described embodiments, and includes various modifications. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the described configurations.

DESCRIPTION OF SYMBOLS 1... Closed container 2... Stator 3... Rotor 4... Crankshaft 4a... Eccentric part 4b, 4c, 4c, 4d, 4e... Oil supply path 5... Main bearing 5b... Radial bearing part 6 Cylinder 6a Inner cylindrical surface 6b Vane insertion groove 7 Sub-bearing 7b Radial bearing 8 Roller 8b Roller inner wall surface 9 Vane 11 Suction pipe 12 Discharge pipe , 14... Suction port, 15... Lubricating oil, 18... Suction chamber, 19... Compression chamber, 20... Rotary compressor, 21... Electric motor part, 22... Compression mechanism part

Claims (5)

a crankshaft having an eccentric portion;
an electric motor unit that rotationally drives the crankshaft to eccentrically drive the eccentric portion;
a compression mechanism section driven by the eccentric section;
a sealed container that houses the crankshaft, the electric motor section, and the compression mechanism section;
The compression mechanism section is
a roller eccentrically driven by the eccentric portion;
a cylinder accommodating the roller and having a vane insertion groove;
a vane that is fitted into the vane insertion groove and contacts the outer circumference of the roller to separate the inside of the cylinder into a suction chamber and a compression chamber;
In a rotary compressor comprising
The tip of the vane is formed with two arcuate surfaces with different curvatures, the radius of curvature R1 on the suction chamber side being larger than the radius of curvature R2 on the compression chamber side,
The center point C1 of the radius of curvature R1 on the suction chamber side is set to be shifted toward the suction chamber side with respect to the center line CL in the thickness direction of the vane,
Of the tangent lines drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the locus of the roller center point, the intersection of the tangent line TL1 on the compression chamber side and the locus of the roller center point is the point of intersection of the roller. When the rotation angle of the crankshaft coincides with the center point C3, the center point C2 of the curvature radius R2 on the compression chamber side is on the suction chamber side with respect to the tangent line TL1 on the compression chamber side,
When the rotation angle of the crankshaft is 0 degree, the center point C2 of the compression chamber side curvature radius R2 is pulled from the center point C1 of the suction chamber side curvature radius R1 to the roller center point C3. is on the compression chamber side with respect to the straight line CCL ,
Of the tangent lines drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the locus of the roller center point, the intersection of the tangent line TL1 on the compression chamber side and the locus of the roller center point is the point of intersection of the roller. A rotary compressor , wherein the position coinciding with the center point C3 is a rotation angle of the crankshaft of 270 degrees . In claim 1 ,
Of the tangent lines drawn from the center point C1 of the radius of curvature R1 on the suction chamber side to the trajectory of the center point of the roller, the intersection of the tangent line TL2 on the suction chamber side and the trajectory of the center point of the roller is the tangent line of the roller. When the rotation angle of the crankshaft coincides with the center point C3, the tangent line TL2 on the suction chamber side drawn from the center point C1 of the radius of curvature R1 on the suction chamber side to the trajectory of the center point of the roller is A rotary compressor, wherein a tip portion of the vane intersects with a radius of curvature R1 on the suction chamber side. In claim 2 ,
Of the tangent lines drawn from the center point C1 of the radius of curvature R1 on the suction chamber side to the trajectory of the center point of the roller, the intersection of the tangent line TL2 on the suction chamber side and the trajectory of the center point of the roller is the tangent line of the roller. The rotary compressor, wherein the position coinciding with the center point C3 is a rotation angle of 90 degrees of the crankshaft. a crankshaft having an eccentric portion;
an electric motor unit that rotationally drives the crankshaft to eccentrically drive the eccentric portion;
a compression mechanism section driven by the eccentric section;
a sealed container housing the crankshaft, the electric motor section, and the compression mechanism section;
The compression mechanism section is
a roller eccentrically driven by the eccentric portion;
a cylinder accommodating the roller and having a vane insertion groove;
a vane that is fitted into the vane insertion groove and contacts the outer circumference of the roller to separate the inside of the cylinder into a suction chamber and a compression chamber;
In a rotary compressor comprising
The tip of the vane is formed with two arcuate surfaces with different curvatures, the radius of curvature R1 on the suction chamber side being larger than the radius of curvature R2 on the compression chamber side,
The center point C1 of the radius of curvature R1 on the suction chamber side is set to be shifted toward the suction chamber side with respect to the center line CL in the thickness direction of the vane,
Of the tangent lines drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the locus of the roller center point, the intersection of the tangent line TL1 on the compression chamber side and the locus of the roller center point is the point of intersection of the roller. When the rotation angle of the crankshaft coincides with the center point C3, the center point C2 of the curvature radius R2 on the compression chamber side is on the suction chamber side with respect to the tangent line TL1 on the compression chamber side,
When the rotation angle of the crankshaft is 0 degrees, the center point C2 of the compression chamber side curvature radius R2 is pulled from the center point C1 of the suction chamber side curvature radius R1 to the roller center point C3. is on the compression chamber side with respect to the straight line CCL,
displacing the center line CL in the thickness direction of the vane with respect to the center point of the rotation trajectory of the center point of the roller;
When the rotation angle of the crankshaft is 270 degrees, the center line CL in the thickness direction of the vane is shifted toward the compression chamber with respect to the center point of the rotation trajectory of the center point of the roller. rotary compressor. a crankshaft having an eccentric portion;
an electric motor unit that rotationally drives the crankshaft to eccentrically drive the eccentric portion;
a compression mechanism section driven by the eccentric section;
a sealed container that houses the crankshaft, the electric motor section, and the compression mechanism section;
The compression mechanism section is
a roller eccentrically driven by the eccentric portion;
a cylinder accommodating the roller and having a vane insertion groove;
a vane that is fitted into the vane insertion groove and contacts the outer circumference of the roller to separate the inside of the cylinder into a suction chamber and a compression chamber;
In a rotary compressor comprising
The tip of the vane is formed with two arcuate surfaces with different curvatures, the radius of curvature R1 on the suction chamber side being larger than the radius of curvature R2 on the compression chamber side,
The center point C1 of the radius of curvature R1 on the suction chamber side is set to be shifted toward the suction chamber side with respect to the center line CL in the thickness direction of the vane,
Of the tangent lines drawn from the center point C1 of the curvature radius R1 on the suction chamber side to the locus of the roller center point, the intersection of the tangent line TL1 on the compression chamber side and the locus of the roller center point is the point of intersection of the roller. When the rotation angle of the crankshaft coincides with the center point C3, the center point C2 of the curvature radius R2 on the compression chamber side is on the suction chamber side with respect to the tangent line TL1 on the compression chamber side,
When the rotation angle of the crankshaft is 0 degree, the center point C2 of the compression chamber side curvature radius R2 is pulled from the center point C1 of the suction chamber side curvature radius R1 to the roller center point C3. is on the compression chamber side with respect to the straight line CCL,
displacing the center line CL in the thickness direction of the vane with respect to the center point of the rotation trajectory of the center point of the roller;
When the rotation angle of the crankshaft is 90 degrees, the center line CL in the thickness direction of the vane is shifted toward the suction chamber with respect to the center point of the rotation locus of the center point of the roller. rotary compressor.

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