KR20130094651A - Vane rotary compressor - Google Patents

Abstract

PURPOSE: A vane rotary compressor is provided to reduce power requirement and to improve compression efficiency by extending the compression stroke, thereby enhancing fuel efficiency of a vehicle. CONSTITUTION: A vane rotary compressor includes a hollow-shaped cylinder (110), a rotor (120), and a vane (130). The rotor is installed in a hollow (111), and rotated by receiving the power of a driving source. The vane is interposed between the rotor and the inner circumferential surface of the cylinder, and rotated together with the rotor by contacting one side with the inner circumferential surface of the cylinder. The maximum clearance between the outer circumferential surface of the rotor and the inner circumferential surface of the cylinder is 5-25mm on a straight line which is extended from the center point of the rotor toward the radial direction of the rotor.

Description

{VANE ROTARY COMPRESSOR}

The present invention relates to a vane rotary compressor in which a fluid such as a refrigerant is compressed while the volume of the compression chamber is reduced during rotation of the rotor. More particularly, the present invention relates to a vane rotary compressor in which the compression efficiency is improved by increasing the compression stroke.

The vane rotary compressor is used in an air conditioner and the like and compresses a fluid such as a refrigerant and supplies it to the outside.

1 is a cross-sectional view schematically showing a conventional vane rotary compressor disclosed in Japanese Patent Laid-Open No. 2010-31759 (Patent Document 1), and FIG. 2 is a cross-sectional view taken along the line A-A of FIG.

1, a conventional vane rotary compressor 10 has a housing H constituted by a rear housing 11 and a front housing 12 as an outer appearance. Inside the rear housing 11, Of the cylinder 13 is accommodated.

At this time, the inner peripheral surface of the cylinder 13 has an elliptical cross-sectional shape as shown in Fig.

A front cover 14 is coupled to the front of the cylinder 13 and a rear cover 15 is coupled to the rear of the cylinder 13. In the rear housing 15, A discharge space Da is formed between the inner circumferential surface of the rear housing 11 and the front cover 14 and the rear cover 15 facing each other.

A rotary shaft 17 is installed in the front cover 14 and the rear cover 15 to be rotatable through the cylinder 13 and a cylindrical rotor 18 is coupled to the rotary shaft 17, And rotates in the cylinder 13 together with the rotary shaft 17 during rotation.

At this time, as shown in FIG. 2, a plurality of slots 18a are radially formed on the outer circumferential surface of the rotor 18, and the vanes 20 are slidably accommodated in each slot 18a. Lubricating oil is supplied in 18a).

When the rotor 18 is rotated by the rotation of the rotary shaft 17, the tip of the vane 20 protrudes outward of the slot 18a and is brought into close contact with the inner peripheral surface of the cylinder 13, An inner circumferential surface of the cylinder 13 and a pair of vanes 20 adjacent to each other; an opposing face 14a of the front cover 14 opposed to the cylinder 13; A plurality of compartments 21 are formed.

In addition, as shown in FIG. 1, a suction port 24 is formed at an upper portion of the front housing 12, and a suction space Sa communicating with the suction port 24 is formed inside the front housing 12. Is formed.

The front cover 14 is provided with a suction port 14b communicating with the suction space Sa, and a suction passage 13b communicating with the suction port 14b is formed through the axial direction of the cylinder 13.

2, discharge chambers 13d recessed inwardly are formed on both sides of the outer circumferential surface of the cylinder 13, and the pair of discharge chambers 13d is compressed by the discharge holes 13a. In communication with 21, a part of the discharge space Da is formed.

The rear housing 11 is formed with a high-pressure chamber 30 which is partitioned by the rear cover 15 and into which compressed refrigerant flows. That is, the inside of the rear housing 11 is partitioned into the discharge space Da and the high-pressure chamber 30 by the rear cover 15. At this time, discharge ports 15e communicating with the high pressure chamber 30 are formed in the pair of discharge chambers 13d, respectively.

Therefore, when the rotor 18 and the vane 20 are rotated during the rotation of the rotary shaft 17, the refrigerant is sucked into the respective compression chambers 21 from the suction space Sa through the suction port 14b and the suction passage 13b, The refrigerant compressed in accordance with the volume reduction of the compression chamber 21 is discharged to the discharge chamber 13d through the discharge hole 13a and flows into the high pressure chamber 30 through the discharge hole 15e, 31). Here, reference numeral 40 denotes an oil separator for separating the lubricating oil from the compressed refrigerant introduced into the high pressure chamber.

Here, in the case of the vane rotary compressor, the stroke in which the volume of the compression chamber 21 is enlarged in accordance with the rotation direction of the rotor 18 is the suction stroke, and the stroke in which the volume of the compression chamber 21 is reduced is the compression stroke. Therefore, the embodiment shown in FIG. 2 corresponds to a one-turn two compression stroke type in which two compression strokes per revolution of the rotor 18 are performed twice.

Meanwhile, FIG. 3 shows a vane rotary compressor 10 'of a general one-turn one compression stroke type, in which the rotor 18' is eccentrically rotated in the cylinder 13 ', where 1 of the rotor 18' is rotated. One compression stroke per revolution.

By the way, in the case of the one-turn two compression stroke type shown in Figure 2, the compression start point (C _s ) is located 90 degrees apart relative to the compression end point (C _e ), of the one-turn one compression stroke type shown in FIG. In this case, the compression start point C _s is located 180 ° away from the compression end point C _e .

That is, the vane rotary compressor of the 1-turn 1-compression stroke type has a compression stroke within the range of 0 ° to 180 ° from the compression start point (C _s ) to the compression end point (C _e ), and the 1-turn 2-compression stroke type vane rotary compressor. The compressor has a compression stroke within the range of 0 ° to 90 ° from the compression start point (C _s ) to the compression end point (C _e ). As such, the vane rotary compressor has a unique short compression stroke, thereby increasing the compression load. The required power HP rises, thereby lowering the compression efficiency COP, which adversely affects the fuel efficiency of the vehicle.

[Patent Document 1] JP 2010-31759 A (2010.2.12)

The present invention has been made to solve the problems described above, an embodiment of the present invention by increasing the compression stroke, the reduction of the required power (HP) and the improvement of the compression efficiency (COP), and thereby It is an object of the present invention to provide a vane rotary compressor that can contribute to improved fuel economy.

According to a preferred embodiment of the present invention, a cylinder having a hollow shape, a rotor installed in the hollow and rotating by receiving power from a driving source, interposed between the rotor and the inner circumferential surface of the cylinder, and one side of the cylinder is disposed on the inner circumferential surface of the cylinder. In the vane rotary compressor comprising a vane rotating in contact with the rotor, the maximum gap between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder on a straight line extending radially from the center point of the rotor is 5mm ~ 25mm Provided is a vane rotary compressor.

Here, when the compression stroke per one rotation of the rotor is made once, the maximum gap is greater than 180 degrees in the opposite direction to the compression rotation direction of the rotor from the point where the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder abuts than 270 ° It is preferably formed spaced at a small or equal angle.

In this case, the rotor may be eccentrically rotated in the hollow of the cylinder, or the hollow of the cylinder may form a cross-sectional involute curve.

On the other hand, when the compression stroke is performed twice per revolution of the rotor, the maximum gap is greater than 90 ° in the opposite direction to the compression rotation direction of the rotor from the point where the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder is in contact with each other than greater than 90 ° It is preferably formed spaced at a small or equal angle.

At this time, the hollow of the cylinder may be made of a long hole cross-section.

In the vane rotary compressor according to an embodiment of the present invention, the compression stroke is extended, thereby reducing the compression load and the required power (HP) and improving the compression efficiency (COP). Allows you to configure packages.

1 is a cross-sectional view schematically showing a vane rotary compressor of the conventional one-turn two compression stroke type.
2 is a sectional view taken along the line AA in Fig.
Figure 3 is a schematic diagram of a conventional one-turn one compression stroke type vane rotary compressor.
4 is a schematic diagram of a one-turn one compression stroke type vane rotary compressor according to a first embodiment of the present invention;
5 is a schematic diagram of a one-turn one compression stroke type vane rotary compressor according to a second embodiment of the present invention;
6 is a schematic view of a one-turn two compression stroke type vane rotary compressor according to a third embodiment of the present invention;

Hereinafter, preferred embodiments of the vane rotary compressor of the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation.

In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are not to be construed as limiting the scope or spirit of the invention as disclosed in the accompanying claims. Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

First Embodiment

4 is a schematic diagram of a one-rotation one compression stroke type vane rotary compressor according to a first embodiment of the present invention.

As shown in FIG. 4, the vane rotary compressor 100 according to the first exemplary embodiment of the present invention is installed in a hollow cylinder 110 and a hollow 111 of the cylinder 110 to provide power of a driving source. The rotor 120 that is received and rotated is interposed between the inner circumferential surface of the cylinder 110 and the rotor 120 and one side contacts the inner circumferential surface of the cylinder 110 to rotate with the rotor 120 to compress fluid such as a refrigerant. And vanes 130.

Here, the cylinder 110 has a hollow 111 therein, the hollow 111 has a circular cross-sectional shape as a whole, one side of the inner circumferential surface of the cylinder 110 constituting the hollow 111 is recessed in the shape of an arc. 112 is formed.

Accordingly, the hollow 111 has a circular cross-sectional shape in which one side is convex by the recess 112, and the gap between the recess 112 and the outer circumferential surface of the rotor 120 forms a maximum gap L _max described later. .

The rotor 111 of a circular cross-sectional shape is installed in the hollow 111 of the cylinder 110 so as to be rotatable, and the center of rotation of the rotor 120 is spaced apart from the center of the hollow 111 of the cylinder 110 to one side. Therefore, the rotor 120 is eccentrically rotated from the center of the cylinder 110 to one side from the center of the hollow 111.

Meanwhile, the hollow 111 of the cylinder 110 is partitioned into a plurality of spaces by a plurality of vanes 130 provided on the outer circumferential surface of the rotor 120 and supported at the inner circumferential surface of the cylinder 110. The space forms a compression chamber 113 sealed by the front cover 14 (see FIG. 1) and the rear cover 15 (see FIG. 1).

At this time, the rotor 120 is coupled to a rotary shaft 17 (see FIG. 1) connected to a clutch (not shown) driven by a drive motor (not shown) or an engine belt (not shown) to rotate along with the rotary shaft.

On the outer circumferential surface of the rotor 120, a plurality of slots 121 are cut away from each other at predetermined intervals, and the vanes 130 are inserted in the slots 121 so as to be slidable. At this time, in the example shown in FIG. 4, the vanes 130 are disposed to be offset from each other to form a predetermined angle with the center of the rotor 120, but differently, the vanes 130 are disposed on straight lines extending radially from the center of the rotor 120. Of course it is possible.

In addition, the vane 130 inserted into the slot 121 of the rotor 120 slides toward the inner circumferential surface of the cylinder 110 by the pressure of the back pressure chamber 122 when the rotor 120 rotates, and the front end thereof has a cylinder ( It is supported on the inner circumferential surface of 110, and rotates with the rotor 120.

At this time, since the center of rotation of the rotor 120 is located eccentrically from the center of the hollow 111 of the cylinder 110, between the outer circumferential surface of the rotor 120 and the inner circumferential surface of the cylinder 110 along the rotational direction of the rotor 120. The gap is changed, and the vane 130 that rotates together with the rotor 120 while the tip portion is supported by the inner circumferential surface of the cylinder 110 is a gap change between the outer circumferential surface of the rotor 120 and the inner circumferential surface of the cylinder 110. This causes the reciprocating movement along the slot 121.

At this time, the outer peripheral surface of the rotor 120 and the cylinder 110 at the point where the above-mentioned recess 112 of the cylinder 110 is located on a straight line extending in the radial direction of the rotor 120 from the center point of the rotor 120. The gap formed by the inner circumferential surface of) becomes the maximum.

Accordingly, the outer circumferential surface of the rotor 120 and the cylinder 110 are formed from the point C _e (compression end point) where the outer circumferential surface of the rotor 120 and the inner circumferential surface of the cylinder 110 abut along the compression rotation direction of the rotor 120. the inner peripheral surface between the gap is up to the mid-point of the concave portion where the (C _s; compression starting point) by the vane 130 along the slots 121 and sliding the inner circumference direction of the cylinder 110, the fluid through the inlet 114, The suction stroke sucked into the compression chamber 113 is made.

In addition, along the compression rotation direction of the rotor 120, the outer peripheral surface of the rotor 120 and the cylinder from the intermediate point C _s of the concave portion at which the gap between the outer peripheral surface of the rotor 120 and the inner peripheral surface of the cylinder 110 becomes maximum. The vane 130 is pushed into the slot 121 to the point C _{e which} the inner circumferential surface of the 110 contacts, and the fluid of the compression chamber 113 is compressed and compressed while the volume of the compression chamber 113 is reduced. The compressed fluid is discharged through the discharge port 115 is made.

That is, the compression stroke is the point (C _e ) where the outer circumferential surface of the rotor 120 and the inner circumferential surface of the cylinder 110 abut from the point C _s where the gap between the outer circumferential surface of the rotor 120 and the inner circumferential surface of the cylinder 110 is maximum. It takes place in the interval up to.

Here, the vane rotary compressor 100 according to the first embodiment of the present invention, as shown in Figure 4, greater than 180 ° in the reverse direction to the compression rotation direction of the rotor 120 from the compression end point (C _e ) At a point separated by an angle α smaller than or equal to 270 °, the inner circumferential surface of the cylinder 110 is recessed in an arc shape to form a compression start point C _s together with the recess 112.

This is compared with the conventional example when the compression start point C _s is separated from the compression end point C _e by an angle equal to or smaller than 180 ° in the reverse direction with respect to the direction of compression rotation of the rotor 120. This is because the compression stroke is the same or shortened, so that the object of the present invention cannot be achieved. If the compression stroke is spaced at an angle greater than 270 °, the suction stroke is too short compared to the compression stroke, and the overall compression efficiency (COP) is lowered. .

In addition, the maximum gap L _max formed between the inner circumferential surface of the cylinder 110 and the outer circumferential surface of the rotor 120 on the imaginary straight line connecting the center point of the rotor 120 and the compression start point C _s is preferably 5 to 25 mm. This is because the compression space is too narrow when the maximum gap L _max is smaller than 5 mm, and the compression load is increased due to the reaction force acting on the vane 130 by a fluid such as a refrigerant.

That is, according to the vane rotary compressor 100 of the one-turn one compression stroke type according to the first embodiment of the present invention, the compression stroke is extended as compared with the conventional one, thereby reducing the required power (HP) and the ideal suction stroke and compression. It is possible to construct an optimal package by providing administration costs and improving the overall efficiency (COP) of the compressor.

Second Embodiment

5 is a schematic diagram of a one-turn one compression stroke type vane rotary compressor according to a second embodiment of the present invention, and the vane rotary compressor according to the second embodiment of the present invention includes one compression stroke per rotation of the rotor. It is the same as the first embodiment described above in that it is a one-turn one compression stroke type.

However, there is a difference in that the inner circumferential surface of the cylinder is formed of an involute curve, the concave portion of the first embodiment is not formed accordingly, and a cantilever-shaped vane is provided. This will be described in detail.

As shown in FIG. 5, the vane rotary compressor 200 according to the second exemplary embodiment of the present invention is installed in a hollow cylinder 210 and a hollow 211 of the cylinder 210 to apply power of a driving source. The rotor 220 which is received and rotates is interposed between the inner circumferential surface of the cylinder 210 and the rotor 220 and one side contacts the inner circumferential surface of the cylinder 210 to rotate together with the rotor 220 to compress fluid such as a refrigerant. And vanes 230.

An inlet 214 is formed at one side of the cylinder 210 to communicate with the hollow 211, and a discharge port 215 is formed at the rear cover 15 (see FIG. 1) to communicate with the hollow 211 of the cylinder 210. The fluid, such as the refrigerant introduced into the hollow 211 of the cylinder 210 through the suction port 214, is compressed and then supplied to the outside through the discharge port 215 under a high pressure.

And, the vane 230 is provided with a plurality of the spaced apart from each other in the circumferential direction along the outer circumferential surface of the rotor 220, the front end portion of the vane 230 protruding by rotating from one side of the rotor 220, the inner circumferential surface of the cylinder 210 By being supported by, the hollow 211 of the cylinder 210 is partitioned into a plurality of spaces, each of which is a compression chamber sealed by the front cover 14 (see FIG. 1) and the rear cover 15 (see FIG. 1). (213).

Fluid such as refrigerant trapped in the compression chamber 213 is compressed as the volume of the compression chamber 213 decreases when the rotor 220 rotates. For this purpose, the inner circumferential surface of the cylinder 210 is discharged from the inlet 214. It is formed in the form of an involute curve whose diameter gradually decreases in the direction.

At this time, the rotor 220 is installed in the hollow 211 of the cylinder 210 such that the inner circumferential surface of the cylinder 210 and the outer circumferential surface of the rotor 220 are concentric in cross section. That is, the involute curve drawn along the inner circumferential surface of the cylinder 210 has the center of the start point and the end point the same as the center of the rotor 220.

Therefore, the diameter of the inner circumferential surface of the cylinder 210 gradually decreases from the inlet 214 in the compression rotation direction of the rotor 220 toward the discharge port 215 along the inner circumferential surface of the cylinder 210, and the inner circumferential surface and the rotor of the cylinder 210 gradually decrease. As the gap between the outer peripheral surfaces of the 220 gradually narrows, the volume of the compression chamber 213 decreases.

The vane 230 is hinged to one side of the outer circumferential surface of the rotor 220 to form a cantilever beam. In this case, the vane 230 includes a hinge portion 231 hinged to one side of the outer circumferential surface of the rotor 220, and a wing portion 232 extending from the hinge portion 231.

Here, the hinge portion 231 of the vane 230 is hinged to one side of the outer peripheral surface of the rotor 220, for example, an insertion groove 221 is formed on one side of the outer peripheral surface of the rotor 220, the insertion groove ( The hinge part 231 may be rotatably inserted into the 221, and when the hinge part 231 is inserted into the insertion groove 221, the hinge part 231 may be prevented from being separated in the radial direction of the rotor 220.

The wing 232 of the vane 230 extends to one side from the hinge 231, and the outer surface of the wing 232 facing the inner circumferential surface of the cylinder 210 corresponds to the outer circumferential surface shape of the rotor 220. It is preferable that it is formed with the curvature which becomes.

This is to allow the outer surface of the vane 230 to contact the inner circumferential surface of the cylinder 210 at the point where the outer circumferential surface of the rotor 220 and the inner circumferential surface of the cylinder 210 are in contact with each other. On the outer circumferential surface of the 220, the receiving groove 222 for receiving the wing portion 232 of the vane 230 is formed to be spaced apart from each other in the circumferential direction corresponding to the number of vanes (230).

At this time, the receiving groove 222, when the wing portion 232 of the vane 230 is completely accommodated in the receiving groove 222, the outer surface of the wing portion 232 and the outer peripheral surface of the rotor 220 of the same curvature It is preferably formed to form a curved surface. That is, the bottom shape of the receiving groove 222 corresponds to the inner surface shape of the wing 232, the depth of the receiving groove 222 corresponds to the thickness of the wing 232.

The vane 230 is hinged to the hinge portion 231 on one side of the outer circumferential surface of the rotor 220. The centrifugal force generated when the rotor 220 rotates and the reaction force of the fluid, (232) is rotated around the hinge portion (231) to rotate outward of the rotor (220), and is tightly supported on the inner circumferential surface of the cylinder (210).

In addition, as the gap between the inner circumferential surface of the cylinder 210 and the outer circumferential surface of the rotor 220 narrows toward the discharge port 215 from the suction port 214 along the compression rotation direction of the rotor 220, the vane 230 The wing portion 232 is folded while the unfolded angle is gradually reduced, the receiving groove 222 of the rotor 220 at the point (C _e ; compression end point) in contact with the outer peripheral surface of the rotor 220 and the inner peripheral surface of the cylinder 210. Fully folded and accommodated.

More specifically, along the compression rotation direction of the rotor 220, from the point C _e where the outer circumferential surface of the rotor 220 and the inner circumferential surface of the cylinder 210 abut, the outer circumferential surface of the rotor 220 and the inner circumferential surface of the cylinder 210. The vane 230 is extended to the inlet adjacent point C _s (compression starting point) where the gap is maximized, and a suction stroke in which fluid such as a refrigerant is sucked into the compression chamber 213 is performed.

In addition, along the direction of compression rotation of the rotor, the vane 230 is folded from the compression start point (C _s ) to the compression end point (C _e ) while the fluid such as the refrigerant is compressed, and the compressed fluid is discharged through the discharge port 215. Compression stroke is done.

Here, the vane rotary compressor 200 according to the second embodiment of the present invention, as shown in Figure 5, greater than 180 ° in the reverse direction to the direction of compression rotation of the rotor 220 from the compression end point (C _e ) At the point spaced at an angle α smaller than or equal to 270 °, the involute curve ends and a compression start point C _s is formed. Preferably, the inlet 214 is formed through the end of the involute curve.

At this time, when the compression start point (C _s ) is spaced apart from the compression end point (C _e ) by an angle equal to or less than 180 ° in the reverse direction with respect to the compression rotation direction of the rotor 220, an example of the conventional one-turn one compression stroke type Compared to (see Fig. 3) the compression stroke is the same or shortened can not achieve the object of the present invention, when spaced at an angle greater than 270 ° the suction stroke is too short compared to the compression stroke overall compression efficiency (COP ) Is lowered.

In addition, the maximum gap L _max between the inner circumferential surface of the cylinder 210 and the outer circumferential surface of the rotor 220 is preferably 5 to 25 mm on an imaginary straight line connecting the center point of the rotor 220 and the compression start point C _s . This is because the compression space is too narrow when the maximum gap L _max is smaller than 5 mm, and the compression load is increased due to the reaction force acting on the vane 230 by a fluid such as a refrigerant.

Third Embodiment

Figure 6 is a schematic diagram of a one-turn two compression stroke type vane rotary compressor according to a third embodiment of the present invention, the vane rotary compressor according to a third embodiment of the present invention, in that a recess is formed on one side of the inner peripheral surface of the cylinder Similar to the first embodiment described above.

However, compared with the first and second embodiments, there is a difference in the fact that it is a one-turn two-compression stroke type in which two compression strokes are performed per revolution of the rotor, and that the hollow shape of the cylinder is generally long in shape. Unlike the first embodiment, there is a difference in that the center of rotation of the rotor coincides with the center of the cylinder hollow.

Hereinafter, a vane rotary compressor according to a third embodiment of the present invention will be described in detail with reference to FIG. 6.

As shown in FIG. 6, the vane rotary compressor 300 according to the third exemplary embodiment of the present invention is installed in a hollow cylinder 310 and a hollow 311 of the cylinder 310 to apply power of a driving source. The rotor 320 that is received and rotates is interposed between the inner circumferential surface of the cylinder 310 and the rotor 320 and one side contacts the inner circumferential surface of the cylinder 310 to rotate together with the rotor 320 to compress fluid such as a refrigerant. And vanes 330.

Here, the cylinder 310 has a hollow 311 therein, the hollow 311 is a long hole-shaped cross-sectional shape as a whole, a pair of depressions in the form of an arc on the inner peripheral surface of the cylinder 310 constituting the hollow 311 Recesses 312 are each formed symmetrically with respect to the center.

Accordingly, the hollow 311 has a long hole cross-sectional shape in which both sides are convex by the recesses 312, and the gap between the recesses 312 and the outer circumferential surface of the rotor 320 forms a maximum gap L _max described later. do.

On the other hand, in the hollow 311 of the cylinder 310, a rotor 320 having a circular cross-sectional shape is installed on the concentric circle so as to be rotatable.

In addition, the hollow 311 of the cylinder 310 is divided into a plurality of spaces by a plurality of vanes 330 provided on the outer circumferential surface of the rotor 320 and supported by the inner circumferential surface of the cylinder 310. The space forms a compression chamber 313 sealed by the front cover 14 (see FIG. 1) and the rear cover 15 (see FIG. 1).

At this time, the rotor 320 is coupled to a rotary shaft 17 (see FIG. 1) connected to a clutch (not shown) driven by a drive motor (not shown) or an engine belt (not shown) to rotate along with the rotary shaft.

A plurality of slots 321 are formed in the outer peripheral surface of the rotor 320 spaced apart from each other at predetermined intervals, and the vanes 330 are inserted into the slots 321 so as to be slidable.

The vane 330 inserted into the slot 321 of the rotor 320 slides in the direction of the inner circumferential surface of the cylinder 310 by the pressure of the back pressure chamber 322 when the rotor 320 rotates, and the front end thereof is the cylinder. It is supported on the inner circumferential surface of 310 and rotates with the rotor 320.

In this case, the outer circumferential surface of the rotor 320 forms a circle, whereas the inner circumferential surface of the cylinder 310 forms a long hole by two circles spaced apart from the center of the rotor 320, so that the rotor 320 is formed. The gap between the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 is changed along the rotation direction of the vane 330 which rotates together with the rotor 320 while the front end is supported on the inner circumferential surface of the cylinder 310. Is reciprocated along the slot 321 due to a change in the gap between the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310.

At this time, the pair of recesses 312 described above are symmetrically formed on a straight line extending from the center point of the rotor 320 in the radial direction of the rotor 320, and at the intermediate point of each recess 312, the rotor ( The gap between the outer circumferential surface of 320 and the inner circumferential surface of the cylinder 310 is maximized.

Therefore, from the point C _e (compression end point) where the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 abut along the compression rotation direction of the rotor 320, the outer circumferential surface of the rotor 320 and the cylinder 310 are formed. the mid-point of the concave portion 312 that is between the gap is up to the inner peripheral surface; along the (C _s compression starting point) by the vane 330, the slots 321 and sliding the inner circumference direction of the cylinder 310, a fluid inlet ( A suction stroke is sucked into the compression chamber 313 through 314.

In addition, along the compression rotation direction of the rotor 320, the rotor 320 is formed from the intermediate point C _s of the recess 312 in which the gap between the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 is maximized. The vane 330 is pushed into the slot 321 to a point C _e where the outer circumferential surface of the cylinder 310 and the inner circumferential surface of the cylinder 310 abut, and the fluid of the compression chamber 313 decreases as the volume of the compression chamber 313 decreases. Is compressed, the compressed fluid is discharged through the discharge port 315 is made.

That is, the compression stroke is the point (C _e ) where the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 abut from the point C _s where the gap between the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 is maximum. The compression stroke is performed twice, while the rotor 320 is rotated once.

Here, the vane rotary compressor 300 according to the third embodiment of the present invention, as shown in Figure 6, is larger than 90 ° in the reverse direction to the compression rotation direction of the rotor 320 from the compression end point (C _e ) To form a compression start point (C _s ) at a point separated by an angle (α) less than or equal to 180 °, both sides of the elongated inner circumferential surface of the cylinder 310 are recessed in an arc shape symmetrical to each other so that the recesses 312 are respectively Is formed.

This is compared with the conventional example when the compression start point C _s is separated from the compression end point C _e by an angle equal to or smaller than 90 ° in the reverse direction with respect to the compression rotation direction of the rotor 320. This is because the compression stroke is the same or shortened, so that the object of the present invention cannot be achieved. When the compression stroke is spaced at an angle greater than 180 °, the suction stroke is too short compared to the compression stroke, and the overall compression efficiency is lowered.

In addition, the maximum gap L _max formed between the inner circumferential surface of the cylinder 310 and the outer circumferential surface of the rotor 320 on the imaginary straight line connecting the center point of the rotor 320 and the compression start point C _s is preferably 5 to 25 mm. This is because the compression space is too narrow when the maximum gap L _max is smaller than 5 mm, and the compression load is increased due to the reaction force acting on the vane 330 by fluid such as a refrigerant.

Therefore, according to the vane rotary compressor 300 of the one-turn two-compression stroke type according to the third embodiment of the present invention, the compression stroke is extended as compared with the conventional one, thereby reducing the required power (HP) and ideal suction stroke and compression. By providing the administration cost and improving the overall efficiency (COP) of the compressor it is possible to configure the optimal package.

100,200,300: vane rotary compressor
110,210,310: Cylinder
111,211,311: hollow
112,312: recessed portion
114,214,314: Inlet
115,215,315: discharge port
120,220,320: rotor
130,230,330: vanes

Claims (6)

The hollow cylinders 110, 210 and 310, the rotors 120, 220 and 320 installed in the hollows 111, 211 and 311 and are rotated by the power of the driving source, are interposed between the rotors 120, 220 and 320 and the inner circumferential surfaces of the cylinders 110, 210 and 310. In the vane rotary compressor comprising a vane (130,230,330) is rotated together with the rotor (120,220,320) in contact with the inner peripheral surface of the (110,210,310),
Vanes, characterized in that the maximum gap between the outer peripheral surface of the rotor (120,220,320) and the inner peripheral surface of the cylinder (110,210,310) on the straight line extending in the radial direction of the rotor (120,220,320) from the center point of the rotor (120,220,320) is 5mm ~ 25mm Rotary compressor.
The method according to claim 1,
Compression stroke is made once per rotation of the rotor (120,220), the maximum gap is in the compression rotation direction of the rotor (120,220) from the point where the outer peripheral surface of the rotor (120,220) and the inner peripheral surface of the cylinder (110,210) abuts A vane rotary compressor, characterized in that spaced apart at an angle greater than 180 ° and less than 270 ° in the reverse direction.
The method according to claim 2,
The rotor 120 is a vane rotary compressor, characterized in that the eccentric rotation in the hollow (111) of the cylinder (110).
The method according to claim 2,
The hollow 211 of the cylinder 210 is a vane rotary compressor, characterized in that the cross-sectional involute curve form.
The method according to claim 1,
The compression stroke is made twice per rotation of the rotor 320, and the maximum gap is in the compression rotation direction of the rotor 320 from a point where the outer circumferential surface of the rotor 320 and the inner circumferential surface of the cylinder 310 abut. A vane rotary compressor, which is formed by being spaced apart at an angle greater than 90 ° and less than 180 ° in the reverse direction.
The method according to claim 5,
The hollow 311 of the cylinder 310 is a vane rotary compressor, characterized in that the cross-section long hole type.

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