KR20140098692A - Vane rotary compressor - Google Patents

Abstract

The present invention relates to a rotary vane compressor including a plurality of curved-surface wing type vanes with the ability to rotate on the outer circumferential surface of a rotor. According to an embodiment of the present invention, a contact support unit is formed on the front end of the vanes to be continuously in contact with the hollow inner circumferential surface, thus preventing a striking noise generated during a rapid deployment of traditional vanes.

Description

{VANE ROTARY COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a vane rotary compressor in which a fluid such as a refrigerant is compressed while reducing the volume of a compression chamber during rotor rotation, and more particularly to a vane rotary compressor having a plurality of curved vane- .

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

FIG. 1 is a 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 sectional view taken along 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.

2, a plurality of slots 18a are radially formed on the outer circumferential surface of the rotor 18, and a straight type vane 20 is slidably accommodated in each slot 18a , And the lubricant is supplied into the slot 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.

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.

1, a suction port 24 is formed in an upper portion of the front housing 12, and a suction space Sa communicating with the suction port 24 is formed in the front housing 12 .

A suction port 14b communicating with the suction space Sa is formed in the front cover 14 and a suction passage 13b communicating with the suction port 14b is formed in the axial direction of the cylinder 13.

As shown in Fig. 2, discharge chambers 13d recessed inward are formed on both sides of the outer circumferential surface of the cylinder 13, and the pair of discharge chambers 13d are connected to the compression chambers 13a, (21) and forms a part of the discharge space (Da).

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, a discharge port 15e communicating with the high-pressure chamber 30 is formed in any one of the pair of discharge chambers 13d.

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).

The oil separator 40 for separating the lubricating oil from the compressed refrigerant introduced into the high pressure chamber 30 is provided in the high pressure chamber 30. The oil separating pipe 43 is installed on the upper portion of the case 41, The oil in the oil distributor chamber 42 is connected to the oil reservoir chamber 41 formed in the lower portion of the high pressure chamber 30 through the oil passage 41b, 32).

The oil stored in the oil storage chamber 32 is lubricated through the oil supply passage 15d through the lubricating space of the bush supporting the rear end of the rotary shaft 17 to lubricate the sliding surface of the rear cover 15 and the rotor 18 And flows into the discharge port 15e through the oil return groove 45 by the pressure difference between the discharge space Da and the high pressure chamber 30. [

In the case where the vane 20 of the straight type is applied as in the conventional vane rotary compressor 10 described above, since the vane 20 is constructed so as to protrude and retreat to the outside of the rotor 18 along the slot 18a, There is a problem that the tip end portion of the piston 20 collides with the inner circumferential surface of the cylinder 13 to generate striking noise.

3 is a cross-sectional view schematically showing a curved vane type vane rotary compressor disclosed in Japanese Patent Laid-Open No. 2002-130169 (Patent Document 2).

The vane rotary compressor shown in Fig. 3 includes a cylindrical cylinder 1, a rotor 2 and a drive shaft 3 thereof. At this time, the cylinder 1 has a suction port 1A and a discharge port 1B, and the rotor 2 is eccentrically installed in the cylinder 1.

A plurality of curved blade vanes 4 are provided on the outer circumferential surface of the rotor 2 to define a plurality of compression chambers 6 between the cylinder 1 and the rotor 2. One side of the vane 4 And is hinged to the outer circumferential surface of the rotor 2 by the hinge pin 5.

While the vane 4 rotates the rotor 2 by a predetermined angle from the time when the vane 4 passes through the discharge port 1B to the time when the compression stroke ends and the suction stroke starts as it passes through the suction port 1A, The back portion of the vane 4 is urged toward the rotor 2 by the inner circumferential surface of the cylinder 1 as shown in the enlarged view. At this time, the leading end portion of the vane 4 is spaced from the inner circumferential surface of the cylinder 1.

Thereafter, as the distance between the outer circumferential surface of the rotor 2 and the inner circumferential surface of the cylinder 1 is increased by the rotation of the rotor 2, the force of pressing the back portion of the vane 4 is momentarily removed, 2 so that the front end of the vane 4 comes into contact with the inner circumferential surface of the cylinder 1.

At this time, in the process of expanding the vane 4 folded in the rotor 2 toward the inner circumferential surface of the cylinder 1 due to the increase in the rotational inertia moment of the vane 4 at high speed rotation of the rotor 2, The striking noise generated when the leading end of the cylinder 1 strikes the inner circumferential surface of the cylinder 1 is caused.

At the initial stage of the suction stroke, the back portion of the vane 4 is in contact with the inner circumferential surface of the cylinder 1. After the intake stroke has progressed to some extent, the vane 4 is rapidly expanded from the rotor 2, The volume expansion of the compression chamber 6 can not be performed smoothly, resulting in a decrease in the suction flow rate.

JP 2010-031759 A (2010.02.12) JP 2002-130169 A (2002.05.09)

SUMMARY OF THE INVENTION The present invention is conceived to solve the problems of the curved vane type vane compressor as described above, and it is an object of the present invention to provide a vane rotary compressor capable of preventing the generation of a sound by the vane during high- The purpose.

According to a preferred embodiment of the present invention, there is provided a vacuum cleaner comprising: a hollow cylinder having a suction port formed at one side thereof; A rotor installed in the hollow and rotated by receiving power from a driving source; And a vane hinged to one end of the outer circumferential surface of the rotor to rotate in the direction of an inner circumferential surface of the cylinder, wherein the vane has, at an entire operating range of the vane varying by the rotation of the rotor, And a contact support portion for keeping contact with the inner circumferential surface of the cylinder.

Here, the vane includes a hinge portion hinged to one side of the outer circumferential surface of the rotor, and a wing portion extending from one side of the hinge portion, and the contact supporting portion is formed to have a width larger than a width of the wing portion at an end of the wing portion .

At this time, the wing portion is formed in the inner region of the virtual circle in which the hinge portion and the contact support portion are in contact with each other at the same time.

Further, when the leading end of the vane is brought into close contact with the rotor, the vane portion is disposed in the inner region of the imaginary circle formed along the circumference of the rotor.

At this time, a receiving groove having a shape corresponding to the inner surface shape of the vane is formed on one side of the outer circumferential surface of the rotor so that the tip of the vane is received in the rotor.

Also, a plurality of the vanes are formed spaced apart from each other in the circumferential direction of the rotor.

In addition, the hollow inner circumferential surface of the cylinder may be formed as an involute curve along the circumferential direction on the cross section.

A hollow cylinder having a suction port formed at one side thereof; A rotor installed in the hollow and rotated by receiving power from a driving source; And a vane hinged to one side of an outer circumferential surface of the rotor, the vane extending in a direction extending from one side of the hinge portion to rotate in the direction of an inner circumferential surface of the cylinder, wherein contact with the inner circumferential surface of the cylinder is maintained The vane rotary compressor is characterized in that a contact support portion is formed at an end of a wing portion of the vane.

At this time, the contact support portion is formed so as to have a width larger than the width of the wing portion.

Further, the outer edge of the wing portion is recessed and formed inside the imaginary circle in which the hinge portion and the contact support portion simultaneously come into contact with each other.

At this time, one side of the rim of the contact support portion may protrude outward.

Further, a receiving groove having a shape corresponding to the inner surface shape of the vane is formed on one side of the outer circumferential surface of the rotor so as to receive the vane.

Further, when the contact support portion is received in the receiving groove, a gap is formed between the inner peripheral surface of the cylinder and the wing portion.

A hollow cylinder having a suction port formed at one side thereof; A rotor installed in the hollow and rotated by receiving power from a driving source; And a vane having one end hinged to one side of the outer circumferential surface of the rotor and rotating in a direction toward an inner circumferential surface of the cylinder, the vane having a hinge portion hinged to one side of the outer circumferential surface of the rotor, And a contact support portion formed at an end of the wing portion and extending in a greater width than the wing portion and contacting the inner circumferential surface of the cylinder. In the entire operating range of the vane varying by the rotation of the rotor, Wherein the contact support portion is in continuous contact with the inner circumferential surface of the cylinder, and the vane portion is continuously spaced from the inner circumferential surface of the cylinder.

At this time, the outer edge of the wing portion is recessed and formed inside the imaginary circle in which the hinge portion and the contact support portion are in contact at the same time.

Further, one side of the contact support portion may be formed to protrude in the direction of the inner circumferential surface of the cylinder.

Further, at the end of the compression stroke, a gap is formed between the inner peripheral surface of the cylinder and the wing portion.

Further, at the end of the compression stroke, the outer edge of the wing portion is disposed in the inner region of the imaginary circle formed along the outer diameter of the rotor.

According to the vane rotary compressor of the preferred embodiment of the present invention, since the contact support portion is extended and formed at the tip end of the curved vane type vane, the contact support portion is always supported on the inner circumferential surface of the cylinder during rotation of the rotor, It is possible to prevent a striking noise from being generated by the vane during switching.

Further, since the volume expansion of the compression chamber progresses smoothly during the suction stroke, it is possible to prevent a decrease in the suction flow rate.

1 is a longitudinal sectional view schematically showing a conventional vane rotary compressor.
2 is a sectional view taken along the line AA in Fig.
3 is a sectional view of a conventional curved blade type vane rotary compressor.
4 is a longitudinal sectional view of a vane rotary compressor according to an embodiment of the present invention.
5 is a sectional view taken along line BB of Fig.
FIG. 6 is a schematic view illustrating a curved blade type vane according to an embodiment of the present invention; FIG.
7 is a schematic view showing an example in which a curved blade type vane according to an embodiment of the present invention is accommodated in a receiving groove of a rotor;
8 is a schematic view showing a cylinder inner circumferential surface contact section of a conventional curved blade type vane.
9 is a schematic view showing a cylinder inner circumferential surface contact section of a curved vane type vane according to an embodiment of the present invention.
10 is a schematic diagram of a vane rotary compressor according to another embodiment of the present invention;
11 is a schematic sectional view showing an example in which the inner circumferential surface of the cylinder is an involute curve shape according to another embodiment of the present invention.

Hereinafter, preferred embodiments of a vane rotary compressor according to an embodiment 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.

In addition, the following embodiments are not intended to limit the scope of the present invention, but merely as exemplifications of the constituent elements set forth in the claims of the present invention, and are included in technical ideas throughout the specification of the present invention, Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

In the following embodiments, the outer appearance of the vane rotary compressor is formed by the engagement of the housing and the second head portion, and the cylinder is accommodated in the housing. However, the present invention is not limited to the housing, But is not limited by the coupling relationship between the head portion and the cylinder.

Example

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

4, a vane rotary compressor (hereinafter referred to as a 'compressor') 100 according to an embodiment of the present invention includes a housing 110 and a second head 114. The compressor 100 Can be formed.

The housing 110 includes a cylinder portion 112 in which a space portion 111 is formed and a cylindrical portion 112 formed integrally with the cylinder portion 112 in the axial direction of the cylinder portion 112, And a first head part 113 closing the front of the cylinder part 200. A hollow cylinder 200 is mounted in the space part 111. [

Inside the cylinder 200, a rotating shaft 310 rotating by the driving force of the driving source, a rotor 300 receiving the rotating force of the rotating shaft 310 and rotating together with the rotating shaft 310, A plurality of vanes 400 hinged to be rotatable in the radial direction of the rotor 300 are mounted.

A second head portion 114 is coupled to the rear of the housing 110 in the axial direction to close the rear portion of the space portion 111.

On the other hand, a suction port (not shown) for sucking the refrigerant from the outside and a discharge port (not shown) for discharging the high-pressure refrigerant compressed in the cylinder 200 to the outside are provided on the outer peripheral surface of the first head portion 113 of the housing 110 Are spaced apart from each other in the circumferential direction.

At this time, a pulley engaging portion 510 is extended so that a pulley 500 of an electromagnetic clutch (not shown) is coupled to the front center of the first head portion 113.

5 is a sectional view taken along the line B-B in Fig.

5, the hollow of the cylinder 200 is slightly eccentric to one side from the center of the cylinder 200 in which the rotary shaft 310 is installed, and the rotor 300 having the vane 400 The hollow of the cylinder 200 forms a compression space in which the introduced refrigerant is compressed by the rotation of the rotor 300.

At this time, a suction hole 210 is formed at one side of the cylinder 200. One side of the suction hole 210 communicates with the suction port of the first head part 113, and the other side communicates with the compression space The refrigerant sucked from the outside through the suction port flows into the hollow of the cylinder 200 which is a compression space through the suction hole 210 and the suction hole 211 of the cylinder 200 .

A discharge port 220 through which the compressed high-pressure refrigerant is discharged is formed at one side of the outer circumferential surface of the cylinder 200. A plurality of discharge ports 220 communicating with a compression chamber 230 (Not shown) for guiding the high-pressure refrigerant toward the discharge port is formed at the other side of the discharge portion 220. [

The rotor 300 is coupled to a rotary shaft 310 connected to a clutch (not shown) driven by a drive motor (not shown) or an engine belt (not shown) and rotates together with the rotary shaft 310.

At this time, the rotating shaft 310 is mounted along the central axis of the cylinder 200, so that the rotor 300 slightly rotates to one side from the center of the cylinder 200 and rotates at an eccentric position in the cylinder 200 .

In addition, a curved vane type vane 400 is hingedly coupled to the outer circumferential surface of the rotor 300 so as to be spaced apart from each other. At this time, one side of the vane 400 is hinged to the outer circumferential slot 320 of the rotor 300, and the other end of the vane 400 is rotated by the centrifugal force and the pressure of the refrigerant when the rotor 300 rotates, So as to divide the compression space into a plurality of compression chambers (230).

That is, each of the compression chambers 230 is formed by a space formed by the adjacent pair of vanes 400, the outer circumferential surface of the rotor 300, and the inner circumferential surface of the cylinder 200.

The tip of the vane 400 rotates together with the inner circumferential surface of the cylinder 200 in the rotating direction of the rotor 300. When the rotor 300 is positioned eccentrically in the hollow, The volume of the compression chamber 230 is reduced and the refrigerant trapped in the compression chamber 230 is compressed.

The vane 400 includes a hinge portion 410 hinged to one side of the outer circumferential surface of the rotor 300, a wing portion 420 formed to be curved from one side of the hinge portion 410, And a contact support 430 having a width formed at an end thereof.

At this time, in order to maximize the volume reduction of the compression chamber in the compression stroke, one side of the outer circumferential surface of the rotor 300 is arranged eccentrically to come in contact with the hollow inner circumferential surface of the cylinder 200.

A plurality of receiving grooves 330 for receiving the vanes 400 of the vane 400 are formed in the circumferential direction corresponding to the number of the vanes 400 on the outer circumferential surface of the rotor 300, The vane 400 includes a wing portion receiving groove 331 for receiving the wing portion 420 of the vane 400 and a contact support receiving groove 332 for receiving the contact supporting portion 430 of the vane 400 .

The hinge portion 410 of the vane 400 is hinged to one side of the outer circumferential surface of the rotor 300 and has a hinge portion 410 having a circular cross section at a slot 320 of an arc cross- It is preferable that the hinge portion 410 is not separated from the rotor 300 in the radial direction.

The wing portion 420 of the vane 400 extends from one side of the hinge portion 410 in the direction of the hollow inner circumferential surface of the cylinder 200 and the contact supporting portion 430 is formed at the end of the wing portion 420 . At this time, a curved surface is protruded at one side of the contact supporting portion 430 in the outer direction of the wing portion 420, so that the curved surface is always kept in contact with the hollow inner circumferential surface of the cylinder 200 when the rotor 300 is rotated So that it is possible to prevent the impact noise generated during the process of rapidly expanding the vane 400 from the receiving groove 330.

FIG. 6 is a schematic view showing a curved blade type vane according to an embodiment of the present invention, and FIG. 7 is a schematic view showing an example in which a curved blade type vane according to an embodiment of the present invention is accommodated in a receiving groove of the rotor.

The contact support portion 430 may be formed on the inner surface of the wing portion 420 at the end of the wing portion 420 so that the contact support portion 430 of the vane 400 can always be kept in contact with the hollow inner circumferential surface of the cylinder 200. [ And the width w2 larger than the width w1.

6, the wing portion 420 is formed inside the imaginary circles C1, C2, C3 in which the hinge portion 410 and the contact support portion 430 are in contact with each other at the same time. That is, the outer edge of the wing portion 420 facing the hollow inner circumferential surface of the cylinder 200 is recessed into the inside of the imaginary circles C1, C2, C3 in which the hinge portion 410 and the contact support portion 430 simultaneously contact .

For example, the outer edge of the wing portion 420 connecting the hinge portion 410 and the contact support portion 430 may have a curved line of the same curvature (e.g., a part of the interval C3 between the hinge portion 410 and the contact supporting portion 430) The wing portion 420 may be formed as shown in FIG. 6 by forming the worn portion 440 at the outer edge of the wing portion 420. [

7, when the vane 400 is completely folded into the receiving groove 330 of the rotor 300 (for example, at the end of the compression stroke), the wing portion 420 is positioned on the outer peripheral surface of the rotor 300 Is disposed in the inner region of the imaginary circle R formed along the circumference.

The radius r1 from the center of the rotor 300 to the outer edge of the wing portion 420 is greater than the radius r1 of the hinge portion 410 and the contact support portion 430 (R2). At this time, a gap is formed between the hollow inner circumferential surface of the cylinder 200 and the outer edge of the wing portion 420.

Accordingly, when the rotor 300 is rotated, the vane 400 is in contact with the hollow inner circumferential surface of the cylinder 200, or when the contact support portion 430 and the hinge portion 410 are simultaneously engaged with the hollow portion of the cylinder 200, The wing portion 420 is always spaced from the inner circumferential surface of the cylinder 200. As shown in Fig.

FIG. 8 is a schematic view showing a cylinder inner circumferential surface contact section of a conventional curved vane type vane, and FIG. 9 is a schematic view showing a cylinder inner circumferential surface contact section of a curved vane type vane according to an embodiment of the present invention.

8, the contact section? Over the entire length of the wing portion of the vane 4 (see FIG. 3) is formed in the hollow of the cylinder 1 (see FIG. 3) And is pressed to the inner peripheral surface.

That is, the contact of the vane 4, which is in contact with the cylinder 1 during the compression stroke, gradually moves from E to D. At the end of the compression stroke, the vane 4 is moved to the outer peripheral surface of the rotor 2 .

Thereafter, when the suction stroke is switched to the compression stroke, the contact is rapidly moved from D to E. When the vane 4 is rapidly expanded to the outside of the rotor 2 and the front end portion thereof collides with the inner circumferential surface of the cylinder 1, .

However, according to the embodiment of the present invention, the contact section between the blade portion 420 and the inner hollow cylindrical surface of the cylinder 200 is eliminated, and as shown in FIG. 9, the contact section? The state of contact with the hollow inner circumferential surface 1 is maintained. Therefore, it is possible to prevent the generation of the sound due to the rapid expansion of the vane 400.

In addition, when the contact support portion 430 passes the compression end point, the vane completely received in the receiving groove 330 is instantly expanded to the outside of the receiving groove 330 so that the volume expansion of the compression chamber 230 is smooth, It is possible to prevent the deployment delay of the vane 400 and the suction flow reduction problem due to the sudden expansion during the suction stroke.

10 is a schematic view of a vane rotary compressor according to another embodiment of the present invention. The vane rotary compressor according to another embodiment of the present invention is similar in overall construction to the above embodiment except that the contact support portion 430 'at the tip of the vane 400' is protruded in the direction of the inner circumferential surface of the cylinder 200 .

Therefore, the same reference numerals are assigned to the same components having the same functions as those of the above-described embodiment, and redundant description will be omitted.

The vane 400 of the above-described embodiment has an outer edge of the contact support portion 430 protruding from the end of the vane portion 420 in the direction of the inner circumferential surface of the cylinder 200, 430 are formed so that the width of the contact supporting portion 430 is larger than the width of the wing portion 420.

On the other hand, in the case of the vane 400 'according to another embodiment of the present invention shown in FIG. 10, one side of the outer rim of the contact support portion 430' protrudes in the direction of the inner circumferential surface of the cylinder 200, 430 'are formed in a shape in which the inner edge of the wing portion 420 is extended. At this time, it is needless to say that the shape such that the outer rim of the contact support part 430 'protrudes and the protrusion width and length can be variously selected as needed.

11 is a schematic sectional view showing an example in which the inner circumferential surface of the cylinder is an involute curve shape according to another embodiment of the present invention.

Another embodiment of the present invention shown in FIG. 11 can be applied to vanes 400 and 400 'having the same configuration as the above-described embodiments, and the hollow inner circumferential surface of the cylinder 200' is in the involute curve form, There is a difference in that the rotor 200 'and the rotor 300 have the same central axis.

Therefore, the same reference numerals are assigned to the same components as those of the above-described embodiment, and redundant description will be omitted.

According to another embodiment of the present invention, as shown in FIG. 11, the hollow inner circumferential surface of the cylinder 200 'is formed in an involute curve shape.

In this case, the rotor 300 is installed in the hollow of the cylinder 200 'so that the inner circumferential surface of the cylinder 200' and the outer circumferential surface of the rotor 300 are concentric with each other.

In other words, the involute curve drawn along the inner circumferential surface of the cylinder 200 'has the center of the start point and the end point coinciding with the center of the rotor 300, and thus the rotor 300 is eccentrically arranged as in the above- The vibration and the noise are reduced.

During the clockwise rotation of the rotor 300, the interval between the cylinder 200 'and the rotor 300 gradually decreases while the vane 400 passes the suction section S → P, and the suction stroke progresses , The compression stroke progresses while the interval between the cylinder 200 'and the rotor 300 gradually approaches while the vane 400 passes the compression section P → S.

At this time, the contact support portion 430 of the vane 400 is moved in contact with the inner circumferential surface of the cylinder 200 ', so that the generation of the sound and the suction flow rate are prevented by the rapid expansion of the vane 400 as in the conventional art .

100: Vane rotary compressor 110: Housing
112: cylinder part 113: first head part
114: second head part 200, 200 ': cylinder
220: discharging portion 221: discharging port
230 compression chamber 300 rotor
310: rotating shaft 320: slot
330: receiving groove 331: wing receiving groove
332: contact support receiving groove 400, 400 ': vane
410: hinge part 420: wing part
430, 430 ': contact support 500: pulley
510: pulley coupling part

Claims (18)

A hollow cylinder 200, 200 ';
A rotor 300 installed in the hollow and rotated by receiving power from the driving source; And
And vanes (400, 400 ') hinged to one side of the outer circumferential surface of the rotor (300) and rotating in the direction of the inner circumference of the cylinder (200)
The vanes 400 and 400 '
In the entire operation period of the vanes 400 and 400 'that are varied by the rotation of the rotor 300, the tip portions of the vanes 400 and 400' are abutted against the contact supporting portions 430 and 430 'for continuously maintaining contact with the inner circumferential surfaces of the cylinders 200 and 200''). The present invention relates to a vane rotary compressor.
The vane according to claim 1, wherein the vanes (400, 400 '
A hinge part 410 hinged to one side of the outer circumferential surface of the rotor 300 and a wing part 420 extending from one side of the hinge part 410. The contact supporting part 430 and 430 ' Is formed to have a width greater than a width of the wing (420) at an end of the vane (420).
The method of claim 2,
Wherein the wing portion (420) is formed in an inner region of an imaginary circle in which the hinge portion (410) and the contact support portion (430, 430 ') are in contact with each other at the same time.
The method of claim 2,
Wherein the wings (420) are disposed in an inner region of an imaginary circle formed along the circumference of the rotor (300) when the tip of the vanes (400, 400 ') is in close contact with the rotor (300) Rotary compressor.
The method according to claim 1,
A receiving groove 330 having a shape corresponding to the inner surface shape of the vanes 400 and 400 'is formed on one side of the outer circumferential surface of the rotor 300 so that the tip of the vanes 400 and 400' Wherein the compressor is a vane rotary compressor.
The method according to claim 1,
Wherein a plurality of vanes (400, 400 ') are formed spaced from each other in the circumferential direction of the rotor (300).
The method according to claim 1,
Characterized in that the hollow inner circumferential surface of the cylinder (200 ') has an involute curved shape along the circumferential direction in the cross section.
A hollow cylinder 200, 200 ';
A rotor 300 installed in the hollow and rotated by receiving power from the driving source; And
A hinge portion 410 is hinged to one side of the outer circumferential surface of the rotor 300 and a wing portion 420 extending from one side of the hinge portion 410 is engaged with a vane rotating in the direction of the inner circumferential surface of the cylinder 200 400, 400 '),
Wherein a contact support portion (430, 430 ') is formed at an end of a wing portion (420) of the vane (400, 400') so that contact with the inner circumferential surface of the cylinder (200) compressor.
The method of claim 8,
Wherein the contact support portions (430, 430 ') are formed so as to have a width larger than a width of the wing portion (420).
The method of claim 8,
Wherein an outer edge of the wing portion (420) is formed inwardly of an inside of an imaginary circle in which the hinge portion (410) and the contact support portion (430, 430 ') are in contact with each other at the same time.
The method of claim 8,
And one side of the rim of the contact support part (430, 430 ') protrudes outward.
The method of claim 8,
Wherein a receiving groove (330) having a shape corresponding to an inner surface shape of the vanes (400, 400 ') is formed on one side of the outer circumferential surface of the rotor (300) so as to accommodate the vanes (400, 400').
The method of claim 12,
Wherein a clearance is formed between the inner circumferential surface of the cylinder (200, 200 ') and the wing portion (420) when the contact supporting portion (430, 430') is received in the receiving groove (330).
A hollow cylinder 200, 200 ';
A rotor 300 installed in the hollow and rotated by receiving power from the driving source; And
And a vane (400, 400 ') having one end hinged to one side of the outer circumferential surface of the rotor (300) and rotating in a direction toward an inner circumferential surface of the cylinder (200)
The vanes 400 and 400 '
A hinge part 410 hinged to one side of the outer circumferential surface of the rotor 300, a wing part 420 extending from one side of the hinge part 410 and a wing part 420 extending from the end of the wing part 420, (430, 430 ') which is formed to be wider than the inner circumferential surface of the cylinder (200, 200') so as to be in contact with the inner circumferential surface of the cylinder (200, 200 '
The contact supports 430 and 430 'continue contact with the inner circumferential surfaces of the cylinders 200 and 200' during the entire operation period of the vanes 400 and 400 'that are varied by the rotation of the rotor 300, Is continuously spaced from the inner peripheral surface of the cylinder (200, 200 ').
15. The method of claim 14,
Wherein an outer edge of the wing portion (420) is formed inwardly of an inside of an imaginary circle in which the hinge portion (410) and the contact support portion (430, 430 ') are in contact with each other at the same time.
15. The method of claim 14,
And one side of the contact support part (430, 430 ') is protruded in the direction of the inner circumferential surface of the cylinder (200, 200').
15. The method of claim 14,
Wherein a gap is formed between the inner circumferential surface of the cylinder (200, 200 ') and the wing portion (420) at the end of the compression stroke.
15. The method of claim 14,
Wherein an outer rim of the wing portion (420) is disposed in an inner region of an imaginary circle formed along the outer diameter of the rotor (300) at the end of the compression stroke.

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