WO2011105085A1

WO2011105085A1 - Rotary compressor

Info

Publication number: WO2011105085A1
Application number: PCT/JP2011/001054
Authority: WO
Inventors: 昌弥中野; 啓椎崎; 大輔船越; 正浩坪川
Original assignee: パナソニック株式会社
Priority date: 2010-02-24
Filing date: 2011-02-24
Publication date: 2011-09-01
Also published as: CN102333957A; JPWO2011105085A1

Abstract

Disclosed is a rotary compressor which prevents vacuum conditions in microscopic gaps which occur from top dead centre and also controls the increase in contact pressure on the blade sliding section. The rotary compressor is comprised of a cylinder chamber (8) formed inside a cylinder (4), where the cylinder chamber (8) is blocked by an upper bearing (5) and a lower bearing (6), a roller (7) is disposed inside the cylinder chamber (8), a blade sliding groove (12) is formed on the cylinder (4), a blade (13) and a spring (14) are formed on the blade sliding groove (12), the spring (14) pushes the blade (13) against the outer surface of the roller (7), and the cylinder chamber (8) is divided by the blade (13) into a high-pressure side compression chamber and a low-pressure side compression chamber opened onto by an inlet aperture (9). One end of a notched section (20A) is positioned at the blade sliding groove (12), and the other extremity is positioned within a projection area X of the inlet aperture (9) on an inside surface (4a) of the cylinder (4).

Description

Rotary compressor

The present invention relates to a rotary compressor.

A conventional rotary compressor is shown in FIG.
The hermetic casing 101 has a cylinder 102, which forms a cylinder chamber 103. The roller 104 is disposed in the cylinder chamber 103. The roller 104 is eccentrically rotated in the cylinder chamber 103 by the rotation of the eccentric shaft 105. A blade slide groove 106 is formed in the cylinder 102, and a blade 107 is disposed in the blade slide groove 106. The blade 107 is always pressed against the outer peripheral surface of the roller 104 by a spring 108 disposed on the back side. The cylinder chamber 103 is divided by the blade 107 into a compression chamber in which a discharge port (not shown) opens and a suction chamber in which a suction hole 110 opens.
FIG. 29 shows a state in which the blade 107 is rotated slightly clockwise (in the direction of the arrow in the drawing) from the position (top dead center) where the blade 107 is pushed in to the maximum by the roller 104.
In this state, a minute space 109 surrounded by the cylinder 102, the roller 104, and the blade 107 is formed. Since the microspace 109 formed past the top dead center is in a vacuum state until it communicates with the suction hole 110, there is a problem that the required power increases.
In order to solve this problem, it has been proposed to form a groove 111 communicating the blade sliding groove 106 with the suction hole 110 on the inner peripheral surface of the cylinder 102 as shown in FIG. Reference 1).

Japanese Utility Model Application Publication No. 02-014492 (Microfilm of Japanese Patent Application No. 63-091486)

As proposed in Patent Document 1, by forming the groove 111 connecting the blade sliding groove 106 and the suction hole 110, it is possible to prevent the vacuum state of the minute space 109 occurring after the top dead center. The surface pressure of the sliding portion on the suction hole 110 side of the blade 107 rises, causing a problem such as seizing of the blade 107 and lowering the reliability.

Therefore, an object of the present invention is to provide a rotary compressor that can prevent a vacuum state of a minute space occurring after top dead center and can suppress an increase in surface pressure of a blade sliding portion.

In the rotary compressor according to the first invention, a cylinder chamber is formed in a cylinder, the cylinder chamber is closed by an upper bearing and a lower bearing, a roller is disposed in the cylinder chamber, and The blade sliding groove is formed, and a blade and a spring are disposed in the blade sliding groove, and the blade is pressed against the outer peripheral surface of the roller by the spring, and the cylinder chamber is The rotary compressor is divided into a high pressure side compression chamber and a low pressure side compression chamber in which a suction hole is opened, and one end thereof is positioned in the blade sliding groove and the other end is the suction hole The present invention is characterized in that a notched portion located within a projection range on the inner peripheral surface of the cylinder is provided.
A second aspect of the invention is the rotary compressor according to the first aspect, wherein the cutaway portion is formed at a corner portion where an inner peripheral surface forming the cylinder chamber and an upper end surface of the cylinder abutted by the upper bearing contact. It is characterized in that it is formed.
A third aspect of the invention is the rotary compressor according to the first aspect, wherein the cutaway portion is formed at a corner portion where an inner peripheral surface forming the cylinder chamber and a lower end surface of the cylinder abutted by the lower bearing contact. It is characterized in that it is formed.
A fourth invention is characterized in that, in the rotary compressor described in the second or third aspect, the cutout portion is formed by a flat inclined surface.
A fifth invention is characterized in that, in the rotary compressor described in the second or third aspect, the cutout portion is formed by a curved surface.
A sixth invention is characterized in that, in the rotary compressor described in the second or third aspect, the cutout portion is formed by a plurality of inclined surfaces having different angles.
A seventh invention is characterized in that, in the rotary compressor described in the second or third aspect, the cutout portion is formed by a flat inclined surface and a curved surface.
An eighth aspect of the invention is the rotary compressor according to any one of the first to the seventh, wherein the height of the cylinder is H, the height of the cutout is h, and the depth of the cutout is b. The height h of the cutout portion is 1 / 7H to 1 / 5H, and the depth b of the cutout portion is 1 / 7H to 1⁄3H.
A ninth aspect of the invention is the rotary compressor according to the first aspect, wherein the cutaway portion is formed by providing a groove along the inner peripheral surface forming the cylinder chamber on the upper end surface of the lower bearing. It is characterized by
According to a tenth invention, in the rotary compressor described in the first, the notch is formed by providing a groove along an inner circumferential surface forming the cylinder chamber on a lower end surface of the upper bearing. It is characterized by
An eleventh invention is characterized in that, in the rotary compressor as described in the eighth or ninth invention, the cutout portion is formed by a concave portion of a flat bottom surface.
A twelfth invention is characterized in that, in the rotary compressor as described in the eighth or ninth invention, the cutout portion is formed by a concave portion of a curved surface.
The thirteenth invention is the rotary compressor as described in the ninth to twelfth embodiments, wherein the height of the cylinder is H, the height of the notch is h, and the depth of the notch is b. The height h of the cutaway portion is 1 / 7H to 1 / 3H, and the depth b of the cutaway portion is 1 / 7H to 1 / 3H.

According to the present invention, the surface pressure applied to the blade does not increase, and the refrigerant gas can be sufficiently supplied, and the low pressure side compression chamber formed from the top dead center to the communication with the suction hole and Since the minute space which does not become is not in a vacuum state, it is possible to prevent an increase in required power.

Longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention AA line sectional view in FIG. 1 Main part enlarged view of Fig. 2 The perspective view which shows the principal part of the same rotary compressor Principal part sectional view of cylinder of same rotary compressor Rotary compressor according to a second embodiment of the present invention Rotary compressor according to a third embodiment of the present invention Rotary compressor according to a fourth embodiment of the present invention A longitudinal sectional view of a rotary compressor according to a fifth embodiment of the present invention BB cross section in FIG. 9 The main part enlarged view of FIG. 10 The perspective view which shows the principal part of the same rotary compressor Principal part sectional view of cylinder of same rotary compressor Rotary compressor according to the sixth embodiment of the present invention Rotary compressor according to a seventh embodiment of the present invention Rotary compressor according to the eighth embodiment of the present invention A longitudinal sectional view of a rotary compressor according to a ninth embodiment of the present invention CC sectional view in FIG. 17 Main part enlarged view of FIG. 18 The perspective view which shows the principal part of the same rotary compressor Principal part sectional view of cylinder of same rotary compressor Rotary compressor according to the tenth embodiment of the present invention The longitudinal cross-sectional view of the rotary compressor in the 11th embodiment of the present invention DD line cross section in FIG. 23 The main part enlarged view of FIG. 24 The perspective view which shows the principal part of the same rotary compressor Principal part sectional view of cylinder of same rotary compressor Rotary compressor according to a twelfth embodiment of the present invention Conventional rotary compressor Conventional rotary compressor

4 cylinder 4a inner circumferential surface 4b upper end surface 4c lower end surface 5 upper bearing 5a lower end surface 6 lower bearing 6a upper end surface 7 roller 8 cylinder chamber 9 suction hole 12 blade sliding groove 13 blade 14 spring 20A notch 20B notch Section 20C Notched portion 20D Notched portion 20E Notched portion 20F Notched portion 20G Notched portion 20H Notched portion 20J Notched portion 20K Notched portion 20L Notched portion 20M Notched portion 21 One end 22 Other end 23 Inclined surface 24 Curved surface 25 Bottom surface 26 Curved surface H Cylinder height b Notch depth h Notch height x Projection range

According to a first aspect of the present invention, a notch is provided with one end located in the blade slide groove and the other end located in a projection range of the suction hole on the inner circumferential surface of the cylinder. Since the minute space which becomes the low pressure side compression chamber formed from the top dead center to the communication with the suction hole does not become vacuum state, it is possible to prevent the increase of the required power, and the surface of the blade sliding portion The pressure rise can be suppressed, and the efficiency and reliability of the rotary compressor can be improved.
In a second aspect based on the first aspect, the notch portion is formed at a corner portion where the inner peripheral surface forming the cylinder chamber and the upper end surface of the cylinder in contact with the upper bearing contact. Machining of the notched part becomes easy.
According to a third invention, in the first invention, the notch is formed at a corner where the inner circumferential surface forming the cylinder chamber and the lower end face of the cylinder, which the lower bearing abuts, contact with each other. Machining of the notched part becomes easy.
In a fourth aspect based on the second or third aspect, the notch portion is formed by a flat inclined surface, which facilitates the processing of the notch portion.
According to a fifth invention, in the second or third invention, the notch portion is formed by a curved surface, and in the case of the same height and the same depth as in the fourth invention, the passage is cut off. As the area increases, a smooth refrigerant gas flow is generated.
In a sixth aspect based on the second or third aspect, the notch may be formed by a plurality of inclined surfaces having different angles.
In a seventh aspect according to the second or third aspect, the notch may be formed by a flat inclined surface and a curved surface.
According to an eighth invention, in the first to seventh invention, when the height of the cylinder is H, the height of the cutout is h, and the depth of the cutout is b, By setting the height h to 1 / 7H or more and 1 / 5H or less and setting the depth b of the notched portion to 1 / 7H or more and 1 / 3H or less, the surface pressure applied to the blade does not increase, and the refrigerant gas Supply enough.
In a ninth aspect based on the first aspect, the notch is formed by providing a groove along the inner circumferential surface forming the cylinder chamber on the upper end surface of the lower bearing. Processing becomes easy.
In a tenth aspect based on the first aspect, the notch is formed by providing a groove along the inner circumferential surface forming the cylinder chamber on the lower end surface of the upper bearing. Processing becomes easy.
In an eleventh aspect based on the eighth or ninth aspect, the notch portion is formed by the recess on the flat bottom surface, so that the notch portion can be easily processed.
According to a twelfth aspect of the present invention, in the eighth or ninth aspect, the notch portion is formed by the concave portion of the curved surface, and in the case of the same height and the same depth as in the eleventh aspect, As the passage cross-sectional area is increased, smooth refrigerant gas flow is generated.
According to a thirteenth aspect of the present invention, in the ninth to twelfth aspects, when the height of the cylinder is H, the height of the cutout is h, and the depth of the cutout is b, By setting the height h to 1/7 H or more and 1/3 H or less, and setting the depth b of the notched portion 1/7 H or more to 1/3 H or less, the refrigerant gas can be supplied without causing a refrigerant gas leak. Can do enough.

A rotary compressor according to a first embodiment of the present invention is shown in FIGS.
1 is a longitudinal sectional view of the rotary compressor, FIG. 2 is a sectional view taken along the line AA in FIG. 1, FIG. 3 is an enlarged view of an essential part of FIG. 2, and FIG. 4 is a perspective view showing an essential part of the rotary compressor FIG. 5 is a cross-sectional view of an essential part of a cylinder of the rotary compressor.

As shown in FIG. 1, an electric mechanism 2 is provided in the cylindrical sealed container 1. A crankshaft 3 is provided on the rotor 2 a of the electric mechanism 2.
Further, in the sealed container 1, a compression mechanism constituted by the cylinder 4, the upper bearing 5, the lower bearing 6, and the roller 7 is provided.
A cylinder chamber 8 is formed in the cylinder 4, and the cylinder chamber 8 is closed by the upper bearing 5 and the lower bearing 6. The roller 7 is disposed in the cylinder chamber 8. Upper bearing 5 and lower bearing 6 receive crankshaft 3, and between upper bearing 5 and lower bearing 6, eccentric shaft 3 a of crankshaft 3 is disposed. The roller 7 is mounted on the eccentric shaft 3a.
A suction hole 9 is formed in the cylinder 4, and the gas refrigerant is introduced into the cylinder chamber 8 from the outside of the closed container 1 by the suction hole 9. Further, the gas refrigerant compressed in the cylinder chamber 8 is discharged from the discharge port (not shown) formed in the upper bearing 5 into the sealed container 1, and thereafter, is discharged from the discharge pipe 10 to the outside of the sealed container 1. . The bottom of the closed container 1 is formed with an oil reservoir 11 for storing lubricating oil.
At the upper end of the inner circumferential surface of the cylinder 4, a notch 20A described later is formed.
In the rotary compressor of the present embodiment, a mixed refrigerant of HFC32 and HFC125, or a natural refrigerant such as carbon dioxide, ammonia, or helium can be used as a refrigerant.

Next, the compression mechanism will be further described using FIG.
A radially extending blade slide groove 12 is formed in the cylinder 4. A blade 13 and a spring 14 are disposed in the blade sliding groove 12, and the blade 13 is always pressed against the outer peripheral surface of the roller 7 by the spring 14. Since the blade 13 is pressed by the spring 14, the blade 13 reciprocates in the blade sliding groove 12 as the roller 7 rotates.
The cylinder chamber 8 is divided by the blade 13 into a high pressure side compression chamber in which the discharge port is opened and a low pressure side compression chamber in which the suction hole 9 is opened.

Next, the notch will be further described using FIGS. 3 to 5.
FIG. 3 shows a state in which the blade 13 is rotated slightly clockwise (in the direction of the arrow in the drawing) from the position (top dead center) where the blade 13 is pushed in to the maximum by the roller 7. A minute space 8a is formed.
As shown in FIGS. 3 and 4, the notch 20A has one end 21 thereof in the blade slide groove 12 and the other end 22 in the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4. It is located in.
Further, as shown in FIGS. 4 and 5, the notch 20A is a part of the corner where the inner circumferential surface 4a forming the cylinder chamber 8 and the upper end surface 4b of the cylinder 4 with which the upper bearing 5 abuts contact. Is formed. The other end 22 of the notch 20A does not communicate with the suction hole 9.
The refrigerant gas flows into the minute gap 8a shown in FIG. 3 from the suction chamber in which the suction hole 9 is opened by the cutout portion 20A, and the vacuum state is not established.
When the other end 22 of the notch 20A does not reach within the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, a slight vacuum occurs. Therefore, it is preferable that the other end 22 of the notch 20A be within the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4. On the other hand, when the other end 22 of the notch 20A exceeds the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, the compression stroke is reduced and the compression ratio is reduced. Therefore, it is preferable that the other end 22 of the notch 20A does not exceed the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4.

As shown in FIG. 5, the notch 20A is formed by notching a corner where the inner circumferential surface 4a and the upper end surface 4b are in contact with each other. The notch 20A shown in FIG. 5 is formed by forming a flat inclined surface 23 by a notch between the inner circumferential surface 4a and the upper end surface 4b.
When the height of the cylinder 4 (the axial direction of the crankshaft 3) is H, the height of the notch 20A is h, and the depth of the notch 20A is b, as shown in FIG. The height h of 20A is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20A is preferably 1 / 7H to 1 / 3H.
When the height h of the notch 20A exceeds 1 / 5H, the surface pressure applied to the blade 13 increases, and when the height h of the notch 20A falls below 1 / 7H, the refrigerant gas passage becomes too narrow, and the pressure The loss causes insufficient supply of the refrigerant gas. The depth b of the notch 20A is preferably equal to or greater than the height h of the notch 20A, so 1 / 7H or more is preferable, and if the depth b of the notch 20A exceeds 1 / 3H Unpreferable for practical use.

A rotary compressor according to a second embodiment of the present invention is shown in FIG.
The present embodiment is the same as the first embodiment except that it will be described with reference to FIG. 6, and thus the description of FIGS. 1 to 4 described in the first embodiment will be omitted.
As shown in FIG. 6, also in the present embodiment, the notch 20B is formed by notching the corner where the inner peripheral surface 4a and the upper end surface 4b are in contact. The notch 20B shown in FIG. 6 is formed by forming a curved surface 24 by a notch between the inner circumferential surface 4a and the upper end surface 4b.
Also in the present embodiment, the height h of the notch 20B is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20B is 1 / 7H to 1 / 3H. Is preferred.
In the second embodiment, when the height h and the depth b of the notch 20A of the first embodiment are the same, the direction of the notch 20B according to the second embodiment is the same. However, since the passage cross-sectional area is increased, a smooth refrigerant gas flow is generated.

A rotary compressor according to a third embodiment of the present invention is shown in FIG.
The present embodiment is the same as the first embodiment except that it will be described with reference to FIG. 7, and thus the description of FIGS. 1 to 4 described in the first embodiment will be omitted.
As shown in FIG. 7, also in the present embodiment, the notch 20 </ b> C is formed by notching the corner where the inner peripheral surface 4 a and the upper end surface 4 b contact. The notch 20C shown in FIG. 7 is formed by forming two flat

inclined surfaces

23a and 23b having different angles by the notch between the inner peripheral surface 4a and the upper end surface 4b. In addition, you may form by two or more inclined surfaces 23. FIG.
Also in the present embodiment, the height h of the notch 20C is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20C is 1 / 7H to 1 / 3H. Is preferred.
As in the present embodiment, the notch 20C may be formed by two flat

inclined surfaces

23a and 23b having different angles.

A rotary compressor according to a fourth embodiment of the present invention is shown in FIG.
The present embodiment is the same as the first embodiment except that it will be described with reference to FIG. 8, and thus the description of FIGS. 1 to 4 described in the first embodiment will be omitted.
As shown in FIG. 8, also in the present embodiment, the notch 20D is formed by notching the corner where the inner circumferential surface 4a and the upper end surface 4b contact. The notch 20D shown in FIG. 8 is formed by forming a flat inclined surface 23 and a curved surface 24 by a notch between the inner peripheral surface 4a and the upper end surface 4b.
Also in the present embodiment, the height h of the notch 20D is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20D is 1 / 7H to 1 / 3H. Is preferred.
As in the present embodiment, the notch 20D may be formed by the flat inclined surface 23 and the curved surface 24.

A rotary compressor according to a fifth embodiment of the present invention is shown in FIGS.
9 is a longitudinal sectional view of the rotary compressor, FIG. 10 is a sectional view taken along the line BB in FIG. 9, FIG. 11 is an enlarged view of an essential part of FIG. 10, and FIG. 12 is a perspective view showing an essential part of the rotary compressor FIG. 13 is a cross-sectional view of an essential part of a cylinder of the rotary compressor. The same members as those of the first embodiment are indicated by the same reference numerals and the description thereof is omitted.

As shown in FIG. 9, in the present embodiment, at the lower end of the inner peripheral surface of the cylinder 4, a notch 20E described later is formed.
As shown in FIGS. 11 and 12, the notch 20E has one end 21 thereof in the blade slide groove 12 and the other end 22 in the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4. It is located in.
Further, as shown in FIGS. 12 and 13, the notch 20E is one of the corner portions where the inner peripheral surface 4a forming the cylinder chamber 8 and the lower end surface 4c of the cylinder chamber 8 with which the lower bearing 6 abuts contact. It is formed in the part. The other end 22 of the notch 20E does not communicate with the suction hole 9.
The refrigerant gas flows into the minute gap 8a shown in FIG. 11 from the suction chamber in which the suction hole 9 is opened by the cutout portion 20E, and the vacuum state is not established.
When the other end 22 of the notch 20E does not reach within the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, a slight vacuum state occurs. Therefore, it is preferable that the other end 22 of the notch 20E be within the projection range X of the suction hole 8 on the inner circumferential surface 4a of the cylinder 4. On the other hand, when the other end 22 of the notch 20E exceeds the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, the compression stroke is reduced and the compression ratio is reduced. Therefore, it is preferable that the other end 22 of the notch 20E does not exceed the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4.

As shown in FIG. 13, the notch 20E is formed by notching the corner where the inner circumferential surface 4a and the lower end surface 4c are in contact with each other. The notch 20E shown in FIG. 13 is formed by forming a flat inclined surface 23 by a notch between the inner peripheral surface 4a and the lower end surface 4c.
Further, as shown in FIG. 13, when the height of the cylinder 4 (the axial direction of the crankshaft 3) is H, the height of the notch 20E is h, and the depth of the notch 20E is b, the notch The height h of 20E is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20E is preferably 1 / 7H to 1 / 3H.
When the height h of the notch 20E exceeds 1 / 5H, the surface pressure applied to the blade 13 increases, and when the height h of the notch 20E is less than 1 / 7H, the refrigerant gas passage becomes too narrow, and the pressure The loss causes insufficient supply of the refrigerant gas. The depth b of the notch 20E is preferably equal to or greater than the height h of the notch 20E, so 1 / 7H or more is preferable, and when the depth b of the notch 20E exceeds 1 / 3H Unpreferable for practical use.

A rotary compressor according to a sixth embodiment of the present invention is shown in FIG.
The present embodiment is the same as the fifth embodiment except that it is described with reference to FIG. 14, and thus the description of FIGS. 9 to 12 described in the fifth embodiment will be omitted.
As shown in FIG. 14, also in the present embodiment, the notch 20F is formed by notching the corner where the inner peripheral surface 4a and the lower end surface 4c are in contact. The notch 20F shown in FIG. 14 is formed by forming a curved surface 24 by a notch between the inner circumferential surface 4a and the lower end surface 4c.
Also in the present embodiment, the height h of the notch 20F is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20F is 1 / 7H to 1 / 3H. Is preferred.
In the sixth embodiment, when the height h and the depth b of the notch 20E of the fifth embodiment are the same, the direction of the notch 20F according to the sixth embodiment is the same. However, since the passage cross-sectional area is increased, a smooth refrigerant gas flow is generated, which is preferable.

A rotary compressor according to a seventh embodiment of the present invention is shown in FIG.
The present embodiment is the same as the fifth embodiment except that it is described with reference to FIG. 15. Therefore, the description of FIGS. 9 to 12 described in the fifth embodiment will be omitted.
As shown in FIG. 15, also in the present embodiment, the notch 20G is formed by notching the corner where the inner circumferential surface 4a and the lower end surface 4c contact. The notch 20G shown in FIG. 15 is formed by forming two flat

inclined surfaces

23a and 23b having different angles by the notch between the inner peripheral surface 4a and the lower end surface 4c. In addition, you may form by two or more inclined surfaces 23. FIG.
Also in the present embodiment, the height h of the notch 20G is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20G is 1 / 7H to 1 / 3H. Is preferred.
As in the present embodiment, the notch 20G may be formed by two flat

inclined surfaces

23a and 23b having different angles.

The rotary compressor in the 8th Embodiment of this invention is shown in FIG.
The present embodiment is the same as the fifth embodiment except that it is described with reference to FIG. 16, and thus the description of FIGS. 9 to 12 described in the fifth embodiment will be omitted.
As shown in FIG. 16, also in the present embodiment, the notch 20H is formed by notching the corner where the inner peripheral surface 4a and the lower end surface 4c are in contact. The notch 20H shown in FIG. 16 is formed by forming a flat inclined surface 23 and a curved surface 24 between the inner circumferential surface 4a and the lower end surface 4c with a notch.
Also in the present embodiment, the height h of the notch 20H is preferably 1 / 7H to 1 / 5H, and the depth b of the notch 20H is 1 / 7H to 1 / 3H. Is preferred.
As in the present embodiment, the notch 20H may be formed by the flat inclined surface 23 and the curved surface 24.

A rotary compressor according to a ninth embodiment of the present invention is shown in FIGS.
17 is a longitudinal sectional view of the rotary compressor, FIG. 18 is a sectional view taken along the line C--C in FIG. 17, FIG. 19 is an enlarged view of an essential part of FIG. 18, and FIG. 20 is a perspective view showing an essential part of the rotary compressor FIG. 21 is a cross-sectional view of an essential part of a cylinder of the rotary compressor. The same members as those of the first embodiment are indicated by the same reference numerals and the description thereof is omitted.

As shown in FIG. 17, in the present embodiment, at the upper end of the lower bearing 6, a notch 20J described later is formed.
As shown in FIGS. 19 and 20, the notch 20J has one end 21 thereof in the blade slide groove 12 and the other end 22 in the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4 It is located in.
Further, as shown in FIGS. 20 and 21, the notch 20J is formed in the lower bearing 6 concentrically with the inner diameter of the cylinder 4 along the inner circumferential surface 4 a forming the cylinder chamber 8.
The refrigerant gas flows into the minute gap 8a shown in FIG. 19 from the suction chamber in which the suction hole 9 is opened by the cutout portion 20J, and the vacuum state is not established.
When the other end 22 of the notch 20J does not reach within the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, a slight vacuum state occurs. Therefore, it is preferable that the other end 22 of the notch 20J be within the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4. On the other hand, when the other end 22 of the notch 20J exceeds the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, the compression stroke is reduced and the compression ratio is reduced. Therefore, it is preferable that the other end 22 of the notch 20J does not exceed the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4.

As shown in FIG. 21, the notch 20 </ b> J is formed by providing a groove in a part of the upper end surface 6 a of the lower bearing 6. The notch 20J shown in FIG. 21 is formed on the upper end surface 6a by a concave portion of the flat bottom surface 25.
When the height of the cylinder 4 (the axial direction of the crankshaft 3) is H, the height of the notch 20J is h, and the depth of the notch 20J is b, as shown in FIG. The height h of 20J is preferably 1 / 7H to 1 / 3H, and the depth b of the notch 20J is preferably 1 / 7H to 1 / 3H.
If the height h of the notched portion 20J exceeds 1 / 3H, processing takes time to deteriorate productivity, and if the height h of the notched portion 20J is less than 1 / 7H, the refrigerant gas passage narrows. Due to pressure loss, the refrigerant gas can not be supplied sufficiently. The depth b of the notch 20J is preferably equal to or greater than the height h of the notch 20J, so 1 / 7H or more is preferable, and when the depth b of the notch 20J exceeds 1 / 3H Unpreferable for practical use.

A rotary compressor according to a tenth embodiment of the present invention is shown in FIG.
The present embodiment is the same as the ninth embodiment except for the case described in FIG. 22, and therefore, the description of FIGS. 17 to 20 described in the ninth embodiment will be omitted.
As shown in FIG. 22, also in the present embodiment, the notch 20K is formed by providing a groove in a part of the upper end surface 6 a of the lower bearing 6. The notch 20K shown in FIG. 22 is formed by the concave portion of the curved surface 26 on the upper end face 6a.
Also in the present embodiment, the height h of the notch 20K is preferably 1 / 7H to 1 / 3H, and the depth b of the notch 20K is 1 / 7H to 1 / 3H. Is preferred.
In the case where the height h and the depth b are the same between the notch 20J of the ninth embodiment and the notch 20K of the tenth embodiment, the ninth embodiment is used. The cutaway portion 20J is preferable because the passage cross-sectional area is larger and a smooth refrigerant gas flow is generated.

The rotary compressor according to an eleventh embodiment of the present invention is shown in FIGS.
23 is a longitudinal sectional view of the rotary compressor, FIG. 24 is a sectional view taken along the line DD in FIG. 23, FIG. 25 is an enlarged view of an essential part of FIG. 24, and FIG. 26 is a perspective view showing an essential part of the rotary compressor FIG. 27 is a cross-sectional view of an essential part of a cylinder of the rotary compressor. The same members as those of the first embodiment are indicated by the same reference numerals and the description thereof is omitted.
As shown in FIG. 23, in the present embodiment, at the lower end of the upper bearing 5, a notch 20L described later is formed.
As shown in FIGS. 25 and 26, the notch 20L has one end 21 in the blade slide groove 12 and the other end 22 in the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4 It is located in.
Further, as shown in FIGS. 26 and 27, the notch 20L is formed on the upper bearing 5 concentrically with the inner diameter of the cylinder 4 along the inner circumferential surface 4a forming the cylinder chamber 8.
The refrigerant gas flows into the minute gap 8a shown in FIG. 25 from the suction chamber in which the suction hole 9 is opened by the cutout portion 20L, and the vacuum state is not established.
When the other end 22 of the notch 20L does not reach within the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, a slight vacuum state occurs. Therefore, it is preferable that the other end 22 of the notch 20L be within the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4. On the other hand, when the other end 22 of the notch 20L exceeds the projection range X of the suction hole 8 onto the inner peripheral surface 4a of the cylinder 4, the compression stroke is reduced and the compression ratio is reduced. Therefore, it is preferable that the other end 22 of the notch 20L does not exceed the projection range X of the suction hole 8 on the inner peripheral surface 4a of the cylinder 4.

As shown in FIG. 27, the notch 20 </ b> L is formed by providing a groove in a part of the lower end surface 5 a of the upper bearing 5. The notch 20L shown in FIG. 27 is formed on the lower end surface 5a by a concave portion of the flat bottom surface 25.
Further, as shown in FIG. 27, when the height of the cylinder 4 (the axial direction of the crankshaft 3) is H, the height of the notch 20L is h, and the depth of the notch 20L is b, the notch The height h of 20 L is preferably 1/7 H or more and 1/3 H or less, and the depth b of the notch 20 L is preferably 1/7 H or more and 1/3 H or less.
If the height h of the notch 20L exceeds 1 / 3H, processing takes time to deteriorate productivity, and if the height h of the notch 20L is less than 1 / 7H, the refrigerant gas passage narrows Due to pressure loss, the refrigerant gas can not be supplied sufficiently. The depth b of the notch 20L is preferably equal to or greater than the height h of the notch 20L, so 1 / 7H or more is preferable, and if the depth b of the notch 20L exceeds 1 / 3H Unpreferable for practical use.

A rotary compressor according to a twelfth embodiment of the present invention is shown in FIG.
The present embodiment is the same as the eleventh embodiment except that it is described in FIG. 28, so that the description of FIGS. 23 to 27 described in the eleventh embodiment is omitted.
As shown in FIG. 28, also in the present embodiment, the notch 20M is formed by providing a groove in a part of the lower end surface 5 a of the upper bearing 5. The notch 20M shown in FIG. 28 is formed by the concave portion of the curved surface 26 on the lower end surface 5a.
Also in the present embodiment, the height h of the notch 20M is preferably 1 / 7H to 1 / 3H, and the depth b of the notch 20M is 1 / 7H to 1 / 3H. Is preferred.
The eleventh embodiment is the case where the height h and the depth b are the same between the notch 20L of the eleventh embodiment and the notch 20M of the twelfth embodiment. The notch 20L is preferable because the passage cross-sectional area is larger and a smooth refrigerant gas flow is generated.

As described above, the rotary compressor according to the present invention can be used as a high efficiency compressor for air conditioning, and can be used as a substitute refrigerant for all HCFCs 22 such as R407C regardless of R410A as the refrigerant used. The present invention can also be applied to natural refrigerants such as carbon dioxide, ammonia, and helium, which are attracting attention from the viewpoint of global environmental protection.

Claims

A cylinder chamber is formed in the cylinder,
The cylinder chamber is closed by an upper bearing and a lower bearing,
A roller is disposed in the cylinder chamber,
A blade slide groove is formed in the cylinder,
A blade and a spring are disposed in the blade sliding groove,
The blade is pressed against the outer peripheral surface of the roller by the spring;
A rotary compressor in which the cylinder chamber is divided by the blade into a high pressure side compression chamber and a low pressure side compression chamber in which a suction hole is opened,
A rotary compressor characterized in that one end is positioned in the blade slide groove and the other end is positioned within a projection range of the suction hole on the inner peripheral surface of the cylinder.
The rotary compressor according to claim 1, wherein the cutaway portion is formed at a corner portion where an inner peripheral surface forming the cylinder chamber and an upper end surface of the cylinder on which the upper bearing abuts contact with each other. .
The rotary compressor according to claim 1, characterized in that the cutaway portion is formed at an angle portion where an inner peripheral surface forming the cylinder chamber and a lower end surface of the cylinder which the lower bearing abuts contact with each other. .
The said notch part was formed by the flat inclined surface, The rotary compressor of Claim 2 or Claim 3 characterized by the above-mentioned.
The said notch part was formed by the curved surface, The rotary compressor of Claim 2 or Claim 3 characterized by the above-mentioned.
The rotary compressor according to claim 2 or 3, wherein the cutout portion is formed by a plurality of inclined surfaces having different angles.
The said notch part was formed of the flat inclined surface and the curved surface, The rotary compressor of Claim 2 or Claim 3 characterized by the above-mentioned.
Assuming that the height of the cylinder is H, the height of the cutout is h, and the depth of the cutout is b, the height h of the cutout is 1 / 7H to 1 / 5H. The rotary compressor according to any one of claims 1 to 7, wherein a depth b of the cutout portion is set to 1 / 7H or more and 1 / 3H or less.
2. The rotary compressor according to claim 1, wherein the notch portion is formed by providing a groove along an inner circumferential surface forming the cylinder chamber on an upper end surface of the lower bearing.
2. The rotary compressor according to claim 1, wherein the cutaway portion is formed by providing a groove along an inner peripheral surface forming the cylinder chamber on a lower end surface of the upper bearing.
The rotary compressor according to claim 8 or 9, wherein the cutaway portion is formed by a recess of a flat bottom surface.
10. The rotary compressor according to claim 8, wherein the cutaway portion is formed by a concave portion of a curved surface.
Assuming that the height of the cylinder is H, the height of the cutout is h, and the depth of the cutout is b, the height h of the cutout is 1 / 7H to 1 / 3H. The rotary compressor according to any one of claims 9 to 12, wherein a depth b of the cutout portion is set to 1 / 7H or more and 1 / 3H or less.