WO2011105085A1 - ロータリー圧縮機 - Google Patents

ロータリー圧縮機 Download PDF

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Publication number
WO2011105085A1
WO2011105085A1 PCT/JP2011/001054 JP2011001054W WO2011105085A1 WO 2011105085 A1 WO2011105085 A1 WO 2011105085A1 JP 2011001054 W JP2011001054 W JP 2011001054W WO 2011105085 A1 WO2011105085 A1 WO 2011105085A1
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WO
WIPO (PCT)
Prior art keywords
rotary compressor
notch
cylinder
blade
height
Prior art date
Application number
PCT/JP2011/001054
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
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 (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to CN2011800012075A priority Critical patent/CN102333957A/zh
Priority to JP2011525056A priority patent/JPWO2011105085A1/ja
Publication of WO2011105085A1 publication Critical patent/WO2011105085A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the present invention relates to a rotary compressor.
  • FIG. 1 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 Conventional rotary compressor Conventional rotary compressor Conventional rotary compressor Conventional
  • 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.
  • 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.
  • 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.
  • the notch portion is formed by a flat inclined surface, which facilitates the processing of the notch portion.
  • 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.
  • the notch may be formed by a plurality of inclined surfaces having different angles.
  • the notch may be formed by a flat inclined surface and a curved surface.
  • 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.
  • 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.
  • the notch portion is formed by the recess on the flat bottom surface, so that the notch portion can be easily processed.
  • 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.
  • the height of the cylinder is H
  • the height of the cutout is h
  • the depth of the cutout is b
  • 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
  • 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.
  • 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.
  • a compression mechanism constituted by the cylinder 4, the upper bearing 5, the lower bearing 6, and the roller 7 is provided 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.
  • a notch 20A described later is formed at the upper end of the inner circumferential surface of the cylinder 4, a notch 20A described later is formed.
  • a mixed refrigerant of HFC32 and HFC125, or a natural refrigerant such as carbon dioxide, ammonia, or helium can be used as a refrigerant.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the height of the cylinder 4 (the axial direction of the crankshaft 3) is H
  • the height of the notch 20A is h
  • the depth of the notch 20A is b
  • the height h of 20A is preferably 1 / 7H to 1 / 5H
  • the depth b of the notch 20A is preferably 1 / 7H to 1 / 3H.
  • 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.
  • FIG. 6 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.
  • 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.
  • 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.
  • 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.
  • FIG. 7 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.
  • 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.
  • 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.
  • the notch 20C may be formed by two flat inclined surfaces 23a and 23b having different angles.
  • FIG. 8 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.
  • 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.
  • 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.
  • the notch 20D may be formed by the flat inclined surface 23 and the curved surface 24.
  • 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
  • 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.
  • a notch 20E described later is formed at the lower end of the inner peripheral surface of the cylinder 4.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the notch The height h of 20E is preferably 1 / 7H to 1 / 5H
  • the depth b of the notch 20E is preferably 1 / 7H to 1 / 3H.
  • 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.
  • FIG. 14 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.
  • 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.
  • 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.
  • 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.
  • FIG. 15 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.
  • 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. 15 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.
  • the notch 20G is formed by notching the corner where the inner circumferential surface 4a and
  • 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.
  • 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.
  • 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.
  • 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.
  • the notch 20H may be formed by the flat inclined surface 23 and the curved surface 24.
  • 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,
  • 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.
  • a notch 20J described later is formed at the upper end of the lower bearing 6, a notch 20J described later is formed.
  • 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.
  • 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.
  • the other end 22 of the notch 20J 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.
  • 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.
  • the height of the cylinder 4 (the axial direction of the crankshaft 3) is H
  • the height of the notch 20J is h
  • the depth of the notch 20J is b
  • the height h of 20J is preferably 1 / 7H to 1 / 3H
  • the depth b of the notch 20J is preferably 1 / 7H to 1 / 3H.
  • 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.
  • FIG. 22 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.
  • 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.
  • the height h of the notch 20K is preferably 1 / 7H to 1 / 3H
  • the depth b of the notch 20K is 1 / 7H to 1 / 3H.
  • 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.
  • 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,
  • 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.
  • FIG. 23 in the present embodiment, at the lower end of the upper bearing 5, a notch 20L described later is formed.
  • 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
  • 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
  • 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.
  • the other end 22 of the notch 20L 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.
  • 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.
  • 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.
  • 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.
  • FIG. 28 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.
  • 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2011/001054 2010-02-24 2011-02-24 ロータリー圧縮機 WO2011105085A1 (ja)

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JP2017053361A (ja) * 2016-12-21 2017-03-16 株式会社富士通ゼネラル ロータリ圧縮機
JP7462579B2 (ja) 2021-01-12 2024-04-05 三菱電機株式会社 圧縮機、空気調和機、圧縮機の製造方法および空気調和機の製造方法

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CN105443392A (zh) * 2016-01-21 2016-03-30 珠海格力节能环保制冷技术研究中心有限公司 压缩机及其气缸总成
CN107191380B (zh) * 2017-07-28 2021-02-12 广东美芝制冷设备有限公司 压缩机构及具有其的压缩机

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JPH0214492U (zh) * 1988-07-12 1990-01-30
JPH05202875A (ja) * 1992-01-29 1993-08-10 Hitachi Ltd ロータリ圧縮機
JP2002188587A (ja) * 2000-12-20 2002-07-05 Fujitsu General Ltd ロータリ圧縮機
JP2008038697A (ja) * 2006-08-03 2008-02-21 Mitsubishi Electric Corp 多段回転式圧縮機
JP2010121546A (ja) * 2008-11-20 2010-06-03 Hitachi Appliances Inc ロータリ圧縮機

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JPH11141481A (ja) * 1997-11-06 1999-05-25 Sanyo Electric Co Ltd 回転式圧縮機
JPH11270480A (ja) * 1998-03-23 1999-10-05 Sanyo Electric Co Ltd 密閉型回転式圧縮機
CN201288665Y (zh) * 2008-09-18 2009-08-12 珠海格力电器股份有限公司 旋转式压缩机气缸

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JPH0214492U (zh) * 1988-07-12 1990-01-30
JPH05202875A (ja) * 1992-01-29 1993-08-10 Hitachi Ltd ロータリ圧縮機
JP2002188587A (ja) * 2000-12-20 2002-07-05 Fujitsu General Ltd ロータリ圧縮機
JP2008038697A (ja) * 2006-08-03 2008-02-21 Mitsubishi Electric Corp 多段回転式圧縮機
JP2010121546A (ja) * 2008-11-20 2010-06-03 Hitachi Appliances Inc ロータリ圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017053361A (ja) * 2016-12-21 2017-03-16 株式会社富士通ゼネラル ロータリ圧縮機
JP7462579B2 (ja) 2021-01-12 2024-04-05 三菱電機株式会社 圧縮機、空気調和機、圧縮機の製造方法および空気調和機の製造方法

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