EP0541801B1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
EP0541801B1
EP0541801B1 EP91910170A EP91910170A EP0541801B1 EP 0541801 B1 EP0541801 B1 EP 0541801B1 EP 91910170 A EP91910170 A EP 91910170A EP 91910170 A EP91910170 A EP 91910170A EP 0541801 B1 EP0541801 B1 EP 0541801B1
Authority
EP
European Patent Office
Prior art keywords
roller
grooves
bearing
generated
shaft
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP91910170A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0541801A1 (en
EP0541801A4 (fi
Inventor
Takao Yoshimura
Ichiro Morita
Hideharu Ogahara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
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 Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Publication of EP0541801A1 publication Critical patent/EP0541801A1/en
Publication of EP0541801A4 publication Critical patent/EP0541801A4/en
Application granted granted Critical
Publication of EP0541801B1 publication Critical patent/EP0541801B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids

Definitions

  • the present invention relates to a rotary compressor which is for use in the refrigerating cycle of a refrigerator or freezer and which is provided with a compression mechanical portion having an excellent volumeric efficiency.
  • the rotary compressor has a drawback in that the motion of a roller is unstable because the direction of the rotation thereof on its own axis changes during a single rotation thereof, deteriorating the volumeric efficiency thereof.
  • Reference numeral 1 denotes a sealed casing and 2 denotes an electric motor portion which is coupled, through a shaft 3, to a mechanical portion body 9 including a cylinder 4, a roller 5, a vane 6, a main bearing 7 and a sub bearing 8.
  • the shaft 3 has a main shaft 3a, a sub shaft 3b and a crank 3c which is eccentric from the axis of the main and sub shafts 3a and 3b by E.
  • the shaft 3 has a hole 3e at the center thereof, and the crank 3c has an oil supplying hole 3f and an oil supplying groove 3g.
  • Reference numeral 10 denotes a spring provided on the rear surface of the vane, and 11a and 11b respectively denote a suction chamber and a compression chamber formed within the cylinder 4 by the roller 5, the vane 6 and the main and sub bearings 7 and 8.
  • the inner peripheral sides of end surfaces 5a and 5b of the roller 5 which respectively face the main and sub bearings 7 and 8 are tapered to form tapered portions 5c and 5d whose cross-sectional area decreases toward the outer peripheral side thereof.
  • Reference numeral 12 denotes an oil supplying mechanism coupled to the shaft 3.
  • Reference numeral 13 denotes a suction pipe which communicates with the suction chamber 11a via a suction passage 14 formed in the sub bearing 8 and the cylinder 4.
  • 15 denotes a discharge hole which communicates with the interior of the sealed casing via a discharge valve 16.
  • 17 denotes a discharge pipe which is opened into the sealed casing 1.
  • 18 denotes a lubricating oil.
  • the arrow of the solid line indicates the direction of the motion of the roller 5 which is obtained at a certain time during the operation of the compressor
  • the arrow of the broken line indicates the direction in which the lubricating oil 18 flows over the end surfaces 5a and 5b of the roller as a consequence of the operation of the roller 5.
  • Reference numeral 5e denotes a portion of the tapered portion 5c or 5d of the roller 5 whose cross-sectional area gradually decreases in the direction indicated by the arrow of the broken line
  • 5f denotes a portion whose cross-sectional area gradually increases in the same direction.
  • a refrigerant gas supplied from a cooling system passes through the suction pipe 13 and the suction hole 14, and then reaches the suction chamber 11a of the cylinder 4. Thereafter, the refrigerant gas is gradually compressed by the rotary motion of the shaft 3 which is generated by the rotation of the electric motor portion 2 in the compression chamber 11b defined by the roller 5 rotatably supported by the crank 3c of the shaft 3 and the vane 6.
  • the compressed refrigerant gas is discharged into the interior of the sealed casing 1 through the discharge hole 15 and the discharge valve 16, and then discharged into the cooling system through the discharge pipe 17.
  • the high-pressure lubricating oil 18 with the refrigerant contained therein and contained in the sealed casing 1 is supplied to the hole 3e of the shaft 3 by means of the oil supplying mechanism 12. Thereafter, the lubricating oil 18 is supplied to the sliding portion of the main and sub bearings 7 and 8 and to the crank 3c and the inner peripheral side of the roller 5 from the oil supplying hole 3f and the oil supplying groove 3g to lubricate the roller end surfaces 5a and 5b. Subsequently, the lubricating oil 18 passes through the suction chamber 11a and the compression chamber 11b, is discharged into the sealed casing 1 from the discharge hole 15, and then stays at the bottom of the sealed casing 1.
  • the roller 5 rotates while turning round about the crank 3c in either of two directions. Consequently, the locus of a certain point on the roller 5 is spiral, and the direction of the movement of the roller 5 changes about 360° while the shaft 3 is rotated. Assuming that the direction of the spiral motion of the roller 5 is that indicated by the arrow in Fig. 4, since the tapered portions 5c and 5d are provided on the end surfaces 5a and 5b of the roller 5 and the cross-section of the portion 5e gradually decreases toward the outer diameter side of the roller, only the lubricating oil 18 which flows into the vicinity of the portion 5e in the tapered portion 5c or 5e generates an oil pressure due to the wedge effect.
  • Such a compressor is disclosed in, for example, Japanese Utility Model Publication No. 61-20317.
  • the above-described structure utilises the wedge effect of the lubricating oil which enters the tapered portion.
  • This wedge effect is generated by the component of the roller rotation in the spiral motion thereof caused by the rotation of the shaft and not generated by the component of the roller rotation about the crank, because the cross-sectional area of the tapered portion remains the same in the circumferential direction, and is thus low.
  • the oil pressure is generated at most of the portion of the end surface.
  • the tapered portion has a shape which continues in the circumferential direction, the pressure generated by the wedge effect may escape in the circumferential direction, reducing the pressure generated by the wedge effect. Therefore, the stability of the roller achieved by the wedge effect is not sufficient, and the improvement in the volumetric efficiency is low.
  • GB 2 012 874A discloses a rotary compressor of a similar type to that of Japanese Utility Model Publication No. 61-20317, although the vanes of the compressor of GB 2 012 874A reciprocatively slide within grooves provided in the roller rather than grooves provided in the cylinder.
  • the rotary compressor of this disclosure goes some way to obviating the abovementioned problem by providing grooves in end surfaces of the roller which face the main bearing and the sub-bearing.
  • the grooves are, however, of a generally open form.
  • US 4 402 653 also discloses a rotary compressor of a similar type to that of both JP-61-20317 and GB 2 012 874A although the roller is made fast with the shaft and, as in the compressor of GB 2 012 874A, its vanes reciprocatively slide in grooves provided in the roller rather than the cylinder.
  • the rotary compressor of this disclosure goes some way to obviating the aforementioned problem by providing grooves in an end surface of each of the main bearing and the sub-bearing.
  • the grooves are of a generally open form.
  • a primary object of the present invention is to stabilise the motion of a roller and thereby improve the volumetric efficiency of the compressing mechanism portion.
  • a secondary object of the present invention is to minimise the amount of lubricating oil with a refrigerant contained therein which flows into a suction chamber and a compression chamber.
  • a groove in each of end surfaces of the roller which respectively face the main bearing and the sub-bearing, characterised in that the groove provided in each of said end surfaces of said roller has a communicating portion for communicating with an inner peripheral side of said roller and a plurality of sealed portions which continue from said communicating portion and whose cross-sectional area decreases as a distance to said communication portion increases.
  • the objects of the invention are achieved in another embodiment of the invention by providing grooves on an end surface of each of the main bearing and the sub-bearing, characterised in that they are provided in such a manner that a cross-sectional area thereof decreases in radial and circumferential directions and that they face an end surface of said roller at least once during a single rotation of said shaft.
  • Figs. 5 and 6 illustrates a first embodiment of the present invention.
  • Reference numeral 19 denotes a roller which is rotatably retained by the crank 3c of the shaft 3, as in the case of the conventional compressor.
  • the same number of grooves 20 through 27 are formed on end surfaces 19a and 19b of the roller 19.
  • the grooves 20 through 27 are respectively formed by communicating portions 20a through 27a which communicate with the inner peripheral portion of the roller 19, and sealing portions 20b through 27b and 20c through 27c which extend from the communicating portions 20a through 27a in the circumferential direction and whose cross-sectional area decreases as a distance to the communicating portions 20a through 27a increases.
  • the refrigerant gas sucked from the suction pipe 13 is compressed and discharged to the cooling system from the discharge pipe 17 in the same manner as that of the conventional compressor.
  • the high-pressure lubricating oil 18 with the refrigerant contained therein which is contained in the sealed casing 1 lubricates the mechanical portion body 9 in the same manner as that of the conventional compressor.
  • the lubricating oil 18 which flows into the inner peripheral side of the roller 19 lubricates the rollers 19a and 19b, and then returns to the bottom portion of the sealed casing in the same manner as that of the conventional compressor.
  • the roller 19 revolves while turning round about the crank, as in the case of the conventional compressor. As a result, the roller 19 goes on the spiral motion.
  • the direction of the spiral motion which is obtained at a certain instance is indicated by the arrow of the solid line, and the direction in which the lubricating oil 18 flows as a consequence of the motion of the roller 19 is indicated by the arrow of the broken line, as in the case of the conventional compressor.
  • the sealed portions 20c, 21c, 23b, 24b, 25b, 26b, 26c and 27c in the sealed portions 20b through 27b and 20c through 27c reduce their cross-sectional area in the direction of flow of the lubricating oil 18 which is indicated by the arrow of the broken line, generating a pressure of the lubricating oil 18 which flows in from the communicating portions 20a through 27a.
  • the oil pressure is generated at either of or both of the sealed portions 20b through 27b and 20c through 27c, and the positions where the oil pressure is generated are thus distributed over the end surface 19a of the roller 19, unlike the conventional compressor in which the oil pressure is generated at only a single position.
  • the oil pressure occurs in the grooves 20 through 27 formed on the end surface 19b in the same manner as that for the grooves 20 through 27 formed on the end surface 19a: in all the grooves except for the groove 22 located at a position symmetrical with respect to the position of the groove 22 formed on the end surface 19a, the oil pressure is generated at either of or both of the sealed portions 20b through 27b and 20c through 27c, and the positions on the end surface 19b where the oil pressure is generated are symmetrical with respect to the positions on the end surface 19a where the oil pressure is generated.
  • the sealed portions 20b through 27b and 20c trough 27c are formed in such a manner that the cross-sectional area thereof decreases substantially in the circumferential direction, the oil pressure due to the wedge effect is generated in the sealed portions whichever direction the roller 19 is rotated about the crank. Furthermore, since the oil pressure is generated near the sealed portions 20b through 27b and 20c through 20c, it cannot escape from the sealed portions, and the oil pressure is thus increased. Therefore, the same amount of oil pressure is generated on the end surfaces 19a and 19b of the roller 19 over the distributed positions, and the generated oil pressures thus balance.
  • the sealed distance is longer than that obtained when the tapered portions are provided.
  • the amount of lubricating oil which flows into the compression chamber and the suction chamber is reduced, and this makes improvement in the volumeric efficiency possible even in the case of a small compressor in which the thickness of the roller is small.
  • grooves 28 through 35 are formed on the end surfaces 19a and 19b of the roller 19.
  • the grooves 28 through 35 are respectively formed by communicating portions 28a through 35a which communicate with the inner peripheral portion of the roller 19, and sealing portions 28b through 35b, 28c through 35c, 28d through 35d, 28e through 35e and 28f through 35f which extend from the communicating portions 28a through 35a substantially radially and whose cross-sectional area decreases as a distance to the communicating portions 28a through 35a increases.
  • the refrigerant gas sucked from the suction pipe 13 is compressed and discharged to the cooling system from the discharge pipe 17 in the same manner as that of the conventional compressor.
  • the high-pressure lubricating oil 18 with the refrigerant contained therein which is contained in the sealed casing 1 lubricates the mechanical portion body 9 in the same manner as that of the conventional compressor.
  • the lubricating oil 18 which flows into the inner peripheral side of the roller 19 lubricates the rollers 19a and 19b, and then returns to the bottom portion of the sealed casing in the same manner as that of the conventional compressor.
  • the roller 19 revolves while rotating about the crank, as in the case of the conventional compressor.
  • the roller 19 performs the spiral motion.
  • the direction of the spiral motion which is obtained at a certain instance is indicated by the arrow of the solid line, and the direction in which the lubricating oil 18 flows as a consequence of the motion of the roller 19 is indicated by the arrow of the broken line, as in the case of the conventional compressor.
  • a pressure of the lubricating oil 18 which flows in from the communicating portions 28a through 35a is generated at the sealed portions whose cross-sectional area decreases in the direction of flow of the lubricating oil 18 which is indicated by the arrow of the broken line in the sealed portions 28b through 35b, 28c through 35c, 28d through 35d, 28e through 35e and 28f through 35f.
  • an oil pressure is generated at the sealed portions 28e and 28f.
  • an oil pressure is generated at the sealed portions 32c and 32d.
  • the oil pressure is generated at two portions, and the positions where the oil pressure is generated are thus distributed over the end surface 19a of the roller 19, unlike the conventional compressor in which the oil pressure is generated at only a single position.
  • generation of the oil pressure occurs on the end surface 19b in the same manner as that for the end surface 19a. Therefore, the positions on the end surface 19b where the oil pressure is generated are symmetrical with respect to the positions on the end surface 19a where the oil pressure is generated, and the oil pressure generated on the end surfaces 19a and 19b thus balance with each other.
  • the sealed portions 28c through 35c, 28d through 35d, 28e through 35e and 28f through 35f are formed in such a manner that the cross-sectional area thereof decreases substantially in the circumferential direction, the oil pressure due to the wedge effect is generated in these sealed portions whichever direction the roller 19 is rotated about the crank. Furthermore, since the oil pressure is generated near the sealed portions 28b through 35b, 28c through 35c, 28d through 35d, 28e through 35e and 28f through 35f, it cannot escape from the sealed portions, and the oil pressure is retained high.
  • the same amount of oil pressure is generated on the end surfaces 19a and 19b of the roller 19 over the distributed positions, and the generated oil pressures thus balance.
  • the sealed distance is longer than that obtained when the tapered portions are provided.
  • the amount of lubricating oil which flows into the compression chamber and the suction chamber is reduced, and this makes an improvement in the volumeric efficiency possible even in the case of a small compressor in which the thickness of the roller is small.
  • Grooves 37 through 44 are formed in each of the end surfaces 36a and 36b of the roller 36.
  • communicating portions 37a through 44a are formed in such a manner that they pass the inner peripheral portion of the roller 36 and the grooves 37 through 44, and sealed portions 37b through 44b, 37c through 44c, 37d through 44d, 37e through 44e and 37f through 44f are formed radially from portions of the communicating portion 37a through 44a which open into the grooves 37 through 44.
  • an oil pressure is generated due to the spiral motion of the roller at the sealed portions 37b through 44f, as in the cases of the previously described embodiments.
  • Reference numerals 45 and 46 respectively denote a main bearing and a sub bearing which rotatably support the shaft 3 in the same manner as that of the conventional compressor.
  • Reference numeral 47 designates a roller which is rotatably retained on the crank 3c of the shaft 3.
  • the same number of grooves 48 through 55 are formed in the main and sub bearings 45 and 46.
  • Each of the grooves 48 through 55 has a shape in which the cross-sectional area thereof is the largest at the center thereof and decreases in the circumferential and radial directions.
  • Fig. 11 dot-dot-dashed lines indicate the inner peripheral surface of the cylinder 4, the vane 6 and the roller 47.
  • Fig. 11 shows the positions relation between the grooves 48 through 55 and the roller 47 which is obtained at a certain rotational position.
  • Figs. 13 and 14 show the positional relation between the grooves 48 through 55 and the roller 47.
  • the grooves 48 through 55 should have a hidden outline, they are indicated by the solid line for the ease of understanding.
  • the refrigerant gas sucked from the suction pipe 13 is compressed and discharged to the cooling system from the discharge pipe 17 in the same manner as that of the conventional compressor.
  • the high-pressure lubricating oil 18 with the refrigerant contained therein which is contained in the sealed casing 1 lubricates the mechanical portion body 9 in the same manner as that of the conventional compressor.
  • the lubricating oil 18 which flows into the inner peripheral side of the roller 19 lubricates the rollers 19a and 19b, and then returns to the bottom portion of the sealed casing in the same manner as that of the conventional compressor.
  • the grooves 50, 51, 52 and 53 in the grooves 48 through 55 of the main bearing 45 are sealed by the end surface of the roller 47.
  • the grooves 48 through 55 of the sub bearing 46 are also sealed similarly. Since the grooves 48 through 55 have a shape in which the cross-sectional area thereof is the largest at the central portion thereof and decreases in the radial and circumferential directions, when the lubricating oil moves within the sealed grooves 50 through 53 in the direction indicated by the solid line, an oil pressure is generated in the grooves 50 through 53.
  • the positions where the oil pressure is generated in the grooves 50 through 53 are symmetrical. That is, in this embodiment, the oil pressure is generated on each of the two end surfaces of the roller 47 at four positions, and the oil pressure generated on one of the end surfaces balances the oil pressure generated on the other end surface.
  • the grooves 48 and 55 are formed in such a manner that the cross-sectional area thereof decreases in the circumferential direction, the oil pressure is generated in the sealed grooves 50 through 53 due the wedge effect whichever direction the roller rotates about the crank.
  • the grooves 48 through 55 are formed separately, the oil pressure generated in the sealed grooves 50 through 53 cannot escape from the sealed grooves, and the oil pressure is thus retained high.
  • the same amount of oil pressure is generated on the end surfaces of the roller 47 over the distributed positions, and the generated oil pressures thus balance.
  • the roller 47 faces only part of the grooves 48 through 55, the sealed distance is longer than that obtained when the tapered portion is provided. Consequently, the amount of lubricating oil which flows into the compression chamber is reduced, and this makes an improvement in the volumeric efficiency possible even in the case of a compressor in which the thickness of the roller is small.
  • the sealed portions of the lubricating oil and the communicating portions which communicate with the inner peripheral surface of the roller are formed in the contact surfaces between the roller and the main and sub bearings, the same amount of oil pressure can be generated over the distributed positions and the generated oil pressures thus balance.
  • the rotary compressor is employed in a refrigerating cycle which is for use in, for example, a refrigerator or a freezer, the performance of the refrigerating cycle can be improved because the motion of the roller is stabilized and the volumeric efficiency is thus improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP91910170A 1991-05-30 1991-05-30 Rotary compressor Expired - Lifetime EP0541801B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1991/000725 WO1992021881A1 (fr) 1991-05-30 1991-05-30 Compresseur rotatif

Publications (3)

Publication Number Publication Date
EP0541801A1 EP0541801A1 (en) 1993-05-19
EP0541801A4 EP0541801A4 (fi) 1995-04-19
EP0541801B1 true EP0541801B1 (en) 1997-03-05

Family

ID=14014435

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91910170A Expired - Lifetime EP0541801B1 (en) 1991-05-30 1991-05-30 Rotary compressor

Country Status (5)

Country Link
EP (1) EP0541801B1 (fi)
BR (1) BR9106801A (fi)
CA (1) CA2088160C (fi)
DE (1) DE69125008T2 (fi)
WO (1) WO1992021881A1 (fi)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108105094B (zh) * 2017-12-07 2023-10-03 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的换热设备

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5470809A (en) * 1977-11-16 1979-06-07 Nippon Denso Co Ltd Emergency sound information reader
JPS56106088A (en) * 1980-01-29 1981-08-24 Matsushita Electric Ind Co Ltd Rotary type fluid equipment
JPS56135780A (en) * 1980-03-27 1981-10-23 Matsushita Electric Ind Co Ltd Compressor

Also Published As

Publication number Publication date
EP0541801A1 (en) 1993-05-19
WO1992021881A1 (fr) 1992-12-10
DE69125008D1 (de) 1997-04-10
EP0541801A4 (fi) 1995-04-19
CA2088160A1 (en) 1992-12-01
DE69125008T2 (de) 1997-08-28
BR9106801A (pt) 1994-01-25
CA2088160C (en) 1995-04-04

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