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EP1239158A2 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP1239158A2
EP1239158A2 EP02004861A EP02004861A EP1239158A2 EP 1239158 A2 EP1239158 A2 EP 1239158A2 EP 02004861 A EP02004861 A EP 02004861A EP 02004861 A EP02004861 A EP 02004861A EP 1239158 A2 EP1239158 A2 EP 1239158A2
Authority
EP
European Patent Office
Prior art keywords
scroll
base plate
wall
movable
distal end
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.)
Withdrawn
Application number
EP02004861A
Other languages
German (de)
English (en)
Inventor
Tatsushi Mori
Masao Iguchi
Shinsuke Asou
Yoshio Fujita
Yoshiharu Yoshida
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1239158A2 publication Critical patent/EP1239158A2/fr
Withdrawn legal-status Critical Current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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps

Definitions

  • the present invention relates to a scroll type compressor and more particularly to structure of a fixed scroll member and a movable scroll member which constitute a compression mechanism in a volute shape.
  • the scroll type compressor has a housing in which the fixed scroll member and the movable scroll member are provided.
  • the fixed scroll member has a fixed scroll base plate and a fixed scroll wall that extends from the fixed scroll base plate.
  • the movable scroll member has a movable scroll base plate and a movable scroll wall that extends from the movable scroll base plate. Each scroll wall is engaged with each other.
  • the fixed scroll member and the movable scroll member cooperatively form a plurality of compression chambers as a compression region. As the movable scroll member orbits about an axis of the fixed scroll member, the compression chambers move radially inward while their volume decreases.
  • a scroll wall 1 was conventionally created in a taper shape from a joining portion to a base plate 2 toward a distal end of the scroll wall 1.
  • the scroll wall 1 is strengthened against bending moment. Therefore, clearance between the scroll walls 1 was effectively restrained from increasing.
  • a tip seal 3 slides the surface of the opposing base plate 2 to ensure sealing performance in the clearance between the distal end of the scroll wall 1 and the opposing base plate 2.
  • the compressor including the scroll wall 1 shown in FIG. 4A has less capacity in the compression chambers than that of FIG. 4B, because of an increase in thickness of the scroll wall 1 provided with the tip seal 3.
  • the configuration of the compressor is inevitably increased in size.
  • the present invention addresses a scroll type compressor which is hard, compact and lightweight with high quality sealing performance.
  • a scroll type compressor has a fixed scroll member and a movable scroll member.
  • the fixed scroll member has a fixed scroll base plate and a fixed scroll wall extending from the fixed scroll base plate.
  • the movable scroll member has a movable scroll base plate and a movable scroll wall extending from the movable scroll base plate.
  • the fixed scroll member and the movable scroll member cooperatively form a compression region.
  • the movable scroll member orbits relative to the fixed scroll member to compress refrigerant in the compression region.
  • Each scroll wall is formed in a taper shape from each base plate toward each distal end of the scroll wall. The distal end is non-contact with the opposing scroll base plate. Clearance between the distal end and the opposing scroll base plate is less than or equal to the limit clearance value which maintains airtight performance between the distal end and the opposing scroll base plate.
  • a front housing 30, a center housing 31 and a rear housing 32 are connected to form a configuration of the compressor.
  • a fixed scroll member 35 is integrally formed with the center housing 31.
  • the fixed scroll member 35 has a fixed scroll base plate 33 and a fixed scroll wall 34 that extends from the fixed scroll base plate 33.
  • An inlet 36 for introducing refrigerant is also formed in the center housing 31 and is connected to an external refrigerant circuit.
  • a movable scroll member 39 is accommodated in a space defined by the center housing 31 and the front housing 30.
  • the movable scroll member 39 has a movable scroll base plate 37 and a movable scroll wall 38 that extends from the movable scroll base plate 37.
  • the fixed scroll wall 34 and the movable scroll wall 38 engage with each other.
  • a plurality of compression chambers 40 is defined as a compression region between the fixed scroll member 35 and the movable scroll member 39.
  • a discharge hole 42 is formed substantially at the center of the fixed scroll base plate 33. Compressed refrigerant in the compression chambers 40 is discharged into a discharge chamber 41 defined between the center housing 31 and the rear housing 32 through the discharge hole 42.
  • An outlet 43 is formed in the rear housing 32 to flow refrigerant in the discharge chamber 41 into the external refrigerant circuit.
  • one end of a drive shaft 45 is rotatably supported in the front housing 30 by bearing 44 and the other end of the drive shaft 45 extends outside of the configuration of the compressor.
  • a crankshaft 46 is mounted on one end of the drive shaft 45.
  • the crankshaft 46 is received by a bushing 47, which is inserted in a boss 48 of the movable scroll member 39.
  • a self rotation preventing mechanism 49 prevents the movable scroll member 39 from rotating about its axis, while allowing the movable scroll member 39 to orbit about an axis of the fixed scroll member 35.
  • the fixed scroll wall 34 and the movable scroll wall 38 are respectively formed in a taper shape from portions joining to the scroll base plates 33 and 37 toward the respective distal ends.
  • the fixed scroll wall 34 has a pair of side surfaces 34a and 34b which incline by angles of ⁇ 1 and ⁇ 2 with respect to the direction of an axis of the drive shaft 45 (which is perpendicular to the scroll base plates 33 and 37), respectively.
  • the movable scroll wall 38 has a pair of side surfaces 38a and 38b which incline by angles of ⁇ 3 and ⁇ 4 with respect to the direction of the axis of the drive shaft 45 (which is perpendicular to the scroll base plates 33 and 37), respectively.
  • the side surfaces 34b and 38a which face each other are equal in inclination angle. That is, ⁇ 2 equals ⁇ 3 .
  • the side surfaces 34a and 38b which face each other are also equal in inclination angle. That is, ⁇ 1 equals ⁇ 4 .
  • ⁇ 1 equals ⁇ 2 .
  • ⁇ 3 also equals ⁇ 4 .
  • the fixed scroll wall 34 and the movable scroll wall 38 are equal in inclination angle.
  • the above inclination angle is formed not only by cutting but also by utilizing a draft upon casting.
  • the value of x-axis represents length of clearance G 1 and G 2 in the direction of the axis expressed by unit of micrometer or ⁇ m and the value of y-axis represents a ratio of Coefficient of Performance or COP of a compressor according to the present invention, which is not provided with the tip seal, to that of a compressor which is provided with the tip seal.
  • the length of the clearance represents distance between the distal end of the scroll wall and the opposing surface of the scroll base plate.
  • efficiency of load L which is required due to a heat absorption in an evaporator is generally expressed by COP as follows.
  • COP Q er /L, where Q er denotes efficiency of refrigeration.
  • the ratio of COP is allowable if it is more than or equal to 0.9.
  • FIG. 3 reads that the length of the clearance is less than or equal to 60 ⁇ m.
  • FIG. 3 reads that the length of the clearance is less than or equal to 47 ⁇ m. Accordingly, it is required that the clearance G 1 and G 2 are each less than or equal to the above upper limit value.
  • the fixed scroll wall 34 and the movable scroll wall 38 are respectively formed in a taper shape from the portions joining to the scroll base plates 33 and 37 toward the respective distal ends, while having relatively sufficient thickness of the portions. Accordingly, the fixed scroll wall 34 and the movable scroll wall 38 are restrained from being deformed, thus effectively maintaining a sealing performance therebetween.
  • the ratio of COP is more than or equal to 1.
  • the ratio of COP is also more than or equal to 1.
  • the thickness of the distal ends of the scroll walls 34 and 38 is prevented from inevitably increasing by providing the tip seal. Accordingly, the thickness of the scroll wall is determined to be minimized. In spite of the relatively sufficient thickness of the joint portion, the configuration of the compressor is not increased in size.
  • the side surface 34a of the scroll wall 34 and the side surface 38b of the scroll wall 38 facing each other are equal in inclination angle.
  • the side surface 34b of the scroll wall 34 and the side surface 38a of the scroll wall 38 facing each other are equal in inclination angle. Therefore, airtight constitution in the compression region is easily obtained by a draft upon casting.
  • the side surfaces 34a and 34b of the scroll wall 34 are each equal in inclination angle.
  • the side surfaces 38a and 38b of the scroll wall 38 are equal in inclination angle.
  • these side surfaces 34a, 34b, 38a and 38b are each set to be equal in inclination angle even between the scroll members 35 and 39, molding for casting is easily manufactured.
  • a scroll type compressor according to a second preferred embodiment of the present invention will be described with reference to FIG. 2.
  • the side surfaces 34a, 34b of the scroll wall 34 are different in inclination angle.
  • the side surfaces 38a, 38b of the scroll wall 38 are different in inclination angle. That is, inclination angles ⁇ 1 , ⁇ 2 of the side surfaces 34a, 34b of the scroll wall 34 are different from each other.
  • inclination angles ⁇ 3 , ⁇ 4 of the side surfaces 38a, 38b of the scroll wall 38 are different from each other.
  • side surfaces of a scroll wall are different in inclination angle.
  • the scroll member is formed, for example, by casting, it may be required that the side surfaces of the scroll wall are different in draft in a casting plan. Accordingly, inclination angles of the side surfaces are predetermined differently.
  • the other constitution of the second embodiment is similar to the constitution of the first embodiment, and the overlapped explanation is omitted.
  • each pair of side surfaces 34a, 38b and 34b, 38a of the scroll walls 34 and 38 facing each other is equal in inclination angle even if the side surfaces 34a, 34b and 38a, 38b of the scroll walls 34 and 38 are each different in inclination angle, sealing performance in the compression chambers 40 is ensured. Thus, compression cycle in the compression chambers 40 is performed without obstruction.
  • the scroll type compressor according to the above embodiments has the drive shaft which protrudes outside of the configuration of the compressor and is operatively connected to the external drive source such as an engine.
  • the above external drive source may be built in type or canned motor type. That is, electric motor for driving the drive shaft may be installed in the compressor.
  • the scroll wall since thickness of the joint portion of the scroll wall is larger than that of the distal end of the scroll wall, the scroll wall is prevented from being deformed. In addition, sealing performance is ensured in clearance between the distal end of the scroll wall and the opposing surface of the scroll base plate. Therefore, airtight performance in the compression region is, as a whole, maintained. As a result, high compressing performance is obtained. Moreover, since the distal end is not provided with the tip seal, the scroll wall has, as a whole, relatively small thickness. As a result, the scroll wall becomes compact and lightweight. Thus, various prominent effects are obtained.
  • a scroll type compressor has a fixed scroll member and a movable scroll member.
  • the fixed scroll member has a fixed scroll base plate and a fixed scroll wall extending from the fixed scroll base plate.
  • the movable scroll member has a movable scroll base plate and a movable scroll wall extending from the movable scroll base plate.
  • the fixed scroll member and the movable scroll member cooperatively form a compression region.
  • the movable scroll member orbits relative to the fixed scroll member to compress refrigerant in the compression region.
  • Each scroll wall is formed in a taper shape from each base plate toward each distal end of the scroll wall. The distal end is non-contact with the opposing scroll base plate. Clearance between the distal end and the opposing scroll base plate is less than or equal to the limit clearance value which maintains airtight performance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP02004861A 2001-03-05 2002-03-04 Compresseur à spirales Withdrawn EP1239158A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001059976A JP2002257059A (ja) 2001-03-05 2001-03-05 スクロール圧縮機
JP2001059976 2001-03-05

Publications (1)

Publication Number Publication Date
EP1239158A2 true EP1239158A2 (fr) 2002-09-11

Family

ID=18919464

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02004861A Withdrawn EP1239158A2 (fr) 2001-03-05 2002-03-04 Compresseur à spirales

Country Status (4)

Country Link
US (1) US20020146340A1 (fr)
EP (1) EP1239158A2 (fr)
JP (1) JP2002257059A (fr)
CA (1) CA2374372A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4821526B2 (ja) * 2006-03-02 2011-11-24 ダイキン工業株式会社 圧縮機のスクロール部材およびそれを用いた圧縮機
WO2017056213A1 (fr) * 2015-09-30 2017-04-06 三菱電機株式会社 Compresseur à spirale
JP2020176587A (ja) * 2019-04-22 2020-10-29 Ntn株式会社 スクロールポンプ用ロータおよびスクロールポンプ

Also Published As

Publication number Publication date
US20020146340A1 (en) 2002-10-10
JP2002257059A (ja) 2002-09-11
CA2374372A1 (fr) 2002-09-05

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