EP3604736B1 - Verdichter und verdichtersystem - Google Patents

Verdichter und verdichtersystem Download PDF

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Publication number
EP3604736B1
EP3604736B1 EP19187098.9A EP19187098A EP3604736B1 EP 3604736 B1 EP3604736 B1 EP 3604736B1 EP 19187098 A EP19187098 A EP 19187098A EP 3604736 B1 EP3604736 B1 EP 3604736B1
Authority
EP
European Patent Office
Prior art keywords
bolts
compressor
housing
bolt
end surface
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.)
Active
Application number
EP19187098.9A
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English (en)
French (fr)
Other versions
EP3604736B8 (de
EP3604736A1 (de
Inventor
Yoshiaki Miyamoto
Hajime Sato
Akihiro Noguchi
Takashi Goto
Shusaku Goto
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3604736A1 publication Critical patent/EP3604736A1/de
Application granted granted Critical
Publication of EP3604736B1 publication Critical patent/EP3604736B1/de
Publication of EP3604736B8 publication Critical patent/EP3604736B8/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to a compressor and a compressor system.
  • a compressor system used in an automotive freezing unit for a large truck or the like and having a compressor compressing a refrigerant gas (see, for example, Japanese Unexamined Patent Application, First Publication No. 2001-18704 ).
  • the compressor system is used after being connected to an evaporator system by means of refrigerant piping.
  • the compressor has a tubular housing accommodating a compression mechanism.
  • the outer surface of the housing is disposed so as to be along a planar attachment surface in the interest of space efficiency when the compressor is mounted.
  • European patent application n° EP 2 072 754 A2 relates to a compressor according to the preamble of claim 1.
  • United States Patent Application Publication n° US20110165006A1 relates to a scroll compressor.
  • the compressor and the compressor system are desired to be further reduced in size due to a limited compressor attachment space.
  • the present invention provides a compressor capable of improving the degree of freedom in housing design and achieving housing width reduction as a result and a compressor system provided with the compressor.
  • a compressor includes a compression mechanism having a rotating shaft, a housing accommodating the compression mechanism and having a housing main body having a tubular side wall extending along an axial direction of the rotating shaft and a bottom portion connected to one end of the side wall in the axial direction, an other end of the side wall in the axial direction being a first end surface formed in a plane and extending in a circumferential direction of an axis of the rotating shaft, a front case having a second end surface facing the first end surface and blocking the housing, and a plurality of bolts disposed in annular shape by being spaced apart in the circumferential direction of the axis and fastening the front case only to the housing.
  • the plurality of bolts have a plurality of first bolts and second bolts disposed between the first bolts adjacent to each other in the circumferential direction, having shaft portions smallest in diameter among the plurality of first bolts, and fastening the front case to the housing.
  • housing width reduction can be achieved from a reduction in the diameter of the shaft portion of the second bolt.
  • the housing has a fixing portion for attaching the housing main body to an attachment target such that the side wall of the housing main body is along an attachment surface of the attachment target and the second bolts may include a bolt closest to the attachment surface and a bolt farthest from the attachment surface among the plurality of bolts disposed in annular shape by being spaced apart in the circumferential direction.
  • the plurality of bolts may be disposed at equal intervals in the circumferential direction.
  • the plurality of bolts may have a third bolt and a shaft portion of the third bolt may be smaller in diameter than the shaft portions of the plurality of first bolts and larger in diameter than the shaft portions of the second bolts.
  • the degree of freedom in housing and front case design can be improved as compared with a case where a front case is fastened by means of a plurality of bolts having the same shaft portion diameter.
  • a compressor system may include a bracket, a drive source fixed to the bracket, and the above-described compressor fixed to the bracket and driven by the drive source.
  • the compressor can be more firmly fixed to the bracket against the force applied to the compressor due to vibration, belt tension, or the like by the width of the compressor being reduced. As a result, product reliability can be further improved.
  • a compressor system may include a drive source and the above-described compressor fixed to the drive source and driven by the drive source.
  • the degree of freedom in housing and front case design can be improved as compared with a case where a front case is fastened by means of a plurality of bolts having the same shaft portion diameter.
  • housing width reduction can be achieved from a reduction in the diameter of the shaft portion of the second bolt.
  • the compressor system of the present embodiment is used in, for example, an automotive freezing unit for a large truck or the like.
  • the compressor system is used after being connected to an evaporator system by means of refrigerant piping.
  • a compressor system 1 has a bracket 2, an engine 3 (drive source) fixed to the bracket 2, and a compressor 10 (open type compressor) driven by the engine 3.
  • the compressor system 1 is attached below a freezer 5 of, for example, a large truck equipped with a freezing unit.
  • the bracket 2 is an attachment target of the compressor 10 and has a flat attachment surface 7.
  • the engine 3 and the compressor 10 are fixed to the attachment surface 7 of the bracket 2 such that a drive shaft 4 of the engine 3 and a rotating shaft 12 of the compressor 10 are parallel.
  • the power of the engine 3 is transmitted to the compressor 10 via a belt 6.
  • the compressor 10 is provided with a compression mechanism 11 having the rotating shaft 12, a housing 13 accommodating the compression mechanism 11, and a front case 16 blocking the housing 13.
  • the direction in which an axis A of the rotating shaft 12 extends is referred to as an axial direction Da and the direction that is orthogonal to the attachment surface 7 (see FIG. 1 ).
  • the axis A and along the normal of the attachment surface 7 is referred to as a width direction W.
  • the housing 13 has a housing main body 14 and two fixing portions 15 for attaching the compressor 10 to the bracket 2 (see FIG. 1 ).
  • the housing main body 14 has a bottomed tubular shape having a tubular side wall 17 extending along the axial direction Da and a bottom portion 18 connected to one end of the side wall 17 in the axial direction Da.
  • a planar first end surface 19 extending in a circumferential direction is formed at the other end of the side wall 17 in the axial direction Da.
  • the first end surface 19 is the end surface of the opening portion of the housing main body 14 having the bottomed tubular shape.
  • the first end surface 19 is formed in a planar shape orthogonal to the axis A.
  • the first end surface 19 is a surface formed in an annular shape.
  • the first end surface 19 is a surface facing the axial direction Da.
  • the front case 16 is attached to the opening portion formed in the housing 13 so as to block the opening portion.
  • the front case 16 has a second end surface 20 facing the first end surface 19.
  • the front case 16 has a boss portion 16A protruding to one side in the axial direction Da.
  • An O-ring 32 is attached to the outer peripheral surface of the boss portion 16A.
  • a sealed space is formed inside by the front case 16 being attached to the housing 13 and the O-ring 32 coming into close contact with the inner peripheral surface of the housing 13.
  • the compression mechanism 11 is accommodated in the sealed space.
  • Formed in the outer peripheral surface of the housing 13 is a suction port 21 allowing a fluid (refrigerant gas) to flow into the sealed space and a discharge port 22 through which the fluid is discharged from the sealed space to the outside after being compressed by the compression mechanism 11.
  • the compression mechanism 11 has the columnar rotating shaft 12 extending along the axis A and a scroll compression unit 23 connected to the rotating shaft 12.
  • the rotating shaft 12 is rotatably supported by the front case 16 via a main bearing 24 and a sub bearing 25.
  • the other end of the rotating shaft 12 protrudes from the front case 16 to the outside via a seal portion 26.
  • a pulley 28 rotatably installed in the outer peripheral portion of the front case 16 via a bearing 27 is connected to the other end of the rotating shaft 12 via an electromagnetic clutch 29. Power from the engine 3 driving the pulley 28 is transmitted to the rotating shaft 12 via the electromagnetic clutch 29 and rotation occurs around the axis A.
  • the electromagnetic clutch 29 has an armature plate 30 integrally provided on the rotating shaft 12 and an electromagnet 31 generating a magnetic force acting on the armature plate 30 by being excited.
  • the electromagnet 31 attracts the armature plate 30 to the electromagnet 31 side when the electromagnet 31 is excited by electric power supply from the outside.
  • the pulley 28 and the armature plate 30 abut against each other and the rotational force of the pulley 28 is transmitted to the armature plate 30.
  • the armature plate 30 rotates around the axis A integrally with the pulley 28.
  • the rotational force of the pulley 28 is not transmitted to the armature plate 30. In other words, the pulley 28 becomes idle.
  • the operations of the armature plate 30 and the rotating shaft 12 are controlled by the operation.
  • a crank pin 33 eccentric in the radial direction of the axis A is integrally provided at one end of the rotating shaft 12.
  • An orbiting scroll 34 of the scroll compression unit 23 is connected to one end of the rotating shaft 12 via the crank pin 33.
  • the scroll compression unit 23 compresses the fluid flowing in from the suction port 21 and discharges the fluid from the discharge port 22 by being driven by the rotating shaft 12.
  • a compression chamber 36 is formed between a fixed scroll 35 and the orbiting scroll 34 by the fixed scroll 35 and the orbiting scroll 34 engaging with each other with a shift in phase of 180°.
  • the fixed scroll 35 and the orbiting scroll 34 have end plates 34A and 35A and spiral wraps 34B and 35B provided on the respective end plates 34A and 35A.
  • a discharge port 37 allowing the compressed fluid to be discharged is formed in the central portion of the fixed scroll 35.
  • the fixed scroll 35 is fixed to the bottom portion 18 of the housing 13 via a bolt 38.
  • the orbiting scroll 34 is connected to the crank pin 33 of the rotating shaft 12 via a driven crank mechanism 39 and supported so as to be capable of revolving with respect to the fixed scroll 35.
  • An O-ring 40 is attached to the outer peripheral portion of the end plate 35A of the fixed scroll 35.
  • the internal space of the housing 13 is divided into a discharge chamber S2 and a suction chamber S1 by the O-ring 40 coming into close contact with the inner peripheral surface of the housing 13.
  • the suction chamber S1 communicates with the suction port 21 formed in the housing 13. A low-pressure fluid taken in through the suction port 21 is suctioned into the compression chamber 36 through the suction chamber S1. In addition, the fluid (compressed refrigerant gas) supplied from the compression chamber 36 flows into the discharge chamber S2 via the discharge port 37.
  • the main bearing 24 supports the rotating shaft 12 on the axis A.
  • the main bearing 24 is disposed closer to the scroll compression unit 23 side than the sub bearing 25.
  • the main bearing 24 is a ball bearing larger in outer diameter than the sub bearing 25.
  • the sub bearing 25 is disposed closer to the scroll compression unit 23 side than the seal portion 26.
  • the sub bearing 25 is a needle bearing smaller in outer diameter than the main bearing 24.
  • the fixing portion 15 of the housing 13 has a bolt insertion hole 44 that extends in a direction orthogonal to the axis A and is formed integrally with the housing main body 14 on the outer surface of the housing main body 14 (see FIG. 2 ).
  • One fixing portion 15 (15A) is provided on one side of the housing 13 in the width direction W.
  • the other fixing portion 15 (15B) is provided on the other side of the housing 13 in the width direction W.
  • the length of the fixing portion 15 in the width direction W is substantially equal to the width of the housing main body 14 in the width direction W.
  • the compressor 10 is fixed to the bracket 2 by a bolt 8 (see FIG. 1 ) inserted through the bolt insertion hole 44.
  • the front case 16 is fixed to the housing 13 by a plurality of bolts 41 and 42.
  • the bolts 41 and 42 are disposed at equal intervals in the circumferential direction of the axis A. In other words, gaps G of the bolts 41 and 42 adjacent to each other in the circumferential direction of the axis A are substantially the same.
  • the bolts 41 and 42 have a plurality of (eight in the present embodiment) first bolts 41 and a plurality of (four in the present embodiment) second bolts 42.
  • the nominal diameter of the first bolt 41 is different from the nominal diameter of the second bolt 42.
  • the diameter of the shaft portion of the first bolt 41 is larger than the diameter of the shaft portion of the second bolt 42.
  • the four second bolts 42 are disposed at both ends in the normal direction (width direction W) of the attachment surface 7 among the plurality of bolts 41 and 42.
  • the second bolts 42 include the bolt closest to the attachment surface 7 (a second bolt 42N in FIG. 3 ) and the bolt farthest from the attachment surface 7 (a second bolt 42F in FIG. 3 ) among the plurality of bolts 41 and 42.
  • the second bolts 42 are the bolts disposed at both ends in the width direction W orthogonal to the attachment surface 7 among the plurality of bolts 41 and 42.
  • these bolts are composed the eight first bolts 41 and the four second bolts 42 disposed outside the eight first bolts 41 in the width direction W.
  • a set of four first bolts 41 and a set of two second bolts 42 are alternately disposed in the circumferential direction.
  • One set of two second bolts 42 is disposed on one side in the width direction W.
  • the other set of two second bolts 42 is disposed on the other side in the width direction W.
  • the degree of freedom in design of the housing 13 and the front case 16 can be improved as compared with a case where the front case 16 is fastened by means of a plurality of bolts having the same shaft portion diameter.
  • the bolts 41 and 42 are disposed at equal intervals in the circumferential direction. As a result, the circumferential distribution of the fastening force resulting from fastening of the plurality of bolts 41 and 42 can be close to being uniform.
  • the compressor 10 can be more firmly fixed to the bracket 2 against the force applied to the compressor 10 due to vibration, belt tension, or the like by the width Wi of the compressor 10 being reduced. As a result, product reliability can be further improved.
  • the present invention is not limited thereto.
  • the first bolt 41 and the second bolt 42 may be mixed.
  • the first bolt 41 and the second bolt 42 may be alternately disposed in the circumferential direction.
  • the front case 16 is fixed to the housing 13 by three types of bolts 41, 42, and 43 in a compressor 10B of the first modification example.
  • the first bolt 41, the second bolt 42, and the third bolt 43 are the plurality of bolts of the modification example.
  • the third bolt 43 is adjacent to the first bolt 41.
  • the first bolt 41 and the second bolt 42 are adjacent to the third bolt 43.
  • the third bolt 43 is adjacent to the second bolt 42.
  • the diameter of the shaft portion of the third bolt 43 is smaller than the diameter of the shaft portion of the first bolt 41 and larger than the diameter of the shaft portion of the second bolt 42.
  • the third bolt 43 smaller in diameter than the first bolt 41 and larger in diameter than the second bolt 42 is disposed between the first bolt 41 having the largest diameter and the second bolt 42 having the smallest diameter.
  • the degree of freedom in design of the housing 13 and the front case 16 can be improved as compared with a case where the front case 16 is fastened by means of a plurality of bolts having the same shaft portion diameter.
  • a compressor system 1C of the second modification example is provided with a bracket 2C, an engine 3C (drive source) fixed to the bracket 2C, and a compressor 10C fixed to the engine 3C and driven by the engine 3C.
  • the engine 3C has a casing 3a.
  • the casing 3a has a flat attachment surface 7C parallel to the drive shaft 4 of the engine 3C.
  • the compressor 10C is fixed to the attachment surface 7C of the casing 3a such that the drive shaft 4 of the engine 3C and the rotating shaft 12 of the compressor 10C are parallel.
  • the compressor 10C is fixed to the casing 3a by the bolt 8.
  • the compressor system 1C can be more compact by the compressor 10C being directly attached to the high-rigidity casing 3a.
  • compressors 10, 10B, and 10C are displacement type compressors in the embodiment described above, the present invention is not limited thereto.
  • a centrifugal compressor having the rotating shaft 12 may be adopted.
  • the compressor system 1 is used in an automotive freezing unit for a large truck or the like according to the description, the present invention is not limited thereto.
  • the compressor system 1 can be any compressor system insofar as the compressor system is provided with a drive source such as an engine and an electric motor and a compressor driven by the drive source.
  • the degree of freedom in housing and front case design can be improved as compared with a case where a front case is fastened by means of a plurality of bolts having the same shaft portion diameter.
  • housing width reduction can be achieved from a reduction in the diameter of the shaft portion of the second bolt.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (5)

  1. Verdichter (10, 10B, 10C), der Folgendes umfasst:
    ;einen Verdichtungsmechanismus (11) mit einer Rotationswelle (12)
    ein Gehäuse (13), in das der Verdichtungsmechanismus (11) aufgenommen ist und das einen Gehäusehauptkörper (14), der eine rohrförmige Seitenwand (17), die sich entlang einer Axialrichtung (Da) der Rotationswelle (12) erstreckt, und einen Bodenabschnitt (18), der mit einem Ende der Seitenwand (17) in der Axialrichtung (Da) verbunden ist, aufweist, wobei ein anderes Ende der Seitenwand (17) in der Axialrichtung (Da) eine erste Endfläche (19) ist, die in einer Ebene gebildet ist, welche sich in eine Umfangsrichtung einer Achse (A) der Rotationswelle (12) erstreckt; und
    ein vorderes Gehäuse (16), das eine zweite Endfläche (20) aufweist, die der ersten Endfläche (19) zugewandt ist und das Gehäuse (13) blockiert; dadurch gekennzeichnet, dass der Verdichter ferner Folgendes umfasst:
    eine Vielzahl von Bolzen (41, 42, 43), die mit Abstand in der Umfangsrichtung der Achse (A) ringförmig angeordnet sind und das vordere Gehäuse (16) nur am Gehäuse (13) festmachen,
    wobei die Vielzahl von Bolzen (41, 42, 43) eine Vielzahl von ersten Bolzen (41) und zweiten Bolzen (42) umfasst, welche zwischen den in der Umfangsrichtung einander benachbart ersten Bolzen (41) angeordnet sind, Schaftabschnitte aufweisen, deren Durchmesser unter der Vielzahl von ersten Bolzen (41) am kleinsten sind, und das vordere Gehäuse (16) am Gehäuse (13) festmachen,
    das Gehäuse (13) weist zum Befestigen des Gehäusehauptkörpers (14) in einer Breitenrichtung (W) an einem Befestigungsziel (2, 3C) einen Fixierungsabschnitt (15) auf, derart, dass die Seitenwand (17) des Gehäusehauptkörpers (14) entlang einer Befestigungsfläche (7) des Befestigungsziels (2, 3C) steht, wobei die Breitenrichtung (W) senkrecht zur Befestigungsfläche (7) verläuft
    die zweiten Bolzen (42) beinhalten zwei Bolzen (42N, 42F), die in der Breitenrichtung (W) an beiden Enden platziert sind, derart, dass von der Vielzahl von Bolzen, die mit Abstand in der Umfangsrichtung ringförmig angeordnet sind, einer der zwei Bolzen der Befestigungsfläche (7) am nächsten ist und einer der zwei Bolzen am weitesten von der Befestigungsfläche (7) entfernt ist,
    erste Bolzenlöcher, in die die ersten Bolzen (41) eingesetzt sind, und zweite Bolzenlöcher, in die die zweiten Bolzen (42) eingesetzt sind, sind in der zweiten Endfläche (20) gebildet, und
    eine Breite eines Abschnitts, in dem die zweiten Bolzenlöcher gebildet sind, der zweiten Endfläche (20) ist in einer Radialrichtung der Achse (A) kleiner als eine Breite eines Abschnitts, in dem die ersten Bolzenlöcher gebildet sind, der zweiten Endfläche (20) in einer Radialrichtung der Achse (A).
  2. Verdichter (10, 10B, 10C) nach Anspruch 1, wobei die Vielzahl von Bolzen (41, 42, 43) in gleichen Intervallen in der Umfangsrichtung angeordnet sind.
  3. Verdichter (10B) nach Anspruch 1 oder 2, wobei die Vielzahl von Bolzen (41, 42, 43) einen dritten Bolzen (43) aufweisen und ein Schaftabschnitt des dritten Bolzens (43) im Durchmesser kleiner ist als die Schaftabschnitte der Vielzahl von ersten Bolzen (41) und im Durchmesser größer ist als die Schaftabschnitte der zweiten Bolzen (42).
  4. Verdichtersystem (1, 1B), das Folgendes umfasst:
    eine Halterung (2);
    eine Antriebsquelle (3), die an der Halterung (2) fixiert ist; und
    den Verdichter (10, 10B) nach einem der Ansprüche 1 bis 3, der an der Halterung (2) fixiert ist und von der Antriebsquelle (3) angetrieben wird.
  5. Verdichtersystem (1C), das Folgendes umfasst:
    eine Antriebsquelle (3C); und
    den Verdichter (10C) nach einem der Ansprüche 1 bis 3, der an der Antriebsquelle (3C) fixiert ist und von der Antriebsquelle (3C) angetrieben wird.
EP19187098.9A 2018-07-31 2019-07-18 Verdichter und verdichtersystem Active EP3604736B8 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2018143347A JP2020020285A (ja) 2018-07-31 2018-07-31 圧縮機及び圧縮機システム

Publications (3)

Publication Number Publication Date
EP3604736A1 EP3604736A1 (de) 2020-02-05
EP3604736B1 true EP3604736B1 (de) 2022-04-20
EP3604736B8 EP3604736B8 (de) 2022-05-25

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JP (1) JP2020020285A (de)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129204A (en) * 1977-07-29 1978-12-12 Caterpillar Tractor Co. Spring operated clutch with small and large bolts

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB130199A (en) * 1918-09-11 1919-07-31 Samuel Arthur Einem Hickson A Multipistonal Rotary Engine.
DE3604206A1 (de) * 1986-02-11 1987-08-13 Provac Gmbh & Co Trockenlaufende drehschieber-vakuumpumpe
JP2001018704A (ja) 1999-07-09 2001-01-23 Mitsubishi Heavy Ind Ltd 陸上輸送用冷凍装置
JP5109642B2 (ja) * 2007-12-18 2012-12-26 株式会社豊田自動織機 電動圧縮機
JP5506227B2 (ja) * 2009-03-31 2014-05-28 三菱重工業株式会社 スクロール圧縮機
JP2012215089A (ja) * 2011-03-31 2012-11-08 Toyota Industries Corp 電動圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129204A (en) * 1977-07-29 1978-12-12 Caterpillar Tractor Co. Spring operated clutch with small and large bolts

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EP3604736B8 (de) 2022-05-25
EP3604736A1 (de) 2020-02-05
JP2020020285A (ja) 2020-02-06

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