EP0761973A2 - Gasverdichter - Google Patents

Gasverdichter Download PDF

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Publication number
EP0761973A2
EP0761973A2 EP96306183A EP96306183A EP0761973A2 EP 0761973 A2 EP0761973 A2 EP 0761973A2 EP 96306183 A EP96306183 A EP 96306183A EP 96306183 A EP96306183 A EP 96306183A EP 0761973 A2 EP0761973 A2 EP 0761973A2
Authority
EP
European Patent Office
Prior art keywords
gas
discharge
openings
block
intake
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Withdrawn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
EP96306183A
Other languages
English (en)
French (fr)
Other versions
EP0761973A3 (de
Inventor
Koichi Shimada
Seiichiro Yoda
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.)
Seiko Seiki KK
Original Assignee
Seiko Seiki KK
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 Seiko Seiki KK filed Critical Seiko Seiki KK
Publication of EP0761973A2 publication Critical patent/EP0761973A2/de
Publication of EP0761973A3 publication Critical patent/EP0761973A3/de
Withdrawn legal-status Critical Current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
    • 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
    • F04C29/0035—Equalization of pressure pulses
    • 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
    • F04C18/344—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 inner member
    • F04C18/3446—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 inner member the inner and outer member being in contact along more than one line or surface

Definitions

  • the present invention relates to a gas compressor used in a refrigerator or air-conditioner and, more particularly, to a sliding-vane rotary compressor.
  • FIG. 8 schematically shows the prior art sliding-vane rotary gas compressor in cross section.
  • Fig. 9 is a view taken on line X-X of Fig. 8.
  • This gas compressor has a rotor 2 rigidly secured to a rotor shaft 1.
  • a motor not shown
  • five vanes 3 slidably held in five slots (not shown), respectively, radially formed in the rotor 2 are rotated in contact with the inner wall of the cylinder chamber 4, thus compressing refrigerant gas.
  • An intake chamber 6 is formed inside a front head 5.
  • An intake port 7 for drawing in the refrigerant gas to be compressed from an evaporator (not shown) is formed over the intake chamber 6.
  • Two intake holes 8 and 9 are formed in the front head 5 symmetrically about a point to place the intake chamber 6 and the cylinder chamber 4 in communication with each other. Accordingly, the refrigerant gas drawn in from the intake port 7 on the intake chamber 6 flows through the intake chamber 6 and through the intake holes 8, 9, as indicated by the arrow A. Finally, the gas is introduced into the cylinder chamber 4.
  • Two discharge holes (not shown) corresponding to the intake holes 8 and 9 in the cylinder chamber 4 are formed in a rear-side block 10 on the side of the cylinder chamber 4 and located symmetrically with respect to a point.
  • Discharge valves (not shown) are mounted in the discharge holes, respectively. As shown in Fig. 9, these discharge holes are in communication with openings 11 and 12, respectively, formed in the rear-side block 10 and connected with discharge passages 13 and 14, respectively, formed between the rear-side block 10 and a block 15 for an oil separator.
  • These discharge passages 13 and 14 are connected to each other at 16 close to their ends. At this location 16, the oil separator, indicated by 17, for separating lubricating oil from the refrigerant gas is mounted.
  • the compressed refrigerant gas discharged from the opening 11 or 12 in this way flows through the discharge passage 13 or 14 and is supplied into the oil separator 17, where the lubricating oil is separated from the refrigerant gas.
  • the refrigerant gas is expelled to the outside from a discharge port 19 in a discharge chamber 18, as indicated by the arrow B.
  • the two pulsating motions produced in the openings 11 and 12 of the cylinder chamber 4 are shifted in phase by a half wavelength, because the timing at which the gas is discharged from the openings 11 and 12 is designed as described above to smoothen the delivery of the gas. Therefore, the pulsating motions of the refrigerant gas should cancel out until the gas is delivered from the discharge port 19 after flowing through the discharge passage 13, the discharge passage 14, the oil separator 17, and the discharge chamber 18. Hence, discharging pulsating motions due to the fifth-order component of the rotational speed of the compressor should not be transmitted to the outside.
  • the discharge passages 13 and 14 are different in length, as shown in Fig. 9.
  • the pulsating motions are transmitted to the outside, producing noise.
  • Use of a silencer may be generally contemplated to solve this problem.
  • the whole machine is made bulky.
  • the cost of fabricating the machine is increased greatly, thus presenting a new problem.
  • a gas compressor comprising a gas compression portion, two discharge passages having the same length, and a common passage connected with both of the two discharge passages near their ends.
  • the gas compression portion has two intake ports and two discharge ports corresponding to the intake ports, respectively.
  • the two intake ports are located symmetrically with respect to a point. Gas is drawn into these two intake ports one after another by rotary motion of a plurality of vanes. The drawn gas is compressed by volume variations caused by the rotary motion of the vanes. The compressed gas is discharged from the two discharge ports successively.
  • the two discharge passages are connected with the two discharge ports, respectively.
  • the gas expelled from the two discharge ports in the gas compression portion produces pulsating motions according to the number of the vanes. These two pulsating motions are shifted in phase by a half wavelength.
  • the two discharge passages connected with the two discharge ports are equal in length. Furthermore, the ends of the two discharge passages are connected with the common passage. Therefore, when the gas discharged from the two discharge ports in the gas compression portion flows through the common passage, the two pulsations of the expelled gas cancel out. As a consequence, the pulsating motions of the expelled gas are not readily transmitted to the outside.
  • Fig. 1 is a partially cutaway cross section of a gas compressor according to the present invention.
  • Fig. 2 is a view taken on line Y-Y of Fig. 1.
  • the gas compressor comprises a gas compression portion 21, a casing 22 surrounding the gas compression portion 21, and a front head 23.
  • the casing 22 has an opening at its one side.
  • the front head 23 is mounted so as to close off the opening in the front head 23.
  • the gas compression portion 21 comprises a cylindrical block 24, a control plate 25 rotatably mounted to the left end surface of the cylindrical block 24 as described later, and a rear-side block 26 firmly secured to the right end surface of the cylindrical block 24.
  • the axial cross section of the inner surface of the cylindrical block 24 assumes an elliptical form.
  • An elliptical cylinder chamber 27 is formed by these gas compression portion 21, the control plate 25, the cylindrical block 24, and the rear-side block 26.
  • a rotor 30 has five vanes 29 slidably held in slits (not shown), and is housed in the cylinder chamber 27.
  • This rotor 30 is mounted integrally with a rotor shaft 31.
  • Bearing support holes 23a and 26a are formed in the front head 23 and the rear-side block 26, respectively, and have a diameter slightly larger than that of the rotor shaft 31.
  • the left and right sides of the rotor shaft 31 are rotatably held in the holes 23a and 26a, respectively.
  • One end of the rotor shaft 31 is connected to a motor (not shown). When the rotor shaft 31 is rotated, the five vanes 29 rotate in contact with the inner wall surface of the cylinder chamber 27, thus compressing refrigerant gas.
  • An intake chamber 32 is formed inside the front head 23.
  • the intake chamber 32 is provided with an intake port (not shown) for drawing the refrigerant gas to be compressed from an evaporator (not shown).
  • the front head 23 has a boss 23b on the side of the cylindrical block 24.
  • the aforementioned control plate 25 which is shaped like a disk fits over the boss 23b via a bearing 28 so as to be rotatable within a given range of angles.
  • the control plate 25 is centrally provided with a fitting hole. Recesses or openings (not shown) are formed in given positions on the outer periphery of the control plate 25, and these recesses or openings are diametrically opposite to each other.
  • the front head 23 is provided with the intake chamber 32, as shown in Fig. 1.
  • the intake chamber 32 can register with any one of the recesses or openings (not shown).
  • the compression volume of the cylinder chamber 27 can be adjusted by adjusting the position of the recess or opening registering with the intake chamber 32 according to the rotation of the control plate 25.
  • the rear-side block 26 is fixedly mounted to the cylindrical block 24 by bolts 48, as shown in Fig. 2.
  • Two discharge holes (not shown) corresponding to the recesses or openings (not shown) in the control plate 25 are formed in the rear-side block 26 on the side of the cylinder chamber 27 and located symmetrically with respect to a point.
  • Discharge valves (not shown) are mounted in the discharge holes, respectively. As shown in Fig. 2, these discharge holes are in communication with openings 37 and 38, respectively, formed in the rear-side block.
  • the discharge holes are also in communication with discharge holes 40 and 41, respectively, which are formed between the rear-side block 26 and an oil separator block 39 as described later.
  • These discharge passages 40 and 41 are connected to each other near their ends, thus forming a common passage 49.
  • An oil separator 42 consisting of a filter for separating lubricating oil from refrigerant gas is mounted in the common passage 49.
  • the discharge passages 40 and 41 are equal in length.
  • An oil reservoir 46 for storing the lubricating oil is formed at the bottom of the discharge chamber 44.
  • Lubricating oil supply passages 47 extend through the rear-side block 26, the cylindrical block 24, and the front head 23 to permit the lubricating oil to be supplied from the oil reservoir 46 into the bearing support holes 23a and 26a.
  • Fig. 3 shows the rear-side block in cross section.
  • Fig. 4 shows the right side surface of the rear-side block.
  • This rear-side block 26 has a given thickness and is shaped like a disk.
  • the aforementioned bearing support hole 26a is formed in the center of the block 26 and designed to support the rotor shaft 31.
  • the openings 37 and 38 are formed in the rear-side block 26 and extend in the direction of the thickness of the block 26.
  • the openings 37 and 38 are located symmetrically with respect to a point.
  • the openings 37 and 38 are connected to the starting points of grooves 261 and 262, respectively, for the discharge passages, respectively.
  • the terminal points of the grooves 261 and 262 are located close to a recess 263 in which one end of the oil separator 42 is received.
  • the terminal points of the grooves 261 and 262 are connected to each other in the recess 263.
  • the grooves 261 and 262 for the discharge passages are equal in length.
  • the groove 261 for one discharge passage is placed opposite to a groove 391 for one discharge passage, the groove 391 being formed in the oil separator block 39 described later. In this way, the discharge passage 40 shown in Fig. 2 is formed.
  • the groove 262 for the other discharge passage is placed opposite to a groove 392 for the other discharge passage, the groove 392 being formed in the oil separator block 39.
  • the discharge passage 41 shown in Fig. 2 is formed.
  • a plurality of mounting holes 264 for mounting the rear-side block 26 to the left side surface of the cylindrical block 24 by the bolts 48 are formed in given positions inside the rear-side block 26. Also, threaded holes 265 for mounting the oil separator block 39 to the rear-side block 26 are formed in given locations inside the block 26.
  • Fig. 5 shows this block 39 in cross section.
  • Fig. 6 shows the left side surface of the block 39.
  • Fig. 7 shows the right side surface of the block 39.
  • the block 39 for the oil separator is provided with the grooves 391 and 392 for the discharge passages.
  • the grooves 391 and 392 form the discharge passages 40 and 41, respectively, and are located opposite to the grooves 261 and 262, respectively, which are formed in the rear-side block 26.
  • the grooves 391 and 392 extend toward a cylindrical portion 394 forming the common passage in which the oil separator 42 is accommodated, the ends of the grooves 391 and 392 being located close to the cylindrical portion 394.
  • the grooves 391 and 392 are both connected to the cylindrical portion 394.
  • the grooves 391 and 392 are equal in length.
  • the top and bottom sides of the cylindrical portion 394 are open.
  • a recess 395 in which the central portion of the rear-side block 26 is accommodated is formed near the bottom of the oil separator block 39.
  • Mounting holes 396 for mounting the block 39 to the rear-side block are formed in given locations inside the block 39.
  • the compressed refrigerant gas discharging from the openings 37 and 38 in this manner flows through the discharge passage 40 or 41 and enters the oil separator 42, where the lubricating oil is separated from the refrigerant gas.
  • the refrigerant gas is discharged to the outside from the discharge port (not shown) in the discharge chamber 44.
  • the pressure is not constant. Rather, high-order pressure variations are produced according to the rotational speed of the rotor 30. Because there exist five vanes 3, the discharge valves in the two openings 37 and 38 produce five pulsating motions per rotation of the rotor 30.
  • the two pulsating motions produced in the openings 37 and 38 in communication with the discharge holes in the cylinder chamber 27 are shifted in phase by a half wavelength.
  • the two discharge passages 40 and 41 connected with the two openings 37 and 38 are equal in length. Furthermore, the ends of the two discharge passages 40 and 41 are connected to the common passage 49. Therefore, the pulsating motions of the discharged gas from the two openings 37 and 38 in the cylinder chamber 27 cancel out each other when the gas flows through the common passage 49. Consequently, the pulsating motions of the discharged gas are not readily transmitted to the outside.
  • the discharge passages 40 and 41 having the same length are connected with the openings 37 and 38 which are in communication with the discharge holes, respectively, in the cylinder chamber 27.
  • the ends of these discharge passages 40 and 41 are connected with the common passage 49.
  • the pulsating motions of the discharged gas from the two openings 37 and 38 in the cylinder chamber 27 which are shifted in phase by a half wavelength cancel out each other when the gas flows through the common passage 49. Consequently, the pulsating motions of the discharged gas are not readily transmitted to the outside. Therefore, in the present embodiment, the pulsations of the discharged gas can be suppressed without increasing the size of the whole machine and without incurring a great increase in the cost of fabricating the machine. As a result, noise due to the pulsations can be reduced.
  • the gas compressor is provided with the cylinder chamber 27 having a variable compression volume.
  • the invention can also be applied to a gas compressor in which the cylinder chamber 27 has a fixed compression volume.
  • the discharge passages 40 and 41 are connected together near their ends to form the common passage 49.
  • the oil separator 42 is positioned in this common passage 49.
  • a separate passage where the oil separator 42 is mounted may be connected with the common passage 49.
  • two discharge passages having the same length are connected with two discharge ports, respectively, in the gas compression portion.
  • the ends of these two discharge passages are connected with a common passage.
  • Pulsating motions of the gas discharged from the two discharge ports in the gas compression portion are shifted in phase by a half wavelength. These pulsating motions cancel out each other when the gas flows through the common passage. In consequence, the pulsating motions of the discharged gas are not readily transmitted to the outside. Accordingly, in the present invention, the pulsations of the discharged gas can be suppressed without increasing the size of the whole machine and without incurring a great increase in the cost of fabricating the machine. As a result, noise due to the pulsations can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP96306183A 1995-09-08 1996-08-23 Gasverdichter Withdrawn EP0761973A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP231372/95 1995-09-08
JP23137295A JPH0979156A (ja) 1995-09-08 1995-09-08 気体圧縮機

Publications (2)

Publication Number Publication Date
EP0761973A2 true EP0761973A2 (de) 1997-03-12
EP0761973A3 EP0761973A3 (de) 1998-05-13

Family

ID=16922594

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96306183A Withdrawn EP0761973A3 (de) 1995-09-08 1996-08-23 Gasverdichter

Country Status (2)

Country Link
EP (1) EP0761973A3 (de)
JP (1) JPH0979156A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7056107B2 (en) * 2001-10-16 2006-06-06 Ebara Corporation Vane type rotary machine
CN112780547A (zh) * 2019-11-11 2021-05-11 罗伯特·博世有限公司 压缩机和车辆

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002161854A (ja) * 2000-11-29 2002-06-07 Zexel Valeo Climate Control Corp 圧縮機
JP3987697B2 (ja) * 2000-12-22 2007-10-10 カルソニックコンプレッサー株式会社 気体圧縮機

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57151090A (en) * 1981-03-12 1982-09-18 Mitsubishi Heavy Ind Ltd Rotary compressor
JPS59200088A (ja) * 1983-04-26 1984-11-13 Toyoda Autom Loom Works Ltd ロ−タリ圧縮機
JPS63263284A (ja) * 1987-04-20 1988-10-31 Koyo Seiko Co Ltd ベ−ンポンプ
JP2963519B2 (ja) * 1990-10-11 1999-10-18 豊田工機株式会社 ベーンポンプ

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7056107B2 (en) * 2001-10-16 2006-06-06 Ebara Corporation Vane type rotary machine
EP1443213A4 (de) * 2001-10-16 2006-12-06 Ebara Corp Drehflügelzellenmaschine
CN112780547A (zh) * 2019-11-11 2021-05-11 罗伯特·博世有限公司 压缩机和车辆

Also Published As

Publication number Publication date
JPH0979156A (ja) 1997-03-25
EP0761973A3 (de) 1998-05-13

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