JP2007064163A - Vane type compressor - Google Patents

Vane type compressor Download PDF

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JP2007064163A
JP2007064163A JP2005254456A JP2005254456A JP2007064163A JP 2007064163 A JP2007064163 A JP 2007064163A JP 2005254456 A JP2005254456 A JP 2005254456A JP 2005254456 A JP2005254456 A JP 2005254456A JP 2007064163 A JP2007064163 A JP 2007064163A
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Prior art keywords
rotor
blocks
vane
type compressor
cylinder
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JP2005254456A
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Japanese (ja)
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Osamu Akita
修 秋田
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Valeo Thermal Systems Japan Corp
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Valeo Thermal Systems Japan Corp
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Priority to JP2005254456A priority Critical patent/JP2007064163A/en
Priority to PCT/JP2006/316347 priority patent/WO2007029481A1/en
Publication of JP2007064163A publication Critical patent/JP2007064163A/en
Pending legal-status Critical Current

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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
    • 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
    • F04C18/3447—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 the vanes having the form of rollers, slippers or the like
    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vane type compressor capable of rotating a rotor properly without seizure even if surface treatment of Teflon coating is not applied on flat surfaces of both side blocks arranged to have the rotor therebetween. <P>SOLUTION: The vane type compressor 1 is comprised of a cylinder 2 having both sides blocked by blocks 4, 5, a rotor 9 rotatably stored in the cylinder 2, vanes 13 sliding in a plurality of vane grooves 11 formed on the rotor 9, a drive shaft 18 supported by both blocks 4, 5 and supporting the rotor 9, and the drive shaft 18 is supported by both blocks 4, 5 via slide bearings 19a, 19b. The slide bearings 19a, 19b project out of a flat surface of both blocks and abut on both side surface of the rotor 9. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、ベーン型圧縮機に係り、特にカーエアコンに用いられるベーン型圧縮機に関する。   The present invention relates to a vane type compressor, and more particularly to a vane type compressor used in a car air conditioner.

ベーン型圧縮機において、ロータを支え且つ駆動力を伝える駆動軸は、軸受を介して両ブロックに支えられている。この軸受は特許文献１の図から明らかなように、ニードルベアリング８，９が用いられている。近年、前記した軸受をニードルベアリングに代えて特許文献２に示すように、滑り軸受１４ｂ，１５ｂが採用されてきている。
実開平４−１３４６９１ 実開平５−６６２９３ In a vane compressor, a drive shaft that supports a rotor and transmits a driving force is supported by both blocks via bearings. As apparent from the drawing of Patent Document 1, needle bearings 8 and 9 are used for this bearing. In recent years, sliding bearings 14b and 15b have been adopted as shown in Patent Document 2 in place of the above-described bearings instead of needle bearings.
4-134691 5-66293

また、ロータと両サイドブロックは、異種の金属材料によりそれぞれ製造されているが、近年アルミニウム合金により両部材が製造されてきている。このため摺動面の溶着の危険を回避するために、両サイドブロックの平端面にテフロン（登録商標）コーティングの表面処理が施されている。   Further, the rotor and both side blocks are respectively made of different metal materials, but in recent years both members have been made of an aluminum alloy. For this reason, in order to avoid the danger of welding of the sliding surfaces, a surface treatment of Teflon (registered trademark) coating is performed on the flat end surfaces of both side blocks.

前記両サイドブロックの平坦面のテフロン（登録商標）コーティングの表面処理は高価であるが、ロータと両サイドブロックの焼付を防止する上では必要不可欠なものであった。   The surface treatment of the Teflon (registered trademark) coating on the flat surfaces of the both side blocks is expensive, but is indispensable for preventing seizure of the rotor and both side blocks.

そこで、この発明はロータを挟むように配された両ブロックの平坦面にテフロン（登録商標）コーティングの表面処理を施さなくても、焼付を起こさず、良好にロータが回転できるベーン型圧縮機を提供することを目的とする。   Therefore, the present invention provides a vane type compressor that can rotate the rotor satisfactorily without causing seizure even if the Teflon (registered trademark) coating surface treatment is not performed on the flat surfaces of both blocks arranged so as to sandwich the rotor. The purpose is to provide.

この発明に係るベーン型圧縮機は両側をブロックにより閉塞されたシリンダと、このシリンダ内に回転可能に収容されたロータと、このロータに形成の複数のベーン溝内を摺動するベーンと、前記両ブロックに支えられ、前記ロータを支える駆動軸とより成るベーン型圧縮機において、前記駆動軸は滑り軸受を介して前記両ブロックに支えられると共に、この滑り軸受を両ブロックの平端面からロータ側に突出させたことにある（請求項１）。   A vane type compressor according to the present invention includes a cylinder closed on both sides by a block, a rotor rotatably accommodated in the cylinder, a vane sliding in a plurality of vane grooves formed in the rotor, In the vane type compressor, which is supported by both blocks and includes a drive shaft for supporting the rotor, the drive shaft is supported by the both blocks via a slide bearing, and the slide bearing is supported on the rotor side from the flat end surface of both blocks. (Claim 1).

これにより、滑り軸受がシリンダの両側に配置されたブロックの平端面から突出し、ロータのスラスト方向を支えるため、該ロータと両面ブロックの平端面との所定の隙間が保たれ、直接接触することがなく、焼付の不具合が生じない。前記ロータと両ブロックの平端面との間の隙間に潤滑油が満たされているから、圧力の吹き抜けも起きないし、潤滑性も充分である。   As a result, the sliding bearing protrudes from the flat end surface of the block arranged on both sides of the cylinder and supports the thrust direction of the rotor, so that a predetermined gap between the rotor and the flat end surface of the double-sided block is maintained and can be in direct contact. There is no seizure defect. Since the lubricating oil is filled in the gap between the rotor and the flat end surfaces of both blocks, no pressure blows out and the lubricity is sufficient.

滑り軸受として円筒形のブシュであり（請求項２）、従来採用のニードベアリングよりも安価である。また滑り軸受の両ブロックの平坦面からの突出寸法は、上限で１００μｍ、下限で５μｍの範囲内としていることから（請求項３）、ロータと両ブロックの平坦面との隙間に潤滑油が満たされ、圧力の吹き抜けが生じないし、両部材が接触せず、焼付が発生することがない。   It is a cylindrical bush as a sliding bearing (Claim 2), and is cheaper than a conventionally used need bearing. Further, since the projecting dimension from the flat surface of both blocks of the slide bearing is within the range of 100 μm at the upper limit and 5 μm at the lower limit (Claim 3), the gap between the rotor and the flat surfaces of both blocks is filled with lubricating oil. Thus, no blow-through of pressure occurs, both members do not contact, and seizure does not occur.

滑り軸受は非アルミニウム材の鉄系材料により製造されることにあり（請求項４）、軸受として使用しても、ロータ、両ブロックのアルミニウム材と異なり鉄系材料使用から溶着の問題は生じない。この滑り軸受は、各々のブロックに圧入して（請求項５）又は鋳込んで装着される（請求項６）。   Sliding bearings are manufactured from non-aluminum ferrous materials (Claim 4). Even if they are used as bearings, there is no problem of welding due to the use of ferrous materials unlike the aluminum materials of the rotor and both blocks. . The slide bearing is press-fitted into each block (Claim 5) or cast and mounted (Claim 6).

以上のように、この発明によれば、軸受として滑り軸受が採用され、ニードルベアリングよりも安価に提供できると共に、滑り軸受が両ブロックの平坦面よりも所定寸法が突出しロータのスラスト方向を支え、これによりロータと両ブロックの平坦面との隙間が確保され、両部材が摺接せず焼付の不具合の発生は回避されるし、隙間には潤滑油が満たされるので、圧力の吹き抜けが起きることがない。当然ながら両ブロックの平坦面にテフロン（登録商標）の表面処理が不必要となる。   As described above, according to the present invention, a sliding bearing is employed as a bearing, which can be provided at a lower cost than a needle bearing, and the sliding bearing projects a predetermined dimension from the flat surfaces of both blocks to support the thrust direction of the rotor. This ensures a gap between the rotor and the flat surfaces of both blocks, prevents both members from sliding and avoids the occurrence of seizure problems, and the gap is filled with lubricating oil, so that pressure blows out. There is no. Of course, the surface treatment of Teflon (registered trademark) is unnecessary on the flat surfaces of both blocks.

以下、この発明の実施例を図面にもとづいて説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１、図２において、この発明に係わるベーン型圧縮機１は、車両用空調装置に用いられ、公知の冷凍サイクルの一部を構成するもので、ベルトやクラッチ等を介して走行用エンジンの回転力により駆動され、蒸発器で低温低圧化された冷媒ガスを圧縮して高温高圧縮し、この圧縮された冷媒ガスをコンデンサに送り出す作用を有している。   1 and 2, a vane type compressor 1 according to the present invention is used in a vehicle air conditioner and constitutes a part of a known refrigeration cycle. The refrigerant gas driven by the rotational force and compressed at low temperature and low pressure by the evaporator is compressed at high temperature and high pressure, and the compressed refrigerant gas is sent to the condenser.

前記ベーン型圧縮機１は、アルミニウム合金より成るフロントヘッド３と同じくアルミニウム合金より成るリアブロック４との間に、同じくアルミニウム合金より成るシリンダ２が配され、このシリンダ２は、その内周面６がほぼ楕円形のシリンダ空間７が形成され、このシリンダ空間内に真円状のアルミニウム合金より成るロータ９が配されている。このロータ９によりシリンダ２のシリンダ空間７は、２つのシリンダ空間７ａ，７ｂに分けられている。   In the vane type compressor 1, a cylinder 2 made of aluminum alloy is disposed between a front head 3 made of aluminum alloy and a rear block 4 made of aluminum alloy. The cylinder 2 has an inner peripheral surface 6 thereof. A substantially elliptical cylinder space 7 is formed, and a rotor 9 made of a perfectly circular aluminum alloy is disposed in the cylinder space. The rotor 9 divides the cylinder space 7 of the cylinder 2 into two cylinder spaces 7a and 7b.

また、シリンダ２の内周面６には、吸入口１４，１４が前記シリンダ空間７ａ，７ｂを回転方向から見て面積が拡大する方向部位に連接され、径方向に形成されている。またこのシリンダ２には、吐出口１６，１６が前記シリンダ空間７ａ，７ｂを回転方向から見て面積が縮小する方向の最も端に開口されている。この吐出口１６，１６には吐出バルブ１７，１７が設けられている。   Further, on the inner peripheral surface 6 of the cylinder 2, suction ports 14, 14 are connected in a radial direction so as to be connected in a direction where the area increases when the cylinder spaces 7 a, 7 b are viewed from the rotation direction. The cylinder 2 has discharge ports 16 and 16 opened at the extreme ends in the direction of reducing the area when the cylinder spaces 7a and 7b are viewed from the rotation direction. Discharge valves 17 and 17 are provided at the discharge ports 16 and 16.

ロータ９は、前記シリンダ２の短径部とほぼ同一の径の真円で、中心に下記する駆動軸１８が挿入される嵌合穴１０が形成されると共に、中心から放射方向に５つのベーン溝１１が形成されている。このベーン溝１１はシリンダの内周面６側のみならず、フロントサイドブロック５、前記リアブロック４側にも開口され、またその底部に背圧室１２が形成されている。   The rotor 9 is a perfect circle having substantially the same diameter as the short diameter portion of the cylinder 2 and has a fitting hole 10 into which a drive shaft 18 described below is inserted at the center, and five vanes radially from the center. A groove 11 is formed. The vane groove 11 is opened not only on the inner peripheral surface 6 side of the cylinder but also on the front side block 5 and the rear block 4 side, and a back pressure chamber 12 is formed at the bottom thereof.

このベーン溝１１にベーン１３が出没自在に挿入され、背圧室１２内の圧力及びロータ９の回転により生じる遠心力により、その先端が内周面６側へ突出し、該内周面６に接触し、該ベーン１３によりシリンダ空間は複数の圧縮室１５に区画されている。   A vane 13 is inserted into the vane groove 11 so as to be able to protrude and retract, and due to the pressure in the back pressure chamber 12 and the centrifugal force generated by the rotation of the rotor 9, the tip protrudes toward the inner peripheral surface 6 side and contacts the inner peripheral surface 6. The cylinder space is partitioned into a plurality of compression chambers 15 by the vanes 13.

駆動軸１８は前記ロータ９の嵌合穴１０に嵌挿され、前記フロントサイドブロック５とリアブロック４とのそれぞれに設けられ下記に説明する滑り軸受１９a,１９bにより回転自在に支持されている。この駆動軸１８はフロントヘッド３との間にシャフトシール２０が設けられ、冷媒の漏れを防いでおり、そのシャフトシール２０から外部へ突出する先端に図示しないが電磁クラッチが取付られる。   The drive shaft 18 is inserted into the fitting hole 10 of the rotor 9 and is provided in each of the front side block 5 and the rear block 4 and is rotatably supported by slide bearings 19a and 19b described below. A shaft seal 20 is provided between the drive shaft 18 and the front head 3 to prevent leakage of the refrigerant, and an electromagnetic clutch (not shown) is attached to a tip protruding from the shaft seal 20 to the outside.

フロントヘッド３は、その内部でフロントサイドブロック５との間に高圧冷媒の通路とオイル分離機能を有する高圧室２２が設けられ、この高圧室２２はその下方に潤滑油が溜まるオイル溜まりとなっており、図示しない吐出孔と連通されている。   The front head 3 is provided with a high-pressure refrigerant passage and a high-pressure chamber 22 having an oil separating function between the front side block 5 and the high-pressure chamber 22 as an oil reservoir in which lubricating oil is accumulated below. And communicated with a discharge hole (not shown).

このフロントヘッド３の内側に配されたフロントサイドロック５は、シリンダ２側（ロータ側）が平坦面となっており、中心に前記駆動軸１８が挿入される挿入穴２３と、その周囲にその穴より大径で円弧形状の背圧溝２４ａ，２４ａが対称位置に２つ形成されている。   The front side lock 5 arranged on the inner side of the front head 3 has a flat surface on the cylinder 2 side (rotor side), an insertion hole 23 into which the drive shaft 18 is inserted in the center, and a periphery thereof. Two back pressure grooves 24a, 24a having a larger diameter than the hole and having an arc shape are formed at symmetrical positions.

リアブロック４は、シリンダ２とに間に吸入室（一部のみ図示）３０が設けられ、この吸入室３０は、逆止弁３１を介して外部機器と連通する吸入孔３２と連通している。このリアブロック４のシリンダ２側が平坦面となっており、中心に前記駆動軸１８が挿入される挿入穴３４と、その周囲にその穴より大径で円弧状の背圧溝２４ｂ，２４ｂが２つ形成されている。そして、前記挿入穴３４に前記駆動軸１８の端が前記したように下記に説明する滑り軸受１９ｂを介して挿入されている。   The rear block 4 is provided with a suction chamber (only part of which is shown) 30 between the cylinder 2 and the suction chamber 30 communicates with a suction hole 32 communicating with an external device via a check valve 31. . The rear block 4 has a flat surface on the cylinder 2 side, and an insertion hole 34 into which the drive shaft 18 is inserted at the center, and arc-shaped back pressure grooves 24b and 24b having a diameter larger than that of the hole around the insertion hole 34. One is formed. The end of the drive shaft 18 is inserted into the insertion hole 34 through the slide bearing 19b described below as described above.

次に、この発明に係わる構成を説明すると、図３乃至図５に示すように、滑り軸受１９ａ．１９ｂは、アルミニウム合金と異なる鉄系金属（鉄（Ｆｅ）に銅（Ｃｕ）が２.０〜４.０％、炭素（Ｃ）が０.３〜０.８％が含有されている。）により形成された円筒形のブシュで、滑り軸受１９ａは前記した挿入穴２３に圧入又は鋳込まれ、また滑り軸受１９ｂは前記した挿入穴３４に圧入又は鋳込まれている。   Next, the structure according to the present invention will be described. As shown in FIGS. 19b is an iron-based metal different from an aluminum alloy (iron (Fe) contains 2.0 to 4.0% of copper (Cu) and 0.3 to 0.8% of carbon (C)). The sliding bearing 19a is press-fitted or cast into the insertion hole 23, and the sliding bearing 19b is press-fitted or cast into the insertion hole 34.

この両滑り軸受１９ａ，１９ｂは、ロータ側へ突出し、フロントサイドブロック５の平坦面より、リアブロック４の平坦面より約５０μｍの突出寸法Ｃで突出している。従って、突出端は、前記ロータ９の両側面に接触することになり、ロータ９のスラスト方向を規制することになる。これによりロータ９と両ブロック４，５との間にＣ寸法の隙間が常時作られることになる。しかしこの隙間Ｃに潤滑油が満たされることから圧力の吹き抜けが起きることがない。   The sliding bearings 19a and 19b protrude to the rotor side and protrude from the flat surface of the front side block 5 with a protrusion dimension C of about 50 μm from the flat surface of the rear block 4. Accordingly, the protruding end comes into contact with both side surfaces of the rotor 9 and restricts the thrust direction of the rotor 9. As a result, a gap of C dimension is always created between the rotor 9 and the blocks 4 and 5. However, since the gap C is filled with lubricating oil, no pressure blow-off occurs.

隙間があることで、同じアルミニウム合金の両ブロック４，５とロータ９とは接触せず焼付ことが防がれる。当然ながら両ブロック４，５の平坦面のテフロン（登録商標）加工は施されていない。この隙間を構成する突出寸法Ｃは１００μｍ程が最大で、これ以上となると圧力の吹き抜けが生じてしまう。また５μｍ以下であると、ロータと駆動軸１８の取付公差にて隙間がなくなり、ロータ９と両ブロック４，５が接触することを回避できない。   Since there is a gap, the blocks 4 and 5 of the same aluminum alloy and the rotor 9 do not come into contact with each other and seizure is prevented. Naturally, the Teflon (registered trademark) processing of the flat surfaces of the blocks 4 and 5 is not performed. The maximum projecting dimension C constituting this gap is about 100 μm, and if it exceeds this, pressure blows out. If it is 5 μm or less, there is no gap due to the mounting tolerance between the rotor and the drive shaft 18, and it is impossible to avoid contact between the rotor 9 and the blocks 4, 5.

なお、滑り軸受１９ａ．１９ｂは、鉄系金属で作られているが、他に銅系金属、樹脂材料により製造しても良い。   The slide bearing 19a. 19b is made of an iron-based metal, but may be made of a copper-based metal or a resin material.

この発明の実施例を示す断面図である。It is sectional drawing which shows the Example of this invention. 同上の切断方向を異にする断面図である。It is sectional drawing which makes a cutting direction same as the above different. フロントサイドブロックの挿入穴に取付られた滑り軸受の突出状態を説明する拡大断面図である。It is an expanded sectional view explaining the protrusion state of the slide bearing attached to the insertion hole of the front side block. リアブロックの挿入穴に取付られた滑り軸受の突出状態を説明する拡大断面図である。It is an expanded sectional view explaining the protrusion state of the slide bearing attached to the insertion hole of a rear block. フロントサイドブロック又はリアブロックの挿入穴に取付られた滑り軸受の斜視図である。It is a perspective view of the sliding bearing attached to the insertion hole of a front side block or a rear block.

符号の説明Explanation of symbols

１ ベーン型圧縮機
２ シリンダ
３ フロントヘッド
４ リアブロック
５ フロントサイドブロック
６ 内周面
９ ロータ
１１ ベーン溝
１３ ベーン
１８ 駆動軸
１９ａ，１９ｂ 滑り軸受
３４ 挿入穴 DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Cylinder 3 Front head 4 Rear block 5 Front side block 6 Inner peripheral surface 9 Rotor 11 Vane groove 13 Vane 18 Drive shaft 19a, 19b Sliding bearing 34 Insertion hole

Claims (6)

両側をブロックにより閉塞されたシリンダと、このシリンダ内に回転可能に収容されたロータと、このロータに形成の複数のベーン溝内を摺動するベーンと、
前記両ブロックに支えられ、前記ロータを支える駆動軸とより成るベーン型圧縮機において、
前記駆動軸は滑り軸受を介して前記両ブロックに支えられると共に、この滑り軸受を両ブロックの平端面からロータ側に突出させたことを特徴とするベーン型圧縮機。 A cylinder closed on both sides by a block, a rotor rotatably accommodated in the cylinder, and a vane sliding in a plurality of vane grooves formed in the rotor;
In the vane type compressor that is supported by the both blocks and includes a drive shaft that supports the rotor,
The drive shaft is supported by the two blocks via sliding bearings, and the sliding bearings protrude from the flat end surfaces of both blocks to the rotor side. 前記滑り軸受は円筒形のブシュであることを特徴とする請求項１記載のベーン型圧縮機。   2. The vane compressor according to claim 1, wherein the sliding bearing is a cylindrical bush. 前記滑り軸受の両ブロックの平端面からの突出寸法は、上限で１００μｍ、下限で５μｍの範囲内とすることを特徴とする請求項１記載のベーン型圧縮機。   The vane type compressor according to claim 1, wherein the projecting dimension from the flat end surface of both blocks of the slide bearing is in the range of 100 µm at the upper limit and 5 µm at the lower limit. 前記滑り軸受は鉄系材料により製造されることを特徴とする請求項１記載のベーン型圧縮機。   The vane compressor according to claim 1, wherein the sliding bearing is made of an iron-based material. 前記滑り軸受はブロックに圧入して装着されることを特徴とする請求項１又は２記載のベーン型圧縮機。   The vane type compressor according to claim 1 or 2, wherein the slide bearing is press-fitted into a block. 前記滑り軸受はブロックに鋳込んで装着されることを特徴とする請求項１又は２記載のベーン型圧縮機。
The vane type compressor according to claim 1 or 2, wherein the slide bearing is cast into a block.
JP2005254456A 2005-09-02 2005-09-02 Vane type compressor Pending JP2007064163A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2005254456A JP2007064163A (en) 2005-09-02 2005-09-02 Vane type compressor
PCT/JP2006/316347 WO2007029481A1 (en) 2005-09-02 2006-08-22 Vane compressor

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JP2005254456A JP2007064163A (en) 2005-09-02 2005-09-02 Vane type compressor

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WO2011080924A1 (en) 2009-12-29 2011-07-07 株式会社ヴァレオジャパン Lubricating oil supply structure of vane-type compressor
WO2014208398A1 (en) 2013-06-27 2014-12-31 株式会社ヴァレオジャパン Vane compressor
CN108691767A (en) * 2017-03-31 2018-10-23 株式会社丰田自动织机 Blade-tape compressor

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Publication number Priority date Publication date Assignee Title
WO2011080924A1 (en) 2009-12-29 2011-07-07 株式会社ヴァレオジャパン Lubricating oil supply structure of vane-type compressor
WO2014208398A1 (en) 2013-06-27 2014-12-31 株式会社ヴァレオジャパン Vane compressor
CN105308323A (en) * 2013-06-27 2016-02-03 法雷奥日本株式会社 Vane compressor
CN108691767A (en) * 2017-03-31 2018-10-23 株式会社丰田自动织机 Blade-tape compressor
CN108691767B (en) * 2017-03-31 2020-04-07 株式会社丰田自动织机 Vane type compressor

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