JP2003120563A - Gas compressor - Google Patents
Gas compressorInfo
- Publication number
- JP2003120563A JP2003120563A JP2001311896A JP2001311896A JP2003120563A JP 2003120563 A JP2003120563 A JP 2003120563A JP 2001311896 A JP2001311896 A JP 2001311896A JP 2001311896 A JP2001311896 A JP 2001311896A JP 2003120563 A JP2003120563 A JP 2003120563A
- Authority
- JP
- Japan
- Prior art keywords
- discharge
- discharge valve
- chamber
- valve
- gas compressor
- 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.)
- Pending
Links
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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
- F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Check Valves (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、カーエアコンシス
テムの一部として車両に搭載される、または空調システ
ムの一部として室外機に搭載される気体圧縮機に関し、
特に、圧縮室から吐出される高圧ガスの逆流を防止する
吐出弁の耐久性を高めるとともに、吐出弁の薄肉化が図
れ、吐出弁の開閉動作特性を高めた気体圧縮機に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas compressor mounted on a vehicle as a part of a car air conditioner system or mounted on an outdoor unit as a part of an air conditioning system,
In particular, the present invention relates to a gas compressor that enhances the durability of a discharge valve that prevents the backflow of high-pressure gas discharged from a compression chamber, reduces the thickness of the discharge valve, and improves the opening / closing operation characteristics of the discharge valve.
【０００２】[0002]
【従来の技術】図６は、この種従来の吐出弁を用いた気
体圧縮機の断面図である。同図の気体圧縮機は一端開口
型のコンプレッサケーシング１内に圧縮機構部Ｃを収容
した構造であり、この圧縮機構部Ｃとコンプレッサケー
シング１の開口端に取り付けられたフロントヘッド１−
２との間が低圧の吸入室６（低圧室）として構成され、
また、コンプレッサケーシング１の内側密閉端と圧縮機
構部Ｃとの間が高圧の吐出室５（高圧室）として構成さ
れている。2. Description of the Related Art FIG. 6 is a sectional view of a gas compressor using a conventional discharge valve of this kind. The gas compressor shown in FIG. 1 has a structure in which a compression mechanism portion C is housed in a compressor casing 1 having an opening at one end, and the compression mechanism portion C and a front head 1 attached to the opening end of the compressor casing 1.
2 is configured as a low pressure suction chamber 6 (low pressure chamber),
A high pressure discharge chamber 5 (high pressure chamber) is formed between the inner closed end of the compressor casing 1 and the compression mechanism portion C.
【０００３】圧縮機構部Ｃは内周略楕円筒状のシリンダ
２を有し、このシリンダ２の両端面にはサイドブロック
３、４が取り付けられ、また、そのシリンダ２の内側に
はロータ７が横架されており、このロータ７はその軸心
のロータ軸８とフロント側サイドブロック３の軸受９及
びリア側サイドブロックの軸受（図示省略）を介して回
転可能に支持されている。The compression mechanism portion C has a cylinder 2 having a substantially elliptic cylinder shape on the inner circumference. Side blocks 3 and 4 are attached to both end faces of the cylinder 2, and a rotor 7 is provided inside the cylinder 2. The rotor 7 is laid horizontally, and is rotatably supported via a rotor shaft 8 of its axis, a bearing 9 of the front side block 3 and a bearing (not shown) of the rear side block.
【０００４】図７に示すように、ロータ７には、複数の
ベーン溝１１が放射状に形成され、これらのベーン溝１
１にはそれぞれ１つずつベーン１２が摺動可能に装着さ
れており、ロータ７の回転による遠心力とベーン背圧で
各ベーン１２はシリンダ２の内周面と摺接しながら回転
する。As shown in FIG. 7, a plurality of vane grooves 11 are radially formed in the rotor 7, and these vane grooves 1 are formed.
One vane 12 is slidably attached to each of the vanes 1, and each vane 12 rotates while slidingly contacting the inner peripheral surface of the cylinder 2 by the centrifugal force and the vane back pressure generated by the rotation of the rotor 7.
【０００５】シリンダ２の内側空間は、シリンダ２内
壁、サイドブロック３、４内面、ロータ７外周面により
画成され、この画成された小室が圧縮室（シリンダ室）
１３であり、このようなシリンダ２内側の圧縮室１３
は、ロータ７並びにベーン１２が図７中矢印イの方向に
回転することにより、吸入室６から吸入した冷媒ガスを
圧縮室１３内で圧縮して吐出室５側へ吐出する。The inner space of the cylinder 2 is defined by the inner wall of the cylinder 2, the inner surfaces of the side blocks 3 and 4, and the outer peripheral surface of the rotor 7. The small chamber thus defined is a compression chamber (cylinder chamber).
13, such a compression chamber 13 inside the cylinder 2
7 rotates the rotor 7 and the vane 12 in the direction of arrow A in FIG. 7 to compress the refrigerant gas sucked from the suction chamber 6 in the compression chamber 13 and discharge the compressed refrigerant gas to the discharge chamber 5 side.
【０００６】すなわち、吸入室６内の低圧冷媒ガスが、
シリンダ２等の吸入通路１４とサイドブロック３、４の
吸入口１５を介して圧縮室１３へ吸入される。そして、
ロータ７並びにベーン１２の回転により、圧縮室１３内
の低圧ガスを圧縮する。圧縮された高圧冷媒ガスの圧力
により圧縮室１３の内圧が上昇するとともに、この圧縮
室１３の内圧が吐出孔１６を塞いでいる吐出弁１７に作
用し、吐出弁１７が開き、圧縮室１３内の高圧冷媒ガス
は、吐出孔１６からシリンダ２外部空間の吐出チャンバ
室１８、サイドブロック３の高圧ガス通路１９、及び油
分離器２０を経て吐出室５側へ吐出される。That is, the low pressure refrigerant gas in the suction chamber 6 is
It is sucked into the compression chamber 13 via the suction passage 14 of the cylinder 2 and the like and the suction ports 15 of the side blocks 3 and 4. And
The rotation of the rotor 7 and the vanes 12 compresses the low pressure gas in the compression chamber 13. The internal pressure of the compression chamber 13 rises due to the pressure of the compressed high-pressure refrigerant gas, and the internal pressure of the compression chamber 13 acts on the discharge valve 17 closing the discharge hole 16 to open the discharge valve 17 and The high-pressure refrigerant gas is discharged from the discharge hole 16 to the discharge chamber 5 side through the discharge chamber chamber 18 in the outer space of the cylinder 2, the high-pressure gas passage 19 of the side block 3, and the oil separator 20.
【０００７】尚、吐出チャンバ室１８内に吐出した高圧
冷媒ガス中には、潤滑用等のオイルがミストの状態で含
まれているが、そのオイル成分は、油分離器２０の金網
等からなる油分離フィルター２１との衝突により分離捕
獲され、かつ吐出室５底部のオイル溜まり２２に滴下し
貯留される。また、オイル溜まり２２には、吐出室５内
に吐出した高圧冷媒ガスの圧力が作用しており、このよ
うな吐出圧力Ｐｄの作用するオイル溜まり２２のオイル
は、サイドブロック３、４やシリンダ２の油穴２３、軸
受９のクリアランス、サイドブロック３、４のシリンダ
対向面側に形成されたサライ溝２４をその順に通って、
最終的にベーン溝１１の底部へ供給され、かつ、ベーン
背圧としてベーン１２の底部に作用する。The high-pressure refrigerant gas discharged into the discharge chamber 18 contains oil for lubrication or the like in the form of mist, and the oil component is composed of a wire mesh of the oil separator 20. It is separated and captured by the collision with the oil separation filter 21, and is dropped and stored in the oil sump 22 at the bottom of the discharge chamber 5. The pressure of the high-pressure refrigerant gas discharged into the discharge chamber 5 acts on the oil sump 22, and the oil in the oil sump 22 on which such discharge pressure Pd acts acts on the side blocks 3 and 4 and the cylinder 2. Through the oil hole 23, the clearance of the bearing 9 and the saray groove 24 formed on the cylinder facing surface side of the side blocks 3 and 4, in that order,
Finally, it is supplied to the bottom of the vane groove 11 and acts on the bottom of the vane 12 as a vane back pressure.
【０００８】ところで、上記のように圧縮室１３の内圧
変化により、吐出弁１７が開閉動作し、圧縮室１３内の
高圧冷媒ガスを吐出チャンバ室１８側に吐出させる従来
構造のものにあっては、図８に示すように、吐出弁１７
は、バルブサポート１７ａにより片持ち式に一端側が支
持され、気体圧縮機の運転停止時、すなわち、吐出チャ
ンバ室１８の内圧Ｐ１と圧縮室１３の内圧Ｐ２が等しい
時は、吐出弁１７はフラット状にシリンダ２の外側面と
当接している。尚、吐出孔１６の開口縁部は、テーパー
状の面取り部１６ａが設けられている。By the way, as described above, in the conventional structure in which the discharge valve 17 is opened / closed by the change in the internal pressure of the compression chamber 13 to discharge the high pressure refrigerant gas in the compression chamber 13 to the discharge chamber 18 side. , As shown in FIG.
Is supported in a cantilevered manner by the valve support 17a, and the discharge valve 17 has a flat shape when the operation of the gas compressor is stopped, that is, when the internal pressure P1 of the discharge chamber chamber 18 and the internal pressure P2 of the compression chamber 13 are equal. Is in contact with the outer surface of the cylinder 2. A tapered chamfered portion 16a is provided at the opening edge of the discharge hole 16.
【０００９】そして、気体圧縮機の運転中、圧縮室１３
の内圧Ｐ２が吐出チャンバ室１８の内圧Ｐ１より高い
時、Ｐ１＜Ｐ２の場合、吐出弁１７が開放され、吐出チ
ャンバ室１８側に高圧ガスが吐出される。この時、吐出
弁１７は、図９中点線で示す位置まで持ち上がり、吐出
孔１６から吐出チャンバ室１８側に高圧ガスが吐出され
る。During operation of the gas compressor, the compression chamber 13
When the internal pressure P2 is higher than the internal pressure P1 of the discharge chamber 18, if P1 <P2, the discharge valve 17 is opened and the high pressure gas is discharged to the discharge chamber 18 side. At this time, the discharge valve 17 is lifted up to the position shown by the dotted line in FIG. 9, and the high pressure gas is discharged from the discharge hole 16 to the discharge chamber 18 side.
【００１０】一方、圧縮室１３の内圧Ｐ２が低い時、Ｐ
１＞Ｐ２の場合、吐出チャンバ室１８側から高圧ガスが
吐出孔１６を通じて圧縮室１３に逆流しないように、図
９中実線で示すように吐出弁１７は、吐出孔１６内に押
し付けられ、この時の内圧差に応じた吸引力により、吐
出弁１７は湾曲状に撓み変形する。On the other hand, when the internal pressure P2 of the compression chamber 13 is low, P
In the case of 1> P2, the discharge valve 17 is pressed into the discharge hole 16 as indicated by the solid line in FIG. 9 so that the high pressure gas does not flow back into the compression chamber 13 through the discharge hole 16 from the discharge chamber chamber 18 side. The discharge valve 17 is bent and deformed into a curved shape by the suction force according to the internal pressure difference at that time.
【００１１】[0011]
【発明が解決しようとする課題】このように、気体圧縮
機における吐出弁１７は、排出された高圧ガスが圧縮室
１３内に逆流しないように吐出チャンバ室１８の内圧Ｐ
１に比べ、圧縮室１３内の内圧Ｐ２が低くなれば、吐出
弁１７が撓み変形して吐出孔１６内に押し込まれる。こ
の時、吐出弁１７に対する弁座部分は吐出孔１６の面取
り部１６ａにおける上縁コーナー部（図９中符号ａで示
す）であり、吐出弁１７に対してエッヂ当たりし、いわ
ゆる線接触状態であるため、この線接触部位に応力が局
部的に集中し、吐出弁割れが発生しやすいという不具合
がある。As described above, the discharge valve 17 in the gas compressor has the internal pressure P of the discharge chamber 18 so that the discharged high pressure gas does not flow back into the compression chamber 13.
When the internal pressure P2 in the compression chamber 13 becomes lower than that in 1, the discharge valve 17 is flexibly deformed and pushed into the discharge hole 16. At this time, the valve seat portion for the discharge valve 17 is the upper edge corner portion (indicated by reference character a in FIG. 9) of the chamfered portion 16a of the discharge hole 16, and the edge hits the discharge valve 17 in a so-called line contact state. Therefore, there is a problem that stress is locally concentrated on the line contact portion, and the discharge valve is easily cracked.
【００１２】この対策として、吐出弁１７の板厚を厚く
設定して機械強度をもたせた場合、圧縮室１３の内圧Ｐ
２が吐出チャンバ室１８の内圧Ｐ１に比べ高圧になった
際、吐出弁１７を開放するタイミングが遅れ、圧縮室１
３内が過圧縮状態となり、気体圧縮機の動力ロスが大き
いという問題点が指摘されている。As a countermeasure against this, when the plate thickness of the discharge valve 17 is set to be thick so as to have mechanical strength, the internal pressure P of the compression chamber 13 is increased.
2 becomes higher than the internal pressure P1 of the discharge chamber chamber 18, the timing of opening the discharge valve 17 is delayed and the compression chamber 1
It has been pointed out that the inside of 3 becomes an over-compression state and the power loss of the gas compressor is large.
【００１３】本発明は、上記問題点を解決するためにな
されたもので、気体圧縮機における吐出チャンバ室から
圧縮室側への高圧ガスの逆流を防ぐ吐出弁の吐出弁割れ
を抑え、耐久性を高めることができ、しかも、吐出弁の
薄肉化を可能とすることで吐出弁の開閉動作特性を向上
させることができ、動力ロスの少ない気体圧縮機を提供
することを目的とする。The present invention has been made to solve the above-mentioned problems, and suppresses discharge valve cracking of the discharge valve that prevents backflow of high-pressure gas from the discharge chamber chamber to the compression chamber side in a gas compressor, and improves durability. It is also possible to improve the open / close operation characteristics of the discharge valve by enabling the discharge valve to be made thinner, and to provide a gas compressor with less power loss.
【００１４】[0014]
【課題を解決するための手段】上記目的を達成するため
に、この出願の請求項１に記載の発明は、一対のサイド
ブロック間に介挿された内周略楕円筒状のシリンダと、
上記シリンダ内に回転可能に横架されたロータと、上記
ロータに放射状に嵌め込まれ、ロータの回転によりシリ
ンダの周面と摺接する複数のベーンと、上記シリンダ、
サイドブロック、ロータにより画成される圧縮室と、こ
の圧縮室内で圧縮された高圧ガスが吐出孔を通じて吐出
される吐出チャンバ室と、開閉動作することにより高圧
ガスの吐出を行なうとともに、高圧ガスの逆流を防ぐ吐
出弁とを有し、前記吐出弁と当接する弁座部分には、吐
出弁が撓み変形して吐出孔内に押し込まれる時、吐出弁
と面接触状態を維持できるＲ加工部が設けられているこ
とを特徴とする。In order to achieve the above-mentioned object, the invention according to claim 1 of the present application is a cylinder having an inner peripheral substantially elliptical cylinder inserted between a pair of side blocks,
A rotor rotatably laterally installed in the cylinder; a plurality of vanes radially fitted to the rotor and slidingly contacting a peripheral surface of the cylinder due to rotation of the rotor;
The compression chamber defined by the side block and the rotor, the discharge chamber chamber in which the high-pressure gas compressed in the compression chamber is discharged through the discharge hole, and the high-pressure gas is discharged by opening and closing, and the high-pressure gas is discharged. The valve seat portion, which has a discharge valve for preventing backflow, has an R processing portion that can maintain a surface contact state with the discharge valve when the discharge valve is bent and deformed and is pushed into the discharge hole. It is characterized by being provided.
【００１５】更に、この出願の請求項２に記載の発明
は、Ｒ加工部は、吐出孔の面取り部の上縁コーナー部に
丸みをもたせるＲ加工により形成されていることを特徴
とする。Further, the invention according to claim 2 of the present application is characterized in that the R-processed portion is formed by the R-processing for rounding the upper edge corner portion of the chamfered portion of the discharge hole.
【００１６】更に、この出願の請求項３に記載の発明
は、Ｒ加工部は、吐出孔の面取り部に凹状、あるいは凸
状のＲ加工により形成されていることを特徴とする。Further, the invention according to claim 3 of the present application is characterized in that the R processing portion is formed in the chamfered portion of the discharge hole by concave or convex R processing.
【００１７】更に、この出願の請求項４に記載の発明
は、Ｒ加工部は、吐出孔の面取り部に外側を凸状、内側
を凹状のＲ加工が連接状に形成されていることを特徴と
する。Further, the invention according to claim 4 of this application is characterized in that the R processing portion is formed such that the chamfered portion of the discharge hole is formed such that the R processing having a convex shape on the outer side and a concave shape on the inner side is connected. And
【００１８】そして、本発明によれば、吐出孔の吐出チ
ャンバ側開口縁部の弁座部分には、Ｒ加工が施されてい
ることにより、圧縮室の内圧が吐出チャンバ室の内圧に
比べ低圧になった時、吐出弁が吐出孔に押し込まれる
が、吐出弁は、開口縁部の弁座面と面接触状態を維持し
て接触するため、従来のように吐出弁とシリンダ弁座部
分とが線接触状態にならない。従って、吐出弁に応力が
局部的に集中することがなく、応力を分散させることに
より、吐出弁割れを可及的に防止できる。Further, according to the present invention, since the valve seat portion of the discharge chamber-side opening edge portion of the discharge hole is rounded, the internal pressure of the compression chamber is lower than the internal pressure of the discharge chamber. However, the discharge valve is pushed into the discharge hole, but since the discharge valve maintains a surface contact with the valve seat surface at the opening edge, it makes contact with the discharge valve and the cylinder valve seat part as in the past. Does not come into line contact. Therefore, the stress is not locally concentrated on the discharge valve, and the stress can be dispersed to prevent cracking of the discharge valve as much as possible.
【００１９】更に、高圧ガスの圧縮室内への逆流を防止
するように、吐出弁が吐出孔に押し込まれる際、吐出弁
と弁座面とは面接触状態であり、吐出弁にかかる負荷を
分散することができるため、吐出弁の薄肉化を図ること
ができ、吐出弁の開閉動作特性を向上させることから、
圧縮室内が過圧縮状態にならず、動力のロスが少ない。Further, when the discharge valve is pushed into the discharge hole so that the high pressure gas is prevented from flowing back into the compression chamber, the discharge valve and the valve seat surface are in surface contact with each other, and the load applied to the discharge valve is dispersed. Therefore, it is possible to reduce the thickness of the discharge valve and improve the opening / closing operation characteristics of the discharge valve.
The compression chamber does not become over-compressed, resulting in less power loss.
【００２０】[0020]
【発明の実施の形態】以下、この発明に係る気体圧縮機
の好適な実施の形態について、図１乃至図５を基に詳細
に説明する。BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, preferred embodiments of a gas compressor according to the present invention will be described in detail with reference to FIGS.
【００２１】図１は本発明に係る気体圧縮機における吐
出弁機構の要部を示す断面図であり、気体圧縮機の運転
停止時、すなわち、圧縮室と吐出チャンバ室との内圧が
等しい時の状態を示す。FIG. 1 is a sectional view showing a main part of a discharge valve mechanism in a gas compressor according to the present invention. When the operation of the gas compressor is stopped, that is, when the internal pressures of the compression chamber and the discharge chamber chamber are equal to each other. Indicates the status.
【００２２】まず、この気体圧縮機の基本的な構成につ
いて、図６及び図７を用いて説明すると、コンプレッサ
ケーシング１内に圧縮機構部Ｃが収容され、この圧縮機
構部Ｃは端面にサイドブロック３、４を取り付けたシリ
ンダ２を有し、該シリンダ２内にはロータ７が回転可能
に配置され、ロータ７の外周面に放射状に形成された複
数のベーン溝１１内にはベーン１２が１つずつ配置さ
れ、ロータ７の回転により、ベーン１２はベーン溝１１
内を摺動し、かつロータ７の外周面からシリンダ２の内
周面に向かって出没可能に設けられていること、及び、
シリンダ２、サイドブロック３、４及びロータ７により
画成されたシリンダ２内側の小室が圧縮室（シリンダ
室）１３であり、この圧縮室１３はロータ７並びにベー
ン１２の回転により、吸入室（低圧室）６の冷媒ガスを
吸入し圧縮すること等は従来と同様なため、従来と同一
部分には同一符号を付し、その詳細な説明は省略する。First, the basic structure of the gas compressor will be described with reference to FIGS. 6 and 7. The compressor mechanism C is housed in the compressor casing 1, and the compressor mechanism C has a side block on the end face. A cylinder 2 having three and four attached thereto is provided, a rotor 7 is rotatably arranged in the cylinder 2, and one vane 12 is provided in a plurality of vane grooves 11 radially formed on the outer peripheral surface of the rotor 7. They are arranged one by one, and when the rotor 7 rotates, the vanes 12 become the vane grooves 11
It is provided so as to slide inside and to be retractable from the outer peripheral surface of the rotor 7 toward the inner peripheral surface of the cylinder 2, and
A small chamber inside the cylinder 2 defined by the cylinder 2, the side blocks 3, 4 and the rotor 7 is a compression chamber (cylinder chamber) 13, and the compression chamber 13 is rotated by the rotor 7 and the vane 12 so that the suction chamber (low pressure Since the refrigerant gas in the chamber 6 is sucked and compressed in the same manner as in the conventional case, the same parts as those in the conventional case are designated by the same reference numerals, and detailed description thereof will be omitted.
【００２３】本実施形態の気体圧縮機においても、吐出
チャンバ室１８は、シリンダ楕円短径部付近のシリンダ
外周面を一部切り欠いてなる切り欠き部２ａ、サイドブ
ロック３、４、及びコンプレッサケーシング１によって
仕切られた空間からなり、このような吐出チャンバ室１
８に吐出弁１７が設けられているとともに、圧縮室１３
で圧縮された高圧の冷媒ガスは、その吐出弁１７を介し
て吐出チャンバ室１８へ吐出されるが、この吐出弁１７
に対する弁座部分の構造が従来と異なる。Also in the gas compressor of this embodiment, the discharge chamber chamber 18 has a notch 2a formed by partially notching the outer peripheral surface of the cylinder near the elliptic minor axis of the cylinder, the side blocks 3 and 4, and the compressor casing. The discharge chamber chamber 1 is composed of a space partitioned by 1.
8 is provided with a discharge valve 17, and the compression chamber 13
The high-pressure refrigerant gas compressed by is discharged to the discharge chamber chamber 18 via the discharge valve 17.
The structure of the valve seat portion is different from the conventional one.
【００２４】すなわち、本実施形態における気体圧縮機
においては、図１に示す吐出弁１７及びこの吐出弁１７
を受ける弁座構成を採用している。That is, in the gas compressor of this embodiment, the discharge valve 17 shown in FIG.
It adopts a valve seat configuration that receives.
【００２５】この吐出弁１７の弁座部分は、吐出孔１６
の開口縁部であり、シリンダ２に設けられている吐出孔
１６の吐出チャンバ室１８側開口は、開口縁部に面取り
部１６ａが設けられているのは従来と同様であるが、こ
の面取り部１６ａとシリンダ２壁面との境界部が従来の
線状ではなく、丸みをもたせたＲ加工部３０として形成
されている。The valve seat portion of the discharge valve 17 has a discharge hole 16
The chamfered portion of the discharge hole 16 provided in the cylinder 2 is the chamfered portion 16a at the side of the discharge chamber 18 that is provided with the chamfered portion 16a. The boundary between 16a and the wall surface of the cylinder 2 is formed as a rounded R processing portion 30 instead of the conventional linear shape.
【００２６】尚、図１は、気体圧縮機の運転停止時であ
り、吐出チャンバ室１８の内圧Ｐ１と圧縮室１３の内圧
Ｐ２とが同一であるため、吐出弁１７はフラット状にな
っている。Note that FIG. 1 shows a state in which the operation of the gas compressor is stopped, and since the internal pressure P1 of the discharge chamber 18 and the internal pressure P2 of the compression chamber 13 are the same, the discharge valve 17 is flat. .
【００２７】そして、気体圧縮機の運転時には、ロータ
７の回転による遠心力とベーン背圧が作用し、ベーン１
２が圧縮室１３内のガスを圧縮するため、圧縮室１３の
内圧Ｐ２が可変し、図２に示すように、吐出チャンバ室
１８の内圧Ｐ１よりも圧縮室１３内の内圧Ｐ２が大きい
場合には、圧縮室１３内の高圧ガスが吐出孔１６を通し
て吐出チャンバ室１８側に吐出できるように吐出弁１７
が図２中点線で示す位置に持ち上がる。During operation of the gas compressor, centrifugal force and vane back pressure due to the rotation of the rotor 7 act and the vane 1
2 compresses the gas in the compression chamber 13, the internal pressure P2 of the compression chamber 13 changes, and as shown in FIG. 2, when the internal pressure P2 of the compression chamber 13 is larger than the internal pressure P1 of the discharge chamber chamber 18. The discharge valve 17 allows the high-pressure gas in the compression chamber 13 to be discharged to the discharge chamber 18 side through the discharge hole 16.
Is lifted to the position shown by the dotted line in FIG.
【００２８】逆に、吐出チャンバ室１８の内圧Ｐ１より
も圧縮室１３の内圧Ｐ２が低圧である場合には、高圧ガ
スが圧縮室１３内に逆流するのを防止するように、薄肉
状のバネ鋼板を素材とする吐出弁１７は、撓み変形し
て、図２中実線で示すように吐出弁１７が吐出孔１６内
に押し込まれる。On the contrary, when the internal pressure P2 of the compression chamber 13 is lower than the internal pressure P1 of the discharge chamber 18, the thin-walled spring is formed so as to prevent the high-pressure gas from flowing back into the compression chamber 13. The discharge valve 17 made of a steel plate is flexibly deformed, and the discharge valve 17 is pushed into the discharge hole 16 as shown by the solid line in FIG.
【００２９】この時、図１で拡大して示すように、吐出
孔１６の面取り部１６ａとシリンダ２の外壁間はＲ加工
部３０として形成されているため、吐出孔１６開口縁部
の弁座面（Ｒ加工部３０）と吐出弁１７とは面接触状態
を維持して吐出弁１７が吐出孔１６側に押し付けられる
ことになる。At this time, as shown in an enlarged view in FIG. 1, since a rounded portion 30 is formed between the chamfered portion 16a of the discharge hole 16 and the outer wall of the cylinder 2, the valve seat at the opening edge portion of the discharge hole 16 is formed. The surface (R processing portion 30) and the discharge valve 17 are kept in surface contact with each other, so that the discharge valve 17 is pressed against the discharge hole 16 side.
【００３０】従って、従来生じていたリング状の線接触
状態を回避できるため、吐出弁１７が吐出孔１６内に押
圧された際の応力を面接触部分に分散でき、負荷荷重が
局部的に集中することがなく、吐出弁割れを可及的に防
止できることから、吐出弁１７の耐久性を高めることが
できる。Therefore, since the ring-shaped line contact state which has conventionally occurred can be avoided, the stress when the discharge valve 17 is pressed into the discharge hole 16 can be dispersed to the surface contact portion, and the load load is locally concentrated. Since it is possible to prevent the discharge valve from cracking as much as possible, the durability of the discharge valve 17 can be improved.
【００３１】そして、吐出弁１７に対する応力荷重の部
分集中を回避できるため、吐出弁１７の薄肉化が図れる
ことにより、吐出弁１７の開閉動作特性を向上させるこ
とで圧縮室１３内での過圧縮を未然に防止でき、動力ロ
スも少なくて済む。Since partial concentration of the stress load on the discharge valve 17 can be avoided, the discharge valve 17 can be made thinner, and the opening / closing operation characteristics of the discharge valve 17 can be improved to thereby cause overcompression in the compression chamber 13. Can be prevented and power loss can be reduced.
【００３２】次に、図３乃至図５は、吐出弁１７に対す
る弁座部分として、吐出孔１６の面取り部１６ａに着目
した変形例を示す。Next, FIGS. 3 to 5 show modifications in which the chamfered portion 16a of the discharge hole 16 is focused as a valve seat portion for the discharge valve 17.
【００３３】図３は、面取り部１６ａにＲ状肉盛りを施
したＲ加工部３１ａが形成されている。また、図４は、
面取り部１６ａにＲ状肉抜きを施したＲ加工部３１ｂが
形成されている。In FIG. 3, the chamfered portion 16a is formed with an R-processed portion 31a having an R-shaped padding. In addition, FIG.
An R-processed portion 31b is formed by rounding the chamfered portion 16a.
【００３４】従って、圧縮室１３内の内圧Ｐ２が低い
時、高圧ガスが圧縮室１３内に逆流しないように吐出弁
１７が撓み変形して吐出孔１６内に押し込まれるが、図
３，図４に示すＲ加工部３１ａ，３１ｂにより、吐出弁
１７と吐出孔１６周囲の弁座部分が面接触状態を維持で
きるため、上述したエッヂ部分に丸みをもたせるＲ加工
部３０の機能と同様に、吐出弁１７の撓み変形時におけ
る接触圧を分散させることができ、応力の局部集中を避
けて、吐出弁１７の耐久性を高めることができるという
Ｒ加工部３０と同じ作用効果がある。Therefore, when the internal pressure P2 in the compression chamber 13 is low, the discharge valve 17 is flexibly deformed and pushed into the discharge hole 16 so that the high pressure gas does not flow back into the compression chamber 13. Since the R processing portions 31a and 31b shown in FIG. 5 can maintain the surface contact state between the discharge valve 17 and the valve seat portion around the discharge hole 16, the discharge processing portion 30 has the same function as the R processing portion 30 for rounding the edge portion as described above. The contact pressure at the time of flexural deformation of the valve 17 can be dispersed, the local concentration of stress can be avoided, and the durability of the discharge valve 17 can be enhanced, which is the same effect as the R-processed portion 30.
【００３５】また、このことにより、吐出弁１７の薄肉
化が図れ、吐出弁１７の開閉動作特性を向上させること
で圧縮室１３内での過圧縮を防止し、動力ロスを防ぐこ
とができる。Further, as a result, the discharge valve 17 can be made thinner, and the open / close operation characteristics of the discharge valve 17 can be improved to prevent overcompression in the compression chamber 13 and prevent power loss.
【００３６】更に、図５に示すように、吐出孔１６の面
取り部１６ａに凸状のＲ加工部３１ｃと凹状のＲ加工部
３１ｄを併用しても良く、図５に示すタイプのもので
は、吐出弁１７が撓み変形する際、吐出弁１７と弁座部
分の接触面積をより多く確保することができ、吐出弁１
７と弁座部分との接触圧をより広範に分散させることが
できるため、耐久性をより高めることができる。Further, as shown in FIG. 5, the chamfered portion 16a of the discharge hole 16 may be provided with a convex R-shaped portion 31c and a concave R-shaped portion 31d, and in the type shown in FIG. When the discharge valve 17 is flexibly deformed, it is possible to secure a larger contact area between the discharge valve 17 and the valve seat portion.
Since the contact pressure between 7 and the valve seat portion can be dispersed in a wider range, durability can be further enhanced.
【００３７】次に、上述した吐出弁１７及びそれを受け
る弁座部分の構成を採用した気体圧縮機の動作につい
て、図１，図６，図７を基に説明する。Next, the operation of the gas compressor that employs the above-described structure of the discharge valve 17 and the valve seat portion that receives the discharge valve 17 will be described with reference to FIGS. 1, 6 and 7.
【００３８】本実施形態の気体圧縮機にあっても、従来
と同じく、圧縮された高圧冷媒ガスの圧力により圧縮室
１３の内圧Ｐ２が上昇する。そして、この圧縮室１３の
内圧Ｐ２の上昇が吐出孔１６を塞いでいる吐出弁１７に
作用し、吐出弁１７が持ち上がり、これにより吐出孔１
６が開状態となる。そうすると、圧縮室１３内の高圧冷
媒ガスは、吐出孔１６、シリンダ２外部空間の吐出チャ
ンバ室１８、サイドブロック３の高圧ガス通路１９、及
び油分離器２０を経て吐出室５側へ吐出される。Even in the gas compressor of this embodiment, the internal pressure P2 of the compression chamber 13 increases due to the pressure of the compressed high-pressure refrigerant gas, as in the conventional case. Then, the rise of the internal pressure P2 of the compression chamber 13 acts on the discharge valve 17 closing the discharge hole 16, and the discharge valve 17 is lifted, whereby the discharge hole 1 is discharged.
6 is opened. Then, the high pressure refrigerant gas in the compression chamber 13 is discharged to the discharge chamber 5 side through the discharge hole 16, the discharge chamber chamber 18 in the outer space of the cylinder 2, the high pressure gas passage 19 of the side block 3, and the oil separator 20. .
【００３９】このようにして、圧縮室１３内の高圧冷媒
ガスが吐出されると、それまで高圧であった圧縮室１３
の内圧Ｐ２が急激に低下し、これにより吐出弁１７が吐
出孔１６内に押し込まれ、吐出孔１６を塞ぎ閉鎖する。
この時、上述したように、吐出弁１７は、吐出孔１６の
開口縁コーナー部に設けたＲ加工部３０、あるいは面取
り部１６ａに設けたＲ加工部３１ａ〜３１ｄにより、吐
出弁１７と弁座面は面接触状態を維持でき、吐出弁１７
にかかる応力の局部集中を回避して、吐出弁１７にかか
る負荷荷重を軽減でき、耐久性をアップさせることがで
きる。また、従来の線接触構造のものに比べ、吐出弁１
７閉鎖時の騒音も低減させることができる。In this way, when the high-pressure refrigerant gas in the compression chamber 13 is discharged, the compression chamber 13 which was at high pressure until then is discharged.
The internal pressure P2 of the valve suddenly drops, and the discharge valve 17 is thereby pushed into the discharge hole 16 to close and close the discharge hole 16.
At this time, as described above, the discharge valve 17 is provided with the discharge valve 17 and the valve seat by the R processed portion 30 provided at the opening edge corner portion of the discharge hole 16 or the R processed portions 31a to 31d provided at the chamfered portion 16a. The surface can maintain the surface contact state, and the discharge valve 17
It is possible to avoid the local concentration of the stress applied to the discharge valve 17, reduce the load applied to the discharge valve 17, and improve the durability. In addition, compared with the conventional line contact structure, the discharge valve 1
7. The noise at the time of closing can also be reduced.
【００４０】[0040]
【発明の効果】以上説明した通り、本発明に係る気体圧
縮機は、圧縮室で圧縮した高圧ガスを吐出チャンバ室側
に吐出するとともに、高圧ガスの逆流を防止する吐出弁
及び吐出弁の弁座部分の構成において、吐出弁の撓み変
形時、吐出弁と面接触できるように吐出孔開口縁コーナ
ー部にＲ加工部、あるいは面取り部にＲ加工部を施すこ
とで吐出弁の撓み変形時にかかる負荷荷重を低減させる
ことにより、吐出弁割れを可及的に防止でき、吐出弁の
耐久性及び信頼性を高めることができるという効果を有
する。As described above, the gas compressor according to the present invention discharges the high-pressure gas compressed in the compression chamber to the discharge chamber chamber side, and prevents the high-pressure gas from flowing backward and the valve of the discharge valve. In the configuration of the seat portion, when the discharge valve is bent and deformed, the discharge valve is bent and deformed by forming an R-processed portion at the corner portion of the opening edge of the discharge hole or a chamfered R-processed portion so that the discharge valve can make surface contact By reducing the load, the discharge valve can be prevented from cracking as much as possible, and the durability and reliability of the discharge valve can be improved.
【００４１】更に、本発明に係る気体圧縮機における吐
出弁は、弁閉鎖時、弁座部分と面接触状態を維持して接
触するため、圧縮室の内圧変化により、吐出弁が開放す
る際のタイミングに遅れ等がなく、吐出弁の開閉動作に
おける信頼性を高め、かつ過圧縮状態を未然に回避でき
ることから、動力ロスも少なくて済む等の作用効果を有
する。Further, since the discharge valve in the gas compressor according to the present invention is in contact with the valve seat portion while maintaining the surface contact state when the valve is closed, the discharge valve is opened when the internal pressure of the compression chamber changes. Since there is no delay in the timing, the reliability in the opening / closing operation of the discharge valve can be improved, and the overcompression state can be avoided in advance, there is an effect that power loss can be reduced.
【図１】図１は本発明に係る気体圧縮機における吐出弁
及び弁座部分の構成を示す運転停止時の説明図である。FIG. 1 is an explanatory diagram showing a configuration of a discharge valve and a valve seat portion in a gas compressor according to the present invention when operation is stopped.
【図２】本発明に係る気体圧縮機における吐出弁の開閉
動作を示す説明図である。FIG. 2 is an explanatory diagram showing an opening / closing operation of a discharge valve in the gas compressor according to the present invention.
【図３】本発明に係る気体圧縮機における吐出弁の弁座
部分の変形例を示す説明図である。FIG. 3 is an explanatory view showing a modified example of the valve seat portion of the discharge valve in the gas compressor according to the present invention.
【図４】本発明に係る気体圧縮機における吐出弁の弁座
部分の変形例を示す説明図である。FIG. 4 is an explanatory view showing a modified example of the valve seat portion of the discharge valve in the gas compressor according to the present invention.
【図５】本発明に係る気体圧縮機における吐出弁の弁座
部分の変形例を示す説明図である。FIG. 5 is an explanatory view showing a modified example of the valve seat portion of the discharge valve in the gas compressor according to the present invention.
【図６】従来の気体圧縮機の断面図である。FIG. 6 is a sectional view of a conventional gas compressor.
【図７】図６中VII −VII 線断面図である。7 is a sectional view taken along line VII-VII in FIG.
【図８】従来の気体圧縮機における吐出弁の構成を示す
運転停止時の説明図である。FIG. 8 is an explanatory diagram showing a configuration of a discharge valve in a conventional gas compressor when operation is stopped.
【図９】従来の気体圧縮機における吐出弁の開閉動作を
示す説明図である。FIG. 9 is an explanatory diagram showing an opening / closing operation of a discharge valve in a conventional gas compressor.
１ コンプレッサケーシング １−２ フロントヘッド ２ シリンダ ２ａ 切り欠き部 ３、４ サイドブロック ５ 吐出室 ６ 吸入室 ７ ロータ ８ ロータ軸 ９ 軸受 １１ ベーン溝 １２ ベーン １３ 圧縮室 １４ 吸入通路 １５ 吸入口 １６ 吐出孔 １６ａ 面取り部 １７ 吐出弁 １７ａ バルブサポート １８ 吐出チャンバ室 １９ 高圧ガス通路 ２０ 油分離器 ２１ 油分離フィルター ２２ オイル溜まり ２３ 油穴 ２４ サライ溝 ３０ Ｒ加工部 ３１ａ〜３１ｄ Ｒ加工部 Ｃ 圧縮機構部 Ｐ１ 吐出チャンバ室の内圧 Ｐ２ 圧縮室の内圧 1 compressor casing 1-2 front head 2 cylinders 2a Notch 3, 4 side block 5 discharge chamber 6 Inhalation chamber 7 rotor 8 rotor shaft 9 bearings 11 vane grooves 12 vanes 13 compression chamber 14 Inhalation passage 15 suction port 16 discharge holes 16a chamfer 17 Discharge valve 17a Valve support 18 Discharge chamber room 19 High-pressure gas passage 20 oil separator 21 Oil separation filter 22 Oil sump 23 oil holes 24 Saray groove 30 R processing section 31a-31d R processing part C compression mechanism P1 Discharge chamber Internal pressure of chamber P2 Internal pressure of compression chamber
───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3H029 AA05 AA17 AB03 BB44 CC15 CC54 CC85 3H040 AA09 BB11 CC09 CC14 DD23 DD28 3H058 AA03 BB27 CB02 CB06 EE05 EE13 ─────────────────────────────────────────────────── ─── Continued front page F-term (reference) 3H029 AA05 AA17 AB03 BB44 CC15 CC54 CC85 3H040 AA09 BB11 CC09 CC14 DD23 DD28 3H058 AA03 BB27 CB02 CB06 EE05 EE13
Claims (4)
周略楕円筒状のシリンダと、上記シリンダ内に回転可能
に横架されたロータと、上記ロータに放射状に嵌め込ま
れ、ロータの回転によりシリンダの周面と摺接する複数
のベーンと、上記シリンダ、サイドブロック、ロータに
より画成される圧縮室と、この圧縮室内で圧縮された高
圧ガスが吐出孔を通じて吐出される吐出チャンバ室と、
開閉動作することにより高圧ガスの吐出を行なうととも
に、高圧ガスの逆流を防ぐ吐出弁とを有し、前記吐出弁
と当接する弁座部分には、吐出弁が撓み変形して吐出孔
内に押し込まれる時、吐出弁と面接触状態を維持できる
Ｒ加工部が設けられていることを特徴とする気体圧縮
機。1. A rotor having a substantially elliptic cylindrical shape having an inner circumference interposed between a pair of side blocks, a rotor rotatably mounted in the cylinder, and a rotor radially fitted into the rotor to rotate the rotor. A plurality of vanes slidably contacting the peripheral surface of the cylinder, the compression chamber defined by the cylinder, the side block, and the rotor, and the discharge chamber chamber in which the high-pressure gas compressed in the compression chamber is discharged through the discharge holes,
It has a discharge valve that discharges high-pressure gas by opening and closing and prevents the high-pressure gas from flowing backward, and the discharge valve is bent and deformed at the valve seat portion that abuts against the discharge valve and is pushed into the discharge hole. The gas compressor is characterized in that it is provided with an R processing part capable of maintaining a surface contact state with the discharge valve when the gas compressor is operated.
ーナー部に丸みをもたせるＲ加工により形成されている
ことを特徴とする請求項１に記載の気体圧縮機。2. The gas compressor according to claim 1, wherein the R-processed portion is formed by R-processing which rounds the upper edge corner portion of the chamfered portion of the discharge hole.
あるいは凸状のＲ加工により形成されていることを特徴
とする請求項１に記載の気体圧縮機。3. The R processed portion has a concave shape in the chamfered portion of the discharge hole,
Alternatively, the gas compressor according to claim 1, wherein the gas compressor is formed by convex R processing.
凸状、内側を凹状のＲ加工が連接状に形成されているこ
とを特徴とする請求項１に記載の気体圧縮機。4. The gas compressor according to claim 1, wherein the R-processed portion is formed such that the chamfered portion of the discharge hole is formed such that the R-processed is convex on the outside and concave on the inside.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001311896A JP2003120563A (en) | 2001-10-09 | 2001-10-09 | Gas compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001311896A JP2003120563A (en) | 2001-10-09 | 2001-10-09 | Gas compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003120563A true JP2003120563A (en) | 2003-04-23 |
Family
ID=19130640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001311896A Pending JP2003120563A (en) | 2001-10-09 | 2001-10-09 | Gas compressor |
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| Country | Link |
|---|---|
| JP (1) | JP2003120563A (en) |
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| JP2011089473A (en) * | 2009-10-22 | 2011-05-06 | Toyota Motor Corp | Fuel pump |
| WO2012043017A1 (en) * | 2010-09-27 | 2012-04-05 | 大豊工業株式会社 | Vane pump |
| JP2012141007A (en) * | 2010-12-28 | 2012-07-26 | Bridgestone Corp | Joint pipe |
| JP2012140908A (en) * | 2010-12-29 | 2012-07-26 | Daikin Industries Ltd | Compressor |
| US8821143B2 (en) | 2011-09-29 | 2014-09-02 | Mitsubishi Electric Corporation | Vane rotary compressor |
| WO2015156144A1 (en) * | 2014-04-07 | 2015-10-15 | 株式会社日立産機システム | Compressor |
| KR101878153B1 (en) * | 2016-11-25 | 2018-07-16 | 국방과학연구소 | Valve assembly and piezoelectric pump-hydrulic actuator having the same and method for driving thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US9777719B2 (en) | 2009-10-22 | 2017-10-03 | Toyota Jidosha Kabushiki Kaisha | Fuel pump with discharge control |
| JP2011089473A (en) * | 2009-10-22 | 2011-05-06 | Toyota Motor Corp | Fuel pump |
| CN102713283A (en) * | 2009-10-22 | 2012-10-03 | 丰田自动车株式会社 | Fuel pump |
| WO2012043017A1 (en) * | 2010-09-27 | 2012-04-05 | 大豊工業株式会社 | Vane pump |
| JP2012141007A (en) * | 2010-12-28 | 2012-07-26 | Bridgestone Corp | Joint pipe |
| JP2012140908A (en) * | 2010-12-29 | 2012-07-26 | Daikin Industries Ltd | Compressor |
| US8821143B2 (en) | 2011-09-29 | 2014-09-02 | Mitsubishi Electric Corporation | Vane rotary compressor |
| WO2015156144A1 (en) * | 2014-04-07 | 2015-10-15 | 株式会社日立産機システム | Compressor |
| CN106164488A (en) * | 2014-04-07 | 2016-11-23 | 株式会社日立产机*** | Compressor |
| JPWO2015156144A1 (en) * | 2014-04-07 | 2017-04-13 | 株式会社日立産機システム | Compressor |
| KR101878153B1 (en) * | 2016-11-25 | 2018-07-16 | 국방과학연구소 | Valve assembly and piezoelectric pump-hydrulic actuator having the same and method for driving thereof |
| JP7013138B2 (en) | 2017-03-28 | 2022-01-31 | 東芝キヤリア株式会社 | Compressor and refrigeration cycle equipment |
| US12006934B2 (en) | 2020-10-01 | 2024-06-11 | Mitsubishi Electric Corporation | Scroll compressor and refrigeration cycle apparatus |
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