JPH0615871B2 - Vane compressor - Google Patents
Vane compressorInfo
- Publication number
- JPH0615871B2 JPH0615871B2 JP62239268A JP23926887A JPH0615871B2 JP H0615871 B2 JPH0615871 B2 JP H0615871B2 JP 62239268 A JP62239268 A JP 62239268A JP 23926887 A JP23926887 A JP 23926887A JP H0615871 B2 JPH0615871 B2 JP H0615871B2
- Authority
- JP
- Japan
- Prior art keywords
- rotation direction
- rotor
- control plate
- suction port
- rotor rotation
- 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.)
- Expired - Lifetime
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
- 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
-
- 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/14—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
-
- 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)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は、例えば自動車用空調装置の冷媒圧縮機として
用いられるベーン型圧縮機に関する。Description: TECHNICAL FIELD The present invention relates to a vane type compressor used as a refrigerant compressor of an air conditioner for an automobile, for example.
（従来技術及びその問題点） 従来、被圧縮ガスの吸入量を調節することによって、圧
縮機の能力を可変制御し得るようにした所謂可変容量式
ベーン型圧縮機として特開昭６２−１２９５９３号公報
が公知である。(Prior Art and Problems Thereof) Japanese Patent Laid-Open No. 62-129593 discloses a so-called variable capacity vane compressor in which the capacity of the compressor can be variably controlled by adjusting the suction amount of the gas to be compressed. The publication is publicly known.
斯かる従来のベーン型圧縮機は、第４図に示す如く円形
ロータａが嵌装されるロータ室ｂの内周面を楕円形とし
たカムリングｃと、第６図に示す如く外周縁部対称位置
に吸入口ｄから吸入した被圧縮ガスを低圧室側へリーク
させる切欠部ｅ、ｅを有し且つ低圧室側圧力と高圧室側
圧力との差に応じて正逆回動して前記切欠部ｅの位置を
変化させて圧縮開始時期を変化させることにより吐出容
量を可変制御する回動制御板ｆとを具備したものであ
る。そして、ロータａが第４図中反時計方向に回転する
ことにより、圧縮室ｈの容積を順次拡大する吸入行程で
被圧縮ガスが吸入口ｄから互いに隣り合うベーンｇ、ｇ
間に吸入された後、圧縮室ｈの容積を縮小する圧縮行程
で、前記被圧縮ガスが圧縮されて、吐出口ｊから吐出さ
れるものである。前記回動制御板ｆが吐出容量増方向
（第４図中時計方向）に最大限回動したとき、切欠部ｅ
の両端部ｅ1，ｅ2が吸入口の両端部ｄ1，ｄ2と対応位置
して、圧縮開始点は第４図中イの部分となって、吐出容
量最大（全稼動状態）となる。また、前記回動制御板ｆ
が吐出容量減方向（第４図中反時計方向）に最大限回動
したとき、第５図に示す如く切欠部ｅの両端部ｅ1，ｅ2
が吸入口ｄのロータ回転方向前側端ｄ1よりロータ回転
方向前側に位置して、圧縮開始点は第５図中ロの部分と
なって、吐出容量最小となる。このような吐出容量最小
運転時において、前記切欠部ｅのロータ回転方向後側端
ｅ2は吸入口ｄのロータ回転方向前側端ｄ1より距離Ｌだ
けロータ回転方向前側に偏位しているため、この距離Ｌ
の間において被圧縮ガスがベーンｇにて押されたとき、
側方への逃げ場がないので、余分な圧縮作用が行なわれ
てしまい、該圧縮作用がロータａの回転に対する抵抗と
なっていた。Such a conventional vane type compressor has a cam ring c having an elliptical inner peripheral surface of a rotor chamber b in which a circular rotor a is fitted, as shown in FIG. 4, and an outer peripheral edge symmetric portion as shown in FIG. Has notches e, e for leaking the compressed gas sucked from the suction port d to the low pressure chamber side at the position, and rotates forward and backward depending on the difference between the pressure of the low pressure chamber and the pressure of the high pressure chamber. The rotation control plate f is variably controlled by changing the position of the portion e to change the compression start timing. Then, the rotor a rotates counterclockwise in FIG. 4, so that in the suction stroke in which the volume of the compression chamber h is sequentially increased, the compressed gas is supplied from the suction port d to adjacent vanes g, g.
After being sucked in between, the compressed gas is compressed and discharged from the discharge port j in a compression stroke in which the volume of the compression chamber h is reduced. When the rotation control plate f is rotated to the maximum in the discharge volume increasing direction (clockwise direction in FIG. 4), the cutout portion e is formed.
Both end portions e 1 and e 2 of the suction port are positioned corresponding to both end portions d 1 and d 2 of the suction port, and the compression start point is the portion (a) in FIG. 4, and the discharge capacity is maximum (full operating state). . Also, the rotation control plate f
When the maximum displacement is made in the discharge capacity decreasing direction (counterclockwise direction in FIG. 4), both end portions e 1 and e 2 of the cutout portion e as shown in FIG.
Is located on the front side in the rotor rotation direction from the front end d 1 in the rotor rotation direction of the suction port d, and the compression start point is the portion B in FIG. 5, which minimizes the discharge capacity. During such a minimum discharge capacity operation, the rear end e 2 of the notch e in the rotor rotation direction is displaced from the front end d 1 of the suction port d in the rotor rotation direction by a distance L to the front side in the rotor rotation direction. , This distance L
Between the compressed gas is pushed by the vane g,
Since there is no escape to the side, an extra compression action is performed, and the compression action becomes a resistance against the rotation of the rotor a.
本発明は上記事情に鑑みてなされたもので、吐出容量最
小時における余分な圧縮作用を削除し、ロータの回転に
対する抵抗を除去し得るようにしたベーン型圧縮機を提
供することを目的とする。The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vane compressor capable of eliminating an excessive compression action at the time of minimum discharge capacity and removing resistance to rotation of a rotor. .
（問題点を解決するための手段） 上述の問題点を解決するため本発明のベーン型圧縮機
は、円形ロータが嵌装されるロータ室内周面を楕円形と
したカムリングと、外周縁部に吸入口から吸入された被
圧縮ガスを低圧室側へリークさせるための切欠部を有し
且つ低圧室側圧力と高圧室側圧力との差に応じて正逆回
動して前記切欠部の位置を変化させて圧縮開始時期を変
化させることにより吐出口から吐出される前記被圧縮ガ
スの吐出容量を可変制御する回動制御板とを具備したベ
ーン型圧縮機において、前記回動制御板の切欠部は、そ
の回転方向前側端から略中間部に亘る第１部分と、該略
中間部から回転方向後側端に亘る第２部分とからなり、
前記第２部分と前記回動制御板の回動軸心との間の距離
を、前記第１部分と前記回動制御板の回動軸心との間の
距離より長く設定し、前記回動制御板が吐出容量増方向
へ最大限回動したとき、前記第１部分の両端部は前記吸
入口の両端部と対応位置すると共に、前記第２部分のロ
ータ回転方向前側端部は前記吸入口の前記ロータ回転方
向後側端部と対応位置し且つロータ回転方向後側端部は
前記吐出口と対応位置し、また、前記回動制御板が吐出
容量減方向に最大限回動したとき、前記第１部分の両端
部は前記吸入口のロータ回転方向前側端よりロータ回転
方向前側に位置すると共に、前記第２部分のロータ回転
方向前側端部は前記吸入口のロータ回転方向前側端より
ロータ回転方向前側に位置し且つロータ回転方向後側端
部は前記吸入口のロータ回転方向前側端よりロータ回転
方向後側に位置するように構成したことを特徴とするも
のである。(Means for Solving the Problems) In order to solve the above problems, a vane compressor according to the present invention is provided with a cam ring having an elliptical inner peripheral surface of a rotor in which a circular rotor is fitted, and an outer peripheral edge portion. It has a cutout portion for leaking the compressed gas sucked from the suction port to the low pressure chamber side, and rotates forward and backward depending on the difference between the low pressure chamber side pressure and the high pressure chamber side pressure, and the position of the cutout portion. And a rotation control plate for variably controlling the discharge capacity of the compressed gas discharged from the discharge port by changing the compression start timing. The portion includes a first portion extending from the front end in the rotation direction to the substantially middle portion, and a second portion extending from the substantially middle portion to the rear end in the rotation direction,
The distance between the second portion and the rotation axis of the rotation control plate is set to be longer than the distance between the first portion and the rotation axis of the rotation control plate, and the rotation is performed. When the control plate is rotated to the maximum in the discharge volume increasing direction, both ends of the first portion are positioned corresponding to both ends of the suction port, and a front end of the second portion in the rotor rotation direction is the suction port. When the rotor rotation direction rear end is located at a position corresponding to the rotor rotation direction rear end and the rotor rotation direction rear end is located at a position corresponding to the discharge port, and when the rotation control plate is rotated to the maximum in the discharge volume decreasing direction, Both ends of the first portion are located forward of the rotor rotation direction front side end of the suction port in the rotor rotation direction, and the rotor rotation direction front side end portion of the second part is located in the rotor rotation direction front side end of the suction port. It is located on the front side in the rotation direction and the rear end in the rotation direction of the rotor is It is characterized in that it has constituted from over motor rotation direction front end so as to be positioned in the direction of rotor rotation rear side.
（作用） 吐出容量最小運転時、切欠部の第２部分のロータ回転方
向後側端が、吸入口のロータ回転方向前側端よりロータ
回転方向後側に位置するため、ベーンにて押された被圧
縮ガスは、第２部分から逃げるので余分な圧縮作用は行
なわれない。(Operation) During the minimum discharge capacity operation, the rear end in the rotor rotation direction of the second portion of the notch is located on the rear side in the rotor rotation direction from the front end in the rotor rotation direction of the suction port. The compressed gas escapes from the second part, so that no extra compression action takes place.
（実施例） 以下、本発明の一実施例を第１図乃至第３図に基づき説
明する。(Embodiment) An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.
第１図は吐出容量最大運転時（全稼動時）における、第
２図は吐出容量最小運転時（一部稼動時）におけるベー
ン型圧縮機の要部断面図、第３図は本発明のベーン型圧
縮機に用いる回動制御板の平面図である。第１図及び第
２図中１はカムリングで、そのロータ室２は楕円形とさ
れ、該ロータ室２内に円形ロータ３が回転軸４にて回転
自在に装着されている。前記ロータ３には周方向に等配
して複数枚のベーン５が出没自在に配設されている。前
記カムリング１のロータ室２の長軸方向両側に位置して
該ロータ室２の内周面とロータ３の外周面との間に圧縮
室６，６が画成されている。FIG. 1 is a sectional view of a main part of a vane type compressor at the maximum discharge capacity operation (at the time of full operation), FIG. 2 is a sectional view of the vane compressor at the minimum discharge capacity operation (at the time of partial operation), and FIG. 3 is a vane of the present invention. It is a top view of the rotation control plate used for a die compressor. In FIGS. 1 and 2, reference numeral 1 denotes a cam ring, the rotor chamber 2 of which has an elliptical shape, and a circular rotor 3 is rotatably mounted in the rotor chamber 2 by a rotary shaft 4. A plurality of vanes 5 are arranged on the rotor 3 at equal intervals in the circumferential direction so as to be retractable. Compression chambers 6, 6 are defined between the inner peripheral surface of the rotor chamber 2 and the outer peripheral surface of the rotor 3 at both sides of the cam ring 1 in the longitudinal direction of the rotor chamber 2.
前記カムリング１の短軸方向両側には吐出口７，７が設
けられている。前記カムリング１の両側には、そのロー
タ室２の長軸部と短軸部との間に位置して吸入口８，８
が設けられている。前記カムリング１の軸方向一側面に
は、回動制御板９が正逆回動自在に設けられている。該
回動制御板９は、第３図に示す如く外周縁部両側対称位
置に切欠部１０，１０を有している。これら切欠部１０
は同一構成で回転方向前側端から略中間部に亘る第１部
分１１と、該略中間部から回転方向後側端に亘る第２部
分１２とからなる。前記第２部分１２と前記回動制御板
９の回動軸心との間の距離Ｌ1を、前記第１部部分１１
と前記回動制御板９の回動軸心との間の距離Ｌ2より長
く設定してある。前記回動制御板９が吐出容量増方向へ
最大限回動したとき、前記第１部分１１の両端部１１
ａ，１１ｂは、第１図に示す如く前記吸入口８の両端部
８ａ，８ｂと対応位置すると共に、前記第２部分１２の
ロータ回転方向前側端部１２ａは前記吸入口８のロータ
回転方向後側端部８ｂと対応位置し、且つロータ回転方
向後側端部１２ｂは前記吐出口７と対応位置する。ま
た、前記回動制御板９が吐出容量減方向に最大限回動し
たとき、前記第１部分11の両端部１１ａ，１１ｂは、第
２図に示す如く前記吸入口８のロータ回転方向前側端部
８ａよりロータ回転方向前側に位置すると共に、前記第
２部分１２のロータ回転方向前側端部１２ａは、前記吸
入口８のロータ回転方向前側端部８ａよりロータ回転方
向前側に位置し且つロータ回転方向後側端部１２ａは、
前記吸入口８のロータ回転方向前側端部８ａよりロータ
回転方向後側に位置する。Discharge ports 7, 7 are provided on both sides of the cam ring 1 in the minor axis direction. On both sides of the cam ring 1, the suction ports 8 and 8 are located between the long shaft portion and the short shaft portion of the rotor chamber 2.
Is provided. A rotation control plate 9 is provided on one side surface of the cam ring 1 in the axial direction so as to be rotatable forward and backward. As shown in FIG. 3, the rotation control plate 9 has notches 10 and 10 at symmetrical positions on both sides of the outer peripheral edge portion. These notches 10
Includes a first portion 11 having the same configuration and extending from the front end in the rotation direction to the substantially middle portion, and a second portion 12 extending from the substantially middle portion to the rear end in the rotation direction. The distance L 1 between the second portion 12 and the rotation axis of the rotation control plate 9 is set to the first portion 11
It is set to be longer than the distance L 2 between the rotation axis of the rotation control plate 9 and. When the rotation control plate 9 rotates to the maximum in the discharge volume increasing direction, both end portions 11 of the first portion 11
As shown in FIG. 1, a and 11b correspond to the both ends 8a and 8b of the suction port 8, and the front end 12a of the second portion 12 in the rotor rotation direction is located at the rear of the suction port 8 in the rotor rotation direction. The position corresponding to the side end 8b and the rear end 12b in the rotor rotating direction correspond to the discharge port 7. Further, when the rotation control plate 9 is rotated to the maximum in the discharge volume reducing direction, both end portions 11a and 11b of the first portion 11 are, as shown in FIG. The rotor rotation direction front side of the portion 8a is located, and the rotor rotation direction front end 12a of the second portion 12 is located on the rotor rotation direction front side of the suction port 8 in the rotor rotation direction. The rear end 12a in the direction is
The suction port 8 is located on the rear side in the rotor rotation direction with respect to the front side end 8a in the rotor rotation direction.
次に上記構成になる本発明のベーン型圧縮機の作動を説
明する。低圧室（吸入室）側圧力が所定値以上になると
回動制御板９が低圧室側圧力の作用で吐出容量増方向
（第２図中時計方向）に回動して第１図の状態となり、
圧縮開始点は同図中イの部分となり、吐出容量最大（全
稼動）となる。Next, the operation of the vane type compressor of the present invention having the above structure will be described. When the pressure on the low pressure chamber (suction chamber) side exceeds a predetermined value, the rotation control plate 9 rotates in the discharge capacity increasing direction (clockwise direction in FIG. 2) due to the action of the pressure on the low pressure chamber side, and the state shown in FIG. ,
The compression start point is the portion (a) in the figure, and the discharge capacity is maximum (full operation).
また、低圧室側圧力が所定値以下になると回動制御板９
が高圧室（吐出室）側圧力の作用で吐出容量減方向（第
１図中反時計方向）に回動して第２図の状態となり圧縮
開始点は同図中ロの部分となり、吐出容量最小（一部稼
動）となる。Further, when the pressure in the low pressure chamber becomes less than or equal to a predetermined value, the rotation control plate 9
Is rotated in the discharge capacity decreasing direction (counterclockwise direction in FIG. 1) by the action of the pressure on the high pressure chamber (discharge chamber) side, and the state shown in FIG. Minimum (partially active).
斯かる吐出容量最小運転時においては、切欠部１０の第
２部分12のロータ回転方向後側端部12ｂが吸入口８のロ
ータ回転方向前側端部８ｂよりロータ回転方向後側に位
置しているので、ベーン５にて被圧縮ガスが押されても
該被圧縮ガスは第２部分１２から直ちに逃げるので余分
な圧縮作用は行なわれない。従って、ロータ３の回転に
対する抵抗が減少する。During such a minimum discharge capacity operation, the rotor rotation direction rear end 12b of the second portion 12 of the cutout portion 10 is located rearward of the rotor rotation direction front end 8b of the intake port 8 in the rotor rotation direction. Therefore, even if the compressed gas is pushed by the vane 5, the compressed gas immediately escapes from the second portion 12, so that no extra compression action is performed. Therefore, the resistance of the rotor 3 to rotation is reduced.
（発明の効果） 上述した如く本発明のベーン型圧縮機は、円形ロータが
嵌装されるロータ室内周面を楕円形としたカムリング
と、外周縁部に吸入口から吸入された被圧縮ガスを低圧
室側へリークさせるための切欠部を有し且つ低圧室側圧
力と高圧室側圧力との差に応じて正逆回動して前記切欠
部の位置を変化させて圧縮開始時期を変化させることに
より吐出口から吐出する前記被圧縮ガスの吐出容量を可
変制御する回動制御板とを具備したベーン型圧縮機にお
いて、前記回動制御板の切欠部は、その回転方向前側端
から略中間部に亘る第１部分と、該略中間部から回転方
向後側端に亘る第２部分とからなり、前記第２部分と前
記回動制御板の回動軸心との間の距離を、前記第１部分
と前記回動制御板の回動軸心との間の距離より長く設定
し、前記回動制御板が吐出容量増方向へ最大限回動した
とき、前記第１部分の両端部は前記吸入口の両端部と対
応位置すると共に、前記第２部分のロータ回転方向前側
端部は前記吸入口の前記ロータ回転方向後側端部と対応
位置し且つロータ回転方向後側端部は前記吐出口と対応
位置し、また、前記回動制御板が吐出容量減方向に最大
限回動したとき、前記第１部分の両端部は前記吸入口の
ロータ回転方向前側端よりロータ回転方向前側に位置す
ると共に、前記第２部分のロータ回転方向前側端部は前
記吸入口のロータ回転方向前側端よりロータ回転方向前
側に位置し且つロータ回転方向後側端部は前記吸入口の
ロータ回転方向前側端よりロータ回転方向後側に位置す
るように構成したことを特徴とするものである。(Effects of the Invention) As described above, the vane type compressor of the present invention is provided with a cam ring having an elliptical inner peripheral surface of a rotor into which a circular rotor is fitted, and a compressed gas sucked from an inlet at an outer peripheral edge portion. It has a cutout portion for leaking to the low pressure chamber side and rotates forward and backward according to the difference between the low pressure chamber side pressure and the high pressure chamber side pressure to change the position of the cutout portion and change the compression start timing. In the vane type compressor provided with the rotation control plate for variably controlling the discharge capacity of the compressed gas discharged from the discharge port, the cutout portion of the rotation control plate is substantially intermediate from the front end in the rotation direction. A second portion extending from the substantially middle portion to the rear end in the rotation direction, and a distance between the second portion and the rotation axis of the rotation control plate is It is set longer than the distance between the first portion and the rotation axis of the rotation control plate, When the rotation control plate is rotated to the maximum in the discharge capacity increasing direction, both end portions of the first portion are positioned corresponding to both end portions of the suction port, and a front end portion of the second portion in the rotor rotation direction is located. The suction port is located at a position corresponding to the rear end in the rotor rotation direction, the rear end in the rotor rotation direction is located at a position corresponding to the discharge port, and the rotation control plate is maximally rotated in the discharge volume decreasing direction. At this time, both ends of the first portion are positioned forward of the rotor rotation direction front side end of the suction port in the rotor rotation direction, and the rotor rotation direction front side end portion of the second portion is in the rotor rotation direction front side of the suction port. It is characterized in that it is located on the front side in the rotor rotation direction with respect to the end, and the rear end in the rotor rotation direction is located on the rear side in the rotor rotation direction from the front end in the rotor rotation direction of the suction port.
従って、吐出容量最小運転時、切欠部の第２部分のロー
タ回転方向後側端が、吸入口のロータ回転方向前側端よ
りロータ回転方向後側に位置するため、ベーンにて押さ
れた被圧縮ガスは、第２部分から逃げるので、余分な圧
縮作用は行なわれず、ロータの回転に対する抵抗が減少
するという効果を奏する。Therefore, at the time of minimum discharge capacity operation, the rear end in the rotor rotation direction of the second portion of the notch is located on the rear side in the rotor rotation direction from the front end in the rotor rotation direction of the suction port, so that the compressed object pushed by the vane is compressed. Since the gas escapes from the second portion, an excessive compression action is not performed, and the resistance to rotation of the rotor is reduced.
第１図乃至第３図は本発明の一実施例を示し、第１図は
吐出容量最大運転時におけるベーン型圧縮機の要部断面
図、第２図は吐出容量最小運転時におけるベーン型圧縮
機の要部断面図、第３図は回動制御板の平面図、第４図
は従来のベーン型圧縮機の吐出容量最大運転時の要部断
面図、第５図は同吐出容量最小運転時の要部断面図、第
６図は同回動制御板の平面図である。 １……カムリング、２……ロータ室、３……ロータ、７
……吐出口、８……吸入口、８ａ……吸入口のロータ回
転方向前側端部、８ｂ……吸入口のロータ回転方向後側
端部、９……回動制御板、１０……切欠部、１１……第
１部分、１１ａ……第１部分のロータ回転方向前側端
部、１１ｂ……第１部分のロータ回転方向後側端部、１
２……第２部分、１２ａ……第２部分のロータ回転方向
前側端部、１２ｂ……第２部分のロータ回転方向後側端
部。1 to 3 show an embodiment of the present invention. FIG. 1 is a sectional view of a main part of a vane compressor at the maximum discharge capacity operation, and FIG. 2 is a vane compression at the minimum discharge capacity operation. 3 is a plan view of a rotation control plate, FIG. 4 is a cross-sectional view of a main portion of a conventional vane type compressor at maximum discharge capacity operation, and FIG. 5 is the same discharge capacity minimum operation. FIG. 6 is a plan view of the rotation control plate of FIG. 1 ... Cam ring, 2 ... Rotor chamber, 3 ... Rotor, 7
...... Discharge port, 8 …… Suction port, 8a …… Suction inlet rotor rotation direction front end, 8b …… Suction port rotor rotation direction rear end, 9 …… Rotation control plate, 10 …… Notch Part, 11 ... First part, 11a ... 1st part rotor rotation direction front side end part, 11b ... 1st part rotor rotation direction rear end part, 1
2 ... 2nd part, 12a ... Rotor rotation direction front side end part of 2nd part, 12b ... Rotor rotation direction rear side end part of 2nd part.
フロントページの続き (72)発明者 山口 利夫 埼玉県大里郡江南町大字千代字東原39番地 ヂーゼル機器株式会社江南工場内 (72)発明者 永躰 和男 埼玉県大里郡江南町大字千代字東原39番地 ヂーゼル機器株式会社江南工場内 (56)参考文献 実開 昭60−192297（ＪＰ，Ｕ)Front page continued (72) Inventor Toshio Yamaguchi, 39, Toyo, Konan-cho, Osa-gun, Saitama-ken, Chiyo-ji, Konan factory (72) Inventor, Kazuo Eizo, 39, Toyo-ji, Chiyo-ji, Konan-cho, Oza-gun, Saitama Diesel Equipment Co., Ltd., within the Gangnam factory (56) References: 60-192297 (JP, U)
Claims (1)
楕円形としたカムリングと、外周縁部に吸入口から吸入
された被圧縮ガスを低圧室側へリークさせるための切欠
部を有し且つ低圧室側圧力と高圧室側圧力との差に応じ
て正逆回動して前記切欠部の位置を変化させて圧縮開始
時期を変化させることにより吐出口から吐出される前記
被圧縮ガスの吐出容量を可変制御する回動制御板とを具
備したベーン型圧縮機において、前記回動制御板の切欠
部は、その回転方向前側端から略中間部に亘る第１部分
と、該略中間部から回転方向後側端に亘る第２部分とか
らなり、前記第２部分と前記回動制御板の回動軸心との
間の距離を、前記第１部分と前記回動制御板の回動軸心
との間の距離より長く設定し、前記回動制御板が吐出容
量増方向へ最大限回動したとき、前記第１部分の両端部
は前記吸入口の両端部と対応位置すると共に、前記第２
部分のロータ回転方向前側端部は前記吸入口の前記ロー
タ回転方向後側端部と対応位置し且つロータ回転方向後
側端部は前記吐出口と対応位置し、また、前記回動制御
板が吐出容量減方向に最大限回動したとき、前記第１部
分の両端部は前記吸入口のロータ回転方向前側端よりロ
ータ回転方向前側に位置すると共に、前記第２部分のロ
ータ回転方向前側端部は前記吸入口のロータ回転方向前
側端よりロータ回転方向前側に位置し且つロータ回転方
向後側端部は前記吸入口のロータ回転方向前側端よりロ
ータ回転方向後側に位置するように構成したことを特徴
とするベーン型圧縮機。1. A cam ring having an elliptical inner surface of a rotor chamber in which a circular rotor is fitted, and a cutout portion at an outer peripheral edge portion for leaking compressed gas sucked from a suction port to a low pressure chamber side. In addition, the compressed gas discharged from the discharge port by changing the position of the notch and changing the compression start timing by rotating forward and reverse according to the difference between the pressure in the low pressure chamber and the pressure in the high pressure chamber. In a vane type compressor provided with a rotation control plate for variably controlling the discharge capacity of the rotation control plate, the cutout portion of the rotation control plate has a first portion extending from a front end in the rotation direction to a substantially middle portion, and the substantially middle portion. A second portion extending from the portion to the rear end in the rotation direction, and the distance between the second portion and the rotation axis of the rotation control plate is determined by the rotation of the first portion and the rotation control plate. Set longer than the distance from the axis of motion to allow the rotation control plate to maximize When moving, with both end portions of the first portion corresponding position and both end portions of the suction port, the second
The rotor rotation direction front end portion of the portion corresponds to the rotor rotation direction rear end portion of the suction port, and the rotor rotation direction rear end portion of the portion corresponds to the discharge port. Both ends of the first portion are located forward of the rotor rotation direction front side end of the suction port and the rotor rotation direction front side end portion of the second portion when fully rotated in the discharge volume decreasing direction. Is configured so that it is located forward of the rotor rotation direction front side end of the suction port, and the rotor rotation direction rear side end thereof is positioned rearward of the rotor rotation direction front end of the suction port in the rotor rotation direction. A vane type compressor characterized by.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62239268A JPH0615871B2 (en) | 1987-09-22 | 1987-09-22 | Vane compressor |
| KR1019870015077A KR900004609B1 (en) | 1987-09-22 | 1987-12-28 | Vane compressor |
| US07/196,318 US4815945A (en) | 1987-07-31 | 1988-05-20 | Variable capacity vane compressor |
| DE3824803A DE3824803A1 (en) | 1987-07-31 | 1988-07-21 | WING COMPRESSOR WITH VARIABLE CAPACITY |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62239268A JPH0615871B2 (en) | 1987-09-22 | 1987-09-22 | Vane compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6480794A JPS6480794A (en) | 1989-03-27 |
| JPH0615871B2 true JPH0615871B2 (en) | 1994-03-02 |
Family
ID=17042237
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62239268A Expired - Lifetime JPH0615871B2 (en) | 1987-07-31 | 1987-09-22 | Vane compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH0615871B2 (en) |
| KR (1) | KR900004609B1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101697148B1 (en) * | 2016-03-04 | 2017-01-17 | 황광선 | Hybrid vane fluid machinery of centrifugal suction type |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60192297U (en) * | 1984-05-28 | 1985-12-20 | 株式会社ボッシュオートモーティブ システム | vane compressor |
-
1987
- 1987-09-22 JP JP62239268A patent/JPH0615871B2/en not_active Expired - Lifetime
- 1987-12-28 KR KR1019870015077A patent/KR900004609B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| KR890005390A (en) | 1989-05-13 |
| JPS6480794A (en) | 1989-03-27 |
| KR900004609B1 (en) | 1990-06-30 |
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