JPS58214696A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPS58214696A JPS58214696A JP9712582A JP9712582A JPS58214696A JP S58214696 A JPS58214696 A JP S58214696A JP 9712582 A JP9712582 A JP 9712582A JP 9712582 A JP9712582 A JP 9712582A JP S58214696 A JPS58214696 A JP S58214696A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder part
- housing chamber
- storage chamber
- rolling piston
- compression
- 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
- 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
- F04C28/16—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 lift valves
Abstract
Description
【発明の詳細な説明】
本発明は回転式圧縮機に関し、特に、その圧縮容量を可
変とすることを目的としたものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary compressor, and in particular, its purpose is to make its compression capacity variable.
従来、回転式圧縮機の圧縮容量に+−’T変する構造と
して、シリンダ途中に開口したバイパスポートから、圧
縮途中のガスを圧縮機の吸入側へバイパスする構造がと
1つ、tlてい/6oシかし、この場合、バイパスボー
1・の面径C11、このボー1・閉鎖時のクリアランス
ポリヨー15等の19.1係に、あ丑り犬きくはできな
かった。、シたが)で、バイパスポートでの流路抵]J
tが犬きぐ、十分なバイパス流計が得られず、その結!
A!、月縮’r; lit ノ制餌1率は、60〜70
1、’度にしか低ドできなかった。Conventionally, as a structure for changing the compression capacity of a rotary compressor by +-'T, there is one structure in which the gas being compressed is bypassed to the suction side of the compressor from a bypass port opened in the middle of the cylinder. However, in this case, the face diameter C11 of bypass bow 1, clearance polyyo 15 when closing this bow 1, etc. 19.1 could not be criticized. , the flow path resistance at the bypass port] J
The result was that I couldn't get a sufficient bypass flowmeter because t was a dog.
A! , monthly contraction'r; lit no feeding rate is 60-70
1. I was only able to lower it to 'degree'.
本発明し1前記の31:つな欠点を解決するもので、十
分なバイパス流11を全1(Iて、圧縮容量の制御率を
50%以下ゼ、゛度にすることにより、必要な圧縮容量
の変化に’t=1応J−るイ、のである。以下に本発明
の一実施例を図面に基ついて説明する。1は回転式圧縮
機で、内部に1111行)部拐2と」二軸受部材3およ
び下+lQb受部(A4で形成されるシリンダ部5があ
る。6,7しj各々シリンダ部5に開口した吸入口お」
:び吐出[−1である。8Q−1回転月、縮機構である
ローリングピストン、9r1シリンダ部6を高圧室と低
圧室に仕切る什I男りヘ−ン、10は吐出弁、11は仕
切ベーン用Q、1”ね、12i1:IE縮縮量量制御機
構、上+Ii+I+受部AA3に設げI’)7+ /リ
ング部6に開口した収納室13と、この収納室13に収
納され、シリンダ部5の一部を構成するスライド壁月1
4と、このスライド壁材14の背面圧力を制御する開側
1ポー)15から構成されている。The present invention solves the above-mentioned 31: drawbacks, and by controlling the control rate of the compression capacity to 50% or less, the necessary compression is achieved. t=1 corresponding to the change in capacity.An embodiment of the present invention will be explained below with reference to the drawings. 1 is a rotary compressor, inside of which there are ``There are two bearing members 3 and a lower +lQb receiving part (cylinder part 5 formed of A4.
: and discharge [-1. 8Q-1 rotating piston, rolling piston that is the compression mechanism, 9r1 the main shaft that partitions the cylinder section 6 into a high pressure chamber and a low pressure chamber, 10 is the discharge valve, 11 is the Q for the partition vane, 1", 12i1 : IE contraction amount control mechanism, provided in upper + Ii + I + receiving part AA3 I')7+ / Storage chamber 13 opened to ring part 6, and stored in this storage chamber 13, forming a part of cylinder part 5 slide wall moon 1
4, and an opening side port 15 for controlling the back pressure of this sliding wall material 14.
16は上軸受部材3内部に設けられ、収納室13のシリ
ンダ部6に近い部分と吸入口6を連通ずるバイパス路で
ある。そして吐出ロアから吐出された冷媒ガスは吐出管
17.凝縮器18.減圧器19、蒸発器20およびアキ
ュームレータ21を経てふたたび吸入口6から回転式圧
縮機1に吸入される。制御ポート15への圧力制御機構
としては、吐出管17から分岐した高圧導入管22と、
アキュームレータ21の上流から分岐した低圧導入管2
3とが三方弁24を介して圧力導入管25から制御ポー
ト15へ圧力を負荷する機構とす一部ている。つきに第
2図において、26は屯動磯(図示せず)で駆動される
クランク軸である。A bypass passage 16 is provided inside the upper bearing member 3 and communicates the suction port 6 with a portion of the storage chamber 13 near the cylinder portion 6 . The refrigerant gas discharged from the discharge lower is discharged from the discharge pipe 17. Condenser 18. After passing through the pressure reducer 19, evaporator 20, and accumulator 21, it is sucked into the rotary compressor 1 again from the suction port 6. The pressure control mechanism for the control port 15 includes a high pressure introduction pipe 22 branched from the discharge pipe 17;
Low pressure introduction pipe 2 branched from the upstream of the accumulator 21
3 serves as a mechanism for applying pressure from the pressure introduction pipe 25 to the control port 15 via the three-way valve 24. In FIG. 2, reference numeral 26 denotes a crankshaft driven by a tonnage (not shown).
以上の構成につき作用を説明する。−まず、大能力で冷
房を行なう場合、三方弁24によって高圧導入管22と
圧力導入管25が連通されている。The operation of the above configuration will be explained. - First, when performing air conditioning at high capacity, the high pressure introduction pipe 22 and the pressure introduction pipe 25 are communicated with each other by the three-way valve 24.
この状態で、クシ/り輔260回転に」:リローリング
ピストン8が矢印B方向に回転していると、市111i
1;lニー1−151’ri<l高Ifカスカ”、’f
i カtL、スフイ)”壁4:A14i1第1図の。1
]うにシリンダ部6の方向に押されて、シリンダ部6の
一部を形成する。すなわち、スライド壁(」14のトー
面の一部をローリングピストン8の1端面が摺±幼して
いることになる。In this state, when the re-rolling piston 8 is rotating in the direction of arrow B, the comb 111i rotates 260 times.
1;l knee 1-151'ri<lhigh If Kasuka'','f
i KatL, Sufi) "Wall 4: A14i1 Figure 1. 1
] is pushed in the direction of the cylinder part 6 to form a part of the cylinder part 6. That is, one end surface of the rolling piston 8 is sliding on a part of the toe surface of the slide wall (14).
寸だ、スライド゛壁4A14Q:J収納室13の内面に
精密に接している/(め冷〃((の漏” it ス11
+7視できる程度の少111゛である。この状態でif
l、吸入口6からシリンダ部6へ吸入された冷媒ガスの
ほぼ全部が吐出ロア」:す111出さ;/’L、吐出管
17を経て凝縮器18で液化さ7j減圧器19で試用さ
t′1蒸発器2oで気化ざ7する3、このとき蒸発X+
’F 20と熱交換された冷風に」ニー)て大能力の冷
房ができる。The slide wall 4A14Q: It is in precise contact with the inner surface of the J storage chamber 13.
It is 111゛, so small that it can be seen as +7. In this state if
l, Almost all of the refrigerant gas sucked into the cylinder part 6 from the suction port 6 is liquefied in the condenser 18 via the discharge pipe 17, and is used on a trial basis in the pressure reducer 19. '1 Vaporization occurs in the evaporator 2o 3, at this time evaporation X+
A high-capacity air conditioner can be achieved by using cold air that exchanges heat with F20.
つき゛に、冷房f′↓6パ[がジ4稈度に減少した場合
は、三方弁24を切換えることによりスライド壁材14
の背面の高圧ガスを曲用11111へ逃がすことにより
、スライド壁4A14. it、シリンダ部6の冷媒圧
力により制忙11ボー!・16f1川にスライドする。If the cooling f'↓6% decreases to 4 degrees, the slide wall material 14 can be removed by switching the three-way valve 24.
By releasing the high pressure gas on the back side of the slide wall 4A14. It is controlled by the refrigerant pressure in the cylinder part 6 at 11 baud!・Slide into the 16f1 river.
これに」二りシリンダ部5が収納室13を介してバイパ
ス路16と連通ずることになる。この場合、ローリング
ピストン8が吸入口6を通過後から収納室13にかかる
点まではシリンダ部5内の冷媒ガスはほとんど圧縮され
ずにバイパス路16から吸入側へ逃がされる。丑だ、そ
の点から収納室13から離れる点までの時間はシリンダ
部5の高圧室と低圧室とが収納室13を介して連通され
るため、o−リングピストン8が収納室13から離れて
本来の圧縮を開始する場合の冷媒ガス圧力はほぼ低圧に
近くなる。したがって吐出ロアから吐出される冷媒量は
大巾に減少することができ、また、その分消費電力も低
下する。したがってこの場合は、蒸発器20を通過する
冷媒量が捗程度に減少しているため冷房負荷に合った冷
房能力が得れる。In addition, the two cylinder portions 5 communicate with the bypass passage 16 via the storage chamber 13. In this case, after the rolling piston 8 passes through the suction port 6 until it reaches the storage chamber 13, the refrigerant gas in the cylinder portion 5 is hardly compressed and is released from the bypass path 16 to the suction side. Unfortunately, during the time from that point to the point where it separates from the storage chamber 13, the high pressure chamber and low pressure chamber of the cylinder section 5 are communicated via the storage chamber 13, so the o-ring piston 8 separates from the storage chamber 13. The refrigerant gas pressure when starting the original compression becomes almost low pressure. Therefore, the amount of refrigerant discharged from the discharge lower can be significantly reduced, and power consumption is also reduced accordingly. Therefore, in this case, since the amount of refrigerant passing through the evaporator 20 is reduced to a certain extent, a cooling capacity matching the cooling load can be obtained.
なお、スライド壁材14のクランク角位置は、圧縮容量
の必要制御率によって設計上変化するが、本実施例の機
構では、幾何学的な押のけ容量から求まる制御率にほぼ
近い制御率を得ることができる。また、スライド壁材1
4の厚さはできる限り6ペ゛
犬きくした方が、収納室13の内壁に密着した場合のす
き間からの冷〃(1漏J1が防止できるとともに、容f
ii: 1lill 1ilil +115にシリンダ
r”11≦6に開1]する収納室13の容積を・大きく
することができ、不必要な圧縮を減少できる。Note that the crank angle position of the sliding wall material 14 changes in design depending on the required control rate of compression capacity, but in the mechanism of this embodiment, the control rate is almost close to the control rate determined from the geometric displacement capacity. Obtainable. In addition, sliding wall material 1
It is better to make the thickness of the housing 13 as thick as possible by 6 pages, as this will prevent the cooling (1 leakage J1) from flowing through the gap when it is in close contact with the inner wall of the storage chamber 13, and will also reduce the
ii: 1lill 1ilil +115, the volume of the storage chamber 13 with cylinder r"11≦6 can be increased, and unnecessary compression can be reduced.
なお、本実施例でCIバイパス路16を設けたが、本発
明に」:れr丁これC11沢すしも必要ではない。この
場合、圧縮容@!fI制御時仁10−リングピストン8
が吸入口6を通過1麦から収納室13にかかる点までは
シリンダ部6内の冷媒ガスは若干圧縮されるが、収納室
13のシリンダ部5内に開口した容積を犬きくすること
に」゛す、この場合の圧力上昇を少なくすることができ
る。Although the CI bypass path 16 is provided in this embodiment, it is not necessary for the present invention. In this case, compressed volume @! fI control Tokihito 10-ring piston 8
Although the refrigerant gas in the cylinder part 6 is slightly compressed from the point where it passes through the suction port 6 to the point where it is applied to the storage chamber 13, the volume opened in the cylinder part 5 of the storage chamber 13 is increased. Therefore, the pressure increase in this case can be reduced.
丑だ、本実施例でし1、回転圧縮機構としてはローリン
グピストン8を用いたが、本発明によれば、スライドベ
ーン方式のものでも同様の効果が得られる。In this embodiment, a rolling piston 8 is used as the rotary compression mechanism, but according to the present invention, a slide vane type mechanism can also achieve the same effect.
以1−のように、本発明によれば、円筒部材と、このシ
リンダ部内に設けられた回転圧縮機構と、上記/リンダ
部に開口する吸入口と、吐出口とを設けるとともに、−
に記シリンダ部の内壁の一部を構成し、かつ、可動自在
なスライド壁材と、このスライド壁材を収納する収納室
と、この収納室に連通し、−に記スライド壁材の背面圧
力を制御する開開jポートよりなる圧縮容量制御機構を
設けたものであるから、圧縮機を犬答量で運転する場合
はスライド壁材が収納室を閉鎖するとともにシリンダ部
に余分の空間が形成されないために性能が低下すること
はない。As described in 1- above, according to the present invention, a cylindrical member, a rotary compression mechanism provided in the cylinder part, an inlet opening to the cylinder part, and a discharge port are provided, and -
A sliding wall material which constitutes a part of the inner wall of the cylinder part and is movable; a storage chamber that stores the sliding wall material; and a storage chamber communicating with the storage chamber; Since it is equipped with a compression capacity control mechanism consisting of an opening/opening J port that controls Performance will not be degraded because it is not done.
1だ、圧縮容量を減少させる場合は、制御ボートへの圧
力を制御することにより簡単に行なうことができる。さ
らに、収納室のシリンダ部に開口した空間容積が犬きく
とれるため回転圧縮機構がシリンダ部内で圧縮容量制御
機構を通過するまではほとんど圧縮を行わないため大き
な圧縮谷量澗御率を得ることができるものである。1. Reducing the compression capacity can be easily done by controlling the pressure on the control boat. Furthermore, since the space volume opened in the cylinder section of the storage chamber is kept small, almost no compression is performed until the rotary compression mechanism passes through the compression capacity control mechanism within the cylinder section, making it possible to obtain a large compression valley rate. It is possible.
載j−た冷凍−リーイクル図、第2図は第1図の回転式
圧縮機の部分断面図である。FIG. 2 is a partial sectional view of the rotary compressor shown in FIG. 1.
1・・・・・回転式t+h縮機、2・・・・・円筒部拐
、3・・自・・」二軸受部材、4・・・・[111II
受部4=415・・川・シリンダ部、6・・・・・・吸
入1−1.7・・・・111出口、8・川・・ローリン
グピストン(回転J1縮機h”7 ) 、12・・・・
圧縮容量制御機構、13・・・・・11Y納室、14ス
ライド壁材、16・・−・1lilJ枦71;lニーl
・。1...Rotary type t+h compressor, 2...Cylindrical part removal, 3...Auto...' double bearing member, 4...[111II
Receiving part 4 = 415... River/Cylinder part, 6... Suction 1-1.7... 111 outlet, 8/ River... Rolling piston (rotation J1 compressor h"7), 12・・・・・・
Compression capacity control mechanism, 13...11Y storage room, 14 sliding wall material, 16...1lilJ枦71;l kneel
・.
Claims (1)
けられた上下軸受部拐とで形成されるシリンダ部と、こ
のシリンダ部内に設けられた回転圧縮機構と、上記シリ
ンダ部に開口する吸入口と、吐出口とを設けるとともに
、上記シリンダ部の内壁の一部を構成し、かつ、可動自
在なスライド壁11と、このスライド壁材を収納する収
納室と、この収納室に連通し一ト記スライド壁材の背面
圧力を制御即する制呻ポートを設けた圧稲答滑訓御・機
構を設けた回転式圧縮機。A cylinder portion formed by a cylindrical member, upper and lower bearing portions provided to close upper and lower end surfaces of the cylindrical member, a rotary compression mechanism provided within the cylinder portion, and an inlet opening to the cylinder portion. A slide wall 11 that forms part of the inner wall of the cylinder section and is movable, a storage chamber that stores the slide wall material, and a port that communicates with the storage chamber. A rotary compressor equipped with a pressure control mechanism equipped with a suppressor port to control the back pressure of the sliding wall material.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9712582A JPS58214696A (en) | 1982-06-07 | 1982-06-07 | Rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP9712582A JPS58214696A (en) | 1982-06-07 | 1982-06-07 | Rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS58214696A true JPS58214696A (en) | 1983-12-13 |
Family
ID=14183837
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9712582A Pending JPS58214696A (en) | 1982-06-07 | 1982-06-07 | Rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58214696A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100111737A1 (en) * | 2007-01-17 | 2010-05-06 | Daikin Industries, Ltd. | Compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5032450A (en) * | 1973-06-07 | 1975-03-29 | ||
JPS54155353A (en) * | 1978-05-29 | 1979-12-07 | Hellberg Protection Ab | Sliding block |
JPS582491A (en) * | 1981-06-25 | 1983-01-08 | Nippon Denso Co Ltd | Rotary compressor |
-
1982
- 1982-06-07 JP JP9712582A patent/JPS58214696A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5032450A (en) * | 1973-06-07 | 1975-03-29 | ||
JPS54155353A (en) * | 1978-05-29 | 1979-12-07 | Hellberg Protection Ab | Sliding block |
JPS582491A (en) * | 1981-06-25 | 1983-01-08 | Nippon Denso Co Ltd | Rotary compressor |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100111737A1 (en) * | 2007-01-17 | 2010-05-06 | Daikin Industries, Ltd. | Compressor |
US8356986B2 (en) * | 2007-01-17 | 2013-01-22 | Daikin Industries, Ltd. | Compressor |
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