JPS60243388A - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JPS60243388A JPS60243388A JP59098704A JP9870484A JPS60243388A JP S60243388 A JPS60243388 A JP S60243388A JP 59098704 A JP59098704 A JP 59098704A JP 9870484 A JP9870484 A JP 9870484A JP S60243388 A JPS60243388 A JP S60243388A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- chamber
- valve body
- back pressure
- scroll
- 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
- F04C29/02—Lubrication; Lubricant separation
-
- 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
- F04C28/28—Safety arrangements; Monitoring
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明はスクロール圧縮機に係り、特に旋回軸受、主軸
受を含む摺動部への給油を安定して行える構造に関する
。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a scroll compressor, and particularly to a structure that allows stable oil supply to sliding parts including a swing bearing and a main bearing.
従来のスクロール圧縮機を第１図により説明する。密閉
容器１内には圧縮機部２が上部に、電動機部３が下部に
連設されて収納されている。圧縮機部は、平板部６ａに
うす巻き状のラップ６ｂを直立させて、旋回運動する旋
回スクロール６と、平板部７ａにうす巻き状のラップ部
７ｂを直立させ、フレーム５に固定された固定スクロー
ル７を互にかみ合わせて形成されている。電動機部３の
回転軸と一体のクランク軸４の下端は密閉容器１の底部
に形成された油溜め９に浸漬され、このクランク軸４に
は下端が軸心に開口し、上端が回転軸心に対し偏心した
位置に開口する油孔４のが穿設されている。旋回スクロ
ール６には、吸入圧力と吐出圧力の中間程度の圧力にな
る位置に連通孔１０を設け、旋回スクロール６とフレー
ム５との間に中間の圧力になる背圧室８を設けている♂
゛クランク軸４上端は、旋回スクロール６の下方に穿設
したボス部６Ｃに嵌合されている。クランク軸４の回転
によシボス部６Ｃがフレーム５の背圧室８内で旋回する
ことにより旋回スクロール６は旋回運動を行い、旋回ラ
ップ６ｂと固定ラップ７ｂの互の接触点の移動により、
吸入管１１より吸入されたガスはうす巻き状の外側室か
ら内側に向けて圧縮され固定スクロール７の中央に設け
た吐出ロアＣより密閉容器ｉ内に吐出される。密閉容器
１内に吐出されたガスは固定スクロール７の外周部に設
けた通路７ｄ、フレーム外周通路５ａを通り、一部は電
動機部３の外周通路３ａ、３ｂを経て、また一部はフレ
ーム５と゛電動４幾部３０間を経て吐出管１２を介して
機外に送出される。旋回スクロール６１ｄ定スクロール
７の両うツ７’６ｂ、７ｂおよび平板部５ａ、７ａによ
り形成される密閉室の容積は外側から中央に移動するに
従い減少し圧力が上昇する。しかして、旋回スクロール
６とフレーム５に形成される背圧室８は前述のように、
連通孔１０により吸入圧力と吐出圧力の中間の圧力に保
持されている。そこで、この中間圧力と圧縮機部内圧力
との差圧により、旋回スクロール６を固定スクロール７
に押し付け、ラップ６ｂ、７ｂの先端と平板部５ａ、７
ａとの隙間のシール部の密着を保持する。更に密閉容器
１内部は吐出モカになっており、背圧室８より高いので
、その圧力差により冷凍機油はクランク軸内の油孔４ａ
に押し上げられ、旋回軸受、主軸受等の摺動部に給油さ
れる。A conventional scroll compressor will be explained with reference to FIG. Inside the airtight container 1, a compressor section 2 is housed in an upper part and an electric motor part 3 is arranged in a lower part. The compressor part includes an orbiting scroll 6 which has a thinly wound wrap 6b standing upright on a flat plate part 6a and rotates, and a stationary scroll 6 which has a thinly wound wrap 7b standing upright on a flat plate part 7a and which is fixed to the frame 5. It is formed by interlocking scrolls 7. The lower end of the crankshaft 4, which is integral with the rotating shaft of the electric motor section 3, is immersed in an oil reservoir 9 formed at the bottom of the closed container 1. An oil hole 4 that opens at an eccentric position with respect to the shaft is drilled. The orbiting scroll 6 is provided with a communication hole 10 at a position where the pressure is approximately intermediate between the suction pressure and the discharge pressure, and a back pressure chamber 8 is provided between the orbiting scroll 6 and the frame 5 where the pressure is intermediate.
``The upper end of the crankshaft 4 is fitted into a boss portion 6C drilled below the orbiting scroll 6. As the grain portion 6C rotates within the back pressure chamber 8 of the frame 5 due to the rotation of the crankshaft 4, the orbiting scroll 6 performs an orbiting motion, and the mutual contact points of the orbiting wrap 6b and the fixed wrap 7b move, resulting in
The gas sucked in through the suction pipe 11 is compressed inward from the thinly wound outer chamber and is discharged from a discharge lower C provided at the center of the fixed scroll 7 into the closed container i. The gas discharged into the airtight container 1 passes through a passage 7d provided on the outer periphery of the fixed scroll 7, a frame outer passage 5a, a part passes through the outer periphery passages 3a and 3b of the electric motor part 3, and a part passes through the frame 5. After passing through the electric motor 4 and several parts 30, it is sent out to the outside of the machine via the discharge pipe 12. The volume of the sealed chamber formed by the two cups 7'6b and 7b of the orbiting scroll 61d and the fixed scroll 7 and the flat plate portions 5a and 7a decreases and the pressure increases as it moves from the outside to the center. Therefore, as described above, the back pressure chamber 8 formed in the orbiting scroll 6 and the frame 5 is
The communication hole 10 maintains the pressure between the suction pressure and the discharge pressure. Therefore, due to the pressure difference between this intermediate pressure and the compressor internal pressure, the orbiting scroll 6 is moved to the fixed scroll 7.
, press the ends of the wraps 6b, 7b and the flat plate parts 5a, 7.
Maintain close contact of the seal part in the gap with a. Furthermore, the inside of the airtight container 1 has a high discharge pressure and is higher than the back pressure chamber 8, so the pressure difference causes the refrigerating machine oil to flow through the oil hole 4a in the crankshaft.
The oil is pushed up by the oil, and the sliding parts such as the swing bearing and main bearing are supplied with oil.
前述したスクロール圧縮機において、背圧室８の圧力は
、連通孔１０により背圧室８と連通ずる密閉室の圧力に
より主に支配され、概略この密閉室の平均圧力に保たれ
る。また、この密閉室の圧力はスクロール圧縮機の特性
上吸入圧力に支配され、その値は連通孔の位置により決
定さ（しる。即ち、中間圧力は吐出圧力にほぼ無関係に
吸入圧力と連通孔位置により決定される。In the scroll compressor described above, the pressure in the back pressure chamber 8 is mainly controlled by the pressure in the sealed chamber communicating with the back pressure chamber 8 through the communication hole 10, and is maintained approximately at the average pressure of this sealed chamber. Also, due to the characteristics of the scroll compressor, the pressure in this sealed chamber is controlled by the suction pressure, and its value is determined by the position of the communication hole. Determined by location.
しかるに、従来のスクロール圧縮機では、軸受の給油用
を吐出圧力と中間圧力との差圧によって得ているので、
この差圧が小さいか、または差圧がない条件では軸受に
給油を行えない、つまり前記の条件では運転ができなく
なるという問題がある。また前記差圧を確保するため、
中間圧力が低くなる位置に連通孔１０を設けた場合には
、吸入出力と吐出圧力との差圧が大きい条件において中
間圧力による両スクロールの押し付は力不足を生じ、ラ
ップ先端と平板部のシールができなくなるという問題が
生ずる。However, in conventional scroll compressors, bearing lubrication is obtained from the differential pressure between discharge pressure and intermediate pressure.
If this differential pressure is small or there is no differential pressure, the bearing cannot be lubricated, that is, there is a problem that the bearing cannot be operated under the above conditions. In addition, in order to ensure the above-mentioned differential pressure,
If the communication hole 10 is provided at a position where the intermediate pressure is low, under conditions where the differential pressure between the suction output and the discharge pressure is large, the intermediate pressure will not be able to press both scrolls, and the pressure between the tip of the wrap and the flat plate will be insufficient. A problem arises in that the seal cannot be formed.
本発明の目的は、中間圧力を制御することにより給油に
必要な差圧を確保して、運転可能領域の拡大を図れるス
クロール圧縮機を提供することにある。An object of the present invention is to provide a scroll compressor that can secure the differential pressure necessary for oil supply by controlling the intermediate pressure and expand the operable range.
本発明は、背圧室と圧縮機構の低圧側室とを連通遮断す
る弁装置を備え、吐出圧力が低下したとき、前記弁装置
により背圧室と低圧側室とを連通し、背圧室の圧力を下
げて吐出圧力と中間圧力とに給油に必要な差圧が確保さ
れるようにしたことを特徴とする。The present invention includes a valve device that communicates and cuts off communication between a back pressure chamber and a low pressure side chamber of a compression mechanism, and when the discharge pressure decreases, the back pressure chamber and the low pressure side chamber are communicated with each other by the valve device, and the pressure in the back pressure chamber is The present invention is characterized in that the differential pressure required for oil supply is ensured between the discharge pressure and the intermediate pressure by lowering the pressure.
以下、本発明の一実施例を第２図および第３図により説
明する。第２図は本発明によるスクロール圧縮機の要部
断面図を示しており、第１図と同一符号のものは同じも
のもしくは相当するものを表わしている。このスクロー
ル圧縮機は、圧縮機部２の吸入室１１ａと背圧室８とを
連通遮断できる弁装置１３を備えている。この弁装置１
３け、固定スクロール７内に形成されたシリンダ１４と
、そのシリンダ１４内に納められる弁体１５と、設定用
の圧縮はね１６と、弁体液は止め用の止め輪１７とを具
えている。前記シリンダ１４の一方は密閉容器１内に開
口し、かつ他方は連通孔１８を弁して背圧室８に連通さ
れると共に、連通孔１９を介して吸入室１１ａに連通し
ている。前記弁体１５は、一端に密閉容器１内圧力の受
圧面１５ａを有し、かつその受圧面１５ａの背面側に背
圧室８内圧力の受圧面１５ｂを有していると共に、他端
に前記連通孔１９を開閉できるニードル部１５Ｃを有し
ている。前記圧縮ばね１６は、弁体１５の受圧面１５ｂ
とシリンダ１４の側壁との間に介在されている。前記止
め輸１７は、シリンダ１４の内壁に設けたリング溝に嵌
め込まれて、弁体１５の抜は出しを阻止するようになっ
ている。An embodiment of the present invention will be described below with reference to FIGS. 2 and 3. FIG. 2 shows a sectional view of essential parts of the scroll compressor according to the present invention, and the same reference numerals as in FIG. 1 represent the same or equivalent parts. This scroll compressor is equipped with a valve device 13 that can communicate and cut off communication between the suction chamber 11a of the compressor section 2 and the back pressure chamber 8. This valve device 1
3. It includes a cylinder 14 formed within the fixed scroll 7, a valve body 15 housed within the cylinder 14, a compression spring 16 for setting, and a retaining ring 17 for stopping the valve fluid. . One side of the cylinder 14 opens into the closed container 1, and the other side communicates with the back pressure chamber 8 through a communication hole 18, and also communicates with the suction chamber 11a through a communication hole 19. The valve body 15 has a pressure receiving surface 15a for receiving the internal pressure of the closed container 1 at one end, a pressure receiving surface 15b for receiving the internal pressure of the back pressure chamber 8 on the back side of the pressure receiving surface 15a, and a pressure receiving surface 15b for receiving the internal pressure of the back pressure chamber 8 at the other end. It has a needle portion 15C that can open and close the communication hole 19. The compression spring 16 is connected to the pressure receiving surface 15b of the valve body 15.
and the side wall of the cylinder 14. The stopper 17 is fitted into a ring groove provided on the inner wall of the cylinder 14 to prevent the valve body 15 from being pulled out.
そして、前記の弁装置１３Ｖｉ、弁体１５の両受圧面に
作用する圧力の差圧が圧縮ばね１６のばね力よりも大き
いときには弁体１５が、そのニードル部１５Ｃで連通孔
１９を塞ぐ位置、即ち背圧室８と吸入室１１ａとを速断
する位置に変位し、また差圧が圧縮ばね１６のばね力よ
りも小さくなると、そのばね力により弁体１５が、その
ニードル部で連通孔１９を開く位置、即ち背圧室８と吸
入室１１ａとを連通させる位置に位置するようになって
いる。and a position where the valve body 15 closes the communication hole 19 with its needle portion 15C when the differential pressure between the pressures acting on both pressure receiving surfaces of the valve device 13Vi and the valve body 15 is larger than the spring force of the compression spring 16; That is, when the back pressure chamber 8 and the suction chamber 11a are moved to a position where they are quickly disconnected, and the differential pressure becomes smaller than the spring force of the compression spring 16, the valve body 15 closes the communication hole 19 with its needle portion due to the spring force. It is located at an open position, that is, at a position where the back pressure chamber 8 and the suction chamber 11a are communicated with each other.
次に本発明の作用について説明する。吸入圧力（ｉ７Ｐ
ｓ、中間圧力をｐｂ、吐出圧力をＰｄ、圧縮ばねのば
ね力をＫとし、シリンダ１４の断面積をＳＡ、連通孔１
０の断面積をＳＢとする。起動前は通常Ｐ日＝Ｐ’ｔ）
＝Ｐｄに保たれているので、ばね力Ｋにより弁装置１３
の弁体１５は第３図に示すように止め輪１７に押し付け
られている、つまり背圧室８と吸入室１１ａとを連通ず
る位置に変位している。この状態で起動した場合、Ｐｄ
Ｘ５Ａ＞ＰｂＸ５Ａ＋に、、、、、、（１）（１）式を
満足する値に吐出圧力が上昇すると、弁体１５は第２図
の位置に変位し、ニードル部１５Ｃで連通孔１９を閉じ
る。この状態においては密閉容器１内、吸入室１１”ａ
１背圧室８はそれぞれ仕切られており、実質的に従来例
と同じ条件で運転される。Next, the operation of the present invention will be explained. Suction pressure (i7P
s, the intermediate pressure is pb, the discharge pressure is Pd, the spring force of the compression spring is K, the cross-sectional area of the cylinder 14 is SA, and the communication hole 1
Let the cross-sectional area of 0 be SB. Before startup, it is usually P days = P't)
= Pd, the spring force K causes the valve device 13 to
As shown in FIG. 3, the valve body 15 is pressed against the retaining ring 17, that is, it is displaced to a position where the back pressure chamber 8 and the suction chamber 11a are communicated with each other. If you start up in this state, Pd
When the discharge pressure increases to a value that satisfies the equation (1) (1) such that X5A>PbX5A+, the valve body 15 is displaced to the position shown in FIG. 2, and the needle portion 15C closes the communication hole 19. . In this state, inside the closed container 1, the suction chamber 11''a
Each of the back pressure chambers 8 is partitioned off and operated under substantially the same conditions as in the conventional example.
また、（１）式を満足する値まで吐出圧力が上昇しない
場合、即ち弁体１５の両受圧面に作用する圧力の差圧が
ばね力によりも小さいときには、弁体１５は第３図の位
置に保たれて、背圧室８を連通孔１８．１９を介して赦
入室１１ａに連絡し、中間圧力ＰＩ）は低い値となる。Furthermore, when the discharge pressure does not rise to a value that satisfies equation (1), that is, when the differential pressure between the pressures acting on both pressure-receiving surfaces of the valve body 15 is smaller than the spring force, the valve body 15 is moved to the position shown in FIG. is maintained, the back pressure chamber 8 is connected to the admission chamber 11a through the communication hole 18, 19, and the intermediate pressure PI) becomes a low value.
そして、中間圧力Ｐｂが通常の中間圧力よりも低い圧力
に保たれることは、吐出圧力との差圧が大きくなって給
辿王力（吐出圧力と中間圧力との差圧）を確保すること
になり、運転範囲の拡大が可能となる。また中間圧力が
低い圧力に保たれることは、旋回スクロール６の押し付
は力を小さくすることになるが、この場合は吐出圧力も
低い状態にあるため押し付は力は小さくて良いわけであ
り好都合でもある次に、運転中に例えば負荷が低下し、
吐出圧力が低下してきた場合について述べる。弁体１５
のニードル部１５０が連通孔１９を閉じている状態にお
いで、
ＰｄＸ５Ａ＜ＰＩ）Ｘ（ＳＡ−８Ｂ）−１−ＰｇＸＳＢ
−１−Ｋ・・・・・・（２）
（２）式を成立させる吐出圧力まで低下した場合、弁体
１５は連通孔１９を開放する方向に変位し、中間圧力は
通常の圧力よりも低い圧力に保持される。従って、前述
と同様に旋回スクロール６の押し付は力を確保できると
共に、給油圧力を確保することができる。The fact that the intermediate pressure Pb is maintained at a lower pressure than the normal intermediate pressure means that the pressure difference between the discharge pressure and the discharge pressure increases to ensure the supply force (differential pressure between the discharge pressure and the intermediate pressure). This makes it possible to expand the operating range. Also, keeping the intermediate pressure at a low pressure means that the pressing force of the orbiting scroll 6 is reduced, but in this case, the discharge pressure is also low, so the pressing force only needs to be small. Next, when the load decreases during operation,
A case where the discharge pressure has decreased will be described. Valve body 15
In the state in which the needle part 150 closes the communication hole 19, PdX5A<PI)X(SA-8B)-1-PgXSB
-1-K... (2) When the discharge pressure decreases to a level that satisfies equation (2), the valve body 15 is displaced in the direction of opening the communication hole 19, and the intermediate pressure is lower than the normal pressure. held at low pressure. Therefore, in the same manner as described above, the pressing force of the orbiting scroll 6 can be secured, and the oil supply pressure can also be secured.
第４図は本発明の他の実施例を示し、第２図の実施例と
異なるのは、連通孔１９の開口位置を中間圧力よりも低
圧となる圧縮機部２の密閉室２０内にした点にある。FIG. 4 shows another embodiment of the present invention, which differs from the embodiment shown in FIG. 2 in that the opening position of the communication hole 19 is located in the closed chamber 20 of the compressor section 2 where the pressure is lower than the intermediate pressure. At the point.
本実施例においても基本的な動作は第２図の場合と同じ
であり、（１）式および（２）式においてもＰ８をＰθ
′（密閉室２０の圧力）と置き代えれば、第２図と同じ
作用、効果を達成できる。In this embodiment, the basic operation is the same as in the case of FIG. 2, and in equations (1) and (2), P8 is
' (pressure in the sealed chamber 20), the same action and effect as in FIG. 2 can be achieved.
以上説明したように、本発明によれば、吐出圧力の圧力
変化に応じて中間圧力を制御して、両王力に給油に必要
な差圧を確保できるので、運転可能領域の拡大を図れる
。As explained above, according to the present invention, the intermediate pressure can be controlled in accordance with pressure changes in the discharge pressure to ensure the differential pressure necessary for oil supply between both forces, thereby expanding the operable range.
第１図は従来のスクロール出縮機の縦断面図、第２図お
よび第３図は本発明の一実施例を示し、第２図は本発明
によるスクロール田縮機の要部断面図、第３図は弁装置
の作動状態を示す断面図、第４図は本発明の他の実施例
を示す袋部断面図である。
１・・・密閉容器 ６・・・旋回スクロール ７・・・
固定スクロール ８・・・背圧室 １１ａ・・・吸入室
１３・・・弁装置 １４・・・シリンダ １５・・・
弁体 １５＆、１５ｂ・・・受王面 １６・・・設定用
の圧縮ばね １８．１９・・・連通孔 ２０・・・密閉
室。
代理人 弁理士 高 橋 明 夫
第１目
幕麺
′４４国
／FIG. 1 is a vertical cross-sectional view of a conventional scroll compressor, FIGS. 2 and 3 show an embodiment of the present invention, and FIG. 2 is a cross-sectional view of essential parts of a scroll compressor according to the present invention. FIG. 3 is a sectional view showing the operating state of the valve device, and FIG. 4 is a sectional view of the bag portion showing another embodiment of the present invention. 1... Airtight container 6... Orbiting scroll 7...
Fixed scroll 8... Back pressure chamber 11a... Suction chamber 13... Valve device 14... Cylinder 15...
Valve body 15&, 15b... King surface 16... Compression spring for setting 18.19... Communication hole 20... Sealed chamber. Agent Patent Attorney Akio Takahashi 1st Makumen '44 Country/
Claims (1)
スクロールを組み合わせた圧縮機構と、旋回スクロール
を支持するフレームとを密閉容器内に納めると共に、圧
縮機構の吐出口を密閉容器内に連通させて該密閉容器内
を高圧圧力に維持する一力、旋回スクロールとフレーム
との間に形成した背圧室に前記子線機構の圧縮途中の圧
力を導入させて旋回スクロールに固定スクロール側への
押し付は力を付与し、密閉容器内の高圧圧力と前記背圧
室の圧力との差圧を利用して、旋回軸受、主軸受を含む
摺動部へ給油するようにして成るスクロール圧縮機であ
って、前記圧縮機構の低圧側室と前記背圧室とを連通遮
断する弁装置が備えられ、該弁装置は、固定スクロール
内に形成され、一方が高圧側室に、他方が背圧室および
圧縮機構の低圧側室にそれぞれ開口するシリンダと、そ
のシリンダ内に納められ、一端に高圧側室圧力の受圧面
を有し、かつ他端に背圧室圧力の受圧面を有する弁体と
、その弁体の背圧室側受圧面とシリンダ壁との間に介設
された設定ばねとで構成され、前記弁体の両受田面に作
用する圧力の差圧が設定ばねのばね力よりも大きいとき
には弁体が背圧室と前記低圧側室とを遮断する位置に変
位し、前記差圧が設定ばねのばね力よυも小さいときに
は、弁体が背圧室と低圧側室とを連通ずる位置に変位す
るようになっていることを特徴とするスクロール圧縮機
。A compression mechanism that combines an orbiting scroll having a thinly wound wrap and a fixed scroll and a frame that supports the orbiting scroll are housed in a closed container, and the discharge port of the compression mechanism is communicated with the inside of the closed container. In order to maintain a high pressure inside, the pressure during the compression of the child wire mechanism is introduced into the back pressure chamber formed between the orbiting scroll and the frame, and the force is applied to push the orbiting scroll against the fixed scroll side. The scroll compressor is configured to supply oil to sliding parts including a swing bearing and a main bearing by using the pressure difference between the high pressure in the closed container and the pressure in the back pressure chamber, the scroll compressor comprising: A valve device is provided that communicates and shuts off communication between the low pressure side chamber of the compression mechanism and the back pressure chamber, and the valve device is formed in the fixed scroll, and one side is connected to the high pressure side chamber and the other side is connected to the back pressure chamber and the low pressure side chamber of the compression mechanism. A cylinder that opens at each side, a valve body housed in the cylinder and having a pressure receiving surface for high pressure side chamber pressure at one end and a pressure receiving surface for back pressure chamber pressure at the other end, and a back pressure chamber of the valve body. It consists of a setting spring interposed between the side pressure receiving surface and the cylinder wall, and when the differential pressure between the pressures acting on both receiving surfaces of the valve body is larger than the spring force of the setting spring, the valve body releases back pressure. When the pressure difference is smaller than the spring force of the set spring, the valve body is displaced to a position where the back pressure chamber and the low pressure side chamber are communicated with each other. A scroll compressor characterized by:
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59098704A JPS60243388A (en) | 1984-05-18 | 1984-05-18 | Scroll compressor |
| KR1019850004907A KR870001409A (en) | 1984-05-18 | 1985-07-10 | Shroul Compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59098704A JPS60243388A (en) | 1984-05-18 | 1984-05-18 | Scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60243388A true JPS60243388A (en) | 1985-12-03 |
Family
ID=14226888
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59098704A Pending JPS60243388A (en) | 1984-05-18 | 1984-05-18 | Scroll compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPS60243388A (en) |
| KR (1) | KR870001409A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0337385A (en) * | 1989-07-04 | 1991-02-18 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| US5141407A (en) * | 1990-10-01 | 1992-08-25 | Copeland Corporation | Scroll machine with overheating protection |
| US5269661A (en) * | 1991-05-15 | 1993-12-14 | Sanden Corporation | Scroll type fluid displacement apparatus having a capacity control mechanism |
| GB2396886A (en) * | 2002-12-31 | 2004-07-07 | Scroll Tech | Restriction in scroll compressor backpressure tapping |
| CN100432442C (en) * | 2004-07-08 | 2008-11-12 | 乐金电子(天津)电器有限公司 | Negative pressure regulating structure of vortex compressor |
| JP2010053798A (en) * | 2008-08-29 | 2010-03-11 | Hitachi Appliances Inc | Scroll compressor |
| EP2177766A2 (en) | 2008-10-15 | 2010-04-21 | LG Electronics Inc. | Scroll compressor and refrigerating machine having the same |
| CN103174648A (en) * | 2011-12-20 | 2013-06-26 | 上海三电贝洱汽车空调有限公司 | Scroll compressor |
| WO2014196314A1 (en) * | 2013-06-03 | 2014-12-11 | 日立アプライアンス株式会社 | Scroll compressor and air conditioner using same |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101810461B1 (en) * | 2011-03-24 | 2017-12-19 | 엘지전자 주식회사 | Scroll compressor |
-
1984
- 1984-05-18 JP JP59098704A patent/JPS60243388A/en active Pending
-
1985
- 1985-07-10 KR KR1019850004907A patent/KR870001409A/en not_active IP Right Cessation
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0337385A (en) * | 1989-07-04 | 1991-02-18 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| US5141407A (en) * | 1990-10-01 | 1992-08-25 | Copeland Corporation | Scroll machine with overheating protection |
| US5527158A (en) * | 1990-10-01 | 1996-06-18 | Copeland Corporation | Scroll machine with overheating protection |
| US5269661A (en) * | 1991-05-15 | 1993-12-14 | Sanden Corporation | Scroll type fluid displacement apparatus having a capacity control mechanism |
| US5362211A (en) * | 1991-05-15 | 1994-11-08 | Sanden Corporation | Scroll type fluid displacement apparatus having a capacity control mechanism |
| GB2396886A (en) * | 2002-12-31 | 2004-07-07 | Scroll Tech | Restriction in scroll compressor backpressure tapping |
| US6896499B2 (en) | 2002-12-31 | 2005-05-24 | Scroll Technologies | Scroll compressor with flow restriction and back pressure chamber tap |
| GB2396886B (en) * | 2002-12-31 | 2005-06-15 | Scroll Tech | Scroll compressor with flow restriction and back pressure chamber tap |
| CN100432442C (en) * | 2004-07-08 | 2008-11-12 | 乐金电子(天津)电器有限公司 | Negative pressure regulating structure of vortex compressor |
| JP2010053798A (en) * | 2008-08-29 | 2010-03-11 | Hitachi Appliances Inc | Scroll compressor |
| EP2177766A2 (en) | 2008-10-15 | 2010-04-21 | LG Electronics Inc. | Scroll compressor and refrigerating machine having the same |
| EP2177766A3 (en) * | 2008-10-15 | 2011-07-06 | LG Electronics Inc. | Scroll compressor and refrigerating machine having the same |
| CN103174648A (en) * | 2011-12-20 | 2013-06-26 | 上海三电贝洱汽车空调有限公司 | Scroll compressor |
| CN103174648B (en) * | 2011-12-20 | 2016-08-24 | 华域三电汽车空调有限公司 | Screw compressor |
| WO2014196314A1 (en) * | 2013-06-03 | 2014-12-11 | 日立アプライアンス株式会社 | Scroll compressor and air conditioner using same |
| JPWO2014196314A1 (en) * | 2013-06-03 | 2017-02-23 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Scroll compressor and air conditioner using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| KR870001409A (en) | 1987-03-13 |
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