JPH0219688A - Horizontal enclosed rotary compressor - Google Patents
Horizontal enclosed rotary compressorInfo
- Publication number
- JPH0219688A JPH0219688A JP17038388A JP17038388A JPH0219688A JP H0219688 A JPH0219688 A JP H0219688A JP 17038388 A JP17038388 A JP 17038388A JP 17038388 A JP17038388 A JP 17038388A JP H0219688 A JPH0219688 A JP H0219688A
- Authority
- JP
- Japan
- Prior art keywords
- oil supply
- crankshaft
- discharge
- static pressure
- bearing
- 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
- 239000003507 refrigerant Substances 0.000 claims abstract description 19
- 230000003068 static effect Effects 0.000 claims abstract description 16
- 239000003921 oil Substances 0.000 claims description 44
- 239000010687 lubricating oil Substances 0.000 claims description 28
- 230000006835 compression Effects 0.000 claims description 13
- 238000007906 compression Methods 0.000 claims description 13
- 238000004891 communication Methods 0.000 claims description 12
- 230000007423 decrease Effects 0.000 claims description 9
- 239000000314 lubricant Substances 0.000 abstract 2
- 230000001050 lubricating effect Effects 0.000 abstract 1
- 230000030279 gene silencing Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 241000208195 Buxaceae Species 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
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
- F04C29/023—Lubricant distribution through a hollow driving shaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、冷凍・空調用の横置式密閉形回転圧縮機に
係９．特に潤滑油の供給手段に関するものである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a horizontal hermetic rotary compressor for refrigeration and air conditioning. In particular, it relates to lubricating oil supply means.
第９図は例えば実公昭５７−２６０６７号公報に示され
た従来の密閉形回転圧縮機の縦断面図、第１０図は第９
図のＸ−Ｘ線断面図であ９１図中（１）は密閉容器で、
この密閉容器（１）内に電動要素（２）と圧縮要素（３
）が収納されてお九両者はクランク軸（４）により連結
されている。そして、吸入孔（図示せず〕を通って円筒
シリンダ（５）内へ吸入され九冷媒ガスが、ピストン（
６）、ベーン（７）、シリンダヘッド（８）およびフレ
ーム（９）よシ構成される圧縮室内にて圧縮された後、
吐出弁（ＩＧを経て吐出マクラαコ内の吐出消音室α２
へ間欠的に吐出され、同消音室ａＺ内の圧縮冷媒ガスが
吐出孔（図示せず〕を通ってガスクーラ（図示せず］へ
あるいは直接密閉容器１１１内へ流出されるように構成
されている。FIG. 9 is a vertical sectional view of a conventional hermetic rotary compressor shown in, for example, Japanese Utility Model Publication No. 57-26067, and FIG.
In the XX-X cross-sectional view of the figure, (1) in Figure 91 is a closed container.
Inside this airtight container (1), there is an electric element (2) and a compression element (3).
) are housed therein, and both are connected by a crankshaft (4). Then, the refrigerant gas is sucked into the cylindrical cylinder (5) through the suction hole (not shown) and flows into the piston (
6) After being compressed in a compression chamber consisting of a vane (7), a cylinder head (8) and a frame (9),
Discharge valve (through IG, discharge muffling chamber α2 inside discharge pillow α)
The compressed refrigerant gas in the silencing chamber aZ is intermittently discharged to the silencing chamber aZ and is configured to flow out through a discharge hole (not shown) to a gas cooler (not shown) or directly into the sealed container 111. .
このように構成される密閉形回転圧縮機において、゛こ
こでは吐出パイプα３が設けられる。この吐出パイプα
３は、一端は吐出消音室α２に接続されるとともに、他
端がクランク軸（４）自給油孔と連なっておシ、吐出消
音室ａ３からは、たとえばガスクーラへ流出した残シの
小量の圧縮冷媒ガスが流入されるもので、この圧縮冷媒
ガスは吐出パイプαｊを通ってクランク軸（４）内へ流
出される。また、上記吐出パイプな３はその中間部が、
密閉容器（１）の下部においてその内周に沿って円弧状
に配置されるもので、この円弧状部分には所定間隔に複
数の小孔（１４＋ 、α９．αＧが穿設される。なお、
密閉容器（１）の下部には潤滑油αηが貯留されている
。In the hermetic rotary compressor configured in this way, a discharge pipe α3 is provided here. This discharge pipe α
3 is connected at one end to the discharge silencing chamber α2, and at the other end is connected to the crankshaft (4) self-lubricating hole. Compressed refrigerant gas is flowed in, and this compressed refrigerant gas is discharged into the crankshaft (4) through the discharge pipe αj. In addition, the middle part of the above-mentioned discharge pipe 3 is
It is arranged in an arc shape along the inner periphery of the lower part of the closed container (1), and a plurality of small holes (14+, α9, αG) are bored at predetermined intervals in this arc-shaped part.
Lubricating oil αη is stored in the lower part of the closed container (1).
上記のような吐出パイプα３を備える密閉形回転圧縮機
においては、今、第１１図のごとく、小孔Ｉが鉛直方向
（矢印ａで示す）最下方にくるように設置すれば、この
小孔α着が潤滑油αη中に開口してこの小孔α４を通し
て潤滑油αηが吐出パイプ０内へ流入し、クランク軸（
４）内へと供給される。すなわち、潤滑油（Ｉη中に浸
った小孔側からは、圧縮要素（３）から吐出弁α１を経
て吐出消音室α２内へ間欠的に吐出される圧縮冷媒ガス
の休止中に、潤滑油σのが吐出パイプａｊ内に流入し、
この潤滑油αηは、吐出弁α０からの圧縮冷媒ガス吐出
開始にともない吐出消音室０３内に生じる衝激オーバー
シュート圧力により、吐出行程中に吐出パイプａ３を通
ってクランク軸（４）へと供給される。一方、圧縮機を
回転させて９０°傾けた場合を第１３図に示すもので、
この場合は鉛直方向最下方に小孔（ｌｅが位置してこの
小孔Ｏｅがｎ滑油（Ｉｎ中に開口する。したがって、こ
の場合も、上述した小孔Ｉの場合と同様にして潤滑油１
１？＋がクランク軸（４）へ供給されるようになる。In a hermetic rotary compressor equipped with the discharge pipe α3 as described above, if it is installed so that the small hole I is at the lowest position in the vertical direction (indicated by arrow a), as shown in FIG. The lubricating oil αη opens into the lubricating oil αη, and the lubricating oil αη flows into the discharge pipe 0 through this small hole α4, and the crankshaft (
4) It is supplied to the inside. That is, from the small hole side immersed in the lubricating oil (Iη), the lubricating oil σ flows into the discharge pipe aj,
This lubricating oil αη is supplied to the crankshaft (4) through the discharge pipe a3 during the discharge stroke due to the impulse overshoot pressure generated in the discharge muffling chamber 03 as compressed refrigerant gas discharge starts from the discharge valve α0. be done. On the other hand, Fig. 13 shows the case where the compressor is rotated and tilted at 90 degrees.
In this case, a small hole (le) is located at the lowest position in the vertical direction, and this small hole Oe opens into the lubricating oil (In). Therefore, in this case as well, the lubricating oil is 1
1? + is now supplied to the crankshaft (4).
また８両者の中間位置に圧縮機を傾けた場合を第１２図
に示すもので、この場合は小孔ｒ１Ｓによって潤滑油ａ
ηがクランク軸（４）へ同様にして供給される。In addition, Fig. 12 shows a case where the compressor is tilted to an intermediate position between the two, and in this case, the lubricating oil a
η is similarly supplied to the crankshaft (4).
従来の給油機構は以上のように構成されているので、吐
出ガス流蓋の変動によって、給油される潤滑油量も大き
く変動する したがって、クランク軸（４）の回転数を
変化させて、容量制御を行なうような場合、潤滑油量η
が十分に供給されない状態が生じるなどの問題点、また
給油管が長くなるため密閉容器内に広い空間を確保しな
ければならないという問題点があった。Since the conventional lubrication mechanism is configured as described above, the amount of lubricating oil supplied varies greatly depending on the variation of the discharge gas flow cover. Therefore, the capacity is controlled by changing the rotation speed of the crankshaft (4). In such cases, the amount of lubricating oil η
There were problems such as a situation in which a sufficient amount of fuel was not supplied, and a problem that a large space had to be secured in the closed container because the refueling pipe was long.
この発明は上記のような問題点を解消するためになされ
たもので、横置形の密閉形圧縮機が可変速運転モードで
、駆動されても、安定した給油状態が確保できるととも
に省スペースで且つ安価な給油機構を得ることを目的と
する。This invention was made to solve the above-mentioned problems, and even when a horizontal hermetic compressor is driven in variable speed operation mode, it is possible to ensure a stable oil supply state, save space, and The purpose is to obtain an inexpensive oil supply mechanism.
この発明に係る横置式密閉形回転圧縮機は密閉容器、こ
の密閉容器に収納され冷媒を圧縮する圧縮要素、この圧
縮要素の各摺動部に潤滑油を供給する給油路を有するク
ランク軸または軸受、前記圧縮要素によって圧縮された
冷媒ガスが高速で通過する吐出ガス通路、この吐出ガス
通路と前記クランク軸又は軸受の給油路を連通させる連
通孔。The horizontal hermetic rotary compressor according to the present invention includes a hermetic container, a compression element that is housed in the hermetic container and compresses a refrigerant, and a crankshaft or a bearing that has an oil supply path that supplies lubricating oil to each sliding part of the compression element. a discharge gas passage through which refrigerant gas compressed by the compression element passes at high speed; and a communication hole that communicates the discharge gas passage with an oil supply passage of the crankshaft or bearing.
前記吐出ガス通路は高速で冷媒が通過する几め静圧が低
下しこの吐出ガス通路に前記連通孔を介して連通してい
る前記クランク軸又は軸受の給油路の静圧も低下するこ
とを利用して前記密閉容器の下部に貯留された潤滑油を
前記クランク軸又は軸受の給油路へ供給する給油手段を
備えたものである。The discharge gas passage takes advantage of the fact that the static pressure of the refrigerant that passes through it at high speed decreases, and the static pressure of the oil supply passage of the crankshaft or bearing that communicates with the discharge gas passage through the communication hole also decreases. The apparatus further includes an oil supply means for supplying the lubricating oil stored in the lower part of the closed container to the oil supply path of the crankshaft or bearing.
この発明における横置式密閉形回転圧縮機は。 The horizontal hermetic rotary compressor in this invention is:
吐出ガス通路の静圧が低下することを利用して密閉容器
に貯留された潤滑油を圧縮要素の摺動部に供給するもの
である。The lubricating oil stored in the closed container is supplied to the sliding part of the compression element by utilizing the decrease in static pressure in the discharge gas passage.
以下、この発明の第１の実施例を第１図によシ説明する
。図において、（１）〜顛は上記従来のものと全く同一
のものである。囚において、 （４ａ）は給油穴、 （
４ｂ）は給油孔、連通孔である（８ａ）は油溝。A first embodiment of the present invention will be described below with reference to FIG. In the figure, sections (1) to 1 are completely the same as the conventional one. In the prisoner, (4a) is the refueling hole, (
4b) is an oil supply hole and a communication hole, and (8a) is an oil groove.
（８ｂ）は連通小孔、ａａは吐出ガス通路である。(8b) is a communicating small hole, and aa is a discharge gas passage.
圧縮機が駆動されると、シリンダ（５）内から吐出弁（
ＩＱを経て吐出されたガスは、シリンダ・ヘッド（８）
と吐出マフラ住υとで形成され友吐出消音室ｔｔａに拡
がシ、その流速を減少する。その後、圧縮機要素（３）
内に設けられた吐出ガス通路（Ｉ・を通って、密閉容器
（１）内へ吐出されるが、吐出ガス通路（［Ｓを通過す
る際には、吐出消音室Ｑ３よシも断面積が減少するので
、その流速が増加する。この時、流速増加による吐出ガ
ス動圧が増加して、その分静圧が減少する為、密閉容器
（１）内の静圧より、吐出ガス通路Ｉ内の静圧が低くな
る。したがって、この吐出ガス通路ａｌと給油管αｊを
連通ずる構造を形成しかつ、この連通部分容積を密閉容
器（１）内から分離した空間として形成すると、給油管
０内の静圧が低下し、密閉容器（１）下部の潤滑油（＋
７１が吸上げられて、クランク軸（４１の給油穴（４ａ
）内へ供給され。When the compressor is driven, the discharge valve (
The gas discharged through the IQ is sent to the cylinder head (8)
It is formed by a discharge muffler housing υ and expands into a discharge muffling chamber tta, reducing its flow velocity. Then the compressor element (3)
The discharge gas is discharged into the sealed container (1) through the discharge gas passage (I) provided in the chamber, but when passing through the discharge gas passage (S), At this time, the dynamic pressure of the discharge gas increases due to the increase in the flow velocity, and the static pressure decreases accordingly, so the static pressure in the discharge gas passage I is lower than the static pressure in the closed container (1). Therefore, if a structure is formed that communicates this discharge gas passage al with the oil supply pipe αj, and this communication partial volume is formed as a space separated from the inside of the closed container (1), the inside of the oil supply pipe 0 becomes lower. The static pressure of the lubricating oil (+
71 is sucked up and the crankshaft (41 oil supply hole (4a)
).
給油孔（４ｂ）を経て各軸受部潤滑の機能を果す。It functions to lubricate each bearing part through the oil supply hole (4b).
第２（２）は、この発明の第２の実施例を示す断面図で
あり、小容量の圧縮機や、可変速駆動圧縮機のように吐
出ガス通路（１１１を通過するガス流速が遅い場合に採
用される機構で、吐出ガス通路αω内にオリフィス（絞
シ）部（８ｃ） を設け、この部分に連通小孔（８ｂ）
の開口部を位愈させた構造であシこのオリアイス（８Ｃ
）部で吐出ガス流速を増加させて給油管（１３内におい
て潤滑油αηを吸上げる為に必要な静圧を得る機構とな
っている。No. 2 (2) is a sectional view showing a second embodiment of the present invention. This is the mechanism adopted in
This Oriais (8C) has a structure that reduces the opening of the
) section increases the discharge gas flow velocity to obtain the static pressure necessary to suck up the lubricating oil αη inside the oil supply pipe (13).
第３図はこの発明の第３の実施例を示す断面図であり、
ンＶ−ム（９）側に取り付けた吐出マフラαυと、フレ
ーム（９）のボス部（９ａ）で吐出ガス通路α梯が構成
されている。第４図に示す様に、フレーム（９）の吐出
弁ａ１を通過した圧縮冷媒は、フレームボス部（９ａ）
と吐出ガス通路α♂を通過する際、高速で流れるため、
軸受の油溝（９リ と吐出ガス通路Ｕとを連通している
連通孔である孔（９ｂ）の部分で圧力降下が生じ、クラ
ンク軸（４）の外周に設けられている油溝（４りやシリ
ンダヘッド（８）の軸受部（８ｄ）に加工しである油溝
（８ａ）を通って、これらの油溝に溜っている潤滑油が
流れ、さらにこの−連の油溝の圧力降下の作用でシリン
ダヘッド（８）に取シ付けられた。油溝（８ａ）と密閉
容器（１１内に溜である潤滑油ａηとを連結する給油管
０３内を潤滑油が上がり、油溝（ａａＪ 部に潤滑油を
供給する仕組となっている。なお、第４図において、矢
印Ａは圧縮冷媒の流れを示し、矢印Ｂは潤滑油の流れを
示す。FIG. 3 is a sectional view showing a third embodiment of the invention,
A discharge gas passage α ladder is constituted by a discharge muffler αυ attached to the frame (9) side and a boss portion (9a) of the frame (9). As shown in Fig. 4, the compressed refrigerant that has passed through the discharge valve a1 of the frame (9) is transferred to the frame boss portion (9a).
Because it flows at high speed when passing through the discharge gas passage α♂,
A pressure drop occurs at the hole (9b), which is a communication hole that communicates the oil groove (9) of the bearing with the discharge gas passage U, and the oil groove (4) provided on the outer periphery of the crankshaft (4) decreases. The lubricating oil accumulated in these oil grooves flows through the oil grooves (8a) machined into the bearing part (8d) of the cylinder head (8), and the pressure drop in these oil grooves is further reduced. The oil is attached to the cylinder head (8) by the action.The lubricating oil rises in the oil supply pipe 03 that connects the oil groove (8a) and the lubricating oil aη, which is a reservoir in the closed container (11). In Fig. 4, arrow A indicates the flow of compressed refrigerant, and arrow B indicates the flow of lubricating oil.
また第５図は、第３図の実施例で示し几吐出マクラの正
面図であ〕、また第６図は第５図のＶＩ−■線断面図を
示す。5 is a front view of the liquid discharge pillow shown in the embodiment of FIG. 3], and FIG. 6 is a sectional view taken along the line VI--■ in FIG. 5.
第７図では、この発明の第４の実施例を示す断面図で、
この場合、軸支部油溝（８ａ）と密閉容器（１）内の潤
滑油αηとを連結する給油管は、シリンダヘッド（８）
のつげｓ（８リ に円管を打ち込むことによシ構成した
ものである。この方法により第３図で示した実施例と同
様の効果が得られるだけでなく、第３図の給油管αＪの
様にシリンダヘッド（８）よシ後方のスペースを必要と
しない分、省スペース化を実現できる。FIG. 7 is a sectional view showing a fourth embodiment of the present invention.
In this case, the oil supply pipe connecting the shaft oil groove (8a) and the lubricating oil αη in the closed container (1) is connected to the cylinder head (8).
This is constructed by driving a circular pipe into the boxwood s (8ri).This method not only provides the same effect as the embodiment shown in Fig. 3, but also allows the oil supply pipe αJ in Fig. Since no space is required behind the cylinder head (8), space can be saved.
第８図は、この発明の第５の実施例を示し、陶図では、
圧縮冷媒は、シリンダヘッド（８）に設けられた吐出バ
ルブ翰を通過して、そこに取り付けられた吐出マフラ（
ｌυから流れ出る。この例の場合は軸支部油溝（８ａ）
、 （９りと密閉容器（１１内の油溜め儂ηとを連結
する給油管α３は、フレーム（９）及びシリンダヘッド
（８）の両方に取シ付けられ上述の第１〜第４の実施例
よシさらに高い給油能力を確保することができる。FIG. 8 shows a fifth embodiment of the present invention, and the ceramic diagram shows:
The compressed refrigerant passes through the discharge valve cover provided in the cylinder head (8) and passes through the discharge muffler (
Flows out from lυ. In this example, the shaft support oil groove (8a)
(The oil supply pipe α3 connecting the oil tank η in the airtight container (11) is attached to both the frame (9) and the cylinder head (8), and is attached to both the frame (9) and the cylinder head (8). For example, even higher refueling capacity can be secured.
この発明による横置式密閉形圧縮機は、密閉容器、この
密閉容器に収納され冷媒を圧縮する圧縮要素、この圧縮
要素の各摺動部に潤滑油を供給する給油路を有するクラ
ンク軸または軸受、前記圧縮要素によって圧縮された冷
媒ガスが高速′で通過する吐出ガス通路、この吐出ガス
通路と前記クランク軸又は軸受の給油路を連通させる連
通孔、前記吐出ガス通路は高速で冷媒が通過するため静
圧が低下しこの吐出ガス通路に前記連通孔を介して連通
している前記クランク軸又は軸受の給油路の静圧も低下
することを利用して前記密閉容器の下部に貯留された潤
滑油を前記クランク軸又は軸受の給油路へ供給する給油
手段を備えた構成にしたので従来の給油方式に比べ給油
手段を小形化できるという効果を奏する。The horizontal hermetic compressor according to the present invention includes a hermetic container, a compression element that is housed in the hermetic container and compresses a refrigerant, a crankshaft or a bearing that has an oil supply passage that supplies lubricating oil to each sliding part of the compression element, A discharge gas passage through which the refrigerant gas compressed by the compression element passes at high speed; a communication hole through which the discharge gas passage communicates with the oil supply path of the crankshaft or bearing; and a communication hole through which the refrigerant passes at high speed through the discharge gas passage. The lubricating oil is stored in the lower part of the sealed container by taking advantage of the fact that the static pressure decreases and the static pressure of the oil supply path of the crankshaft or bearing that communicates with the discharge gas passage through the communication hole also decreases. Since the structure includes an oil supply means for supplying oil to the oil supply passage of the crankshaft or bearing, the oil supply means can be made smaller in size compared to conventional oil supply systems.
第１図はこの発明の第１の実施例を示す部分縦断面図、
第２図はこの発明の第２の実施例を示す要部縦断面図、
第３図はこの発明の第３の実施例を示す縦断面図、第４
図はＥ３図の第３の実施例の要部拡大図、第５図はＭ３
図の第３の実施例の吐出マフラの正面図、第６図は同側
面図、第７図はこの発明の第４の実施例を示す縦断面図
、第８図はこの発明の第５の実施例を示す縦断面図、第
９図は従来の密閉形圧縮機の部分縦断面図、第１０図は
第９図のＸ−Ｘ線断面図、第１１図〜第１３図は第９因
の従来の密閉形圧縮機の設置例を示す図である。
図において（１）は密閉容器、（３）は圧縮要素、（４
）はクランク軸、 （４ａ）は給油穴、（８）はシリン
ダヘッド。
（８ａ）は油溝、 （８ｔ））は連通小孔、 ａｎは
吐出７７う。
α２は吐出消音室、 （１３は給油管、罰は潤滑油、ａ
♂は吐出ガス通路である。
なお、各図中、同一符号は同−又は相当部分を示す。FIG. 1 is a partial vertical sectional view showing a first embodiment of the invention;
FIG. 2 is a vertical cross-sectional view of main parts showing a second embodiment of the present invention;
FIG. 3 is a vertical sectional view showing a third embodiment of the present invention, and FIG.
The figure is an enlarged view of the main part of the third embodiment in figure E3, and figure 5 is M3.
FIG. 6 is a front view of the discharge muffler of the third embodiment of the invention, FIG. 6 is a side view of the same, FIG. 7 is a vertical sectional view of the fourth embodiment of the invention, and FIG. 9 is a partial vertical sectional view of a conventional hermetic compressor, FIG. 10 is a sectional view taken along the line X-X in FIG. 9, and FIGS. 11 to 13 are views showing the ninth factor. FIG. 2 is a diagram showing an installation example of a conventional hermetic compressor. In the figure, (1) is a closed container, (3) is a compression element, and (4
) is the crankshaft, (4a) is the oil supply hole, and (8) is the cylinder head. (8a) is an oil groove, (8t)) is a small communication hole, and an is a discharge 77. α2 is the discharge silencing chamber, (13 is the oil supply pipe, the penalty is the lubricating oil, a
♂ is a discharge gas passage. In each figure, the same reference numerals indicate the same or corresponding parts.
Claims (2)
る圧縮要素、この圧縮要素の各摺動部に潤滑油を供給す
る給油路を有するクランク軸または軸受、前記圧縮要素
によつて圧縮された冷媒ガスが高速で通過する吐出ガス
通路、この吐出ガス通路と前記クランク軸又は軸受の給
油路を連通させる連通孔、前記吐出ガス通路は高速で冷
媒が通過するため静圧が低下しこの吐出ガス通路に前記
連通孔を介して連通している前記クランク軸又は軸受の
給油路の静圧も低下することを利用して前記密閉容器の
下部に貯留された潤滑油を前記クランク軸又は軸受の給
油路へ供給する給油手段を備えた横置式密閉形圧縮機。(1) An airtight container, a compression element housed in the airtight container that compresses the refrigerant, a crankshaft or bearing having an oil supply passage that supplies lubricating oil to each sliding part of the compression element, and a refrigerant compressed by the compression element. A discharge gas passage through which the refrigerant gas passes at high speed, a communication hole that communicates this discharge gas passage with the oil supply passage of the crankshaft or bearing, and a communication hole through which the refrigerant passes at high speed, the static pressure decreases and this discharge occurs. The lubricating oil stored in the lower part of the sealed container is transferred to the crankshaft or bearing by taking advantage of the fact that the static pressure in the oil supply path of the crankshaft or bearing, which communicates with the gas passage through the communication hole, decreases. A horizontal hermetic compressor equipped with a means of supplying oil to the oil supply path.
設けたことを特徴とする特許請求の範囲第１項記載の横
置式密閉形回転圧縮機。(2) The horizontal hermetic rotary compressor according to claim 1, wherein the discharge gas passage is provided between the discharge muffler and the outer periphery of the bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17038388A JPH0219688A (en) | 1988-07-08 | 1988-07-08 | Horizontal enclosed rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17038388A JPH0219688A (en) | 1988-07-08 | 1988-07-08 | Horizontal enclosed rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0219688A true JPH0219688A (en) | 1990-01-23 |
Family
ID=15903918
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17038388A Pending JPH0219688A (en) | 1988-07-08 | 1988-07-08 | Horizontal enclosed rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0219688A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0601960A1 (en) * | 1992-12-07 | 1994-06-15 | Carrier Corporation | Lubrication system for horizontal rotary compressor |
| KR20010018081A (en) * | 1999-08-17 | 2001-03-05 | 구자홍 | Muffler noise reduction structure for sealed type rotary compressor |
| JP2021116727A (en) * | 2020-01-24 | 2021-08-10 | 日立ジョンソンコントロールズ空調株式会社 | Horizontal compressor |
-
1988
- 1988-07-08 JP JP17038388A patent/JPH0219688A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0601960A1 (en) * | 1992-12-07 | 1994-06-15 | Carrier Corporation | Lubrication system for horizontal rotary compressor |
| KR20010018081A (en) * | 1999-08-17 | 2001-03-05 | 구자홍 | Muffler noise reduction structure for sealed type rotary compressor |
| JP2021116727A (en) * | 2020-01-24 | 2021-08-10 | 日立ジョンソンコントロールズ空調株式会社 | Horizontal compressor |
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