JPH02230985A - Parallel compression type refrigerator - Google Patents
Parallel compression type refrigeratorInfo
- Publication number
- JPH02230985A JPH02230985A JP5222889A JP5222889A JPH02230985A JP H02230985 A JPH02230985 A JP H02230985A JP 5222889 A JP5222889 A JP 5222889A JP 5222889 A JP5222889 A JP 5222889A JP H02230985 A JPH02230985 A JP H02230985A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- oil
- pressure
- suction
- pipe
- 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.)
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は互いに並列に接続された圧縮機の並列運転時
，或に任意の圧縮機の単独運転時のいずれの場合でも圧
縮機の油面を適正に保つようにした並列圧縮式冷凍装置
に関するものである。[Detailed Description of the Invention] [Industrial Application Field] This invention provides a method for controlling the oil level of a compressor, whether in parallel operation of compressors connected in parallel with each other or in individual operation of any compressor. This invention relates to a parallel compression type refrigeration system that maintains a proper temperature.
第２図は従来の並列圧縮式冷凍装置を示すものであり、
（１） ， （２１ ， （３）は第１、第２、第３の
半密閉形圧縮機、（ｌａ），（２ａ），（３ａ）はこの
圧縮機（１１ ， ＋２１ ，（３》のクランクケース
で、この中には隔壁（ｌｂ），（２ｂ），（３ｂ）によ
りモータ室（１０ ， （２ｃ），（３ｃ）と圧縮要素
（ｌｄ），（２ｄ），（３ｄ）として区画形成されてい
る。Figure 2 shows a conventional parallel compression refrigeration system.
(1), (21, (3) are the first, second, and third semi-hermetic compressors, and (la), (2a), and (3a) are the compressors (11, +21, (3)). The crankcase is divided into motor chambers (10, (2c), (3c) and compression elements (ld), (2d), (3d) by partition walls (lb), (2b), (3b). has been done.
（ １ ｅ ） Ｔ （ ２ｅ ） ＋ （ ３ ｅ
） ＊ ’ ” ｆ ） ＊ （ ２ ｆ ） ＋ （
３ ｆ ）は各々モータ室（ ＩＣ） ， （２Ｃ）
， （３Ｃ）、圧縮要素室（ｘａ），（２ｄ） ，（３
ｄ）に収容されたモータ及び、圧縮要素である。(1 e) T (2e) + (3 e
) * ' ” f ) * ( 2 f ) + (
3f) are motor chambers (IC) and (2C) respectively.
, (3C), compression element chamber (xa), (2d), (3
d) a motor and a compression element housed in.
（Ｉｇ） ， （２ｇ） ， （３ｇ）は両要素（ １
ｅ ） ＋ （２ ｅ ） ＋ （ ３ｅ ） ＊（
ｔｒ），（ｚｒ），（：＋ｒ） を接続するクランク
軸、（１ｈ），（２ｈ），（３ｈ）は隔壁（ｌｂ） ，
（２ｂ） ， （３ｂ）の上部に設けられた均圧用差
圧弁で、起動時のようにモータ室（１（） ， （２Ｃ
） ，（３Ｃ）の圧力が、圧縮要素室（ｘｄ），（２ｄ
冫，（３ｄ）の圧力よりも著しく低くなるような時、閉
となるものである。（１ ｉ） ， （２ｉ） ， （
３ｉ）は隔壁（ｌｂ），（ｚｂ），（３ｂ）の下部に設
けた均油用逆止弁で、モータ室（ｌｃ） ， （２ｃ）
， （３ｃ）底部の油溜（１１），（２ｊ），（Ｊ）
から圧縮要素室（ ｌｄ） ， （２ｄ） ， （３ｄ
）底部の油溜（１ｋ）．（２ｋ），（３ｋ）へのみ油の
流入を許容するものである。(Ig), (2g), (3g) are both elements (1
e) + (2 e) + (3e) *(
tr), (zr), (:+r), (1h), (2h), (3h) are bulkheads (lb),
(2b), (3b) are pressure equalizing differential pressure valves installed at the top of motor chambers (1(), (2C)
), (3C), the pressure in the compression element chamber (xd), (2d
When the pressure becomes significantly lower than (3d), it closes. (1 i) , (2i) , (
3i) is an oil equalizing check valve installed at the bottom of the bulkheads (lb), (zb), (3b), and the motor chamber (lc), (2c)
, (3c) Bottom oil sump (11), (2j), (J)
From compression element chamber (ld), (2d), (3d
) Oil sump at the bottom (1k). This allows oil to flow only into (2k) and (3k).
（４） ｌｉ各圧縮機（１） ， ＋２１ ， （３１
の圧縮要素室（ ｌｄ）（２ｄ），（３ｄ）を連通ずる
均圧均油管、（７）は蒸発器（図示せず）に接続された
冷凍サイクルの吸入管，（８》はこの吸入管（７）と第
１の圧縮機（１）のモータ室（１ｃ）とを接続する第１
の圧縮機（１）の吸入分岐管，（９）は吸入管（７》と
第２の圧縮機（２）のモータ室（２ｃ）とを接続する第
２の圧縮機《２》の吸入分岐管、σｑは吸入管（７）と
第３の圧縮機（３》のモータ室（３Ｃ）とを接続する第
３の圧縮機（３）の吸入分岐管で、第１の吸入分岐管（
８）は第２の吸入分岐管《８》は第２の吸入分岐管（９
）より太い径で、第２の吸入分岐管（９）は第３の吸入
分岐管αＱより太い径であり、第１の吸入分岐管（８）
は第２及び第３の吸入分岐管（９） ， （１０より，
配管長さが短《されている。αυは各圧縮機（１） ，
＋２１ ，《３》の共通吐出管で、凝縮器，膨張弁（
図示せず）を介して蒸発器（図示せず）に接続されてい
る。(4) li each compressor (1) , +21 , (31
(7) is the suction pipe of the refrigeration cycle connected to the evaporator (not shown), and (8) is this suction pipe. (7) and the motor chamber (1c) of the first compressor (1).
(9) is the suction branch of the second compressor (2) connecting the suction pipe (7) and the motor chamber (2c) of the second compressor (2). The pipe σq is the suction branch pipe of the third compressor (3) that connects the suction pipe (7) and the motor chamber (3C) of the third compressor (3), and the first suction branch pipe (
8) is the second suction branch pipe (8) is the second suction branch pipe (9).
), the second suction branch pipe (9) has a larger diameter than the third suction branch pipe αQ, and the second suction branch pipe (8) has a larger diameter than the third suction branch pipe αQ.
are the second and third suction branch pipes (9), (from 10,
Piping length has been shortened. αυ is each compressor (1),
+21,《3》 common discharge pipe, condenser, expansion valve (
It is connected to an evaporator (not shown) via an evaporator (not shown).
従釆の３台の圧縮機による並列圧縮式冷凍装置において
は、各圧縮機間に均圧均油配管が設けられ、これ等の配
管は並列運転を問わず運転中は連通した状態で運転して
いた。この結果吸入室要素と圧縮室要素に区分された半
密閉形冷凍機においては、単独運転中、停止した圧縮機
の吸入管，モータ室、圧縮要素室及び均圧管を通して、
運転中の圧縮機の圧縮要素室に圧力がかかる為運転中の
圧縮機の均油逆止弁が閉となり、せっかく吸入室へ戻っ
た油が圧縮要素室へ戻らず、圧縮室の油面を正常に維持
することは難しく，圧縮機の摺動部への潤滑油の供給不
良等により焼付や運転中の圧縮機の油上り量過大による
冷凍能力の低下、及び油圧縮による弁部分の損傷の恐れ
があった。また、単独運転中吸入室へ戻り溜った油はモ
ータによりかき上げられ吐出され、油上がりが過大にな
るのを防止するため、圧縮機の吐出側に油分離器を取付
け、吐出ガス中に含まれている油を分離して圧縮機へ返
送する方法もめるが，高温の油がクランクケースに戻り
、油温を上昇させること、及び長時間停止後の再始動時
には温度の低い分離器内で凝縮した液冷媒が圧縮機に返
送され、油を泡立たせ潤滑不良を発生すること等の危険
性があった。In a parallel compression type refrigeration system with three subordinate compressors, pressure equalization oil piping is installed between each compressor, and these piping must be operated in a connected state during operation, regardless of parallel operation. was. As a result, in a semi-hermetic refrigerator that is divided into a suction chamber element and a compression chamber element, during independent operation, the suction pipe, motor chamber, compression element chamber, and pressure equalization pipe of the stopped compressor are
Because pressure is applied to the compression element chamber of the compressor during operation, the oil equalization check valve of the compressor during operation closes, and the oil that has returned to the suction chamber does not return to the compression element chamber, causing the oil level in the compression chamber to drop. It is difficult to maintain the compressor in normal condition, and it can cause seizure due to insufficient supply of lubricating oil to the sliding parts of the compressor, decrease in refrigeration capacity due to excessive oil flow from the compressor during operation, and damage to valve parts due to oil compression. There was fear. In addition, during independent operation, the oil that returns to the suction chamber and accumulates is scraped up by the motor and discharged.In order to prevent the oil from becoming excessive, an oil separator is installed on the discharge side of the compressor to prevent oil from being contained in the discharged gas. A method is also being considered to separate the oil contained in the oil and send it back to the compressor, but the problem is that the high temperature oil returns to the crankcase and raises the oil temperature, and that it condenses in the low temperature separator when restarting after a long stop. There was a risk that the liquid refrigerant would be returned to the compressor, causing oil to bubble and causing poor lubrication.
また，圧縮機の圧縮要素室に微小な差圧が生じ、運転中
の圧縮機の油面がアンバランスとなり易い傾向があり、
保守に当り油窓からの油面位置の確認が難しく保守業務
がやり難くなり、また第２及び第３の圧縮機がフオーミ
ングを起こすと必要以上の油が第１の圧縮機に流出して
、第２及び第３の圧縮機の油面が低下する等の問題点が
あった。In addition, a small pressure difference occurs in the compression element chamber of the compressor, which tends to cause the oil level of the compressor to become unbalanced during operation.
During maintenance, it is difficult to check the oil level position through the oil window, making maintenance work difficult, and if the second and third compressors start forming, more oil than necessary will leak into the first compressor. There were problems such as a drop in the oil level in the second and third compressors.
この発明は上記の様な問題点を解消する為になされたも
ので，互いに並列に接続された圧縮機の並列運転時、或
は任意の圧縮機の単独運転時のいずれの場合でも圧縮機
の油面が適正に維持できる並列圧縮式冷凍装置を得るこ
とを目的とする。This invention was made to solve the above-mentioned problems, and the compressor can be operated in parallel with each other, or when any compressor is operated independently. The objective is to obtain a parallel compression type refrigeration system that can maintain an appropriate oil level.
〔課題を解決するための手段ｌ
この発明に係る並列圧縮式冷凍装置は、吸入配管途中に
冷媒ガスと油に分離する手段を設け・、分離後の冷媒ガ
スの一部と油を第１の圧縮機に吸引させ、残りの冷媒を
第２の圧縮機並びに第３の圧縮機に吸引させると共に、
上記各圧縮機の油溜を均圧均油管により互いに連通し、
この均圧均油管中に上記第２、第３の圧縮機より第１の
圧縮機側へのガスの流れを塞圧する逆止弁を設けると共
に、第１，第２、第３の圧縮機の均圧均油管の接続口部
にオリフィスを設け、上記冷凍サイクルの吸入管の分岐
点から上記各圧縮機の吸入口までの吸入分岐管の圧力損
失を、（第１の圧縮機の吸入分岐管の圧損）仝（第２の
圧縮機の吸入分岐管の圧損）〜（第３の圧縮機の吸入分
岐管の圧損）にしたものである。[Means for Solving the Problems] The parallel compression type refrigeration system according to the present invention is provided with means for separating refrigerant gas and oil in the middle of the suction pipe, and a part of the refrigerant gas and oil after separation are separated into a first The remaining refrigerant is sucked into the second compressor and the third compressor, and
The oil reservoirs of each of the above compressors are communicated with each other by pressure equalizing oil pipes,
A check valve is provided in this pressure equalizing oil pipe to block the flow of gas from the second and third compressors to the first compressor side, and An orifice is provided at the connection port of the pressure equalizing oil pipe, and the pressure loss of the suction branch pipe from the branch point of the suction pipe of the refrigeration cycle to the suction port of each compressor is determined by (pressure loss in the suction branch pipe of the second compressor) to (pressure loss in the suction branch pipe of the third compressor).
この発明における均圧均油管は，逆止弁並びにオリフィ
スを介して連結され、ガスの逆流入を塞止すると共に、
オリフィスにより抵抗をつけ、必要以上の油の流入を防
止する。The pressure equalizing oil pipe in this invention is connected via a check valve and an orifice to block the backflow of gas, and
The orifice provides resistance and prevents more oil from flowing in than necessary.
以下、この発明の一実施例を図について説明する。第１
図において、＋１） ， １２＋ ， （３Ｊは第１，
第２，第３の半密閉形圧縮機、ｔ１ａ） ， Ｈａ）
， ｔａａ）はこの圧縮機（１１ ， ＋２１ ， （
３）のクランクケースで、この中には隔壁（ｘｂ） ，
（２ｂ） ， （３ｂ）により区画されたモータ室（
ｌｃ） ， （２ｃ） ． （３ｃ）と圧縮要素室＋
ｌｄ），（２ｄ）， （３ｄ）が形成されている。（１
６），（２ｅ），（３ｅ），（Ｉｆ），（２ｆ），（３
ｆ）は各々モータ室（Ｉｃ） ， （２ｃ） ， （３
ｃ）及び圧縮要素室（ｌｄ） ， （２ｄ） ， （３
ｄ）に収容されたモータ及び圧縮要素である。ｔｔｇ）
， （ｚｇ） ， （３ｇ）は両要素（１ｅ），（ｚ
６），（３ｅ）と（Ｉｆ） ， （２ｆ） ， （３ｆ
）とを接続するクランク軸、（ ｌｈ） ， （２ｈ）
， （３ｈ）は隔壁（ｌｂ），＋２ｂ），（３ｂ）の
上部に設けられた均圧用差圧弁で、起動時の様にモータ
室（ｌｃ） ， （２ｃ） ， （３ｃ）の圧力が圧縮
要素室（ｌｄ） ， （２ｄ） ， （３ｄ）の圧力よ
りも著し《低くなる様？時、閉となるものである。An embodiment of the present invention will be described below with reference to the drawings. 1st
In the figure, +1), 12+, (3J are the first,
Second and third semi-hermetic compressors, t1a), Ha)
, taa) is this compressor (11, +21, (
3), which includes the bulkhead (xb),
The motor room (2b) and (3b)
lc), (2c). (3c) and compression element chamber +
ld), (2d), and (3d) are formed. (1
6), (2e), (3e), (If), (2f), (3
f) are motor chambers (Ic), (2c), (3
c) and compression element chambers (ld), (2d), (3
d) the motor and compression element housed in. ttg)
, (zg), (3g) are both elements (1e), (z
6), (3e) and (If) , (2f) , (3f
), (lh), (2h)
, (3h) is a pressure equalizing differential pressure valve installed on the top of the partition wall (lb), +2b), (3b), and the pressure in the motor chamber (lc), (2c), (3c) is compressed like at startup. It seems to be significantly lower than the pressure in the element chambers (ld), (2d), and (3d)? It closes at the time.
（ｉｉ） ， （ｚｉ）， （３ｉ）は隔壁（ｌｂ）
， （２ｂ） ， （３ｂ）の下部に設けた均油用逆止
弁で，モータ窒１１ｃ） ， （２Ｃ），（３ｃ）底部
の油溜（ｌｊ） ， （２ｊ） ， （３ｊ）から圧縮
要素室（ｌｄ） ， （２ｄ） ， （３ｄ）底部の油
溜（ｌｋ） ， （２ｋ） ， （３ｋ）へのみ油の流
入を許容するものである。(ii) , (zi), (3i) are bulkheads (lb)
, (2b), (3b) are installed at the bottom of the motor nitrogen 11c), (2C), (3c) to compress the oil from the oil sump (lj), (2j), (3j) at the bottom. This allows oil to flow only into the oil reservoirs (lk), (2k), and (3k) at the bottom of the element chambers (ld), (2d), and (3d).
（４）は各圧縮機（１） ， ＋２１ ， （３）の圧
縮要素室（ｌｄ），（２ｄ），（３ｄ）を連通ずる均圧
均油管、（５）はこの均圧均油管（４》に設けられ、第
２の圧縮機《２》の圧縮要素室（２ｄ）より第１の圧縮
機（１）の圧縮要素室（１ｄ）及び第３の圧縮機（３》
の圧縮要素室（３ｄ）より第１の圧縮機（１）の圧縮要
素室（ｌｄ）へのガスの流れを塞止する逆比弁で、（６
》は上記均圧均油管（４》と各圧縮機（１） ， ＋２
１ ， ＋３１の接続口部に設けられたオリフィスであ
る。（７》は蒸発器（図示せず）に接続された冷凍サイ
クルの吸入管、（９）はこの吸入管の途中より第２の圧
縮機（２）のモータ室（２ｃ）とを接続する第２の圧縮
機（２》の吸入分岐管． Ｃｌ■は吸入管（７）の途中
より第３の圧縮機（３》のモータ室（３ｃ）とを接続す
る第３の圧縮機（３）の吸入分岐管で、第２の吸入分岐
管（９》は第３の吸入分岐管ＣＩＧより太い径となって
いる。ａ優は各圧縮機（ｔ） ， （２１ ， （３）
の共通吐出管で、凝縮器、膨張弁（図示せず）を介して
蒸発器（図示せず）に接続されている。(4) is a pressure equalizing oil pipe that communicates the compression element chambers (ld), (2d), and (3d) of each compressor (1), +21, and (3), and (5) is this pressure equalizing oil pipe (4). The compression element chamber (1d) of the first compressor (1) and the third compressor (3) are provided in the compression element chamber (2d) of the second compressor (2).
(6) is an inverse ratio valve that blocks the flow of gas from the compression element chamber (3d) of
>> is the pressure equalizing oil pipe (4) and each compressor (1), +2
This is an orifice provided at the connection port of 1 and +31. (7) is the suction pipe of the refrigeration cycle connected to the evaporator (not shown), and (9) is the suction pipe that connects the motor chamber (2c) of the second compressor (2) from the middle of this suction pipe. Suction branch pipe of compressor 2 (2》). Cl■ connects the motor chamber (3c) of the third compressor (3》) from the middle of the suction pipe (7). Among the suction branch pipes, the second suction branch pipe (9) has a larger diameter than the third suction branch pipe CIG.
A common discharge pipe connects the condenser and the evaporator (not shown) via an expansion valve (not shown).
次に動作について説明する。各圧縮機＋１） ， ＋２
１ ，（３》が運転されている時は、通常、冷媒循環量
の０．５％程度含まれた油は冷媒サイクルの吸入管（７
）内を蒸発した冷媒ガスと共に圧縮機（１） ， （２
１ ， （３）側へ戻って《る。この時、この油の大部
分は重力の影響で第１の圧縮機《１》の吸入管（７）へ
流入し、第１の圧縮機（１）のモータ室《１ｃ）均油逆
止弁（ｌｉ）を通り、圧縮要素室（１ｄ）へ供給される
。第２、第３の吸入分岐管（９） ， ＱＱは吸入管（
７》より細い径となっている為，吸入管（７）及び吸入
分岐管（’ｌ） ， （１０における冷媒の圧力損失は
第２及び第３の吸入分岐管（９） ， ＱＧの方が大き
くな・る。従って各モータ室（ＩＣ） ， ＋２Ｃ）
， （３Ｃ）と各圧縮要素室（ｌｄ） ， （２ｄ）
， （３ｄ）の圧力の関係は、第３の圧縮機（３》の圧
縮要素室（３ｄ）の圧力句第２の圧縮機《２》の圧縮要
素室（２ｄ）の圧力〈第１の圧縮機（１）の圧縮要素室
（１ｄ）の圧力≦第１の圧縮機（１）のモータ室（１ｃ
）の圧力となり、油は第１の圧縮機（１）の圧縮要素室
（１ｄ）から均圧均油管（４）及び、逆圧弁（５）を通
り第２の圧縮機（２）の圧縮要素室（２ｄ）並びに第３
の圧縮機（３》の圧縮要素室（３ｄ）へ供給され正常に
潤滑機能を果たすことができる。Next, the operation will be explained. Each compressor +1), +2
1, (3) is in operation, oil containing about 0.5% of the refrigerant circulation amount is normally pumped into the suction pipe (7) of the refrigerant cycle.
) together with the evaporated refrigerant gas in the compressors (1), (2
1. Return to the (3) side. At this time, most of this oil flows into the suction pipe (7) of the first compressor (1) due to the influence of gravity, and the oil equalizes the check valve in the motor room (1c) of the first compressor (1). (li) and is supplied to the compression element chamber (1d). 2nd and 3rd suction branch pipes (9), QQ is suction pipe (
7》Since the diameter is smaller, the pressure loss of the refrigerant in the suction pipe (7) and the suction branch pipes ('l), (10) is smaller in the second and third suction branch pipes (9), QG. Therefore, each motor chamber (IC), +2C)
, (3C) and each compression element chamber (ld), (2d)
, (3d) is the pressure of the compression element chamber (3d) of the third compressor (3), the pressure of the compression element chamber (2d) of the second compressor (2), Pressure in the compression element chamber (1d) of the compressor (1)≦motor chamber (1c) of the first compressor (1)
), and the oil passes from the compression element chamber (1d) of the first compressor (1) through the pressure equalization pipe (4) and the counter pressure valve (5) to the compression element of the second compressor (2). Chamber (2d) and 3rd
The lubricant is supplied to the compression element chamber (3d) of the compressor (3) and can perform its lubrication function normally.
次に、第１の圧縮機（１）だけが運転する場合、吸入管
（７）より冷媒ガスは第１の圧縮機《１）のモータ室《
１ｃ）へ流入する。この間の配管の圧力損失により，圧
力低下する。また、圧縮要素室（１ｄ）の圧力も均圧差
圧弁（１ｈ）の作用で低下する。一方，油もガスと同様
にして第１の圧縮機（１）の圧縮要素室（ｌｄ）へ流入
する。このとき各モータ室（ｌｃ） ， （２ｃ） ，
（３ｃ）と各圧縮要素室（ｌｄ）， （２ｄ） ，
（３ｄ）の圧力の関係は、第１の圧縮機《１）の圧縮要
素室（１ｄ）の圧力≦第１の圧縮機（１）のモータ室（
１ｃ）の圧力く第３の圧縮機（３）の圧縮要素室（３ｄ
）の圧力勺第２の圧縮機（２）の圧縮要素室（２ｄ）の
圧力となる。この時均圧均油管（４）に逆圧弁（５冫が
無い場合、上記圧力差により停止中の第２の圧縮機（２
）と第３の圧縮機（３》に溜った油が均圧均油管（４》
を介して第１の圧縮機（１）の圧縮要素室ｕｄ）へ供給
され、油上り量過大による能力低下等の問題が発生する
可能性があったが、この発明では低い圧力で作用する逆
止弁（５》を均圧均油管《４｝に設けている為、第２、
第３の圧縮機＋２１ ， （３）から第１の圧縮機（１
）へのガスの流入が阻止され、正常運転を行うことが可
能となる。Next, when only the first compressor (1) is operated, the refrigerant gas is pumped from the suction pipe (7) to the motor room of the first compressor (1).
1c). During this time, the pressure drops due to pressure loss in the piping. Further, the pressure in the compression element chamber (1d) is also reduced by the action of the equalizing pressure differential valve (1h). On the other hand, oil also flows into the compression element chamber (ld) of the first compressor (1) in the same manner as gas. At this time, each motor chamber (lc), (2c),
(3c) and each compression element chamber (ld), (2d),
The pressure relationship (3d) is that the pressure in the compression element chamber (1d) of the first compressor (1)≦the motor chamber (1) of the first compressor (1)
1c) and the compression element chamber (3d) of the third compressor (3).
) becomes the pressure in the compression element chamber (2d) of the second compressor (2). At this time, if there is no back pressure valve (5 valve) in the pressure equalization oil pipe (4), the second compressor (2
) and the third compressor (3) are transferred to the pressure equalizing oil pipe (4).
The oil is supplied to the compression element chamber (ud) of the first compressor (1) through Since the stop valve (5) is installed on the pressure equalizing oil pipe (4), the second,
from the third compressor +21, (3) to the first compressor (1
), and normal operation is possible.
次に，第２の圧縮機（２》の１台運転及び第１の圧縮機
（１）と第２の圧縮機《２》の２台運転を行う場合、各
モータ室（ｌｃ） ， （２ｃ） ， （３ｃ）と各圧
縮要素室（ｌｄ），（２ｄ），（３ｄ）の圧力の関係は
、第２の圧縮機（２）の圧縮要素室（２ｄ）の圧力〈第
１の圧縮機（１）の圧縮要素室（１ｄ）の圧力≦第１の
圧縮機（１）のモータ室（１ｃ）の圧力≦第３の圧縮機
《３》の圧縮要素室（３ｄ）の圧力となり、第１の圧縮
機＋１１のモータ室（ＩＣ）へ戻った油は圧力差により
第１の圧縮機（１）の圧縮要素室（１ｄ）を介し、均圧
均油管（４》、逆止弁（５》を通り第２の圧縮機《２》
の圧縮要素室（２ｄ）へ供給される。又、第３の圧縮機
１３１に溜った油の第１の圧縮機（１）への流入は均圧
均油管（４》に設けられた逆止弁（５月とよって阻止さ
れるので、正常な油而維持及び、運転を行うことができ
る。Next, when operating one unit of the second compressor (2) and operating two units of the first compressor (1) and the second compressor (2), each motor room (lc), (2c ), (3c) and the pressure in each compression element chamber (ld), (2d), (3d) is the pressure in the compression element chamber (2d) of the second compressor (2) <the pressure in the compression element chamber (2d) in the first compressor The pressure in the compression element chamber (1d) of (1)≦the pressure in the motor chamber (1c) of the first compressor (1)≦the pressure in the compression element chamber (3d) of the third compressor (3), and Due to the pressure difference, the oil returned to the motor chamber (IC) of the compressor 1 and motor chamber 11 passes through the compression element chamber (1d) of the first compressor (1), and then passes through the pressure equalizing oil pipe (4) and the check valve (5). 》 to the second compressor《2》
is supplied to the compression element chamber (2d). In addition, the oil accumulated in the third compressor 131 is prevented from flowing into the first compressor (1) by the check valve (5) installed in the pressure equalizing oil pipe (4), so that it is not normal. Able to maintain and operate properly.
次に，第３の圧縮機（３）の１台運転及び第１の圧縮機
《１》と第３の圧縮機（３》の２台運転の場合，各モー
タ室（ｌｃ） ， ＋２ｃ） ， （３ｃ）と各圧縮要
素室ｔｔａ），（ｚｄ），（３ｄ）の圧力の関係は，第
３の圧縮機（３）の圧縮要素室（３ｄ）の圧力〈第１の
圧縮機＋１）の圧縮要素室（ｌｄ）の圧力≦第１の圧縮
機（１）のモータ室（１ｃ）の圧力≦第２の圧縮機《２
》の圧縮要素室（２ｄ）の圧力となり、第１の圧縮機＋
１）のモータ室（１ｃ）へ戻った油は圧力差により第１
の圧縮機（１）の圧縮要素室（１ｄ）を介し、均圧均油
管（４）．逆止弁（５）を通り第３の圧縮機（３》の圧
縮要素室（３ｄ）へ供給される。又，停止中の第２の圧
縮機（２》に溜った油は均圧均油管（４）に設けられた
逆止弁（５）の作用により、第１の圧縮機（１）への流
通は阻止されるので正常な油面維持及び、運転を行うこ
とができる。Next, in the case of operation of one third compressor (3) and operation of two units of the first compressor <<1>> and the third compressor (3>>), each motor room (lc), +2c), The relationship between (3c) and the pressure in each compression element chamber tta), (zd), (3d) is the pressure in the compression element chamber (3d) of the third compressor (3) (first compressor + 1). Pressure in the compression element chamber (ld)≦Pressure in the motor chamber (1c) of the first compressor (1)≦Second compressor《2
>> pressure in the compression element chamber (2d), and the pressure in the first compressor +
The oil returned to the motor chamber (1c) in 1) is
through the compression element chamber (1d) of the compressor (1) of the pressure equalizing oil pipe (4). The oil is supplied to the compression element chamber (3d) of the third compressor (3) through the check valve (5).Also, oil accumulated in the stopped second compressor (2) is passed through the pressure equalization pipe. By the action of the check valve (5) provided in (4), the flow to the first compressor (1) is blocked, so that normal oil level can be maintained and operation can be performed.
又、第２の圧縮機｛２｝と第３の圧縮機（３）の２台運
転を行う場合、各モータ室（ＩＣ） ， ｔｚｃ） ，
（３Ｃ）と各圧縮要素室（ｘｄ） ， （ｚｄ） ．
（３ｄ）の圧力の関係は、第１の圧縮機（１）と第２
の圧縮機《２》と第３の圧縮機（３》の３台運転の場合
と同じ関係となるので正常運転が行える。In addition, when operating two compressors, the second compressor {2} and the third compressor (3), each motor chamber (IC), tzc),
(3C) and each compression element chamber (xd), (zd).
The pressure relationship (3d) is between the first compressor (1) and the second compressor (1).
Since the relationship is the same as when three compressors (2) and 3 (3) are operated, normal operation can be performed.
又、各圧縮機＋１１ ， ＋２１ ， （３１が運転さ
れている場合、例えば第１の圧縮機（１）がフオーミン
グを起こした場合、必要以上の油が第２の圧縮機《２》
もし《は第３の圧縮機（３）へ流出してしまっていたが
、各圧縮機（１１ ， ＋２１ ， ＋３）の均圧均油
管取付口に設けられたオリフィス（６》により流出する
油に抵抗をつけ、第２の圧縮機《２》もし《は第３の圧
縮機（３冫への必要以上の油の流入を阻止する。よって
、常に油面を正常に維持して、安定した運転を行うこと
ができ層。In addition, when the compressors +11, +21, (31) are in operation, for example, if the first compressor (1) has formed, more oil than necessary will flow into the second compressor (2).
If the oil had leaked to the third compressor (3), the orifice (6) provided at the pressure equalization pipe installation port of each compressor (11, +21, +3) would prevent the oil from flowing out. By adding resistance, the second compressor (2) prevents more oil from flowing into the third compressor (3) than necessary.Therefore, the oil level is always maintained at a normal level and stable operation is achieved. You can do the layers.
従ってこの方式によれば合計７段階の容量制御が可能と
なり、負可変動の多い食品店舗のオーブンショーケース
等の冷却用冷凍機として使用した場合、負荷変動に対応
して冷凍機の能力をコントロールし、常に設計条件に近
い蒸発温度で運転可能となりエネルギー利用効率が大幅
に改善される。Therefore, this system enables a total of 7 levels of capacity control, and when used as a refrigerator for cooling oven showcases in food stores where there are many negative fluctuations, the capacity of the refrigerator can be controlled in response to load fluctuations. However, it can always be operated at an evaporation temperature close to the design conditions, greatly improving energy usage efficiency.
この考案は、クランクケース内をモータ室側と圧縮要素
室側とに区画する隔壁の所定位置に、均圧用差圧弁及び
上記モータ室側から、圧縮要素室側へのみ油の流通を許
容する均油逆上弁を有する第１、第２、第３のそれぞれ
容量の異なる圧縮機を互いに並列Ｃこ配管接続したもの
Ｃこおいて、吸入配管途中に冷媒ガスと油ｆこ分離する
手段を設け、分離後の冷媒ガスの一部と油を第１の圧縮
機に吸引させ、残りの冷媒ガスを第２及び第３の圧縮機
に吸引させると共に、上記各圧縮機の油溜を均圧均油管
により互いに連通し、この均圧均油管中に上記第２、第
３の両圧縮機より第１の圧縮機側へのガスの流れを塞止
する逆止弁を設け，かつ第１、第２、第３の各圧縮機の
均圧均油管接続口に、それぞれオリフィスを設け、上記
冷凍サイクルの吸入管の分岐点から上記各圧縮機の吸入
口までの吸入分岐管の圧力損失が、（第１の圧縮機の吸
入分岐管の圧損）≦（第２の圧縮機の吸入分岐管の圧損
）Ｌｒ（第３の圧縮機の吸入分岐管の圧損）となるよう
に構成したことにより、一つの圧縮機に対して積極的に
冷凍サイクル中の油を戻しながら、各圧縮機による全運
転、及び何れかの圧縮機による部分運転と全ての運転条
件において各圧縮機の油面を適正に維持することが可能
であり、従来のように摺動部の焼付、油上り量過大によ
る冷凍能力の低下、弁部分損傷を防止することができる
。This idea includes a pressure equalizing differential pressure valve installed at a predetermined position on the partition wall that divides the inside of the crankcase into the motor chamber side and the compression element chamber side. First, second, and third compressors each having a different capacity and each having an oil reverse valve are connected in parallel with each other in piping, and a means for separating refrigerant gas and oil is provided in the middle of the suction piping. , part of the separated refrigerant gas and oil are sucked into the first compressor, the remaining refrigerant gas is sucked into the second and third compressors, and the oil reservoirs of each of the compressors are pressure-equalized. A check valve is provided in the pressure equalizing oil pipe to block the flow of gas from the second and third compressors to the first compressor side, and the first and third compressors are connected to each other by an oil pipe. An orifice is provided at the pressure equalization oil pipe connection port of each of the second and third compressors, and the pressure loss of the suction branch pipe from the branch point of the suction pipe of the refrigeration cycle to the suction port of each of the compressors is ( By configuring such that (pressure loss in the suction branch pipe of the first compressor) ≦ (pressure loss in the suction branch pipe of the second compressor) Lr (pressure loss in the suction branch pipe of the third compressor), While actively returning oil in the refrigeration cycle to each compressor, the oil level in each compressor is maintained at an appropriate level under all operating conditions, including full operation of each compressor and partial operation of either compressor. This makes it possible to prevent seizure of sliding parts, reduction in refrigeration capacity due to excessive oil flow, and damage to valve parts, as in the past.
第１図はこの発明の一実施例を示す並列圧縮式冷凍装置
の構成図、第２図は従来の並列圧縮式冷凍装置を示す構
成図である。
図において、＋１１ ， ＋２１ ， （３）は第１１
第２、第３の半密閉形圧縮機、［ＩＣ） ， （２Ｃ）
， （３Ｃ）はモータ室、＋１ａ） ， ＋２ｄ）
， 《３ｄ）は圧縮要素室、（ｌｈ），（２ｈ），（３
ｈ）は均圧用差圧弁、（ｌｉ），（２ｉ），（３ｉ）は
均油用逆止弁、（４）は均圧均油管、（５）は逆止弁、
（６》はオリフィス、（７）は吸入管、（９） ， Ｑ
Ｏは第２％第３の吸入分岐管である。
な８、図中、同一符号は同一、又は相当部分を示す。FIG. 1 is a block diagram of a parallel compression type refrigeration system showing one embodiment of the present invention, and FIG. 2 is a block diagram showing a conventional parallel compression type refrigeration system. In the figure, +11, +21, (3) are the 11th
Second and third semi-hermetic compressors, [IC], (2C)
, (3C) is the motor room, +1a), +2d)
, 《3d) is the compression element chamber, (lh), (2h), (3
h) is a pressure equalizing differential pressure valve, (li), (2i), (3i) are oil equalizing check valves, (4) is a pressure equalizing oil pipe, (5) is a check valve,
(6) is the orifice, (7) is the suction pipe, (9), Q
O is the 2nd % third suction branch pipe. 8. In the figures, the same reference numerals indicate the same or equivalent parts.
Claims (1)
する隔壁の所定位置に、均圧用差圧弁及び上記モータ室
側から、圧縮要素室側へのみ油の流通を許容する均油逆
上弁を有する第１、第２、第３のそれぞれ容量の異なる
圧縮機を互いに並列に配管接続したものにおいて、吸入
配管途中に冷媒ガスと油に分離する手段を設け、分離後
の冷媒ガスの一部と油を第１の圧縮機に吸引させ、残り
の冷媒ガスを第２及び第３の圧縮機に吸引させると共に
、上記各圧縮機の油溜を均圧油管により互いに連通し、
この均圧均油管中に上記第２、第３の両圧縮機より第１
の圧縮機側へのガスの流れを塞止する均止弁を設け、か
つ第１、第２、第３の各圧縮機の均圧均油管接続口に、
それぞれオリフィスを設け、上記冷凍サイクルの吸入管
の分岐点から上記各圧縮機の吸入口までの吸入分岐管の
圧力損失を、（第１の圧縮機の吸入吸入分岐管の圧損）
≦（第２の圧縮機の吸入分岐管の圧損）≒（第３の圧縮
機の吸入分岐管の圧損）にしたことを特徴とする並列圧
縮式冷凍装置。A pressure equalizing differential pressure valve and an oil equalizing reverse valve that allow oil to flow only from the motor chamber side to the compression element chamber side are installed at predetermined positions on the partition wall that divides the inside of the crankcase into the motor chamber side and the compression element chamber side. A first, second, and third compressor having different capacities are connected in parallel with each other by piping, and a means for separating refrigerant gas and oil is provided in the middle of the suction piping, and a part of the refrigerant gas after separation is and oil to the first compressor, and the remaining refrigerant gas to the second and third compressors, and the oil reservoirs of the respective compressors are communicated with each other by pressure equalizing oil pipes,
In this pressure equalizing oil pipe, the first compressor is connected to the second and third compressors.
Provided with an equalizing valve for blocking the flow of gas to the compressor side, and at the pressure equalizing oil pipe connection port of each of the first, second, and third compressors,
Each has an orifice, and the pressure loss of the suction branch pipe from the branch point of the suction pipe of the refrigeration cycle to the suction port of each compressor is calculated as follows: (Pressure loss of the suction suction branch pipe of the first compressor)
≦(Pressure loss in the suction branch pipe of the second compressor)≒(Pressure loss in the suction branch pipe of the third compressor).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5222889A JPH02230985A (en) | 1989-03-03 | 1989-03-03 | Parallel compression type refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5222889A JPH02230985A (en) | 1989-03-03 | 1989-03-03 | Parallel compression type refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02230985A true JPH02230985A (en) | 1990-09-13 |
Family
ID=12908880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5222889A Pending JPH02230985A (en) | 1989-03-03 | 1989-03-03 | Parallel compression type refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02230985A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04214983A (en) * | 1990-12-13 | 1992-08-05 | Daikin Ind Ltd | Connected compression device |
| JPH04287880A (en) * | 1991-03-18 | 1992-10-13 | Daikin Ind Ltd | Connected compression device |
| JPH04287882A (en) * | 1991-03-18 | 1992-10-13 | Daikin Ind Ltd | Connected type compression device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60142071A (en) * | 1983-12-28 | 1985-07-27 | Mitsubishi Electric Corp | Parallel compressive type refrigerating plant |
| JPS6334451A (en) * | 1986-07-28 | 1988-02-15 | 株式会社日立製作所 | multi-refrigeration machine |
-
1989
- 1989-03-03 JP JP5222889A patent/JPH02230985A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60142071A (en) * | 1983-12-28 | 1985-07-27 | Mitsubishi Electric Corp | Parallel compressive type refrigerating plant |
| JPS6334451A (en) * | 1986-07-28 | 1988-02-15 | 株式会社日立製作所 | multi-refrigeration machine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04214983A (en) * | 1990-12-13 | 1992-08-05 | Daikin Ind Ltd | Connected compression device |
| JPH04287880A (en) * | 1991-03-18 | 1992-10-13 | Daikin Ind Ltd | Connected compression device |
| JPH04287882A (en) * | 1991-03-18 | 1992-10-13 | Daikin Ind Ltd | Connected type compression device |
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