JPH0128233B2 - - Google Patents
Info
- Publication number
- JPH0128233B2 JPH0128233B2 JP56019848A JP1984881A JPH0128233B2 JP H0128233 B2 JPH0128233 B2 JP H0128233B2 JP 56019848 A JP56019848 A JP 56019848A JP 1984881 A JP1984881 A JP 1984881A JP H0128233 B2 JPH0128233 B2 JP H0128233B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- rotor
- suction
- casing
- end wall
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000011295 pitch Substances 0.000 claims description 13
- 239000003507 refrigerant Substances 0.000 claims description 11
- 239000012530 fluid Substances 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 140
- 238000002347 injection Methods 0.000 description 11
- 239000007924 injection Substances 0.000 description 11
- 238000007789 sealing Methods 0.000 description 10
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 238000003756 stirring Methods 0.000 description 8
- 238000005461 lubrication Methods 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000008016 vaporization Effects 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
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は、互に噛み合う１対のスクリユーロー
タをロータ室の内で回転せしめて冷媒を圧縮する
スクリユー圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a screw compressor that compresses refrigerant by rotating a pair of screw rotors that mesh with each other within a rotor chamber.
「従来の技術と発明が解決しようとする課題」
従来例としては特公昭50−17686号公報に示さ
れるスクリユー圧縮機がある。従来この種のスク
リユー圧縮機において、ロータ作用空間に液体噴
射を行なう型式のものでは、雄、雌ロータ及び軸
受への給油は吐出配管中の油分離器で分離した油
を油冷却器にて40〜50℃前後に冷却して、最低高
低圧差を利用して給油するか、又は油ポンプを使
つて強制給油する方法が行なわれている。従つて
油は吐出圧〜吐出圧＋２〜３Kg／cm2の圧力にて軸
受に給油される。吸込側軸受を潤滑冷却し、60℃
前後の温度に上昇する。又吐出側においては圧縮
熱の影響を受けてさらに高い温度となる。これら
の油を総て通路を介して、吸入側又は吸込口とじ
込み前後のロータ作用空間に戻し、ロータの潤
滑、及びロータ作用空間のシール並びに圧縮機の
吸収用に供されて、作用流体といつしよに圧縮機
より吐出され、油分離器で分離回収し再循環利用
される。"Prior Art and Problems to be Solved by the Invention" A conventional example is a screw compressor shown in Japanese Patent Publication No. 17686/1986. Conventionally, in this type of screw compressor, in the type that injects liquid into the rotor working space, the male and female rotors and bearings are lubricated using oil separated by an oil separator in the discharge piping, and then separated by an oil cooler. The method used is to cool it to around 50°C and supply oil using the difference between the lowest pressure and the lowest pressure, or to forcefully supply oil using an oil pump. Therefore, oil is supplied to the bearing at a pressure of from discharge pressure to discharge pressure + 2 to 3 kg/cm 2 . The suction side bearing is lubricated and cooled to 60℃.
The temperature rises to around. Furthermore, on the discharge side, the temperature becomes even higher due to the influence of compression heat. All these oils are returned to the rotor working space on the suction side or before and after the suction port through the passages, and are used for rotor lubrication, sealing of the rotor working space, and absorption of the compressor, and are used to keep the working fluid and The oil is then discharged from the compressor, separated and recovered by an oil separator, and recycled.
このようにロータ作用空間には、吐出側軸受を
潤滑冷却した高温で粘性の低下した油を供給した
為、ロータの潤滑、及びロータ作用空間のシー
ル、並びに圧縮熱の除去は充分とはいえず、圧縮
機の信頼性及び効率は高いものとは言えなかつ
た。特に吐出側軸受を潤滑した高温の油を吸込口
とじ込み位置のロータ作用空間に送つている場合
には低温冷媒を加熱して膨張させロータ溝内圧力
上昇の為圧縮機に必要とする動力を増大させる欠
点がある。 In this way, the rotor working space was supplied with high-temperature, low-viscosity oil that had lubricated and cooled the discharge side bearing, so it was not sufficient to lubricate the rotor, seal the rotor working space, and remove compression heat. However, the reliability and efficiency of the compressor could not be said to be high. In particular, when high-temperature oil that lubricates the discharge side bearing is sent to the rotor working space at the suction port closing position, the low-temperature refrigerant is heated and expanded, increasing the pressure in the rotor groove and increasing the power required by the compressor. There are drawbacks to doing so.
さらに冷凍機用として用いられる圧縮機におい
ては負荷及び冷凍機の凝縮器に供給される冷却水
入口温度条件により吐出圧力が変化する為圧縮機
の吸入圧力と吐出圧力が大きく変化し軸受前後に
作用する圧力差もかなり変化する。この圧力差が
高い時に油が適量以上流れ、ロータ作用空間に余
分に供給されてしまう。この為、油撹拌動力が増
加し、圧縮機の効率を低下させていた。 Furthermore, in compressors used for refrigerators, the discharge pressure changes depending on the load and the temperature conditions at the inlet of the cooling water supplied to the condenser of the refrigerator, so the suction pressure and discharge pressure of the compressor change greatly, which affects the front and rear of the bearing. The pressure difference also varies considerably. When this pressure difference is high, more than the appropriate amount of oil flows, and an excess amount is supplied to the rotor working space. For this reason, the power for stirring the oil increases, reducing the efficiency of the compressor.
本発明の目的はスクリユー圧縮機のロータ作用
空間へ送る油とロータ作用空間における冷媒の温
度差を可及的少なくすることにより、上記欠点を
完全に除去できないまでも極めて小さくして、圧
縮機の信頼性及び効率を改善することである。 The purpose of the present invention is to minimize the temperature difference between the oil sent to the rotor working space of a screw compressor and the refrigerant in the rotor working space. The goal is to improve reliability and efficiency.
「課題を解決するための手段」
本発明はケーシング内に平行に、かつ軸間距離
がその直径よりも小なる如く互に重なり合つて設
けられた二個の円筒状ボアの中に、それぞれ前記
ボア軸を中心に回転可能に支えられて互に噛み合
う雄ロータと雌ロータとを備え、前記ケーシング
には前記ボアの両端に前記ボア軸に直角な吸入側
端壁及び吐出側端壁を備え、該吸入側端壁及び吐
出側端壁にはそれぞれ端壁吸込口及び端壁吐出
口、さらに前記雄、雌ロータを支承する軸受を吸
込側と吐出側に備え、容量制御を行なうスライド
バルブを有し、作動流体を冷媒とし、圧縮機の外
部より冷却された油を吸込口完全とじ込み位置の
ロータ作用空間にスライドバルブを介して供給す
る油路を備えたスクリユー圧縮機において、圧縮
機の外部より冷却された油を各軸受に供給する油
路と、吐出側に設けた軸受に給油した油を吐出側
の通路に送る油路と、吸込側に設けた軸受及びバ
ランスピストンに送つた油を吸込口とじ込み縁よ
り２ピツチ位置又は該位置直後の吐出側のロータ
作用空間に送る油路を設けたことを特徴とするス
クリユー圧縮機である。``Means for Solving the Problems'' The present invention provides two cylindrical bores provided in a casing parallel to each other and overlapping each other such that the distance between the axes is smaller than the diameter thereof. A male rotor and a female rotor are rotatably supported around a bore axis and mesh with each other, and the casing has a suction side end wall and a discharge side end wall perpendicular to the bore axis at both ends of the bore, The suction side end wall and the discharge side end wall each include an end wall suction port and an end wall discharge port, and bearings for supporting the male and female rotors on the suction side and the discharge side, respectively, and a slide valve for controlling the capacity. In a screw compressor, the working fluid is a refrigerant, and the screw compressor is equipped with an oil passage that supplies cooled oil from the outside of the compressor to the rotor working space at the suction port completely closed position via a slide valve. An oil passage that supplies cooled oil to each bearing, an oil passage that sends oil supplied to the bearings installed on the discharge side to the passage on the discharge side, and an oil passage that sends oil sent to the bearings and balance piston installed on the suction side. This is a screw compressor characterized in that an oil passage is provided for sending oil to the rotor working space on the discharge side at a position two pitches from the mouth closing edge or immediately after the position.
「作用」
圧縮機の運転状態において、外部より供給され
た冷たい油はスライドバルブを介して吸込口完全
とじ込み位置のロータ作用空間に供給される。又
圧縮機の外部より供給された油は吐出側軸受を冷
却して昇温し、吐出側の通路に送られ、高温とな
つた冷媒に混合して送り出される。更に又圧縮機
の外部より吸込側に設けた軸受及びバランスピス
トンに送つた油を吸込口とじ込み縁より２ピツチ
位置又は該位置直後の吐出側のロータ作用空間に
送られる。"Operation" When the compressor is in operation, cold oil supplied from the outside is supplied to the rotor working space at the suction port completely closed position via the slide valve. Also, the oil supplied from the outside of the compressor cools the discharge-side bearing, raises its temperature, is sent to the discharge-side passage, and is mixed with the high-temperature refrigerant and sent out. Furthermore, the oil sent from the outside of the compressor to the bearing and balance piston provided on the suction side is sent to the rotor working space at a position two pitches from the suction port closing edge or on the discharge side immediately after the position.
「実施例」
以下、本発明の実施例について図面に従つて説
明する。図面は何れもスクリユー圧縮機を示し、
第１図は従断面図、第２図は第１図のＡ−Ａ断面
図、第３図は第１図のＢ−Ｂ断面図である。"Embodiments" Examples of the present invention will be described below with reference to the drawings. The drawings all show screw compressors.
1 is a sub-sectional view, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIG. 3 is a sectional view taken along line BB in FIG. 1.
ロータケーシング１の両側は吸込側端壁及び吐
出側端壁をなしており、吸込ケーシング２、吐出
ケーシング３により密閉され、第３図に示すよう
な形状の雄ロータ４、雌ロータ５がかみ合つてお
り、両ロータはケーシング１の吐出し側の双円弧
形外周と接している。両ロータは図示矢印の方向
に回転するとき夫々同一リードでもつてかみ合う
位置が漸次移動するようになつており、外周にリ
ードの大きいねじ溝とねじ山を設けてかみ合う雄
ロータ４、雌ロータ５は一体となつた軸部４ａ，
４ｂ，５ａ，５ｂが夫々吸込ケーシング２に嵌入
したジヤーナル軸受６，７及び夫々吐出ケーシン
グ３に嵌入したジヤーナル軸受８，９によりラジ
アル方向荷重を支承され、吐出ケーシング３に嵌
入したスラスト玉軸受１２，１３の内輪に雄ロー
タ４の軸部４ａ、雌ロータ５の軸部５ａが嵌入し
て段部との間において夫々の軸部にねじ込まれた
ナツト１４，１５により軸方向移動を制止されて
いる。 Both sides of the rotor casing 1 form a suction side end wall and a discharge side end wall, which are sealed by a suction casing 2 and a discharge casing 3, and a male rotor 4 and a female rotor 5 having shapes as shown in FIG. 3 are engaged with each other. Both rotors are in contact with the bicircular arc-shaped outer periphery of the casing 1 on the discharge side. When both rotors rotate in the direction of the arrow shown in the figure, the positions where they engage each other gradually move even though they have the same lead.The male rotor 4 and female rotor 5, which engage with each other by providing thread grooves and threads with large leads on their outer peripheries, The integrated shaft portion 4a,
4b, 5a, 5b are supported in the radial direction by journal bearings 6, 7 fitted into the suction casing 2, respectively, and journal bearings 8, 9 fitted into the discharge casing 3, respectively, and thrust ball bearings 12, fitted into the discharge casing 3. The shaft portion 4a of the male rotor 4 and the shaft portion 5a of the female rotor 5 are fitted into the inner ring 13, and their axial movement is restrained between them and the stepped portion by nuts 14 and 15 screwed into the respective shaft portions. .
雄ロータ４の一体となつた軸部４ａは機外に突
出して軸端部４ｃとなつており、軸端部４ｃによ
り雄ロータ４が駆動されるようになつている。 An integral shaft portion 4a of the male rotor 4 projects outside the machine to form a shaft end portion 4c, and the male rotor 4 is driven by the shaft end portion 4c.
軸部４ａは吐出ケーシング３に固定されたカバ
ー１６に固定されたシールカバー１７中のメカニ
カルシールのような軸封装置１８により軸封され
ている。カバー１６には又軸部４ａのとおる部分
にシールリング１９が打込まれている。 The shaft portion 4a is sealed by a shaft sealing device 18 such as a mechanical seal in a seal cover 17 fixed to a cover 16 fixed to the discharge casing 3. A seal ring 19 is also driven into the cover 16 at a portion through which the shaft portion 4a passes.
吸込ケーシング２端はカバー２１により蔽われ
ている。 The two ends of the suction casing are covered by a cover 21.
吸込ケーシング２は上方に吸込通路２２が設け
てあり、雄ロータ４、雌ロータ５の間の上側端面
となる位置に吸込口２３が開口している。吸込口
２３の下方の雄ロータ４と雌ロータ５が相会する
位置の反対側の吐出ケーシング３の端面には吐出
口２４が設けてあり、吐出ケーシング３中の吐出
通路２５が機外に通じている。 A suction passage 22 is provided in the upper part of the suction casing 2, and a suction port 23 is opened at a position on the upper end surface between the male rotor 4 and the female rotor 5. A discharge port 24 is provided on the end surface of the discharge casing 3 opposite to the position below the suction port 23 where the male rotor 4 and the female rotor 5 meet, and a discharge passage 25 in the discharge casing 3 communicates with the outside of the machine. ing.
吸込ケーシング２にはシリンダ２６が嵌入され
カバー２７により押えられている。 A cylinder 26 is fitted into the suction casing 2 and is held down by a cover 27.
シリンダ２６内には密封輪２９によりシールさ
れたピストン２８が嵌入しており、ピストンロツ
ド３１が吸込ケーシング２の孔に嵌め込まれた密
封輪３３を通じてロータケーシング１内に延出さ
れ、吸込側容積を変化させて吸込量を調節するス
ライドバルブ３２に固定されている。 A piston 28 sealed by a sealing ring 29 is fitted into the cylinder 26, and a piston rod 31 is extended into the rotor casing 1 through a sealing ring 33 fitted into a hole in the suction casing 2 to change the suction side volume. It is fixed to a slide valve 32 that adjusts the suction amount by adjusting the suction amount.
シリンダ２６はカバー２１に固定されたカバー
２７により蔽われており、ピストンロツド３１は
カバー２７中の孔に挿入した密封輪３３′の部分
を挿通して外部に出ており、外部において該ピス
トンロツド３１の位置を検知されて吸込量を制御
される如くなつている。３４，３５はシリンダ２
６の圧油出入口である。 The cylinder 26 is covered by a cover 27 fixed to the cover 21, and the piston rod 31 passes through a sealing ring 33' inserted into a hole in the cover 27 and comes out to the outside. The position is detected and the amount of suction is controlled. 34 and 35 are cylinder 2
6 is the pressure oil inlet/outlet.
軸端部４ｃが第３図に矢印で示すように雄ロー
タ４を回転するとかみ合う雌ロータ５は雄ロータ
４と反対方向に同一速度で回転する。これらの回
転数は実例として同期速度が3000r.p.m位の電動
機により高速度で回転する。 When the shaft end 4c rotates the male rotor 4 as shown by the arrow in FIG. 3, the female rotor 5 that engages with the male rotor 4 rotates at the same speed in the opposite direction to the male rotor 4. These rotation speeds are rotated at high speed by an electric motor with a synchronous speed of about 3000 rpm, as an example.
雄ロータ４、雌ロータ５が回転すると図示され
ない配管より吸込通路２２をとおり吸込口２３よ
りロータケーシング１、雄ロータ４、雌ロータ５
により構成せられた吸込空気は気体は吸込まれ、
符号３６で示される部分よりは雄ロータ４、雌ロ
ータ５の夫々の外周はケーシング１の内周と密接
しており、それよりこれらのロータの１ピツチ吐
出側が吸込口完全とじ込み後のロータ作用空間と
なり、第１図、第２図において気体はロータ４，
５の回転により次第に雄ロータ４、雌ロータ５と
ケーシング１間のロータ溝空間の容積の減少によ
り圧縮され、吐出口２４にて吐出され吐出通路２
５より吐出側配管に送られる。 When the male rotor 4 and female rotor 5 rotate, they pass through the suction passage 22 from piping (not shown) and from the suction port 23 to the rotor casing 1, male rotor 4, and female rotor 5.
The suction air composed of
The outer peripheries of the male rotor 4 and female rotor 5 are in close contact with the inner periphery of the casing 1 than the part indicated by the reference numeral 36, and the one-pitch discharge side of these rotors is the rotor working space after the suction port is completely closed. Therefore, in Figs. 1 and 2, the gas is transferred to the rotor 4,
5, the rotor groove space between the male rotor 4, the female rotor 5, and the casing 1 is gradually compressed by decreasing its volume, and is discharged from the discharge port 24 into the discharge passage 2.
5 to the discharge side piping.
軸部４ｂ端には雄ロータ４と雌ロータ５の推力
のバランスをとるためのピストン３７が係止さ
れ、ピストン３７は吸込ケーシング２中に固定せ
られたシリンダ３８に滑入していてシリンダ室３
９が形成されている。 A piston 37 for balancing the thrust of the male rotor 4 and female rotor 5 is locked at the end of the shaft portion 4b, and the piston 37 slides into a cylinder 38 fixed in the suction casing 2 and is inserted into the cylinder chamber. 3
9 is formed.
次に冷却並びに潤滑油供給路についてのべる。
第２図に示すように図示されないポンプより送ら
れる圧油は吐出ケーシング３に設けた入口４１に
配管される。入口４１よりは吐出側のジヤーナル
軸受８への油路４２、ジヤーナル軸受６及びシリ
ンダ室３９への油路４３に分れる。 Next, let's talk about the cooling and lubricating oil supply channels.
As shown in FIG. 2, pressure oil sent from a pump (not shown) is piped to an inlet 41 provided in the discharge casing 3. The inlet 41 is divided into an oil path 42 to the journal bearing 8 on the discharge side, and an oil path 43 to the journal bearing 6 and the cylinder chamber 39.
油路４２はジヤーナル軸受８の外周の溝４５よ
り油路４６をとおり、ジヤーナル軸受９の外周の
溝４７につながる。第２図の一部拡大図の第２ａ
図に示すようにジヤーナル軸受８，９においては
外周の溝４５，４７より半径方向に貫通した孔４
５ａ，４７ａにより、夫々軸側の油溝４９，５１
につながる。 The oil passage 42 passes through an oil passage 46 from a groove 45 on the outer periphery of the journal bearing 8 and is connected to a groove 47 on the outer periphery of the journal bearing 9 . Part 2a of a partially enlarged view of Figure 2
As shown in the figure, in the journal bearings 8 and 9, holes 4 that penetrate in the radial direction from the grooves 45 and 47 on the outer periphery.
5a, 47a, oil grooves 49, 51 on the shaft side, respectively.
Leads to.
油溝４９，５１端は第２ａ図に示すように油溝
４９はオリフイス５２により、油溝５１はオリフ
イス５３により、各々ジヤーナル軸受８，９とス
ラスト玉軸受１２，１３間の空間につながり、該
スラスト玉軸受１２，１３の間を通じてカバー１
６内の空間５４に連通しており、空間５４よりは
第１図に示されるように吐出ケーシング３にあけ
た通路５５より吐出通路２５に続いている。 As shown in FIG. 2a, the ends of the oil grooves 49 and 51 are connected to the space between the journal bearings 8 and 9 and the thrust ball bearings 12 and 13 through an orifice 52 and an orifice 53, respectively. The cover 1 is inserted between the thrust ball bearings 12 and 13.
The space 54 is connected to the discharge passage 25 through a passage 55 bored in the discharge casing 3, as shown in FIG.
油路４３はロータケーシング１中を通じて吸込
ケーシング２に到り、吸込ケーシング２において
油路４３ａ，４３ｂに分岐してシリンダ室３９と
ジヤーナル軸受６の外周の溝５６につながり外周
の溝５６より吸込ケーシング中の油路５７により
ジヤーナル軸受７の外周の溝５８につながつてい
る。第２図の一部拡大図の第２ｂ図に示すように
ジヤーナル軸受６，７においては外周の溝５６，
５８より半径方向に貫通した孔５６ａ，５８ａに
より、夫々軸側の油溝５９，６１につながる。 The oil passage 43 reaches the suction casing 2 through the rotor casing 1, and branches into oil passages 43a and 43b in the suction casing 2, and connects to the cylinder chamber 39 and the groove 56 on the outer periphery of the journal bearing 6. It is connected to a groove 58 on the outer periphery of the journal bearing 7 through an oil passage 57 therein. As shown in FIG. 2b, which is a partially enlarged view of FIG.
Holes 56a and 58a penetrating radially from 58 connect to oil grooves 59 and 61 on the shaft side, respectively.
油溝５９，６１端は第２ｂ図に示すように油溝
５９はオリフイス６２、油溝６１はオリフイス６
３を通じて吸込ケーシング２の室６４，６５に
夫々通じており、室６４，６５間は通路６６によ
り連通している。 As shown in FIG. 2b, the ends of the oil grooves 59 and 61 have an orifice 62 in the oil groove 59 and an orifice 6 in the oil groove 61.
3 to the chambers 64 and 65 of the suction casing 2, respectively, and the chambers 64 and 65 are communicated through a passage 66.
室６５よりは油路６７が吸込ケーシング２より
ロータケーシング１に通じている。 From the chamber 65, an oil passage 67 communicates from the suction casing 2 to the rotor casing 1.
油路６７の端末は吸込側端壁の吸込口とじ込み
縁２３ａ（第４図）より２ピツチの位置又は該位
置の吐出側直後にロータケーシング１内に開口す
る油路６８として設けてある。 The end of the oil passage 67 is provided as an oil passage 68 that opens into the rotor casing 1 at a position two pitches from the suction port closing edge 23a (FIG. 4) of the suction side end wall, or immediately after the discharge side of the position.
第３図に示すようにロータケーシング１には入
口４１と同じ潤滑油源より配管が連結される油の
入口７１を備えた油路７１ａが設けてあり、油路
７１ａはスライドバルブ３２の表面に軸方向に刻
設した油溝７２に開口し、油溝７２は潤滑系統図
の第４図に示されるようにロータケーシング１の
軸方向の油溝７３と重なつて連通し、又、スライ
ドバルブ３２の移動により重なりがなくなり断絶
するようになつている。油溝７３はスライドバル
ブ３２の軸方向の短い油溝７４と重なつている。 As shown in FIG. 3, the rotor casing 1 is provided with an oil passage 71a having an oil inlet 71 connected to a pipe from the same lubricating oil source as the inlet 41, and the oil passage 71a is connected to the surface of the slide valve 32. It opens into an oil groove 72 carved in the axial direction, and the oil groove 72 overlaps and communicates with the oil groove 73 in the axial direction of the rotor casing 1, as shown in FIG. 4 of the lubrication system diagram. The movement of 32 eliminates the overlap and creates a disconnection. The oil groove 73 overlaps with a short oil groove 74 in the axial direction of the slide valve 32.
スライドバルブに設けた油溝７２よりはスライ
ドバルブ３２中を貫通して雄ロータ４、雌ロータ
５の吸込開始位置より、即ち、スライドバルブ３
２端よりロータの１ピツチ吐出側のロータ作用空
間に開口した噴射口７５が設けてあり、ロータケ
ーシングの油溝７３からはロータケーシング１に
吸込側端壁の吸込口とじ込み縁２３ａより１ピツ
チの位置に噴射口７６ａがあるように油路７６が
穿設してある。即ち吸込口とじ込み後のロータ作
用空間に給油を計つてある。 The oil groove 72 provided in the slide valve penetrates the inside of the slide valve 32 from the suction start position of the male rotor 4 and female rotor 5, that is, the slide valve 3.
An injection port 75 is provided that opens into the rotor action space on the discharge side of the rotor by one pitch from the two ends, and from the oil groove 73 of the rotor casing, a jet of one pitch from the suction port closing edge 23a of the suction side end wall is provided to the rotor casing 1. An oil passage 76 is bored so that an injection port 76a is located at the position. That is, oil is supplied to the rotor working space after the suction port is closed.
ロータ作用空間は、ロータ４，５の回転により
吐出側へ移動し、溝容積（ロータ作用空間）が減
少し、冷媒ガスの圧力・温度が上昇し、低圧部か
ら高圧部での適正の噴射油量は異なる。 The rotor working space moves toward the discharge side due to the rotation of the rotors 4 and 5, the groove volume (rotor working space) decreases, the pressure and temperature of the refrigerant gas rises, and the proper injection oil is adjusted from the low pressure part to the high pressure part. Amounts vary.
油量を増やすと、体積効率が向上するが、油の
撹拌動力が増加する。この為、本発明では、吸込
口とじ込み縁より２ピツチ迄の溝長さの長い圧力
の低い分には雄雌ロータ４，５の溝に吸込側軸受
６，７及びシリンダを経由した冷たい油を少量噴
射し、油の撹拌動作を抑える。但し油中の冷媒は
減圧により吸込側に洩れる際体積が30〜120倍と
なり洩れた場合損失は大きい。 Increasing the amount of oil improves the volumetric efficiency, but increases the power for stirring the oil. For this reason, in the present invention, cold oil is supplied to the grooves of the male and female rotors 4, 5 via the suction side bearings 6, 7 and the cylinder for low pressure areas with a long groove length up to 2 pitches from the suction port closing edge. A small amount is sprayed to suppress the oil stirring action. However, when the refrigerant in the oil leaks to the suction side due to depressurization, the volume increases by 30 to 120 times, resulting in a large loss if it leaks.
この為、ロータ作用空間の圧力の低い部分に
は、吸込口とじ込み後１ピツチ位置の噴射口７６
ａより直接冷えた油を少量噴射して、撹拌動力を
抑えながら溝空間の密封を最小限行つて体積効率
を向上させている。 For this reason, the injection port 76 at one pitch position after the suction port is closed in the low pressure area of the rotor working space.
A small amount of cooled oil is injected directly from A to improve volumetric efficiency by minimizing the sealing of the groove space while suppressing the stirring power.
スライドバルブ３２の噴射口７５（２ピツチ以
後の圧力の高い部分）からは歯形の洩れを防止す
る為又、撹拌動力増加より体積効率の向上が大き
い為油を追加噴射して油量を増やし体積効率の低
下を防止する。 In order to prevent tooth profile leakage from the injection port 75 (high pressure area after 2nd pitch) of the slide valve 32, additional oil is injected to increase the oil volume and volume, since the improvement in volumetric efficiency is greater than the increase in stirring power. Prevent loss of efficiency.
さらに圧力、温度の上昇する吸込口とじ込み縁
２３ａより２ピツチ位置又は該位置の吐出側直後
の油路６８より、吸込側軸受６，７を潤滑冷却し
た比較的温度の低い油を供給することにより、溝
前後の圧力差が増大したロータ作用空間の油量を
増して、体積効率を向上させている。 Furthermore, by supplying relatively low-temperature oil that lubricates and cools the suction side bearings 6 and 7 from the oil passage 68 at a position two pitches from the suction port closing edge 23a where the pressure and temperature rise or immediately after the discharge side of this position. The volumetric efficiency is improved by increasing the amount of oil in the rotor working space where the pressure difference before and after the grooves has increased.
尚、吐出側の軸受８，９に給油した温度の高い
油は冷媒ガスの過熱及び撹拌動力を抑える為吐出
通路２５に戻す。 Note that the high temperature oil supplied to the bearings 8 and 9 on the discharge side is returned to the discharge passage 25 in order to suppress overheating of the refrigerant gas and the stirring power.
以上説明したスクリユー圧縮機は冷凍機用とし
て用いられたもので油分離器で冷媒ガスを分離回
収された油は油冷却器で40℃〜50℃前後に冷却さ
れ、ポンプで加圧されて入口４１，７１より給油
される。入口４１よりは油路４２をとおつて溝４
５に入り、溝４５より孔４５ａをとおつて油溝４
９に入りジヤーナル軸受８の摺動面が冷却潤滑さ
れる。 The screw compressor described above was used for refrigerators, and the oil, after the refrigerant gas was separated and recovered in the oil separator, was cooled to around 40℃ to 50℃ in the oil cooler, and then pressurized by the pump to the inlet. Refueled from 41 and 71. From the inlet 41, the oil passage 42 is passed through the groove 4.
5 and enters the oil groove 4 through the hole 45a from the groove 45.
9, the sliding surface of the journal bearing 8 is cooled and lubricated.
一方溝４５より油路４６をとおり溝４７に入つ
た圧油は孔４７ａより油構５１に入りジヤーナル
軸受９の摺動面が、冷却潤滑される。 On the other hand, the pressure oil that enters the groove 47 from the groove 45 through the oil passage 46 enters the oil mechanism 51 through the hole 47a and cools and lubricates the sliding surface of the journal bearing 9.
油溝４９，５１の圧油はオリフイス５２，５３
で油量を調節されて夫々スラスト玉軸受１２，１
３を冷却、潤滑して空間５４、通路５５をとお
り、温度上昇し、粘度も低下して吐出通路２５に
入る。 Pressure oil in oil grooves 49, 51 is supplied to orifices 52, 53.
The oil amount is adjusted by the thrust ball bearings 12 and 1, respectively.
3 is cooled and lubricated, passes through a space 54 and a passage 55, and enters the discharge passage 25 with its temperature rising and its viscosity decreasing.
ロータケーシング１と吐出ケーシング３の接す
る吐出側端壁は圧縮熱の影響を受けて60〜90℃の
温度となつていて前記油は軸受の発生熱以上の温
度上昇があり65〜75℃前後の温度となつている。 The end wall on the discharge side where the rotor casing 1 and the discharge casing 3 are in contact is at a temperature of 60 to 90℃ due to the influence of compression heat, and the temperature of the oil rises more than the heat generated by the bearing, and the temperature of the oil is around 65 to 75℃. It's the temperature.
油路４３に分岐された圧油は吸込ケーシング２
中で分れて一方の油路４３ａをとおつた圧油は溝
５６より孔５６ａをとおり、油溝５９に入りジヤ
ーナル軸受６を冷却潤滑し、他方の油路４３ｂを
とおつた圧油はシリンダ室３９に入り作動圧をピ
ストン３７に及ぼし、ピストン３７とシリンダ３
８間より洩れる油は室４６に入る。溝５６より油
路５７に入つた圧油は溝５８に到り孔５８ａを通
じて油溝６１に入りジヤーナル軸受７を冷却潤滑
する。油溝５９，６１の圧油はオリフイス６２，
６３により給油量が調節されて室６４，６５に
夫々入り、室６４の油はシリンダ室３９より洩れ
る油も併せて室６４，６５間に設けた通路６６を
とおつて室６５に流れ、室６５から油路６７に送
られる。 The pressure oil branched into the oil path 43 is transferred to the suction casing 2
The pressure oil that splits in the middle and passes through one oil passage 43a passes through the hole 56a from the groove 56 and enters the oil groove 59 to cool and lubricate the journal bearing 6, and the pressure oil that passes through the other oil passage 43b enters the cylinder chamber. 39 and applies working pressure to the piston 37, causing the piston 37 and cylinder 3
Oil leaking from the chamber 46 enters the chamber 46. Pressure oil entering the oil passage 57 from the groove 56 reaches the groove 58 and enters the oil groove 61 through the hole 58a to cool and lubricate the journal bearing 7. The pressure oil in the oil grooves 59, 61 is supplied to the orifice 62,
63 adjusts the amount of oil supplied and enters the chambers 64 and 65, respectively.The oil in the chamber 64, together with the oil leaking from the cylinder chamber 39, flows into the chamber 65 through a passage 66 provided between the chambers 64 and 65. The oil is sent to the oil passage 67 from there.
油路６７に送られる圧油はジヤーナル軸受６，
７が吸込側であつて比較的低い温度であり粘性も
あり潤滑性能が保たれている。これらの圧油は油
路６８より雌ロータ５とロータケーシング１間の
摺動面に入り潤滑と密閉が行われ、又雄ロータ４
と雌ロータ５間の密閉と潤滑が行われる。 The pressure oil sent to the oil passage 67 is sent to the journal bearing 6,
7 is the suction side, which has a relatively low temperature and viscosity, and maintains lubrication performance. These pressure oils enter the sliding surface between the female rotor 5 and the rotor casing 1 through the oil passage 68, where lubrication and sealing are performed, and the male rotor 4.
Sealing and lubrication between the female rotor 5 and the female rotor 5 are performed.
ロータケーシング１と吸込ケーシング２の接し
ている吸込側端壁は吸込口２３と接しているため
圧縮機の吸込側の温度一般、−40〜10℃に影響さ
れて冷たくなつているので通過する油はジヤーナ
ル軸受６，７の発生熱量では温度上昇がわずかで
該軸受に給油される前の温度とそれ程変らないか
低い場合もあるのである。 The end wall on the suction side where the rotor casing 1 and the suction casing 2 are in contact is in contact with the suction port 23, so the temperature on the suction side of the compressor is generally influenced by -40 to 10 degrees Celsius and is cold, so the oil passing through it is cold. In terms of the amount of heat generated by the journal bearings 6 and 7, the temperature rise is small and may be lower or not much different from the temperature before the bearings are lubricated.
入口７１より入つた油は油溝７２をとおり、噴
射口７５より雄ロータ４、雌ロータ５の外周作用
空間に噴出する。この噴射口７５はスライドバル
ブ３２を右行させると移動するので部分負荷とす
る場合に噴射した油が吸込空間に洩れ込まない様
スライドバルブの低圧制御縁３１より１ピツチ吐
出側としている。油溝７２，７３，７４をとおつ
て油路７６をとおつて噴射口７６から雄ロータ
４、雌ロータ５の外周作用空間に吸込側端壁より
１ピツチ吐出側の位置において給油される。 Oil entering from the inlet 71 passes through the oil groove 72 and is ejected from the injection port 75 into the outer working spaces of the male rotor 4 and female rotor 5. Since this injection port 75 moves when the slide valve 32 is moved to the right, it is positioned one pitch on the discharge side from the low pressure control edge 31 of the slide valve so that the injected oil does not leak into the suction space when a partial load is applied. Oil is supplied from the injection port 76 through the oil grooves 72, 73, 74 and through the oil passage 76 to the outer working spaces of the male rotor 4 and female rotor 5 at a position one pitch on the discharge side from the suction side end wall.
スライドバルブ３２が右行して油溝７２，７３
間が離れると油溝７３には油は行かなくなり、油
は油路７６より給油されない。即ち、一定以下の
部分負荷の場合は雄ロータ４、雌ロータ５の外周
への給油はスライドバルブ３２を介する。給油は
油路６８及び噴射口７５のみとなる。従つてスラ
イドバルブ３２が移動して油路７６より潤滑油が
吸込空間に溢流することがない。 Slide valve 32 moves to the right and oil grooves 72, 73
If the space is far apart, no oil will flow to the oil groove 73 and no oil will be supplied from the oil passage 76. That is, in the case of a partial load below a certain level, oil is supplied to the outer peripheries of the male rotor 4 and female rotor 5 through the slide valve 32. Oil is supplied only through the oil passage 68 and the injection port 75. Therefore, the lubricating oil does not overflow into the suction space from the oil passage 76 due to movement of the slide valve 32.
油路６８、噴射口７５、噴射口７６ａよりの給
油は冷却された油であり、それぞれの断面は小さ
なオリフイスでよい特徴がある。 Cooled oil is supplied from the oil passage 68, the injection port 75, and the injection port 76a, and the cross section of each of them is characterized by requiring a small orifice.
以上のとおり、本発明のスクリユー圧縮機によ
れば次の如き、顕著な効果を有する。
As described above, the screw compressor of the present invention has the following remarkable effects.
(1) ロータ作用空間の圧縮室に供給される油は、
温度を低めに出来、油の粘性も増加させている
為、ロータの潤滑及びロータ作用空間の密封性
を向上できる。圧縮は等温圧縮に近くなり、圧
縮効率を向上出来る。さらに圧縮室への適正油
量を少なくすることが出来てロータによる油の
撹拌動力が低減される。(1) The oil supplied to the compression chamber of the rotor working space is
Since the temperature can be lowered and the viscosity of the oil has also been increased, rotor lubrication and sealing of the rotor working space can be improved. Compression becomes close to isothermal compression, and compression efficiency can be improved. Furthermore, the appropriate amount of oil to the compression chamber can be reduced, and the power for stirring the oil by the rotor is reduced.
(2) 運転条件が変化しても油量の変化が従来のも
のより変化が小さく改善出来て吸入、吐出の圧
力差が大きい時の油の撹拌動力の低減が出来
る。(2) Even if the operating conditions change, the change in oil amount is smaller than that of conventional models, which can be improved, and the power for stirring oil can be reduced when the pressure difference between suction and discharge is large.
(3) 吸込側に設けた軸受及びバランスピストンに
送つた油を吸込口とじ込み後のロータ作用空間
に戻したことにより、油及び油中に含まれて来
た冷媒の気化による、圧縮機の有効吸入側の低
下を防止出来る。(3) The oil sent to the bearing and balance piston on the suction side is returned to the working space of the rotor after the suction port is closed, thereby increasing the efficiency of the compressor by vaporizing the oil and the refrigerant contained in the oil. It is possible to prevent a drop on the suction side.
図面は何れも本発明の実施例を示すもので、第
１図は縦断面図、第２図は第１図のＡ−Ａ断面
図、第２ａ図、第２ｂ図は第２図の一部拡大図、
第３図は第１図のＢ−Ｂ断面図、第４図は潤滑系
統図である。
１……ロータケーシング、２……吸込ケーシン
グ、３……吐出ケーシング、４……雄ロータ、４
ａ，４ｂ，５ａ，５ｂ……軸部、５……雌ロー
タ、６，７，８，９……ジヤーナル軸受、１２，
１３……スラスト玉軸受、１６……カバー、１７
……シールカバー、１８……軸封装置、１９……
シールリング、２１……カバー、２２……吸込通
路、２３……吸込口、２４……吐出口、３１……
スライドバルブ低圧制御縁、３６……位置、４１
……入口、４２，４３……油路、４５，４７……
溝、４６……油路、４９……油溝、５１……油
溝、５２，５３……オリフイス、５４……空間、
５５……通路、５６……溝、５７……油路、５
９，６１……油溝、６２，６３……オリフイス、
６４，６５……室、６６……通路、６７，６８…
…油路。
The drawings all show embodiments of the present invention; FIG. 1 is a longitudinal sectional view, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIGS. 2a and 2b are parts of FIG. 2. Enlarged view,
FIG. 3 is a sectional view taken along line BB in FIG. 1, and FIG. 4 is a lubrication system diagram. 1... Rotor casing, 2... Suction casing, 3... Discharge casing, 4... Male rotor, 4
a, 4b, 5a, 5b... shaft portion, 5... female rotor, 6, 7, 8, 9... journal bearing, 12,
13... Thrust ball bearing, 16... Cover, 17
... Seal cover, 18 ... Shaft sealing device, 19 ...
Seal ring, 21...cover, 22...suction passage, 23...suction port, 24...discharge port, 31...
Slide valve low pressure control edge, 36...position, 41
... Entrance, 42, 43... Oil passage, 45, 47...
Groove, 46... Oil passage, 49... Oil groove, 51... Oil groove, 52, 53... Orifice, 54... Space,
55... Passage, 56... Groove, 57... Oil passage, 5
9, 61... Oil groove, 62, 63... Orifice,
64, 65...Room, 66...Aisle, 67, 68...
...Oil road.
Claims (1)
直径よりも小なる如く互に重なり合つて設けられ
た二個の円筒状ボアの中に、それぞれ前記ボア軸
を中心に回転可能に支えられて互に噛み合う雄ロ
ータと雌ロータとを備え、前記ケーシングには前
記ボアの両端に前記ボア軸に直角な吸入側端壁及
び吐出側端壁を備え、該吸入側端壁及び吐出側端
壁にはそれぞれ端壁吸込口及び端壁吐出口、さら
に前記雄、雌ロータを支承する軸受を吸込側と吐
出側に備え、容量制御を行なうスライドバルブを
有し、作動流体を冷媒とし、圧縮機の外部より冷
却された油を吸込口完全とじ込み位置のロータ作
用空間にスライドバルブを介して供給する油路を
備えたスクリユー圧縮機において、圧縮機の外部
より冷却された油を各軸受に供給する油路と、吐
出側に設けた軸受に給油した油を吐出側の通路に
送る油路と、吸込側に設けた軸受及びバランスピ
ストンに送つた油を吸入口とじ込み縁より２ピツ
チ位置又は該位置直後の吐出側のロータ作用空間
に送る油路を設けたことを特徴とするスクリユー
圧縮機。1 Supported rotatably about the bore axis in two cylindrical bores provided in parallel in the casing and overlapping each other such that the distance between the axes is smaller than the diameter thereof. The casing includes a male rotor and a female rotor that mesh with each other, and the casing has a suction side end wall and a discharge side end wall perpendicular to the bore axis at both ends of the bore, and the suction side end wall and the discharge side end wall have each has an end wall suction port and an end wall discharge port, bearings for supporting the male and female rotors on the suction side and the discharge side, slide valves for capacity control, the working fluid is the refrigerant, and the compressor In a screw compressor equipped with an oil passage that supplies cooled oil from the outside to the rotor working space at the suction port completely closed position via a slide valve, the oil that supplies cooled oil from the outside of the compressor to each bearing. an oil passage that sends the oil supplied to the bearing on the discharge side to the passage on the discharge side, and an oil passage that sends oil to the bearing and balance piston installed on the suction side at a position two pitches from the suction port closing edge or immediately after the position. A screw compressor characterized in that an oil passage is provided for sending oil to a rotor working space on the discharge side of the screw compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984881A JPS57135292A (en) | 1981-02-12 | 1981-02-12 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984881A JPS57135292A (en) | 1981-02-12 | 1981-02-12 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57135292A JPS57135292A (en) | 1982-08-20 |
| JPH0128233B2 true JPH0128233B2 (en) | 1989-06-01 |
Family
ID=12010665
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1984881A Granted JPS57135292A (en) | 1981-02-12 | 1981-02-12 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57135292A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04111347U (en) * | 1991-03-12 | 1992-09-28 | 恒真産業株式会社 | Simple heating element for chemical liquids |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005061900A1 (en) * | 2003-12-22 | 2005-07-07 | Mitsubishi Denki Kabushiki Kaisha | Screw compressor |
| JP4588708B2 (en) | 2004-08-03 | 2010-12-01 | 株式会社前川製作所 | Lubricating oil supply system and operation method for multi-system lubricated screw compressor |
| JP6126512B2 (en) | 2013-10-15 | 2017-05-10 | 株式会社神戸製鋼所 | Compressor |
| WO2015094464A1 (en) | 2013-12-18 | 2015-06-25 | Carrier Corporation | Refrigerant compressor lubricant viscosity enhancement |
| CN109779906B (en) * | 2019-03-14 | 2020-08-18 | 西安交通大学 | Radial bearing combination structure of double-screw compressor with sealing function |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5546011A (en) * | 1978-09-26 | 1980-03-31 | Hokuetsu Kogyo Co Ltd | Oil cooled screw compressor with regulating valve |
-
1981
- 1981-02-12 JP JP1984881A patent/JPS57135292A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5546011A (en) * | 1978-09-26 | 1980-03-31 | Hokuetsu Kogyo Co Ltd | Oil cooled screw compressor with regulating valve |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04111347U (en) * | 1991-03-12 | 1992-09-28 | 恒真産業株式会社 | Simple heating element for chemical liquids |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57135292A (en) | 1982-08-20 |
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