JPH08232863A - Shaft-through scroll compressor - Google Patents
Shaft-through scroll compressorInfo
- Publication number
- JPH08232863A JPH08232863A JP3669895A JP3669895A JPH08232863A JP H08232863 A JPH08232863 A JP H08232863A JP 3669895 A JP3669895 A JP 3669895A JP 3669895 A JP3669895 A JP 3669895A JP H08232863 A JPH08232863 A JP H08232863A
- Authority
- JP
- Japan
- Prior art keywords
- wrap
- curve
- scroll
- center
- shaft
- 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.)
- Granted
Links
Landscapes
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷凍空調用・冷蔵庫用
等の冷媒用圧縮機として用いられる密閉形スクロール圧
縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic scroll compressor used as a refrigerant compressor for refrigeration and air conditioning, refrigerators and the like.
【０００２】[0002]
【従来の技術】スクロール圧縮機の１種である軸貫通方
式スクロ−ル圧縮機は、特開昭５７−１３１８９６号
（従来例１）や特開平５−５４８５号（従来例２）で開
示されているように、旋回スクロール部材の中心部に旋
回軸受部を設け、該旋回軸受部にクランク軸の偏心軸部
をラップ先端部まで挿入した構造である。2. Description of the Related Art A shaft penetrating scroll compressor, which is one type of scroll compressor, is disclosed in JP-A-57-131896 (conventional example 1) and JP-A-5-5485 (conventional example 2). As described above, the orbiting scroll member is provided with the orbiting bearing portion at the center thereof, and the eccentric shaft portion of the crankshaft is inserted into the orbiting bearing portion up to the tip of the wrap.
【０００３】[0003]
【発明が解決しようとする課題】上記従来例１は、固定
スクロ−ル側に上記軸心軸部を支承する軸受部を設けて
いるが、該軸受部は固定スクロ−ルの鏡板部に配置した
構成となっている。このため、吐出孔の大きさが軸受部
に制約され、吐出冷媒ガス通路を広く確保できず、ま
た、上記従来例にあるように該吐出通路が屈折通路形状
となっているなどその通路内での流れにともなう通路損
失（圧力損失）が大きく増大し、圧縮機の性能面で不利
となっていた。また、従来例２では、固定スクロールラ
ップ側のラップ巻き始め部では、ラップ部の曲率が大き
くまたラップ部の厚さが薄くなっているため、ラップの
径方向の倒れなどラップ強度が弱いという問題がある。
また、スクロール圧縮機の外径寸法が制約された条件で
は、必要な固有圧縮比がとれないので、高圧力比条件で
は、吐出孔からのガスの逆流による動力損失が発生しや
すく、効率が低下するという性能面で課題がある。本発
明では上記した課題を解決することにある。In the above-mentioned conventional example 1, the bearing portion for supporting the shaft center shaft portion is provided on the fixed scroll side. The bearing portion is arranged on the end plate portion of the fixed scroll. It has been configured. For this reason, the size of the discharge hole is restricted by the bearing portion, so that the discharge refrigerant gas passage cannot be secured widely, and the discharge passage has a bent passage shape as in the above-mentioned conventional example. The passage loss (pressure loss) due to the flow of the compressor significantly increased, which was a disadvantage in terms of the performance of the compressor. Further, in Conventional Example 2, at the wrap winding start portion on the fixed scroll wrap side, the wrap portion has a large curvature and the wrap portion has a small thickness, so that the wrap strength is weak such as the wrap falling in the radial direction. There is.
In addition, under the condition that the outer diameter of the scroll compressor is restricted, the required specific compression ratio cannot be obtained.Therefore, under the high pressure ratio condition, power loss is likely to occur due to the reverse flow of gas from the discharge hole, and the efficiency decreases. There is a problem in terms of performance. The present invention is to solve the above-mentioned problems.
【０００４】[0004]
【課題を解決するための手段】本発明では、軸貫通スク
ロ−ル圧縮機において、固定スクロ−ルの鏡板中央部に
大口径と小口径を有する段差を備えた吐出孔を設けて死
容積を減少せしめ、該小口径の吐出孔部の中心が鏡板中
心と一致し、反ラップ側の鏡板面に吐出弁機能部を備え
る構成とすること、また、クランク軸が偏心軸先端に更
に軸心軸部を固定スクロ−ル側に延長し、該軸心軸部の
先端部が反ラップ側の鏡板中央面に備えた吐出弁部近傍
まで延長し、吐出孔での死容積をさらに減少せしめたこ
とを特徴とするものである。According to the present invention, in a shaft-through scroll compressor, a dead volume is provided by providing a discharge hole having a step having a large diameter and a small diameter in the central portion of the end plate of the fixed scroll. The center of the small-diameter discharge hole is aligned with the center of the end plate, and a discharge valve function part is provided on the end plate surface on the opposite lap side. The end portion of the shaft is extended to the vicinity of the discharge valve portion provided on the central surface of the end plate on the side opposite to the wrap side to further reduce the dead volume in the discharge hole. It is characterized by.
【０００５】次ぎに、旋回スクロ−ルの旋回軸受部を構
成する歯形の巻始め部を鏡板中心とする円弧曲線とし、
相対する固定スクロ−ルのラップ厚さを旋回側より厚く
せしめるため、固定スクロ−ルのラップ始点から内側曲
線として大円弧曲線にて凹部を形成し、外側曲線として
小円弧曲線からなる凸部を形成し、その外側をインボリ
ュ−ト曲線で構成し、旋回スクロ−ルのラップ始点から
外側曲線として大円弧曲線にて凸部を形成し、内側曲線
として半周を小円弧曲線からなる凹部を形成し、その外
側をインボリュ−ト曲線で構成したラップ巻始め形状と
したことを特徴とするものである。また、その固定スク
ロ−ルのラップ中央部となる内側曲線部の大円弧曲線部
と外側曲線の小円弧曲線部のラップ根本部に軸方向の大
きな円弧形状もしくは面取り部からなり、該根本部の厚
さをラップ先端部の厚さより厚く設定し、旋回スクロ−
ルのラップ中央部の外側曲線側の大円弧曲線部と内側曲
線の小円弧曲線部のラップ先端部を軸方向の大きな円弧
形状もしくは面取り部からなるラップ巻始め形状とした
ことを特徴とする。Next, an arc curve whose center of the end plate is the winding start portion of the tooth profile which constitutes the orbiting bearing portion of the orbiting scroll,
In order to make the wrap thickness of the opposing fixed scroll thicker than the turning side, a concave portion is formed from the lap start point of the fixed scroll with a large arc curve as an inner curve and a convex portion consisting of a small arc curve as an outer curve. The outer side is formed by an involute curve, the convex portion is formed by a large arc curve as an outer curve from the lap start point of the turning scroll, and the concave portion formed by a small arc curve is formed on a half circumference as an inner curve. The outer side of the wrapping winding is formed by an involute curve. In addition, the large circular arc curved portion of the inner curved portion and the small circular curved portion of the outer curved portion, which are the central portion of the wrap of the fixed scroll, are formed of a large axial arc shape or a chamfered portion in the lap root portion of the outer curved portion. Set the thickness thicker than the thickness of the tip of the lap, and rotate the scroll.
It is characterized in that the wrap ends of the large circular arc curved portion on the outer curved side and the small circular curved portion of the inner curved line of the lap center portion of the lap have a large circular arc shape in the axial direction or a wrap winding start shape composed of a chamfered portion.
【０００６】[0006]
【作用】本発明の作用を図１から図１２をもとにして説
明する。図１と図２に示すように、固定スクロ−ル５側
の鏡板中央部５ａに設けた吐出孔１０には、鏡板中央部
に大口径用穴１０ａと小口径用穴１０ｂを有し、図のよ
うに段差を備えて連通している。このように吐出孔１０
を段差構造とすることで、死容積を減少せしめることが
できるとともに、冷媒ガスが圧縮室から吐出孔１０ａに
移動するための間口が広いため、吐出過程で冷媒ガスの
吐出作用をスム−スに行なわせることが可能となる。該
小口径の吐出孔部１０ｂの中心が鏡板５ａの中心と一致
し、反ラップ側の鏡板面に吐出弁機能部９０を備える構
成とすることで、高圧力比条件において、吐出孔からの
ガスの逆流による動力損失を最小限に抑え、効率が従来
機に対して向上するという効果が得られる。また、図１
２に示すように、クランク軸１４の偏心軸１４ａ先端部
１４ｃに更に軸心軸部１４ｍを固定スクロ−ル５側に延
長しているため、かつ該軸心軸部１４ｍの先端部が反ラ
ップ側の鏡板中央面に備えた吐出弁部９０近傍まで延長
しているため、吐出孔１０での死容積（デッドボリュ−
ム）をさらに減少せしめることができる。The operation of the present invention will be described with reference to FIGS. As shown in FIGS. 1 and 2, the discharge hole 10 provided in the central portion 5a of the end plate on the side of the fixed scroll 5 has a large diameter hole 10a and a small diameter hole 10b in the central portion of the end plate. There is a step like this and it communicates. In this way, the discharge hole 10
By adopting a step structure, the dead volume can be reduced, and since the opening for moving the refrigerant gas from the compression chamber to the discharge hole 10a is wide, the discharging action of the refrigerant gas can be made smooth during the discharging process. It becomes possible to do it. The center of the small-diameter discharge hole portion 10b coincides with the center of the end plate 5a, and the discharge valve function part 90 is provided on the end plate surface on the side opposite to the lap side. The effect that the power loss due to the reverse flow of is minimized and the efficiency is improved compared to the conventional machine is obtained. Also, FIG.
As shown in FIG. 2, since the shaft center shaft portion 14m is further extended to the fixed scroll 5 side to the eccentric shaft 14a tip end portion 14c of the crankshaft 14, the tip end portion of the shaft center shaft portion 14m is an anti-wrap. Since it extends to the vicinity of the discharge valve portion 90 provided on the central surface of the end plate on the side, the dead volume in the discharge hole 10 (dead volume)
Can be further reduced.
【０００７】図９に示すように、旋回スクロ−ルの旋回
軸受部３１を構成する歯形の巻始め部を鏡板６ａの中心
Ｏｍとする円弧曲線ｐとし、相対する固定スクロ−ルの
ラップ巻き始め部のラップ厚さを旋回６側及び固定側ラ
ップ外周部のラップ厚さＴ1よりＴ2 と厚くしているた
め、ラップ強度を大きく向上できる。すなわち、図９に
て、旋回スクロ−ル６のラップ始点７７から外側曲線と
して大円弧曲線ｐにて凸部を形成し、内側曲線として半
周を小円弧曲線ｚからなる凹部を形成し、その外側をイ
ンボリュ−ト曲線で構成したラップ巻始め形状としてい
る。いいかえれば、旋回側は巻き始め部６ｍにおいてｔ
3 寸法分（Ｔ2 −Ｔ1 ）小さく設定している。具体的に
は、Ｔ1 ＝３．５ｍｍに対してＴ2 ＝４．５〜５．５ｍ
ｍ前後の寸法差となる。図１の固定スクロ−ル５におい
て、固定スクロ−ル５のラップ５ｂの始点６０から内側
曲線として大円弧曲線５ｖにて凹部を形成し、外側曲線
として小円弧曲線からなる円弧（６０〜６１）の凸部６
０ａを形成し、その外側をインボリュ−ト曲線で構成し
ている。点６０から点６２の内側曲線５ｖは、破線で示
した従来曲線ａより鏡板中心側に位置し設定している。
内側曲線５ｖは、鏡板中心Ｏｆｏを中心とする円弧曲線
である。なお、破線の曲線ａは、インボリュ−ト曲線で
従来の曲線を参考までに示し、ラップ中央部のみラップ
厚さを（Ｔ2−Ｔ1 ）分厚くしているものである。な
お、Ｏｆｏは、インボリュ−ト曲線（点６２から点６８
の内側曲線部と点６１から点６７の外側曲線部の基礎円
中心で、鏡板中心Ｏｆに対してラップ始点６０，６１側
に偏心している。As shown in FIG. 9, the winding start portion of the tooth profile forming the orbiting bearing portion 31 of the orbiting scroll is an arc curve p having the center Om of the end plate 6a as the arc winding p, and the wrap winding start of the opposing fixed scroll is started. Since the lap thickness of the portion is made thicker than the lap thickness T 1 of the wrap 6 side and the fixed side lap outer peripheral portion by T 2 , the lap strength can be greatly improved. That is, in FIG. 9, a convex portion is formed from the lap start point 77 of the turning scroll 6 with a large circular arc curve p as an outer curve, and a concave portion consisting of a small circular arc curve z is formed halfway around the inner curve as the outer curve. Has a wrapping start shape composed of an involute curve. In other words, the turning side is t at the winding start part 6m.
3 dimension of (T 2 -T 1) is set to be smaller. Specifically, for T 1 = 3.5 mm, T 2 = 4.5 to 5.5 m
There will be a dimensional difference of around m. In the fixed scroll 5 shown in FIG. 1, a circular arc (60 to 61) is formed from a starting point 60 of the lap 5b of the fixed scroll 5 by forming a concave portion with a large arc curve 5v as an inner curve and a small arc curve as an outer curve. Convex part 6
0a is formed, and the outside thereof is constituted by an involute curve. The inside curve 5v from the point 60 to the point 62 is set on the end plate center side from the conventional curve a shown by the broken line.
The inner curve 5v is an arc curve centered on the end plate center Ofo. The broken line curve a is an involute curve which is a conventional curve for reference, and the lap thickness is increased by (T 2 −T 1 ) only in the central portion of the lap. Note that Ofo is the involute curve (point 62 to point 68).
Is eccentric to the wrap start points 60, 61 side with respect to the end plate center Of at the center of the basic circle of the inner curved portion of the curve and the outer curved portion of point 67 from the point 67.
【０００８】また、図１０に示すように、固定スクロ−
ル５のラップ中央部となる内側曲線部の大円弧曲線部５
ｖと外側曲線の小円弧曲線部６０ａ及び外側曲線部（点
６１−６１ａ近辺）のラップ根本部に軸方向の大きな円
弧形状部５５を、旋回側にはラップ先端部に面取り部５
４としているので、該根本部５６の厚さをラップ先端部
の厚さより大きく厚く設定でき、該根元部の強度を向上
できる。なお、旋回スクロ−ルのラップ中央部の外側曲
線側の大円弧曲線部ｐと内側曲線の小円弧曲線部ｚのラ
ップ先端部を軸方向の大きな円弧形状もしくは面取り部
５４からなるラップ巻始め形状としているので、該旋回
根元部の強度をも向上できることになる。根元部の半径
Ｒは、０．３ｍｍから０．６ｍｍ前後に設定すれば充分
強度改善がはかれるものである。従来の根元部の半径Ｒ
は、０．１ｍｍから０．１５ｍｍ位であり、その根本部
での応力集中の大幅な緩和化が図れる。勿論根元部の半
径Ｒは１ｍｍから２ｍｍ前後の寸法でも良く、さらに強
度アップがはかれるものである。Further, as shown in FIG. 10, a fixed scroll is used.
Large arc curved portion 5 of the inner curved portion that is the lap center portion of the rule 5
v and a small arc-shaped curved portion 60a of the outer curve and a large arc-shaped portion 55 in the axial direction at the wrap root portion of the outer curved portion (around points 61-61a), and a chamfered portion 5 at the wrap tip end on the turning side.
Since it is set to 4, the thickness of the root portion 56 can be set to be larger than the thickness of the wrap tip portion, and the strength of the root portion can be improved. It should be noted that the wrap winding start shape formed by the large arc shape in the axial direction or the chamfered portion 54 at the wrap tips of the large arc curve portion p on the outer curve side of the wrap center of the turning scroll and the small arc curve portion z of the inner curve. Therefore, it is possible to improve the strength of the turning root portion. If the radius R of the root portion is set to around 0.3 mm to 0.6 mm, the strength is sufficiently improved. Conventional root radius R
Is about 0.1 mm to 0.15 mm, so that stress concentration at the root can be significantly reduced. Needless to say, the radius R of the root portion may be about 1 mm to about 2 mm, and the strength can be further increased.
【０００９】[0009]
【実施例】本発明の実施例を図１から図１６にわたって
示す。図１と図２は、固定スクロ−ル５の平面図と縦断
面図である。図１において、固定スクロ- ル５のラップ
曲線は円弧曲線とインボリュ−ト曲線を組み合わせてい
る。ラップ終端部５ｎには冷媒ガスの入る吸入孔１６を
配置する。５ｆは吸入室である。鏡板５ａの中心は点Ｏ
ｆで、吐出孔１０ｂの中心と一致する。中心点Ｏｆより
ラップ終端部５ｎと反対側に偏心した点Ｏｆo は、ラッ
プ部５ｂのインボリュ−ト曲線部の基礎円の中心であ
る。固定スクロ−ル５側の鏡板５ａのほぼ中央部にあっ
てややラップ始端部６０の方向に偏心した位置に設けた
のが吐出孔１０ａである。その吐出孔１０ａの外縁部は
ラップ始端部６０の円弧曲線である内側曲線５ｖと近接
もしくは一致している。このように、固定スクロ−ルの
吐出孔１０ａの径Ｄｄ1 は、その大きさが旋回軸受部３
１の内径寸法Ｄｍより若干大きく設定し冷媒ガスの吐出
作用できる間口を広めている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention is shown in FIGS. 1 and 2 are a plan view and a vertical sectional view of the fixed scroll 5. In FIG. 1, the lap curve of the fixed scroll 5 is a combination of an arc curve and an involute curve. A suction hole 16 into which the refrigerant gas enters is arranged at the wrap end portion 5n. 5f is an inhalation chamber. The center of the end plate 5a is point O
At f, it coincides with the center of the discharge hole 10b. A point Ofo that is eccentric to the opposite side of the wrap end portion 5n from the center point Of is the center of the basic circle of the involute curve portion of the lap portion 5b. The discharge hole 10a is provided at a position slightly eccentric in the direction toward the lap start end portion 60 at a substantially central portion of the end plate 5a on the fixed scroll 5 side. The outer edge of the discharge hole 10a is close to or coincides with the inner curve 5v which is the arc curve of the wrap start end 60. As described above, the diameter Dd 1 of the discharge hole 10 a of the fixed scroll has a size that is different from that of the swivel bearing portion 3.
1 is set to be slightly larger than the inner diameter dimension Dm of 1 to widen the frontage capable of discharging the refrigerant gas.
【００１０】図１と図２に示すように、固定スクロ−ル
５側の鏡板中央部５ａに設けた吐出孔１０は、鏡板中央
部に大口径用穴１０ａと小口径穴１０ｂを有し、図のよ
うに段差を備えて連通している。このように吐出孔１０
を段差構造とし、両者孔１０ａ，１０ｂは連通してい
る。該小口径の吐出孔部１０ｂの中心が鏡板５ａの中心
とほぼ一致し、反ラップ側の鏡板面に吐出弁機能部９０
を備える構成とする。このことで、高圧力比条件におい
て、吐出孔からのガスの逆流による動力損失を最小限に
抑え、効率が従来機に対して向上するという効果が得ら
れる。また、小口径の吐出孔部１０ｂの中心を鏡板５ａ
の中心とほぼ一致させることで、吐出弁機能部９０の位
置決めが容易となり組立て性が改善されること、吐出室
１ａでのガスのながれが平均化されてその吐出室１ａで
の油分離性能が向上できることなどの効果が有る。As shown in FIGS. 1 and 2, the discharge hole 10 provided in the central portion 5a of the end plate on the fixed scroll 5 side has a large aperture hole 10a and a small aperture hole 10b in the central portion of the end plate. As shown in the figure, they are connected with a step. In this way, the discharge hole 10
Has a stepped structure, and the holes 10a and 10b communicate with each other. The center of the small-diameter discharge hole portion 10b substantially coincides with the center of the end plate 5a, and the discharge valve function part 90 is provided on the end plate surface on the opposite lap side.
Is provided. As a result, under the high pressure ratio condition, the power loss due to the reverse flow of the gas from the discharge hole is minimized, and the efficiency is improved as compared with the conventional machine. In addition, the center of the small-diameter discharge hole portion 10b is set to the end plate 5a.
By substantially matching the center of the discharge valve function part 90, the positioning of the discharge valve function part 90 is facilitated, the assembling property is improved, the gas flow in the discharge chamber 1a is averaged, and the oil separation performance in the discharge chamber 1a is improved. There are effects such as being able to improve.
【００１１】図１の固定スクロ−ル５において、固定ス
クロ−ル５のラップ５ｂの始点６０から内側曲線として
大円弧曲線５ｖにて凹部を形成し、外側曲線として小円
弧曲線からなる円弧（６０〜６１）の凸部６０ａを形成
し、その外側をインボリュ−ト曲線で構成している。点
６０から点６２の内側曲線５ｖは、従来曲線ａより鏡板
中心側に寄った内側に設定している。内側曲線５ｖは、
鏡板中心Ｏｆｏを中心とする円弧曲線である。点６２の
位置は、円弧曲線５ｖと内側インボリュート曲線５ｕと
のつなぎ目の位置であり、その位置は始点６０から円弧
曲線が約半周延びたところである。この図ではその円弧
角は約１４０度として例示されている。なお、破線の曲
線ａは、インボリュ−ト曲線を参考までに示し、ラップ
中央部のみラップ厚さを（Ｔ2 −Ｔ1 ）分厚くしている
ものである。なお、Ｏｆｏは、インボリュ−ト曲線部、
具体的には点６２から点６８の内側曲線部と点６１から
点６７の外側曲線部の基礎円中心で、鏡板中心Ｏｆに対
してラップ始点６０，６１側に偏心している。In the fixed scroll 5 of FIG. 1, a concave portion is formed from the starting point 60 of the wrap 5b of the fixed scroll 5 with a large arc curve 5v as an inner curve, and an arc (60 with a small arc curve as an outer curve. To 61), the convex portion 60a is formed, and the outside thereof is constituted by an involute curve. The inner curve 5v from the point 60 to the point 62 is set to the inner side closer to the center side of the end plate than the conventional curve a. The inner curve 5v is
It is an arc curve centered on the end plate center Ofo. The position of the point 62 is the position of the joint between the circular arc curve 5v and the inner involute curve 5u, and the position is where the circular arc curve extends from the starting point 60 by about half a circumference. In this figure, the arc angle is exemplified as about 140 degrees. The broken line curve a shows the involute curve for reference, and the lap thickness is increased by (T 2 −T 1 ) only in the central portion of the lap. In addition, Ofo is an involute curve part,
Specifically, at the center of the base circle of the inner curved portion from the points 62 to 68 and the outer curved portion from the points 61 to 67, the eccentricity is deviated to the wrap start points 60, 61 side with respect to the end plate center Of.
【００１２】固定スクロールラップ外側曲線５ｓはイン
ボリュート曲線で形成され、その始点は点６１であり、
終点は圧縮開始点となる点６４とそれより外側の位置
で、吸入室５ｆを形成するための延長した曲線の終点で
ある点６７となる。一方固定スクロールラップ内側曲線
５ｕの始点は点６０であり、終点は圧縮開始点となる点
６３とそれより外側の位置で、吸入室５ｆを形成するた
めの延長した曲線の終点である点６８となる。ラップ部
５ｂの内側曲線５ｕの巻き始め部となる所は、始点６０
から点６２が円弧曲線であり、点６２から終点６４を経
て点６７までがインボリュ−ト曲線となる。外側曲線５
ｓは点６１から圧縮開始点となる点６４を経て終点６６
の範囲でインボリュ−ト曲線をなし、点６７と点６８と
を半径ｒ3の円弧５ｍにて滑らかに結ばれている。半径
ｒ3 は、例えばｒ3 ＝６．５ｍｍから５．５ｍｍ前後に
設定している。The fixed scroll wrap outer curve 5s is formed by an involute curve, and its starting point is a point 61,
The end point is a point 64 which is a compression start point and a position outside thereof, which is a point 67 which is an end point of an extended curve for forming the suction chamber 5f. On the other hand, the start point of the fixed scroll wrap inner curve 5u is a point 60, and the end point is a point 63 that is a compression start point and a point 68 that is an end point of an extended curve for forming the suction chamber 5f at a position outside thereof. Become. The starting point of the winding of the inner curve 5u of the wrap portion 5b is 60
From the point 62 to the point 62 is an arc curve, and from the point 62 to the point 64 to the point 67 is an involute curve. Outer curve 5
s is an end point 66 from a point 61 through a point 64 which is a compression start point
An involute curve is formed in the range of, and points 67 and 68 are smoothly connected by an arc 5 m of radius r 3 . The radius r 3 is set, for example, from r 3 = 6.5 mm to around 5.5 mm.
【００１３】また、ラップ始端部では点６０と点６１と
を半径ｒ1 の円弧６０ａにて滑らかに結ばれている。半
径ｒ1 ＝１．５ｍｍから２．５ｍｍ前後に設定してい
る。また、点６０と点６２とを半径Ｒ2 の円弧５ｖにて
滑らかに結ばれている。半径Ｒ2 は、Ｒ2 ＝２４ｍｍ前
後に設定している。このようなラップ曲線を構成するこ
とにより、該固定スクロ−ルのラップ始端部のラップ厚
さＴ1 をその他のラップ厚さＴ2 より大きく設定してい
る。例えば、Ｔ1 ＝Ｔ2 ＋１．０ｍｍからＴ1 ＝Ｔ2 ＋
２．５ｍｍ前後の寸法関係とし、ラップ強度の向上を図
っている。固定スクロ−ルラップ巻き終り角を通常の位
置（Ｖの位置）より旋回スクロ−ルのラップ巻き終わり
角より１８０度の範囲で延長した点６４としている。そ
して、Ｄｄ1 ／Ｄｍの比をＤｄ1 ／Ｄｍ＝１．２５前後
の値、もしくは、Ｄｄ1 ／（２×Ｒ2 ）の値をＤｄ1 ／
（２×Ｒ2 ）＝１．０前後に設定することが実用的であ
る。この寸法比関係をもとにして、適切な寸法Ｄｄ1 、
Ｄｍ、Ｒ2 が概ね決められる。例えば、その孔１０ａの
直径がＤｄ1 ＝３８ｍｍの大きい円形孔としている。吐
出孔１０ｂの孔径Ｄｄ2 はＤｄ2 ＝１０ｍｍ前後の円形
孔としている。一方Ｄｍ＝３０ｍｍ前後の値としてい
る。Further, at the wrap start end, points 60 and 61 are smoothly connected by an arc 60a having a radius r 1 . The radius r 1 is set to around 1.5 mm to 2.5 mm. Further, the points 60 and 62 are smoothly connected by an arc 5v having a radius R 2 . The radius R 2 is set to around R 2 = 24 mm. By constructing such a lap curve, the lap thickness T 1 at the lap start end portion of the fixed scroll is set larger than the other lap thickness T 2 . For example, from T 1 = T 2 +1.0 mm to T 1 = T 2 +
The dimensional relationship is around 2.5 mm to improve the lap strength. The fixed scroll wrap winding end angle is set to a point 64 extending from the normal position (position V) by 180 degrees from the wrap winding end angle of the orbiting scroll. Then, the ratio of Dd 1 / Dm is a value around Dd 1 /Dm=1.25, or the value of Dd 1 / (2 × R 2 ) is Dd 1 /
It is practical to set around (2 × R 2 ) = 1.0. Based on this dimensional ratio relationship, an appropriate dimension Dd 1 ,
Dm and R 2 are generally determined. For example, the diameter of the hole 10a is a large circular hole with Dd 1 = 38 mm. The diameter Dd 2 of the discharge hole 10b is a circular hole having a diameter of about Dd 2 = 10 mm. On the other hand, the value is around Dm = 30 mm.
【００１４】図２と図３に示すように、固定スクロ−ル
５の反ラップ側の鏡板中央面に吐出弁機能部９０を備
え、該吐出弁９１に対向する固定鏡板面側の材質（通常
鋳鉄材を使用）と異なるテフロン（登録商標）系軟質材
のシ−ト部８０を、上記吐出孔１０ｂの周辺部に埋込
み、もしくは充填し構成している。これは、リ−ド弁部
９１が上下動するときに発生するバルブ音を緩和し音の
強さを軽減する作用が得られる。９０ａは受け部で、９
３は受け部（リテ−ナ部）９０ａとリ−ド弁部９１の端
部を固定するボルトである。テフロン系軟質材のシ−ト
部８０としては、耐熱性と耐摩耗性に富む高機能樹脂材
料を当てることができる。例えば、ポリイミド樹脂にグ
ラファイトやテフロンを充填混合した材料、あるいは自
己潤滑性材料であってもよい。As shown in FIGS. 2 and 3, a discharge valve function portion 90 is provided on the center surface of the end plate of the fixed scroll 5 on the side opposite to the lap side, and the material on the side of the fixed end plate facing the discharge valve 91 (normally A sheet portion 80 of a Teflon (registered trademark) -based soft material different from a cast iron material is embedded or filled in the peripheral portion of the discharge hole 10b. This has the effect of reducing the valve sound generated when the lead valve portion 91 moves up and down and reducing the sound intensity. 90a is a receiving part, 9
3 is a bolt for fixing the receiving portion (retainer portion) 90a and the end portion of the lead valve portion 91. As the sheet portion 80 of the Teflon-based soft material, a high-performance resin material having high heat resistance and abrasion resistance can be applied. For example, a material in which graphite or Teflon is filled and mixed in a polyimide resin, or a self-lubricating material may be used.
【００１５】図４は、上記固定スクロ−ル５側の反ラッ
プ側の鏡板中央面に設けた吐出弁部９０のリテ−ナ部９
０ａの受け面に固体潤滑剤９６（たとえば、二硫化モリ
ブデンなど）をコ−ティング（裏付け）した構造を示
す。なお、該リテ−ナ部９０ａの受け面に前記したテフ
ロン系軟質材などを裏付けしてもよい。この構造とする
ことにより、さらにリ−ド弁部９１が上下動するときに
発生するバルブ音を軽減する作用が大きく得られる。す
なわち、図４は、吐出弁の背面を支えるリテ−ナ部表面
に、テフロン系軟質材もしくは軟質系固体潤滑剤をコ−
ティングしたことを特徴としている。FIG. 4 shows the retainer portion 9 of the discharge valve portion 90 provided on the center surface of the end plate on the side opposite to the fixed scroll 5 side.
The structure in which the solid lubricant 96 (for example, molybdenum disulfide) is coated (backed) on the receiving surface of 0a is shown. Incidentally, the receiving surface of the retainer portion 90a may be backed with the above-mentioned Teflon-based soft material or the like. With this structure, the effect of further reducing the valve noise generated when the lead valve portion 91 moves up and down can be greatly obtained. That is, in FIG. 4, a Teflon-based soft material or a soft-based solid lubricant is coated on the surface of the retainer portion that supports the back surface of the discharge valve.
It is characterized by having been started.
【００１６】図５は、固定スクロ−ル５側の鏡板中央部
５ａに設けた吐出孔１０には、鏡板歯底面を開口部とす
る大口径穴１０ａがあり、その深さｈ1 が１ｍｍから数
ｍｍ程度に浅く設定した構造を示す。この構造と上記し
た反ラップ側の鏡板面に吐出弁部９０を備える構成とす
ることで、さらに死容積を減少して、高圧力比条件にお
ける吐出孔からのガスの逆流による動力損失を最小限に
抑え、全断熱効率が従来機に対して向上するという効果
が大きく得られる。In FIG. 5, the discharge hole 10 provided in the central portion 5a of the end plate on the side of the fixed scroll 5 has a large diameter hole 10a having an opening at the bottom surface of the end face of the end plate, and the depth h 1 thereof is from 1 mm. The structure is shown as shallow as several mm. By adopting this structure and the structure in which the discharge valve section 90 is provided on the end plate surface on the side opposite to the lap side, the dead volume is further reduced, and the power loss due to the reverse flow of gas from the discharge hole under the high pressure ratio condition is minimized. The effect that the total adiabatic efficiency is improved compared to the conventional machine can be obtained.
【００１７】図２乃至図５の実施例は、今回開示した軸
貫通方式スクロール圧縮機のみに適用されるだけでな
く、従来例特開昭６２−２０３９９２号、特開昭６３−
６５１８７号に示されるスクロール圧縮機に対して適用
可能であり、同等の作用効果を奏する。The embodiment shown in FIGS. 2 to 5 is applied not only to the shaft-through type scroll compressor disclosed this time, but also to the conventional examples, Japanese Patent Laid-Open Nos. 62-203992 and 63-63.
It can be applied to the scroll compressor shown in No. 65187, and has the same effect.
【００１８】図６は、固定スクロ−ル５のラップ中央部
となる内側曲線部５ｖの大円弧曲線部と外側曲線の小円
弧曲線部のラップ根本部に軸方向の大きな円弧形状部１
０１，１０２を形成した実施例である。一方旋回スクロ
−ル６のラップ中央部６ｇとなる外側曲線部ｐのラップ
根本部に面取り部１１０を形成している。この構成によ
り、該ラップ中央部の根本部のみのラップ厚さをラップ
先端部の厚さより厚く設定し、また、スクロ−ルラップ
外周端部のラップ先端部のラップ厚さをより厚く設定で
きるので、ラップ強度をさらに強くするように改善でき
る。FIG. 6 shows a large arc-shaped portion 1 in the axial direction at the wrap root of the large circular curve portion of the inner curved portion 5v and the small circular curve portion of the outer curved portion which are the central portion of the wrap of the fixed scroll 5.
This is an example in which 01 and 102 are formed. On the other hand, a chamfered portion 110 is formed at the wrap root portion of the outer curved portion p which is the lap central portion 6g of the turning scroll 6. With this configuration, the lap thickness of only the root portion of the lap center portion can be set thicker than the thickness of the wrap tip portion, and the wrap thickness of the wrap tip portion of the scroll wrap outer peripheral end portion can be set thicker. It can be improved to further increase the lap strength.
【００１９】図７、図８及び図９に示すように、旋回ス
クロ−ル６の旋回軸受部３１を包含するようにラップ中
央部を構成している。図７と図９において、旋回スクロ
−ル６のラップ始点７７から外側曲線として大円弧曲線
ｐにて凸部を形成し、内側曲線として半周を小円弧曲線
ｚからなる凹部を形成し、その外側をインボリュ−ト曲
線で構成したラップ巻始め形状としている。大円弧曲線
ｐの範囲は点７７から点７２の領域となり、点７２と点
７７は前記点６０と点６２と同様に約半周延びた位置関
係にされ、図示例では約１４０度であり、また小円弧曲
線ｚの範囲は点７７から点７８の領域となる。As shown in FIG. 7, FIG. 8 and FIG. 9, the lap central portion is constructed so as to include the slewing bearing portion 31 of the slewing scroll 6. In FIG. 7 and FIG. 9, a convex portion is formed from the lap start point 77 of the turning scroll 6 with a large circular arc curve p as an outer curve, and a concave portion consisting of a small circular arc curve z is formed halfway around the inner curve as an outer curve. Has a wrapping start shape composed of an involute curve. The range of the large arc curve p is a region from the point 77 to the point 72, and the point 72 and the point 77 are in a positional relationship extending by about a half circumference like the points 60 and 62, and are about 140 degrees in the illustrated example, and The range of the small arc curve z is the area from point 77 to point 78.
【００２０】いいかえれば、図９に示すように、旋回側
は巻き始め部６ｍにおいてｔ3 寸法分（＝Ｔ2 −Ｔ1 ）
小さく設定している。具体的には、Ｔ1 ＝３．５ｍｍに
対してＴ2 ＝４．５〜５．５ｍｍ前後の寸法差となる。
このように、相対する固定スクロ−ルのラップ巻き始め
部のラップ厚さを旋回６側及び固定側ラップ外周部のラ
ップ厚さＴ1 よりＴ2 と厚くしている。このため、従来
機にたいして、ラップ強度を大きく向上できる。In other words, as shown in FIG. 9, on the turning side, at the winding start portion 6 m, the amount of t 3 (= T 2 −T 1 )
It is set small. Specifically, the dimensional difference is about T 2 = 4.5 to 5.5 mm with respect to T 1 = 3.5 mm.
Thus, opposite the fixed scroll - it is as thick as T 2 than the wrap thickness T 1 of the lap of the lap winding start portion of the Le thickness swirling 6 side and the fixed side wrap outer peripheral portion. Therefore, the lap strength can be greatly improved as compared with the conventional machine.
【００２１】大円弧曲線ｐの半径Ｒ3 はＲ3 ＝２０ｍｍ
前後とし、上記した半径Ｒ2 とはＲ2 ＝Ｒ3 ＋εth、
（ここで、εthは旋回半径である）の関係がある。小円
弧曲線ｚからなる凹部の半径Ｒは、溝幅Ｗｃに対してＷ
ｃ／２の大きさのＲ＝５．５ｍｍ前後となる。なお、小
円弧曲線ｚは、旋回スクロールのラップ巻き始め部７７
となる外側曲線の始点と旋回スクロールの内側曲線の始
点７８とをラップ溝幅Ｗｃを直径とする円弧曲線にて接
続し、該円弧曲線部ｚの側壁面に旋回内線室側の吐出行
程を旋回外線室側より早期に行なわせる吐出口６ｔを設
定している。該吐出口６ｔは、円弧の端点７７から角度
６８度前後の範囲にある点７３に開口している。その円
弧角度をθd の記号で示している。The radius R 3 of the large arc curve p is R 3 = 20 mm
Before and after, the radius R 2 is R 2 = R 3 + εth,
(Where εth is the turning radius). The radius R of the concave portion formed by the small arc curve z is W with respect to the groove width Wc.
The size of c / 2 is about R = 5.5 mm. The small arc curve z is the wrap winding start portion 77 of the orbiting scroll.
The starting point of the outer curve and the starting point 78 of the inner curve of the orbiting scroll are connected by an arc curve having a diameter of the wrap groove width Wc, and the discharge stroke on the side of the swirling extension chamber is swung to the side wall surface of the arc curve portion z. The discharge port 6t is set to be performed earlier than the outside line room side. The discharge port 6t is open at a point 73 in the range of about 68 degrees from the end point 77 of the arc. The arc angle is indicated by the symbol of θd.
【００２２】旋回スクロール６のラップ巻き終わり端部
６ｎの外縁端部７５であるラップ部６ｂの外側曲線6sの
終端部は、鏡板６ａの外終端より大きくしている。この
旋回スクロ−ルの鏡板外形寸法をＤｓo と記す。ラップ
部６ｂの外側曲線６ｓは、始点７７から点７８が円弧曲
線であり、点７８から終点７５までがインボリュウト曲
線となる。内側曲線６ｕは点７２から圧縮開始点となる
点７６の範囲でインボリュウト曲線をなし、点７２と点
７７とが半径Ｒ3 の円弧ｐにて滑らかに結ばれている。
なお、点Ｏｍｓは、インボリュ−ト曲線部、具体的には
点７２から点７５の外側曲線部と点７８から点７６の内
側曲線部のインボリュ−ト曲線の基礎円中心で、鏡板中
心Ｏｍに対してラップ始点７７側に偏心している。The end of the outer curve 6s of the wrap 6b, which is the outer edge 75 of the wrap winding end 6n of the orbiting scroll 6, is larger than the outer end of the end plate 6a. The outer dimension of the end plate of this turning scroll is referred to as Dso. In the outer curve 6s of the wrap portion 6b, a starting point 77 to a point 78 are arcuate curves, and a point 78 to an end point 75 are involute curves. The inner curve 6u forms an involute curve in the range from the point 72 to the point 76 which is the compression start point, and the points 72 and 77 are smoothly connected by the arc p having the radius R 3 .
The point Oms is the center of the base circle of the involute curve, specifically, the center of the involute curve of the outer curve of the points 72 to 75 and the inner curve of the points 78 to 76, and the center Om of the end plate. On the other hand, it is eccentric to the lap start point 77 side.
【００２３】また、図９に示すように、ラップ終端部で
は点７５と点７６とを半径ｒｏ（＝ラップ厚さ／２の大
きさ）の円弧６ｗにて滑らかに結んでもよい。上記早期
吐出口６ｔは、吐出溝６ｐとつながっている。該吐出溝
６ｐは旋回スクロールの中央部６ｇ側の旋回軸受３１外
周部３１ａのハウジング面に係合する扇形状のように設
定している。Further, as shown in FIG. 9, the points 75 and 76 may be smoothly connected by an arc 6w having a radius ro (= the thickness of the wrap / 2) at the end of the lap. The early ejection port 6t is connected to the ejection groove 6p. The discharge groove 6p is set to have a fan shape that engages with the housing surface of the outer peripheral portion 31a of the orbiting bearing 31 on the side of the central portion 6g of the orbiting scroll.
【００２４】早期吐出口６ｔ及び吐出溝６ｐの深さｈｏ
は、図８に示すように、旋回軸受上端面３１ｂの位置ま
で設定している。圧縮ガスは早期吐出口６ｔから矩形通
路６ｐにて旋回軸受３１側に吐出される。この早期吐出
口６ｔ、吐出溝通路６ｐは極力通路面積を大きく設定す
る。なお、図９において、旋回スクロール部材６の中心
部の旋回軸受部３１としてすべり軸受を設けている。該
軸受３１としては、比較的耐久性のある含油軸受タイプ
や四ふっかエチレン樹脂を軸受材料に適用したドライタ
イプ仕様スベリ軸受を用いている。The depth ho of the early ejection port 6t and the ejection groove 6p
Is set up to the position of the slewing bearing upper end surface 31b, as shown in FIG. The compressed gas is discharged to the orbiting bearing 31 side from the early discharge port 6t through the rectangular passage 6p. The early discharge port 6t and the discharge groove passage 6p set the passage area as large as possible. In FIG. 9, a slide bearing is provided as the orbiting bearing portion 31 at the center of the orbiting scroll member 6. As the bearing 31, a relatively durable oil-impregnated bearing type or a dry type sliding bearing using tetrafluoroethylene resin as a bearing material is used.
【００２５】また、図１０に示すように、ラップ中央部
のボス部６ｇの内周面や吐出孔１０ｂの内周面にＲ4 や
Ｒ5 などの円弧形状とすることでさらに、吐出ガスの流
動が吐出過程時におけるガス冷媒の流れをスム−スに行
なえ、流体抵抗が小さくなって圧力損失が減少し、ひい
ては過圧縮損失動力が大きく低下する。Further, as shown in FIG. 10, the inner peripheral surface of the boss portion 6g at the center of the lap and the inner peripheral surface of the discharge hole 10b are formed into an arc shape such as R 4 or R 5 so that the discharge gas The flow allows the gas refrigerant to flow smoothly during the discharge process, the fluid resistance is reduced, the pressure loss is reduced, and the overcompression loss power is greatly reduced.
【００２６】なお、図１１はラップ外周部のラップ厚さ
関係を示す両スクロ−ル組合せ時の模様を示す部分断面
図である。ラップ根本部の円弧部の半径Ｒ6 は０．１ｍ
ｍから０．１５ｍｍの範囲であり、一方、図１０に示し
たラップ根本部の円弧部の半径Ｒ5 は０．３ｍｍから
０．５ｍｍ前後と大きく設定している。この比率Ｒ5 ／
Ｒ6 がＲ5 ／Ｒ6 ＝２倍から５倍と大きく設定するのが
本発明の特徴でもある。ラップ高さが高くなっても、従
来技術より数倍のラップ強度が得られる効果がある。FIG. 11 is a partial cross-sectional view showing a pattern when the two scrolls are combined, showing the relationship between the lap thicknesses of the outer peripheral portion of the lap. Radius R 6 of the arc part of the lap root is 0.1m
The radius R 5 of the circular arc portion of the lap root portion shown in FIG. 10 is set to a large value of about 0.3 mm to about 0.5 mm. This ratio R 5 /
It is also a feature of the present invention that R 6 is set to be as large as R 5 / R 6 = 2 to 5 times. Even if the lap height is increased, it is possible to obtain the lap strength several times higher than that of the conventional technique.
【００２７】図１２は、クランク軸１４が偏心軸１４ａ
の先端に更に軸心軸部１４ｍを固定スクロ−ル５側に延
長し、該軸心軸部１４ｍの先端部が反ラップ側の鏡板中
央面に備えた吐出弁部９０近傍まで延長した実施例であ
る。該構造によって、吐出孔１０での死容積をさらに減
少せしめることが出来る。吐出ガスは、勿論吐出孔１０
（１０ａ、１０ｂ）と軸心軸部１４ｍとの間の空間を通
ることになる。In FIG. 12, the crankshaft 14 is an eccentric shaft 14a.
An example in which the shaft center shaft portion 14m is further extended to the fixed scroll 5 side at the tip of the above, and the tip end portion of the shaft center shaft portion 14m is extended to the vicinity of the discharge valve portion 90 provided on the center surface of the end plate on the opposite lap side. Is. With this structure, the dead volume at the discharge hole 10 can be further reduced. The discharge gas is of course the discharge hole 10
It will pass through the space between (10a, 10b) and the shaft center shaft portion 14m.
【００２８】ここで、図１３を用いて本発明の軸貫通式
スクロールの場合の圧縮作用を説明する。軸貫通式スク
ロールの場合、図１３に示すように、ラップ中央部に旋
回軸受部３１が有るためスクロールラップの巻き始め部
を旋回軸受部の外周部から設定している。このため、必
要な圧縮比Ｖｒを得るためには、スクロールラップの巻
き角度が大きくなり、その分スクロールラップの外径が
大きくなる。この欠点を補うため、図１に示すように、
固定スクロ−ルの巻き終わり部を従来の点（Ｖ）の位置
から点（Ｔ）の位置６３となる１８０度分ラップ巻き角
を延長し、これまで吸入室であった空間を無駄なく圧縮
室となるようにしている。Here, the compression action in the case of the shaft-through type scroll of the present invention will be described with reference to FIG. In the case of the shaft-penetrating scroll, as shown in FIG. 13, since the orbiting bearing portion 31 is provided in the central portion of the wrap, the winding start portion of the scroll wrap is set from the outer peripheral portion of the orbiting bearing portion. Therefore, in order to obtain the required compression ratio Vr, the winding angle of the scroll wrap increases, and the outer diameter of the scroll wrap increases accordingly. To compensate for this drawback, as shown in FIG.
The winding end of the fixed scroll is extended from the conventional position of point (V) to the position 63 of point (T) by a wrap wrap angle of 180 degrees, so that the space which was the suction chamber up to now is not wasted. I am trying to become.
【００２９】したがって、固定スクロ−ルの巻き終わり
部の内側曲線と、旋回スクロ−ルの巻き終わり部の外側
曲線とで囲まれる空間で、圧縮室（以後「旋回外線室」
と呼ぶ）を形成することになる。また、旋回スクロ−ル
の内側曲線と固定スクロ−ルの外側曲線により圧縮室
（以後「旋回内線室」と呼ぶ）を形成する。このよう
に、固定スクロールラップ内側曲線と旋回スクロールラ
ップ外側曲線とで形成される旋回外線室（圧縮室）８
ａ、８ｃ、８ｅがあり、固定スクロールラップ外側曲線
と旋回スクロールラップ内側曲線とで形成される旋回内
線室（圧縮室）８ｂ、８ｄを形成する。上記早期吐出口
６ｔ、吐出溝通路６ｐは、主に圧縮室８ｂ、８ｄから吐
出されるガスの通路となるものである。Therefore, in the space surrounded by the inner curve of the winding end portion of the fixed scroll and the outer curve of the winding end portion of the swirling scroll, the compression chamber (hereinafter referred to as "swirl outer line chamber") is formed.
Will be formed). A compression chamber (hereinafter referred to as "swirl extension chamber") is formed by the inner curve of the swirl scroll and the outer curve of the fixed scroll. In this way, the orbiting outer line chamber (compression chamber) 8 formed by the fixed scroll wrap inner curve and the orbiting scroll wrap outer curve
a, 8c and 8e, which form orbiting extension chambers (compression chambers) 8b and 8d formed by the fixed scroll wrap outer curve and the orbiting scroll wrap inner curve. The early discharge port 6t and the discharge groove passage 6p mainly serve as passages for gas discharged from the compression chambers 8b and 8d.
【００３０】図１４に示すように、旋回スクロール６の
鏡板背面に背圧室３６を設けている。また、図７に示す
ように、該背圧室３６に圧縮室内部のガス圧を導入する
絞り孔６ｄを旋回スクロールラップ外側曲線６ｓに沿っ
た位置の鏡板部に設けている。背圧室３６は、吸入圧力
と吐出圧力との中間圧力となる。その結果、旋回外線室
の理論押しのけ量（行程容積）は例えば、５馬力を想定
した場合、行程容積Ｖth1 ＝４３．０ｃｍ3 /rev で、
旋回内線室の場合はＶth2 ＝３７．０ｃｍ3 /revとな
り、１対の圧縮室の理論押しのけ量が異なる。言い替え
れば、Ｖth1 とＶth2 の比がＶth1 ／Ｖth2 ＝１．１〜
１．２前後の値となる。この場合、両側の圧縮室の吸入
開始する位置は、図１において点６３（Ｔ）と点６４
（Ｑ）の位置であり、吸入開始のタイミングは互いに回
転角にして１８０度ずれている。この圧縮機の固有圧縮
比Ｖｒは、巻き数で変わるものの、概ね、旋回外線室側
がＶr＝２．５前後に、旋回内線室側がＶr ＝２．３前
後となろう。As shown in FIG. 14, a back pressure chamber 36 is provided on the rear surface of the end plate of the orbiting scroll 6. Further, as shown in FIG. 7, a throttle hole 6d for introducing the gas pressure inside the compression chamber to the back pressure chamber 36 is provided in the end plate portion at a position along the outer curve 6s of the orbiting scroll wrap. The back pressure chamber 36 has an intermediate pressure between the suction pressure and the discharge pressure. As a result, the theoretical displacement (stroke volume) of the swirl line room is, for example, when assuming 5 horsepower, the stroke volume V th1 = 43.0 cm 3 / rev,
In the case of the swirling extension chamber, V th2 = 37.0 cm 3 / rev, and the theoretical displacement of the pair of compression chambers is different. In other words, the ratio of V th1 and V th2 is V th1 / V th2 = 1.1-
The value is around 1.2. In this case, the positions at which suction is started in the compression chambers on both sides are the points 63 (T) and 64 in FIG.
In the position (Q), the suction start timings are shifted from each other by 180 degrees in terms of rotation angle. Although the natural compression ratio Vr of this compressor varies depending on the number of turns, it will be about Vr = 2.5 on the side of the swirling outer line chamber and about Vr = 2.3 on the side of the swirling inner line chamber.
【００３１】本発明では、従来機での屈折通路がないの
で、吐出ポ−トの拡大構造の効果とあわせて、吐出圧力
損失が大きく低減できる。ひいては転覆モ−メントの作
用しない構造による旋回スクロ−ルの挙動の安定化によ
る圧縮室内部漏れの損失低減などの波及効果との相乗効
果により軸貫通方式のスクロ−ル圧縮機の性能が大幅に
向上できる。In the present invention, since there is no refraction passage in the conventional machine, the discharge pressure loss can be greatly reduced in addition to the effect of the enlarged structure of the discharge port. As a result, the performance of the scroll compressor of the shaft penetration type is greatly increased by the synergistic effect with the ripple effect such as the reduction of leakage loss in the compression chamber due to the stabilization of the behavior of the swirl scroll due to the structure without the overturning moment. Can be improved.
【００３２】図１４は、密閉形軸貫通スクロール圧縮機
の全体構造を示す縦断面図である。図１４において、密
閉容器１内の上方に圧縮機部１００が、下方に電動機部
３が収納されている。そして、密閉容器１内は上部室１
ａ（吐出室）と電動機室１ｂ、１ｃとに区画されてい
る。FIG. 14 is a vertical sectional view showing the entire structure of the hermetically sealed shaft-through scroll compressor. In FIG. 14, the compressor unit 100 is accommodated in the upper part of the closed container 1, and the electric motor unit 3 is accommodated in the lower part. And inside the closed container 1 is the upper chamber 1.
It is divided into a (discharge chamber) and electric motor chambers 1b and 1c.
【００３３】圧縮機部１００は固定スクロール部材５と
旋回スクロール部材６を互に噛合せて圧縮室（密閉空
間）７を形成している。固定スクロール部材５の中心部
に吐出孔１０、外周部に吸入口１６を備えている。フレ
ーム１１は中央部に主軸受部４０を形成し、この軸受部
に回転軸１４が支承され、回転軸先端の偏心軸１４ａ
は、上記旋回軸受部３１内に旋回運動が可能なように挿
入されている。圧縮室のガス圧で形成されるガス圧荷重
（ラジアル荷重）は軸受部３１と主軸受部４０と下軸受
部３２にて支持される。４６は補助フレ−ムである。な
お、１３３はシ−ル軸受部で油が電動機室１ｂ側に漏れ
るのを防止している。該シ−ル軸受部１３３では、主軸
１４の上下動を支えるスラスト軸受部１３４ａ（図１６
参照）と一体化しているツバツキ軸受構造としている。In the compressor section 100, the fixed scroll member 5 and the orbiting scroll member 6 are meshed with each other to form a compression chamber (closed space) 7. The fixed scroll member 5 is provided with a discharge hole 10 in the central portion and an intake port 16 in the outer peripheral portion. The frame 11 has a main bearing portion 40 formed in the center thereof, and the rotary shaft 14 is supported by this bearing portion, and the eccentric shaft 14a at the tip of the rotary shaft is
Are inserted in the swivel bearing portion 31 so that swivel motion is possible. The gas pressure load (radial load) formed by the gas pressure in the compression chamber is supported by the bearing portion 31, the main bearing portion 40, and the lower bearing portion 32. Reference numeral 46 is an auxiliary frame. A seal bearing portion 133 prevents oil from leaking to the electric motor chamber 1b side. In the seal bearing portion 133, a thrust bearing portion 134a that supports the vertical movement of the main shaft 14 (see FIG. 16).
(See) and has a camellia bearing structure.
【００３４】また、主軸１４の下端部にはスラスト軸受
部１３５を備え、該スラスト軸受部１３５は、主軸１４
と第一と第二のバランスウエイト８ａ、８ｂとロ−タ３
ｂなどの自重分を受け持つことになる。またフレーム１
１には固定スクロール部材５が複数本のボルトによって
固定され、旋回スクロール部材６はオルダムリングおよ
びオルダムキーよりなるオルダム機構１１２によってフ
レーム１１に支承され、旋回スクロール部材６は固定ス
クロール部材５に対して、自転しないで旋回運動をする
ように形成されている。A thrust bearing portion 135 is provided at the lower end of the main shaft 14, and the thrust bearing portion 135 is provided in the main shaft 14.
And the first and second balance weights 8a, 8b and the rotor 3
You will be responsible for the weight of b. Also frame 1
1, a fixed scroll member 5 is fixed by a plurality of bolts, the orbiting scroll member 6 is supported by a frame 11 by an Oldham mechanism 112 including an Oldham ring and an Oldham key, and the orbiting scroll member 6 is fixed to the fixed scroll member 5. It is formed so as to make a turning motion without rotating.
【００３５】主軸１４には下部に、ロータ３ｂに固定さ
れ、電動機部３を直結している。固定スクロール部材５
の吸入口１６には密閉容器１を貫通して垂直方向の吸入
管１７が接続され、吸入管１７と吸入口１６の間には、
逆止弁部１５が介在する。吐出口１０が開口している上
部室１ａは通路１８ａ、１８ｂを介して上部電動機室１
ｂと連通している。この上部電動室１ｂは電動機ステー
タ３ａと密閉容器１側壁との間の通路２１を介して下部
電動機室１ｃに連通している。また上部電動機室１ｂは
密閉容器１を貫通する吐出管２０に連通している。The lower portion of the main shaft 14 is fixed to the rotor 3b and is directly connected to the electric motor unit 3. Fixed scroll member 5
A vertical suction pipe 17 is connected to the suction port 16 of the penetrating the closed container 1, and between the suction pipe 17 and the suction port 16.
The check valve portion 15 is interposed. The upper chamber 1a where the discharge port 10 is open is connected to the upper electric motor chamber 1 through the passages 18a and 18b.
It communicates with b. The upper electric motor chamber 1b communicates with the lower electric motor chamber 1c via a passage 21 between the electric motor stator 3a and the side wall of the closed casing 1. Further, the upper electric motor chamber 1b communicates with a discharge pipe 20 penetrating the closed container 1.
【００３６】なお、下軸受部３２では球面すべり軸受構
造としている。また、そのシャフト下端部には、給油管
２３を内包するようにして、シャフト１４、ロ−タの自
重などを支えるコロガリタイプのスラスト軸受手段１３
５をそなえている。該スラスト軸受１３５での摺動速度
は最も小さくなる構成としているため、その部分のスラ
スト負荷による摩擦損失を極微に抑えることができる。The lower bearing portion 32 has a spherical plain bearing structure. At the lower end of the shaft, an oil supply pipe 23 is included to support the shaft 14, the weight of the rotor, and the like.
5 is provided. Since the sliding speed of the thrust bearing 135 is minimized, the friction loss due to the thrust load at that portion can be extremely suppressed.
【００３７】なお、２２は密閉容器底部の油溜りを示
す。なお、８ａと８ｂは、旋回スクロール６の旋回運動
に伴う遠心力を相殺するための第一と第二のバランスウ
エイトである。バランスウエイト８ａを電動機コイル部
３ｍの内周部と係合する位置に設定することにより、飛
散した油を電動機コイル部３ｍに衝突させて該電動機コ
イル部３ｍの冷却効果と油分離作用が得られる。次に潤
滑油の流れについて説明する。Reference numeral 22 denotes an oil sump at the bottom of the closed container. It should be noted that 8a and 8b are first and second balance weights for canceling the centrifugal force caused by the orbiting movement of the orbiting scroll 6. By setting the balance weight 8a at a position that engages with the inner peripheral portion of the electric motor coil portion 3m, the splashed oil collides with the electric motor coil portion 3m, and a cooling effect and an oil separating operation of the electric motor coil portion 3m are obtained. . Next, the flow of lubricating oil will be described.
【００３８】潤滑油２２ａは、密閉容器１の下部に油溜
り２２として溜められる。主軸1 ４には、各軸受部への
給油を行なうための中心縦孔１４７が主軸14の下端から
旋回軸受部付近まで形成される。２３は、主軸1 ４の下
端と底部油溜り２２を連ねる揚油管である。潤滑油２２
ａの油溜り２２内に浸漬けされた揚油管２３の下端は高
圧の吐出圧力Ｐｄを受けており、一方、下流となる旋回
軸受３１及び主軸受４０のまわりは、吐出圧の雰囲気に
あるも、シ−ル手段（シ−ルリング部、図１６参照）３
５の外側空間３６が、背圧室の圧縮途中の圧力である中
間圧力Ｐｍを受けているため、（Ｐｄ−Ｐｍ）の圧力差
によって、容器底部の油溜り２２中の潤滑油２２ａは、
中心縦孔１４７内を上昇する。このように、各軸受部へ
の給油を、中心縦孔給油による差圧給油法と複数の横孔
１４４ａ、１４４ｃによる遠心給油作用によって行な
う。The lubricating oil 22a is stored in the lower part of the closed container 1 as an oil sump 22. The main shaft 14 is formed with a central vertical hole 147 for supplying oil to each bearing portion from the lower end of the main shaft 14 to the vicinity of the orbiting bearing portion. Reference numeral 23 is a pumping oil pipe that connects the lower end of the main shaft 14 and the bottom oil sump 22. Lubricating oil 22
The lower end of the oil pumping pipe 23 immersed in the oil sump 22 of a receives the high discharge pressure Pd, while the surroundings of the slewing bearing 31 and the main bearing 40 on the downstream side are in the discharge pressure atmosphere. , Sealing means (sealing part, see FIG. 16) 3
Since the outer space 36 of 5 receives the intermediate pressure Pm which is the pressure in the middle of compression of the back pressure chamber, the lubricating oil 22a in the oil sump 22 at the bottom of the container is changed by the pressure difference of (Pd-Pm).
Ascending in the central vertical hole 147. As described above, the oil is supplied to each bearing by the differential pressure oil supply method by the central vertical hole oil supply and the centrifugal oil supply operation by the plurality of lateral holes 144a, 144c.
【００３９】なお、中心縦孔１４７内を上昇した潤滑油
２２ａは、主軸受４０及び旋回軸受３１へ給油され、旋
回軸受３１へ給油された油は、直接吐出孔１０側に流出
する。油圧室３９に給油された油は、内側シ−ルリング
３５を介して適量の油が背圧室３６に流入する。背圧室
３６に流入した油は、その部分の冷媒ガスと混合し、前
記絞り孔６ｄを介して圧縮室７、８ｃに移動する。The lubricating oil 22a rising in the central vertical hole 147 is supplied to the main bearing 40 and the slewing bearing 31, and the oil supplied to the slewing bearing 31 directly flows out to the discharge hole 10 side. An appropriate amount of oil supplied to the hydraulic chamber 39 flows into the back pressure chamber 36 via the inner seal ring 35. The oil that has flowed into the back pressure chamber 36 mixes with the refrigerant gas in that portion, and moves to the compression chambers 7 and 8c through the throttle hole 6d.
【００４０】圧縮室７などに至った油は、冷媒ガスとと
もに加圧され、冷媒ガスと油は、吐出孔１０を経て固定
スクロ−ル５上方の吐出室１ａにいたる。さらに連通路
１８を経て、電動機室１ｂへと移動する。この電動機室
１ｂと下方の空間１ｃで冷媒ガスと油はさらに分離さ
れ、油は密閉容器１の下部の油溜り２２に落下し、再び
各摺動部に供給される。このように、チャンバ底部の油
は、旋回軸受部へ供給され、ひいては吐出孔１０へ流れ
る経路と、油圧室から背圧室へ流れ、ひいては中間圧孔
を介して圧縮室へ流れる経路の２つの油流路を構成し、
極力圧縮室に油を注入しない構成としていることも特徴
点である。これは、背圧室への油を抑えることにより、
油による吸入室における加熱防止効果と圧縮過程での図
示効率向上などの効果が得られる作用があるからであ
る。また、主軸１４全体を転がり支持方式とすることに
より軸受隙間が微少に管理され、クランク軸系の軸方向
の挙動を安定化することができる。また圧縮機始動時の
油切れに対しては、少量の油でも軸受部での耐久性を確
保でき信頼性の面で有利となる。また、軸貫通スクロ−
ル圧縮機における主軸回りの挙動が安定化し、圧縮機の
信頼性が向上できる作用効果が得られる。The oil reaching the compression chamber 7 and the like is pressurized together with the refrigerant gas, and the refrigerant gas and the oil reach the discharge chamber 1a above the fixed scroll 5 through the discharge hole 10. Further, it passes through the communication passage 18 and moves to the electric motor room 1b. The refrigerant gas and the oil are further separated in the electric motor chamber 1b and the space 1c below, and the oil drops into the oil sump 22 at the lower part of the closed container 1 and is supplied again to each sliding portion. In this way, the oil at the bottom of the chamber is supplied to the slewing bearing, and thus flows to the discharge hole 10, and flows from the hydraulic chamber to the back pressure chamber, and thus to the compression chamber via the intermediate pressure hole. Constitutes the oil flow path,
Another feature is that the oil is not injected into the compression chamber as much as possible. This is because by suppressing the oil to the back pressure chamber,
This is because the effect of preventing heating in the suction chamber by oil and the effect of improving the drawing efficiency in the compression process can be obtained. In addition, since the entire main shaft 14 is of the rolling support type, the bearing clearance is controlled minutely and the behavior of the crankshaft system in the axial direction can be stabilized. Further, with respect to oil shortage at the time of starting the compressor, durability can be secured in the bearing portion even with a small amount of oil, which is advantageous in terms of reliability. In addition, shaft through scroll
The behavior around the main axis in the compressor is stabilized, and the operational effect of improving the reliability of the compressor can be obtained.
【００４１】図１５と図１６は、フレ−ム１１の平面図
と縦断面図である。フレ−ム１１の外周部には長方形の
通路１８ｂが周上に複数個設けている。フレーム１１の
中央部に主軸受部４０とガスシ−ル用軸受部３８を形成
している。１１ｇは内側シ−ルリング３５が挿入できる
環状溝部である。１１ｍはオルダムキ溝部である。１１
ｅは旋回鏡板背面部が摺接する台座部である。１１ｓは
固定スクロ−ル５をフレ−ム１１側にとめるためのネジ
孔部である。旋回スクロール部材６の鏡板６ａ背面の中
央部のフレ−ム１１と対向するスラスト部に内側シ−ル
リング３５を配している。該内側シ−ルリング３５の外
側領域を、吐出圧力（Ｐｄ）と吸入圧力（Ｐｓ）との中
間圧力とせしめるため、旋回スクロ−ル６の鏡板６ａを
貫通する絞り孔６ｄを設けている。15 and 16 are a plan view and a vertical sectional view of the frame 11. A plurality of rectangular passages 18b are provided on the outer periphery of the frame 11. A main bearing portion 40 and a gas seal bearing portion 38 are formed in the center of the frame 11. 11g is an annular groove portion into which the inner seal ring 35 can be inserted. 11m is Oldhamki groove. 11
Reference numeral e is a pedestal portion with which the back surface of the turning end plate is in sliding contact. 11s is a screw hole for fixing the fixed scroll 5 to the frame 11 side. An inner seal ring 35 is arranged in a thrust portion facing the frame 11 at the center of the rear surface of the end plate 6a of the orbiting scroll member 6. A throttle hole 6d penetrating the end plate 6a of the swivel scroll 6 is provided in order to make the outer region of the inner seal ring 35 have an intermediate pressure between the discharge pressure (Pd) and the suction pressure (Ps).
【００４２】旋回鏡板背面部とフレ−ム１１側の主軸受
部４０の間に油圧室３９を設け、該油圧室３９の高圧を
シ−ルするシ−ル軸受部１３３を上記油圧室３９と主軸
受部４０との間のフレ−ム内周部に設けている。旋回鏡
板背面の空間３９と電動機室とをシ−ルするシ−ル軸受
部１３３を、旋回スクロ−ル鏡板背面部と上記主軸受け
部との間にもうけるとともに、該シ−ル軸受部１３３に
は、電動機の磁気推力などのスラスト方向の軸荷重を支
えるつば付き部１３４ａを備えている。本構造により、
軸が上方向に移動しても該つば付き部１３４ａでささえ
る事ができる。また、主軸受部４０の周囲がガス域とな
って、転がり部によるかくはん損失が大きく低減でき
る。A hydraulic chamber 39 is provided between the rear portion of the swivel end plate and the main bearing 40 on the frame 11 side, and a seal bearing 133 for sealing the high pressure of the hydraulic chamber 39 is used as the hydraulic chamber 39. It is provided on the inner peripheral portion of the frame between the main bearing portion 40. A seal bearing portion 133 for sealing the space 39 on the rear surface of the swivel end plate and the electric motor chamber is provided between the rear portion of the swivel end plate and the main bearing portion, and the seal bearing portion 133 is provided. Includes a flanged portion 134a that supports axial load in the thrust direction such as magnetic thrust of the electric motor. With this structure,
Even if the shaft moves upward, it can be supported by the flanged portion 134a. Further, the periphery of the main bearing portion 40 becomes a gas region, and the stirring loss due to the rolling portion can be greatly reduced.
【００４３】なお、上述した軸貫通式スクロ−ル構造と
することにより、旋回スクロ−ルには転覆モ−メントが
作用しないため、旋回スクロ−ルの挙動の安定化が図ら
れ、圧縮室内部漏れの損失低減などの効果（特に、旋回
スクロ−ルの挙動の安定化は、内部漏れの影響を受けや
すい回転数の低い領域で顕著に性能改善効果がある。）
との相乗効果により本発明も軸貫通方式スクロ−ル圧縮
機の性能が大幅に向上できる。By adopting the above-described shaft-penetrating scroll structure, the overturning moment does not act on the orbiting scroll, so that the behavior of the orbiting scroll is stabilized and the inside of the compression chamber is stabilized. Effects such as reduction of leakage loss (In particular, stabilization of the behavior of the orbiting scroll has a remarkable effect of improving the performance in a low rotational speed region where internal leakage is easily affected.)
According to the synergistic effect with the present invention, the performance of the shaft penetration type scroll compressor can be greatly improved in the present invention.
【００４４】[0044]
【発明の効果】本発明によれば次の効果がある。The present invention has the following effects.
【００４５】（１）固定スクロールラップ側のラップ巻
き始め部では、ラップ部の曲率が大きくてもラップ部の
厚さを厚く、しかもラップ根元部を厚く設定しているた
め、ラップの径方向の倒れなどをちいさくし、ラップ強
度を向上できる。(1) At the wrap winding start portion on the fixed scroll wrap side, even if the wrap portion has a large curvature, the thickness of the wrap portion is set to be thick and the wrap base portion is set to be thick. The wrap strength can be improved by reducing the collapse.
【００４６】（２）吐出通路側での圧力損失と過圧縮動
力を小さくし、全断熱効率の向上が図れる。(2) The pressure loss and overcompression power on the discharge passage side can be reduced to improve the overall adiabatic efficiency.
【００４７】（３）吐出弁構造と死容積の縮小化構造の
組合せによって、スクロール圧縮機の外径寸法が制約さ
れた条件でも、必要な固有圧縮比がとれ、高圧力比条件
での、吐出孔からのガスの逆流による動力損失を極小に
抑え、効率が向上するという性能面で効果がある。ま
た、空調用途と冷凍機用途への圧縮機に共用化できると
いう使い勝って性も良くなる。(3) Due to the combination of the discharge valve structure and the dead volume reduction structure, even if the outer diameter of the scroll compressor is restricted, the required specific compression ratio can be obtained, and the discharge can be performed under the high pressure ratio condition. The power loss due to the backflow of gas from the holes is suppressed to a minimum, which is effective in improving efficiency. In addition, it is easy to use because it can be used as a compressor for air conditioning and refrigerator applications.
【００４８】（４）軸貫通スクロ−ル圧縮機における主
軸回りの挙動が安定化し、圧縮機の信頼性が向上でき
る。(4) The behavior around the main shaft in the shaft-through scroll compressor is stabilized, and the reliability of the compressor can be improved.
【００４９】（５）上記（１）項と（２）項と関連し
て、軸貫通方式の圧縮機構造により、旋回スクロ−ルの
鏡板変位が小さくなって、旋回スクロ−ルの傾きが小さ
くなる。このため、低い回転数域での性能向上効果と、
スラスト摺動面での片当たりの度合いが低下し、面圧も
低下して、その摺動部での潤滑性も改善され摺動部の摩
耗を抑え且つ焼き付きを未然に防止できる。(5) With respect to the above items (1) and (2), due to the axial penetrating compressor structure, the end plate displacement of the orbiting scroll is reduced, and the inclination of the orbiting scroll is reduced. Become. Therefore, the performance improvement effect in the low rotation speed range,
The degree of uneven contact on the thrust sliding surface is reduced, the surface pressure is also reduced, the lubricity at the sliding portion is also improved, the abrasion of the sliding portion can be suppressed, and seizure can be prevented in advance.
【図１】本発明によるスクロール圧縮機の固定スクロ−
ルの１実施例の平面図FIG. 1 shows a fixed scroll of a scroll compressor according to the present invention.
Plan view of one embodiment of
【図２】本発明によるスクロール圧縮機の固定スクロ−
ルの１実施例の縦断面図FIG. 2 is a fixed scroll of a scroll compressor according to the present invention.
1 is a vertical sectional view of one embodiment of
【図３】本発明によるスクロール圧縮機の１実施例の吐
出弁機能部の平面図FIG. 3 is a plan view of a discharge valve functional portion of one embodiment of the scroll compressor according to the present invention.
【図４】本発明によるスクロール圧縮機の１実施例の吐
出弁機能部の縦断面図FIG. 4 is a vertical cross-sectional view of a discharge valve functional portion of one embodiment of the scroll compressor according to the present invention.
【図５】本発明によるスクロール圧縮機の固定スクロ−
ルの１実施例の縦断面図FIG. 5 is a fixed scroll of a scroll compressor according to the present invention.
1 is a vertical sectional view of one embodiment of
【図６】本発明によるスクロール圧縮機の固定スクロ−
ルの実施例を示す図１のＡ〜Ｄに沿う断面図FIG. 6 is a fixed scroll of a scroll compressor according to the present invention.
1 is a cross-sectional view taken along the lines A to D of FIG.
【図７】本発明によるスクロール圧縮機の１実施例の旋
回スクロールの平面図FIG. 7 is a plan view of an orbiting scroll of one embodiment of the scroll compressor according to the present invention.
【図８】本発明によるスクロール圧縮機の１実施例の旋
回スクロールの縦断面図FIG. 8 is a vertical sectional view of an orbiting scroll of one embodiment of the scroll compressor according to the present invention.
【図９】本発明によるスクロール圧縮機の１実施例の旋
回スクロールの平面図FIG. 9 is a plan view of an orbiting scroll of one embodiment of the scroll compressor according to the present invention.
【図１０】本発明による１実施例の固定スクロ−ル中央
部のラップ組合せとなる周辺部の詳細を示す部分断面図FIG. 10 is a partial cross-sectional view showing details of a peripheral portion which is a lap combination of a fixed scroll central portion according to one embodiment of the present invention.
【図１１】本発明による１実施例の固定スクロ−ル中央
部のラップ組合せとなる周辺部を示す部分断面図FIG. 11 is a partial cross-sectional view showing a peripheral portion which is a lap combination of a central portion of a fixed scroll according to one embodiment of the present invention.
【図１２】本発明によるスクロール圧縮機の１実施例の
固定スクロ−ル中央部のラップ組合せとなる周辺部の詳
細を示す部分断面図FIG. 12 is a partial cross-sectional view showing details of a peripheral portion of a scroll compressor according to an embodiment of the present invention which is a lap combination of a fixed scroll central portion.
【図１３】本発明によるスクロール圧縮機の１実施例の
固定スクロール５と旋回スクロール６を組み合わせた横
断面図FIG. 13 is a cross-sectional view in which the fixed scroll 5 and the orbiting scroll 6 of one embodiment of the scroll compressor according to the present invention are combined.
【図１４】本発明による１実施例の密閉形スクロール圧
縮機の全体構造を示す縦断面図FIG. 14 is a vertical cross-sectional view showing the entire structure of a hermetic scroll compressor of one embodiment according to the present invention.
【図１５】本発明による１実施例のフレ−ムの平面図FIG. 15 is a plan view of a frame according to one embodiment of the present invention.
【図１６】本発明による１実施例のフレ−ムの縦断面図FIG. 16 is a vertical sectional view of a frame according to an embodiment of the present invention.
２ ： 密閉容器 ６ ： 旋回ス
クロ−ル ５ ： 固定スクロ−ル ５ａ、６ａ ：ス
クロ−ル鏡板部 １８： 連通路 ６ｄ： 絞り孔 ４０ ： 主軸受 ３１： 旋回軸受 ３３： スラスト軸受 １１： フレ−ム １０： 吐出孔2: Closed container 6: Swirl scroll 5: Fixed scroll 5a, 6a: Scroll end plate part 18: Communication passage 6d: Throttle hole 40: Main bearing 31: Slewing bearing 33: Thrust bearing 11: Frame 10: Discharge hole
Claims (7)
固定スクロール部材及び旋回スクロール部材を、ラップ
を内側にしてかみ合せ、旋回スクロール部材を自転する
ことなく固定スクロール部材に対し旋回運動させ、固定
スクロール部材には中心部に開口する吐出孔と外周部に
開口する吸入口を設け、吸入口よりガスを吸入し、両ス
クロール部材にて形成される圧縮空間を中心に移動させ
容積を減少してガスを圧縮し、固定スクロール部材を固
定するフレ−ムの中央部に主軸受部を備え、旋回スクロ
ール部材の中心部には旋回軸受部を設け、該旋回軸受部
にクランク軸の偏心軸部をラップ先端部まで挿入した軸
貫通スクロ−ル圧縮機において、旋回スクロ−ルの旋回
軸受部を構成する歯形の巻始め部を鏡板中心とする円弧
曲線とし、相対する固定スクロ−ルのラップ始端部のラ
ップ厚さを旋回側より厚くせしめるため、固定スクロ−
ルのラップ始点から内側曲線として大円弧曲線にて凹部
を形成し、外側曲線として小円弧曲線からなる凸部を形
成し、その外側をインボリュ−ト曲線で構成し、旋回ス
クロ−ルのラップ始点から外側曲線として大円弧曲線に
て凸部を形成し、内側曲線として半周を小円弧曲線から
なる凹部を形成し、その外側をインボリュ−ト曲線で構
成したラップ巻始め形状としたことを特徴とする軸貫通
スクロール圧縮機。1. A fixed scroll member and an orbiting scroll member which stand upright a spiral wrap on a disk-shaped end plate are engaged with each other with the wrap inside, and the orbiting scroll member is orbitally moved with respect to the fixed scroll member without rotating. , The fixed scroll member is provided with a discharge hole opening in the center and a suction port opening in the outer periphery, sucking gas from the suction port and moving it around the compression space formed by both scroll members to reduce the volume. The main bearing portion is provided in the center of the frame for compressing the gas to fix the fixed scroll member, the orbiting bearing portion is provided in the center of the orbiting scroll member, and the eccentric shaft of the crankshaft is attached to the orbiting bearing portion. In a shaft-penetrating scroll compressor in which the end portion is inserted to the wrap tip, the winding start portion of the tooth profile that constitutes the orbiting bearing portion of the orbiting scroll is made into an arc curve with the center of the end plate, and they face each other. In order to make the wrap thickness at the wrap start end of the fixed scroll thicker than the turning side, the fixed scroll
From the lap starting point of the roll, a concave part is formed as a large arc curve as an inner curve, a convex part consisting of a small arc curve is formed as an outer curve, and the outside is formed by an involute curve. From the above, a convex portion is formed as a large arc curve as an outer curve, and a concave portion formed of a small arc curve is formed as a semicircle as an inner curve, and a wrap winding start shape is formed on the outer side of the concave curve. Axial penetration scroll compressor.
固定スクロール部材及び旋回スクロール部材を、ラップ
を内側にしてかみ合せ、旋回スクロール部材を自転する
ことなく固定スクロール部材に対し旋回運動させ、固定
スクロール部材には中心部に開口する吐出孔と外周部に
開口する吸入口を設け、吸入口よりガスを吸入し、両ス
クロール部材にて形成される圧縮空間を中心に移動させ
容積を減少してガスを圧縮し、固定スクロール部材を固
定するフレ−ムの中央部に主軸受部を備え、旋回スクロ
ール部材の中心部には旋回軸受部を設け、該旋回軸受部
にクランク軸の偏心軸部をラップ先端部まで挿入した軸
貫通スクロ−ル圧縮機において、固定スクロ−ルの鏡板
中央部に大口径と小口径を有する段差を備えた吐出孔を
設けて死容積を減少せしめ、該小口径の吐出孔部の中心
が鏡板中心とほぼ一致し、反ラップ側の小口径吐出孔部
と対向した鏡板面に吐出弁機能部を備えたことを特徴と
する軸貫通スクロール圧縮機。2. A fixed scroll member and an orbiting scroll member, which stand upright with a spiral wrap on a disk-shaped end plate, are engaged with each other with the wrap inside, and the orbiting scroll member is orbitally moved with respect to the fixed scroll member without rotating. , The fixed scroll member is provided with a discharge hole opening in the center and a suction port opening in the outer periphery, sucking gas from the suction port and moving it around the compression space formed by both scroll members to reduce the volume. The main bearing portion is provided in the center of the frame for compressing the gas to fix the fixed scroll member, the orbiting bearing portion is provided in the center of the orbiting scroll member, and the eccentric shaft of the crankshaft is attached to the orbiting bearing portion. In a shaft-through scroll compressor in which the part is inserted to the tip of the wrap, the dead volume is reduced by providing a discharge hole with a step with a large diameter and a small diameter in the center of the end plate of the fixed scroll. At the very least, the center of the small-diameter discharge hole portion substantially coincides with the center of the end plate, and the end plate surface facing the small-diameter discharge hole portion on the opposite lap side is provided with a discharge valve function portion, which is a shaft-through scroll compression. Machine.
側曲線部の大円弧曲線部と外側曲線の小円弧曲線部のラ
ップ根本部に軸方向の大きな円弧形状もしくは面取り部
を形成し、該根本部の厚さをラップ先端部の厚さより厚
く設定し、旋回スクロ−ルのラップ中央部の外側曲線側
の大円弧曲線部と内側曲線の小円弧曲線部のラップ先端
部を軸方向の大きな円弧形状もしくは面取り部からなる
ラップ巻始め形状としたことを特徴とする請求項１記載
の軸貫通スクロール圧縮機。3. A large arc shape or chamfer in the axial direction is formed at the wrap root part of the large arc curve part of the inner curve part and the small arc curve part of the outer curve, which is the center part of the lap of the fixed scroll, and Set the thickness of the root part thicker than the thickness of the tip of the wrap, and make the wrap tip of the large arc curve part of the outer curve side and the small arc curve part of the inner curve of the wrap center part of the swivel scroll larger in the axial direction. 2. The shaft-penetrating scroll compressor according to claim 1, wherein the wrap winding start shape has an arc shape or a chamfered portion.
を固定スクロ−ル側に延長し、該軸心軸部の先端部が反
ラップ側の鏡板中央面に備えた吐出弁部近傍まで延長
し、吐出孔での死容積を減少せしめたことを特徴とする
請求項２記載の軸貫通スクロール圧縮機。4. The crankshaft further extends the shaft center shaft portion to the fixed scroll side at the tip of the eccentric shaft, and the tip end portion of the shaft center shaft portion is near the discharge valve portion provided on the center surface of the end plate on the side opposite to the lap. The shaft-through scroll compressor according to claim 2, wherein the dead volume at the discharge hole is reduced.
央面に吐出弁機能部を備え、該吐出弁に対向する固定鏡
板面側にテフロン系軟質材のシ−ト部材を上記吐出孔の
周辺部に充填したことを特徴とする請求項１記載の軸貫
通スクロール圧縮機。5. A discharge valve function portion is provided on the center surface of the end plate on the side opposite to the fixed scroll side of the lap side, and a sheet member made of Teflon-based soft material is provided on the side of the fixed end plate surface facing the discharge valve. The shaft-penetrating scroll compressor according to claim 1, wherein the compressor is filled in the peripheral portion of the shaft.
央面に吐出弁機能部を備え、該吐出弁の背面を支えるリ
テ−ナ部表面に、テフロン系軟質材もしくは軟質系固体
潤滑剤をコ−ティングしたことを特徴とする請求項１記
載の軸貫通スクロール圧縮機。6. A Teflon-based soft material or a soft solid lubricant is provided on a surface of a retainer, which supports a rear surface of the discharge valve, on a central surface of an end plate on the side opposite to the fixed scroll and on which the end plate is provided. The shaft-penetrating scroll compressor according to claim 1, wherein the shaft-through scroll compressor is coated.
の円弧部の半径Ｒ5をラップ外周部におけるラップ根本
部の円弧部の半径Ｒ6 に対して、その比であるＲ5 ／Ｒ
6 ＝２倍から５倍前後に設定することを特徴とする請求
項３記載の軸貫通スクロール圧縮機。7. A ratio R 5 / R of the radius R 5 of the arc portion of the lap root portion in the central portion of the scroll wrap to the radius R 6 of the arc portion of the lap root portion in the outer periphery of the wrap.
6. The shaft-through scroll compressor according to claim 3, wherein 6 = 2 to 5 times or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07036698A JP3110970B2 (en) | 1995-02-24 | 1995-02-24 | Shaft penetrating scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07036698A JP3110970B2 (en) | 1995-02-24 | 1995-02-24 | Shaft penetrating scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08232863A true JPH08232863A (en) | 1996-09-10 |
| JP3110970B2 JP3110970B2 (en) | 2000-11-20 |
Family
ID=12477005
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07036698A Expired - Fee Related JP3110970B2 (en) | 1995-02-24 | 1995-02-24 | Shaft penetrating scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3110970B2 (en) |
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| EP3990785B1 (en) | 2019-07-30 | 2024-10-30 | Samsung Electronics Co., Ltd. | Scroll compressor |
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1995
- 1995-02-24 JP JP07036698A patent/JP3110970B2/en not_active Expired - Fee Related
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| KR100971578B1 (en) * | 2002-05-15 | 2010-07-20 | 파나소닉 주식회사 | Scroll compressor |
| JP2008002387A (en) * | 2006-06-23 | 2008-01-10 | Toshiba Kyaria Kk | Refrigerant compressor and refrigeration cycle device using same |
| JP2008121481A (en) * | 2006-11-10 | 2008-05-29 | Matsushita Electric Ind Co Ltd | Scroll fluid machine |
| CN102192145A (en) * | 2010-03-10 | 2011-09-21 | 日立空调·家用电器株式会社 | Vortex type fluid machine and assembling method thereof |
| JP2011185208A (en) * | 2010-03-10 | 2011-09-22 | Hitachi Appliances Inc | Scroll fluid machine and method of assembling the same |
| KR101277414B1 (en) * | 2010-03-10 | 2013-06-20 | 히타치 어플라이언스 가부시키가이샤 | Scroll fluid machine and assembling method thereof |
| JP2012189079A (en) * | 2011-03-09 | 2012-10-04 | Lg Electronics Inc | Scroll compressor |
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| CN103291617A (en) * | 2012-02-29 | 2013-09-11 | 日立空调·家用电器株式会社 | Scroll compressor and air conditioner |
| US20130219950A1 (en) * | 2012-02-29 | 2013-08-29 | Hitachi Appliances, Inc. | Scroll Compressor and Air Conditioner |
| US10190586B2 (en) | 2012-02-29 | 2019-01-29 | Hitachi-Johnson Controls Air Conditioning, Inc. | Scroll compressor and air conditioner |
| CN102927012B (en) * | 2012-11-21 | 2015-04-22 | 霍勇贤 | Scroll plate structure |
| CN102927012A (en) * | 2012-11-21 | 2013-02-13 | 霍勇贤 | Scroll plate structure |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3110970B2 (en) | 2000-11-20 |
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