JPH06147162A - Closed rotary compressor - Google Patents
Closed rotary compressorInfo
- Publication number
- JPH06147162A JPH06147162A JP32149892A JP32149892A JPH06147162A JP H06147162 A JPH06147162 A JP H06147162A JP 32149892 A JP32149892 A JP 32149892A JP 32149892 A JP32149892 A JP 32149892A JP H06147162 A JPH06147162 A JP H06147162A
- Authority
- JP
- Japan
- Prior art keywords
- discharge hole
- cylinder
- bore
- cut
- roller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は密閉型回転圧縮機、詳し
くは冷凍空調機器全般に搭載される密閉型回転圧縮機に
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic rotary compressor, and more particularly to a hermetic rotary compressor mounted on refrigeration and air conditioning equipment in general.
【0002】[0002]
【従来の技術】まず、従来の密閉型回転圧縮機の基本構
造について、後述する実施例を示す図1を参照して説明
する。図1には密閉型回転圧縮機の全体構成が示されて
おり、1は密閉容器であり、密閉容器1内には電動要素
2及び圧縮要素3が収容されている。そして、圧縮要素
3は、内側にボア4aを有するシリンダ4と、回転軸5
の偏心部6によってシリンダ4内を偏心回転するローラ
7と、シリンダ4のボア4aを封じる上枠体11及び下
枠体12と、シリンダ4の案内溝に滑動係合するベーン
(図示せず)とで構成されている。ローラ7は偏心部6
の外周面に緩く嵌め合わされており、シリンダ4の内周
面に沿って偏心回転するようになっている。又、上枠体
11にはシリンダ4内に連通する吐出孔13が設けら
れ、シリンダ4には吸込口(図示せず)が設けられてい
る。次に、上述の密閉型回転圧縮機の作動については、
電動要素2の回転軸5の偏心部6によってローラ7がシ
リンダ4内を偏心回転し、一方、シリンダ4の内周面と
ローラ7の外周面との間に形成される空間は、ローラ7
に追従して摺動するベーンによって吸込室(低圧)と圧
縮室(高圧)とに仕切られており、吸込口から吸い込ま
れたガスはローラ7の偏心回転によって圧縮されるので
ある。圧縮されたガスは、吐出孔13、吐出弁14、吐
出マフラー15を経て吐出口16から吐出される。上述
のような構造の密閉型回転圧縮機の吐出孔13の径の大
小は圧縮効率に大きく影響し、吐出孔径が大のものは再
膨張損失を大きくし、吐出孔径が小のものは過圧縮損失
を大きくする。そこで、最適吐出孔径はこれらの圧縮損
失(再膨張損失+過圧縮損失)を考慮して決めている。2. Description of the Related Art First, the basic structure of a conventional hermetic rotary compressor will be described with reference to FIG. FIG. 1 shows the overall structure of a hermetic rotary compressor, in which 1 is a hermetic container, and an electric element 2 and a compression element 3 are housed in the hermetic container 1. The compression element 3 includes a cylinder 4 having a bore 4a inside and a rotating shaft 5
A roller 7 that eccentrically rotates in the cylinder 4 by the eccentric portion 6, an upper frame body 11 and a lower frame body 12 that seal the bore 4a of the cylinder 4, and a vane that slidably engages with the guide groove of the cylinder 4 (not shown). It consists of and. Roller 7 is eccentric part 6
Is loosely fitted to the outer peripheral surface of the cylinder 4, and is eccentrically rotated along the inner peripheral surface of the cylinder 4. Further, the upper frame 11 is provided with a discharge hole 13 communicating with the inside of the cylinder 4, and the cylinder 4 is provided with a suction port (not shown). Next, regarding the operation of the above-mentioned hermetic rotary compressor,
The roller 7 is eccentrically rotated in the cylinder 4 by the eccentric portion 6 of the rotary shaft 5 of the electric element 2, while the space formed between the inner peripheral surface of the cylinder 4 and the outer peripheral surface of the roller 7 is
It is divided into a suction chamber (low pressure) and a compression chamber (high pressure) by a vane that follows and slides, and the gas sucked from the suction port is compressed by the eccentric rotation of the roller 7. The compressed gas is discharged from the discharge port 16 through the discharge hole 13, the discharge valve 14, and the discharge muffler 15. In the hermetic rotary compressor having the above-described structure, the diameter of the discharge hole 13 has a large influence on the compression efficiency, the discharge hole having a large diameter has a large re-expansion loss, and the discharge hole having a small diameter has an excessive compression. Increase loss. Therefore, the optimum discharge hole diameter is determined in consideration of these compression losses (reexpansion loss + overcompression loss).
【0003】[0003]
【発明が解決しようとする課題】ところが、上記の圧縮
損失については、さらに改善して性能を向上させる余地
がないかという課題があった。However, there is a problem in that there is room to further improve the compression loss to improve the performance.
【0004】[0004]
【課題を解決するための手段】本発明では、上記の圧縮
損失を改善して性能を向上させるために、密閉容器内に
収納される電動要素と圧縮要素とが備えられ、前記圧縮
要素は内側にボアを有するシリンダと、回転軸の偏心部
によって前記シリンダの内壁に沿って回転するローラ
と、このローラに接してシリンダのボアを高圧室及び低
圧室に区画するベーンと、前記シリンダのボアを封じる
枠体とで構成され、前記枠体には吐出孔が、前記シリン
ダには切欠きが設けられ、前記ボアの高圧室で圧縮され
た冷媒を吐出する通路を前記吐出孔と前記切欠きとで形
成している密閉型回転圧縮機であって、前記切欠きを前
記吐出孔より小さく形成し、かつ、前記切欠きは吐出孔
側よりボア側の開口端を大きく形成するように構成し
た。According to the present invention, in order to improve the compression loss and improve the performance, an electric element and a compression element housed in a closed container are provided, and the compression element is an inner side. A cylinder having a bore, a roller that rotates along the inner wall of the cylinder by an eccentric portion of the rotating shaft, a vane that is in contact with the roller and divides the bore of the cylinder into a high pressure chamber and a low pressure chamber, and a bore of the cylinder. A frame for sealing, the frame has a discharge hole, the cylinder has a cutout, and a passage for discharging the refrigerant compressed in the high pressure chamber of the bore is provided with the discharge hole and the cutout. The hermetically sealed rotary compressor is formed so that the cutout is smaller than the discharge hole, and the cutout has a larger opening end on the bore side than on the discharge hole side.
【0005】[0005]
【作用】密閉型回転圧縮機の最適吐出孔径は、前述のよ
うに、過圧縮損失と再膨張損失の関係で決まり、吐出孔
径大は過圧縮損失を小さくし、吐出孔径小は再膨張損失
を小さくする。そこで、本発明による吐出孔及び切欠き
は下記のように作用する。バルブの板厚を変更せずに強
度的に安全な径まで最適吐出孔径を大きくすることによ
って過圧縮損失が小さくなる。吐出孔径を大きくすると
再膨張損失が大きくなるので、切欠きの幅を小さくする
ことによって再膨張損失が小さくなる。切欠きの幅を小
さくすると圧縮ガスの流れが悪くなるので、切欠きは吐
出孔側よりボア側の開口端を大きく形成することによっ
て圧縮ガスの流れがよくなる。As described above, the optimum discharge hole diameter of the hermetic rotary compressor is determined by the relationship between overcompression loss and reexpansion loss. A large discharge hole diameter reduces the overcompression loss, and a small discharge hole diameter reduces the reexpansion loss. Make it smaller. Therefore, the discharge hole and the notch according to the present invention operate as follows. Overcompression loss is reduced by increasing the optimum discharge hole diameter to a diameter that is safe in terms of strength without changing the valve plate thickness. Since the re-expansion loss increases as the discharge hole diameter increases, the re-expansion loss decreases by reducing the width of the notch. If the width of the notch is reduced, the flow of the compressed gas becomes worse. Therefore, the flow of the compressed gas is improved by forming the opening end of the notch larger on the bore side than on the discharge hole side.
【0006】[0006]
【実施例】以下、本発明による密閉型回転圧縮機の実施
例について、図1乃至図4を参照して説明する。図1は
本発明による密閉型回転圧縮機の縦断正面図、図2は図
1に含まれるシリンダの切欠きの部分を示す断面平面
図、図3(A)は図2に示されるシリンダの切欠き部分
の断面平面図、図3(B)は図3(A)の断面正面図、
図4は図2のA−A線断面図である。図1には密閉型回
転圧縮機の全体構成が示されており、その基本構成につ
いては従来の技術の項で説明したのと同じであるため、
説明は省略する。本発明においては、吐出部における圧
縮効率を向上させるために、上述の基本構成に新たに切
欠き17が設けられている。Embodiments of the hermetic rotary compressor according to the present invention will be described below with reference to FIGS. 1 to 4. FIG. 1 is a vertical sectional front view of a hermetic rotary compressor according to the present invention, FIG. 2 is a sectional plan view showing a cutout portion of a cylinder included in FIG. 1, and FIG. 3A is a sectional view of the cylinder shown in FIG. 3B is a cross-sectional plan view of the cutout portion, FIG. 3B is a cross-sectional front view of FIG.
FIG. 4 is a sectional view taken along the line AA of FIG. FIG. 1 shows the overall configuration of the hermetic rotary compressor, and the basic configuration thereof is the same as that described in the section of the related art.
The description is omitted. In the present invention, in order to improve the compression efficiency in the discharge part, the notch 17 is newly provided in the above-mentioned basic configuration.
【0007】以下その切欠き17について詳述する。 過圧縮損失を小さくするために、バルブの板厚を変更
せずに強度的に安全な径まで最適吐出孔径dを大きくす
る(図2参照)。 吐出孔の内径を大きくすると、再膨張損失が大きくな
るので、これを小さくするために切欠き17の幅を小さ
くする(吐出孔13の内径dと切欠き17の幅wとの比
を1:0.5〜0.8にする。図3参照)。 切欠き17の幅wを小さくすると圧縮ガスの流れが悪
くなるので、流れをよくするために切欠き17の角度を
大きくする(シングル吐出の場合、深さdに対する高さ
hの比を1:2.4〜2.8にする。図4参照)。 上記により、吐出部における圧縮効率の改善が図られ性
能が向上する。The notch 17 will be described in detail below. In order to reduce the over-compression loss, the optimum discharge hole diameter d is increased to a safe diameter without changing the plate thickness of the valve (see FIG. 2). When the inner diameter of the discharge hole is increased, the re-expansion loss is increased. Therefore, the width of the notch 17 is reduced to reduce the loss (the ratio of the inner diameter d of the discharge hole 13 to the width w of the notch 17 is 1: 0.5 to 0.8, see FIG. 3). If the width w of the notch 17 is reduced, the flow of the compressed gas becomes worse. Therefore, the angle of the notch 17 is increased to improve the flow (in the case of single discharge, the ratio of the height h to the depth d is 1: 2.4-2.8, see FIG. 4). By the above, the compression efficiency in the discharge part is improved and the performance is improved.
【0008】次に、本発明の作用効果を示す実験結果を
以下に記す。実験条件は次のとおりである。 蒸発温度 7.2℃ 凝縮温度 54.4℃ 雰囲気温度 35.0℃ この場合の実験結果は次のようになり、本発明の方が従
来のものより優れていることが確認された。 冷凍能力 入力 EER Kcal/h W Kcal/h 本発明 4678 1686 2.77 従 来 4638 1720 2.70 この実験結果から、本発明の次の特長が考察される。 冷凍能力は切欠きを小さくして残留冷媒量が少なくな
るようにしたことから向上した。 入力はシリンダのボアから切欠きに冷媒が流れやすく
なったことから少なくてすむようになった。Next, experimental results showing the action and effect of the present invention will be described below. The experimental conditions are as follows. Evaporation temperature 7.2 ° C Condensation temperature 54.4 ° C Ambient temperature 35.0 ° C The experimental results in this case are as follows, and it was confirmed that the present invention is superior to the conventional one. Refrigeration capacity input EER Kcal / h W Kcal / h The present invention 4678 1686 2.77 Conventional 4638 1720 2.70 From the results of this experiment, the following features of the present invention are considered. The refrigerating capacity was improved by reducing the notches to reduce the amount of residual refrigerant. The input was reduced because the refrigerant could easily flow from the cylinder bore into the notch.
【0009】[0009]
【発明の効果】本発明による密閉型回転圧縮機は、上述
のように構成されているので、下記の効果がある。 切欠きを吐出孔より小さく形成することにより、この
切欠きに残留する圧縮冷媒量を少なくでき、冷凍能力の
低下を防止できる。 切欠きは吐出口側よりボア側の開口端を大きくするこ
とにより、高圧室から切欠きに圧縮冷媒が流れやすくで
き、吐出行程時の入力の増加を防止できる。Since the hermetic rotary compressor according to the present invention is constructed as described above, it has the following effects. By forming the cutout smaller than the discharge hole, it is possible to reduce the amount of compressed refrigerant remaining in the cutout and prevent a reduction in the refrigerating capacity. By making the opening end of the notch on the bore side larger than the discharge port side, the compressed refrigerant can easily flow from the high pressure chamber to the notch, and an increase in the input during the discharge stroke can be prevented.
【図1】本発明による密閉型回転圧縮機の実施例の縦断
正面図である。FIG. 1 is a vertical sectional front view of an embodiment of a hermetic rotary compressor according to the present invention.
【図2】図1に含まれるシリンダの切欠きの部分を示す
断面平面図である。FIG. 2 is a cross-sectional plan view showing a cutout portion of the cylinder included in FIG.
【図3】図2に示されるシリンダの切欠きの部分を示す
もので、(A)は断面平面図、(B)は(A)の断面正
面図である。3A and 3B show a notch portion of the cylinder shown in FIG. 2, where FIG. 3A is a sectional plan view and FIG. 3B is a sectional front view of FIG.
【図4】図2のA−A線断面図である。4 is a cross-sectional view taken along the line AA of FIG.
1 密閉容器 2 電動要素 3 圧縮要素 4 シリンダ 5 回転軸 6 偏心部 7 ローラ 11 上枠体 12 下枠体 13 吐出孔 14 吐出弁 15 吐出マフラー 16 吐出口 17 切欠き 1 Airtight Container 2 Electric Element 3 Compression Element 4 Cylinder 5 Rotating Shaft 6 Eccentric Part 7 Roller 11 Upper Frame 12 Lower Frame 13 Discharge Hole 14 Discharge Valve 15 Discharge Muffler 16 Discharge Port 17 Notch
Claims (1)
要素とが備えられ、前記圧縮要素は内側にボアを有する
シリンダと、回転軸の偏心部によって前記シリンダの内
壁に沿って回転するローラと、このローラに接してシリ
ンダのボアを高圧室及び低圧室に区画するベーンと、前
記シリンダのボアを封じる枠体とで構成され、前記枠体
には吐出孔が、前記シリンダには切欠きが設けられ、前
記ボアの高圧室で圧縮された冷媒を吐出する通路を前記
吐出孔と前記切欠きとで形成している密閉型回転圧縮機
であって、前記切欠きは前記吐出孔より小さく形成さ
れ、かつ、前記切欠きは吐出孔側よりボア側の開口端が
大きく形成されていることを特徴とする密閉型回転圧縮
機。1. A cylinder provided with an electric element and a compression element housed in a closed container, the compression element having a bore inside, and a roller rotating along an inner wall of the cylinder by an eccentric portion of a rotation shaft. A vane that contacts the roller and divides the bore of the cylinder into a high-pressure chamber and a low-pressure chamber, and a frame that seals the bore of the cylinder.The frame has a discharge hole and the cylinder has a notch. A hermetic rotary compressor in which a passage for discharging the refrigerant compressed in the high pressure chamber of the bore is formed by the discharge hole and the cutout, the cutout being smaller than the discharge hole. The hermetically sealed rotary compressor is characterized in that the cutout is formed such that the opening end on the bore side is larger than the discharge hole side.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32149892A JPH06147162A (en) | 1992-11-06 | 1992-11-06 | Closed rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32149892A JPH06147162A (en) | 1992-11-06 | 1992-11-06 | Closed rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH06147162A true JPH06147162A (en) | 1994-05-27 |
Family
ID=18133235
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP32149892A Pending JPH06147162A (en) | 1992-11-06 | 1992-11-06 | Closed rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH06147162A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1997012148A1 (en) * | 1995-09-28 | 1997-04-03 | Daikin Industries, Ltd. | Rotary compressor |
CN107120279A (en) * | 2017-06-30 | 2017-09-01 | 广东美芝制冷设备有限公司 | Compressor and the refrigerating plant with it |
CN107202010A (en) * | 2017-06-30 | 2017-09-26 | 广东美芝制冷设备有限公司 | Compressor and the refrigerating plant with it |
-
1992
- 1992-11-06 JP JP32149892A patent/JPH06147162A/en active Pending
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1997012148A1 (en) * | 1995-09-28 | 1997-04-03 | Daikin Industries, Ltd. | Rotary compressor |
EP0851125A1 (en) * | 1995-09-28 | 1998-07-01 | Daikin Industries, Limited | Rotary compressor |
EP0851125A4 (en) * | 1995-09-28 | 2000-02-23 | Daikin Ind Ltd | Rotary compressor |
US6077058A (en) * | 1995-09-28 | 2000-06-20 | Daikin Industries, Ltd. | Rotary compressor |
KR100338266B1 (en) * | 1995-09-28 | 2002-10-25 | 다이킨 고교 가부시키가이샤 | Rotary compressor |
CN107120279A (en) * | 2017-06-30 | 2017-09-01 | 广东美芝制冷设备有限公司 | Compressor and the refrigerating plant with it |
CN107202010A (en) * | 2017-06-30 | 2017-09-26 | 广东美芝制冷设备有限公司 | Compressor and the refrigerating plant with it |
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