KR0149972B1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- KR0149972B1 KR0149972B1 KR1019950014026A KR19950014026A KR0149972B1 KR 0149972 B1 KR0149972 B1 KR 0149972B1 KR 1019950014026 A KR1019950014026 A KR 1019950014026A KR 19950014026 A KR19950014026 A KR 19950014026A KR 0149972 B1 KR0149972 B1 KR 0149972B1
- Authority
- KR
- South Korea
- Prior art keywords
- scroll
- crankshaft
- eccentric shaft
- frame
- shaft portion
- 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 - Fee Related
Links
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- 238000003754 machining Methods 0.000 description 4
- 238000007796 conventional method Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
- F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
크랭크축(4)을 편심축부(4a)로부터 구동원(3)과 결합한 측에서 지지하고, 또 크랭크축 선단부는 선회스크롤(6)이 랩 선단면 보다도 스크롤의 경판측에 있게한 구조로 했다.The crankshaft 4 was supported by the eccentric shaft part 4a by the side which couple | bonded with the drive source 3, and the crankshaft front end part was made into the structure which made the turning scroll 6 more in the hard board side of a scroll than the lap | tip end surface.
본 발명에 의하면 크랭크축의 편심축부 지름을 필요 최소한으로 억제할 수가 있어, 압축기의 소형화가 도모되고, 또 토출포트의 유로저항을 작게할 수가 있어 높은 효율을 얻을 수가 있다.According to the present invention, the diameter of the eccentric shaft portion of the crankshaft can be minimized to the minimum, the compactness of the compressor can be achieved, and the flow resistance of the discharge port can be reduced, and high efficiency can be obtained.
Description
제1도는 본 발명의 일 실시예를 나타낸 압축기 전체의 종단면도.1 is a longitudinal sectional view of the entire compressor showing one embodiment of the present invention.
제2도는 본 발명의 일 실시예를 나타낸 부분 단면도.2 is a partial cross-sectional view showing an embodiment of the present invention.
제3도는 본 발명의 일 실시예를 나타낸 크랭크축의 정면도.3 is a front view of the crankshaft showing an embodiment of the present invention.
제4도는 종래의 방법을 나타낸 부분 단면도.4 is a partial cross-sectional view showing a conventional method.
제5도는 종래의 방법에 의한 크랭크축의 부분 정면도.5 is a partial front view of the crankshaft by the conventional method.
* 도면의 주요부분에 대한 부호의 설명* Explanation of symbols for main parts of the drawings
1 : 케이싱 2 : 압축기구부1: Casing 2: Compressor
3 : 전동기 4 : 크랭크축3: electric motor 4: crankshaft
4a : 편심축부 5 : 프레임4a: eccentric shaft portion 5: frame
5b : 시일링 6 : 선회스크롤5b: sealing 6: turning scroll
6a : 경판부(평판부) 6b : 랩부6a: hard plate part (flat plate part) 6b: wrap part
6c : 보스부 7 : 고정스크롤6c: boss portion 7: fixed scroll
8 : 자전방지기구 9 : 급유통로8: anti-rotation mechanism 9: oil supply passage
10 : 급유파이프 11 : 중간압실10: oil supply pipe 11: intermediate pressure chamber
12 : 흡입관 13 : 토출관12 suction tube 13 discharge tube
15 : 토출포트 17 : 카운터웨이트15: discharge port 17: counterweight
19 : 연장축심축부 21 : 편심축부19: extended shaft center portion 21: eccentric shaft portion
본 발명은 축 관통식 스크롤 압축기에 관한 것으로, 특히 공조기 및 냉동기용의 냉매압축기, 기타 팽창기 또는 공기 압축기에 가장 적합한 축관통식 스크롤 압축기에 관한 것이다.The present invention relates to a through shaft scroll compressor, and more particularly to a through shaft scroll compressor most suitable for refrigerant compressors, other expanders or air compressors for air conditioners and refrigerators.
종래의 축관통식 스크롤 압축기로서는 일본국 특개 소57-131896호에 기재된 바와 같이, 선회스크롤내의 압축가스에 의한 래디알 하중점검과, 크랭크축 편심축부의 지지점을 일치시킴으로써 선회스크롤에 전복 모멘트가 발생하지 않게 하고, 압축기의 성능을 향상시키기 위하여 그 크랭크축의 편심축을 선회스크롤 랩 선단부까지 삽입함과 동시에, 편심축 선단에 다시 축심축부를 토출구멍을 통하여 연장하고, 고정스크롤에 상기 연장축심 축부를 지지하는 베어링부를 형성한 구조의 것이 있다.As a conventional shaft-through scroll compressor, as described in Japanese Patent Application Laid-Open No. 57-131896, the overload moment is not generated in the swing scroll by matching the radial load check by the compressed gas in the swing scroll with the support point of the crankshaft eccentric shaft portion. In order to improve the performance of the compressor, the eccentric shaft of the crankshaft is inserted to the turning scroll wrap tip, and the axial shaft section is extended through the discharge hole at the tip of the eccentric shaft, and the extension shaft shaft section is supported on the fixed scroll. There is a structure having a bearing portion.
상기 공지기술에서는 연장축심축경은 편심축경에 비하여 작게 설계할 필요가 있다.In the known art, it is necessary to design the extension shaft axis diameter smaller than the eccentric shaft diameter.
즉, 제5도에 있어서, 연장축심축부(19)의 지름(D1), 편심축부(21)의 지름(D2), 그들간의 갭(G) 및 선회방경(E)라 하면, 편심축부(21)의 지름은,That is, in FIG. 5, the diameter D 1 of the extended axial shaft 19, the diameter D 2 of the eccentric shaft 21, the gap G therebetween, and the turning radius E are eccentric shafts. The diameter of 21 is
로 할 필요가 있다. 이 때문에 고정스크롤에 형성된 베어링부 면압의 규정치를 확보하고, 또한 크랭크축에 가공상 필요한 충분한 강성을 가지게 하여, 가공정밀도를 유지하도록 연장축심축경(D1)을 정하면, 식 (1)로부터 편심축경(D2)의 최소치가 결정된다. 이 때문에 편심축경은 그 편심축부(22)의 면압의 기준치 단독으로는 선정할 수 없고 연장축심축부지름(D1)의 제약으로부터 편심축경을 필요이상으로 크게 하는 경우가 발생한다. 따라서, 선회스크롤 중앙부의 선회베어링 보스부(6C)가 커져 필요 압축비를 얻도록 스크롤랩을 설치하면, 중앙부분의 최대압축실의 치수가 커지게 되므로, 스크롤부재의 외경이 커지고, 그에 따라 압축기 전체의 외경이 커져버린다는 문제가 있었다.You need to. For this reason, when the extension shaft axle diameter D 1 is determined so as to secure a prescribed value of the bearing portion surface pressure formed on the fixed scroll, and to have sufficient rigidity for machining on the crankshaft, and to maintain the machining accuracy, the eccentric shaft diameter is determined from Equation (1). The minimum value of (D 2 ) is determined. For this reason, the eccentric shaft diameter cannot be selected solely by the reference value of the surface pressure of the eccentric shaft portion 22, and the eccentric shaft diameter may be made larger than necessary due to the constraint of the extended axial shaft diameter D 1 . Therefore, when the scroll wrap is provided such that the swing bearing boss portion 6C of the swing scroll center portion is enlarged to obtain the required compression ratio, the size of the maximum compression chamber at the center portion is increased, so that the outer diameter of the scroll member is increased, and thus the entire compressor. There was a problem that the outer diameter of the.
또, 연장축심 베어링 면압을 확보하도록 베어링폭을 크게 하거나, 혹은 베어링 하중을 저감시키도록 베어링과 선회스크롤의 압축가스 하중점과의 거리를 크게 하는 것도 가능하나, 이 경우, 그 연장축심축 부분을 길게 할 필요가 생겨, 충분한 강도를 유지하는 것이 곤란하다는 문제도 있었다.It is also possible to increase the bearing width to secure the extended shaft bearing surface pressure, or to increase the distance between the bearing and the compressed gas load point of the swing scroll to reduce the bearing load. There was a problem that it was necessary to lengthen, and it was difficult to maintain sufficient strength.
또, 상기 공지기술에서는 연장축심축부는 고정스크롤에 설치된 토출구멍의 내측을 관통시키는 구조이기 때문에, 토출유로의 저항이 커져 높은 효율이 얻어지지 않는다는 문제가 있었다.In addition, in the above-mentioned known technology, since the extended shaft core portion penetrates the inside of the discharge hole provided in the fixed scroll, there is a problem that the resistance of the discharge flow path becomes large and high efficiency is not obtained.
본 발명은 이러한 문제에 감안하여 이루어진 것으로, 그 목적은 선회스크롤에 전복 모멘트가 작용하지 않는 축관통식의 구조이고, 또한 압축기의 소형화를 도모할 수가 있는 축관통식 스크롤 압축기를 제공하는데 있다. 또 본 발명의 다른 목적은 토출유로 저항이 작은 고효율의 축관통식 스크롤 압축기를 제공하는데 있다.SUMMARY OF THE INVENTION The present invention has been made in view of such a problem, and an object thereof is to provide a shaft-through scroll compressor which has a shaft-through structure in which a rollover moment does not act on the turning scroll, and that the compressor can be miniaturized. Another object of the present invention is to provide a highly efficient shaft through scroll compressor having a small discharge flow resistance.
상기 목적을 달성하기 위하여 축관통식 스크롤 압축기에 있어서, 상기 크랭크축을 그 편심축부 선단부 위치가 선회스크롤 랩 선단면 보다도 선회 평판측이 되는 구조로 했다. 또, 크랭크축을 편심축으로부터 구동원과 결합한 측에서 적어도 1개의 베어링부에 의하여 지지하는 구조로 했다. 또, 상기 크랭크축을 지지하는 베어링부는 프레임 중앙부에 설치한 주베어링부와, 구동원에 대하여 프레임과 반대측에 설치한 부베어링부에 의하여 구성된다.In order to achieve the above object, in the axial-through scroll compressor, the crankshaft has a structure in which the eccentric shaft portion tip end position is on the swing plate side rather than the swing scroll wrap end face. Moreover, the structure which supports a crankshaft by the at least 1 bearing part from the side which engaged the drive source from the eccentric shaft was made. Moreover, the bearing part which supports the said crankshaft is comprised by the main bearing part provided in the frame center part, and the sub bearing part provided in the opposite side to the frame with respect to a drive source.
본 발명에 의하면 축의 선단부를 선회스크롤 랩 선단면 보다 저위치로 함으로써 크랭크축의 편심축부 보다 더 연장한 연장축심축부의 베어링 신뢰성, 가공정밀도를 확보하기 위하여 선회베어링 지름을 필요이상으로 크게 하는 일이 없으므로 압축기 전체의 소형화가 도모된다. 또, 구동원의 양측에서 크랭크축을 지지하는 구조이기 때문에 베어링간 거리를 길게 할 수가 있어, 베어링 하중을 저감하여 고신뢰성 성능을 얻을 수가 있게된다. 또, 토출유로의 저항이 저감됨으로써 높은 성능이 얻어진다.According to the present invention, since the tip of the shaft is positioned lower than the tip of the turning scroll lap, the diameter of the turning bearing is not made larger than necessary in order to ensure the bearing reliability and machining precision of the extended shaft shaft portion extending longer than the eccentric shaft portion of the crank shaft. Miniaturization of the whole compressor can be attained. Moreover, since the structure supports the crankshaft on both sides of the drive source, the distance between the bearings can be lengthened, so that the bearing load can be reduced and high reliability performance can be obtained. Moreover, high performance is obtained by reducing the resistance of a discharge flow path.
이하, 본 발명의 일 실시예를 제1도, 제2도 및 제3도에 의거하여 설명한다.Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1, 2 and 3.
밀폐케이싱(1)내에는 스크롤 압축기구부(2)가 상부에 전동기(3)가, 하부에 수납되어 있다. 그리고 이 스크롤 압축기구부(2)와 상기 전동기(3)는 크랭크축(4)을 거쳐 연결되어 있다. 압축기구부(2)는 평판부 또는 경판부(6a)에 소용돌이상의 랩부(6b)를 직립시켜 선회운동하는 선회스크롤(6)과, 평판부 또는 경판부(7a)에 소용돌이상의 랩부(7b)를 직립시켜 프레임(5)에 볼트등으로 고정된 고정스크롤(7)을 서로 랩을 내측으로 하여 맞물리게 하여 형성되어 있다. 크랭크축(4)의 일단에는 편심축부(4a)가 형성되어 있고, 상기 편심축부(4a)를 선회스크롤(6)의 중심부에 설치한 보스부(6c)에 삽입 배치되어 있다. 또, 프레임(5)과 선회스크롤(6)과의 사이에는 중간압실(11)이 설치되고, 이 중간압실(11)은 프레임(5)에 설치된 시일링(5b)에 의하여 밀폐케이싱(1)내실과 격리되어 기밀이 유지되고 있다. 그 중간압실(11)에는 압축도중의 가스를 도입하여 이 입력에 의하여 선회스크롤(6)에 고정스크롤(7)측에의 강압력을 부여하여 스크롤랩과 경판면과의 시일을 유지함과 동시에, 선회스크롤(6)의 거동 안정화를 도모하고 있다. 크랭크축(4)의 회전과 함께, 편심축부(4a)에 결합되어 있는 선회스크롤(6)은 중간압실(11)내에 배치된 올덤링 등의 자전방지기구(8)에 의하여 자전하는 일없이 선회운동을 행한다.In the hermetic casing 1, the scroll compressor mechanism 2 is housed in an upper portion and an electric motor 3 is housed in a lower portion. The scroll compressor mechanism 2 and the electric motor 3 are connected via a crank shaft 4. The compression mechanism (2) includes a swirling scroll (6) which pivots by erecting a spiral wrap portion (6b) on a flat plate or a hard plate portion (6a), and a spiral wrap portion (7b) on a flat plate or a hard plate portion (7a). The fixed scrolls 7 fixed to the frame 5 by bolts or the like are engaged with the wraps inside each other. An eccentric shaft portion 4a is formed at one end of the crank shaft 4, and the eccentric shaft portion 4a is inserted into the boss portion 6c provided at the center of the swing scroll 6. Moreover, the intermediate | middle pressure chamber 11 is provided between the frame 5 and the turning scroll 6, and this intermediate | middle pressure chamber 11 is sealed casing 1 by the sealing ring 5b provided in the frame 5. As shown in FIG. It is isolated from the interior and kept confidential. The gas under compression is introduced into the intermediate pressure chamber 11, and by this input, a strong pressure on the fixed scroll 7 side is applied to the swing scroll 6 to maintain the seal between the scroll wrap and the hard plate surface. It aims at stabilizing the behavior of the turning scroll 6. With the rotation of the crankshaft 4, the turning scroll 6 coupled to the eccentric shaft portion 4a is rotated without rotating by an anti-rotation mechanism 8 such as Oldham Ring disposed in the intermediate pressure chamber 11. Do exercise.
선회스크롤(6)과 고정스크롤(7)의 랩 측면에 있어서의 접촉점이 소용돌이 내측으로 이동하는 방향에 선회운동의 방향을 취하면, 소용돌이상의 외측실에 들어간 흡입가스는 압축공간을 중심으로 이동시켜 용적을 감소시켜 가스를 압축하고, 고정스크롤(7)의 중앙부에 설치된 토출포트(15)를 통하여 밀폐케이싱(1)내에 토출된다. 그 후, 토출가스는 프레임(5)의 외주에 설치된 통로(도시생략) 및 전동기(3)의 외주부에 설치된 통로(14)를 통하여 밀폐케이싱내 하부공간에 유도되고, 전동기의 로터와 스테이터의 사이를 상승하여 전동기(3)의 냉각을 행한 후, 토출관(13)을 거쳐 압축기 외부로 나온다. 또한, 프레임(5)의 외주에 설치된 상기 통로(도시생략) 및 통로(14)와, 토출관(13)의 공기흡입부와는 압축기의 수평단면에 있어서 다른 장소에 위치하고 있고, 서로는 연통되고 있지 않다.When the contact point on the lap side of the swing scroll 6 and the fixed scroll 7 is in the direction of the swing movement in the direction moving to the vortex inner side, the suction gas entering the vortex outer chamber moves about the compression space. The volume is reduced to compress the gas and discharged into the closed casing 1 through the discharge port 15 provided in the center portion of the fixed scroll 7. Thereafter, the discharge gas is guided to the lower space in the closed casing through a passage (not shown) provided on the outer periphery of the frame 5 and a passage 14 provided on the outer periphery of the electric motor 3, and between the rotor and the stator of the electric motor. After cooling to cool the electric motor 3, it exits out of a compressor via the discharge pipe 13. As shown in FIG. In addition, the passage (not shown) and the passage 14 provided on the outer circumference of the frame 5 and the air suction portion of the discharge pipe 13 are located at different places in the horizontal cross section of the compressor, and are in communication with each other. Not.
크랭크축(4)은 상기 축부(4d)가 전동기(3)의 회전자에 결합되고, 편심축부(4a)의 선단부 위치가 선회스크롤(6)의 랩 선단부 보다 선회 경판측에 있는 구조로 되어 있고, 그 선단부는 랩 선단부 보다 실질적으로 돌출하지 않는다. 또, 크랭크축(4)의 축부(4b, 4e)는 각각 프레임(5)에 설치한 주베어링(5a)과, 밀폐케이싱(1)내의 전동기(3)의 아래쪽에 위치하는 하프레임(16)에 설치한 부베어링(16a)에 의하여 지지되어 있다. 또, 하프레임(16)에는 드러스트 베어링(16b)이 설치되어 있고, 선회스크롤(6)에 작용하는 드러스트력을 크랭크축(4)을 거쳐 받는 구조로 되어 있다. 또, 크랭크축(4)내에는 급유통로(9)가 형성되어 있고, 축의 하단에는 급유파이프(10)가 설치되어 있어 원심펌프 작용에 의하여 밀폐케이싱(1) 저부의 유류(油溜)(18)에 괴여있는 윤활유가 급유파이프(10), 급유통로(9)를 통하여 크랭크축(4)내를 상승하여 각 베어링부에 공급되는 구조로 되어 있다. 또한, 도면에 있어서, 5b는 시일링, 12는 흡입관, 19a는 고정스크롤측부베어링, 20은 연장축심부이다.The crankshaft 4 has a structure in which the shaft portion 4d is coupled to the rotor of the electric motor 3, and the position of the distal end portion of the eccentric shaft portion 4a is located on the side of the swinging slab rather than the lap distal end of the turning scroll 6. The tip of the tip does not protrude substantially more than the wrap tip. In addition, the shaft parts 4b and 4e of the crankshaft 4 are the main bearing 5a provided in the frame 5, and the lower frame 16 located below the electric motor 3 in the airtight casing 1, respectively. It is supported by the sub-bearing 16a provided in this. Moreover, the thrust bearing 16b is provided in the lower frame 16, and it has a structure which receives the thrust force acting on the turning scroll 6 via the crankshaft 4. As shown in FIG. In addition, an oil supply passage 9 is formed in the crankshaft 4, and an oil supply pipe 10 is provided at the lower end of the shaft, and an oil flow at the bottom of the sealed casing 1 is caused by a centrifugal pump action ( The lubricant entrapped in 18) rises in the crankshaft 4 through the oil supply pipe 10 and the oil supply passage 9, and is supplied to each bearing part. In addition, in the figure, 5b is a seal ring, 12 is a suction pipe, 19a is a fixed scroll side bearing, and 20 is an extended shaft part.
크랭크축(4)의 베어링(축받이) 축부는 편심축부(4a) 및 그 편심축부(4a)의 하방의 축심축부(4b)에 형성되어 있다. 이들중 편심축부(4a)의 지름(D2)은 상기한 바와 같이 선회스크롤(6)의 외경을 결정하고, 나아가서는 압축기 전체의 외경을 결정한다. 이 지름은 선회 베어링의 소망성능만에 의하여 설계되므로, 종래와 같이 연장축심축부의 가공을 위한 강성이나, 베어링 면압을 충분히 확보하기 위하여 상기 편심축경을 필요이상으로 크게 하지 않아도 된다. 이 때문에 압축기 전체의 외경을 필요 최소한으로 역제 할 수가 있다.The bearing (bearing) shaft portion of the crankshaft 4 is formed in the eccentric shaft portion 4a and the axial shaft portion 4b below the eccentric shaft portion 4a. Among them, the diameter D 2 of the eccentric shaft portion 4a determines the outer diameter of the swing scroll 6 as described above, and further determines the outer diameter of the entire compressor. Since the diameter is designed only by the desired performance of the slewing bearing, the eccentric shaft diameter does not have to be made larger than necessary in order to sufficiently secure the rigidity for machining the extended shaft shaft portion and the bearing surface pressure as in the prior art. For this reason, the outer diameter of the whole compressor can be reversed to the minimum required.
또 크랭크축(4)을 주베어링(5a)과 부베어링(축받이)(16a)에 의하여 지지하는 구조에 있어서는 압축가스 하중점(荷重点)과 베어링간 거리가 커져 베어링 하중을 작게 할 수가 있으므로 베어링지름, 폭이 작게 취해져서 베어링의 신뢰성이 향상에 이어진다는 효과도 있다. 또, 주베어링(5a)의 폭이 작게 취해지면, 그만큼 축부(4c)에 설치한 카운터웨이트(17)의 외경을 작게할 수가 있어, 압축기 전체의 외경을 작게 할 수가 있다.In the structure in which the crankshaft 4 is supported by the main bearing 5a and the secondary bearing 16a, the distance between the compressed gas load point and the bearing can be increased, so that the bearing load can be reduced. It is also effective that the diameter and width are taken small, resulting in an improvement in the reliability of the bearing. If the width of the main bearing 5a is made small, the outer diameter of the counterweight 17 provided on the shaft portion 4c can be made smaller, and the outer diameter of the entire compressor can be made smaller.
크랭크축(4)은 그 선단부 위치가 서노히스크롤 랩 선단면 보다 선회 경판측에 있는 구조로 되어 있고, 이 때문에 고정스크롤(7)의 중앙부에 설치한 토출포트(15)의 연장축심축부에 의한 유로저항의 증가가 없다. 따라서, 높은 효율을 얻을 수가 있다. 또 토출포트(15)의 형상 및 크기도 자유롭게 결정할 수 있다는 효과가 있다.The crankshaft 4 has a structure in which the distal end position thereof is on the side of the swinging slab rather than the west-roll scroll lap end face. Therefore, the flow path of the crank shaft 4 by the extended shaft center portion of the discharge port 15 provided in the center of the fixed scroll 7 is provided. There is no increase in resistance. Therefore, high efficiency can be obtained. In addition, there is an effect that the shape and size of the discharge port 15 can also be freely determined.
또, 고정스크롤측의 축받이가 없어지므로 부품점수도 적어져 코스트 저감이 가능하게 된다. 또, 고정스크롤 배면측의 베어링이 1개 없어짐으로써 축의 중심잡기가 용이해지므로 조립성, 생산성이 향상되고, 또한 압축기의 높이도 얕게 할 수 있다는 효과도 있다.In addition, since the bearing on the fixed scroll side is eliminated, the number of parts is also reduced, which enables cost reduction. In addition, since one bearing on the fixed scroll back side is eliminated, centering of the shaft is facilitated, so that the assemblability and productivity are improved, and the height of the compressor can also be made shallow.
이상 설명한 바와 같이, 본 발명에 의하면, 선회스크롤에 전복 모멘트가 작용하지 않는 축관통식의 구조이고, 또 압축기의 소성화가 도모될 수 있다. 또 토출유로 저항을 작게할 수 있어 고효율화가 도모된다.As described above, according to the present invention, it is a shaft-through structure in which the rollover moment does not act on the turning scroll, and the plasticization of the compressor can be achieved. In addition, the discharge flow path can reduce the resistance, thereby achieving high efficiency.
Claims (3)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP94-127838 | 1994-06-09 | ||
| JP06127838A JP3124437B2 (en) | 1994-06-09 | 1994-06-09 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR960001492A KR960001492A (en) | 1996-01-25 |
| KR0149972B1 true KR0149972B1 (en) | 1999-03-30 |
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ID=14969922
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR1019950014026A Expired - Fee Related KR0149972B1 (en) | 1994-06-09 | 1995-05-31 | Scroll compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP3124437B2 (en) |
| KR (1) | KR0149972B1 (en) |
| CN (1) | CN1065594C (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101469712B (en) * | 2007-12-27 | 2011-10-05 | 上海日立电器有限公司 | Method for assembling rolling rotor type compressor |
| JP5588751B2 (en) * | 2010-06-11 | 2014-09-10 | 日立アプライアンス株式会社 | Positive displacement compressor |
| KR20120042494A (en) * | 2010-10-25 | 2012-05-03 | 엘지전자 주식회사 | Hermetic compressor |
| KR101059880B1 (en) | 2011-03-09 | 2011-08-29 | 엘지전자 주식회사 | Scroll compressor |
| KR102234708B1 (en) | 2014-08-06 | 2021-04-01 | 엘지전자 주식회사 | compressor |
| JP6675480B2 (en) | 2016-06-06 | 2020-04-01 | 三菱電機株式会社 | Scroll compressor |
| CN116624387B (en) * | 2023-07-18 | 2023-11-21 | 珠海凌达压缩机有限公司 | Scroll compressor and air conditioner |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2712777B2 (en) * | 1990-07-13 | 1998-02-16 | 三菱電機株式会社 | Scroll compressor |
| JP2718295B2 (en) * | 1991-08-30 | 1998-02-25 | ダイキン工業株式会社 | Scroll compressor |
-
1994
- 1994-06-09 JP JP06127838A patent/JP3124437B2/en not_active Expired - Fee Related
-
1995
- 1995-05-31 KR KR1019950014026A patent/KR0149972B1/en not_active Expired - Fee Related
- 1995-06-09 CN CN95107377A patent/CN1065594C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP3124437B2 (en) | 2001-01-15 |
| JPH07332258A (en) | 1995-12-22 |
| CN1065594C (en) | 2001-05-09 |
| KR960001492A (en) | 1996-01-25 |
| CN1126282A (en) | 1996-07-10 |
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