DK156672B - HERMETIC CLOSED ROTATION COMPRESSOR - Google Patents
HERMETIC CLOSED ROTATION COMPRESSOR Download PDFInfo
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- DK156672B DK156672B DK389183A DK389183A DK156672B DK 156672 B DK156672 B DK 156672B DK 389183 A DK389183 A DK 389183A DK 389183 A DK389183 A DK 389183A DK 156672 B DK156672 B DK 156672B
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- DK
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- oil
- closed container
- rotary compressor
- gas
- lubricating oil
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Description
DK 156672 BDK 156672 B
Den foreliggende opfindelse angâr en rotationskompressor af den i ind-ledningen til krav 1 angivne type, d.v.s en rotationskompressor af en type, hvori sm0reolien afkples ved hjælp af en varmeveksler med hen-blik pâ at forbedre ydeevnen og pâlideligheden i drift.The present invention relates to a rotary compressor of the type set forth in the preamble of claim 1, i.e. a rotary compressor of a type wherein the lubricating oil is cooled by means of a heat exchanger for the purpose of improving performance and reliability in operation.
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En sâdan rotationskompressor kendes fra US-patentskrifterne nr.Such a rotary compressor is known from U.S. Pat.
1,967,035 og nr. 2,623,365. I en kompressor, der er beskrevet i fprst-nævnte patentskrift, suges olie fra sumpen via en kanal gennem en olie-kpler, som er anbragt udenfor den lukkede beholder. Efter olien er af-10 kplet returneres den til den lukkede beholder. I den kompressor, der er beskrevet i sidstnævnte patentskrift, afkdles smpreolie ligeledes i en oliekpler, der en anbragt udenfor den lukkede beholder. Et spiral-stempel, som er roterbart forbundet med en kompressorvinge, leder olie frem og tilbage fra oliekpleren.1,967,035 and No. 2,623,365. In a compressor described in the aforementioned patent, oil is sucked from the sump via a duct through an oil cooler located outside the closed container. After the oil is removed, it is returned to the sealed container. In the compressor described in the latter patent, lubricating oil is also cooled in an oil burner which is placed outside the closed container. A spiral piston rotatably connected to a compressor vane directs oil back and forth from the oil burner.
15 I de konventionelle kompressorer, navnlig i kompressorer med stor ka-pacitet, dannes der en forpget mængde varme fra forskellige af kom-pressorens elementer, medens den afgivne varmemængde ikke forpges til-svarende, hvilket medfprer at kompressorens temperatur som helhed sti-20 ger. Pâ baggrund heraf opstâr der ikke alene en præopvarmning af ind-strpmningsgas, en forringelse i tætning mod lækage af smpreolie, en sækning i driftseffektivitet for elektriske motorer o.s.v., som bevir-ker en formindskelse i kompressorens driftsydeevne, men der optræder ogsâ en sænkning af smpreoliefilmens bærekraft, en forringelse i iso-25 leringsmaterialet til den elektriske motor o.s.v., hvilket medfprer en formindskelse i kompressorens driftspâlîdelighed.In the conventional compressors, especially in large capacity compressors, a packaged amount of heat is generated from various of the compressor elements, while the amount of heat delivered is not appropriately packaged, which causes the compressor temperature as a whole to rise. . Against this background, not only does preheating of compression gas, a decrease in seal against leakage of lubricating oil, a decrease in operating efficiency of electric motors, etc., which causes a decrease in compressor operating performance, but also a reduction in lubricating oil. sustainability, a deterioration in the insulation material for the electric motor, etc., which leads to a decrease in compressor reliability.
Derfor har der, med henblik pâ at forpge den afgivne varmemængde for kompressorer, været anvendt forskellige organer, som for eksempel olie-30 kplere o.s.v. En konventionel oliekpler vil imidlertid, da en del af den kplemiddelkreds trækkes ind i en hermetisk lukket beholder, fâ en kompliceret rprfpring og -sammenstilling i den tætnede beholders indre, og desuden bliver en enhed, der anvender en sâdan kompressor, kompliceret, hvilket medfprer en forpgelse i fremstillingsomkostningerne.Therefore, in order to utilize the delivered amount of heat for compressors, various means, such as oil coolers, etc. have been used. However, a conventional oil burner, as a portion of the refrigerant circuit will be drawn into a hermetically sealed container, will have a complicated scratching and assembly in the interior of the sealed container, and furthermore, a unit using such a compressor will be complicated, disregard for manufacturing costs.
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Det er formai et med den foreliggende opfindelse, at undgâ de ulemper, som optræder i forbindelse med de konventionelle kompressorer, og at tilvejebringe en kompressor af den indledningsvis nævnte type, hvori smpreolien f0res til en varmeveksler ved anvendelse af en sugning, derIt is an object of the present invention to avoid the drawbacks associated with the conventional compressors and to provide a compressor of the type mentioned in the introduction, wherein the lubricating oil is fed to a heat exchanger using a suction which
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2 ud0ves nâr kolemiddelgassen udlades, og hvilken kompressor nemt kan samles og har en udmærket driftsydeevne og -pâlidelighed.2 is discharged when the coolant gas is discharged and which compressor can be easily assembled and has an excellent operating performance and reliability.
Dette formai opnâs med en rotationskompressor, som er ejendommelig ved 5 de i den kendetegnende del af krav 1 angivne foranstaltninger.This is achieved with a rotary compressor which is characterized by the measures specified in the characterizing part of claim 1.
Herved opnâs at sm0reolien tilfores varmeveksleren sammen med gassen, der er udladet fra kompressionskammeret, hvorved bâde gassen og olien afkoles. Folgeligt vil den varme, der overfores fra den lukkede behol-10 der til varmeveksleren, og som afgives derfra, være meget storre end det er tilfældet, nâr varmen alene overfores ved hjælp af gassen. Dette skyldes forskellen i specifik varme for gas og olie. Som folge her-af kan afkolingseffekten foroges.This results in the lubricating oil being fed to the heat exchanger together with the gas discharged from the compression chamber, thereby cooling both the gas and the oil. Accordingly, the heat transmitted from the closed container to the heat exchanger emitted therefrom will be much greater than is the case when the heat alone is transmitted by the gas. This is due to the difference in specific heat for gas and oil. As a result, the cooling effect can be increased.
15 For at overfore olie til en ydre varmeveksl er, uden at anvende den udladede gas, kræves der en pumpe, som er anbragt i eller nær indlobet for en passage til varmeveksleren, eller i eller nærved udlobet for returpassagen. Tilvejebringelse af en pumpe vil foroge konstruktionens kompleksitet, og vil tillige bidrage væsentligt til fremstillingsom-20 kostningerne. I modsætning hertil vil det med rotationskompressoren ifolge opfindelsen være tiltrækkeligt at indfore den udladede gas i indlobet for passagen, der forer til varmeveksleren. Folgeligt vil denne rotationskompressor være mere enkel, og fremstillingsomkostnin-gerne vil være 1 avéré.15 In order to transfer oil to an external heat exchanger, without using the discharged gas, a pump is placed in or near the inlet for a passage to the heat exchanger, or in or near the outlet for the return passage. Providing a pump will increase the complexity of the construction and will also contribute significantly to the cost of manufacture. In contrast, with the rotary compressor of the invention, it will be sufficient to introduce the discharged gas into the inlet of the passage leading to the heat exchanger. Accordingly, this rotary compressor will be simpler and the manufacturing cost will be 1 avéré.
25 I modsætning til de traditionelle rotationskompressorer, hvor k0le-kredsen er indeholdt i den lukkede beholder, og hvor rorforing og mon-teringsarbejde er vanskelige, vil der opnâs en væsentlig lettere mon-tering og en mindre kompleks konstruktion med en rotationskompressor 30 ifolge opfindelsen.In contrast to the traditional rotary compressors where the cooling circuit is contained within the closed container and where piping and mounting work are difficult, a considerably easier assembly and a less complex construction with a rotary compressor 30 according to the invention will be obtained.
Opfindelsen vil herefter forklares nærmere under henvisning til den medfolgende tegning, hvor 35 fig. 1 viser et snitbillede gennem en forste udforelsesform for en rotationskompressor ifolge den foreliggende opfindelse, fig. 2 et perspektivisk bi11ede, partielt i snit, til belysning af en væsentlig del af en rotationskompressoren, som er vist i fig. 1,The invention will now be explained in more detail with reference to the accompanying drawing, in which: FIG. 1 is a sectional view through a first embodiment of a rotary compressor according to the present invention; FIG. 2 is a perspective view, partially in section, of illuminating a substantial portion of the rotary compressor shown in FIG. 1
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3 fi g. 3 et sm'tbillede gennem en anden udfprelsesform for en rota-tionskompressor ifplge den foreliggende opfindelse, hvor en indretning til afkpling af smpreolien er tilvejebragt, fig. 4 et perspektivisk billede, partielt i snit, til belysning af 5 en væsentlig del af den rotationskompressor, som er vist i fig. 3, fig. 5 et snitbillede gennem en tredje udf0relsesform for en rotationskompressor ifplge den foreliggende opfindelse, hvor en kplekreds for smpreolie er tilvejebragt, 10 fig. 6 et perspektivisk billede, partielt i snit, af en væsentlig del af rotationskompressoren if0lge den foreliggende opfindelse, fig. 7 et snitbillede gennem en fjerde udfprelsesform for en rotationskompressor ifplge den foreliggende opfindelse, 15 fig. 8A et planbillede af en oliesump i den rotationskompressor, som er vist i fig. 7, fig. 8B et snitbillede gennem oliesumpen, der er vist i fig. 8A taget efter linien A-A i fig. 8A, fig. 9 et sidebillede, partielt i snit, af en femte udfprelsesform 20 for en rotationskompressor ifplge den foreliggende opfindel se, fig. 10A et planbillede af oliesumpen i rotationskompressoren, som er vist i fig. 9, fig. 10B et snitbillede gennem oliesumpen, der er vist i fig. 10A, 25 taget efter linien B-B i fig. 10A, og fig. 11 et snitbillede, set fra siden, gennem en sjette udfprelses-form for en hermetisk, lukket rotationskompressor ifplge den foreliggende opfindelse.Fig. 3 shows a smear image through another embodiment of a rotary compressor according to the present invention, where a device for decoupling the smear oil is provided; 4 is a perspective view, partially in section, of illuminating 5 a substantial portion of the rotary compressor shown in FIG. 3, FIG. Fig. 5 is a sectional view through a third embodiment of a rotary compressor according to the present invention, in which a compressor oil supply circuit is provided; 6 is a perspective view, partially in section, of a substantial portion of the rotary compressor of the present invention; FIG. 7 is a sectional view through a fourth embodiment of a rotary compressor according to the present invention; FIG. 8A is a plan view of an oil sump in the rotary compressor shown in FIG. 7, FIG. 8B is a sectional view through the oil sump shown in FIG. 8A taken along line A-A in FIG. 8A, FIG. 9 is a side view, partially in section, of a fifth embodiment 20 of a rotary compressor according to the present invention; FIG. 10A is a plan view of the oil sump in the rotary compressor shown in FIG. 9, FIG. 10B is a sectional view through the oil sump shown in FIG. 10A, 25 taken along line B-B of FIG. 10A, and FIG. 11 is a side sectional view through a sixth embodiment of a hermetically sealed rotary compressor according to the present invention.
30 i det fplgende vil den foreliggende opfindelse blive beskrevet mere detaljeret under henvisning til fig. 1 og 2, der viser en fprste fore-trukken udfprelsesform for opfindelsen.30 In the following, the present invention will be described in more detail with reference to FIG. 1 and 2 illustrating a first preferred embodiment of the invention.
Fig. 1 viser et snitbillede gennem en rotationskompressor ifplge den 35 fprste udfprelsesform for den foreliggende opfindelse og fig. 2 er et perspektivisk billede af en væsentlig del af rotationskompressoren ifplge den fprste udfprelsesform for den foreliggende opfindelse. I tegningen betegner 1 en hermetisk lukket beholder, 2 og 3 angiver hen-holdsvis en elektrisk motor og kompressionselementer, der er huset iFIG. 1 is a sectional view through a rotary compressor according to the first embodiment of the present invention; and FIG. 2 is a perspective view of a substantial portion of the rotary compressor according to the first embodiment of the present invention. In the drawing, 1 denotes a hermetically sealed container, 2 and 3 respectively indicate an electric motor and compression elements housed in
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4 den hermetisk lukkede beholder og 7 angiver en krumtapaksel, der er beregnet til at blive drevet ved hjælp af den elektriske motor 2 m.v. Kompressionselementerne 3 omfatter et stempel 8, som er anbragt pâ krumtapakslen, et blad (ikke vist i tegningen), der med sin ene ende 5 er i kontakt med stemplet, og som udforer en reciprokerende bevægelse, hoved- og endelejer 5, 6, der er beregnet til at understotte krumtap-akslen 7, samt en cylinder 4, der er tilvejebragt mellem de to lejer.4 shows the hermetically sealed container and 7 indicates a crankshaft intended to be driven by the electric motor 2, etc. The compression elements 3 comprise a piston 8, which is arranged on the crankshaft, a blade (not shown in the drawing) which is in contact with the piston with one end 5 and which performs a reciprocating movement, main and end bearings 5, 6 which is intended to support the crankshaft 7, and a cylinder 4 provided between the two bearings.
Det indre af denne cylinder er, sâledes som det er velkendt, ved hjælp af det nævnte tætningsblad opdelt i et hojtrykskammer og en lavtryks-10 kammer for kolemidlet, sâledes at kolemidlets indlob og udlob kan gen-tages ved krumtapakslen's excentriske drejning.The interior of this cylinder, as is well known, is divided by means of said sealing blade into a high pressure chamber and a low pressure chamber for the coolant, so that the inlet and outlet of the coolant can be repeated by the eccentric rotation of the crankshaft.
Kolemiddelgassen, der er komprimeret pâ den ovenfor beskrevne mâde, passerer gennem en udladningsport 12 og en udladningsventil 13, der er 15 dannet i og tilvejebragt pâ hovedlejet 5 og udlades i et lyddæmpnings-kammer 14, der er tilvejebragt udenfor hovedlejet ved kolemidlets ud-ladningsside. Der er tilvejebragt en gaspassage 15 gennem cylinderen 4 mellem hovedlejet 5 og endelejet 6. Et gasudladningsror 16, der er tilvejebragt med sin faste ende indfort i denne gaspassage, og hvis 20 anden ende er en gasudladningsendedel 16a, som udmunder i et oliefO-rende ror 17, hvis ene ende ogsâ udmunder i en smoreolie-sump 19 i den hermetisk lukkede beholder 1. Dette olieforende ror (eller olieti1 for-sel sror) 17, der ved sin anden ende udmunder i den lukkede beholder, passerer gennem en varmeveksler 18, som er tilvejebragt udenfor behol-25 deren. Som fplge heraf fpres den afladede gas fra kompressionskammeret ind i olietilfprselsrpret 17's tilfprselsende 17a gennem gasudladnings-rpret 16's udladningsendedel 16a. I dette tilfælde vil smpreolien 19, der stâr i den nederste de! af lukkede beholder 1, trækkes ind i olie-tilfprselsroret 17 gennem en spalte A, der er dannet i et omrâde, hvor 30 gasudladningsrpret og olietilforselsrpret overlapper hinanden, og olien fpres sammen med en udstpdt gas fra gasudladningsrpret frem til varme-veksleren 18, der er tilvejebragt udenfor den lukkede beholder, og olien fores atter tilbage til den lukkede beholder 1 gennem en tilfor-sel sendedel 17b.The coolant gas compressed in the manner described above passes through a discharge port 12 and a discharge valve 13 formed in and provided on the main bed 5 and discharged into a sound attenuation chamber 14 provided outside the main bed at the discharge side of the refrigerant . A gas passage 15 is provided through the cylinder 4 between the main bearing 5 and the end bearing 6. A gas discharge tube 16 provided with its fixed end inserted into this gas passage and the other end of which is a gas discharge end 16a, which opens into an oil-feeding tube 17, one end of which also culminates in a lubricating oil sump 19 in the hermetically sealed container 1. This oil-lined rudder (or oil-sealed sump) 17, which at its other end opens into the sealed container, passes through a heat exchanger 18, which is provided outside the container. As a result, the discharged gas from the compression chamber is fed into the supply end 17a of the oil supply ratchet 17 through the discharge end 16a of the gas discharge ratchet 16. In this case, the lubricating oil 19, which is in the lower one! of closed container 1, is drawn into the oil feed tube 17 through a slot A formed in an area where 30 gas discharge ratchets and oil supply ramps overlap, and the oil is pressed together with an ejected gas from gas discharge ratchet to the heat exchanger 18 which is provided outside the closed container, and the oil is again fed back to the closed container 1 through a feeding dispenser 17b.
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Da den forste udforselsform for rotationskompressoren i folge den fore-liggende opfindelse er konstrueret, sâledes som nævnt ovenfor, vil smoreolien i den indre nederste de! af den lukkede beholder cirkulere i olietilforselsroret, medens der afgives varme, hvorved den vedhol- 5Since the first embodiment of the rotary compressor according to the present invention is constructed, as mentioned above, the lubricating oil in the inner lower part will of the closed container circulating in the oil supply tube while providing heat, thereby maintaining
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dende afgiver varme, der er overfprt fra den elektriske motor, kompres-sionselementerne o.s.v. Pâ denne mâde vil temperaturen af kompressoren sorti helhed inklusiv kompressionselementerne, smpreolien o.s.v blive sænket med den deraf fplgende virkning, at ikke alene kompressorens 5 ydeevne bliver forbedret pâ grund af at indsugningsgassen forhindres i præopvarmning og ved forbedringer i tætning mod smdreolielækage o.s.v., men ogsâ kompressorens pâlidelig-hed bliver fordget som for eksempel ved en forbedring i smpreegenskaberne.the same emits heat transmitted from the electric motor, the compression elements, etc. In this way, the temperature of the compressor variety including the compression elements, the lubricating oil, etc. will be lowered with the effect that not only the performance of the compressor is improved because the suction gas is prevented in preheating and by improvements in sealing against the compressor oil leakage, etc. reliability is required as, for example, by an improvement in the spreading properties.
10 I det fplgende vil den anden udfdrelsesform for den foreliggende op-findelse blive forklaret detaljeret under henvisning til fig. 3 og 4.10 In the following, the second embodiment of the present invention will be explained in detail with reference to FIG. 3 and 4.
Det bemærkes at dele, som er identiske med eller svarer til de, der er vist i udf0relsesformen i fig. 1 vil blive betegnet med samme henvis-ningsbetegnelser. Ifplge denne udfprelsesform for opfindelsen virker 15 rotationskompressoren pâ en mâde, som vil blive beskrevet i det f0l-gende.It is noted that parts which are identical to or similar to those shown in the embodiment of FIG. 1 will be denoted by the same reference numerals. According to this embodiment of the invention, the rotary compressor operates in a manner which will be described below.
Kdlemiddelgas vil efterhânden, som det suges ind fra indsugnings r0r 9, blive komprimeret ved hjælp af stemplet 8, som drejer excentrisk i 20 cylinderen 4. Den sâledes komprimerede k0lemiddelgas passerer gennem udladningsventilen 13, der er tilvejebragt pâ hovedlejet 5, for sâledes at blive udladet i lyddæmningskammeret 14 og passerer derefter gennem gaspassagen 15 gennem hoved- og endelejerne 5, 6 samt cylinderen 4 derimellem og fpres ind i et forbindelsesrpr 20, hvis ene ende 25 er forbundet med gaspassagen. Dette forbindelsesrpr, der er beregnet til at lede den afladede gas, fâr en udvidet diameter i smdre-olien 19, som stâr i den indre nederste del af den lukkede beholder 1. Smâ huiler 24, der er beregnet til at suge smpreolie, er dannet i umiddel-bar nærhed af en aftrappet del 23 mellem en del med lille diameter 21 30 og en del med stor diameter 22 af forbindelsesrpret 20. Den anden ende af dette forbindelsesrpr 20 fpres til varmeveksleren 18, som er place-ret udenfor den lukkede beholder 1 ved hjælp af dennes nederste del og bliver forbundet med et andet forbindelsesrdr 25, som igen udmunder i den lukkede beholder 1 efter varmevekslingen med den ydre luft.Coolant gas will eventually be compressed from suction tube 9 by means of the piston 8 which rotates eccentrically in the cylinder 4. The thus compressed refrigerant gas passes through the discharge valve 13 provided on the main bed 5 to be discharged. in the sound attenuation chamber 14 and then pass through the gas passage 15 through the main and end bearings 5, 6 and the cylinder 4 therebetween and spring into a connecting pipe 20, one end of which 25 is connected to the gas passage. This connecting tube, intended to conduct the discharged gas, has an expanded diameter in the lubricating oil 19 which is in the inner lower part of the closed container 1. Small cavities 24 intended to suck lubricating oil are formed. in the immediate vicinity of a stepped portion 23 between a small diameter portion 21 30 and a large diameter portion 22 of connecting ratchet 20. The other end of this connecting ratchet 20 is provided to the heat exchanger 18 which is located outside the closed container. 1 by means of its lower part and is connected to another connecting pipe 25, which in turn opens into the closed container 1 after the heat exchange with the external air.
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Fplgeligt vil den komprimerede kdlemiddelgas, der gennem gaspassagen 15 er blevet fprt ind i forbindelsesrpret 20, derefter fpres til varmeveksleren 18, som er tilvejebragt udenfor den lukkede beholder 1 sammen med smpreolien 19, som er blevet suget ind i forbindelsesrpretConsequently, the compressed refrigerant gas which has been fed through the gas passage 15 into connection ratchet 20 will then be fed to the heat exchanger 18 provided outside the closed container 1 together with the lubricating oil 19 which has been sucked into the connection ratchet.
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gennem de smâ huiler 24, der er tilvejebragt i den aftrappede de! af forbindelsesrpret, og som er beregnet til at suge smpreolien ind, og vil derefter atter fpres ind i den lukkede beholder 1 gennem varmeveks-leren 18's forbindelsesrpr 25. Dette betyder, at den varme, som er 5 genereret af den elektriske motor 2 og kompressionselementerne 3 hele tiden udlades uden for beholderen, da smpreolien 19 gentager sin cir-kulation sammen med den komprimerede k0lemiddelgas, medens den udlader varme derfra. Pâ denne mâde kan temperaturen i den elektriske motor 2, kompressionselementerne 3 og sm0reolien 19 m.v. blive sænket, hvorved 10 temperaturen for kompressoren som helhed kan formindskes. Som fplge heraf forbedres kompressorens ydeevne pâ grund af at indsugningsgassen forhindres i at blive præopvarmet, at der tilvejebringes en tætning mod smpreolielækage, at motoren driftseffektivitet forbedres o.s.v. og samtidig vil kompressorens pâlidelighed blive forbedret pâ grund af at 15 nedbrydning af den elektriske motors isoleringsmateriale forhindres.through the small howls 24 provided in the stepped ones! of connection ratchet, which is intended to suck the lubricating oil, and will then again be pressed into the closed container 1 through the heat exchanger 18 of connection ratchet 25. This means that the heat generated by the electric motor 2 and the compression elements 3 is constantly discharged outside the container as the lubricating oil 19 repeats its circulation with the compressed refrigerant gas while discharging heat therefrom. In this way, the temperature of the electric motor 2, the compression elements 3 and the lubricating oil 19, etc. be lowered, thereby reducing the temperature of the compressor as a whole. As a result, the compressor's performance is improved by preventing the suction gas from being preheated, providing a seal against lubricating oil leakage, improving engine operating efficiency, and so on. and at the same time, the reliability of the compressor will be improved by preventing the breakdown of the insulating material of the electric motor.
I det fplgende vil den tredje udfprelsesform for den foreliggende op-findelse blive forklaret under henvisning til fig. 5 og 6. Det bemær-kes at dele, som er identiske med eller svarer til de, der er vist i 20 udfprelsesformen i fig. 1 vil blive betegnet med samme henvisningsbe- tegnelser. Ifplge denne udforelsesfdrm for opfindelsen virker rota-tionskompressoren pâ en mâde, som vil blive beskrevet i det fplgende.In the following, the third embodiment of the present invention will be explained with reference to FIG. 5 and 6. It is noted that parts which are identical to or similar to those shown in the embodiment of FIG. 1 will be denoted by the same reference numerals. According to this embodiment of the invention, the rotary compressor operates in a manner which will be described below.
Kplemiddelgassen, som er suget ind fra indsugningsrpret 9 og komprime-25 reret passerer gennem udladningsporten 12 og udladningsventilen 13, der er dannet i og tilvejebragt pâ hovedlejet 5 og udlades i lyddæmp-ningskammeret 14 ved udladningssiden, hvorefter den yderligere passerer gennem gaspassagen 15 gennem hoved- og endelejerne 5, 6 samt cy-linderen 4 derimellem og fores derefter ind igennem gasudledningsrpret 30 16, hvis faste ende er indfprt i gaspassagen. Der er tilvejebragt et olietilfprselsrpr 30, hvis ene ende udmunder i den de! af den lukkede beholder 1, der er beregnet til opsamling af smpreolien 19, samt en varmeveksler 31, der er beregnet til at afkple smpreolien, og som er tilvejebragt udenfor den lukkede beholder, endvidere er der tilveje-35 bragt et forbindelsesrpr 32, som udmunder pâ den lukkede beholder l's sidevæg for sâledes at være i forbindelse med cylinderen 4's 0vre rum.The adhesive gas sucked in from intake manifold 9 and compressed 25 passes through the discharge port 12 and discharge valve 13 formed in and provided on the main bed 5 and discharged into the sound attenuation chamber 14 at the discharge side, after which it further passes through the gas passage 15 - and the end bearings 5, 6 and the cylinder 4 therebetween and are then inserted through gas discharge ratchet 30 16, the fixed end of which is embedded in the gas passage. An oil supply tube 30 is provided, one end of which ends in it! of the closed container 1 intended for collecting the butter oil 19, as well as a heat exchanger 31 intended to decouple the oil, which is provided outside the closed container, furthermore, a connecting tube 32 is provided which opens on the side wall of the closed container 1 so as to be in connection with the upper space of the cylinder 4.
Dette forbindelsesrpr er, i sérié, forbundet med varmeveksleren 31 samt olietilfprselsrpret 30, og den anden ende af det ovenfor nævnte gasudladningsrpr udmunder i olietilfprselsrpret 30.This connection tube is, in series, connected to the heat exchanger 31 as well as the oil supply 30, and the other end of the gas discharge tube mentioned above opens into the oil supply 30.
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Fplgeligt vil den komprimerede kplemiddelgas fra kompressionskammeret udlades i olietilfprselsrpret 30 fra gasudladningsrpret 16's endedel. Smpreolien, der star i den lukkede beholder l's nederste del, suges ved hjælp af udladningsrpret 16 gennem en spalte 33, der er dannet 5 mellem overlappende dele af udladningsrpret 16 og olietilfprselsrpret 30, og passerer derefter gennetn varmeveksleren 31, som er tilvejebragt udenfor den lukkede beholder 1 og fpres derefter atter ind i den lukkede beholder.Consequently, the compressed coolant gas from the compression chamber will be discharged into oil feed ratchet 30 from the end portion of gas discharge ratchet 16. The lubricating oil staring in the lower part of the closed container 1 is sucked by discharge ratchet 16 through a slot 33 formed 5 between overlapping portions of discharge ratchet 16 and oil supply ratchet 30, and then passes through the heat exchanger 31 provided outside the closed container 1 and then fpres into the closed container again.
10 Som nævnt i det foregâende vil den tredje udfprelsesform for den fore-liggende opfindelse fâ smpreolien til at cirkulere, medens der afgives varme gennem varmeveksleren. Ved at afgive varme, der er overfprt fra kompressionselementerne, den elektriske motor o.s.v., bliver tempera-turen i kompressionselementerne, den elektriske motor samt smpreolien 15 m.v. sænket og sâledes formindskes temperaturen af kompressoren som helhed, og kompressorens ydeevne kan forbedres pâ grund af at præop-varmning af indstrpmningsgassen forhindres, at der tilvejebringes for-bedringer i tætning mod smpreolielækage, at den elektriske motors driftseffektivitet forbedres m.v. Endvidere kan kompressorens pâlide-20 lighed forbedres bemærkelsesværdigt som fplge af forbedringen i smpre-egenskaberne, forhindring mod nedbrydning af den elektriske motors isoleringsmateriale o.s.v.As mentioned above, the third embodiment of the present invention will cause the lubricating oil to circulate while heat is released through the heat exchanger. By supplying heat transferred from the compression elements, the electric motor, etc., the temperature of the compression elements, the electric motor and the lubricating oil are 15, etc. lowered and thus the temperature of the compressor as a whole is reduced and the compressor performance can be improved by preventing preheating of the compression gas to provide improvements in sealing against the lubricating oil leakage, improving the operating efficiency of the electric motor, etc. Furthermore, the reliability of the compressor can be remarkably improved as a result of the improvement in the lubricant properties, the prevention of degradation of the insulating material of the electric motor, etc.
Ved at tilvejebringe et organ, ved hvilket gasudladningsrpret og olie-25 tilfprselsrpret bliver forbundet ved en stillîrtg uden for den lukkede beholder, vil kompressorens indvendige rum desuden kunne blive reduce-ret, hvilket er medvirkende til at tilvejebringe en reduktion i kompressorens stprrelse.In addition, by providing a means by which gas discharge ratchet and oil supply ratchet are connected at a position outside the closed container, the interior space of the compressor may be reduced, which contributes to a reduction in the size of the compressor.
30 I det fplgende vil den fjerde udfprelsesform for den foreliggende opfindelse blive forklaret under henvisning til fig. 7, der viser en vandret rotationskompressor. I fig. 7 betegner 41 den lukkede beholder, 42, 43 henholdsvis den elektriske motorsektion og kompressionselementerne, der er huset i den lukkede beholder og 47 angiver krum-35 tapakslen, der er beregnet til at blive drevet ved hjælp af den elektriske motorsektion 42, som er placeret i vandret retning. Kompressionselementerne 43 omfatter stemplet 48, der er anbragt pâ krumtap-akslen, bladet (ikke vist i tegningen), der med sin ene ende er i kon-takt med stemplet, og som udfprer en reciprokerende bevægelse, hoved-In the following, the fourth embodiment of the present invention will be explained with reference to FIG. 7, showing a horizontal rotary compressor. In FIG. 7, 41 denotes the closed container, 42, 43, respectively, the electric motor section and the compression elements housed in the closed container, and 47 denotes the crankshaft intended to be driven by the electric motor section 42 located in the horizontal direction. The compression elements 43 comprise the plunger 48 disposed on the crankshaft, the blade (not shown in the drawing), which at one end is in contact with the plunger, and which exhibits a reciprocating movement,
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og endelejet (45, 46), der er beregnet til at understptte krumtapakslen 47 og cylinderen 44, soin er anbragt mellem de to lejer. Det indre af denne cylinder er, sâledes som velkendt ved hjælp af ovennævnte tæt-ningsblad, adskilt i et hpjtrykskammer og et lavstrykkammer, sâledes 5 at kolemidlets indldb og udlob kan gentages ved krumtapakslens 47's excentriske rotation.and the end bearing (45, 46) intended to support the crankshaft 47 and the cylinder 44 are positioned between the two bearings. The interior of this cylinder is, as is well known by means of the above sealing blade, separated into a high pressure chamber and a low pressure chamber, so that the inlet and outlet of the coolant can be repeated by the eccentric rotation of the crankshaft 47.
Kdlemiddelgassen, som er blevet komprimeret pâ den ovenfor beskrevne mâde, passerer gennem udladningsventilen 53, der er tilvejebragt pâ 10 hovedlejet 45 og udlades ved udladningssiden i lyddæmpningskammeret 54, der er tilvejebragt udenfor hovedlejet 45. 55 betegner gaspassagen gennem hoved- og endelejet 45, 46 samt cylinderen 44, der er placeret mellem disse.The refrigerant gas, which has been compressed in the manner described above, passes through the discharge valve 53 provided on the main bed 45 and discharges at the discharge side of the sound attenuation chamber 54 provided outside the main bed 45. 55 denotes the gas passage through the main and end members 45. and the cylinder 44 located between them.
15 56 betegner en forbindelsesport, der er dannet pâ en sâdan mâde, at den ene ende udmunder pâ cylinderen 43's nedre flade og den anden ud-munder i en stilling, der vender væk fra gaspassagens âbne ende 55a, der udmunder mod endelejet 46. Denne forbindelsesport har en del 57 med stor diameter i umiddelbar nærhed af cylinderens nedre ende, hvor 20 forbindelsesportens diameter er udvidet. 58 angiver et ejektorrdr, hvis ene ende er indfort i denne forbindelsesport, og hvis anden ende udmunder i delen 57, der har en stor diameter og som er sammenhængende med den lukkede beholder 41. Dette ejektorrpr danner en spalte mellem sin ydre omkreds og delen med stor diameter. 59 angiver en olieindfo-25 ringsbane, som passerer gennem cylinderen 43's indre for sâledes at være rettet mod ejektorr0ret 58's sideflade. Denne olieindfpringsbane udmunder i sm0reolien 60, der star i den lukkede beholder 41's indre bunddel.15 56 denotes a connecting port formed in such a way that one end opens onto the lower face of cylinder 43 and the other opens into a position facing away from the open end 55a of the gas passage which opens to the end bearing 46. connecting port has a large diameter portion 57 in the immediate vicinity of the lower end of the barrel where the diameter of the connecting port is expanded. 58 indicates an ejector tube, one end of which is inserted into this connecting port and the other end of which opens into the portion 57 having a large diameter and which is connected to the closed container 41. This ejector tube forms a gap between its outer circumference and the portion with large diameter. 59 denotes an oil entry path which passes through the interior of the cylinder 43 so as to be directed to the side surface of the ejector tube 58. This oil indentation path opens into the lubricating oil 60, which is located in the inner bottom portion of the closed container 41.
30 61 betegner et olietilfprselsror, hvis ene ende er forbundet med et ringformet stykke 62, og som udmunder mod den lukkede beholder 41's nedre overfladevæg modsat delen 57 med stor diameter, og hvis anden ende er forbundet med olietilforselsbanen 63, der er tilvejebragt i cylinderen 43 og som passerer gennem beholderen 41's pvre overflade-35 væg. En varmeveksler 64, der er forbundet med olietilfprselsrpret, er tilvejebragt uden for den lukkede beholder. 65 angiver et stort set kopformet oliesump-kar med en oliesump-del mellem endefladerne af endelejet 46. Oliesump-karret har en flangedel 65a, der er beregnet til at blive anbragt pâ endelejet 46's ydre flade, og som danner en gas- 930 61 denotes an oil supply tube, one end of which is connected to an annular piece 62, which opens against the lower surface wall of the closed container 41 opposite the large diameter portion 57 and the other end of which is connected to the oil supply path 63 provided in the cylinder 43 and passing through the upper surface wall of the container 41. A heat exchanger 64 associated with the oil supply riser is provided outside the closed container. 65 indicates a substantially cup-shaped oil sump vessel having an oil sump portion between the end faces of the end bearing 46. The oil sump vessel has a flange portion 65a which is intended to be disposed on the outer surface of the end bearing 46 and forms a gas 9.
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strpmningsbane 66 ved en udbuling af flangedelen 65a pâ en mâde, for sâledes at forbinde den âbne ende af gaspassagen 55a i endelejet 46 med den âbne ende 56a af forbindelsesporten. Desuden vil oliesump-kar-ret 65 og olietilforselsroret 63 være forbundet ved hjælp af olietil-5 forselsroret 61. Endvidere betegner 67 en olietilf0rselsport, der pas-serer koncentrisk gennem krumtapakslen 47. Ved hjælp af denne olietil-fprselsport fores olien til de glidende dele gennem en afgreningsport 67a.the stripping path 66 by bulging the flange portion 65a in a manner so as to connect the open end of the gas passage 55a in the end portion 46 with the open end 56a of the connecting port. In addition, the oil sump 65 and the oil supply pipe 63 will be connected by the oil supply pipe 61. Furthermore, 67 denotes an oil supply port which passes concentrically through the crankshaft 47. By means of this oil supply port, the oil is fed to the sliding parts. through a branch gate 67a.
10 Pâ grund af denne konstruktion passerer den udladede gas fra kompres-sionskammeret, gennem lyddæmpningskammeret 54 ved kompressionskamme-rets udladningsside, gennem gaspassagen 55 og fores ind i ejektorrpret 58 i forbindelsesporten gennem gasstromningsbanen, der er dannet i det nævnte oliesump-kar 65. Derefter udstodes gassen ved delen 57 med stor 15 diameter og fores frem til varmeveksleren 64 udenfor den lukkede be-holder sammen med olie, der skal afkoles og som trækkes ind i delen med stor diameter gennem spalten, som er dannet mellem ejektorroret og delen med stor diameter, hvorefter olien og gassen returneres til den lukkede beholder 41, hvor olien fores til oliesump-karret 65 gennem 20 olietilfprselsbanen 63 og tilfprSelsrpret 61, hvorefter den fordeles til aile glidende dele medens kolemiddelgassen udlades i den lukkede beholder 41 fra krumtapakslen 47's endeflade ved den elektriske motor.Because of this construction, the discharged gas passes from the compression chamber, through the sound attenuation chamber 54 at the discharge side of the compression chamber, through the gas passage 55 and enters the ejector ridge 58 in the connecting port through the gas flow path formed in said oil sump vessel 65. the gas is ejected at the large diameter portion 57 and fed to the heat exchanger 64 outside the closed container together with oil to be cooled and drawn into the large diameter portion through the gap formed between the ejector tube and the large diameter portion. , after which the oil and gas are returned to the closed container 41, where the oil is fed to the oil sump vessel 65 through the oil supply web 63 and feed ratchet 61, whereupon it is distributed to all sliding parts while the coolant gas is discharged into the closed container 41 from the crank shaft 47 engine.
IfOlge den fjerde udforelsesform for den foreliggende opfindelse, og 25 sâledes som beskrevet i det foregâende, vil smoreolien ved den lukkede beholders indre nederste del cirkulere, medens den fjerner varme, hvor-ved den fortsat bortleder varme, der overfores fra den elektriske mo-torsektion, kompressionselementerne og andre. Pâ denne mâde vil tempe-raturen af kompressionselementerne, smoreolien o.s.v. og dermed tempe-30 raturen af kompressoren som helhed blive sænket. Pâ baggrund heraf vil ikke alene kompressoren ydeevne blive forbedret pâ grund af at præop-hedning af indstrdmningsgassen forhindres, at der tilvejebringes for-bedringer i tætningen imod lækage af smoreolie o.s.v., men ogsâ kom-pressorens driftspâlidelighed vil blive forbedret som for eksempel ved 35 en forbedring af smoreegenskaberne o.s.v.According to the fourth embodiment of the present invention, and as described above, the lubricating oil will circulate at the inner bottom of the closed container while removing heat, thereby continuing to dissipate heat transmitted from the electric motor section. , the compression elements and others. In this way, the temperature of the compression elements, the lubricating oil, etc. thus lowering the temperature of the compressor as a whole. Against this background, not only will the compressor performance be improved by preventing preheating of the inlet gas to provide improvements in the seal against leakage of lubricating oil, etc., but also the compressor's reliability will be improved as, for example, at improving the lubrication properties, etc.
Herefter vil den femte udforeselsform for rotationskompressoren ifplge den foreliggende opfindelse blive forklaret under henvisning til fig.Next, the fifth embodiment of the rotary compressor according to the present invention will be explained with reference to FIG.
9. Det bemærkes at de dele, som er identiske med eller svarer til de- 109. It should be noted that the parts which are identical or similar to the parts 10
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lene i den udfprelsesform, som er vist i fig. 7, er betegnet ved samme henvisningsbetegnelser. I fig. 9 betegner 70 gaspassagen, der passerer gennem hovedlejet 45 ved en stilling nær ved udladningsventilen 53, og som passerer gennem cylinderen 44 i form af et L, og som udmunder ra-5 dialt ved cylinderens nedre flade. Denne gaspassage er forbundet med forbindelsesporten 71 med stor diameter.in the embodiment shown in FIG. 7, are designated by the same reference numerals. In FIG. 9, 70 denotes the gas passage which passes through the main bearing 45 at a position close to the discharge valve 53 and which passes through the cylinder 44 in the form of an L, which opens radially at the lower surface of the cylinder. This gas passage is connected to the large diameter connecting port 71.
72 betegner ejektomiret, der har sin ene ende i prespasning i forbin-delsesportens de! med lille diameter. Ejektorrpret 72's anden ende 10 udmunder i forbindelsesporten 71's de! med stor diameter i nærheden af indgangen til varmeveksleren, der er monteret uden for den lukkede beholder. 73 angiver olieindfpringsbanen, der udmunder i cylinderen neddykket i smpreolien 60 i bunden af den lukkede beholder for sâledes vinkelret at skære forbindelsesporten 71's del med stor diameter. Den-15 ne olieindfpringsbane er forbundet med spalten 74 mellem forbindelsesporten 71's inderdiameter og ejektorrpret 72's yderdiameter. Desuden er den ydre varmeveksler 64, der er beregnet til at afkple smpreolien, gennem rpret 75 forbundet med forbindelsesporten 71's del med stor diameter ved cylinderens ydre omkredsdel, Den anden ende af varmevek-20 sleren 64 er, gennem det oli'efprende r0r 76, der passerer gennem den lukkede beholder 41, forbundet med det stort set kopformet oliesump-kar 77, som i prespasning er anbragt pâ den ydre omkreds af den flan-geforsynede del af endelejet 46, hvorved smpreolien i oliesump-karret fordeles til hver af de glidende dele gennem olietilfprselsportene 25 (ikke vist pâ tegningen), som udmunder i krumtapakslen 47. Desuden er den ydre omkredsdel af dette oliesump-kar anbragt i prespasning og fastgjort pâ endelejet 46's flangedel.72 denotes the ejectomir, which has one end in press fit in the connection port they! of small diameter. Ejector ratchet 72's other end 10 opens into the connecting port 71's! of large diameter near the entrance to the heat exchanger mounted outside the closed container. 73 denotes the oil indentation path which culminates in the cylinder submerged in the lubricating oil 60 at the bottom of the closed container so as to cut perpendicularly to the large diameter portion of the connecting port 71. This oil indentation path is connected to the gap 74 between the inner diameter of the connecting port 71 and the outer diameter of the ejector 72. In addition, the outer heat exchanger 64, which is intended to decouple the oil, is connected through ratchet 75 to the large diameter portion of the connecting port 71 at the outer circumferential portion of the cylinder. The other end of the heat exchanger 64 is through the oil-extending tube 76. passing through the closed container 41, connected to the largely cup-shaped oil sump vessel 77, which is press-fit on the outer circumference of the flanged portion of the end bearing 46, thereby distributing the lubricating oil in the oil sump vessel to each of the sliding portions through the oil supply ports 25 (not shown in the drawing) which open into the crankshaft 47. In addition, the outer circumferential portion of this oil sump vessel is arranged in a press fit and secured to the flange portion of the end bearing 46.
Den udladede k0lemiddelgas fra kompressionskammeret passerer sâledes 30 gennem lyddæmpningskammeret 54 ved udladningssiden samt gaspassagen 70 og udstpdes fra ejektorrpret 72 i indgangsdelen af varmeveksleren, det vil sige ind i den del af forbindelsesporten 71's del, der har en stor diameter. Herefter fpres kplemiddelgassen ind i varmeveksleren 64, der er tilvejebragt uden for den lukkede beholder sammen med smpreolie 60, 35 der er trukket ind i gassen gennem spalten 74, der er tilvejebragt i omrâdet, hvor forbindelsesporten 71's indre del og ejektomiret 72's ydre del overlapper hinanden. Efter varmeudvekslingen fpres gassen. atter tilbage til den lukkede beholder. Pâ den anden side fpres smpre-olien tilbage til det stort set kopformet oliesump-kar 77 gennem detThe discharged coolant gas from the compression chamber thus passes through the sound attenuation chamber 54 at the discharge side as well as the gas passage 70 and is ejected from the ejector chute 72 into the input portion of the heat exchanger, that is, the portion of the connecting port 71 having a large diameter. Thereafter, the adhesive gas is squeezed into the heat exchanger 64 provided outside the sealed container together with crepe oil 60, 35 which is drawn into the gas through the slot 74 provided in the region where the inner portion of the connecting port 71 and the outer portion of the ejector 72 overlap. . After the heat exchange, the gas is compressed. back to the closed container. On the other hand, the lubricating oil is pressed back into the largely cup-shaped oil sump vessel 77 through it.
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11 o1ief0rende r0r 76 i den lukkede beholder. Derefter fordeles smdre-olien til hver af de glidende dele, medens kdlemiddelgassen udlades i den lukkede beholder fra krumtapakslen 47's endeflade ved den elek-triske motor.11 sealed tube 76 in the closed container. Then, the lubricating oil is distributed to each of the sliding parts while the coolant gas is discharged into the closed container from the crankshaft 47's end surface at the electric motor.
55
Da den femte udfprelsesform for rotationskompressoren ifplge den fore-liggende opfindelse er konstrueret, sâledes som beskrevet ovenfor, vil smdreolien i den lukkede beholders indre bunddel cirkulere, medens det bortleder vanne, hvorved den fortsat bortleder vanne, der bliver over-10 f0rt fra den elektriske motorsektion, kompressionselementerne og andre.As the fifth embodiment of the rotary compressor according to the present invention is constructed as described above, the lubricating oil in the inner bottom portion of the closed container circulates as it discharges the water, thereby continuing to drain the water which is transferred from the electric engine section, compression elements and others.
Da temperaturen af kompressoren som helhed inkl. kompressionselementerne, smdreolien o.s.v. pâ denne mâde sænkes, vil ikke alene kompres-sorens ydeevne blive forbedret pâ grund af at præopvarmning af ind-str0mningsgassen forhindres, at der tilvejebringes forbedring i tæt-15 ningsegenskaberne mod smdreolielækage o.s.v., men ogsâ kompressorens pâlidelighed vil blive forbedret som for eksempel ved en forbedring i smdreegenskaberne. Med en sâdan konstruktion, som er tilvejebragt ifdl-ge den foreliggende opfindelse, kan kompressoren desuden monteres en-ten vandret eller lodret, hvorved dens bedste anvendelsesmâde kan for-20 ventes samtidig med en pladsbesparende monterings.As the temperature of the compressor as a whole incl. the compression elements, the lubricating oil, etc. in this way, not only will the compressor's performance be improved because preheating of the inlet gas prevents improvement in the sealing properties against lubricating oil leaks, etc., but also the compressor's reliability will be improved, for example by improvement in the smear properties. In addition, with such a construction provided in accordance with the present invention, the compressor can be mounted either horizontally or vertically, whereby its best mode of use can be expected at the same time as a space-saving mounting.
Den sjette udfprelsesform for rotationskompressoren ifdlge den foreliggende opfindelse vil i det f0lgende blive forklaret under henvis-ning til fig. 11. Det bemærkes, at de dele, som er identiske med eller 25 som svarer til dele af konstruktionen, der er vïst i fig. 1, vil blive betegnet med samme henvisningsbetegnelser, og forklaringen af disse vil blive udeladt.The sixth embodiment of the rotary compressor according to the present invention will be explained below with reference to FIG. 11. It should be noted that the parts identical to or 25 corresponding to parts of the structure shown in FIG. 1, will be denoted by the same reference numerals and the explanation thereof will be omitted.
Denne udfprelsesform for den foreliggende opfindelse angâr en forbed-30 ring af konstruktionen, der er vist i fig. 2, hvor kdlemiddelgassen, der udlades ved siden af hovedlejet 5, passerer gennem hovedlejet 5, cylinderen 4 og endelejet 6, for sâledes at nâ udladningsr0ret 83, og for sâledes at mîndske det tryktab, der kan optræde mellem disse dele, og for sâledes at forpge kompressorens driftseffektivitet, som ville 35 blive sænket pâ grund af tryktabet og, samtidig, vil der, pâ grund af at det olief0rende r0r 17 er placeret ved beholderen l's nederste del, være tilvejebragt en stor h0jdeforskel mellem det oliefprende r0r 17 og olietilf0rselsenden 17b, hvilket medfdrer at smdreolien sam!es i det olieforende rdr 17, og sâledes forhindrer den udladede kdlemiddel-This embodiment of the present invention relates to an improvement of the construction shown in FIG. 2, wherein the refrigerant gas discharged next to the main bed 5 passes through the main bed 5, the cylinder 4 and the end bed 6 so as to reach the discharge pipe 83, and to reduce the pressure loss which may occur between these parts and so as to compressing the compressor's operating efficiency, which would be lowered due to the pressure loss and, at the same time, because the oil-carrying tube 17 is located at the lower part of the container 1, a large height difference is provided between the oil-leaning tube 17 and the oil supply end 17b, which causes the lubricating oil to settle in the oil-lined tube 17, thus preventing the discharged refrigerant
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12 gas i at str0mme tilbage i sm0reo1ien 19 fra det olief0rende r0r 17.12 gas flowing back into the lubricating oil 19 from the oil-carrying tube 17.
I fig. 11 betegner 80 udladningsventilen, der er tilvejebragt ved en-delejet (cylindertopstykke) 6 og udladningslyddæmperen 81 er monteret 5 ved cylindertopstykket 6, det vil sige ved den nedre flade af cylinde-ren 4. 82 angiver en indfpringsport for olietilf0rselsr0ret, som er dannet i den nedre sideflade af den hermetisk lukkede beholder 1, hvor smpreolien 19 samler sig. Indf0ringen foregâr sâledes at kompressions-elementerne 3 og det elektriske motorelement 2 f0rst indf0res i den 10 hermetisk lukkede beholder 1 og dernæst indfpres et forbindelsesr0r 83, der pâ forhând er blevet placeret i det oliefprende rpr 17, i en àbning 84 i et ringformet stykke, der er dannet i udladningslyddæmperen 81 fra det oliefprende rprs indfpringsport 82. Diameteren af âb-ningen 84 og diameteren af forbindelsesrdret 83, der skal indfdres i 15 denne âbning er stort set den samme, sâledes at de er i en stram pas-ning og tætnede ved indfpring af den ene i den anden.In FIG. 11 represents 80 the discharge valve provided by the one-piece (cylinder head) 6 and the discharge silencer 81 mounted 5 at the cylinder head 6, that is, at the lower surface of the cylinder 4. 82 indicates an indentation port for the oil supply tube formed in the the lower side surface of the hermetically sealed container 1 where the smear oil 19 collects. The insertion is carried out so that the compression elements 3 and the electric motor element 2 are first inserted into the 10 hermetically sealed container 1 and then inserted a connecting tube 83, which has been previously placed in the oil-pronged rpr 17, in an opening 84 in an annular piece, formed in the discharge muffler 81 from the oil-spring rpr's inlet port 82. The diameter of the aperture 84 and the diameter of the connecting tube 83 to be inserted into this aperture are substantially the same so that they are in a tight fit and sealed. by inserting one into the other.
Efter det olief0rende r0r 17 er indfprt, fastsvejses det hermetisk ved en lodning til indfdringsporten.After the oil-bearing pipe 17 is inserted, it is welded hermetically by a solder to the entry port.
20 Sâledes som beskrevet i det foregâende, og da den sjette udfprelses-form for den foreliggende opfindelse er sâledes konstrueret, at det oliefprende r0r 17 indf0res direkte i udladningslyddæmperen 81, vil tryktabet ved forbindelseshullet blive elimineret i sammenligning med 25 den udfprelsesform, der er vist i fig. 2. Da kplemiddelgassen udtages fra den hermetisk lukke beholders sideflade, kan en hpjdeforskel mel-lem olietilfprselsporten og oliereturneringsporten desuden blive redu-ceret.20 As described above, and since the sixth embodiment of the present invention is constructed such that the oil spring tube 17 is inserted directly into the discharge silencer 81, the pressure loss at the connection hole will be eliminated in comparison with the embodiment shown. in FIG. 2. Furthermore, as the adhesive gas is withdrawn from the side surface of the hermetically sealed container, a height difference between the oil supply port and the oil return port can be reduced.
30 3530 35
Claims (10)
Applications Claiming Priority (12)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15031982A JPS5939991A (en) | 1982-08-30 | 1982-08-30 | Rotary compressor |
| JP15031982 | 1982-08-30 | ||
| JP14847482 | 1982-09-30 | ||
| JP14847382 | 1982-09-30 | ||
| JP14847482U JPS5952198U (en) | 1982-09-30 | 1982-09-30 | Horizontal rotary compressor |
| JP14847382U JPS5952197U (en) | 1982-09-30 | 1982-09-30 | rotary compressor |
| JP15769782U JPS5962289U (en) | 1982-10-19 | 1982-10-19 | Rotary compressor lubricating oil cooling system |
| JP15769782 | 1982-10-19 | ||
| JP17527882U JPS5979574U (en) | 1982-11-19 | 1982-11-19 | rotary compressor |
| JP17527982 | 1982-11-19 | ||
| JP17527882 | 1982-11-19 | ||
| JP17527982U JPS5979575U (en) | 1982-11-19 | 1982-11-19 | Closed type rotary compressor |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK389183D0 DK389183D0 (en) | 1983-08-25 |
| DK389183A DK389183A (en) | 1984-03-01 |
| DK156672B true DK156672B (en) | 1989-09-18 |
| DK156672C DK156672C (en) | 1990-02-12 |
Family
ID=27553044
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK389183A DK156672C (en) | 1982-08-30 | 1983-08-25 | HERMETIC CLOSED ROTATION COMPRESSOR |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0105127B1 (en) |
| AU (1) | AU548548B2 (en) |
| DE (1) | DE3372117D1 (en) |
| DK (1) | DK156672C (en) |
| MX (2) | MX158883A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS618492A (en) * | 1984-06-25 | 1986-01-16 | Mitsubishi Electric Corp | Rotary compressor |
| JPS61210285A (en) * | 1985-03-14 | 1986-09-18 | Toshiba Corp | Rotary compressor |
| DE3712468C2 (en) * | 1987-04-14 | 1995-04-20 | Mitsubishi Electric Corp | Shut-off valve for a refrigeration system |
| CN114017334B (en) * | 2021-11-08 | 2023-09-05 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration equipment with same |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB382227A (en) * | 1931-05-15 | 1932-10-20 | Bosch Robert | Improvements in or relating to refrigerating machines |
| US1967035A (en) * | 1933-05-08 | 1934-07-17 | Lipman Patents Corp | Motor compressor unit |
| US2178425A (en) * | 1937-02-18 | 1939-10-31 | Gen Electric | Refrigerating machine |
| US2623365A (en) * | 1947-07-14 | 1952-12-30 | Leonard J Daniel | Refrigerator pump |
-
1983
- 1983-08-04 AU AU17607/83A patent/AU548548B2/en not_active Ceased
- 1983-08-04 EP EP19830107665 patent/EP0105127B1/en not_active Expired
- 1983-08-04 DE DE8383107665T patent/DE3372117D1/en not_active Expired
- 1983-08-25 DK DK389183A patent/DK156672C/en not_active IP Right Cessation
- 1983-08-29 MX MX56783A patent/MX158883A/en unknown
- 1983-08-29 MX MX19853483A patent/MX153949A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| AU1760783A (en) | 1984-03-08 |
| AU548548B2 (en) | 1985-12-19 |
| MX153949A (en) | 1987-02-24 |
| EP0105127A1 (en) | 1984-04-11 |
| EP0105127B1 (en) | 1987-06-16 |
| MX158883A (en) | 1989-03-29 |
| DK389183D0 (en) | 1983-08-25 |
| DK389183A (en) | 1984-03-01 |
| DE3372117D1 (en) | 1987-07-23 |
| DK156672C (en) | 1990-02-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |