CN101835988A - 2 stage rotary compressor - Google Patents
2 stage rotary compressor Download PDFInfo
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- CN101835988A CN101835988A CN200880112844A CN200880112844A CN101835988A CN 101835988 A CN101835988 A CN 101835988A CN 200880112844 A CN200880112844 A CN 200880112844A CN 200880112844 A CN200880112844 A CN 200880112844A CN 101835988 A CN101835988 A CN 101835988A
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- low pressure
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- mandarin
- rotary compressor
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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
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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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention provides a 2 stage rotary compressor including a hermetic container (101), a 2 stage compression assembly provided in the hermetic container (101 ) and including a low pressure compression assembly (120), a middle plate (140) and a high pressure compression assembly (130), a low pressure refrigerant inflow portion (126) provided in the low pressure compression assembly (120) to introduce low pressure refrigerant, and a middle pressure refrigerant inflow portion (130a) provided in the high pressure compression assembly (130) to introduce middle pressure refrigerant compressed in the low pressure compression assembly (120), wherein a diameter of the middle pressure refrigerant inflow portion (130a) larger than 0.5 times of a diameter of the low pressure refrigerant inflow portion (126) and smaller than 1.1 times thereof. This configuration can prevent a pressure of middle pressure refrigerant sucked into the high pressure compression assembly (130) from being excessively raised or dropped by appropriately controlling a volume flow of refrigerant introduced into the high pressure compression assembly (130) through the middle pressure refrigerant inflow portion (130a).
Description
Technical field
The present invention relates to a kind of 2 stage rotary compressor, relate more specifically to a kind of become a mandarin 2 stage rotary compressor of portion of refrigeration agent that comprises, this refrigeration agent portion of becoming a mandarin is designed to be suitable for low pressure compression assembly and high pressure compressed assembly compression volume separately.
Background technique
Usually, compressor is to produce the mechanical device that equipment such as motor, turbo machine etc. receive power from power, and it compresses to improve pressure air, refrigeration agent or various working gas.Compressor is widely used in the household electric appliance of for example refrigerator and air-conditioning and is applied in other words in the whole industry.
Compressor roughly is categorized as: reciprocal compressor, wherein between piston and cylinder, be limited with compression volume, working gas is inhaled into and discharges this compression volume, and piston in the inside of cylinder linearly to-and-fro motion with compressed refrigerant; Rotary compressor wherein is limited with compression volume between the roller (roller) of off-centre rotation and cylinder, working gas is inhaled into and discharges compression volume, and roller along the inwall eccentric ground rotation of cylinder with compressed refrigerant; And scroll compressor, wherein between moving scroll and fixed scroll, being limited with compression volume, working gas is inhaled into and discharges this compression volume, and the moving scroll is rotated with compressed refrigerant along fixed scroll.
Particularly, rotary compressor develops into: two rotary compressors, two rollers and two cylinders wherein are set, the part that pair roller on top and cylinder compress whole compression volumes and that pair roller of bottom and another part that cylinder compresses whole compression volumes in the upper and lower; And 2 stage rotary compressor, two rollers and two cylinders wherein are set in the upper and lower, and two cylinders communicate with each other, make a pair of can the lower refrigeration agent of compression pressure and another is to compressing the higher refrigeration agent of pressure through the low pressure compression step.
Publication number is that the Korean registered patent documentation of 1994-0001355 discloses a kind of rotary compressor.Motor is arranged in the housing, and installs and pass this shaft of motor.In addition, cylinder is arranged under the motor, around the adaptive eccentric part of rotating shaft, and the roller that fits on this eccentric part is set in cylinder.In cylinder, be formed with refrigeration agent tap hole and refrigeration agent and go into discharge orifice, and go into to be equipped with between the discharge orifice at this refrigeration agent tap hole and this refrigeration agent and be used to the blade (vane) that prevents that unpressed low pressure refrigerant from mixing with the high-pressure refrigerant of compression.In addition, spring is installed, makes the roller of eccentric rotary and blade Continuous Contact each other at an end of blade.When rotating shaft was rotated, eccentric part and roller rotated with compression refrigerant gas along the inner periphery of cylinder, and refrigerant compressed gas is discharged from by the refrigeration agent tap hole.
Publication number provides a kind of pair of rotary compressor for Korea S's publication document of 10-2005-0062995.With reference to Fig. 1, be provided with two identical cylinders 1035 of intermediate plate 1030 and compression volume and 1045, compression volume is risen to the twice of a stage compressor.
Publication number be 10-2007-0009958 Korea S's publication document teaching a kind of 2 stage rotary compressor.As shown in Figure 2, compressor 2001 comprises the motor 2014 of the internal upper part that is positioned at seal container 2013 and the rotating shaft 2002 that is connected to motor 2014, and motor 2014 has stator 2007 and rotor 2008, and rotating shaft 2002 comprises two eccentric parts.Begin to pile up continuously from motor 2014 and rotating shaft 2002 relative sides main bearing 2009 is arranged, high pressure compressed unit 2020b, intermediate plate 2015, low pressure compression unit 2020a and assembly bearing 2019.In addition, intervalve 2040 is installed will in low pressure compression unit 2020a, refrigerant compressed introducing high pressure compressed unit 2020b.
Summary of the invention
Technical problem
One object of the present invention is, a kind of 2 stage rotary compressor that can improve compression efficiency is provided, wherein is used for the low pressure refrigerant that low pressure refrigerant is introduced the low pressure compression assembly the become a mandarin diameter ratio of portion of middle compacting cryogen that diameter and the compacting cryogen that is used for compressing at the low pressure compression assembly of portion introduce the high pressure compressed assembly that becomes a mandarin is in the predetermined scope.
Another object of the present invention is to, a kind of 2 stage rotary compressor is provided, it comprises and is used for the low pressure refrigerant portion of becoming a mandarin is connected to the become a mandarin connecting passage of portion of compacting cryogen.
Another purpose of the present invention is, a kind of 2 stage rotary compressor is provided, and wherein ascending pipe is connected to connecting passage.
Technological scheme
According to the present invention, a kind of 2 stage rotary compressor is provided, comprising: seal container; The secondary compression assembly is arranged in the seal container and comprises low pressure compression assembly, intermediate plate and high pressure compressed assembly; The low pressure refrigerant portion that becomes a mandarin is arranged in the low pressure compression assembly to introduce low pressure refrigerant; And the middle compacting cryogen portion that becomes a mandarin, be arranged in the high pressure compressed assembly to be introduced in the middle compacting cryogen that compresses in the low pressure compression assembly, wherein in the become a mandarin diameter of portion of compacting cryogen become a mandarin 0.5 times of portion's diameter and greater than low pressure refrigerant less than become a mandarin 1.1 times of portion's diameter of low pressure refrigerant.This structure can raise or descends by suitably controlling excessive pressure that the volume flowrate of introducing the refrigeration agent in the high pressure compressed assembly via the middle compacting cryogen portion of becoming a mandarin prevents to suck the middle compacting cryogen in the high pressure compressed assembly.
According to a scheme of the present invention, the become a mandarin diameter of portion of middle compacting cryogen is become a mandarin 0.6 times to 1.0 times of portion's diameter of low pressure refrigerant.By this structure, energy effciency ratio (EER) can rise to greater than 9.8.
According to other scheme of the present invention, the become a mandarin diameter of portion of middle compacting cryogen is become a mandarin 0.9 times to 1.0 times of portion's diameter of low pressure refrigerant.By this structure, EER can rise to greater than 10.0.
According to other scheme of the present invention, the low pressure compression assembly comprises the low pressure (LP) cylinder in the space that is used to provide compressed refrigerant, thereby and the low pressure refrigerant portion of becoming a mandarin be the pipe that is inserted into the refrigeration agent compression volume that arrives low pressure (LP) cylinder.By this structure, can stably low pressure refrigerant be supplied to compression volume in low pressure (LP) cylinder inside.Herein, the internal diameter of pipe becomes the become a mandarin diameter of portion of low pressure refrigerant.
According to other scheme of the present invention, the low pressure compression assembly comprises the low pressure (LP) cylinder in the space that is used to provide compressed refrigerant, and the low pressure refrigerant portion of becoming a mandarin is included in hole that forms in the low pressure (LP) cylinder and the pipe that inserts this hole.Herein, the part internal diameter that is processed in the cylinder outside when the hole is big and less at the part internal diameter of cylinder inboard, and when having ladder poor (step difference), the pipe that is used to introduce refrigeration agent can only be inserted into end difference (stepped portion).Therefore, help installing the pipe that is used to introduce refrigeration agent.
According to other scheme of the present invention, 2 stage rotary compressor also comprises and is used for the low pressure refrigerant portion of becoming a mandarin is connected to the become a mandarin middle pressure passageway of portion of compacting cryogen.By this structure, refrigerant compressed can be introduced in the high pressure compressed assembly in the low pressure compression assembly.
According to other scheme of the present invention, middle pressure passageway is the U-shaped pipe that passes seal container.By this structure, be easy to install the pipe that is used for realizing pressure passageway.
According to other scheme of the present invention, middle pressure passageway is the internal channel that is limited to secondary compression assembly inside.In this structure, middle compacting cryogen only flows in seal container, thereby can reduce the vibration and the noise of whole compressor.In addition, the length of the middle pressure passageway that the compacting refrigerant flow is crossed in can shortening reduces the pressure loss thus.
According to other scheme of the present invention, 2 stage rotary compressor also comprises the ascending pipe that is connected to middle pressure passageway.In this structure, in phase separator, isolate vapor phase refrigerant from the refrigeration agent of the condenser of flowing through, this vapor phase refrigerant is injected in the 2 stage rotary compressor, thereby can improve the compression efficiency of compressor.
According to other scheme of the present invention, 2 stage rotary compressor also comprises the middle pressure chamber that is arranged on the middle pressure passageway.By this structure, can remedy at the discharge process of low pressure compression assembly and high pressure compressed assembly and the phase difference between the suction process, stably middle compacting cryogen is supplied to the high pressure compressed assembly.
According to other scheme of the present invention, middle pressure chamber is limited by bearing and bearing cap.By this structure, press chamber in can forming easily and need not any independent member.
According to other scheme of the present invention, middle pressure chamber is arranged on one of any the locating in the upper and lower of secondary compression assembly.
Beneficial technical effects
According to 2 stage rotary compressor of the present invention, can be according to the compression volume and the volume flowrate of each compression assembly, control and be used for the low pressure refrigerant that refrigeration agent is introduced the low pressure compression assembly the become a mandarin size of portion of middle compacting cryogen that the size of portion and the compacting cryogen that is used for compressing at the low pressure compression assembly introduce the high pressure compressed assembly that becomes a mandarin is improved the compression efficiency of compressor thus.
In addition,, can control the become a mandarin size of portion of each refrigeration agent, improve the compression efficiency of compressor thus according to the become a mandarin structure of portion of each refrigeration agent according to 2 stage rotary compressor of the present invention.
Description of drawings
Fig. 1 is the view that shows an example of traditional two rotary compressors;
Fig. 2 is the view that shows an example of traditional 2 stage rotary compressor;
Fig. 3 is the schematic representation that shows an example of circuit that comprises 2 stage rotary compressor;
Fig. 4 shows the view of 2 stage rotary compressor according to an embodiment of the invention;
Fig. 5 shows the view of the low pressure compression assembly of 2 stage rotary compressor according to an embodiment of the invention;
Fig. 6 and Fig. 7 observe the view of a plurality of parts of 2 stage rotary compressor according to an embodiment of the invention for showing from top and bottom respectively;
Fig. 8 shows the sectional view of 2 stage rotary compressor according to an embodiment of the invention;
Fig. 9 shows an example that is arranged on the rotating shaft in the 2 stage rotary compressor according to an embodiment of the invention;
Figure 10 is the view that shows the 2 stage rotary compressor that ascending pipe according to an embodiment of the invention, wherein is installed;
Figure 11 and Figure 12 for be in respectively U-shaped pipe and internal channel as under the situation of middle pressure passageway, according to the schematic representation of the suction diameter of 2 stage rotary compressor of the present invention;
Figure 13 and Figure 14 are for showing the become a mandarin view of example of portion of the low pressure refrigerant that is included in the 2 stage rotary compressor according to an embodiment of the invention respectively;
Figure 15 is the view that shows an example of high-pressure cylinder, the diameter of portion so that the middle compacting cryogen that comparison forms with multiple size becomes a mandarin; And
Figure 16 is become a mandarin portion's diameter d 2 and low pressure refrigerant become a mandarin the ratio d2/d1 of portion's diameter d 1 and the chart of EER of compacting cryogen in showing.
Embodiment
Below, describe the preferred embodiments of the present invention in detail with reference to accompanying drawing.
Fig. 3 is the schematic representation that shows an example of the refrigerating circulation system (freezing cycle) of being constructed by 2 stage rotary compressor.Refrigerating circulation system comprises 2 stage rotary compressor 100, condenser 300, vaporizer 400; Phase separator 500, four-way valve 600 etc.Condenser 300 constitutes indoor unit, and compressor 100, vaporizer 400 and phase separator 500 constitute outdoor unit.Refrigerant compressed is introduced in the condenser 300 by four-way valve 600 in compressor 100.Refrigerant compressed gas and ambient air carry out heat exchange and are condensed.The refrigeration agent that is condensed becomes low pressure by expansion valve.The refrigeration agent that flows through expansion valve is separated into gas and liquid in phase separator 500.Liquid inflow evaporator 400.Liquid carries out heat exchange and is evaporated in vaporizer 400, be introduced in the storage 200 and be transported to low pressure compression assembly (not shown) from the refrigeration agent inflow pipe 151 of storage 200 by compressor 100 with gas phase.In addition, isolated gas is introduced in the compressor 100 by ascending pipe 153 in phase separator 500.Middle compacting cryogen that compresses in the low pressure compression assembly of compressor 100 and the refrigeration agent of carrying by ascending pipe 153 are supplied to the high pressure compressed assembly (not shown) of compressor, thereby are compressed into high pressure and are discharged to outside the compressor 100 by refrigerant discharge leader 152.
Fig. 4 shows the view of 2 stage rotary compressor according to an embodiment of the invention.2 stage rotary compressor 100 begins to comprise low pressure compression assembly 120, intermediate plate 140, high pressure compressed assembly 130 and motor 110 from the bottom in seal container 101 according to an embodiment of the invention.In addition, 2 stage rotary compressor 100 comprises the refrigeration agent inflow pipe 151 that is connected to storage 200 and is used for refrigerant compressed is discharged to refrigerant discharge leader 152 outside the seal container 101 that this refrigeration agent inflow pipe 151 and refrigerant discharge leader 152 pass seal container 101.
Low pressure compression assembly 120 and high pressure compressed assembly 130 can be with the intermediate plates 140 that is arranged between them, according to the sequence stack that begins low pressure compression assembly 120-intermediate plate 140-high pressure compressed assembly 130 from the bottom.On the contrary, low pressure compression assembly 120 and high pressure compressed assembly 130 also can be according to the sequence stacks that begins high pressure compressed assembly 130-intermediate plate 140-low pressure compression assembly 120 from the bottom.In addition, stacking order regardless of low pressure compression assembly 120, intermediate plate 140 and high pressure compressed assembly 130, below the assembly that piles up and above lower bearing 161 and upper bearing (metal) 162 are installed, be beneficial to the rotation of rotating shaft 113 and support the load of assembly of each vertical stacking of secondary compression assembly.Upper bearing (metal) 162 is fixed to seal container to support the load of secondary compression assembly by three spot welding.
The refrigeration agent inflow pipe 151 that passes seal container 101 from the outside is connected to low pressure compression assembly 120.In addition, below low pressure compression assembly 120, be provided with lower bearing 161 and lower cover 171.Press chamber P between lower bearing 161 and lower cover 171, being limited with
mThe middle chamber P that presses
mBe the space that refrigerant compressed is discharged in low pressure compression assembly 120, and be the space of interim storage refrigeration agent before refrigeration agent is introduced into high pressure compressed assembly 130.The middle chamber P that presses
mFlow to buffer space on the passage of high pressure compressed assembly 130 from low pressure compression assembly 120 as refrigeration agent.
Be formed with the exhaust port (not shown) on the top that is arranged at the upper bearing (metal) 162 on the high pressure compressed assembly 130.The high-pressure refrigerant of discharging by the exhaust port of upper bearing (metal) 162 from high pressure compressed assembly 130 is discharged to the outside by the refrigerant discharge leader 152 that is arranged on seal container 101 tops.
At lower bearing 161, low pressure compression assembly 120, be formed with internal channel 180 in intermediate plate 140 and the high pressure compressed assembly 130, this internal channel is connected to such an extent that make refrigeration agent flow to high pressure compressed assembly 130 from low pressure compression assembly 120.Thereby internal channel 180 is vertically that form and parallel to an axis compressor 100.
Fig. 5 is the sectional view that shows low pressure compression assembly 120.Low pressure compression assembly 120 comprises low pressure (LP) cylinder 121, low pressure eccentric part 122, low pressing roller 123, low pressure blade 124, low pressure resilient member 125, low pressure goes into discharge orifice 126 and middle pressure portals 127.The central part of low pressure (LP) cylinder 121 is passed in rotating shaft 113, and low pressure eccentric part 122 is fixed to rotating shaft 113.Herein, low pressure eccentric part 122 can form with rotating shaft 113.In addition, hang down pressing roller 123 and be installed in rotation on the low pressure eccentric part 122, make low pressing roller 123 roll and rotation along the internal diameter of low pressure (LP) cylinder 121 owing to the rotation of rotating shaft 113.Low pressure is gone into discharge orifice 126 and middle pressure 127 both sides that are formed on low pressure blade 124 of portalling.In addition, separated by low pressure blade 124 and low pressing roller 123 in low pressure (LP) cylinder 121 volume inside, refrigeration agent before the feasible compression and compression refrigeration agent afterwards coexist in low pressure (LP) cylinder 121.Separate and comprise that low pressure goes into the part of discharge orifice 126 and be called the low pressure refrigerant S of portion that becomes a mandarin by low pressure blade 124 and low pressing roller 123
1, and in comprising pressure portal 127 part be called in compacting cryogen discharge portion D
mAt this moment, thus low pressure resilient member 125 be used for to low pressure blade 124 apply power make low pressure blade 124 can with the device of low pressing roller 123 Continuous Contact.Be formed with vane hole 124h so that low pressure blade 124 is set in this vane hole in low pressure (LP) cylinder 121, this vane hole along continuous straight runs passes low pressure (LP) cylinder 121.Low pressure blade 124 is conducted through vane hole 124h, and the low pressure resilient member 125 that low pressure blade 124 is applied power passes low pressure (LP) cylinder 121 and passes vane hole 124h and extends to seal container 101.One end of low pressure resilient member 125 contacts with low pressure blade 124, and the other end of low pressure resilient member 125 contacts with seal container 101, contacts continuously with low pressing roller 123 so that promote low pressure blade 124.
In addition, press intercommunicating pore 120a in low pressure (LP) cylinder 121, being formed with, make the middle pressure chamber P of refrigerant compressed in low pressure compression assembly 120 by limiting by lower bearing 161
mBe introduced in the high pressure compressed assembly 130.Middle pressure intercommunicating pore 120a forms and avoids refrigeration agent inflow pipe 151, and the feasible middle intercommunicating pore 120a that presses can not overlap with the refrigeration agent inflow pipe 151 that insertion low pressure is gone in the discharge orifice 126, and promptly internal channel 180 can not overlap with refrigeration agent inflow pipe 151.Even middle pressure intercommunicating pore 120a and refrigeration agent inflow pipe 151 parts overlap joint, the compacting cryogen was therefrom pressed chamber P during middle pressure intercommunicating pore 120a also made
mFlow to high pressure compressed assembly 130.Yet, in this case, can take place as with the identical loss of sectional area of the internal channel 180 of refrigeration agent inflow pipe 151 overlap joint.In addition, because refrigeration agent is walked around refrigeration agent inflow pipe 151, so can reduce pressure.
As shown in Figure 5, when low pressure eccentric part 122 rotate owing to the rotation of rotating shaft 113 and low pressing roller 123 when low pressure (LP) cylinder 121 rolls, the low pressure S of portion that becomes a mandarin
1Volume increase the low pressure S of portion that becomes a mandarin thus
1Has low pressure.Therefore, refrigeration agent is gone into discharge orifice 126 by low pressure and is introduced into.Simultaneously, middle pressure discharge portion D
mVolume reduce, make and to press discharge portion D in being filled in
mIn refrigeration agent be compressed and portal and 127 be discharged from by middle pressure.The low pressure S of portion that becomes a mandarin
1With middle pressure discharge portion D
mVolume change continuously corresponding to the rotation of low pressure eccentric part 122 and low pressing roller 123, and rotate each time and discharge compressed refrigeration agent.
Fig. 6 to Fig. 8 shows the view of a plurality of parts of 2 stage rotary compressor according to an embodiment of the invention.Lower bearing 161, low pressure compression assembly 120, intermediate plate 140 and high pressure compressed assembly 130 begin to pile up continuously from the bottom.As mentioned above, low pressure refrigerant is gone into discharge orifice 126 by refrigeration agent inflow pipe 151 and low pressure and is introduced in the low pressure (LP) cylinder 121, is compressed and portals by middle pressure 127 to press chamber P in being discharged to
m, pressing chamber in this is the space that bottom surface, lower bearing 161 and lower cover 171 by low pressure compression assembly 120 limit.In the pressure 161h that portals be formed in the lower bearing 161, with middle pressure 127 overlap joints that portal, portalling in the middle pressure of lower bearing 161 is equipped with the valve (not shown) below the 161h.As middle pressure discharge portion D at low pressure compression assembly 120
mWhen middle refrigerant compressed is compressed into predetermined pressure, during being discharged to, this refrigeration agent presses chamber P
mPress chamber P in being discharged to
mRefrigeration agent by be formed on middle pressure intercommunicating pore 161a in the lower bearing 161, be formed on middle pressure intercommunicating pore 120a in the low pressure (LP) cylinder 121, be formed on the middle pressure intercommunicating pore 140a in the intermediate plate 140 and be formed in the high-pressure cylinder 131 in be pressed into stream groove 130a and be introduced in the high pressure compressed assembly 130.At the middle compacting cryogen that in low pressure compression assembly 120, is compressed out, be pressed into stream groove 130a in the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 161a of lower bearing 161, the middle pressure intercommunicating pore 120a of low pressure compression assembly 120, intermediate plate 140 and the high pressure compressed assembly 130 and limit internal channel 180.Herein, high pressure compressed assembly 130 in be pressed into the shape that stream groove 130a forms inclined groove and be communicated with inner space with high-pressure cylinder 131.In be pressed into stream groove 130a the part bottom contact with the middle pressure intercommunicating pore 140a of intermediate plate 140, thereby become the part of internal channel 180.The middle compacting cryogen of compression by in be pressed into stream groove 130a and be introduced in the high-pressure cylinder 131.In the middle of compacting cryogen when being supplied to high pressure compressed assembly 130 by internal channel 180, high pressure compressed assembly 130 is compressed to high pressure with the running principle identical with low pressure compression assembly 120 with middle compacting cryogen.
As mentioned above, when the internal channel 180 that is used for suppressing cryogen is not to be limited by independent pipe, and when being formed in the seal container 101, can suppressing noise and can reduce the length of internal channel 180, thereby can reduce the refrigerant pressure loss that causes by resistance.In the above description, although middle pressure chamber P
mBe formed on lower bearing 161 places, but also can be formed on one of any the locating in upper bearing (metal) 162 and the intermediate plate 140.Therefore, detailed structure can change a little.Yet in each case, internal channel 180 all is formed in the secondary compression assembly, is directed to high pressure compressed assembly 130 with the middle compacting cryogen that will compress in middle pressure compression assembly 120.By this structure because reduced to be used for to guide the length of the passage of compacting cryogen, so can make the flow losses minimum, and because refrigeration agent can't flow through and pass the connecting tube of seal container 101, so can suppress noise and vibration.
Herein, in order to prevent 151 blocking-up of 180 cooled doses of inflow pipes of internal channel, as axial finding along compressor 100, constitute the middle pressure intercommunicating pore 140a of middle pressure intercommunicating pore 120a, intermediate plate 140 of the low pressure compression assembly 120 of internal channel 180 and high pressure compressed assembly 130 in be pressed into stream groove 130a and refrigeration agent inflow pipe 151 spaced apart.
The middle pressure intercommunicating pore 161a of lower bearing 161 forms the insertion position of the refrigeration agent inflow pipe 151 of avoiding being connected to low pressure (LP) cylinder 121, presses in thus the intercommunicating pore 161a can cooled dose of inflow pipe 151 blocking-up.Refrigeration agent inflow pipe 151 is inserted in the low pressure that forms in the low pressure (LP) cylinder 121 and goes in the discharge orifice 126.It is adjacent with low pressure blade patchhole 124h that low pressure is gone into discharge orifice 126, and low pressure blade 124 (referring to Fig. 5) will be inserted into this low pressure blade and insert in the hole.This is because if low pressure is gone into discharge orifice 126 and (shown in Figure 5) low pressure blade 124 distance, and then in the inner space of low pressure (LP) cylinder 121, the dead volume that is helpless to the refrigeration agent compression can increase.
In addition, be pressed into stream groove 130a in the high-pressure cylinder 131 and be not from the bottom of high-pressure cylinder 131 and form to ground, top, but be formed obliquely to the inner space from the bottom of high-pressure cylinder 131.Herein, in be pressed into stream groove 130a adjacent with high pressure vane hole 134h, high pressure blade (not shown) will be inserted in this high pressure vane hole.This is because if in low pressure compression assembly 120, in the middle of be pressed into stream groove 130a when adjacent, the dead volume minimizing in the inner space of high-pressure cylinder 131 with high pressure blade (not shown).
Low pressure blade 124 is arranged on the identical axis with high pressure blade (not shown).Therefore, the middle pressure intercommunicating pore 161a that in lower bearing 161, forms with in high-pressure cylinder 131, form in be pressed into stream groove 130a and be not formed on the identical axis, but along continuous straight runs is spaced apart from each other.According to third embodiment of the invention, the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 forms spirality, with the middle pressure intercommunicating pore 161a with lower bearing 161 be connected to high-pressure cylinder 131 in be pressed into stream groove 130a.The middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 forms spirality to overlap each other.That is to say, the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 form spirality with each other the overlap joint, thereby limit the spiral intercommunicating pore.At this moment, the middle pressure intercommunicating pore 161a of an end of spiral intercommunicating pore and lower bearing 161 overlap joint, and the other end of spiral intercommunicating pore and high-pressure cylinder 131 in be pressed into stream groove 130a and overlap.Herein, the end of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 is connected to the middle pressure intercommunicating pore 161a of lower bearing 161.That is to say, an end that contacts with middle pressure intercommunicating pore 161a lower bearing 161 the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 is to form along the vertical direction of low pressure (LP) cylinder 121, and the other parts of middle pressure intercommunicating pore 120a are entirely formed as spirality, and promptly its bottom passes through and raises gradually.On the contrary, the other end of the middle pressure intercommunicating pore 140a of intermediate plate 140, promptly above-mentioned spiral intercommunicating pore with high-pressure cylinder 131 in be pressed into stream groove 130a overlap joint the other end be that vertical direction along intermediate plate 140 forms.In addition, middle pressure intercommunicating pore 140a is entirely formed as spirality, promptly its upper end from lower bearing 161 end to end of pressure intercommunicating pore 161a overlap joint raise gradually.
Form under the spiral situation at the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and the middle pressure intercommunicating pore 140a of intermediate plate 140, when refrigeration agent flows through the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140, reduced the resistance that acts on refrigeration agent.Simultaneously, the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 can form the circular arc and the spirality of top height or bottom constant height.
In addition, when the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 formed spirality or circular arc, fixed hole 120b and 140b can be formed on the middle pressure intercommunicating pore 120a of spirality or circular arc and the central part of 140a.In general, by bolt lower bearing 161, low pressure (LP) cylinder 121, intermediate plate 140, high-pressure cylinder 131 and upper bearing (metal) 162.Herein, bolt hole 161b, 120b, 130b, 140b and 162b should form and avoid various members and internal channel, for example the refrigeration agent inflow pipe 151, middle pressure intercommunicating pore 161a, 120a, 140a and 162a, in be pressed into stream groove 130a and middle pressure and portal 127.In addition, should form fixed hole 161b, 120b, 130b, 140b and 162b at least three positions, to disperse retention force equably to whole compression assembly 105.At this moment, the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 is longer than being pressed into stream groove 130a in the middle pressure intercommunicating pore 161a of lower bearing 161 and the high-pressure cylinder 131, and this makes and is difficult to form fixed hole 161b, 120b, 130b, 140b and 162b with a plurality of numbers.Therefore, when the middle pressure intercommunicating pore 140a of the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121 and intermediate plate 140 forms spirality or circular arc, because fixed hole 161b, 120b, 130b, 140b and 162b are formed on the central authorities of spirality or circular arc, fixed hole 161b, 120b, 130b, 140b and 162b can be disperseed to be arranged in the whole compression assembly 105.
Fig. 9 shows the view that is arranged on according to an example of the rotating shaft in the 2 stage rotary compressor of the present invention.Low pressure eccentric part 122 and high pressure eccentric part 132 link to rotating shaft 113.In order to reduce vibration, low pressure eccentric part 122 and high pressure eccentric part 132 common phase differences with 180 ° link to rotating shaft 113.In addition, rotating shaft 113 is axles of hollow, is being formed with oil hole 103a under the low pressure eccentric part 122 and on high pressure eccentric part 132.In addition, thin plate stirrer (thin-plate stirrer) 103b with helically bent is inserted in the rotating shaft 113.Stirrer 103b is fitted in the rotating shaft 113, and rotates with rotating shaft 113 during rotating shaft 113 is rotated.When stirrer 103b rotated owing to the rotation of rotating shaft 113, the inside along rotating shaft 113 was raised by stirrer 103b to be filled in oil in the bottom of seal container 101 (referring to Fig. 4).Part oil is discharged to low pressure (LP) cylinder 121, intermediate plate 140 and high-pressure cylinder 131 by the oil hole 103a that is formed in the rotating shaft 113, lubricated thus low pressing roller 123 (referring to Fig. 5) and high pressing roller (not shown).
Figure 10 shows according to view first embodiment of the invention, that insert the compressor of ascending pipe in it.In two stage compressor 100 according to the present invention, because internal channel 180 is not independent pipe, so be used for being infused in the arbitrary portion that the ascending pipe of phase separator 500 isolated refrigerant gas can be installed in internal channel 180.For example, through hole 153h is formed on and presses chamber P in the formation
mLower bearing 161, intermediate plate 140 and high-pressure cylinder 131 in any one in, and ascending pipe 153 is inserted in the through hole 153h to inject refrigerant gas.As shown in Figure 8, form the middle pressure of passing low pressure (LP) cylinder 121 at through hole 153h and portal 127 or be formed under the situation in the lower bearing 161, when ascending pipe 153 is inserted into through hole 153h, along in press chamber P
mThe pressure loss takes place with internal channel 180.Yet,, press chamber P during liquid phase refrigerant is collected in although introduced liquid phase refrigerant by ascending pipe 153
mThe bottom, so compressor 100 can stably move.
Figure 11 and Figure 12 be illustrate U-shaped pipe and internal channel by under the state of pressure passageway in being used separately as, according to the schematic representation of the suction diameter of 2 stage rotary compressor of the present invention.
With reference to Figure 11, utilize pressure passageway in 182 conducts of U-shaped pipe according to one embodiment of the invention, refrigeration agent inflow pipe 151 is inserted into low pressure compression assembly 120.The low pressure refrigerant of introducing by refrigeration agent inflow pipe 151 is compressed and is discharged to the middle chamber P that presses in low pressure compression assembly 120
mSubsequently, refrigeration agent is introduced into high pressure compressed assembly 130 by U-shaped pipe 182, is compressed into high pressure and is discharged to seal container 101, presses chamber P during the two ends of this U-shaped pipe 182 are connected to
mWith high pressure compressed assembly 130.Herein, the diameter of refrigeration agent inflow pipe 151 (referring to Fig. 5, refrigeration agent inflow pipe 151 low pressure that is inserted in the low pressure compression assembly 120 of diameter is thus gone into discharge orifice 126) becomes the become a mandarin diameter d 1 of portion of low pressure refrigerant.In addition, press chamber P in being connected to of U-shaped pipe 182
mThe diameter of an end equal the diameter of the other end that is connected to high pressure compressed assembly 130 of this U-shaped pipe, and the diameter of U-shaped pipe 182 is become a mandarin diameter d 2 of portion of middle compacting cryogen.
With reference to Figure 12, utilize pressure passageway in internal channel 180 conducts according to another embodiment of the present invention, refrigeration agent inflow pipe 151 is inserted into low pressure compression assembly 120, and the middle compacting cryogen of compression in low pressure compression assembly 120 is introduced in the high pressure compressed assembly 130 by the internal channel 180 that is limited in the secondary compression assembly 105.Be similar to the embodiment who utilizes pressure passageway in 182 conducts of U-shaped pipe of the present invention, the diameter of refrigeration agent inflow pipe 151 (referring to Fig. 5, refrigeration agent inflow pipe 151 low pressure inserted in the low pressure compression assembly 120 of diameter is thus gone into discharge orifice 126) becomes the become a mandarin diameter d 1 of portion of low pressure refrigerant.In the become a mandarin diameter d 2 of portion of compacting cryogen become the diameter of internal channel 180.
Figure 13 and Figure 14 are for showing the become a mandarin view of example of portion of the low pressure refrigerant that is included in the 2 stage rotary compressor according to an embodiment of the invention respectively.Figure 13 shows first example.From the external diameter of low pressure (LP) cylinder 121 to internal diameter, be formed at low pressure in the low pressure (LP) cylinder 121 and go under the situation of constant diameter of discharge orifice 126, the constant diameter that low pressure is gone into discharge orifice 126 is the become a mandarin diameter d 1 of portion of low pressure refrigerant.
Figure 14 shows second example.Low pressure go into discharge orifice 126 at the diameter of the internal side diameter of low pressure (LP) cylinder 121 less than diameter at the outside diameter of low pressure (LP) cylinder 121.That is to say that low pressure is gone into discharge orifice 126, and to have a ladder poor.What herein, low pressure was gone into discharge orifice 126 is the become a mandarin diameter d 1 of portion of low pressure refrigerant at internal side diameter than minor diameter.Go into discharge orifice 126 in low pressure and have under the situation of ladder difference, be restricted because refrigeration agent inflow pipe 151 (referring to Fig. 4) insertion low pressure is gone into the insertion position of discharge orifice 126, so refrigeration agent inflow pipe 151 (referring to Fig. 4) can be installed easily.
Figure 15 is the view that shows an example of high-pressure cylinder, in order to the become a mandarin diameter of portion of the middle compacting cryogen that relatively forms with multiple size, and Figure 16 is become a mandarin diameter d 2 and the low pressure refrigerant of portion 136 become a mandarin the ratio d2/d1 of diameter d 1 of portion 126 and the chart of EER of compacting cryogen in showing.As Figure 15 and shown in Figure 16, the compacting cryogen portion 136 that becomes a mandarin in high-pressure cylinder 131, being formed with, U-shaped pipe 182 (referring to Figure 11) will insert in this compacting cryogen and become a mandarin in the portion.In the compacting cryogen become a mandarin portion 136 diameter d 2 can less than, be equal to and greater than the become a mandarin diameter d 1 (referring to Figure 11) (A, B and C) of portion 126 of low pressure refrigerant.Herein, under middle compacting cryogen became a mandarin the excessive situation of the diameter d 2 of portion 136, the internal capacity that can be actually used in compression of high-pressure cylinder 131 reduced, and suction pressure descends.That is to say that actual compression distance shortens and suction pressure descends, and has increased loss thus.Therefore, preferably, become a mandarin diameter d 2 and the low pressure refrigerant of portion 136 of middle compacting cryogen becomes a mandarin the ratio d2/d1 of diameter d 1 of portion 126 less than 1.1.
Simultaneously, under middle compacting cryogen became a mandarin the too small situation of the diameter d 2 of portion 136, actual compression distance prolonged and the internal capacity of high-pressure cylinder 131 increases.Yet, when central compacting cryogen flows,, make total losses increase because friction etc. have produced flow losses.Therefore, preferably, become a mandarin diameter d 2 and the low pressure refrigerant of portion 136 of middle compacting cryogen becomes a mandarin the ratio d2/d1 of diameter d 1 of portion 126 greater than 0.5.
That is to say that preferably, middle compacting cryogen the become a mandarin diameter ratio d2/d1 of portion 126 of diameter d 2 and the low pressure refrigerant of portion 136 that becomes a mandarin satisfies following formula:
In this case, according to experiment, EER can rise to greater than 9.6.Particularly, become a mandarin under the situation of ratio d2/d1 in 0.6 to 1.0 scope of diameter d 1 of portion 126 at become a mandarin diameter d 2 and the low pressure refrigerant of portion 136 of middle compacting cryogen, EER can rise to greater than 9.8.
Most preferably, be that EER can rise to greater than 10.0 under 0.9 to 1.0 the situation in middle compacting cryogen the become a mandarin value of ratio d2/d1 of diameter d 1 of portion 126 of diameter d 2 and the low pressure refrigerant of portion 136 that becomes a mandarin
Figure 15 illustrate be arranged on according to an embodiment utilize the U-shaped pipe as in high-pressure cylinder in the two stage compressor of pressure passageway.On the other hand, utilize according to another embodiment internal channel as under the situation of high-pressure cylinder of pressure passageway, the compacting cryogen diameter d 2 of portion 136 that becomes a mandarin during the diameter of internal channel becomes, and utilize identical condition.
With reference to Fig. 3 to Figure 10 the schematic running principle of 2 stage rotary compressor according to an embodiment of the invention is described.
The circuit refrigeration agent was stored in the storage 200 before being introduced into compressor 100 temporarily in refrigerating circulation system.Storage 200 is used as the interim storage area of refrigeration agent, and is used as gas-liquid separator only gas is introduced in the compressor 100.Gaseous refrigerant flows to low pressure compression assembly 120 low pressure (LP) cylinders 121 from storage 200 by refrigeration agent inflow pipe 151.Refrigeration agent inflow pipe 151 passes seal container 101 and by being welded and fixed to seal container 101.In addition, refrigeration agent inflow pipe 151 is inserted into the refrigeration agent that is formed in the low pressure (LP) cylinder 121 and goes in the discharge orifice 126.Refrigeration agent is gone into discharge orifice 126 and is formed the internal diameter that arrives low pressure (LP) cylinder 121.Go into the refrigeration agent that discharge orifice 126 is introduced low pressure (LP) cylinders 121 inner spaces by refrigeration agent, be compressed by the space that limits by low pressure (LP) cylinder 121, low pressing roller 123 and low pressure blade 124 the caused volume-variation of relative movement because of low pressure (LP) cylinder 121 and low pressing roller 123.Refrigerant compressed is transported to high-pressure cylinder 131 by internal channel 180 from low pressure (LP) cylinder 121, and is compressed by high pressure compressed assembly 130.
During internal channel 180 connects into and makes the compacting cryogen by the middle pressure of low pressure (LP) cylinder 121 portal 127, middle pressure chamber P
m, the middle pressure intercommunicating pore 140a of middle pressure intercommunicating pore 120a, intermediate plate 140 of middle pressure intercommunicating pore 161a, low pressure (LP) cylinder 121 of lower bearing 161 and high-pressure cylinder 131 in be pressed into stream groove 130a, flow to high-pressure cylinder 131 from low pressure (LP) cylinder 121.Herein, middle pressure chamber P
mCan replace or can be removed by pipeline.
That is to say, portal and 127 be discharged to the middle pressure chamber P that is formed under the low pressure (LP) cylinder 121 by being formed on middle pressure in the low pressure (LP) cylinder 121 by low pressure compression assembly 120 refrigerant compressed
mThe middle chamber P that presses
mLimit by lower bearing 161 and lower cover 171.In addition, the middle pressure 161h that portals is formed in the lower bearing 161, with the middle pressure of low pressure (LP) cylinder 121 127 overlap joints that portal.In addition, be used for opening and closing the portal valve 191 of 161h of pressure and be installed in lower bearing 161.When surpassing setting pressure, the middle pressure that valve 191 is opened low pressure (LP) cylinder 121 portals 127 and the middle pressure of lower bearing 161 161h that portals.Be discharged to the middle chamber P that presses owing to opening valve 191
mThe middle pressure intercommunicating pore 140a of middle pressure intercommunicating pore 120a, intermediate plate 140 of the middle pressure intercommunicating pore 161a of middle compacting cryogen by lower bearing 161, low pressure (LP) cylinder 121 and high-pressure cylinder 131 in be pressed into the inner space that stream groove 130a is introduced into high-pressure cylinder 131.Herein, ascending pipe 153 is connected to the middle pressure intercommunicating pore 120a of low pressure (LP) cylinder 121, thereby the gaseous refrigerant that will separate in phase separator 500 injects internal channel 180.The pressure of the refrigeration agent that separates in phase separator 500 is higher than the refrigeration agent of the vaporizer 400 of flowing through.Therefore, when the refrigeration agent (refrigerant compressed in low pressure compression assembly 120) that separates is introduced in the high pressure compressed assembly 130, and when being compressed and discharging, can reduce the input power of compressor 200 in phase separator 500.
The refrigeration agent that in phase separator 500, separates and in low pressure compression assembly 120 refrigerant compressed be introduced in the high-pressure cylinder 131 by being pressed into stream groove 130a in the high-pressure cylinder 131, and be compressed into high pressure with the running principle identical with low pressure compression assembly 120 by high pressure compressed assembly 130.The refrigeration agent that is compressed to high pressure in high pressure compressed assembly 130 is discharged to the discharge space D that is limited between upper bearing (metal) 162 and the loam cake 172 by the high pressure tap hole 137 of high-pressure cylinder 131 and the high pressure tap hole 162h of upper bearing (metal) 162.Herein, valve 192 is installed with the high pressure tap hole 137 of opening and closing high-pressure cylinder 131 and the high pressure tap hole 162h of upper bearing (metal) 162 on upper bearing (metal) 162.Therefore, only be compressed when surpassing predetermined pressure when refrigeration agent in high pressure compressed assembly 130, valve 192 is opened the high pressure tap hole 137 of high-pressure cylinder 131 and the high pressure tap hole 162h of upper bearing (metal) 162, refrigeration agent is expelled to discharge space D thus.High-pressure refrigerant is stored in temporarily discharges among the D of space, is discharged to the top of seal container 101 subsequently by the exhaust port 172p of loam cake 172.High-pressure refrigerant is filled in the seal container 101.The discharge tube 152 that is filled in the top of high-pressure refrigerant by passing seal container 101 in the seal container 101 is discharged to the outside and circulates in refrigerating circulation system, introduce in the compressor 100 by storage 200 and phase separator 500 once more, and in compressor 100, be compressed.
In addition, the lubricant oil that is used for lubricated compression assembly is filled in seal container 101 bottoms.Lubricant oil is raised along the inboard of rotating shaft 113 owing to insert the rotation of the stirrer 103b in the rotating shaft 113, and is supplied to low pressure compression assembly 120 and high pressure compressed assembly 130 so that compression assembly 105 is lubricated by being formed on oil hole 103a in the rotating shaft 113.In addition, oil can be supplied to low pressure compression assembly 120 and high pressure compressed assembly 130 with lubricated compression assembly 105 by being formed on vane hole 124h in low pressure (LP) cylinder 121 and the high- pressure cylinder 131 and 134h.
Claims (12)
1. 2 stage rotary compressor comprises:
Seal container;
The secondary compression assembly is arranged in the described seal container and comprises low pressure compression assembly, intermediate plate and high pressure compressed assembly;
The low pressure refrigerant portion that becomes a mandarin is arranged in the described low pressure compression assembly to introduce low pressure refrigerant; And
In the compacting cryogen portion that becomes a mandarin, be arranged in the described high pressure compressed assembly being introduced in the middle compacting cryogen that compresses in the described low pressure compression assembly,
In wherein said the compacting cryogen become a mandarin portion diameter greater than described low pressure refrigerant become a mandarin portion 0.5 times of diameter and less than become a mandarin 1.1 times of diameter of portion of described low pressure refrigerant.
2. 2 stage rotary compressor as claimed in claim 1, wherein said in the become a mandarin diameter of portion of compacting cryogen be become a mandarin 0.6 times to 1.0 times of diameter of portion of described low pressure refrigerant.
3. 2 stage rotary compressor as claimed in claim 2, wherein said in the become a mandarin diameter of portion of compacting cryogen be become a mandarin 0.9 times to 1.0 times of diameter of portion of described low pressure refrigerant.
4. 2 stage rotary compressor as claimed in claim 1, wherein said low pressure compression assembly comprises the low pressure (LP) cylinder in the space that is used to provide compressed refrigerant, thereby and the described low pressure refrigerant portion of becoming a mandarin be the pipe that is inserted into the refrigeration agent compression volume that arrives described low pressure (LP) cylinder.
5. 2 stage rotary compressor as claimed in claim 1, wherein said low pressure compression assembly comprises the low pressure (LP) cylinder in the space that is used to provide compressed refrigerant, and the described low pressure refrigerant portion of becoming a mandarin is included in the hole that forms in the described low pressure (LP) cylinder and inserts pipe in the described hole.
6. 2 stage rotary compressor as claimed in claim 1 also comprises being used for the described low pressure refrigerant portion of becoming a mandarin is connected to the become a mandarin middle pressure passageway of portion of described compacting cryogen.
7. 2 stage rotary compressor as claimed in claim 6, wherein said middle pressure passageway is the U-shaped pipe that passes described seal container.
8. 2 stage rotary compressor as claimed in claim 6, wherein said middle pressure passageway is the internal channel that is limited to described secondary compression assembly inside.
9. 2 stage rotary compressor as claimed in claim 6 also comprises the ascending pipe that is connected to described middle pressure passageway.
10. 2 stage rotary compressor as claimed in claim 6 also comprises the middle pressure chamber that is arranged on the described middle pressure passageway.
11. 2 stage rotary compressor as claimed in claim 10, the wherein said middle chamber of pressing is limited by bearing and bearing cap.
12. 2 stage rotary compressor as claimed in claim 10 presses in wherein said chamber to be set in the upper and lower of described secondary compression assembly any one.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020070115656A KR101381085B1 (en) | 2007-11-13 | 2007-11-13 | 2 stage rotary compressor |
| KR10-2007-0115656 | 2007-11-13 | ||
| PCT/KR2008/001797 WO2009064042A1 (en) | 2007-11-13 | 2008-03-31 | 2 stage rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101835988A true CN101835988A (en) | 2010-09-15 |
| CN101835988B CN101835988B (en) | 2012-11-21 |
Family
ID=40638871
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801128448A Active CN101835988B (en) | 2007-11-13 | 2008-03-31 | 2 stage rotary compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20100284847A1 (en) |
| KR (1) | KR101381085B1 (en) |
| CN (1) | CN101835988B (en) |
| WO (1) | WO2009064042A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671120A (en) * | 2012-09-25 | 2014-03-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Intermediate cooling medium flow passage and compressor comprising same |
| CN103807175A (en) * | 2012-11-13 | 2014-05-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Dual-rotor two-stage enthalpy increasing compressor, air conditioner and heat pump water heater |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012251485A (en) * | 2011-06-03 | 2012-12-20 | Fujitsu General Ltd | Rotary compressor |
| JP5586537B2 (en) * | 2011-07-28 | 2014-09-10 | 三菱電機株式会社 | Rotary two-stage compressor |
| JP6574519B2 (en) * | 2016-03-25 | 2019-09-11 | 東芝キヤリア株式会社 | Hermetic rotary compressor and refrigeration cycle apparatus |
| CN106168214A (en) * | 2016-06-29 | 2016-11-30 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of cylinder that turns increases enthalpy piston compressor and has its air conditioning system |
| JP6744062B2 (en) * | 2016-07-28 | 2020-08-19 | 広東美芝制冷設備有限公司 | Compressor, cooling/heating type refrigerating apparatus including the same, cooling-only type refrigerating apparatus |
Family Cites Families (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0420751A (en) * | 1990-05-15 | 1992-01-24 | Toshiba Corp | Freezing cycle |
| JP2768004B2 (en) * | 1990-11-21 | 1998-06-25 | 松下電器産業株式会社 | Rotary multi-stage gas compressor |
| JP2699724B2 (en) * | 1991-11-12 | 1998-01-19 | 松下電器産業株式会社 | Two-stage gas compressor |
| JP2000073974A (en) * | 1998-08-26 | 2000-03-07 | Daikin Ind Ltd | Two stage compressor and air conditioner |
| US7128540B2 (en) * | 2001-09-27 | 2006-10-31 | Sanyo Electric Co., Ltd. | Refrigeration system having a rotary compressor |
| CA2373905A1 (en) * | 2002-02-28 | 2003-08-28 | Ronald David Conry | Twin centrifugal compressor |
| US6631617B1 (en) * | 2002-06-27 | 2003-10-14 | Tecumseh Products Company | Two stage hermetic carbon dioxide compressor |
| JP4045154B2 (en) * | 2002-09-11 | 2008-02-13 | 日立アプライアンス株式会社 | Compressor |
| US6929455B2 (en) * | 2002-10-15 | 2005-08-16 | Tecumseh Products Company | Horizontal two stage rotary compressor |
| US6752605B2 (en) * | 2002-10-15 | 2004-06-22 | Tecumseh Products Company | Horizontal two stage rotary compressor with a bearing-driven lubrication structure |
| DE602004025560D1 (en) * | 2003-04-26 | 2010-04-01 | Camcon Ltd | ELECTROMAGNETIC VALVE CONTROL DEVICE |
| US6752608B1 (en) * | 2003-05-29 | 2004-06-22 | Tecumseh Products Company | Compressor crankshaft with bearing sleeve and assembly method |
| TWI344512B (en) * | 2004-02-27 | 2011-07-01 | Sanyo Electric Co | Two-stage rotary compressor |
| JP2006152931A (en) | 2004-11-30 | 2006-06-15 | Hitachi Home & Life Solutions Inc | Rotary two-stage compressor |
| JP2006177226A (en) * | 2004-12-22 | 2006-07-06 | Hitachi Home & Life Solutions Inc | Rotary compressor and air conditioner using the same |
| JP2006177223A (en) * | 2004-12-22 | 2006-07-06 | Hitachi Home & Life Solutions Inc | Rotary two stage compressor |
| JP2006177227A (en) | 2004-12-22 | 2006-07-06 | Hitachi Home & Life Solutions Inc | Rotary two-stage compressor |
| JP2007113542A (en) | 2005-10-24 | 2007-05-10 | Hitachi Appliances Inc | Hermetic two-stage rotary compressor |
| JP2008175111A (en) * | 2007-01-17 | 2008-07-31 | Daikin Ind Ltd | Compressor |
| JP4859694B2 (en) * | 2007-02-02 | 2012-01-25 | 三菱重工業株式会社 | Multistage compressor |
| JP5071967B2 (en) * | 2007-03-30 | 2012-11-14 | アネスト岩田株式会社 | Rotary compressor and operation control method thereof |
| JP2009097485A (en) * | 2007-10-19 | 2009-05-07 | Mitsubishi Heavy Ind Ltd | Compressor |
| JP2009167828A (en) * | 2008-01-11 | 2009-07-30 | Fujitsu General Ltd | Rotary compressor |
-
2007
- 2007-11-13 KR KR1020070115656A patent/KR101381085B1/en active IP Right Grant
-
2008
- 2008-03-31 WO PCT/KR2008/001797 patent/WO2009064042A1/en active Application Filing
- 2008-03-31 CN CN2008801128448A patent/CN101835988B/en active Active
- 2008-03-31 US US12/742,600 patent/US20100284847A1/en not_active Abandoned
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671120A (en) * | 2012-09-25 | 2014-03-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Intermediate cooling medium flow passage and compressor comprising same |
| CN103807175A (en) * | 2012-11-13 | 2014-05-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Dual-rotor two-stage enthalpy increasing compressor, air conditioner and heat pump water heater |
| CN103807175B (en) * | 2012-11-13 | 2016-11-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Birotor two-stage enthalpy-increasing compressor, air-conditioner and Teat pump boiler |
Also Published As
| Publication number | Publication date |
|---|---|
| US20100284847A1 (en) | 2010-11-11 |
| KR101381085B1 (en) | 2014-04-10 |
| KR20090049411A (en) | 2009-05-18 |
| CN101835988B (en) | 2012-11-21 |
| WO2009064042A1 (en) | 2009-05-22 |
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