CN102900669B - Two stage rotary compressor - Google Patents
Two stage rotary compressor Download PDFInfo
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- CN102900669B CN102900669B CN201210176442.2A CN201210176442A CN102900669B CN 102900669 B CN102900669 B CN 102900669B CN 201210176442 A CN201210176442 A CN 201210176442A CN 102900669 B CN102900669 B CN 102900669B
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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
- F04C23/008—Hermetic pumps
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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
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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
- 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
- F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
Abstract
The invention provides a two stage rotary compressor which can improve tracing ability of refrigerating fluid imported into an advanced compressing portion, restrain pressure fluctuation in intermediate flow paths, and prevent running efficiency from reducing in low load running. The two stage rotary compressor (100) of the internal high-pressure type includes a low stage cover (19) that covers a low stage outlet port (16) and forms a low stage discharge space (20) therein. Further, the two stage compressor (100) includes a compression mechanism (3) provided with an intermediate passage (51) that connects the low stage discharge space (20) and the high stage compression chamber (35) and a bypass mechanism (a bypass port (23), a bypass valve (24), and a bypass valve guard (25) in the low stage cover (19), in which the bypass mechanism opens when a load is smaller than a predetermined load and in which the bypass mechanism connects the low stage discharge space (20) and a discharge pressure space (53).
Description
Technical field
The present invention relates to the two stage rotary compressor with two press parts.
Background technique
In the past, had following two stage rotary compressor: be provided with two press parts (rudimentary press part and advanced compression portion) at compression mechanical part, this rudimentary press part and advanced compression portion are connected in series.In such two stage rotary compressor, rudimentary press part by the refrigerant compression that sucks from heat pump cycle to the pressure (arrival pressure) of regulation.This arrival pressure decides according to the setting of the compression chamber volume in the compression chamber volume of rudimentary press part and advanced compression portion.The refrigeration agent that advanced compression portion has compressed further through rudimentary compressing section compresses.Further, when the two stage rotary compressor of internal high pressure type, the refrigeration agent through the compression of advanced compression portion is discharged from advanced compression portion to the inner space of seal container, discharges afterwards from the inner space of seal container to heat pump cycle.
In the past, in the two stage rotary compressor of internal high pressure type, for the refrigeration agent of pressure in the middle of rudimentary compressing section compresses is imported the intermediate flow passage in advanced compression portion to be formed by the mode of seal container outside.
But for intermediate flow passage with the two stage rotary compressor in the past formed by the mode of seal container outside, intermediate flow passage becomes long especially.As a result, there is following problem, that is, the tracing ability of the refrigeration agent in intermediate flow passage when importing to advanced compression portion worsens, or causes the pressure pulsation in intermediate flow passage, the effect of the pressure pulsation that can not be fully suppressed.
Therefore, for the two stage rotary compressor of internal high pressure type in the past, the technology making intermediate flow passage be formed in seal container inside is proposed.
As such two stage rotary compressor in the past, propose following technology: on the intermediate clapboard in the rudimentary press part in interval and advanced compression portion, form the discharge space forming intermediate flow passage, compression refrigerant (refrigeration agent from rudimentary press part is discharged) in the middle of discharging in this discharge space, prevent middle compression refrigerant from excessively flowing out (for example, referring to patent documentation 1) to advanced compression portion.
In addition, as such two stage rotary compressor in the past, also proposed following technology: the phase shifting making the suction port of the phase place of the suction port in advanced compression portion and rudimentary press part, thus intermediate flow passage is located at (for example, referring to patent documentation 2) in compression mechanical part.
In addition, as such two stage rotary compressor in the past, also proposed following technology: between blade groove and rudimentary, senior suction passage, configure intermediate flow passage, intermediate flow passage (for example, referring to patent documentation 3) is set in the mode in through compression mechanical part.
Patent documentation 1: Japanese Unexamined Patent Publication 2000-87892 publication
Patent documentation 2: Japanese Unexamined Patent Publication 2007-113542 publication
Patent documentation 3: Japanese Unexamined Patent Publication 2010-156226 publication
In the heat pump system (heat pump cycle) using compressor, there is following situation: in the situations such as load is little, the pressure (in other words, flowing into the pressure of the refrigeration agent of condenser) of the refrigeration agent that compressor is discharged is low also passable.But, intermediate flow passage is made to be formed in two stage rotary compressor in the past in compression mechanical part (such as, with reference to patent documentation 1 ~ patent documentation 3) situation when not considering such a low load operation, the pressure of refrigeration agent of therefore sometimes discharging from two stage rotary compressor higher than desired pressure, and becomes overcompression state.Therefore, the problem points that running efficiency when making the intermediate flow passage two stage rotary compressor be in the past formed in compression mechanical part there is low load operation reduces.
In addition, in the two stage rotary compressor described in patent documentation 1, intermediate clapboard is formed the discharge space of discharging for middle compression refrigerant, and therefore the distance between bearings (be located at compressing mechanism upper and lower end with the bearing distance each other of rotatable mode supporting driving shaft) of compressing mechanism becomes large.Therefore, there are the following problems the point of the two stage rotary compressor described in patent documentation 1: the deflection degree of live axle increases when the load of refrigeration agent acts in pressing chamber, and the reliability of bearing is reduced.
In addition, in the two stage rotary compressor described in patent documentation 2, make the phase shifting of the suction port of the phase place of the suction port in advanced compression portion and rudimentary press part, therefore there are the following problems point: dead volume increases in the pressing chamber in advanced compression portion, causes compression efficiency to reduce.
In addition, in the two stage rotary compressor described in patent documentation 3, the setting area of intermediate flow passage is narrow, therefore there are the following problems point: the flow path area of intermediate flow passage is restricted, and causes efficiency to reduce due to the pressure loss.
Summary of the invention
The present invention makes in order at least one problem solved in problem as described above, its object is to obtain a kind of two stage rotary compressor, it can improve the tracing ability of the refrigeration agent imported to advanced compression portion, suppress the pressure pulsation in intermediate flow passage, can prevent the running efficiency when low load operation from reducing.
Two stage rotary compressor of the present invention has: seal container; Compression mechanical part, it is configured in the inside of this seal container; Motor, it is configured in the inside of above-mentioned seal container, as the driving source in compression mechanism portion; Live axle, it transmits the driving force of this motor to above-mentioned compression mechanical part, and compression mechanism portion has: low-level framework; Rudimentary cylinder, it is formed with the 1st through hole becoming rudimentary pressing chamber, utilizes the opening portion of a side of inaccessible above-mentioned 1st through hole of above-mentioned low-level framework; Intermediate clapboard, the opening portion of the opposing party of its inaccessible above-mentioned 1st through hole; Senior cylinder, it is formed with the 2nd through hole becoming advanced compression room, utilizes the opening portion of a side of inaccessible above-mentioned 2nd through hole of above-mentioned intermediate clapboard; High-level framework, the opening portion of the opposing party of its inaccessible above-mentioned 2nd through hole; Rudimentary rotary-piston, it is located at the eccentric part of above-mentioned live axle, carries out eccentric rotational motion in the inside of above-mentioned rudimentary pressing chamber; Senior rotary-piston, it is located at the eccentric part of above-mentioned live axle, carries out eccentric rotational motion in the inside of above-mentioned advanced compression room; Low grade blade, the inside of above-mentioned rudimentary pressing chamber is divided into and sucks space and compression volume by it; High grade blade, the inside of above-mentioned advanced compression room is divided into and sucks space and compression volume by it, low-level framework, rudimentary cylinder, intermediate clapboard, senior cylinder and high-level framework stack gradually, form rudimentary press part and advanced compression portion, the refrigeration agent sucked from the pipe arrangement be connected with the rudimentary suction port of above-mentioned rudimentary press part is compressed by above-mentioned rudimentary pressing chamber, this refrigeration agent is imported above-mentioned advanced compression room via intermediate flow passage and second compression again, the refrigeration agent that have compressed through above-mentioned advanced compression room is discharged to the discharge pressure space of the inner space as above-mentioned seal container
The rudimentary exhaust port of discharging the refrigeration agent that be have compressed by above-mentioned rudimentary pressing chamber is formed at above-mentioned low-level framework, this two stage rotary compressor has rudimentary cover, this rudimentary covering covers this rudimentary exhaust port, rudimentary discharge space is formed in inside, above-mentioned intermediate flow passage is with through above-mentioned low-level framework, the mode of above-mentioned rudimentary cylinder and above-mentioned intermediate clapboard is formed, above-mentioned rudimentary discharge space is communicated with above-mentioned advanced compression room, above-mentioned rudimentary cover is provided with bypass mechanism, this bypass mechanism is opening when load is less than given load, above-mentioned rudimentary discharge space is made to press space to be communicated with above-mentioned discharge.
In two stage rotary compressor of the present invention, intermediate flow passage is not formed in the mode of stretching out to seal container extension, and is formed in compression mechanical part, therefore, it is possible to intermediate flow passage is formed shorter.Therefore, it is possible to improve the tracing ability of the refrigeration agent imported to advanced compression portion, suppress the pressure pulsation in intermediate flow passage.
In addition, two stage rotary compressor of the present invention has bypass mechanism, and this bypass mechanism is opening when load is less than given load, makes above-mentioned rudimentary discharge space press space to be communicated with above-mentioned discharge.Therefore, when low load operation, the refrigeration agent that can make through rudimentary compressing section compresses is not by advanced compression portion bypass discharging to heat pump cycle compressively.Therefore, the overcompression loss occurred when two stage rotary compressor of the present invention can be reduced in low load operation, can prevent the running efficiency when low load operation from reducing.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the compound compressor representing embodiments of the present invention.
Fig. 2 is the A-A sectional view of Fig. 1.
Fig. 3 is the B-B sectional view of Fig. 1.
Fig. 4 is the C-C sectional view of Fig. 1.
Fig. 5 is the D-D sectional view of Fig. 1.
Fig. 6 is the E-E sectional view of Fig. 1.
Fig. 7 compares the compound compressor of present embodiment and the figure of the running efficiency of two stage rotary compressor in the past.
Embodiment
Mode of execution
Below, the structure of an example (compound compressor 100) of two stage rotary compressor of the present invention is described.
Fig. 1 is the longitudinal section of the compound compressor representing embodiments of the present invention.In addition, Fig. 2 represents the A-A sectional view of Fig. 1, and Fig. 3 represents the B-B sectional view of Fig. 1, and Fig. 4 represents the C-C sectional view of Fig. 1, and Fig. 5 represents the D-D sectional view of Fig. 1, and Fig. 6 represents the E-E sectional view of Fig. 1.In addition, Fig. 1 is by the figure of the longitudinal section combination after deciding what is right and what is wrong in multiple position of deciding what is right and what is wrong in order to the structure of easy understand compound compressor 100.Therefore, from depression angle or look up the tram of each structure that angle is observed for the position shown in Fig. 2 ~ Fig. 6.
In the compound compressor 100 of present embodiment, in compression mechanical part 3, be provided with two press parts (rudimentary press part 10 and advanced compression portion 30).This compound compressor 100 has motor 2 (motor part), rudimentary press part 10, advanced compression portion 30, rudimentary cover 19, senior cover 39, low-level framework (frame) 14, high-level framework 34, intermediate clapboard 50 and live axle 4 etc.More specifically, senior cover 39, high-level framework 34, advanced compression portion 30, intermediate clapboard 50, rudimentary press part 10, low-level framework 14, rudimentary cover 19 and motor 2 is configured with in the inside of seal container 1 successively from lower to upper part.Further, live axle 4 is arranged along the above-below direction of seal container 1, is formed with the lubricant oil reservoir 6 for storing lubricant oil 6a in the bottom (that is, the underpart of live axle 4) of seal container 1.This lubricant oil 6a is used for lubricating compression mechanical part 3, bearing portion etc.
The rudimentary press part 10 of compression mechanical part 3 is made up of rudimentary cylinder 11, rudimentary rotary-piston 12 and low grade blade 26 (with reference to Fig. 4) etc.Rudimentary cylinder 11, in roughly writing board shape, is formed with the through hole of the substantially cylindrical shape becoming rudimentary pressing chamber 15 in substantially central portion.The upper opening of this through hole is inaccessible by low-level framework 14, and lower openings is inaccessible by intermediate clapboard 50, forms rudimentary pressing chamber 15.In addition, rudimentary pressing chamber 15 is communicated with the rudimentary exhaust port 16 being formed at low-level framework 14 with rudimentary suction port 21.Rudimentary suction port 21 is connected with suction pipe 8 via the connecting pipe 9 of the outer installment at seal container 1 and suction silencer 7.That is, rudimentary suction port 21 is connected with the low voltage side of heat pump cycle.In addition, rudimentary exhaust port 16 is provided with the leaf valve (with reference to Fig. 3) utilizing rivet 18a to be provided with the rudimentary expulsion valve 17 of tabular and rudimentary valve guard 18.By boosting the rudimentary expulsion valve 17 of this leaf valve and being opened by rudimentary exhaust port 16, rudimentary pressing chamber 15 is communicated with rudimentary discharge space 20 described later.
Rudimentary rotary-piston 12 and low grade blade 26 is provided with in rudimentary pressing chamber 15.Rudimentary rotary-piston 12, in substantially cylindrical shape, is located at the eccentric part of live axle 4.Low grade blade 26 is located at rudimentary blade groove 27 in the mode slid freely, and this rudimentary blade groove 27 is formed at rudimentary cylinder 11.In addition, low grade blade 26 is imposed the power to live axle 4 direction by force application components such as springs, and its tip portion can follow the peripheral part of rudimentary rotary-piston 12 freely.Thus, rudimentary pressing chamber 15 is divided into the suction space be communicated with rudimentary suction port 21 and the compression volume be communicated with rudimentary exhaust port 16.From Fig. 3 and Fig. 4, from depression angle, the rudimentary suction port 21 of rudimentary pressing chamber 15 is communicated with rudimentary pressing chamber 15 near the left side of low grade blade 26.In addition, from depression angle, rudimentary exhaust port 16 is communicated with rudimentary pressing chamber 15 near the right side of low grade blade 26.
Advanced compression portion 30 is made up of senior cylinder 31, senior rotary-piston 32 and high grade blade 42 (with reference to Fig. 5) etc.Senior cylinder 31, in roughly writing board shape, is formed with the through hole of the substantially cylindrical shape becoming advanced compression room 35 in substantially central portion.The upper opening of this through hole is inaccessible by intermediate clapboard 50, and lower openings is inaccessible by high-level framework 34, forms advanced compression room 35.The volume of advanced compression room 35 is formed less than rudimentary pressing chamber 15.In addition, advanced compression room 35 is communicated with the senior exhaust port 36 being formed at high-level framework 34 with the senior suction port 41 being formed at senior cylinder 31.The senior suction port 41 in advanced compression portion 30 can be communicated with the rudimentary exhaust port 16 of rudimentary press part 10 via rudimentary discharge space 20 described later and intermediate flow passage 51.In addition, the leaf valve (with reference to Fig. 6) utilizing rivet 38a to be provided with the senior expulsion valve 37 of tabular and senior valve guard 38 is provided with at senior exhaust port 36.By boosting the senior expulsion valve 37 of this leaf valve and being opened by senior exhaust port 36, advanced compression room 35 is communicated with senior discharge space 40 described later.
Senior rotary-piston 32 and high grade blade 42 is provided with in advanced compression room 35.Senior rotary-piston 32, in substantially cylindrical shape, is located at the eccentric part of live axle 4.In the present embodiment, from depression angle, senior rotary-piston 32 roughly contrary with the phase place of rudimentary rotary-piston 12 (have rotated the position of roughly 180 ° centered by the running shaft of live axle 4).High grade blade 42 is located at senior blade groove 43 in the mode slid freely, and this senior blade groove 43 is formed at senior cylinder 31.Further, high grade blade 42 is imposed the power to live axle 4 direction by force application components such as springs, and its tip portion can follow the peripheral part of senior rotary-piston 32 freely.Thus, advanced compression room 35 is divided into the suction space be communicated with senior suction port 41 and the compression volume be communicated with senior exhaust port 36.From Fig. 5 and Fig. 6, from depression angle, senior suction port 41 is communicated with advanced compression room 35 near the left side of high grade blade 42.In addition, from depression angle, senior exhaust port 36 is communicated with advanced compression room 35 near the right side of high grade blade 42.
In addition, from Fig. 3 ~ Fig. 6, from depression angle, the rudimentary suction port 21 of rudimentary pressing chamber 15 is roughly the same phase place with the senior suction port 41 of advanced compression room 35.From depression angle, rudimentary exhaust port 16 is roughly the same phase place with senior exhaust port 36.Therefore, the compound compressor 100 of present embodiment is different from the two stage rotary compressor shown in patent documentation 2, and the dead volume of advanced compression room 35 can not increase, and compression efficiency can not reduce.
Low-level framework 14 has upper axis bearing portion, supports the roughly intermediate portion of live axle 4 in rotatable mode.On low-level framework 14, be formed with the rudimentary exhaust port 16 of rudimentary press part 10 as described above.Rudimentary cover 19 is the cup shape container of lower openings.This rudimentary cover 19 is arranged in the mode covering rudimentary exhaust port 16 from top, and its inside is formed with rudimentary discharge space 20.
Further, rudimentary discharge space 20 is also communicated with intermediate flow passage 51.This intermediate flow passage 51 is through low-level framework 14, rudimentary cylinder 11 and intermediate clapboard 50 in the vertical direction, and rudimentary discharge space 20 is communicated with senior suction port 41.That is, the refrigeration agent flowing into rudimentary discharge space 20 is drawn into advanced compression portion 30 via intermediate clapboard 50.
In addition, from depression angle, this intermediate flow passage 51 is when through rudimentary cylinder 11, namely through away from the position of low grade blade 26 (that is, rudimentary blade groove 27) than rudimentary suction port 21 on the left of low grade blade 26.In other words, with the central shaft of live axle 4 for benchmark and with from low grade blade 26 to the sense of rotation of the near side of the distance of rudimentary suction port 21 for (direction of arrow shown in Fig. 4) during postive direction, intermediate flow passage 51 is formed at the position than rudimentary suction port 21 downstream in the positive direction.
High-level framework 34 has lower bearing portion, with the underpart of rotatable mode supporting driving shaft 4.In high-level framework 34, be formed with the senior exhaust port 36 in advanced compression portion 30 as described above.Senior cover 39 is the cup shape container of upper opening.This senior cover 39 is arranged in the mode covering senior exhaust port 36 from below, is formed with senior discharge space 40 in inside.
Further, in senior discharge space 40, be formed with the discharge duct 52 be communicated with the inner space of seal container 1.This discharge duct 52 is through high-level framework 34, senior cylinder 31, intermediate clapboard 50, rudimentary cylinder 11 and low-level framework 14 in the vertical direction, and senior discharge space 40 is communicated with the inner space of seal container 1.That is, the compound compressor 100 of present embodiment is the compressor becoming the internal high pressure type of discharging pressure space 53 (when steady running, becoming the space of the pressure of the high-pressure refrigerant of discharging from advanced compression portion 30) in seal container 1.Be provided with discharge tube 5 on the such as top of seal container 1, the high-pressure refrigerant being discharged to seal container 1 is externally discharged from this discharge tube 5.In addition, from depression angle, this discharge duct 52 is through relative to the point-symmetric position that intermediate flow passage 51 is being benchmark with the central shaft of live axle 4.
Motor 2 is the driving source in rudimentary press part 10 and advanced compression portion 30.This motor 2 has stator 2a and rotor 2b.Stator 2a is substantially cylindrical shape, is fixed on the inner peripheral portion of seal container 1.Rotor 2b is substantially cylindrical shape, is configured in the inner peripheral portion of stator 2a in the mode being separated with specified gap.In addition, the upper end portion intercalation of live axle 4 is in the inner peripheral portion of rotor 2b.
In addition, in the compound compressor 100 of present embodiment, rudimentary cover 19 is provided with sparger (injector) 60.One end of this sparger 60 is to rudimentary discharge space 20 opening, and the other end is connected with injection pipe (injection pipe) 61.Wherein, sparger 60 is for the refrigeration agent in the heat pump cycle beyond the refrigerant injection compound compressor 100 of discharging from rudimentary press part 10.Therefore, the link position of sparger 60 is not limited to rudimentary cover 19, as long as be inhaled into the stream (rudimentary discharge space) before advanced compression portion 30 from the refrigeration agent of rudimentary press part 10 discharge, can be connected to arbitrary position.
In addition, in the compound compressor 100 of present embodiment, rudimentary cover 19 is formed with by-pass port 23, this by-pass port 23 makes rudimentary discharge space 20 press space 53 to be communicated with the discharge of the inner space as seal container 1.By-pass port 23 is provided with and utilizes rivet 29 that the bypass valve 24 of tabular and the leaf valve (with reference to Fig. 2) of bypass valve guard 25 are installed.They are called bypass mechanism.
In addition, in the present embodiment, the position relationship of by-pass port 23 and intermediate flow passage 51 as shown in Figure 2.Namely, with the central shaft of live axle 4 for benchmark and with from rudimentary exhaust port 16 to the sense of rotation of the near side of the distance of by-pass port 23 for (direction of arrow shown in Fig. 2) during postive direction, intermediate flow passage 51 is formed in the position than by-pass port 23 downstream in the positive direction.
Next, the action of compound compressor 100 is described.
During supply electric power, motor 2 carries out action.Motor 2 and compression mechanical part 3 utilize live axle 4 to be connected, and the power produced by motor 2 is delivered to compression mechanical part 3 via live axle 4.Specifically, when receiving the supply of electric power, the rotor 2b of motor 2 rotates.When rotor 2b rotates, the live axle 4 being intercalated in rotor 2b also rotates.Further, when live axle 4 rotates, intercalation has the rudimentary rotary-piston 12 of live axle 4 and senior rotary-piston 32 to rotate at the internal eccentric of rudimentary pressing chamber 15 and advanced compression room 35 respectively.Due to rudimentary rotary-piston 12 and senior rotary-piston 32 eccentric rotary, can in rudimentary press part 10 and advanced compression portion 30 compressed refrigerant.
Carrying out in the compound compressor 100 of action like this, flowing has refrigeration agent as described below.
First, the refrigeration agent of low pressure flow into suction silencer 7 from outside via suction pipe 8.The refrigeration agent flowing into the low pressure of suction silencer 7 is drawn into rudimentary pressing chamber 15 via connecting pipe 9.The refrigeration agent being drawn into the low pressure of rudimentary pressing chamber 15 is compressed into middle pressure in rudimentary pressing chamber 15.When refrigeration agent is compressed into middle pressure, under the effect of the pressure difference of the refrigeration agent in the refrigeration agent in rudimentary pressing chamber 15 and rudimentary discharge space 20, rudimentary expulsion valve 17 is opened, and the refrigeration agent in rudimentary pressing chamber 15 is discharged from rudimentary exhaust port 16 to rudimentary discharge space 20.At this, middle pressure is the pressure determined with the ratio of the volume of the suction chamber of advanced compression room 35 according to the volume of the suction chamber of rudimentary pressing chamber 15.
The refrigeration agent being discharged to the middle pressure in rudimentary discharge space 20 is drawn into advanced compression room 35 via intermediate flow passage 51.The refrigeration agent being drawn into the middle pressure of advanced compression room 35 is compressed in advanced compression room 35 discharges pressure.When refrigeration agent is compressed into discharge pressure, under the effect of the pressure difference of the refrigeration agent in the refrigeration agent in advanced compression room 35 and senior discharge space 40, senior expulsion valve 37 is opened, and the refrigeration agent in advanced compression room 35 is discharged from senior exhaust port 36 to senior discharge space 40.The refrigeration agent being discharged to the discharge pressure in senior discharge space 40 is discharged via the discharge pressure space 53 of discharge duct 52 to the top of rudimentary press part 10.Then, the refrigeration agent being discharged to the discharge pressure of discharging pressure space 53 is externally discharged from discharge tube 5.
In addition, in the heat pump system heat pump cycle of compound compressor 100 (use) with compound compressor 100, when carrying out injections and operating, from the injection pipe 61 shown in Fig. 1 via sparger 60 to rudimentary discharge space 20 injecting jet refrigeration agent.Ejector refrigeration agent mixes in rudimentary discharge space 20 with the middle refrigeration agent of pressing of discharging from rudimentary pressing chamber 15, and is compressed in advanced compression portion 30.
It is (following when the load of heat pump system is little, during also referred to as low load operation) etc., sometimes the compression by means of only rudimentary press part 10 just becomes the overcompression state reaching and discharge pressure (in other words, flowing into the pressure of the refrigeration agent of condenser).That is, be the pressure higher than required discharge pressure when the centre of above-mentioned refrigeration agent is pressed with.Under these circumstances, in the compound compressor 100 of present embodiment, under the effect of the pressure difference of the refrigeration agent in space 53 is pressed in refrigeration agent in rudimentary discharge space 20 and discharge, bypass valve 24 is opened, and the refrigeration agent in rudimentary discharge space 20 is discharged from by-pass port 23 to discharge pressure space 53.In other words, in the compound compressor 100 of present embodiment, when the pressure ratio in rudimentary discharge space 20 is discharged more than the pressure large specified value in pressure space 53, bypass valve 24 is out of shape and by-pass port 23 is opened.That is, the refrigeration agent making to be discharged to rudimentary discharge space 20 from rudimentary press part 10 is not by advanced compression portion 30 bypass discharging to discharge pressure space 53 compressively.
Under overcompression state, the compression by means of only rudimentary press part 10 just reaches discharges pressure, and therefore the compression futile effort in advanced compression portion 30 is useless, if utilize advanced compression portion 30 to carry out compressing, and degradation in efficiency.But, in compound compressor 100, when becoming overcompression state, the ground, refrigerant bypass advanced compression portion 30 that have compressed through rudimentary press part 10 is discharged.Therefore, it is possible to suppress the loss (overcompression loss) when there is overcompression state, the running efficiency when low load operation can be improved.
Particularly, in the compound compressor 100 of present embodiment, rudimentary cover 19 is formed with by-pass port 23.Therefore, do not discharge to the discharge pressure space 53 in seal container 1 via intermediate flow passage 51 ground from by-pass port 23 to discharging the refrigeration agent of discharging in pressure space 53.That is, the compression loss caused via intermediate flow passage 51 can not be there is from by-pass port 23 to the refrigeration agent of discharging the discharge of pressure space 53, discharge to discharge pressure space 53 from by-pass port 23.Therefore, when low load operation, can effectively suppress overcompression to be lost.
In addition, as described above, be formed with lubricant oil reservoir 6 in the downside of seal container 1, and be incorporated with lubricant oil 6a.In order to lubricant oil 6a being supplied to the mechanical part of compression mechanical part 3, at least load the amount being dipped into the press part (being rudimentary press part 10 in FIG) being configured in upside.In general two stage rotary compressor (with reference to patent documentation 1 ~ patent documentation 3), when longitudinally placing two stage rotary compressor, rudimentary press part is located at the downside in advanced compression portion.Therefore, two stage rotary compressor as described in patent documentation 2 and patent documentation 3, to be discharged in the two stage rotary compressor in (rudimentary discharge space) in rudimentary cover by refrigeration agent through rudimentary compressing section compresses, rudimentary discharge space is located at the downside of rudimentary press part.That is, the rudimentary downside being located at rudimentary press part.Therefore, rudimentary cover becomes the state be immersed in lubricant oil.In this case, if form the by-pass port 23 of present embodiment on rudimentary cover, then lubricant oil enters rudimentary discharge space from by-pass port 23.Further, lubricant oil being swept away from during by-pass port 23 discharging refrigerant, the outflow of lubricant oil from two stage rotary compressor is increased.Therefore, in general two stage rotary compressor, the by-pass port 23 of present embodiment can not be formed on rudimentary cover.Therefore, in the two stage rotary compressor described in patent documentation 2 and patent documentation 3, when longitudinally placing two stage rotary compressor, by-pass port 23 can only be set in the narrow stream making rudimentary discharge space be connected with advanced compression portion.
But when the compound compressor 100 of present embodiment is longitudinally placed, with usually contrary, rudimentary press part 10 is located at the upside in advanced compression portion 30.Therefore, it is possible to rudimentary discharge space 20 to be located at the upside of rudimentary press part 10, rudimentary cover 19 is made to be positioned at the height that can not impregnated in lubricant oil 6a.As a result, by-pass port 23 can be set on rudimentary cover 19.
In addition, in the compound compressor 100 of present embodiment, be not in intermediate flow passage 51 but arrange by-pass port 23 on rudimentary cover 19, therefore bypass valve 24 can adopt simply constructed leaf valve.Therefore, bypass valve 24 and bypass valve guard 25 can adopt the part identical with rudimentary expulsion valve 17 and rudimentary valve guard 18, senior expulsion valve 37 and senior valve guard 38.By making, part is common can be suppressed low by cost.In addition, the simple structure of bypass valve 24, therefore can also suppress low by assembling the cost spent.
Next, the feature of the intermediate flow passage 51 of the compound compressor 100 of present embodiment is described.
As described above, intermediate flow passage 51 is through low-level framework 14, rudimentary cylinder 11 and intermediate clapboard 50 in the vertical direction, and rudimentary discharge space 20 is communicated with senior suction port 41.That is, the refrigeration agent that have compressed through rudimentary press part 10 flows into intermediate flow passage 51 after being discharged to rudimentary discharge space 20.Therefore, different from the two stage rotary compressor described in patent documentation 1, there is no need the discharge space forming rudimentary press part 10 on intermediate clapboard 50.Therefore, the compound compressor 100 of present embodiment is different from the two stage rotary compressor described in patent documentation 1, the distance between low-level framework 14 and high-level framework 34 also played a role as the bearing portion of live axle 4 can be reduced, the reliability of compound compressor 100 (low-level framework 14 more specifically, also played a role as the bearing portion of live axle 4 and high-level framework 34) can be improved.
In addition, than rudimentary suction port 21 away from low grade blade 26 (in other words intermediate flow passage 51 is formed in, rudimentary blade groove 27) position, being namely formed at is not position between rudimentary suction port 21 with low grade blade 26 (in other words, rudimentary blade groove 27).Therefore, the intermediate flow passage 51 of present embodiment is different from the intermediate flow passage described in patent documentation 3, and can guarantee that flow path area is comparatively large, the main cause that the efficiency that the pressure loss can be caused reduces is got rid of.In addition, intermediate flow passage 51 does not interfere rudimentary suction port 21 and low grade blade 26 (in other words, rudimentary blade groove 27), and therefore the degrees of freedom that arranges of stream increases.In addition, in Fig. 4 etc., illustrate the intermediate flow passage 51 that opening portion is circular, as long as but the area of opening portion is formed larger than the area of rudimentary exhaust port 16, can have any shape.
In intermediate flow passage due to flow into volume of the cooling medium, density density and there is pressure pulsation.Particularly in the two stage rotary compressor of VFC, easily there is pressure pulsation due to the increase and decrease of rotating speed.Be configured in the two stage rotary compressor in the past of seal container outside in intermediate flow passage, the tracing ability importing to the refrigeration agent in advanced compression portion is poor, therefore, in order to make the pressure pulsation in this intermediate flow passage disappear by resonance, have to set the intermediate flow passage of several stream pipe range.But, the compound compressor 100 of present embodiment makes flow path length shorten by intermediate flow passage 51 being located in compression mechanical part 3, therefore, it is possible to improve the tracing ability of the refrigeration agent imported to advanced compression portion 30 from rudimentary press part 10, suppress pressure pulsation, therefore, it is possible to improve running efficiency.
As described above, with the central shaft of live axle 4 for benchmark and with from rudimentary exhaust port 16 to the sense of rotation of the near side of the distance of by-pass port 23 for (direction of arrow shown in Fig. 2) during postive direction, intermediate flow passage 51 is formed in the position than by-pass port 23 downstream in the positive direction.This postive direction is the main flow direction of the refrigeration agent flowed from rudimentary exhaust port 16 to by-pass port 23.By making by-pass port 23 and intermediate flow passage 51 with the configuration of such position relationship, discharged in seal container 1 from by-pass port 23 before arrival intermediate flow passage 51 from the refrigeration agent of the overcompression state of rudimentary press part 10 discharge by bypass mechanism (by-pass port 23, bypass valve 24 and bypass valve guard 25).Therefore, more reliably make not discharge to discharge pressure space 53 with not flowing through in intermediate flow passage 51 to discharging the refrigeration agent of discharging in pressure space 53, the effect of above-mentioned bypass mechanism becomes large.On the other hand, even if be configured in intermediate flow passage in the two stage rotary compressor in the past of seal container 1 outside, bypass mechanism of the present invention (being located at the bypass mechanism of low-pressure cover) is set, because the flow path length of intermediate flow passage is elongated, therefore the refrigeration agent of overcompression state cannot be drained from by-pass port 23, a part for the refrigeration agent of overcompression state flows into advanced compression portion and futile useless compression occurs, therefore degradation in efficiency.
Finally, the improvement effect of the running efficiency of the compound compressor 100 of present embodiment is described.
Fig. 7 compares the compound compressor of present embodiment and the figure of the running efficiency of two stage rotary compressor in the past.Wherein, the two stage rotary compressor in the past shown in Fig. 7 is the two stage rotary compressor that intermediate flow passage is configured in the internal high pressure type of seal container outside, does not have bypass mechanism as the present embodiment.In addition, Fig. 7 illustrates the running efficiency of the compound compressor 100 of present embodiment for benchmark (100%) with the running efficiency of two stage rotary compressor in the past.
Compare the running efficiency of when steady running (rated condition shown in Fig. 7), the running efficiency of the compound compressor 100 of present embodiment is about 102%, and compared with two stage rotary compressor in the past, running efficiency improves about 2%.From this result, by being formed in compression mechanical part 3 by intermediate flow passage 51, the tracing ability of the refrigeration agent imported to advanced compression portion 30 can be improved, suppressing the pressure pulsation in intermediate flow passage, can running efficiency be improved.
Compare the running efficiency of (low load condition shown in Fig. 7) during low load operation, the running efficiency of the compound compressor 100 of present embodiment is about 101.5%, and compared with two stage rotary compressor in the past, running efficiency improves about 1.5%.From this result, in the compound compressor 100 of present embodiment, by arranging bypass mechanism (by-pass port 23, bypass valve 24 and bypass valve guard 25) on rudimentary cover 19, the refrigerant bypass advanced compression portion 30 that have compressed through rudimentary press part 10 can be made when becoming overcompression state and discharge, can running efficiency be improved.
In addition, intermediate flow passage 51 is formed in the compound compressor 100 in compression mechanical part 3, because the component becoming intermediate flow passage is not given prominence to from seal container 1, therefore can also obtains the effects such as miniaturization, easily packaging and carrying, easily dismounting.
Description of reference numerals
1 seal container, 2 motor, 2a stator, 2b rotor, 3 compression mechanical parts, 4 live axles, 5 discharge tubes, 6 lubricant oil reservoir, 6a lubricant oil, 7 suction silencers, 8 suction pipes, 9 connecting pipes, 10 rudimentary press parts, 11 rudimentary cylinders, 12 rudimentary rotary-pistons, 14 low-level framework, 15 rudimentary pressing chambers, 16 rudimentary exhaust ports, 17 rudimentary expulsion valves, 18 rudimentary valve guards, 18a rivet, 19 rudimentary covers, 20 rudimentary discharge spaces, 21 rudimentary suction ports, 23 by-pass ports, 24 bypass valve, 25 bypass valve guards, 26 low grade blades, 27 rudimentary blade grooves, 29 rivets, 30 advanced compression portions, 31 senior cylinders, 32 senior rotary-pistons, 34 high-level framework, 35 advanced compression rooms, 36 senior exhaust ports, 37 senior expulsion valves, 38 senior valve guards, 38a rivet, 39 senior covers, 40 senior discharge spaces, 41 senior suction ports, 42 high grade blades, 43 senior blade grooves, 50 intermediate clapboards, 51 intermediate flow passage, 52 discharge duct, 53 discharge pressure space, 60 spargers, 61 injection pipes, 100 compound compressors.
Claims (6)
1. a two stage rotary compressor, has:
Seal container;
Compression mechanical part, this compression mechanical part is configured in the inside of above-mentioned seal container;
Motor, this motor is configured in the inside of above-mentioned seal container, as the driving source in compression mechanism portion;
Live axle, this driving axial compression mechanism portion transmits the driving force of above-mentioned motor,
Compression mechanism portion has:
Low-level framework;
Rudimentary cylinder, this rudimentary cylinder is formed with the 1st through hole becoming rudimentary pressing chamber, by the opening portion of a side of inaccessible above-mentioned 1st through hole of above-mentioned low-level framework;
Intermediate clapboard, the opening portion of the opposing party of inaccessible above-mentioned 1st through hole of this intermediate clapboard;
Senior cylinder, this senior cylinder is formed with the 2nd through hole becoming advanced compression room, by the opening portion of a side of inaccessible above-mentioned 2nd through hole of above-mentioned intermediate clapboard;
High-level framework, the opening portion of the opposing party of inaccessible above-mentioned 2nd through hole of this high-level framework;
Rudimentary rotary-piston, the eccentric part of above-mentioned live axle is located at by this rudimentary rotary-piston, carries out eccentric rotational motion in the inside of above-mentioned rudimentary pressing chamber;
Senior rotary-piston, the eccentric part of above-mentioned live axle is located at by this senior rotary-piston, carries out eccentric rotational motion in the inside of above-mentioned advanced compression room;
Low grade blade, the inside of above-mentioned rudimentary pressing chamber is divided into and sucks space and compression volume by this low grade blade;
High grade blade, the inside of above-mentioned advanced compression room is divided into and sucks space and compression volume by this high grade blade,
Low-level framework, rudimentary cylinder, intermediate clapboard, senior cylinder and high-level framework stack gradually, and form rudimentary press part and advanced compression portion,
The refrigeration agent that the pipe arrangement be connected from the rudimentary suction port of the above-mentioned rudimentary pressing chamber with above-mentioned rudimentary press part sucks is compressed at above-mentioned rudimentary pressing chamber, this refrigeration agent imports to above-mentioned advanced compression room via intermediate flow passage and is re-compressed, the refrigeration agent that have compressed in above-mentioned advanced compression room is discharged to the discharge pressure space as the inner space of above-mentioned seal container
It is characterized in that,
The rudimentary exhaust port of discharging the refrigeration agent that have compressed at above-mentioned rudimentary pressing chamber is formed at above-mentioned low-level framework,
This two stage rotary compressor has rudimentary cover, and this is rudimentary covers to cover and state rudimentary exhaust port, is formed with rudimentary discharge space in inside,
Above-mentioned intermediate flow passage is formed in the mode of through above-mentioned low-level framework, above-mentioned rudimentary cylinder and above-mentioned intermediate clapboard, and above-mentioned rudimentary discharge space is communicated with above-mentioned advanced compression room,
Above-mentioned rudimentary cover has bypass mechanism, and this bypass mechanism is opening when load is less than given load, makes above-mentioned rudimentary discharge space press space to be communicated with above-mentioned discharge,
With the central shaft of above-mentioned live axle for benchmark, with from above-mentioned rudimentary exhaust port to the sense of rotation of the near side of the distance of above-mentioned bypass mechanism for postive direction time,
The opening portion towards above-mentioned rudimentary discharge space of above-mentioned intermediate flow passage is formed at the position than above-mentioned bypass mechanism downstream in above-mentioned postive direction.
2. two stage rotary compressor according to claim 1, is characterized in that,
Opening when above-mentioned bypass mechanism is more than the pressure height specified value in the pressure ratio in above-mentioned rudimentary discharge space above-mentioned discharge pressure space.
3. two stage rotary compressor according to claim 2, is characterized in that,
In compression mechanism portion, above-mentioned rudimentary press part is configured in the top in above-mentioned advanced compression portion,
Above-mentioned bypass mechanism has:
By-pass port, this by-pass port is formed at above-mentioned rudimentary cover;
Valve, this valve is arranged in the mode of the above-mentioned by-pass port of obturation, is out of shape when being subject to the pressure of more than specified value, is opened by above-mentioned by-pass port.
4. the two stage rotary compressor according to any one in claim 1 ~ claim 3, is characterized in that,
Above-mentioned rudimentary discharge space is connected with the pipe arrangement of ejector refrigeration agent.
5. the two stage rotary compressor according to any one in claim 1 ~ claim 3, is characterized in that,
Refrigeration agent is roughly the same phase place with refrigeration agent to the position that above-mentioned advanced compression room sucks to the position that above-mentioned rudimentary pressing chamber sucks.
6. the two stage rotary compressor according to any one in claim 1 ~ claim 3, is characterized in that,
With the central shaft of above-mentioned live axle for benchmark, with from above-mentioned low grade blade to the sense of rotation of the near side of the distance of above-mentioned rudimentary suction port for postive direction time,
Above-mentioned intermediate flow passage is formed at the position than above-mentioned rudimentary suction port downstream in above-mentioned postive direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011165094A JP5586537B2 (en) | 2011-07-28 | 2011-07-28 | Rotary two-stage compressor |
| JP2011-165094 | 2011-07-28 |
Publications (2)
| Publication Number | Publication Date |
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| CN102900669A CN102900669A (en) | 2013-01-30 |
| CN102900669B true CN102900669B (en) | 2015-04-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210176442.2A Active CN102900669B (en) | 2011-07-28 | 2012-05-31 | Two stage rotary compressor |
Country Status (5)
| Country | Link |
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| EP (1) | EP2551526B1 (en) |
| JP (1) | JP5586537B2 (en) |
| KR (1) | KR101376872B1 (en) |
| CN (1) | CN102900669B (en) |
| RU (1) | RU2501978C1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104251206A (en) * | 2013-06-28 | 2014-12-31 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary double-stage compressor |
| CZ2016565A3 (en) * | 2014-03-14 | 2017-01-25 | Mitsubishi Electric Corporation | A cooling cyclical device |
| CN103883533B (en) * | 2014-03-14 | 2017-06-16 | 安徽美芝精密制造有限公司 | Double-stage compressor |
| CN105332920B (en) * | 2014-07-07 | 2018-02-09 | 珠海格力节能环保制冷技术研究中心有限公司 | Baffle assembly and three cylinder double-stage compressors for three cylinder double-stage compressors |
| CN105020135A (en) * | 2015-08-18 | 2015-11-04 | 武汉凌达压缩机有限公司 | Refrigerating system and compressor thereof |
| 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 |
| RU2637281C1 (en) * | 2016-11-10 | 2017-12-01 | Петр Андреевич Семчук | Two-rotor pump |
| CN106382227A (en) * | 2016-11-18 | 2017-02-08 | 广东美芝制冷设备有限公司 | Multi-stage compression type rotary compressor and refrigerating circulating device provided with same |
| JP2018188986A (en) * | 2017-04-28 | 2018-11-29 | パナソニックＩｐマネジメント株式会社 | Internal intermediate pressure-type two-stage compression compressor |
| JP7364043B2 (en) * | 2020-03-26 | 2023-10-18 | 三菱電機株式会社 | Method for manufacturing a discharge valve mechanism for a compressor and a compressor equipped with the discharge valve mechanism |
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- 2012-05-17 KR KR1020120052277A patent/KR101376872B1/en active IP Right Grant
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Also Published As
| Publication number | Publication date |
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| EP2551526A2 (en) | 2013-01-30 |
| RU2012122456A (en) | 2013-12-10 |
| EP2551526B1 (en) | 2019-05-01 |
| KR20130014337A (en) | 2013-02-07 |
| CN102900669A (en) | 2013-01-30 |
| JP2013029059A (en) | 2013-02-07 |
| EP2551526A3 (en) | 2017-08-09 |
| JP5586537B2 (en) | 2014-09-10 |
| KR101376872B1 (en) | 2014-03-20 |
| RU2501978C1 (en) | 2013-12-20 |
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