CN100343518C - Multi-cylinder compressor - Google Patents
Multi-cylinder compressor Download PDFInfo
- Publication number
- CN100343518C CN100343518C CNB031034519A CN03103451A CN100343518C CN 100343518 C CN100343518 C CN 100343518C CN B031034519 A CNB031034519 A CN B031034519A CN 03103451 A CN03103451 A CN 03103451A CN 100343518 C CN100343518 C CN 100343518C
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- China
- Prior art keywords
- cylinder
- mentioned
- suction
- intake line
- pipe
- Prior art date
Links
- 238000005192 partition Methods 0.000 abstract 1
- 230000014509 gene expression Effects 0.000 description 15
- 239000003507 refrigerant Substances 0.000 description 11
- 230000002411 adverse Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 230000000576 supplementary Effects 0.000 description 6
- 241000237970 Conus <genus> Species 0.000 description 4
- 238000003825 pressing Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000001939 inductive effect Effects 0.000 description 3
- 230000003111 delayed Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 210000000088 Lip Anatomy 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000875 corresponding Effects 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—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
-
- 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
Abstract
The invention provides a multi-cylinder compressor. A compressing mechanism part is provided with a plurality of cylinders 6a, 6b, each cylinder 6a, 6b is provided with a plurality of operating chambers 51, 52 defined by a partition plate 50 and a pair of end plates 5, 8. A crank shaft 3 is provided with a plurality of crank pins 13, 14 of different phases. A suction chamber 51 is provided with suction ports 20a, 20b communicated to suction pipes 19a, 19b through a suction channel. The suction channel has a channel part 30 communicating a channel part of each cylinder 6a, and channel parts 23a, 23b of the cylinder enlarged to both end faces of the cylinder. The Multi-cylinder compressor improves the efficiency by reducing suction loss by preventing the interference of pressure pulsation generated by one of the cylinders disturbing suction to an operating chamber of the other cylinder.
Description
Technical field
The present invention relates to multi-cylinder compressor, particularly relate to the multi-cylinder compressor that in the freeze cycle of refrigerator or air conditioner etc., uses.
Background technique
As multi-cylinder compressor in the past, can exemplify the spy and drive the compressor shown in the flat 8-270580 communique, just be housed in the seal container by bent axle connection motor part and compressor arrangement portion, the above-mentioned compressor structural portion has 2 cylinders, in above-mentioned each cylinder, form simultaneously and separate 2 working rooms that form by dividing plate and a pair of end plate, above-mentioned bent axle has eccentric a plurality of crank pins on different phase places, simultaneously in above-mentioned each crank pin, embed piston, make its eccentric rotation in stating each working room, above-mentioned working room has the suction port that is communicated with by intake line and the suction pipe that is connected with above-mentioned cylinder, and above-mentioned intake line has the pipe section between the pipe section that is communicated with above-mentioned each cylinder.
In above-mentioned technology in the past, also represented to connect suction pipe, had the concrete example of the pipe section that is communicated with the suction port of another cylinder from the inboard of this suction pipe simultaneously at specific cylinder.
In addition, in above-mentioned technology in the past, also represented on two cylinders, to connect suction pipe respectively, had the concrete example of the pipe section that is communicated with two cylinders simultaneously in the inboard of the part that connects above-mentioned suction pipe.
In above-mentioned conventional art, after the compressor starts running, thereby the volume of each working room changes intake is also changed, and occurs pressure surge in intake line.Thus, the suction effect of another working room of the easy overslaugh of pressure surge that produces by a side working room.But do not take into full account more above-mentioned in the conventional art.
Be not provided at the pipeline portions that is communicated with between each cylinder pipe section in the prior art, to the flow resistance of the suction port direction of specific cylinder and the relation between the flow resistance of the suction port direction of another cylinder.When appearing in the induction stroke of specific cylinder operation chamber greater than to the flow resistance of the suction port direction of specific cylinder the time, be inhaled into gas in another cylinder operation chamber in advance to the problem of specific cylinder operation chamber adverse current to the flow resistance of the suction port direction of another cylinder.
Summary of the invention
1 of the object of the invention provides a kind of can preventing and hinders the phenomenon that sucks to the working room of opposite side cylinder by the pressure surge of side cylinder generation, thus the multi-cylinder compressor that reduces suction loss, raises the efficiency.
2 of the object of the invention provides a kind of can preventing and produces the adverse current phenomenon that the opposite side working room sucks gas by the induction stroke of a side working room, thus the multi-cylinder compressor that reduces suction loss, raises the efficiency.
To know the purpose except that above-mentioned of the present invention more by following explanation.
In order to achieve the above object 1, multi-cylinder compressor of the present invention is to be housed in the seal container by bent axle connection motor part and compressor arrangement portion, the above-mentioned compressor structural portion has multi cylinder, in above-mentioned each cylinder, form simultaneously and separate a plurality of working rooms that form by dividing plate and end plate, on the different phase place of above-mentioned bent axle, be provided with eccentric a plurality of crank pins, simultaneously in each crank pin, embed piston, make its eccentric rotation in above-mentioned each working room, be provided with the suction port that is communicated with by intake line and the suction pipe that is connected with above-mentioned cylinder in the above-mentioned working room, it is characterized in that above-mentioned intake line has the pipe section between the pipe section that is communicated with above-mentioned each cylinder and extends to the cylinder pipe section of cylinder both ends of the surface.
In order to achieve the above object 2, multi-cylinder compressor of the present invention is to be housed in the seal container by bent axle connection motor part and compressor arrangement portion, the above-mentioned compressor structural portion has multi cylinder, in above-mentioned each cylinder, form simultaneously and separate a plurality of working rooms that form by dividing plate and end plate, eccentric a plurality of crank pins are set on the out of phase of above-mentioned bent axle, simultaneously in each crank pin, embed piston, make its eccentric rotation in above-mentioned each working room, above-mentioned working room has the suction port that is communicated with by intake line and the suction pipe that is connected with above-mentioned cylinder, it is characterized in that, be provided with the specific cylinder that connects above-mentioned suction pipe and another cylinder that is not connected in the above-mentioned cylinder with above-mentioned suction pipe, above-mentioned intake line has being communicated with the pipe section of getting up between the above-mentioned suction port, above-mentioned connecting pipe partly has the fluid restriction, makes to the resistance that flows of the suction port direction of above-mentioned another cylinder less than the resistance that flows to the suction port direction of above-mentioned specific cylinder.
To know other mechanism of the present invention more by the following description.
Description of drawings
Fig. 1 is the longitudinal section of the multi-cylinder rotary air compressor of the embodiment of the invention 1.
Fig. 2 is the major component expanded view of Fig. 1.
Fig. 3 is that the A-A of Fig. 1 is to sectional view.
Fig. 4 is the major component cross-sectional view of the multi-cylinder rotary air compressor of the embodiment of the invention 2.
Fig. 5 is that the B-B of Fig. 4 is to sectional view.
Embodiment
Embodiments of the invention are described with reference to the accompanying drawings.In embodiment 2, omitted a part of structure identical, omitted the explanation that repeats simultaneously with embodiment 1.Each prosign of implementing in the illustration is represented same object or corresponding object.
Multi-cylinder compressor with reference to accompanying drawing 1 to the 3 explanation embodiment of the invention 1.Fig. 1 is the longitdinal cross-section diagram of the multi-cylinder compressor of the embodiment of the invention 1, and Fig. 2 is the expanded view of the major component among Fig. 1, and Fig. 3 is that the A-A of Fig. 1 is to sectional view.
In Fig. 1 to Fig. 3,1 expression seal container, 2 expression motor part, 2a represents the rotor of motor, 2b represents stator, 3 expression bent axles, 4 expression main bearings, 5 expression compressor arrangement portions, 6a represents the 1st cylinder, 6b represents the 2nd cylinder, 50 expression dividing plates, 8 vice bearings, 9 expression shells, 10a represents the 1st piston, 10b represents the 2nd piston, 11 expression shells, 12a, 12b represents impeller, 13 expressions the 1st crank pin, 14 expressions the 2nd crank pin, the chamber is discharged in 15 expressions, 16 expression exhaust passageways, the chamber is discharged in 17 expressions, 18 expression discharge tubes, 19a, 19b represents suction pipe, 20a, 20b represents the suction port of cylinder, 21a, 21b represents to arrive suction port 20a, the intake line part of 20b, 22a, 22b represents from suction pipe 19a, the intake line part that 19b extends, 23a represents to be communicated with the pipe section of intake line part 21a and 22a, 23b represents to be communicated with the intake line part of intake line part 21b and 22b, 30 expressions are communicated with the intake line part of intake line part 23a and 23b.
Following embodiment 1 is possessing 2 cylinder rotary compressors of 2 cylinders as object.
The main bearing 4 that supports bent axle 3 is fixed by welding on the inwall of seal container 1.And in a side space built-in electric motor portion 2 of above-mentioned main bearing 4, compressor having internally mounted structural portion 5 in another space.Motor part 2 be by the rotor 2a that embeds fixed crankshaft 3 with relative with rotor 2a and constitute with the coaxial stator 2b of rotor 2a, stator 2b is fixed in the seal container 1.
In compressor arrangement portion 5, bent axle 3 further extends from main bearing 4, supports its front end by supplementary bearing 8.With 2 cylinder 6a, 6b and dividing plate 50 above-mentioned main bearing 4 and supplementary bearing 8 are separated, form 2 groups of working spaces.Be separately positioned on the crank pin portion 13,14 that forms on the bent axle 3 in the inside of above-mentioned cylinder 6a, 6b.Inside at above-mentioned cylinder 6a, 6b is equipped with piston 10a, 10b respectively.Above-mentioned piston 10a, 10b are embedded in respectively in the crank pin 13,14.Crank pin 13,14 has 180 ° phase difference on the circumferencial direction of bent axle 3.
By motor part 2, rotation drives bent axle 3, and then with the rotation of crank pin portion 13,14, piston 10a, 10b rotate with 180 ° phase difference, passes through spring members impeller crimping 12a, 12b in above-mentioned piston 10a, 10b usually.In addition, though not shown impeller 12b for the ease of understanding, encloses symbol 12b and describes.In cylinder 6a,, form the working room that constitutes by suction chamber 51 and pressing chamber 52 by piston 10a and impeller 12a.And in cylinder 6b,, form the working room that constitutes by suction chamber 51 and pressing chamber 52 by piston 10b and impeller 12b.In addition, though not shown suction chamber 51 in cylinder 6b side for easy understanding, is enclosed symbol 6b and is described.
By the off-centre rotation of the piston 10a, the 10b that are undertaken by the rotation of bent axle 3, suction chamber 51 and pressing chamber 52 in cylinder 6a, the 6b are compressed repeatedly, expand.When the suction chamber 51 of cylinder 6a, 6b expands, supply refrigerant gas by freeze cycle by suction pipe 19a, 19b, and be drawn into respectively in the suction chamber 51 by intake line.
With bent axle 3 rotations, pressing chamber 52 is reduced, and refrigerant gas is compressed thus, if reach certain pressure (head pressure), compression refrigeration gas in the cylinder 6a sprays in the exhaust chamber 17 that is formed by main bearing 4 and its shell 11, and the compression refrigeration gas in the cylinder 6b sprays in the discharge chamber 15 that is formed by supplementary bearing 8 and its shell 9 simultaneously.By cylinder 6a, 6b alternate compression refrigerant gas, and pass through to discharge chamber 17,15 and in seal container 1, discharge refrigerant gas, arrange to freeze cycle by discharge tube 18 from seal container 1 then.
The part that the direction to seal container 1 of suction pipe 19a, 19b and cylinder 6a, 6b is extended is connected, and be communicated with by suction port 20a, the 20b of intake line in suction chamber 51 formation, described intake line forms at cylinder 6a, 6b.Above-mentioned intake line is to constitute by the intake line part 22a that forms at cylinder 6a, 23a, 21a and the intake line part 22b that forms at cylinder 6b, 23b, 21b and in the intake line part 30 that dividing plate 50 forms.
The lip part that intake line part 23a, 30,23b run through cylinder 6a, 6b and dividing plate 50 is provided with, and the cross-section area of above-mentioned pipe section is a circular hole.The direction that intake line part 23a, 30,23b are communicated with parallels (being above-below direction among the figure) with bent axle, and its two ends are the flange surface sealings by main bearing 5 and supplementary bearing 8.
Intake line part 22a, 22b extend to radial direction, and suction pipe 19a, 19b and intake line part 23a, 23b are connected.Intake line part 21a, 21b extend to radial direction, and intake line part 23a, 23b and suction port 20a, 20b are connected.Thus, suction port 20a, 20b are interconnected by intake line part 21a, 23a, 30,23b, 21b.And suction port 20a is communicated with suction pipe 19b by intake line part 21a, 23a, 30,23b, 22b.And suction port 20b is communicated with suction pipe 19a by intake line part 21b, 23b, 30,23a, 22a.
According to present embodiment, big when the Volume Changes of the suction chamber 51 of the 1st cylinder 6a, when inhalation flow is big, refrigerant gas is mainly by intake line part 22a, 23a, 21a, be drawn into the 1st suction port 20a from the 1st suction pipe 19a, but also, be drawn into the 1st suction port 20a from the 2nd suction pipe 19b by intake line part 22b, 23b, 30,23a, 21a.But because 180 ° of the 2nd cylinder piston-rod displacements at this moment, so the Volume Changes of the suction chamber 51 of the 2nd cylinder 6b is little, inhalation flow is little.
On the contrary, big when the Volume Changes of the suction chamber 51 of the 2nd cylinder 6b, when inhalation flow is big, refrigerant gas is mainly by intake line part 22b, 23b, 21b, be drawn into the 2nd suction port 20b from the 2nd suction pipe 1 9b, but also by intake line part 22a, 23a, 30,23b, 21b, from the 1st suction pipe 19a, be drawn among the 2nd suction port 20b.At this moment because of 180 ° of the 1st cylinder piston-rod displacements, so the Volume Changes of the suction chamber of the 1st cylinder 6a is little, inhalation flow is little.
2 cylinder rotary compressors, its Volume Changes of once rotating is big, the variation of inhalation flow is also big, the maximum inhalation flow that cylinder 6a, 6b when 180 ° of displacements, occur, in the present embodiment, because by intake line part 30, be communicated with the intake line of cylinder 6a, 6b as mentioned above, so can suck refrigerant gas to side draught inlet 20a or 20b from both sides suction pipe 19a, 19b, thereby can in suction pipe 19a, 19b, reduce the loss that causes by the pipeline fluid resistance.
But, because the Volume Changes of the suction chamber 51 of each cylinder 6a, 6b produces pressure surge on the intake line of each cylinder 6a, 6b, so if only each intake line is communicated with, then be subjected to pressure surge each other sometimes, become instability or inhalation flow of suction condition descends.In the present embodiment intake line part 23a, the 23b of each cylinder 6a, 6b are connected to and form great pipe section on main bearing 4 or the supplementary bearing 8, wherein main bearing 4 or supplementary bearing 8 are as the end plate of expanding to the cylinder both ends of the surface until opening.Pipe section 23a, 23b have length on the axle direction of cylinder 6a, 6b, intake line part 21a, 21b, 22a and 22b are bigger at sectional area ratio pipe section 23a, the 23b sectional area on cylinder 6a, 6b axle direction on the gas flow direction simultaneously.Therefore, have the gas flow rate that flows to from suction pipe 19a, 19b and slow down, thereby can make the little effect of pressure surge at suction line part 23a, 23b.In addition, because be communicated with intake line part 23a, 23b by intake line part 30, the flow of intake line 23a, 23b averages out, pressure surge is minimum so flow into.
Therefore,, can make the pressure surge in the intake line of each cylinder 6a, 6b little, prevent cylinder 6a, 6b suction interference each other, reduce the inhalation flow loss, improve the efficient of compressor according to present embodiment.
Below, with reference to accompanying drawing 4,5 explanation embodiments of the invention 2.Fig. 4 is the major component sectional view of the multi-cylinder compressor of the embodiment of the invention 2, and Fig. 5 is that the B-B of Fig. 4 is to sectional view.This embodiment 2 is different with embodiment 1 on the point of the following stated, and other point is substantially the same manner as Example 1.
In Fig. 4 and Fig. 5, cross-section area is arranged on the 1st cylinder 6a for circular intake line part 23a, and is communicated with suction pipe 19a by intake line part 22a.Intake line part 30 is arranged on dividing plate 50, is to be made of conus portion 30a and edge part 30b.Conus portion 30a narrows down gradually from the 1st cylinder 6a side direction the 2nd cylinder 6b side.The diameter of edge part 30b is consistent with the narrow diameter of conus portion 30a, to the 2nd cylinder 6b side opening.The intake line part 23b of circular cross-section is that the end face since the 2nd cylinder 6b extends to a position that arrives before the other end.And cross-section area is set on the 2nd cylinder 6a for circular intake line part 23b, and is communicated with intake line part 30 by above-mentioned opening portion.Form the groove of thin width at the suction chamber 51 of groove cylinder 6a, 6b, and it as suction port 20a, 20b.Intake line part 21a, 21b are communicated with suction port 20a, 20b and intake line part 23a, 23b, simultaneously with the inscribed of intake line part 23a, 23b, finish connection.In this embodiment 2, do not connect suction pipe at cylinder 6b.
In this embodiment 2, Volume Changes by each cylinder 6a, 6b sucks refrigerant gas, when the intake of the 1st cylinder 6a is big, refrigerant gas flows to intake line part 23a from suction pipe 19a, pipeline section is long-pending to be enlarged, and after flow velocity descends thus,, be inhaled in the suction chamber 51 of the 1st cylinder 6a by intake line part 21a, suction port 20a.At this moment, by the variation in pressure that produces in suction line part 23a, gas is from suction line part 23b side adverse current, but because the throttling action of intake line part 21b, 23b and intake line part 30 can reduce the adverse current flow.That is to say, when producing from adverse current that the 2nd cylinder 6b flows out, refrigerant gas from intake line part 23b in connect and the suction line part 21b that puts, flow into to intake line part 23b along the direction that connects, produce eddy current in this course, further reduce by edge part 30b throttling and the adverse current that produces from pipe section 30.
In addition, when the inhalation flow of the 2nd cylinder 6b was big, refrigerant gas flowed into the intake line part 23a from suction pipe 19a, and is inhaled into by intake line part 30,23b, 21b and suction port 20b in the suction chamber 51 of the 2nd cylinder 6b.At this moment, 23a reduces flow velocity by the intake line part, and pressure surge reduces the pipe resistance decline that produces owing to bending simultaneously.In addition, by conus portion 30a, the pipe resistance that sucks direction increases hardly.In addition, because flow, so pipe resistance does not in this course almost increase yet from intake line part 23b along inwall to intake line part 21b.When the intake of above-mentioned the 2nd cylinder 6b is big, produce the adverse current that flows out from the suction chamber 51 of the 1st cylinder 6a, but the inertia by the gas that flows into from suction pipe 19a is pressed into the fluid that flows out from intake line part 21a, reduces adverse current.
In addition,, constitute by the groove of width, also have following effect, effect less than the internal diameter of intake line and suction pipe 19a to suction port 20a, the 20b of cylinder 6a, 6b opening as shown in the foregoing description 2.In rotary compressor, because in rotary course, during the compression beginning, suction port 20a, 20b are to suction chamber 51 openings of cylinder 6a, 6b, so the time of compression beginning is delayed, stopped up by piston 10a, 10b until above-mentioned suction port 20a, 20b, the pressurized gas that remains in simultaneously in the tap hole 24 expands again, from suction port 20a, 20b adverse current.Therefore, as suction port 20a, when 20b is big, the above-mentioned compression elapsed time is delayed and increases reflux flow.And in this embodiment 2, because the width of suction port 20a, 20b is narrow, thus have the compression elapsed time early, and reduce the effect of reflux flow.And,, reduce the effect of inhalation flow loss so the resistance that has on the intake line 21b is little because flow into to intake line part 21b along the inwall of the circular cross-section of intake line part 23b.
Clear from the above description, according to the present invention, prevent that the pressure surge that is produced by a side cylinder from hindering the phenomenon that sucks to the working room of opposite side cylinder, thus the multi-cylinder compressor that can be reduced suction loss, raise the efficiency.
According to the present invention, by preventing to produce the adverse current phenomenon that the opposite side working room sucks gas by the induction stroke of a side working room, thus the multi-cylinder compressor that can be reduced suction loss, raise the efficiency.
Claims (3)
1, a kind of multi-cylinder compressor, connect motor part and compressor arrangement portion and be housed in the seal container by bent axle, the above-mentioned compressor structural portion has multi cylinder, in above-mentioned each cylinder, form simultaneously and separate a plurality of working rooms that form by dividing plate and end plate, eccentric a plurality of crank pins are set on the different phase place of above-mentioned bent axle, simultaneously in each crank pin, embed piston, and its off-centre in above-mentioned each working room is rotated, above-mentioned working room has the suction port that is communicated with by intake line and the suction pipe that is connected with above-mentioned cylinder, it is characterized in that above-mentioned intake line has the connecting pipe part between the pipe section that is communicated with above-mentioned each cylinder and extends to the cylinder pipe section of cylinder both ends of the surface.
2, multi-cylinder compressor according to claim 1 is characterized in that, connects suction pipe on above-mentioned all cylinders, and above-mentioned all cylinders have the cylinder pipe section that extends to the cylinder both ends of the surface simultaneously.
3, multi-cylinder compressor according to claim 1 is characterized in that, the volume of above-mentioned intake line is greater than wherein 1 maximum volume of above-mentioned a plurality of working rooms.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002025043 | 2002-02-01 | ||
| JP2002025043A JP2003227485A (en) | 2002-02-01 | 2002-02-01 | Multi-cylinder compressors |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101468610A Division CN101158354A (en) | 2002-02-01 | 2003-01-30 | Multi-cylinder compressors |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1435572A CN1435572A (en) | 2003-08-13 |
| CN100343518C true CN100343518C (en) | 2007-10-17 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031034519A CN100343518C (en) | 2002-02-01 | 2003-01-30 | Multi-cylinder compressor |
| CNA2007101468610A CN101158354A (en) | 2002-02-01 | 2003-01-30 | Multi-cylinder compressors |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101468610A CN101158354A (en) | 2002-02-01 | 2003-01-30 | Multi-cylinder compressors |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2003227485A (en) |
| CN (2) | CN100343518C (en) |
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| JP2005207306A (en) * | 2004-01-22 | 2005-08-04 | Mitsubishi Electric Corp | Two cylinder rotary compressor |
| JP5070097B2 (en) * | 2007-08-28 | 2012-11-07 | 東芝キヤリア株式会社 | Two-cylinder rotary compressor and refrigeration cycle apparatus using the same |
| CN101169117A (en) * | 2007-11-17 | 2008-04-30 | 美的集团有限公司 | Volume controlled rotary compressor air-breathing device |
| CN104806528B (en) * | 2014-01-23 | 2017-02-22 | 珠海格力电器股份有限公司 | Compressor gas suction structure and compressor |
| JP2016114049A (en) * | 2014-12-15 | 2016-06-23 | 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． | Rotary compressor |
| US10458408B2 (en) * | 2014-12-19 | 2019-10-29 | Fujitsu General Limited | Rotary compressor having communication path hole overlap with discharge chamber concave portion |
| CN105756930A (en) * | 2014-12-19 | 2016-07-13 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
| CN105545754B (en) * | 2016-03-01 | 2019-01-15 | 珠海凌达压缩机有限公司 | A kind of refrigeration equipment and its double suction air compressor |
| CN105626529A (en) * | 2016-03-04 | 2016-06-01 | 广东美芝制冷设备有限公司 | Multi-cylinder rotary compressor and refrigeration circulating device provided with same |
| JP2018080589A (en) | 2016-11-14 | 2018-05-24 | 株式会社富士通ゼネラル | Rotary Compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08270580A (en) * | 1995-03-31 | 1996-10-15 | Sanyo Electric Co Ltd | Hermetically sealed rotary compressor |
| CN1148141A (en) * | 1995-01-30 | 1997-04-23 | 三洋电机株式会社 | Multi-cylinder rotary air compressor |
| CN1233716A (en) * | 1998-04-27 | 1999-11-03 | 三星电子株式会社 | Hermetic rotary compressor |
| JP2001073976A (en) * | 1999-08-31 | 2001-03-21 | Sanyo Electric Co Ltd | Internal intermediate pressure type two-stage compression type rotary compressor |
-
2002
- 2002-02-01 JP JP2002025043A patent/JP2003227485A/en active Pending
-
2003
- 2003-01-30 CN CNB031034519A patent/CN100343518C/en active IP Right Grant
- 2003-01-30 CN CNA2007101468610A patent/CN101158354A/en not_active Application Discontinuation
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1148141A (en) * | 1995-01-30 | 1997-04-23 | 三洋电机株式会社 | Multi-cylinder rotary air compressor |
| JPH08270580A (en) * | 1995-03-31 | 1996-10-15 | Sanyo Electric Co Ltd | Hermetically sealed rotary compressor |
| CN1233716A (en) * | 1998-04-27 | 1999-11-03 | 三星电子株式会社 | Hermetic rotary compressor |
| JP2001073976A (en) * | 1999-08-31 | 2001-03-21 | Sanyo Electric Co Ltd | Internal intermediate pressure type two-stage compression type rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2003227485A (en) | 2003-08-15 |
| CN101158354A (en) | 2008-04-09 |
| CN1435572A (en) | 2003-08-13 |
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