CN103765012A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN103765012A CN103765012A CN201280042991.9A CN201280042991A CN103765012A CN 103765012 A CN103765012 A CN 103765012A CN 201280042991 A CN201280042991 A CN 201280042991A CN 103765012 A CN103765012 A CN 103765012A
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- chamber side
- blade groove
- suction chamber
- blade
- pressing chamber
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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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
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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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A rotary compressor of the present invention comprises has a cylinder (30), an eccentric part (31a) of a shaft, a piston (32), and a vane (33), wherein an intake chamber-side contact surface (33a) and a compression chamber-side contact surface (33b) are formed in the vane (33), lubrication oil is supplied to the intake chamber-side contact surface (33a) and the compression chamber-side contact surface (33b) from an oil accumulator (6), and a pressure-difference creation mechanism, which causes the pressure added to the compression chamber-side contact surface (33b) to be greater than that of the intake chamber-side contact surface (33a), is formed in a state in which the pressure difference between an intake chamber (39a) and a compression chamber (39b) is equal to or less than a predetermined pressure, whereby refrigerant gas and the lubrication oil are prevented from leaking into the intake chamber (39a) and the compression chamber (39b) through a gap between the vane (33) and a vane groove (30b).
Description
Technical field
The present invention relates to the rotary compressor for air conditioner, refrigerating machine, blower, hot-warer supplying machine etc.
Background technique
Up to now, in refrigerating plant, air bells conditioner etc., use compressor, it is for gas refrigerant in evaporator evaporation is sucked, and is compressed to the required pressure of gas refrigerant that condensation sucks, and sends the gas refrigerant of High Temperature High Pressure.As the one of this compressor, known have a rotary compressor.
Rotary compressor is linked motor and compression mechanical part be accommodated in seal container by bent axle.Compression mechanical part comprises cylinder, upper bearing (metal), lower bearing and piston.The end plate of upper bearing (metal) and the end plate obturation of lower bearing for the both ends of the surface of cylinder.Upper bearing (metal) and lower bearing supporting for bent axle.Between upper bearing (metal) and lower bearing, dispose the eccentric part of bent axle.Piston is embedded in the eccentric part of bent axle.Cylinder, upper bearing (metal), lower bearing and piston form compression volume.
At cylinder, be formed with blade groove, in blade groove, dispose blade.The eccentric rotary that blade is followed piston moves reciprocatingly, and will in compression volume, be divided into suction chamber and pressing chamber.In bent axle, at axis, portion is provided with oilhole, in the wall portion of the bent axle with respect to upper bearing (metal), lower bearing, is respectively arranged with the oil supply hole being communicated with oilhole.
In addition, in the wall portion of eccentric part, be provided with the oil supply hole being communicated with oilhole, at the outer circumferential face of eccentric part, be formed with oil groove.
On the other hand, at cylinder, be provided with the inhalation port that refrigerant gas is drawn into suction chamber.At upper bearing (metal), be provided with from the discharge port of pressing chamber discharging refrigerant gas.The exhaust end degree of lip-rounding becomes hole rounded while connecting the overlooking of upper bearing (metal), and at the upper surface of discharging port, is provided with the expulsion valve of opening in the situation that being subject to authorized pressure.This expulsion valve is covered by cup type silencing apparatus.
Suction chamber, with the expansion in space, sucks refrigerant gas from inhalation port, and pressing chamber dwindles with space, more than refrigerant gas is compressed to authorized pressure.Refrigerant gas after compression is opened expulsion valve, and flows out from discharging port, via cup type silencing apparatus, is expelled in seal container.
In addition, in blade groove, be provided with spring eye, when this spring eye is used for being accommodated in compressor start, blade pressed to the spring of piston, in spring eye, be full of lubricant oil and higher pressure refrigerant gas.Lubricant oil and pressurized gas are the gap via blade and blade groove from this spring eye, and bleed suction chamber and pressing chamber, cause decrease in efficiency.
In order to reduce this leakage, there is the structure shown in a kind of Figure 11.
Figure 11 is the major component plan view that represents the cylinder of the rotary compressor of prior art.
Figure 11 represents the part of cylinder 130 and is configured in the part of the piston 132 in cylinder 130.At cylinder 130, be formed with blade groove 130b.At blade groove 130b, dispose blade 133.
At blade 133, be formed with oil storage tank 133a.Oil storage tank 133a is formed with multiple with interval arbitrarily in the direction of intersecting with the glide direction of blade 133.By oil storage tank 133a, between blade 133 and blade groove 130b, form sufficient oil film.This oil film performance labyrinth sealing (Labyrinth Seal) effect, can prevent the leakage (for example,, with reference to patent documentation 1) of lubricant oil, refrigerant gas etc.
Prior art document
Patent documentation
Patent documentation 1: Japanese kokai publication hei 3-185292 communique
Summary of the invention
The technical problem solving is wanted in invention
As Patent Document 1, by forming oil storage tank 133a at blade 133, can bring into play labyrinth sealing effect, the leakage of inhibition refrigerant gas etc., improves compression efficiency.
But, when suction chamber and pressing chamber are in uniform pressure lower time, the pressure putting on the face (suction chamber side contacts face 133b and pressing chamber side contacts face 133c) forming at the thickness direction of blade 133 does not produce difference, therefore blade 133 can not be inclined to suction chamber side, blade 133 does not come in contact with blade groove 130b, and produces gap between blade 133 and blade groove 130b.
That is, in patent documentation 1, can, by labyrinth sealing effect, realize the inhibition of the leakage of lubricant oil, refrigerant gas etc., but when suction chamber and pressing chamber are under uniform pressure, cannot will between blade 133 and blade groove 130b, seal completely.
The present invention makes for the problem that solves above-mentioned prior art, its object is to provide a kind of rotary compressor, its pressure difference at suction chamber and pressing chamber is under the state below authorized pressure, can suppress refrigerant gas and lubricant oil via the gap between blade and blade groove bleed suction chamber and pressing chamber.
For the technological scheme of dealing with problems
To achieve these goals, the present invention is a kind of rotary compressor, it is characterized in that, comprising: cylinder, be configured in the eccentric part of the axle in described cylinder, be entrenched in the piston of described eccentric part, and blade, follow the eccentric rotary of described piston, in the blade groove that is arranged at described cylinder, move reciprocatingly, suction chamber and pressing chamber will be divided in described cylinder, at described blade, be formed with the suction chamber side contacts face contacting with the described blade groove of described suction chamber side, with the pressing chamber side contacts face contacting with the described blade groove of described pressing chamber side, lubricant oil is supplied to described suction chamber side contacts face and described pressing chamber side contacts face from store oil portion, in described rotary compressor, be formed with differential pressure generating mechanism, its pressure difference at described suction chamber and described pressing chamber is under the state below authorized pressure, the pressure that the pressure ratio that makes to put on described pressing chamber side contacts face puts on described suction chamber side contacts face is large.By by blade at the direction of the suction chamber side of blade groove is pressed and setting is communicated with store oil portion differential pressure generating mechanism, when suction chamber and pressing chamber are under uniform pressure, can suppress refrigerant gas, the lubricant oil gap via blade and blade groove, the suction chamber that bleeds, pressing chamber.
Invention effect
According to said structure, suction chamber and pressing chamber produce difference in uniform pressure lower time at thickness direction (suction chamber side contacts face and the pressing chamber side contacts face) applied pressure of blade, make blade tendency suction chamber side, blade is contacted with blade groove, thereby refrigerant gas, the lubricant oil of can suppress to bleed suction chamber and pressing chamber, raise the efficiency.And then, easily oil is remained between blade and blade groove, sliding mode is improved, and can suppress blade and shake in blade groove, therefore also can improve reliability.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the rotary compressor of embodiments of the present invention.
Fig. 2 is the amplification sectional view of the compression mechanical part of the rotary compressor of embodiments of the present invention.
(a) of Fig. 3 is the major component plan view that represents the cylinder of the rotary compressor of present embodiment, and (b) of Fig. 3 is from the major component side view of the A direction shown in this Fig. 3 (a) and the observation of B direction.
(a) of Fig. 4 is the major component plan view of the relation of near the cylinder of piston blade upper dead center time that represent present embodiment and blade, and (b) of Fig. 4 is the major component plan view of the relation of cylinder while reaching the pressure of regulation of the pressing chamber that represents present embodiment and blade.
(a) of Fig. 5 is the major component plan view that represents the cylinder of the rotary compressor of comparative example, and (b) of Fig. 5 is from the major component side view of the A direction shown in this Fig. 5 (a) and the observation of B direction.
(a) of Fig. 6 is the major component plan view of the relation of near the cylinder of piston blade upper dead center time that represent comparative example and blade, and (b) of Fig. 6 is the major component plan view of the relation of cylinder while reaching the pressure of regulation of the pressing chamber that represents the present embodiment of comparative example and blade.
Fig. 7 is the plotted curve with the blade efficiency different from the contact area rate of blade groove of the rotary compressor of explanation embodiments of the present invention.
(a) of Fig. 8 is the major component plan view that represents the cylinder of the rotary compressor of another embodiment of the present invention, and (b) of Fig. 8 is from the major component side view of the A direction shown in this Fig. 8 (a) and the observation of B direction.
Fig. 9 is the major component plan view that represents the cylinder of the rotary compressor of another embodiment of the invention.
(a) of Figure 10 is the major component plan view that represents the cylinder of the rotary compressor of another embodiment of the invention, and (b) of Figure 10 is from the major component side view of the A direction shown in this Figure 10 (a) and the observation of B direction.
Figure 11 is the blade of prior art and the plan view of cylinder.
Reference character
1 seal container
2 motor
3 compression mechanical parts
30 cylinders
30b blade groove
30c spring eye
31 bent axles
31a eccentric part
32 pistons
33 blades
34 upper bearing (metal)s
35 lower bearings
36 expulsion valves
37 cup type silencing apparatuss
38 discharge port
39 compression volumes
39a suction chamber
39b pressing chamber
40 inhalation ports
41 oilholes
42 oil supply holes
44 oil supply holes
45 oil grooves
46 spaces
47 spaces
60 spot-facings
Embodiment
The first invention is a kind of rotary compressor, it is characterized in that, comprising: cylinder, be configured in the eccentric part of the axle in described cylinder, be entrenched in the piston of described eccentric part, and blade, follow the eccentric rotary of described piston, in the blade groove that is arranged at described cylinder, move reciprocatingly, suction chamber and pressing chamber will be divided in described cylinder, at described blade, be formed with the suction chamber side contacts face contacting with the described blade groove of described suction chamber side, with the pressing chamber side contacts face contacting with the described blade groove of described pressing chamber side, lubricant oil is supplied to described suction chamber side contacts face and described pressing chamber side contacts face from store oil portion, in described rotary compressor, be formed with differential pressure generating mechanism, its pressure difference at described suction chamber and described pressing chamber is under the state below authorized pressure, the pressure that the pressure ratio that makes to put on described pressing chamber side contacts face puts on described suction chamber side contacts face is large.According to this structure, when suction chamber and pressing chamber are under uniform pressure, thickness direction (suction chamber side contacts face and pressing chamber side contacts face) applied pressure at blade produces difference, can make blade force, blade is contacted with blade groove, improve sealing, thereby can suppress refrigerant gas, lubricant oil via the gap between blade and blade groove bleed suction chamber and pressing chamber.In addition, because differential pressure generating mechanism is communicated with store oil portion, therefore easily lubricant oil is remained between blade and blade groove, improved reliability.
Specifically a kind of rotary compressor of the second invention, it is characterized in that, in the rotary compressor of the first invention, above-mentioned differential pressure generating mechanism, makes above-mentioned suction chamber side contacts face face large with area of contact above-mentioned blade groove with the above-mentioned pressing chamber side contacts of contact area rate above-mentioned blade groove.According to this structure, differential pressure generating mechanism is arranged at blade groove, while being arranged at the blade of motion with this differential pressure generating mechanism compared with, the retentivity of lubricant oil is improved.
Specifically a kind of rotary compressor of the 3rd invention, is characterized in that, in the rotary compressor of the second invention, in above-mentioned differential pressure generating mechanism, in the direction orthogonal with above-mentioned blade groove, is provided with the spot-facing being communicated with above-mentioned blade groove.According to this structure, can easily process with boring, facing cutter etc.
Specifically a kind of rotary compressor of the 4th invention, it is characterized in that, in the rotary compressor of the 3rd invention, as above-mentioned spot-facing, be provided with the suction chamber side spot-facing being communicated with the above-mentioned blade groove of above-mentioned suction chamber side and the pressing chamber side spot-facing being communicated with the above-mentioned blade groove of above-mentioned pressing chamber side.Conventionally, the height of cylinder is 4～6 times of left and right with respect to the width of blade groove.If consider general tool life, can only be drilled into the degree of depth of 2～3 times of hole diameter, therefore utilize the spot-facing being only communicated with a side of blade groove to be difficult to axially connecting by a hole processing.Spot-facing is not in the structure axially connecting, and in upper axle side and the lower shaft side of blade, the pressure balance on thickness direction (suction chamber side contacts face and pressing chamber side contacts face) loses, and therefore causes decrease in efficiency.With the spot-facing that suction chamber side and the pressing chamber side of blade groove are communicated with, the diameter of boring can be obtained larger than blade groove width, therefore passes through a hole easy processing in axial perforation.In addition, because the diameter of boring can be got greatly, so also extended tool life, processability is also improved.
Specifically a kind of rotary compressor of the 5th invention, it is characterized in that, in the rotary compressor of the second invention, above-mentioned pressing chamber side contacts face with area of contact above-mentioned blade groove and above-mentioned suction chamber side contacts ratio face and area of contact above-mentioned blade groove be more than 70%.According to this structure, when suction chamber and pressing chamber are in same pressure lower time, at the thickness direction (suction chamber side contacts face and pressing chamber side contacts face) of blade, applied pressure is poor can be not excessive, therefore can make the contact force of the suction chamber side of blade and blade groove diminish.In addition, when the contact force of blade and blade groove is while being maximum, because pressing chamber reaches the pressure of regulation, therefore store oil portion and pressing chamber become roughly equal pressure.Therefore, the gap of the pressing chamber side of blade and blade groove is roughly full of by high pressure, and differential pressure generating mechanism is inoperative, therefore becomes the pressure distribution equal with general rotary compressor, and blade and blade groove do not slide strongly, and reliability can variation.
Specifically a kind of rotary compressor of the 6th invention, it is characterized in that, in the rotary compressor of the first invention to the five inventions, as working fluid, use by the unitary system cryogen that refrigeration agent was formed that is basic ingredient with the HF hydrocarbon between carbon and carbon with two keys or the mix refrigerant that comprises above-mentioned refrigeration agent.This refrigeration agent has following characteristic, sucks density little, for aspect as with the equal ability of R410A, need the circulating load of 1.7 times, it is large that the difference of high low pressure becomes, and it is large that the impact of the leakage of lubricant oil and refrigerant gas becomes, and therefore can further effectively improve the efficiency of compressor.In addition, this refrigeration agent can not destroy ozone, and greenhouse effect index is low, therefore can work to the structure of the Air-conditioning Cycle of environment protection type.
Below, with reference to accompanying drawing, embodiments of the present invention are described.Wherein, the present invention is not limited to these mode of executions.
Fig. 1 is the longitudinal section of the rotary compressor of embodiments of the present invention.Fig. 2 is the amplification sectional view of the compression mechanical part of embodiments of the present invention.
As depicted in figs. 1 and 2, in the rotary compressor of present embodiment, motor 2 and compression mechanical part 3 are linked and are accommodated in seal container 1 by bent axle 31.On the top of seal container 1, be provided with discharge tube 5.In the bottom of seal container 1, be formed with store oil portion 6.Because the refrigeration agent after compression is discharged in seal container 1, therefore head pressure acts on store oil portion 6.
Compression mechanical part 3 comprises cylinder 30, upper bearing (metal) 34, lower bearing 35 and piston 32.The both ends of the surface of piston 30 are by the end plate obturation of the end plate of upper bearing (metal) 34 and lower bearing 35.Bent axle 31 is supported by upper bearing (metal) 34 and lower bearing 35.Between upper bearing (metal) 34 and lower bearing 35, dispose the eccentric part 31a of bent axle 31.Piston 32 is fitted to the eccentric part 31a of bent axle 31.Cylinder 30, upper bearing (metal) 34, lower bearing 35 form compression volume 39 together with piston 32.
At cylinder 30, be formed with inhalation port 40.
At bent axle 31, at axial direction, be provided with oilhole 41.In the wall portion of the bent axle 31 with respect to upper bearing (metal) 34, lower bearing 35, be respectively arranged with the oil supply hole 42,43 being communicated with oilhole 41.In addition, in the wall portion of eccentric part 31a, be provided with the oil supply hole 44 being communicated with oilhole 41, at the outer circumferential face of eccentric part 31a, be formed with oil groove 45.Lubricant oil is supplied to oilhole 41 from store oil portion 6.
Space 46 is surrounded by the inner peripheral surface of eccentric part 31a, upper bearing (metal) 34 and piston 32.Space 47 is surrounded by the inner peripheral surface of eccentric part 31a, lower bearing 35 and piston 32.Lubricant oil from oilhole 41 via oil supply hole 42 space 46 of bleeding.Lubricant oil from oilhole 41 via oil supply hole 43 space 47 of bleeding.Therefore, head pressure puts on space 46,47, so the state of space 46,47 in the pressure higher than compression volume 39 inside.
In addition, the height setting of cylinder 30 is the height of a little higher than piston 32, so that piston 32 can slide in inside.Consequently, between the end face of piston 32 and upper bearing (metal) 34 and between the end face of piston 32 and lower bearing 35, there is gap.Therefore lubricant oil leaks to compression volume 39 from space 46,47 via this gap.
Fig. 3 and Fig. 4 represent the cylinder of the rotary compressor of present embodiment.(a) of Fig. 3 is the major component plan view that represents the cylinder of the rotary compressor of present embodiment, and (b) of Fig. 3 is from the major component side view of the A direction shown in this Fig. 3 (a) and the observation of B direction.
At cylinder 30, be formed with blade groove 30b.At blade groove 30b, dispose the blade 33 shown in Fig. 1 and Fig. 2.In cylinder 30, compression volume 39, across blade groove 30b, is formed with suction chamber 39a and pressing chamber 39b.Suction chamber 39a is communicated with inhalation port 40.
(a) of Fig. 4 is near cylinder 30 while representing that piston 32 is positioned at blade 33 upper dead centers and the major component plan view of the relation of blade 33, and (b) of Fig. 4 is cylinder 30 while representing that pressing chamber 39b reaches the pressure of regulation and the major component plan view of the relation of blade 33.
As shown in Figure 4, at blade 33, be formed with the suction chamber side contacts face 33a contacting with the blade groove 30c of suction chamber 39a side and the pressing chamber side contacts face 33b contacting with the blade groove 30c of pressing chamber 39b side.Lubricant oil is supplied to suction chamber side contacts face 33a and pressing chamber side contacts face 33b from store oil portion 6.
, before explanation embodiments of the present invention, utilize Fig. 5 and Fig. 6 herein, the technical problem of the cylinder to rotary compressor as a comparative example describes.
(a) of Fig. 5 is the major component plan view that represents the cylinder of the rotary compressor of comparative example.(b) of Fig. 5 is from the major component side view of the A direction shown in this figure (a) and the observation of B direction.In addition, to giving identical symbol with the parts of the identical formation of present embodiment, also description thereof is omitted.(a) of Fig. 6 is near cylinder 130 while representing that piston 32 is positioned at blade 33 upper dead centers and the major component plan view of the relation of blade 33, and (b) of Fig. 6 is cylinder 130 while representing that pressing chamber 39b reaches the pressure of regulation and the major component plan view of the relation of blade 33.
The spring eye 130c of comparative example is equal length in suction chamber 39a side and pressing chamber 39b side.
Therefore, the area of contact of the suction chamber side contacts face of blade 33 pressing chamber side contacts face 3b 33a and area of contact blade groove 30b and blade 33 and blade groove 30b is covert etc.
As shown in Fig. 6 (a), when suction chamber 39a and pressing chamber 39b are in uniform pressure lower time, be the pressure difference of suction chamber 39a and pressing chamber 39b while being the low pressure below authorized pressure, between suction chamber side contacts face 33a and pressing chamber side contacts face 33b, do not produce pressure difference.Therefore, blade 33 can not be inclined to suction chamber 39a side, and suction chamber side contacts face 33a does not contact with blade groove 30b, and pressing chamber side contacts face 33b does not contact with blade groove 30b, in generation gap, the left and right of blade 33.Thus, be full of the higher pressure refrigerant gas of spring eye 30c or lubricant oil and can, via the gap of the left and right of blade 33 compression volume 39 that bleeds, cause decrease in efficiency.
Below, the differential pressure generating unit of present embodiment is described.
As shown in Figure 3, in the differential pressure generating unit of present embodiment, the pressing chamber side spring eye 30e that is positioned at pressing chamber 39b side is longer than the suction chamber side spring eye 30f that is positioned at suction chamber 39a side.Thus, the suction chamber side contacts face 33a of blade 33 and the pressing chamber side contacts face 33b of the contact area rate blade 33 of blade groove 30b and the area of contact of blade groove 30b are large.The region representing with oblique line in Fig. 3 (b) is the surface of contact of blade 33 and blade groove 30b.
As shown in Fig. 4 (a), when suction chamber 39a and pressing chamber 39b are in uniform pressure lower time, when the pressure difference of suction chamber 39a and pressing chamber 39b is the low pressure below authorized pressure, head pressure puts on spring eye 30c.Therefore, by making the contact area rate pressing chamber side contacts face 33b of suction chamber side contacts face 33a and blade groove 30b and the area of contact of blade groove 30b large, the pressure ratio suction chamber side contacts face 33a that can make to put on pressing chamber side contacts face 33b is large, by this pressure official post blade 33, tilts.Thus, can make blade 33 contact with blade groove 30b, improve sealing, can prevent that refrigerant gas and lubricant oil are from the suction chamber side contacts face 33a of blade 33 and the pressing chamber side contacts face 33b compression volume 39 that bleeds.
In addition, lubricant oil more easily remains between blade 33 and blade groove 30b, and reliability is also improved.On the other hand, when the contact force of the face of the suction chamber side contacts face 33a of blade 33 and the suction chamber 39a side of blade groove 30b reaches maximum, pressing chamber 39b reaches authorized pressure.Therefore, store oil portion 6 and pressing chamber 39b become roughly equal pressure.Therefore, the gap of the face of the pressing chamber side contacts face 33b of blade 33 and the pressing chamber 39b side of blade groove 30b is roughly full of by high pressure.This and the general blade 33 of rotary compressor and the pressure distribution (with reference to Fig. 6) of blade groove 30b are equal to, and therefore blade 33 can not slide strongly with blade groove 30b, and reliability can variation.
In addition, though not shown, in said structure, in blade 33 sides, be provided with spot-facing etc., thereby even if imported lubricant oil, also can obtain equal effect.
Then, Fig. 7 is the area of contact that represents the face of the pressing chamber side contacts face 33b of blade 33 and the pressing chamber 39b side of blade groove 30b, with respect to suction chamber side contacts face 33a and the ratio of area of contact of the face of the suction chamber 39a side of blade groove 30b and the plotted curve of the relation of efficiency of blade 33.
As shown in Figure 7, if making pressing chamber side contacts face 33b and the area of contact of blade groove 30b is more than 70% with respect to suction chamber side contacts face 33a with the ratio of the area of contact of blade groove 30b, when suction chamber 39a and pressing chamber 39b are under uniform pressure, be the pressure difference of suction chamber 39a and pressing chamber 39b while being the low pressure below authorized pressure, the pressure difference that puts on suction chamber side contacts face 33a and pressing chamber side contacts face 33b can be not excessive.Therefore, can reduce the contact force of the face of the suction chamber 39a side of suction chamber side contacts face 33a and blade groove 30b, can suppress again lubricant oil and refrigerant gas from blade 33 and the gap of blade groove 30b, bleed suction chamber 39a and pressing chamber 39b, and raise the efficiency.
As mentioned above, preferably making pressing chamber side contacts face 33b and the area of contact of blade groove 30b is more than 70% with respect to suction chamber side contacts face 33a with the ratio of the area of contact of blade groove 30b.
Fig. 8 is the cylinder of the rotary compressor of another embodiment of the present invention.Only point different from the embodiment described above is described, omit to the explanation of above-mentioned mode of execution same structure.
(a) of Fig. 8 is the major component plan view that represents the cylinder of the rotary compressor of another embodiment of the present invention, and (b) of Fig. 8 is from the major component side view of the A direction shown in this figure (a) and the observation of B direction.
As shown in Figure 8, as differential pressure generating unit, the spot-facing 60 that also can be communicated with blade groove 30b in the direction setting orthogonal with blade groove 30b.Thus, can change the area of contact of the face of the area of contact of face of the suction chamber side contacts face 33a of blade 33 and the suction chamber 39a side of blade groove 30b and the pressing chamber 39b side of the pressing chamber side contacts face 33b of blade 33 and blade groove 30b.That is, as shown in Fig. 8 (b), spot-facing 60 is set as differential pressure generating unit, the suction chamber side contacts face 33a of blade 33 and the pressing chamber side contacts face 33b of the contact area rate blade 33 of blade groove 30b and the area of contact of blade groove 30b are large thus.It in Fig. 8 (b), with the region shown in oblique line, is the surface of contact of blade 33 and blade groove 30b.
In addition, in the mode of execution shown in Fig. 8, be provided with the differential pressure generating unit of realizing by spot-facing 60, carry out the alternative pressing chamber side spring eye 30e that is positioned at pressing chamber 39b side and establish than the long differential pressure generating unit of suction chamber side spring eye 30f that is positioned at suction chamber 39a side.But, also the pressing chamber side spring eye 30e that is positioned at pressing chamber 39b side can be established to such an extent that than the long differential pressure generating unit of suction chamber side spring eye 30f that is positioned at suction chamber 39a side, arrange together with the differential pressure generating unit of realizing by spot-facing 60.
Spot-facing 60 can utilize rig or facing cutter easily to process.
Fig. 9 is the cylinder of the rotary compressor of another embodiment of the invention.Only point different from the embodiment described above is described, omit to the explanation of above-mentioned mode of execution same structure.
As shown in Figure 9, if make spot-facing 60 center be formed on the position more in the outer part than blade groove 30b, spot-facing 60 becomes acute angle with the cross part (edge) of blade groove 30b, therefore the lubricity variation of oil.Therefore, what preferably make spot-facing 60 is centered close to blade groove 30b, makes spot-facing 60 and the cross part of blade groove 30b become obtuse angle (with reference to Fig. 8).
Figure 10 is the cylinder of the rotary compressor of another embodiment of the invention.Only point different from the embodiment described above is described, omit to the explanation of above-mentioned mode of execution same structure.
(a) of Figure 10 is the major component plan view that represents the cylinder of the rotary compressor of another embodiment of the invention, and (b) of Figure 10 is from the major component side view of the A direction shown in Figure 10 (a) and the observation of B direction.
As shown in figure 10, as spot-facing 60, also can be provided with the suction chamber side spot-facing 60a being communicated with the blade groove 30b of suction chamber 39a side and the pressing chamber side spot-facing 60b being communicated with the blade groove 30b of pressing chamber 39b side.
Conventionally, the height of cylinder 30 is 4～6 times of left and right of the width of blade groove 30b.If consider general tool life, can only be drilled into the degree of depth of 2～3 times of hole diameter, therefore utilize the spot-facing 60 being only communicated with a side of blade groove 30b to be difficult to axially connecting by a hole processing.
Spot-facing 60, in the structure axially not connecting, at upper axle side 34a and the lower shaft side 35a of blade 33, loses the pressure balance of thickness direction, therefore causes decrease in efficiency.As spot-facing 60, suction chamber side spot-facing 60a and pressing chamber side spot-facing 60b are set, the diameter of boring can be obtained larger than the width of blade groove 30b, therefore easily by a hole, processes in axial perforation.In addition, because the diameter of boring can be got greatly, so also extended tool life, processability is also improved.
In addition, comprise standing shape and be combined with piston peripheral part and pressing chamber is divided into low voltage side and on high-tension side blade and freely shake and the rotary compressor of the shake lining (bush) of the ground supporting blade of freely advancing and retreat in, also can obtain the effect same with foregoing.In addition, comprising in the rotary compressor of the blade being freely joltily connected at front end with piston, also can obtain the effect same with foregoing.
In addition, as working fluid, use the unitary system cryogen being formed as the refrigeration agent of basic ingredient by the HF hydrocarbon (HFO) to there are two keys between carbon and carbon or the mix refrigerant that comprises above-mentioned refrigeration agent.This refrigeration agent has following characteristic, suck density little, for aspect as with the equal ability of R410A, need the circulating load of 1.7 times, therefore, it is large that the difference of the high low pressure in compression becomes, and it is large that the impact of the leakage of lubricant oil and refrigerant gas becomes, and therefore can further effectively improve the efficiency of compressor.In addition, this refrigeration agent can not destroy ozone, and greenhouse effect index is low, therefore can work to the structure of the Air-conditioning Cycle of environmental protection.
In addition, as duty cryogen, can use and adopt tetrafluoeopropene (HFO1234yf) as HF hydrocarbon, adopt the mix refrigerant of difluoromethane (HFC32) as hydrogen fluorohydrocarbon.
In addition, as duty cryogen, also can use and adopt tetrafluoeopropene (HFO1234yf) as HF hydrocarbon, adopt the mix refrigerant of pentafluoroethane (HFC125) as hydrogen fluorohydrocarbon.
In addition, as duty cryogen, also can use and adopt tetrafluoeopropene (HFO1234yf) as HF hydrocarbon, adopt pentafluoroethane (HFC125), difluoromethane (HFC32) mix refrigerant being formed by three kinds of compositions as hydrogen fluorohydrocarbon.
In addition, in the above-described embodiment, as an example of a piston type rotary compressor of a cylinder example, be illustrated, but also can adopt the rotary compressor with multiple cylinders 30.
Utilizability in industry
As mentioned above, rotary compressor of the present invention, makes blade press to the direction of the suction chamber side of blade groove, and arranges by the differential pressure generating unit being communicated with store oil portion.Thus, do not reduce reliability, the lubricant oil in the time of can reducing suction chamber and pressing chamber and be uniform pressure and refrigerant gas, from the clearance leakage of blade and blade groove, significantly improve the efficiency of compressor.Therefore,, except using the air regulator of HFC class refrigeration agent or HCFC class refrigeration agent with compressor, can also be applicable to use natural refrigerant CO
2the purposes of air regulator, heat pump type hot-warer supplying machine etc.
Claims (according to the modification of the 19th article of treaty)
1. a rotary compressor, is characterized in that, comprising:
Cylinder;
Be configured in the eccentric part of the axle in described cylinder;
Be entrenched in the piston of described eccentric part; With
Blade, follows the eccentric rotary of described piston, in the blade groove that is arranged at described cylinder, moves reciprocatingly, and will in described cylinder, be divided into suction chamber and pressing chamber,
At described blade, be formed with the suction chamber side contacts face contacting with the described blade groove of described suction chamber side and the pressing chamber side contacts face contacting with the described blade groove of described pressing chamber side,
Lubricant oil is supplied to described suction chamber side contacts face and described pressing chamber side contacts face from store oil portion, in described rotary compressor,
Be formed with differential pressure generating mechanism, its pressure difference at described suction chamber and described pressing chamber is under the state below authorized pressure, and the pressure that the pressure ratio that makes to put on described pressing chamber side contacts face puts on described suction chamber side contacts face is large,
Described differential pressure generating mechanism, makes described suction chamber side contacts face face large with area of contact described blade groove with pressing chamber side contacts described in contact area rate described blade groove,
In the direction orthogonal with described blade groove, be provided with the spot-facing being communicated with described blade groove.
2.(deletes)
3.(deletes)
4. rotary compressor as claimed in claim 3, is characterized in that:
As described spot-facing, be provided with the suction chamber side spot-facing being communicated with the described blade groove of described suction chamber side and the pressing chamber side spot-facing being communicated with the described blade groove of described pressing chamber side.
5. rotary compressor as claimed in claim 2, is characterized in that:
Described pressing chamber side contacts face with area of contact described blade groove and described suction chamber side contacts ratio face and area of contact described blade groove be more than 70%.
6. the rotary compressor as described in any one in claim 1～5, is characterized in that:
As working fluid, use by the unitary system cryogen that refrigeration agent was formed that is basic ingredient with the HF hydrocarbon between carbon and carbon with two keys or the mix refrigerant that comprises described refrigeration agent.
Claims (6)
1. a rotary compressor, is characterized in that, comprising:
Cylinder;
Be configured in the eccentric part of the axle in described cylinder;
Be entrenched in the piston of described eccentric part; With
Blade, follows the eccentric rotary of described piston, in the blade groove that is arranged at described cylinder, moves reciprocatingly, and will in described cylinder, be divided into suction chamber and pressing chamber,
At described blade, be formed with the suction chamber side contacts face contacting with the described blade groove of described suction chamber side and the pressing chamber side contacts face contacting with the described blade groove of described pressing chamber side,
Lubricant oil is supplied to described suction chamber side contacts face and described pressing chamber side contacts face from store oil portion, in described rotary compressor,
Be formed with differential pressure generating mechanism, its pressure difference at described suction chamber and described pressing chamber is under the state below authorized pressure, and the pressure that the pressure ratio that makes to put on described pressing chamber side contacts face puts on described suction chamber side contacts face is large.
2. rotary compressor as claimed in claim 1, is characterized in that:
In described differential pressure generating mechanism, make described suction chamber side contacts face face large with area of contact described blade groove with pressing chamber side contacts described in contact area rate described blade groove.
3. rotary compressor as claimed in claim 2, is characterized in that:
In described differential pressure generating mechanism, in the direction orthogonal with described blade groove, be provided with the spot-facing being communicated with described blade groove.
4. rotary compressor as claimed in claim 3, is characterized in that:
As described spot-facing, be provided with the suction chamber side spot-facing being communicated with the described blade groove of described suction chamber side and the pressing chamber side spot-facing being communicated with the described blade groove of described pressing chamber side.
5. rotary compressor as claimed in claim 2, is characterized in that:
Described pressing chamber side contacts face with area of contact described blade groove and described suction chamber side contacts ratio face and area of contact described blade groove be more than 70%.
6. the rotary compressor as described in any one in claim 1～5, is characterized in that:
As working fluid, use by the unitary system cryogen that refrigeration agent was formed that is basic ingredient with the HF hydrocarbon between carbon and carbon with two keys or the mix refrigerant that comprises described refrigeration agent.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011258967 | 2011-11-28 | ||
| JP2011-258967 | 2011-11-28 | ||
| PCT/JP2012/007594 WO2013080519A1 (en) | 2011-11-28 | 2012-11-27 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103765012A true CN103765012A (en) | 2014-04-30 |
Family
ID=48535013
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280042991.9A Pending CN103765012A (en) | 2011-11-28 | 2012-11-27 | Rotary compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPWO2013080519A1 (en) |
| CN (1) | CN103765012A (en) |
| WO (1) | WO2013080519A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5991958B2 (en) * | 2013-11-28 | 2016-09-14 | 三菱電機株式会社 | Rotary compressor |
| CN106930943A (en) * | 2015-12-29 | 2017-07-07 | 珠海凌达压缩机有限公司 | Compressor, pump assembly and its cylinder |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56147388U (en) * | 1980-04-03 | 1981-11-06 | ||
| JPS6186590U (en) * | 1984-11-13 | 1986-06-06 | ||
| JPS63201390A (en) * | 1987-02-18 | 1988-08-19 | Matsushita Refrig Co | Rotary type compressor |
| JP3867006B2 (en) * | 2002-04-12 | 2007-01-10 | 東芝キヤリア株式会社 | Rotary compressor |
-
2012
- 2012-11-27 CN CN201280042991.9A patent/CN103765012A/en active Pending
- 2012-11-27 WO PCT/JP2012/007594 patent/WO2013080519A1/en active Application Filing
- 2012-11-27 JP JP2013546992A patent/JPWO2013080519A1/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2013080519A1 (en) | 2015-04-27 |
| WO2013080519A1 (en) | 2013-06-06 |
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Application publication date: 20140430 |