CN107076148A - Rotary compressor and freezing cycle device - Google Patents
Rotary compressor and freezing cycle device Download PDFInfo
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- CN107076148A CN107076148A CN201580057254.XA CN201580057254A CN107076148A CN 107076148 A CN107076148 A CN 107076148A CN 201580057254 A CN201580057254 A CN 201580057254A CN 107076148 A CN107076148 A CN 107076148A
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- Prior art keywords
- mentioned
- blade
- supply tank
- oil supply
- cylinder
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- 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
Abstract
The rotary compressor of embodiment has container, cylinder, blocking plate, roller, blade and oil supply tank.Container lubricating oil.Cylinder is the tubular being accommodated in container.Blocking plate blocks the opening portion of cylinder, and cylinder chamber is formed together with cylinder.Roller eccentric rotary in cylinder chamber.Blade can retreat along with the eccentric rotary of roller in cylinder chamber on the direction of rotation of roller in parting-off cylinder room.Oil supply tank is formed at the opposed faces opposed with blocking plate in blade, extends along the moving direction of blade, also, the 1st end, with being connected in container, the 2nd end is in leaf on-die termination.Also, oil supply tank is, when blade in cylinder chamber at utmost protrude when the 2nd end be located at cylinder chamber in, and by the 2nd end part with tend to the 2nd end face and groove depth shoals.
Description
Technical field
Embodiments of the present invention are related to rotary compressor and freezing cycle device.
Background technology
It is used as the rotary compressor used in the freezing cycle device of conditioner etc., it is known to possess tubular
Cylinder, block cylinder opening portion blocking plate, eccentric rotary is carried out in the cylinder chamber formed by cylinder and blocking plate
Roller structure.In addition, discharge chambe and suction chamber will be divided into by being equipped with the blade groove for be formed at cylinder in cylinder chamber
Blade.Blade is connected to roller, and advance and retreat movement is carried out along with the eccentric rotary of roller in cylinder chamber.
However, above-mentioned blade is folded with the state of lubricating oil relative to blocking plate preferably between blade and blocking plate
Slide.Thus, it is believed that the abrasion between blade and blocking plate can be reduced, and be able to ensure that close between blade and blocking plate
Feng Xing.
But, in above-mentioned rotary compressor, between blade and blocking plate the desired amount of lubricating oil of sandwiched this
Room for improvement is remained on a bit.Specifically, because in discharge chambe with the differential pressure in suction chamber to the side of blade (towards roller
Direction of rotation face) apply load.Especially in blade from lower dead center (in cylinder chamber at utmost prominent state) court
Operation range (hereinafter referred to as compression travel second half section of top dead centre (state at utmost retreated from cylinder chamber) transformation.) in,
Pressure in discharge chambe rises big.Thus, in the compression travel second half section, the load for putting on the side of blade is big.Therefore, in leaf
Substantial amounts of lubricating oil is needed between piece and blocking plate.In this case it is assumed that lubrication shortage of oil between blade and blocking plate and it is oily
Film is broken, then the abrasion increase between blade and blocking plate.As a result, there is Reliability of Microprocessor reduction.If in addition,
Sealing reduction between blade and blocking plate, refrigerant leakage etc. occurs between discharge chambe and suction chamber, then there is compression
The possibility of performance reduction.
On the other hand, operation range (the hereinafter referred to as compression travel first half changed in blade from top dead centre towards lower dead center
Section.) in, the pressure compared with the compression travel second half section in discharge chambe rises small.Thus, in compression travel front half section, put on
The load of the side of blade is smaller.Therefore, lubricating oil required between blade and blocking plate is few.
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 4-191491 publications
The content of the invention
Invent problem to be solved
Problem to be solved by this invention is the rotation for providing the raising that can realize Reliability of Microprocessor and compression performance
Rotary compressor and freezing cycle device.
Means for solving the problems
The rotary compressor of embodiment has container, cylinder, blocking plate, roller, blade and oil supply tank.Container
Lubricating oil.Cylinder is the tubular being accommodated in container.Blocking plate blocks the opening portion of cylinder, and cylinder chamber is formed together with cylinder.
Roller eccentric rotary in cylinder chamber.Blade on the direction of rotation of roller in parting-off cylinder room, and can along with roller bias
Rotate and retreated in cylinder chamber.Oil supply tank is formed at the opposed faces opposed with blocking plate in blade, along moving for blade
Direction extends, also, the 1st end, with being connected in container, the 2nd end is in leaf on-die termination.Also, oil supply tank is, when blade exists
The 2nd end is located in cylinder chamber when at utmost being protruded in cylinder chamber, and leans on the part of the 2nd end with the 2nd end face of trend
Groove depth shoals.
Brief description of the drawings
Fig. 1 is the summary knot of the freezing cycle device including the sectional view of the rotary compressor of the 1st embodiment
Composition.
Fig. 2 is the sectional view of the compression mechanical part along Fig. 1 II-II lines.
Fig. 3 is the sketch structure figure of the groove forming apparatus for the blade for showing the 1st embodiment.
Fig. 4 is the side view of the blade of the 2nd embodiment.
Fig. 5 is the sketch structure figure of the groove forming apparatus for the blade for showing the 2nd embodiment.
Fig. 6 is the side view of the blade of the 3rd embodiment.
Fig. 7 is the sketch structure figure of the groove forming apparatus for the blade for showing the 3rd embodiment.
Embodiment
Hereinafter, the rotary compressor and freezing cycle device of embodiment are illustrated referring to the drawings.
(the 1st embodiment)
First, freezing cycle device is briefly described.
As shown in figure 1, the freezing cycle device 1 of present embodiment possesses rotary compressor 2 and rotary compressor 2
The condenser 3 of connection, the expansion gear 4 being connected with condenser 3 and it is connected between expansion gear 4 and rotary compressor 2
Evaporator 5.
Rotary compressor 2 is so-called helicoid compressor.2 pairs of rotary compressor is taken into the gas of the low pressure of inside
Cryogen is compressed and makes high temperature and the gas refrigerant of high pressure.In addition, for the specific of rotary compressor 2
Structure will be aftermentioned.
The high temperature and the gas refrigerant of high pressure that condenser 3 is sent into from self-rotation compressor 2 release heat, make high temperature and height
The gas refrigerant of pressure turns into the liquid refrigerant of high pressure.
Expansion gear 4 reduces the pressure of the liquid refrigerant for the high pressure sent into from condenser 3, makes the liquid refrigerant of high pressure
Liquid refrigerant as low temperature and low pressure.
Evaporator 5 makes the liquid refrigerant gasification for the low temperature and low pressure sent into from expansion gear 4, makes low temperature and the liquid of low pressure
Cryogen turns into the gas refrigerant of low pressure.Also, in evaporator 5, the liquid refrigerant of low pressure is when gasification from surrounding
Capture heat of gasification, surrounding is cooled.In addition, being taken into by the gas refrigerant of the low pressure after evaporator 5 above-mentioned rotary
In compressor 2.
So, in the freezing cycle device 1 of present embodiment, gas is turned to as refrigerant one side phase transformation of working fluid
Cryogen is with liquid refrigerant while circulation.
Then, above-mentioned rotary compressor 2 is illustrated.
The rotary compressor 2 of present embodiment possesses compressor main body 11 and accumulator 12.
Accumulator 12 is so-called gas-liquid separator.Accumulator 12 is arranged at above-mentioned evaporator 5 and compressor main body 11
Between.Accumulator 12 is connected by suction line 21 with the cylinder described later 41 of compressor main body 11.Accumulator 12 only will be by evaporating
Device 5 gasify after gas refrigerant and gas refrigerant in the liquid refrigerant that is not gasified by evaporator 5 towards compression owner
Body 11 is supplied.
Compressor main body 11 possesses rotary shaft 31, motor part 32, compression mechanical part 33 and closed container (container) 34.
Motor part 32 rotates rotary shaft 31.Compression mechanical part 33 is along with the rotation of rotary shaft 31 to gas refrigeration
Agent is compressed.Closed container 34 stores rotary shaft 31, motor part 32 and compression mechanical part 33.In addition, closed container 34
Be formed as tubular.Lubricating oil J is contained in the inside of closed container 34.A part for compression mechanical part 33 is immersed in lubricating oil J
It is interior.
Closed container 34 and rotary shaft 31 are configured on coaxial along axes O.In addition, in the following description, by edge
The direction for axes O is referred to as axial direction, the side in axial direction by motor part 32 is referred to as into upside, by by compression mechanical part 33
Side is referred to as downside.In addition, direction orthogonal to the axial direction is referred to as radially, the direction that will be around axes O is referred to as circumference.
Motor part 32 is the DC brushless motors of so-called inner-rotor type.Specifically, motor part 32 possesses tubular
Stator 35 and be configured at stator 35 inner side columned rotor 36.
Stator 35 is fixed on the internal face of closed container 34 by hot jacket etc..Rotor 36 is fixed on the top of rotary shaft 31.
Rotor 36 is diametrically configured at the inner side of stator 35 at spaced intervals.
Compression mechanical part 33 possesses the cylinder 41 of tubular, the base bearing in the both ends open portion for blocking cylinder 41 respectively and (blocked
Plate) 42 and supplementary bearing (blocking plate) 43.
Rotary shaft 31 is run through in cylinder 41.Base bearing 42 and supplementary bearing 43 support rotary shaft 31 to rotate.
The space formed by cylinder 41, base bearing 42 and supplementary bearing 43 constitutes cylinder chamber 46 (reference picture 2).By the gas-liquid point of accumulator 12
Gas refrigerant from after is taken into cylinder chamber 46 by above-mentioned suction line 21.
In above-mentioned rotary shaft 31 be located at cylinder chamber 46 in be formed in part with it is diametrically eccentric relative to axes O
Eccentric part 51.
Roller 53 is embedded with outside eccentric part 51.Roller 53 is configured to the rotation along with rotary shaft 31, outer peripheral face and cylinder
While 41 inner peripheral surface sliding contact, relative to axes O eccentric rotary.
As shown in Figure 1 and Figure 2, the blade groove 54 for the outside depression being radially oriented is formed with cylinder 41.Blade groove 54 times
And the axial of cylinder 41 is integrally formed.Blade groove 54 is connected in the outboard end (rearward end) of radial direction with closed container 34.
The blade 55 that can be moved along radially sliding is provided with blade groove 54.Blade 55 (is applied by forcing unit 57
Power apparatus) be radially oriented inner side force.The inner side end (hereinafter referred to as front end face (the 2nd end face)) of the radial direction of blade 55 exists
The outer peripheral face of roller 53 is connected in cylinder chamber 46.Thus, blade 55 is configured to spinning movement with roller 53 correspondingly in gas
Retreated in cylinder chamber 46.In addition, in the top view from end on observation, the inner side that the front end face of blade 55 is formed towards radial direction is convex
The arc-shaped gone out.In addition, will be aftermentioned for the concrete structure of blade 55.
Cylinder chamber 46 divides (segmentation) into suction chamber and discharge chambe by roller 53 and blade 55.Also, in compression mechanical part
In 33, by the spinning movement and the moving back and forth of blade 55 of roller 53, action is compressed in cylinder chamber 46.
In cylinder 41, in the inboard positioned at blade groove 54 along the direction of rotation of roller 53 (arrow in reference picture 2)
(in Fig. 2's, the left side of blade groove 54) is formed in part with inlet hole 56.Inlet hole 56 is along radial direction insertion cylinder 41.In suction
The outboard end of the radial direction in hole 56 is connected with above-mentioned suction line 21 (reference picture 1).On the other hand, the radial direction of inlet hole 56 is interior
Side end is in the inner opening of cylinder chamber 46.
In the inner peripheral surface of cylinder 41, the direction of rotation along roller 53 positioned at blade groove 54 nearby side (in Fig. 2, leaf
The right side of film trap 54) be formed in part with discharge groove 58.Discharge groove 58 is connected with tap 64 described later.Groove 58 is discharged from axle
Be formed as semi-circular shape into the top view of observation.
As shown in figure 1, base bearing 42 blocks the upper end opening portion of cylinder 41, and gas is compared into being located in rotary shaft 31
The part supporting of cylinder 41 by the top is to rotate.Specifically, base bearing 42 possess for rotary shaft 31 insert cylinder portion 61, with
And the flange part 62 for the setting protruding outside being radially oriented from the bottom in cylinder portion 61.Flange part 62 blocks cylinder chamber from top
46。
Above-mentioned discharge groove 58 is formed through in a circumferential part for flange part 62 and will be connected inside and outside cylinder chamber 46
Tap 64 (reference picture 2).The axially insertion flange part 62 of tap 64.In addition, being equipped with flange part 62 not shown
Discharge valve system, the discharge valve system along with cylinder chamber 46 (discharge chambe) pressure rise and be opened and closed tap 64, court
The outer discharging refrigerant of cylinder chamber 46.
The muffler 65 for covering from above base bearing 42 is provided with base bearing 42.Being formed with muffler 65 to disappear
The intercommunicating pore 66 of the inside and outside connection of sound device 65.The high temperature and the gas refrigerant of high pressure discharged by above-mentioned tap 64 pass through
Intercommunicating pore 66 is discharged towards closed container 34 is interior.
Supplementary bearing 43 blocks the lower end opening portion of cylinder 41, and being located in rotary shaft 31 is compared into cylinder 41 on the lower
Part supporting can to rotate.Specifically, supplementary bearing 43 possesses the cylinder portion 71 that is inserted for rotary shaft 31 and from cylinder portion 71
The flange part 72 of setting protruding outside that is radially oriented of upper end.Flange part 72 blocks cylinder chamber 46 from below.
Above-mentioned blade 55 is formed as the rectangular shape radially extended.In blade 55 and the internal face of blade groove 54
And it is folded with lubricating oil J between the flange part 62,72 of each bearing 42,43.Therefore, the side of the circumferential both sides of direction in blade 55
Face can via oil film relative to blade groove 54 internal face slide.In addition, the upper surface of blade 55 can be relative via oil film
Slided in the lower surface of flange part 62.The lower surface of blade 55 can be via oil film relative to flange part 72 upper surface slide.
In the upper and lower end face (with the opposed opposed faces of flange part 62,72) of blade 55, in the width of blade 55
Centre portion radially extends the oil supply tank 81 being provided with towards the inner side depression of axial direction.Oil supply tank 81 is in the top view from end on observation
In be formed as along radially (moving direction of blade 55) extension it is linear.The width of oil supply tank 81 is throughout being integrally formed into phase
Together.Specifically, oil supply tank 81 have positioned at radial direction outboard end (the 1st end) side rectilinear extension 82 and with it is straight
The connected rake 83 of the medial end (the 2nd end) of the radial direction of line extension 82.The groove depth of rectilinear extension 82 is throughout entirety
Be formed as identical.With the front end face for tending to blade 55, groove depth gradually becomes shallower as rake 83.
Rear end face upper shed of 1st end of rectilinear extension 82 in blade 55.1st end of rectilinear extension 82 passes through
Blade groove 54 in closed container 34 with connecting.Lubricating oil J in closed container 34 is stored in by blade groove 54 towards oil supply tank 81
Interior supply.
The bottom of rake 83 is formed towards the arc-shaped of axial inner side protrusion in the side view from circumferential.
The radius of curvature of rake 83 is R.2nd end of rake 83 is in the state of the front end face close to blade 55 in blade 55
Terminate.That is, oil supply tank 81 does not reach the front end face of blade 55, not with being connected in cylinder chamber 46.
In addition, oil supply tank 81 is formed as being located in cylinder chamber 46 when blade 55 is at utmost protruded in cylinder chamber 46.
Wrapped as by the tripartite in addition to the outside of radial direction part beyond the upper and lower end face of blade 55, oil supply tank 81
Enclose the sealing surface function of oil supply tank 81.The sealing surface of blade 55 is opposed with the difference of flange part 62,72 across oil film.In the feelings
Under condition, by the connection between in the discharge chambe between the sealing surface and flange part 62,72 of blade 55 and in suction chamber by oil film
Cut-off.In the present embodiment, the width S 1 of the part for being located at circumferential both sides relative to oil supply tank 81 in sealing surface, S2,
And the width S 3 along radial direction between another ora terminalis of oil supply tank 81 and the front end face of blade 55 be respectively formed as it is equal.
Herein, the capacity of the volume of oil supply tank 81 and the lubricating oil J needed for the compression travel second half section is matchingly set.And
And, the maximum groove depth E (being in the present embodiment the depth of rectilinear extension 82) of oil supply tank 81 is deeper than H.In addition, oil supply tank 81
Width H it is smaller than the minimum widith of sealing surface.
Then, the method that oil supply tank 81 is formed on above-mentioned blade 55 is illustrated.In the present embodiment, pass through
The machining formation oil supply tank 81 of discoideus cutter 91,92 is used.
Groove forming apparatus 90 shown in Fig. 3 have can around the rotary shaft rotation being parallel to each other a pair of cutters 91,92,
And the conveying mechanism (not shown) of conveying blade 55.
Cutter 91,92 is respectively formed as identical structure.Cutter 91,92 to separate than blade 55 therebetween
The mode in highly small gap is arranged.In addition, in the present embodiment, the gap between cutter 91,92 is set as blade 55
Height and each oil supply tank 81 maximum groove depth E difference.
Conveying mechanism makes blade 55 relative to the gap advance and retreat movement between each cutter 91,92.Specifically, conveyer
The Working position and blade 55 that structure enters between cutter 91,92 in blade 55 keep out of the way position from what is kept out of the way between cutter 91,92
Moved between putting.
In the case where using the above-mentioned formation oil supply tank 81 of groove forming apparatus 90, first, using positioned at retreating position
Conveying mechanism keeps blade 55, and cutter 91,92 and blade 55 are aligned.Then, the mutually opposing rotation of cutter 91,92 is made,
Blade 55 is conveyed from the 1st end towards Working position using conveying mechanism.Then, cutter 91,92 is entered along with blade 55
Between gap, the upper and lower end face of blade 55 is cut.
Also, after blade 55 is entered scheduled volume, conveying mechanism is moved to retreating position again, make blade 55 from cutting
Disconnected device 91,92 is kept out of the way.Now, the inlet of blade 55 is set to the journey that cutter 91,92 does not reach the front end face of blade 55
Degree.Thus, the rake 83 of the arc-shaped for the radius of curvature for copying cutter 91,92 is formed in the leading section of blade 55.
In accordance with the above, the blade 55 of present embodiment is completed.
According to the structure, only by making relative to a pair of cutters of blade 55 91,92 retreat movement, it becomes possible in blade 55
Upper and lower end face formed oil supply tank 81.In this case, for example compared with the Milling Process for having used slotting cutter, use can be shortened
During the processing of oil supply tank 81 is formed.As a result, it is possible to realize raising and the cost degradation of manufacture efficiency.
Then, the effect to above-mentioned rotary compressor 2 is illustrated.
As shown in figure 1, during 35 supply electric power of stator of present dynasty's motor part 32, rotary shaft 31 is together with rotor 36 around axis
O rotates.Also, along with the rotation of rotary shaft 31, eccentric part 51 and roller 53 eccentric rotary in cylinder chamber 46.Now, roller
53 inner peripheral surface sliding contact respectively with cylinder 41, from there through suction line 21 towards being taken into gas refrigerant in cylinder chamber 46, and
And the gas refrigerant being taken into cylinder chamber 46 is compressed.
Specifically, gas refrigerant is inhaled into the suction chamber in cylinder chamber 46 by inlet hole 56, also, in compression
First the gas refrigerant sucked from inlet hole 56 is compressed in room.Gas refrigerant after compression is passed through into base bearing 42
Tap 64 is discharged towards the outside (in muffler 65) of cylinder chamber 46, afterwards by the intercommunicating pore 66 of muffler 65 towards closed container
Discharged in 34.In addition, the gas refrigerant that will drain in closed container 34 sends into condenser 3 as described above.
Herein, connect, therefore filled by lubricating oil J by the way that blade groove 54 and closed container 34 are interior in the oil supply tank 81 of blade 55
It is full.Lubricating oil J in oil supply tank 81 is flowed between sealing surface and each flange part 62,72, forms oil film between the two.Thus, leaf
Piece 55 is in the state of the direct contact with flange part 62,72 is inhibited, along with the eccentric rotary of roller 53 relative to cylinder
Retreat and move along radial direction in room 46.
During blade 55 retreats movement, in the lubricating oil J being located between blade 55 and flange part 62,72
In, produce speed difference between the part by the part of blade 55 and by flange part 62,72., can be right if producing speed difference
Lubricating oil J effects are along with sticky shearing force.It is particularly due to form rake 83 in the 2nd end of oil supply tank 81, so
In compression travel second half section, with the rear for the moving direction for tending to blade 55, the gap between blade 55 and flange part 62,72
Narrow.Therefore, by lubricating oil J viscous effect and rake 83 inclination, lubricating oil J in oil supply tank 81 is by towards radial direction
Inner side pulls in and (produces so-called chock effect).Thus, lubricating oil J is between the upper and lower end face of blade 55 and flange part 62,72
Enter to the front end surface side of blade 55.Thereby, it is possible to effectively supply lubricating oil J towards between blade 55 and flange part 62,72.
On the other hand, because the 1st end of oil supply tank 81 is opened by rectilinear extension 82, therefore in compression travel first half
Section is difficult to produce above-mentioned chock effect.Therefore, in compression travel front half section, compared with the compression travel second half section, lubricating oil J is difficult
To be flowed towards the inner side of radial direction.Thereby, it is possible to which in compression travel front half section, the lubricating oil J suppressed in oil supply tank 81 is largely flowed into
The front end surface side of blade 55.
So, in the present embodiment, due to forming rake 83 in the other end of oil supply tank 81, so in compressed line
The journey second half section easily produces chock effect.Therefore, between blade 55 (sealing surface) and flange part 62,72, lubricating oil J is towards forward
End face side is effectively supplied.Therefore, it is possible to suppress the oil film breakage between blade 55 and flange part 62,72, and it can suppress
Blade 55 is directly contacted with flange part 62,72.Thereby, it is possible to reduce the abrasion of blade 55 and flange part 62,72, it is possible to increase dynamic
Make reliability.
Further, since oil supply tank 81 is formed as being located at cylinder chamber 46 when blade 55 is at utmost protruded in cylinder chamber 46
It is interior, so being separated by the connection in the discharge chambe between blade 55 and flange part 62,72 and in suction chamber by oil film.Cause
This, it can be ensured that the sealing between blade 55 and flange part 62,72.Therefore, it is possible to suppress by blade 55 and flange
The leakage of discharge chambe between portion 62,72 and the refrigerant between suction chamber, can realize the raising of compression performance.
And then, as described above, the 1st end of oil supply tank 81 is opened by rectilinear extension 82, therefore, before compression travel
Half section, the forward end face side that can suppress lubricating oil J towards blade 55 is largely flowed into.Therefore, in compression travel front half section, it can press down
System superfluous sandwiched lubricating oil J between blade 55 and flange part 62,72, is able to maintain that between blade 55 and flange part 62,72
Sealing.Thereby, it is possible to suppress to be located in the superfluous lubricating oil J inflows cylinder chamber between blade 55 and flange part 62,72
In 46, or suppression refrigerant is flowed into together with lubricating oil J in cylinder chamber 46, can suppress the reduction of compression performance.
Moreover, in the present embodiment, because the maximum groove depth E of oil supply tank 81 is deeper than width H, so being able to ensure that fuel feeding
Volume in groove 81, and it is able to ensure that the width of sealing surface.It is accordingly possible to ensure the capacity of the lubricating oil J in oil supply tank 81, and
It is able to ensure that the sealing between blade 55 and flange part 62,72.Thereby, it is possible to realize Reliability of Microprocessor and compression performance
Further raising.
In addition, in the present embodiment, because the width H of oil supply tank 81 is smaller than the minimum widith of sealing surface, so can
Ensure the width of sealing surface.In this case, no matter gap caused by business poor between blade 55 and flange part 62,72
Deviation how, the sealing (so-called robustness can be improved) between blade 55 and flange part 62,72 can be ensured.
As a result, it is possible to realize the further raising of Reliability of Microprocessor and compression performance.
Also, in the freezing cycle device 1 of present embodiment, the rotary compressor 2 above-mentioned due to possessing, so energy
High-performance and freezing cycle device 1 of excellent in reliability are enough provided.
(the 2nd embodiment)
In the blade 155 shown in Fig. 4, the bottom of oil supply tank 181 is formed as convex throughout the inner side integrally towards axial direction
The arc-shaped gone out.Thus, with the both sides for tending to the 1st end and the 2nd end, groove depth gradually becomes shallower as oil supply tank 181.Fuel feeding
Rear end face upper shed of 1st end of groove 181 in blade 155.2nd end of oil supply tank 181 is terminated in blade 155.
As shown in figure 5, in the groove forming apparatus 190 of present embodiment, a pair of cutters 191,192 are configured to phase
Mutually close or separation.Specifically, blade 155 of the cutter 191,192 between cutter 191,192 is pointed to is processed
Working position, move between the retreating position that is separated with from the blade 155 between cutter 191,192.
Conveying mechanism makes blade 155 lead to successively from upstream towards downstream by the gap between a pair of cutters 191,192
Cross.
In order that with the above-mentioned formation oil supply tank 81 of groove forming apparatus 190, first, being moved back being located at cutter 191,192
Keep away in the state of position, blade 155 is delivered between cutter 191,192 using conveying mechanism.Then, make cutter 191,
192 mutually opposing rotations, and cutter 191,192 is moved towards Working position.Then, cutter 191,192 enters leaf
The upper and lower end face of piece 155, cuts the upper and lower end face of blade 155.Now, by the entering to blade 155 of cutter 191,192
Enter the maximum groove depth E that amount is set as each oil supply tank 181.Thus, oil supply tank 181 is formed as copying the curvature of cutter 191,192
The arc-shaped of radius.
Afterwards, cutter 191,192 is moved again towards retreating position, cutter 191,192 is separated from blade 155.
Then, drive conveying mechanism, by the blade 155 after processing relative to cutter 191,192 towards downstream transport, and using as
The blade 155 of next processing object is delivered between cutter 191,192 successively.Afterwards, by same as the above-mentioned method
Method to being delivered to cutter 191,192 between blade 155 carry out machining.Thus, relative to being delivered to cutter
191st, the blade 155 between 192 sequentially forms oil supply tank 181.
According to the structure, due to the arc-shaped for being integrally formed into the inner side protrusion towards axial direction of oil supply tank 181, so energy
Enough by making cutter 191,192 be moved back and forth relative to the blade 155 conveyed in one direction, oil supply tank 181 is formed.By
This, can realize raising and the cost degradation of further manufacture efficiency.
(the 3rd embodiment)
In the blade 255 shown in Fig. 6, the bottom of oil supply tank 281 is with from the 1st end the 2nd end of trend towards axial direction
Outside be linearly extended.End face upper shed of 1st end of oil supply tank 281 in blade 255.Oil supply tank 281
2nd end is terminated in blade 255.
As shown in fig. 7, in the groove forming apparatus 290 of present embodiment, cutter 291 is supported to rotate.
Conveying mechanism 292 conveys blade 255 relative to cutter 291 from upstream towards downstream.Conveying mechanism 292 is relative
Blade 255 is kept in the state of conveying direction inclination.Specifically, conveying mechanism 292 is by the 1st end face court of blade 255
Downstream and the end face of a side is set to keep blade 255 in the state of being tilted (towards the direction of cutter 291) upward.
In order that with the above-mentioned formation oil supply tank 281 of groove forming apparatus 290, it is sharp in the state of cutter 291 is rotated
With conveying mechanism 292 by blade 255 towards downstream transport.Then, cutter 291 enters blade from the 1st end of blade 255
The end face of 255 side.Then, blade 255 is made to pass through relative to cutter 291 towards downstream, thus relative to the one of blade 255
The end face formation oil supply tank 281 of side.In addition, when the blade 255 after processing is by cutter 291, next processing will be used as
The blade 255 of object is delivered to cutter 291 successively.Also, it is next to being used as by method same as the above-mentioned method
The blade 255 of processing object carries out machining.Thus, relative to the blade 255 conveyed towards cutter 291 a side end
Face sequentially forms oil supply tank 281.
Then, the blade 255 that the end face made in a side forms oil supply tank 281 is spun upside down, by with above-mentioned method
End face formation oil supply tank 281 of the identical method relative to the opposing party.Thus, the blade 255 of above-mentioned present embodiment is completed.
According to the structure, blade 255 is set just to form oil supply tank 281, institute by a cutter 291 due to only relying on
So that simplification and the cost degradation of groove forming apparatus 290 can be realized.In addition, blade 255 is conveyed while by cutter 291
It is processed, therefore the conveying of blade 255 will not be stopped.Therefore, it is possible to realize the further shortening during processing.
In addition, in the above-described embodiment, to using base bearing 42 and the situation of supplementary bearing 43 to enter as blocking plate
Go explanation, but be not limited to this.For example, the upper end opening portion for blocking cylinder 41 can also be used as blocking plate and for revolving
Bearing portion and block the lower end opening portion of cylinder 41 and be by the axial lower end surface bearing of rotary shaft 31 that rotating shaft 31 is inserted
The air cylinder board that can be slided.
In addition, in the above-described embodiment, cylinder chamber 46 is illustrated for the structure of one, but is not limited to
This, can also set multiple cylinder chamber 46.
In addition, in the above-described embodiment, the situation for making axial direction consistent with above-below direction is illustrated, but not
This is defined in, axial direction can also be made consistent with horizontal direction.
And then, in the above-described embodiment, the situation that roller 53 is formed with blade split is illustrated, but not
This is defined in, roller 53 and blade can also be integrally formed.
In addition, in the above-described embodiment, being carried out to the situation for forming oil supply tank respectively in the upper and lower end face of blade
Illustrate, but be not limited to the structure of this or the end face formation oil supply tank at least one party.
And then, in the above-described embodiment, the situation to the end face 1 row oil supply tank of formation relative to blade is said
It is bright, but this is not limited to, multiple row oil supply tank can also be formed.
In addition, in the above-described embodiment, arc-shaped is formed as or linear situation to the 2nd end of oil supply tank
It is illustrated, but is not limited to this.As long as the structure gradually become shallower as with the front end face for tending to blade, for example, also may be used
To be stepped.As long as in addition, (the 2nd end is leaned in the center section compared to bearing of trend of oil supply tank for oil supply tank at least the 2nd end
Part) shoal towards the 2nd end.
In addition, in the above-described embodiment, in the top view from end on observation oil supply tank be formed as along blade
The linear situation of moving direction (radial direction) extension be illustrated, but be not limited to this.As long as example, along blade
Moving direction extension, oil supply tank can for example be formed as waveform or relative to moving direction tilt.
In addition, in the above-described embodiment, being carried out to the width of oil supply tank throughout identical structure is integrally formed into
Explanation, but it is also possible to the width of appropriately designed change oil supply tank.In such a situation it is preferred that the minimum widith of sealing surface compares oil supply tank
Breadth Maximum it is small.
At least one embodiment from the description above, because oil supply tank becomes with the 2nd end is tended to from the 1st end
It is shallow, so easily producing chock effect in the compression travel second half section.Therefore, between blade and blocking plate, towards by the 2nd end face side
Effectively supply lubricating oil.
Therefore, it is possible to suppress the oil film breakage between blade and blocking plate, and blade can be suppressed directly to connect with blocking plate
Touch.Thereby, it is possible to reduce the abrasion of blade and blocking plate.As a result, it is possible to improve Reliability of Microprocessor.
Further, since separated by the connection in the discharge chambe between blade and blocking plate and in suction chamber by oil film,
So being able to ensure that the sealing between blade and blocking plate.Therefore, it is possible to suppress by the compression between blade and blocking plate
The leakage of refrigerant between room and suction chamber, realizes the raising of compression performance.
And then, because the other end of oil supply tank in closed container with connecting, so can press down in compression travel front half section
Lubricating oil processed is largely flowed into towards roller by the 2nd end face side.Therefore, in compression travel front half section, blade and blocking plate can be suppressed
Between superfluous ground sandwiched lubricating oil, and maintain the sealing between blade and blocking plate.Thereby, it is possible to suppress to be located in blade with
Superfluous lubricating oil between blocking plate is flowed into cylinder chamber, or suppression refrigerant is flowed into cylinder chamber together with lubricating oil, energy
Enough suppress the reduction of compression performance.
Several embodiments of the invention is illustrated, but these embodiments are shown as an example, and unexpectedly
Taste to be defined to the scope of invention.These embodiments can be carried out in other various modes, not depart from hair
Various omissions, displacement, change can be carried out in the range of bright purport.These embodiments and its deformation are contained in the model of invention
Enclose and purport in, and be contained in the invention described in claims and the scope being equal with it.
Claims (6)
1. a kind of rotary compressor, possesses：
Container, lubrication oil；
The cylinder of tubular, is accommodated in said vesse；
Blocking plate, blocks the opening portion of above-mentioned cylinder, cylinder chamber is formed together with above-mentioned cylinder；
Roller, the eccentric rotary in above-mentioned cylinder chamber；
Blade, splits on the direction of rotation of above-mentioned roller in above-mentioned cylinder chamber, and can along with above-mentioned roller eccentric rotary
And retreated in above-mentioned cylinder chamber；And
Oil supply tank, is formed at the opposed faces opposed with above-mentioned blocking plate in above-mentioned blade, along the moving direction of above-mentioned blade
Extension, also, the 1st end and said vesse are interior connects, the 2nd end in above-mentioned leaf on-die termination,
Above-mentioned oil supply tank is that above-mentioned 2nd end is located at above-mentioned gas when above-mentioned blade is at utmost protruded in above-mentioned cylinder chamber
In cylinder chamber, also, by above-mentioned 2nd end part with tend to the 2nd end face and groove depth shoals.
2. rotary compressor as claimed in claim 1, wherein,
Above-mentioned oil supply tank is in the arc-shaped that groove depth gradually becomes shallower as with trend above-mentioned 2nd end face.
3. rotary compressor as claimed in claim 1, wherein,
Above-mentioned oil supply tank is in tending to above-mentioned 2nd end from above-mentioned 1st end and that groove depth gradually becomes shallower as is linear.
4. rotary compressor as claimed any one in claims 1 to 3, wherein,
The maximum groove depth of above-mentioned oil supply tank is deeper than the width of above-mentioned oil supply tank.
5. the rotary compressor as any one of Claims 1-4, wherein,
In the above-mentioned opposed faces of above-mentioned blade, width of the minimum widith than above-mentioned oil supply tank of the part beyond above-mentioned oil supply tank
It is wide.
6. a kind of freezing cycle device, possesses：
Rotary compressor any one of claim 1 to 5；
Condenser, is connected with above-mentioned rotary compressor；
Expansion gear, is connected with above-mentioned condenser；And
Evaporator, is connected between above-mentioned expansion gear and above-mentioned rotary compressor.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-044695 | 2015-03-06 | ||
| JP2015044695 | 2015-03-06 | ||
| PCT/JP2015/077508 WO2016143177A1 (en) | 2015-03-06 | 2015-09-29 | Rotary compressor and refrigeration cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107076148A true CN107076148A (en) | 2017-08-18 |
| CN107076148B CN107076148B (en) | 2020-06-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580057254.XA Active CN107076148B (en) | 2015-03-06 | 2015-09-29 | Rotary compressor and refrigeration cycle device |
Country Status (3)
| Country | Link |
|---|---|
| JP (2) | JPWO2016143177A1 (en) |
| CN (1) | CN107076148B (en) |
| WO (1) | WO2016143177A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01227890A (en) * | 1988-03-04 | 1989-09-12 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH04191491A (en) * | 1990-11-22 | 1992-07-09 | Matsushita Refrig Co Ltd | Closed type compressor |
| JPH08159071A (en) * | 1994-12-02 | 1996-06-18 | Matsushita Refrig Co Ltd | Rotary compressor |
| JP2006258001A (en) * | 2005-03-17 | 2006-09-28 | Toshiba Kyaria Kk | Hermetic compressor and refrigeration cycle device using the same |
| CN203374488U (en) * | 2013-07-12 | 2014-01-01 | 广东美芝制冷设备有限公司 | Sliding vane of compressor |
| JP2014077415A (en) * | 2012-10-11 | 2014-05-01 | Toshiba Carrier Corp | Hermetic type compressor and refrigeration cycle device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6143597B2 (en) * | 2013-07-31 | 2017-06-07 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Rotary compressor |
-
2015
- 2015-09-29 CN CN201580057254.XA patent/CN107076148B/en active Active
- 2015-09-29 JP JP2017504556A patent/JPWO2016143177A1/en active Pending
- 2015-09-29 WO PCT/JP2015/077508 patent/WO2016143177A1/en active Application Filing
-
2018
- 2018-11-06 JP JP2018208558A patent/JP6652623B2/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01227890A (en) * | 1988-03-04 | 1989-09-12 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH04191491A (en) * | 1990-11-22 | 1992-07-09 | Matsushita Refrig Co Ltd | Closed type compressor |
| JPH08159071A (en) * | 1994-12-02 | 1996-06-18 | Matsushita Refrig Co Ltd | Rotary compressor |
| JP2006258001A (en) * | 2005-03-17 | 2006-09-28 | Toshiba Kyaria Kk | Hermetic compressor and refrigeration cycle device using the same |
| JP2014077415A (en) * | 2012-10-11 | 2014-05-01 | Toshiba Carrier Corp | Hermetic type compressor and refrigeration cycle device |
| CN203374488U (en) * | 2013-07-12 | 2014-01-01 | 广东美芝制冷设备有限公司 | Sliding vane of compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107076148B (en) | 2020-06-16 |
| WO2016143177A1 (en) | 2016-09-15 |
| JP6652623B2 (en) | 2020-02-26 |
| JP2019049267A (en) | 2019-03-28 |
| JPWO2016143177A1 (en) | 2017-08-03 |
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