CN1431403A - Enclosed rotary compressor and freezing air conditioning unit - Google Patents
Enclosed rotary compressor and freezing air conditioning unit Download PDFInfo
- Publication number
- CN1431403A CN1431403A CN 03101634 CN03101634A CN1431403A CN 1431403 A CN1431403 A CN 1431403A CN 03101634 CN03101634 CN 03101634 CN 03101634 A CN03101634 A CN 03101634A CN 1431403 A CN1431403 A CN 1431403A
- Authority
- CN
- China
- Prior art keywords
- fuel feeding
- cylinder barrel
- oil
- chamber
- pump chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000007710 freezing Methods 0.000 title abstract description 8
- 230000008014 freezing Effects 0.000 title abstract description 8
- 238000004378 air conditioning Methods 0.000 title abstract 2
- 239000003921 oil Substances 0.000 claims abstract description 64
- 238000007906 compression Methods 0.000 claims abstract description 19
- 230000006835 compression Effects 0.000 claims abstract description 18
- 239000000446 fuel Substances 0.000 claims description 97
- 239000000314 lubricant Substances 0.000 claims description 24
- 238000005057 refrigeration Methods 0.000 claims description 24
- 239000003795 chemical substances by application Substances 0.000 claims description 22
- 230000005520 electrodynamics Effects 0.000 claims description 11
- 239000012530 fluid Substances 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 claims description 11
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 claims description 8
- 239000006200 vaporizer Substances 0.000 claims description 6
- 239000004215 Carbon black (E152) Substances 0.000 claims description 4
- 229910021529 ammonia Inorganic materials 0.000 claims description 4
- 229930195733 hydrocarbon Natural products 0.000 claims description 4
- 150000002430 hydrocarbons Chemical class 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 claims description 4
- 238000001816 cooling Methods 0.000 claims description 2
- 238000005461 lubrication Methods 0.000 abstract description 4
- 239000010687 lubricating oil Substances 0.000 abstract description 2
- 230000001050 lubricating effect Effects 0.000 abstract 2
- 230000002950 deficient Effects 0.000 abstract 1
- 238000000638 solvent extraction Methods 0.000 abstract 1
- 230000007423 decrease Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 239000011148 porous material Substances 0.000 description 6
- 238000003825 pressing Methods 0.000 description 6
- 238000007789 sealing Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000005755 formation reaction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
An enclosed rotary compressor and freezing air conditioning unit. A closed rotary compressor can increase a reliability by preventing defective lubrication due to shortage of the oil amount supplied to the sliding parts of a compression mechanism. The compression mechanism and a lubricating mechanism are stored in a closed container 6 having lubricating oil 16 stored therein. The compression mechanism comprises a roller part 81a revolving in a cylinder chamber 51a and a vane part 81b partitioning the cylinder chamber 51a. The lubricating mechanism comprises an oil supply pump chamber 51c formed on the outside of the cylinder chamber 51a and the tip part of the vane part 81b reciprocating in the oil supply pump chamber 51c. The tip part of the vane part 81b is formed so that the oil supply pump chamber 51c is made wider toward a supply oil flow direction.
Description
Technical field
The present invention relates to a kind of closed rotating compressor and freezing, aircondition, relate in particular to and be applicable to that the front end that makes blade part can be at indoor closed rotating compressor and freezing, the aircondition that moves back and forth supplying lubricating oil of oil feed pump.This freezing, aircondition for example is refrigerator, air regulator, dehumidifier, water-heating machine, car air conditioner etc.
Background technique
As rotary compressor in the past, opening in the flat 5-231367 communique the spy once had report.That is, this rotary compressor has: the seal container of dress lubricant oil, the live axle that is accommodated in compression unit in the seal container and electrodynamic element, compression unit is driven by the rotation of electrodynamic element.And this compression unit has compressing mechanism and oil feeding mechanism.In addition, compressing mechanism has: two cylinder barrels that the cylinder barrel chamber arranged, to the parts of the two end part sealing of two cylinder barrel chambers, carry out two cylinder portions of revolution motion two indoor outs of phase with 180 degree of cylinder barrel, two blade parts that will extend from the periphery of two cylinder portions along radial direction, two cylinder barrel chambers are divided respectively.Oil feeding mechanism has: two fuel feeding pump chambers that form in the outside of two cylinder barrel chambers, the front end at two indoor two blades that move back and forth of oil feed pump, the Fluid diode (fluidic diode) that two fuel feeding pump chambers are communicated with, a side who makes the fuel feeding pump chamber are communicated to the interconnecting part in the lubricant oil of seal container and make the opposing party of fuel feeding pump chamber be communicated to the fuel feeding road of the slide part of compressing mechanism.And the front end of two blade parts is formed and drives the straight line shape of axis parallel.
But, in compressor in the past, because the front end of blade part is formed and drives the straight line shape of axis parallel, so the extrusion function of the indoor lubricant oil of oil feed pump is not in full use.For this reason, in rotary compressor in the past, operating condition according to compressor, particularly under the condition of live axle low speed, draw not enough to the lubricant oil of live axle, to each slide part of compressor and the fuel delivery minimizing that has the press part between the crack, the problem that reduces compressor performance and freeze cycle performance is just arranged.And, in rotary compressor in the past, at the replacement refrigeration agent, for example HFC class refrigeration agent, hydrocarbon, the CO that use HCFC class refrigeration agent
2, during natural series refrigeration agent such as ammonia, because the reliability decrease that low and load increases etc. because of lubricity, so the problem that is difficult to fully to guarantee to the fuel delivery of sliding position is arranged.
The object of the present invention is to provide a kind of can preventing because of not enough insufficient lubrication and high closed rotating compressor and freezing, the aircondition of reliability that causes of fuel delivery to the slide part of compressor.
Summary of the invention
In order to reach above-mentioned purpose, closed rotating compressor of the present invention, in the closed container that stores lubricant oil, compressing mechanism and oil feeding mechanism have been taken in, the above-mentioned compressor structure, have in the indoor cylinder portion that carries out revolution motion of cylinder barrel, the blade part that extends and above-mentioned cylinder barrel chamber is divided to radial direction from the outer peripheral surface of cylinder portion, above-mentioned oil feeding mechanism, has the fuel feeding pump chamber that forms in the outside of above-mentioned cylinder barrel chamber, at the front end of the indoor above-mentioned blade part that moves back and forth of above-mentioned oil feed pump, and the front end of above-mentioned blade part is formed along the fuel feeding flow direction and makes the above-mentioned fuel feeding pump chamber wealthy shape that broadens.
Description of drawings
Fig. 1 is the longitudinal sectional view of the closed rotating compressor of one embodiment of the invention.
Fig. 2 is the figure of different operating state among expression and Fig. 1.
Fig. 3 is the A-A sectional drawing of Fig. 2.
Fig. 4 is the stereogram of the oscillating-piston that uses in the compressor.
Fig. 5 is to use the pie graph of freeze cycle of the refrigerating plant of compressor.
Fig. 6 is the stereogram of variation 1 of the oscillating-piston of presentation graphs 1.
Fig. 7 is the stereogram of variation 2 of the oscillating-piston of presentation graphs 1.
Among the figure: 2-main bearing, 2a, 3a-bearing portion, 2b, 3b-exhaust port, 2c, 3c-discharge chamber, 3-supplementary bearing, 4-live axle, 4a, 4b-eccentric part, 5-rotor, 6-closed container, 7-stator, 9-slide member, 10-pressing chamber, 11-suction chamber, 12-suction pipe, 13-interconnecting part, 14a, 14b-discharge cap, 15-discharge tube, 16-lubricant oil, 17-Fluid diode (fluidic diode), 18-oil storage portion, 19-fuel supply line, 20-spiral chute, 21-intercommunicating pore portion (Fluid diode), 22-fuel feeding circulation flow path, 26-demarcation strip, 39-condenser, 39a-condenser fan, 40-expansion valve, 41-vaporizer, 41a-vaporizer fan, 42-compressor, 43-electrodynamic element, 44-compression unit, 50-the 1 cylinder barrel, 50a, 51a-cylinder barrel chamber, 50b, 51b-slid chamber, 50c, 51c-fuel feeding pump chamber, 51-the 2 cylinder barrel, 80,81-oscillating-piston, 80a, 81a-cylinder portion, 80b, 81b-blade part.
Embodiment
Below, with Fig. 1～Fig. 7 embodiments of the invention are described.
At first, present embodiment is also also described with reference to Fig. 1～Fig. 5.
Fig. 1 is the longitudinal sectional view of the closed rotating compressor of one embodiment of the invention.Fig. 2 is the figure of the different operating state among Fig. 1, and Fig. 3 is the A-A sectional drawing of Fig. 2, and Fig. 4 is the stereogram that is applied to the oscillating-piston in the compressor of Fig. 1, and Fig. 5 is the pie graph with the freeze cycle of the refrigerating plant of the compressor of Fig. 1.
The freeze cycle of the refrigerating plant of present embodiment, shown in Figure 5 shown in, be freezing (air-cooling system) special-purpose endless form.This freeze cycle, with compressor 42, condenser 39, decompressor 40, vaporizer 41 orders connect and constitute with the refrigeration pipe arrangement.Compressor 42 is made of horizontal sealing oscillating-piston shape compressor.Condenser 39 is carried out forced ventilation by condenser with fan 39a, but for constituting, do not have condenser also can use the present invention with the situation of fan 39a with natural convection formula heat exchanger.Decompressor 40 is made of institutes such as expansion valve, capillary tubies.Vaporizer 41 is by evaporator fan 41a forced ventilation.
Refrigeration agent in the freeze cycle, starting operation by compressor 42, under the compression of compressor 42, become the gas of high temperature, high pressure, shown in the solid arrow of Fig. 5, flow into condenser 39 from discharge tube 15, and by in condenser heat release, liquefaction and the inflow decompressor 40 with the air-supply effect of fan 39a, by decompressor 40 throttlings, carry out adiabatic expansion and become low-temp low-pressure, in the inflow evaporator 41, in vaporizer 41,, make its gasification after suction pipe 12 sucks the compressor 42 on every side from absorbing heat by the air-supply effect of evaporator fan 41a.As this refrigeration agent, can use the replacement refrigeration agent of HCFC class refrigeration agent, HFC class refrigeration agent for example, hydrocarbon, CO
2, natural series such as ammonia refrigeration agent all.
The refrigerating plant of present embodiment owing to used compressor of the present invention, can become the good refrigerating plant of energy efficiency.Particularly because compressor 42 makes pressure in the closed container 6 below head pressure, so when the compressor 42 of intermittent working stopped, the refrigeration agent that can make high temperature, high pressure in the inflow evaporator 41, can reduce the energy loss that intermittently causes slightly.
Compressing mechanism has: the 1st cylinder barrel the 50, the 2nd cylinder barrel 51, two press parts that rotatably are configured in oscillating- piston 80,81 in each cylinder barrel 50,51, main bearing 2, supplementary bearing 3 and the demarcation strip 26 etc. of the both ends open shutoff of each cylinder barrel 50,51 are formed.Oscillating- piston 80,81 is made of the 80a of cylinder portion, 81a and blade part 80b, 81b.
Oil feeding mechanism is by the fuel feeding pump chamber 50c of the 1st cylinder barrel 50, the fuel feeding pump chamber 51c of the 2nd cylinder barrel 51, and blade part 80b, 81b, interconnecting part 13, intercommunicating pore portion 21, fuel feeding circulation flow path 22 and Fluid diode 17, fuel supply line 19, spiral chute 20 etc. are made up of these parts.Formations such as these fuel feeding circulation flow paths 22, fuel supply line 19 and helical oil groove 20.These fuel feeding circulation flow paths 22, fuel supply line 19 and helical oil groove 20 etc. have constituted the fuel feeding road to slide part.
Fuel feeding pump chamber 50c and fuel feeding pump chamber 51c are communicated with by intercommunicating pore portion 21.Intercommunicating pore portion 21 has the inclination inner face that narrows down in fuel feeding pump chamber 51c one side.Thus, intercommunicating pore portion 21 has the fluid of making and flows to fuel feeding pump chamber 51c from fuel feeding pump chamber 50c easily, and is difficult to carry out the Fluid diode function of reverse flow.In addition, fuel feeding pump chamber 50c is communicated with oil storage portion 18 by interconnecting part 13.
Fuel feeding pump chamber 51c is communicated with oil storage portion 18 by Fluid diode 17 and fuel feeding circulation flow path 22, is communicated with fuel supply line 19 by fuel feeding circulation flow path 22 simultaneously.Fuel supply line 19 will be communicated with between fuel feeding circulation flow path 22 and the spiral chute 20.
At the central part of the 1st cylinder barrel the 50, the 2nd cylinder barrel 51, be formed with cylinder barrel chamber 50a, 51a as the 1st cylindrical hole portion.The both ends open of these cylinder barrel chambers 50a, 51a is with main bearing 2, supplementary bearing 3 and demarcation strip 26 sealings of double as packaged unit.On main bearing 2 and supplementary bearing 3, be formed with the 2a of bearing portion, 3a respectively, and by they supporting rotatable live axle 4.In addition, on main bearing 2 and supplementary bearing 3, the axis of rotation of live axle 4 is fixed on the 1st cylinder barrel the 50, the 2nd cylinder barrel 51 in the mode consistent with the axle center of cylinder barrel chamber 50a, the 51a of the 1st cylinder barrel the 50, the 2nd cylinder barrel 51.The outer circumference portion of main bearing 2 is fixed on the closed container 6.The rotor 5 of electrodynamic element 43 is fixed on the live axle 4, and the stator 7 of electrodynamic element 43 is fixed on the closed container 6.
On live axle 4, be formed with eccentric part 4a, 4b in the cylinder barrel chamber 50a that is positioned at the 1st cylinder barrel the 50, the 2nd cylinder barrel 51, the part of 51a.The cylindrical shape inner peripheral surface of the 80a of cylinder portion, the 81a of the cylindrical shape outer peripheral surface of this eccentric part 4a, 4b and oscillating- piston 80,81 can be chimeric rotatably.Then, be rotated when driving oscillating- piston 80,81 and being rotated at live axle 4, the cylindrical shape outer peripheral surface of the 80a of cylinder portion, 81a and form between the cylindrical shape inner peripheral surface of cylinder barrel chamber 50a, 51a and exist the mode in small gap to decide each size.And, because two eccentric part 4a are formed the outs of phase of 180 degree between mutually, thus can make the variation equalization of the gas compression torque that produces at two press parts, thus the vibration that can lower compressor.
In cylinder barrel 50,51, in the outside of cylinder barrel chamber 50a, 51a, be formed with have the central hub that parallels with the central hub of cylinder barrel chamber 50a, 51a, be the 50b of slid chamber, the 51b of the 2nd cylinder-shaped hole portion.In the outside of the 50b of slid chamber, 51b, form fuel feeding pump chamber 50c, the 51c of promising the 3rd cylindrical portion.Then, the 50b of slid chamber, 51b, the one side is communicated with cylinder barrel chamber 50a, 51a, and opposite side is communicated with fuel feeding pump chamber 50c, 51c.Main bearing 2, supplementary bearing 3 and demarcation strip 26 extend to the two end part of the 50b of slid chamber, 51b and fuel feeding pump chamber 50c, 51c.
From integrally formed blade part 80b, the 81b that prolongs along radial direction of the cylindrical shape outer peripheral surface of the 80a of cylinder portion, 81a.Blade part 80b, 81b will be divided into suction chamber 11 and pressing chamber 10 in cylinder barrel chamber 50a, the 50b, simultaneously can be by in the 50b of slid chamber, the 51b and extend in fuel feeding pump chamber 50c, the 51c.
Between the cylindrical shape inner peripheral surface of blade part 80b and the 50b of slid chamber, 51b, be assembled with slide member 9.This slide member 9 has planar surface portion that contacts with the planar surface portion of blade part 80b, 81b slidably and the cylinder face that contacts with the cylindrical shape inner peripheral surface of the 50b of slid chamber, 51b slidably.This slide member 9 is disposed in the mode that sandwiches blade part 80b, 81b.Its result, blade part 80b, 81b are towards the advance and retreat motion and around the oscillating motion of central shaft of the central shaft of the 50b of slid chamber, 51b.
The front end of blade part 80b, 81b moves back and forth in fuel feeding pump chamber 50c, 51c, and does not interfere with the 1st cylinder barrel 50 and the 2nd cylinder barrel 51.And the front end of blade part 80b, the 81b that moves back and forth is formed the fuel feeding pump chamber 50c, the 51c that the make relative fuel feeding flow direction wealthy shape that broadens.Specifically, as shown in Figure 4, the length of the blade part of upper reaches one side is L1, and the length of the blade part of a dirty side is L2, and be set to the relation of length L 2 of length L a 1＞dirty side of upper reaches one side, and front end is formed the shape with the oblique portion of face that inclines.In the present embodiment because rake is formed straight line shape, so easy processing can be made at an easy rate.
Next, the compressed action to compression unit 44 describes.
When rotor 5 being rotated, with rotor 5 rotations, make oscillating- piston 80,81 in cylinder barrel chamber 50a, 51a, be accompanied by swing and carry out revolution motion with eccentric part 4a, 4b by live axle 4 when electrodynamic element 43 is switched on.Thus, refrigerant gas is drawn in the suction chamber 11, and transfers to the increase and decrease of carrying out volume in the pressing chamber 10 repeatedly, refrigerant gas is compressed.
Concretely, refrigerant gas is inhaled in the closed container 6 from the suction pipe 12 that has been installed on the closed container 6, be drawn in the suction chamber 11 through sucking path, after the minimizing with the volume of pressing chamber 10 is compressed simultaneously, by at the exhaust port 2b, the exhaust port 3b that form on main bearing 2 and the supplementary bearing 3, in formed discharge chamber 2c on main bearing 2 and the discharge cap 14a and formed discharge chamber 2c, discharge chamber 3c discharge on supplementary bearing 3 and discharge cap 14b, be discharged to outside the closed container 6 from discharge tube 15 then.
Below, action describes to the fuel feeding of oil feeding mechanism.Move by rotary oscillation piston 80,81, together carry out the fuel feeding action by oil feeding mechanism with the compressed action that is undertaken by compressing mechanism by live axle 4.
At first, as shown in Figure 1, the oscillating-piston 80 to the 1st cylinder barrel 50 describes in the action situation of upper dead center at the oscillating-piston 81 of lower dead centre, the 2nd cylinder barrel 51 respectively.
Follow the rising of the blade part 81b of the 2nd cylinder barrel 51 1 sides, the lubricant oil 16 that is stored in the oil storage portion 18 of closed container 6 is attracted up from Fluid diode 17, is attracted to fuel feeding pump chamber 51c place through fuel feeding circulation flow path 22.On the other hand, follow the decline of the blade part 80b of the 1st cylinder barrel 50 1 sides, the lubricant oil 16 in the fuel feeding pump chamber 50c is forced among the fuel feeding pump chamber 51c through intercommunicating pore portion 21, flows in the oil storage portion 18 from interconnecting part 13 simultaneously.
In this action, because the front end of blade part 80b is formed making the fuel feeding pump chamber 50c wealthy mode that broadens with respect to the direction that flows to fuel feeding pump chamber 51c fuel feeding, institute so that the lubricant oil 16 of interior anti-fuel feeding pump chamber 51c one side of oil feed pump chamber 50c can easily discharge to fuel feeding pump chamber 51c.Fuel delivery can be increased thus.Particularly,, also fuel delivery can be increased from this point so the lubricant oil 16 in the fuel feeding pump chamber 50c is applied the component of pressing to fuel feeding pump chamber 51c one side because the front end of blade part 80b is formed the plane of inclination.The increase of this fuel delivery is the simple change of the front end shape of blade part 80b having been carried out change, can realize at an easy rate.
To as shown in Figure 2, at upper dead center, the situation that the oscillating-piston 81 of the 2nd cylinder barrel 51 moves when lower dead centre describes to the oscillating-piston 80 of the 1st cylinder barrel 50 from the state of Fig. 1.
Be accompanied by the decline of the blade part 81b of the 2nd cylinder barrel 51, the lubricant oil 16 that drinks up from fuel feeding pump chamber 51c is pressed towards in the fuel feeding circulation flow path 22, be drawn onto an end of live axle 4 again through fuel supply line 19 from fuel feeding circulation flow path 22, and then the spiral chute 20 that is provided with on week by outer garden at live axle 4, supplementary bearing 3, eccentric part 4a, 4b, main bearing 2 are lubricated, are fed back into again in the oil storage portion 18 in the closed container 6.
In this action, owing to the front end of blade part 81b formed with respect to the fuel feeding flow path direction that flows to fuel feeding circulation flow path 22 makes the fuel feeding pump chamber 51c wealthy mode that broadens, so that the anti-fuel feeding circulation flow path 22 1 side lubricant oil 16 in the 51c of oil feed pump chamber can be are easily discharged to fuel feeding circulation flow path 22, can prevent that lubricant oil 16 from flowing out to fuel feeding pump chamber 50c simultaneously.Can increase fuel delivery thus.Particularly,, see also from this point to increase fuel delivery so the lubricant oil 16 in the fuel feeding pump chamber 50c is applied the component of pressing to fuel feeding pump chamber 51c one side because the front end of blade part 81b is formed the plane of inclination.The increase of this fuel delivery is by the simple change to the shape change of the front end of blade part 81b, can realize at an easy rate.And the effect by Fluid diode 17, can prevent lubricant oil 16 adverse currents that extrude from the fuel feeding pump chamber 51c oil storage portion 18 in the closed container 6.
Like this, rotation by live axle, the blade part 80b, the 81b that tilt to the fuel feeding flow direction are moved back and forth in fuel feeding pump chamber 50c, 51c, and the effect of the blade oil feed pump that changes by the volume that makes fuel feeding pump chamber 50c, 51c, can be drawn onto live axle 4 to the lubricant oil 16 that is stored in closed container 6 bottoms with q.s.
According to above formation,, can prevent because of the low on fuel insufficient lubrication even when variation has taken place operating condition when low-speed running (for example), also lubricant oil 16 suitably can be supplied with each slide part.The closed rotating compressor of high reliability can be provided thus.And, at the replacement refrigeration agent that uses HCFC class refrigeration agent, for example, HFC class refrigeration agent, hydrocarbon, CO
2, during natural series refrigeration agent such as ammonia, in general low and load increases and causes reliability decrease because of lubricity, but as just can prevent the decline of reliability according to present embodiment, in closed rotating compressor, can adopt the replacement refrigeration agent.
Below, two variation limits of oscillating- piston 80,81 are described with reference to Fig. 6 and Fig. 7 limit.Variation 1 shown in Figure 6 is that the front end shape of blade part 80b, 81b is formed the inclination arcuation.In addition, the variation of representing in Fig. 72 is that the front shape of blade part 80b, 81b is formed the shape with ladder.In these variation 1,2, though process some the trouble since the same with said structure make broaden to fuel feeding pump chamber 50c, the 51c of fuel feeding flow direction wealthy, so these common structures can obtain same effect.
In the above-described embodiment, to cylinder and blade-shaped all-in-one-piece wobble-piston type compressor are illustrated, even but be that the rotary compressor of split is suitable for too to cylinder and blade.This means so long as the compressor of blade oil feed pump formula all is fine.
And not only single stage compressor also can be a two stage compressor.In addition, refrigerating plant but also not only applicable to aircondition.
(invention effect)
Know significantly from above explanation,, can prevent because of fuel delivery deficiency insufficient lubrication, thereby can provide a kind of reliability high closed rotating compressor to the slide part of compressing mechanism according to using the present invention.
Claims (6)
1. closed rotating compressor is characterized by:
In the closed container that stores lubricant oil, taken in compressing mechanism and oil feeding mechanism,
Described compressing mechanism is formed with at indoor cylinder portion that carries out revolution motion of cylinder barrel and the blade part that extends and described cylinder barrel chamber is divided to radial direction from the outer peripheral surface of cylinder portion,
Described oil feeding mechanism is formed with the fuel feeding pump chamber that forms in the outside of described cylinder barrel chamber and at the front end of the indoor described blade part that moves back and forth of described oil feed pump,
The front end of described blade part is formed along the fuel feeding flow direction and makes the described fuel feeding pump chamber wealthy shape that broadens.
2. closed rotating compressor according to claim 1 is characterized by:
The length of described blade part upper reaches one side is longer than the length of a dirty side, and the front end of this blade part is formed the plane of inclination shape.
3. 1 or 2 described closed rotating compressors as requested is characterized by:
The pressure in the space in the described closed container is made as the pressure lower than head pressure.
4. according to any described closed rotating compressor in the claim 1～3, it is characterized by:
As the replacement refrigeration agent of refrigerant compressed HCFC, use be hydrocarbon, the CO of HFC class refrigeration agent
2, natural series refrigeration agent such as ammonia any one.
5. closed rotating compressor is characterized by:
Have: store lubricant oil closed container, be accommodated in the live axle that compression unit in the described closed container and electrodynamic element, the rotation by described electrodynamic element drive described compression unit,
Described compression unit has compressing mechanism and oil feeding mechanism,
Described compressing mechanism, be provided with: the parts that have the cylinder barrel of two cylinder barrel chambers, the two end part of described two cylinder barrel chambers are sealed, the indoor outs of phase of described two cylinder barrels with 180 degree carry out revolution motion two cylinder portions, extend and to indoor two blade parts that advance to divide respectively of described two cylinder barrels to radial direction from the outer peripheral surface of described two cylinder portions
Described oil feeding mechanism, be provided with: two fuel feeding pump chambers that form in described two cylinder barrel outdoors, at the front end of indoor described two blade parts that move back and forth of described two oil feed pumps, be communicated with the Fluid diode of described two fuel feeding pump chambers, interconnecting part that a side of described two fuel feeding pump chambers is communicated with the lubricant oil of described closed container, fuel feeding road that the opposing party of described two fuel feeding pump chambers is communicated with slide part
The front end of described two blade parts is formed along the fuel feeding flow direction and makes the described fuel feeding pump chamber wealthy shape that broadens.
6. closed rotating compressor is characterized by:
With closed rotating compressor, condenser, decompressor, vaporizer connect and form the cooling cycle system of the replacement refrigeration agent of inclosure HCFC class refrigeration agent with the refrigeration pipe arrangement,
Described closed rotating compressor, have: be made as in the container than the low pressure of head pressure and store lubricant oil closed container, be accommodated in the live axle that compression unit in the described closed container and electrodynamic element, rotation by described electrodynamic element drive described compression unit
Described compression unit has compressing mechanism and oil feeding mechanism,
Described compressing mechanism, be provided with: parts that have the cylinder barrel of cylinder barrel chamber, the two end part of described cylinder barrel chamber are sealed, in the indoor cylinder portion that carries out revolution motion of described cylinder barrel, extend and to the indoor blade part of dividing of described cylinder barrel to radial direction from the outer peripheral surface of described cylinder portion
Described oil feeding mechanism, be provided with: the fuel feeding pump chamber that forms in the outside of described cylinder barrel chamber, the Fluid diode that is communicated with described fuel feeding pump chamber at the front end of the indoor described blade part that moves back and forth of described oil feed pump, with the lubricant oil of described closed container, the fuel feeding road that described fuel feeding pump chamber is communicated with the slide part of described compression mechanical part
The front end of described blade part is formed along the fuel feeding flow direction and makes the described fuel feeding pump chamber wealthy shape that broadens.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002003260A JP4074760B2 (en) | 2002-01-10 | 2002-01-10 | Hermetic rotary compressor and refrigeration / air conditioner |
| JP2002003260 | 2002-01-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1431403A true CN1431403A (en) | 2003-07-23 |
| CN1231680C CN1231680C (en) | 2005-12-14 |
Family
ID=19190860
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 03101634 Expired - Fee Related CN1231680C (en) | 2002-01-10 | 2003-01-10 | Enclosed rotary compressor and freezing air conditioning unit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4074760B2 (en) |
| CN (1) | CN1231680C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103912495A (en) * | 2012-12-28 | 2014-07-09 | Lg电子株式会社 | Compressor |
| US9394904B2 (en) | 2012-12-28 | 2016-07-19 | Lg Electronics Inc. | Compressor |
| CN111120316A (en) * | 2018-10-31 | 2020-05-08 | 上海海立电器有限公司 | Compressor and air conditioning system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7541257B1 (en) | 2023-03-20 | 2024-08-28 | ダイキン工業株式会社 | Rotary compressor and refrigeration device |
-
2002
- 2002-01-10 JP JP2002003260A patent/JP4074760B2/en not_active Expired - Fee Related
-
2003
- 2003-01-10 CN CN 03101634 patent/CN1231680C/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103912495A (en) * | 2012-12-28 | 2014-07-09 | Lg电子株式会社 | Compressor |
| CN103912495B (en) * | 2012-12-28 | 2016-06-15 | Lg电子株式会社 | Compressor |
| US9394904B2 (en) | 2012-12-28 | 2016-07-19 | Lg Electronics Inc. | Compressor |
| US9429156B2 (en) | 2012-12-28 | 2016-08-30 | Lg Electronics Inc. | Compressor |
| CN111120316A (en) * | 2018-10-31 | 2020-05-08 | 上海海立电器有限公司 | Compressor and air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4074760B2 (en) | 2008-04-09 |
| JP2003206876A (en) | 2003-07-25 |
| CN1231680C (en) | 2005-12-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100540901C (en) | Rotary compressor and use the refrigerating circulatory device of this rotary compressor | |
| CN103089631B (en) | Rotary compressor | |
| CN1573115A (en) | Plural compressors | |
| CN200971846Y (en) | Sealed compressor | |
| CN1231680C (en) | Enclosed rotary compressor and freezing air conditioning unit | |
| CN1629490A (en) | Vortex compressor | |
| JP4696530B2 (en) | Fluid machinery | |
| US12055325B2 (en) | Rotary compressor and home appliance including the same | |
| KR100612811B1 (en) | Horizontal Rotary Compressor | |
| US20100132382A1 (en) | Method and apparatus for orientation independent compression | |
| EP0864751A2 (en) | Compressor for use in a transcritical refrigeration cycle system | |
| JP3045961B2 (en) | Scroll gas compression | |
| US7186098B2 (en) | Eccentric pump and method for operation of said pump | |
| CN1237313C (en) | Enclosed rotary compressor | |
| JPH10148193A (en) | Rotary compressor | |
| JP2010065589A (en) | Hermetic compressor and refrigerating cycle device | |
| JP2004225578A (en) | Rotary compressor | |
| CN2602188Y (en) | Enclosed type motor compressor | |
| CN205172942U (en) | Rotary compressor | |
| US11953001B2 (en) | Horizontal type rotary compressor and home appliance including the same | |
| CN1916424A (en) | Exhaust structure of main bearing and rotation axis in revolve type compressor | |
| JP2003139082A (en) | Sealed rotary compressor | |
| CN1291157C (en) | Enclosed type electric compressor | |
| WO2022004028A1 (en) | Rotary compressor and refrigeration cycle device | |
| KR101128791B1 (en) | gear type compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: HITACHI APPLIANCES, INC. Free format text: FORMER OWNER: HITACHI,LTD. Effective date: 20150630 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20150630 Address after: Tokyo, Japan, Japan Patentee after: Hitachi Appliances Inc. Address before: Tokyo, Japan, Japan Patentee before: Hitachi Ltd. |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20160901 Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee after: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. Address before: Tokyo, Japan, Japan Patentee before: Hitachi Appliances Inc. |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20180712 Address after: Tokyo, Japan, Japan Patentee after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
|
| TR01 | Transfer of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20051214 Termination date: 20200110 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |