CN101187373A - Variable capacity type rotary compressor - Google Patents
Variable capacity type rotary compressor Download PDFInfo
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- CN101187373A CN101187373A CNA2007101485601A CN200710148560A CN101187373A CN 101187373 A CN101187373 A CN 101187373A CN A2007101485601 A CNA2007101485601 A CN A2007101485601A CN 200710148560 A CN200710148560 A CN 200710148560A CN 101187373 A CN101187373 A CN 101187373A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
- F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
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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
- F04C18/344—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 inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
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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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Abstract
A capacity-variable rotary compressor, in which a vane can be restricted by a pressure difference generated between both side surfaces of the vane when the compressor performs a saving driving, and simultaneously be restricted rapidly and stably by rapidly decreasing a pressure of a vane chamber by leaking a discharge pressure of the vane chamber to an inlet via a low pressure passage and thereby increasing a pressurizing force applied to a side surface of the vane relatively greater than a supporting force applied to a rear surface thereof, whereby the vane can be previously prevented from being vibrated due to a weak restriction force of the vane when a power mode of the compressor is switched into the saving mode, which results in preventing of noise from being increased due to design conditions, thereby enhancing comfortable feeling.
Description
Technical field
The present invention relates to a kind of variable capacity rotary compressor.
Background technique
Usually, use variable capacity rotary compressor to make cooling capacity can change (promptly increase or reduce), to optimize the input output ratio according to environmental conditions.As one of wherein method, recently, the frequency variator motor is applicable to compressor, is used to change the cooling capacity of compressor.But, be applicable at the frequency variator motor under the situation of compressor that cost for manufacturing compressor increases because of the high price of frequency variator motor, thereby has reduced price competitiveness.In addition, replace the frequency variator motor is applicable to compressor, study the refrigeration agent that is compressed in the cylinder of compressor widely and partly be diverted to the outside so that change the technology of the capacity of pressing chamber.But this technical requirements is used for refrigeration agent is diverted to the complicated pipeline system of cylinder outside.Therefore, the flow resistance of refrigeration agent increases, thereby lowers efficiency.
Similarly, propose a kind of method, by this method, pipe-line system can be simplified under the situation of not using the frequency variator motor, and can change the capacity of compressor.
Pressure in the inner space of first method permission cylinder is changed (change) and becomes suction pressure or head pressure.Therefore, when motivational drive (pattern), suction pressure puts on the inner space of cylinder, and blade carries out sliding movement usually, thereby forms pressing chamber.On the contrary, when energy-conservation driving, head pressure puts on the inner space of cylinder, and blades retracted, thereby does not form pressing chamber (hereinafter, this method is called " the first variable capacity method ").
Implement second method, make the refrigeration agent of suction pressure only apply, and suction pressure and head pressure alternately put on the back of blade by import.Therefore, when motivational drive, blade is carried out sliding movement usually, thereby forms pressing chamber.On the contrary, when energy-conservation driving, blades retracted, thus do not form pressing chamber (hereinafter, this method is called " the second variable capacity method ").
But for stable system, two kinds of above-mentioned methods are limit blade continuously, particularly in energy saver mode.Therefore, should be provided for the vane limits unit of limit blade.
For example, about the first variable capacity method, as shown in Figure 1, magnet 4 is set in place the back place of the blade 3 in the blade groove 2 of cylinder 1, or as shown in Figure 2, and the back pressure changing valve 5 that is used to supply suction pressure is arranged on the place, back of blade 3.Therefore, blade 3 remains in the retracted mode.Unaccounted reference character 6 expression rolling pistons, 7 expression mode switch valves, and 8 expression imports.
In addition, about the second variable capacity method, as shown in Figure 3, side pressure passage 9 is arranged in the cylinder 1, to supply head pressure and limit blade 3 by the side from blade 3.Unaccounted reference character 10 expression vane room, and 11 expression back pressure changing valves.
But in the conversion of the operating mode of compressor, the vane limits unit of prior art can not limit blade 3, thereby has reduced the performance of compressor.Especially, vibration noise produces from blade 3, and this has greatly increased compressor noise.For example, in the method for Fig. 1, in order to carry out the compressor mode conversion reposefully, magnet 4 can not apply big magnetic force.As a result, when energy conservation of compressor drove, magnet 4 is limit blade 3 promptly, produced noise thereby can beat because of blade.On the other hand, in the method for Fig. 2, when the motivational drive of compressor, the pressure of blade 3 back can not be changed into suction pressure from head pressure rapidly, thereby blade 3 is not limited in mode switch.As a result, noise can produce because of the bump between rolling piston 6 and the blade 3.And in the method for Fig. 3, the side force F2 that is transferred to blade 3 by side pressure passage 9 does not have sufficiently the power F1 greater than the pressure in the vane room 10.And the pressure of blade 3 back can not promptly be changed into suction pressure from head pressure, thereby blade 3 is not limited in the compressor mode conversion.As a result, clash between blade 3 and rolling piston 6, this has made noise.Especially, under the special drive condition of compressor, as shown in Figure 4, when compressor when dynamic mode is converted to energy saver mode, in determining time t, produce excessive noise.
Summary of the invention
Therefore, the purpose of this invention is to provide a kind of variable capacity rotary compressor, it can reduce the noise that produces because of the bump between blade and the rolling piston significantly by quick limit blade when changing compressor mode.
In order to realize that this is with other advantages and according to purpose of the present invention, as implement herein and broadly described, provide a kind of variable capacity rotary compressor, wherein rolling piston is carried out the eccentric orbit motion in the inner space of the cylinder assembly of sealing, blade pass is crossed the touch scrolling piston and is being carried out linear motion in the radial direction, thereby the inner space is divided into pressing chamber and suction chamber, then when energy-conservation drive by putting on pressure difference on the blade limit blade.
In order to realize that this is with other advantages and according to purpose of the present invention, provide a kind of variable capacity rotary compressor, it comprises: be installed in the cylinder assembly in the shell of sealing, this cylinder assembly comprises compression volume, import and blade groove, refrigeration agent is inhaled in this compression volume so that be compressed, this import is connected to described compression volume, and blade groove is formed on a side place of import; Rolling piston, described rolling piston are used for transmitting refrigeration agent by carry out the eccentric orbit motion in the compression volume of cylinder assembly; Blade, described blade inserts in the blade groove of cylinder assembly slidably, and has the inner that contacts with rolling piston, so that compression volume is divided into suction chamber and pressing chamber; And mode switching unit, described mode switching unit is used for operating mode according to compressor makes blade with the rolling piston contact or separate, wherein, suction pressure is applied on the side surface of blade, and head pressure is applied on the opposite side of blade, make blade can contact blade groove, thereby when compressor is carried out energy-conservation driving, be limited.
In conjunction with the accompanying drawings, aforementioned purpose, feature, aspect and the advantage with other of the present invention will become more obvious from the following detailed description of the present invention.
Description of drawings
This accompanying drawing illustrates embodiments of the invention, and with describing in order to explain principle of the present invention, wherein this accompanying drawing is involved further understanding of the present invention to be provided and to be merged in this specification and the part of formation specification.
In the accompanying drawings:
Fig. 1 is the horizontal cross that illustrates according to an embodiment of the variable capacity rotary compressor of prior art;
Fig. 2 is the horizontal cross that illustrates according to another embodiment of the variable capacity rotary compressor of prior art;
Fig. 3 is the horizontal cross that illustrates according to another embodiment of the variable capacity rotary compressor of prior art;
Fig. 4 is the plotted curve that the noise characteristic of variable capacity rotary compressor when translative mode of Fig. 3 is shown;
Fig. 5 is the longitudinal sectional view that illustrates according to an embodiment of variable capacity rotary compressor of the present invention;
Fig. 6 is the horizontal cross that the releasing state of the blade of variable capacity rotary compressor according to the present invention when dynamic mode are shown;
Fig. 7 is the horizontal cross that the restriction state of the blade of variable capacity rotary compressor according to the present invention when energy saver mode is shown;
Fig. 8 is the enlarged view of process that the limit blade of Fig. 7 at length is shown;
Fig. 9 is the plotted curve that the noise characteristic of variable capacity rotary compressor according to the present invention when translative mode is shown; And
Figure 10 and Figure 11 are the horizontal cross that illustrates respectively according to another embodiment of variable capacity rotary compressor of the present invention.
Embodiment
With reference to the accompanying drawings, will describe the present invention in detail.
Typically, rotary compressor can be monotype rotary compressor or dimorphism rotary compressor according to the quantitative classification of cylinder.For example, for the monotype rotary compressor, the rotating force that pressing chamber utilization is partly transmitted from motor and forming, and, utilize the rotating force that partly transmits from motor for the dimorphism rotary compressor, be vertically formed a plurality of pressing chambers that have 180 degree phase differences therebetween.Hereinafter, with providing the explanation of dimorphism variable capacity rotary compressor, wherein be vertically formed a plurality of pressing chambers, and the capacity of at least one pressing chamber can change.
Hereinafter, with reference to an embodiment shown in the accompanying drawing, at length explain according to variable capacity dimorphism rotary compressor of the present invention.
Fig. 5 is the longitudinal sectional view that illustrates according to an embodiment of variable capacity rotary compressor of the present invention, Fig. 6 is the horizontal cross that the releasing state of the blade of variable capacity rotary compressor according to the present invention when dynamic mode are shown, Fig. 7 is the horizontal cross that the restriction state of the blade of variable capacity rotary compressor according to the present invention when energy saver mode is shown, Fig. 8 is the enlarged view of process that the limit blade of Fig. 7 at length is shown, and Fig. 9 is the plotted curve that the noise characteristic of variable capacity rotary compressor according to the present invention when changing pattern is shown.
As shown in Figure 5, dimorphism variable capacity rotary compressor according to the present invention comprises: the shell 100 with seal space, be installed in shell 100 the upside place, be used to produce the motor part 200 of rotating force at the uniform velocity or frequency variator rotating force, be separately positioned on shell 100 than the downside place, be used for first compression member 300 and second compression member 400 by the rotating force compressed refrigerant that produces from motor part 200, and be used for the conversion operation pattern and make second compression member 400 carry out the mode switching unit 500 of motivational drives or energy-conservation driving.
The seal space of shell 100 remains on the head pressure atmosphere by the refrigeration agent from first compression member 300 and 400 discharges of second compression member.The first sucking pipe SP1 and the second sucking pipe SP2 are connected respectively to the following circumferential surface of shell 100, so that allow refrigeration agent to be inhaled in first and second compression members 300 and 400.An outlet pipe DP is connected to the upper end of shell 100, makes the refrigeration agent that is discharged to seal space from first and second compression members 300 and 400 can be transferred to cooling system.
Motor part 200 comprises: be installed in the stator 210 that also receives in the shell 100 from the energy of outside, be arranged in the stator 210 and by interacting and rotor rotated 220 with certain air gap, and be connected with rotor 220 and be used to transmit the rotating shaft 230 of rotating force to first compression member 300 and second compression member 400 with stator 210.
As shown in Figure 5, first cylinder 310 comprises: be formed on first blade groove 311 of a side of the inner circumferential surface of first cylinder 310, its composition is used for first blade 350 at the radially reciprocating first compression volume V1; Radially be formed on first blade groove, 311 1 sides, be used for refrigeration agent is introduced the first import (not shown) of the first compression volume V1; And be mounted obliquely within vertically first blade groove 311 opposite side, be used for discharging refrigerant and discharge the guide groove (not shown) to first of shell 100.
One of upper bearing (metal) 320 and middle (center) bearing 330 have the diameter less than the diameter of first cylinder 310, and the head pressure that makes the outer end " rear end " of use (or hereinafter be equal to) of the blade 350 of winning can be received in the refrigeration agent in the seal space of shell 100 supports.
In case of necessity, the second compression volume V2 of second cylinder 410 can have the identical or different capacity of the first compression volume V1 with first cylinder 310.For example, have under the situation of identical capacity at two cylinders 310 and 410, when second cylinder 410 drove under energy saver mode, with the capacity Driven Compressor corresponding to the capacity of another cylinder (as first cylinder 310), so the function of compressor can change 50%.On the other hand, have under the situation of different capacity at two cylinders 310 and 410, the function of compressor can change ratio corresponding to the capacity of carrying out power-actuated cylinder.
As shown in Figs. 5 to 7, second cylinder 410 comprises: be formed on second blade groove 411 of a side of the inner circumferential surface of second cylinder 410, its composition is used for second blade 440 at the radially reciprocating second compression volume V2; Radially be formed on second blade groove, 411 1 sides, be used for refrigeration agent is introduced second import 412 of the second compression volume V2; And be formed obliquely opposite side vertically, be used for discharging refrigerant and discharge the guide groove (not shown) to second of shell 100 in second blade groove 411.
And vane room 413 is formed on the back of second blade groove 411 hermetically, and is connected in the common side connecting tube 530 of back with the mode switching unit 500 of explanation.Vane room is also separated from the seal space of shell 100, is suction pressure atmosphere or head pressure atmosphere so that keep the back of second blade 440.High-pressure channel 414 be used for along perpendicular to or the direction that favours the moving direction of second blade 440 connect the inside and second blade groove 411 of shell 100, thereby and limit second blade 440 by the head pressure of shell 100 inside, high-pressure channel 414 is formed on second cylinder 440.Low-pressure channel 415 is used to connect second blade groove 411 and second import 412, thus the pressure difference of generation and high-pressure channel 414, and so that limit second blade 440 fast, low-pressure channel 415 is formed on the opposing face of high-pressure channel 414.
Be connected to the back vane room 413 of the common side connecting tube 530 explained is had certain internal capacity.Therefore, even second blade 440 moves fully backward, make to be received in second blade groove, 411 inside that the rear surface of second blade 440 can have the pressure surface that is used for by the pressure of common side connecting tube 530 supplies.
As shown in Figure 5 and Figure 6, high-pressure channel 414 is positioned at the side based on the discharge guide groove (not shown) of second cylinder 410 of second blade 440, and the center from the external peripheral surface of second cylinder 410 towards second blade groove 411 is penetratingly formed.
High-pressure channel 414 forms has two-stage, and it utilizes two-stage drill bit straitly to form towards second blade groove 411.The outlet of high-pressure channel 414 is formed on about intermediate portion of second blade groove 411 along the longitudinal direction, makes second blade 440 can carry out stable linear reciprocating motion.
Preferably, the section area of high-pressure channel 414 is equal to or less than the pressure surface that puts on the rear surface of second blade 440 by vane room, i.e. the section area of second blade groove 411, thus prevent that second blade 440 from exceedingly being limited.
Though it is not shown in figures, high-pressure channel 414 can be in the certain degree of depth of the upper and lower sides of second cylinder 410 surface depression, or forms in the certain degree of depth of the lower bearing 420 of the both side surface that is connected to second cylinder 410 or middle (center) bearing 330 depressions or by lower bearing 420 or middle (center) bearing 330.Herein, if high-pressure channel 414 in the upper surface of one of lower bearing 420 or middle (center) bearing 330 depression, it can form when second cylinder 410 or each bearing 420 and 330 are handled by sintering, thereby reduces manufacture cost.
Low-pressure channel 415 preferably be arranged on high-pressure channel 414 same straight lines on, make to produce pressure difference between head pressure and the suction pressure, thereby allow second blade, 440 contacts, second blade groove 411 in the both side surface of second blade 440.But low-pressure channel 415 can be formed on the parallel lines with high-pressure channel 414 or make itself and high-pressure channel 414 intersect in certain angle.
As shown in Figure 8, when compressor was in energy saver mode, low-pressure channel 415 preferably was arranged to be connected in vane room 413 by the gap between second blade 440 and second blade groove 411.But, if second blade 440 moves forward when compressor is in dynamic mode, when low-pressure channel 415 was connected to vane room 413, the head pressure Pd that is filled into vane room 413 leaked into second import 412, and the refrigeration agent of suction pressure is incorporated in this second import.Therefore, second blade 440 is supported unsatisfactorily.Therefore, low-pressure channel 415 preferably forms within the reciprocating scope that is arranged on second blade 440.
Though not shown in figures, high-pressure channel 414 and low-pressure channel 415 can form a plurality of along the short transverse of second blade 440.The section area of high-pressure channel 414 and low-pressure channel 415 can be identical or different.
Low voltage side connecting tube 510 connects between the suction side sucking pipe of the suction side of second cylinder 410 and accumulator 110, or connects between the suction side of second cylinder 410 and outlet side sucking pipe (the second sucking pipe SP2).
High pressure side connecting tube 520 can be connected to shell 100 than lower part, thereby directly the oil of shell 100 inside is incorporated in the vane room 413, maybe can be from the intermediate portion bifurcated of outlet pipe DP.Here, when vane room 413 became sealing, oil can not be supplied between second blade 440 and second blade groove 411, and this may produce friction loss.Therefore, the oil supply hole (not shown) is formed on the lower bearing 420, makes that oil can access supply when second blade 440 is carried out to-and-fro motion.
Operational effect according to variable capacity dimorphism rotary compressor of the present invention will be described below.
That is, when the stator 210 that puts on motor part 200 owing to energy made rotor 220 rotations, rotating shaft 230 was with rotor 220 rotations.Therefore, the rotating force of motor part 200 correspondingly is transferred to first compression member 300 and second compression member 400.Capacity according to air conditioner, first and second compression members 300 and 400 all normally drive (as at dynamic mode), so that produce jumbo cooling capacity, or normal driving of first compression member, 300 execution, and second compression member 400 is carried out energy-conservation driving, so that produce the cooling capacity of small capacity.
Here, at compressor or have under the situation of air conditioner at dynamic mode of this compressor, as shown in Figure 6, energy puts on the second mode switch valve 550.Therefore, when high pressure side connecting tube 520 was connected in common side connecting tube 530, low voltage side connecting tube 510 was blocked.The high pressure air of shell 100 inside or high pressure oil are supplied in the vane room 413 of second cylinder 410 by high pressure side connecting tube 520, thereby second blade 440 is withdrawn under the pressure effect of vane room 413.As a result, second blade 440 remains on and second rolling piston, 430 state of contact, and normally compresses the refrigerant gas that is incorporated among the second compression volume V2, discharges compressed refrigerant gas then.
At this moment, high-pressure refrigerant or high pressure oil are supplied to the high-pressure channel 414 that is formed in second cylinder 410 or bearing 430 or 420, thus a side surface of second blade 440 that pressurizes.But because the section area of high-pressure channel 414 is less than the section area of second blade groove 411, vane room 413 moulding pressure in the horizontal is less than the moulding pressure of vane room 413 on fore-and-aft direction.Therefore, second blade 440 is not limited.
Similarly, first blade 350 contacts with 440 with rolling piston 340 respectively with second blade 440, thereby the first compression volume V1 and the second compression volume V2 are divided into suction chamber and pressing chamber.Therefore, first blade 310 and 440 compressions of second blade are drawn into each refrigeration agent in each suction chamber, discharge compressed refrigeration agent then.As a result, compressor or air conditioner with this compressor are carried out 100% and are driven.
On the other hand, when compressor or air conditioner with this compressor are in energy saver mode similarly during initial driving, as shown in Figure 7, mode switch valve 510 runs to normally (power) driving in opposite mode, thereby connects low voltage side connecting tube 510 to common side connecting tube 530.As a result, the low pressure refrigerant that is drawn into second cylinder 410 partly is incorporated in the vane room 413.Therefore, second blade 440 is withdrawn under the pressure effect of the second compression volume V2, and being contained in second blade groove, 411 inside, and therefore suction chamber and the pressing chamber of the second compression volume V2 are connected to each other.The refrigeration agent that is drawn into the second compression volume V2 is not compressed thus.
Here, the pressure difference that is applied on the both side surface of second blade 440 increases by high-pressure channel 414 and the low-pressure channel 415 that is formed in second cylinder 410 or bearing 330 or 420.Therefore, second blade 440 can be limited rapidly effectively.For example, shown in Fig. 7 and 8, high pressure oil or refrigeration agent are introduced in high-pressure channel 414, and the refrigeration agent or the oil leakage that are retained in the head pressure of vane room 413 simultaneously leak in second import 412 to the gap between second blade 440 and the blade groove 411 with by low-pressure channel 415.Therefore, when the operating mode of compressor was changed, second blade 440 can more promptly be limited.In particular, when compressor when dynamic mode is transformed into energy saver mode, if the head pressure Pd that is filled in the vane room 413 does not promptly therefrom discharge, the restraint F2 that is transferred to second blade 440 by high-pressure channel 414 is not very greater than the support force F1 that is transferred to second blade 440 from vane room 413, wherein the little section area owing to high-pressure channel 414 makes vane room have big relatively pressurization area, thereby makes second blade move instability.But if be connected in the opposite that the low-pressure channel 41 5 of second import 412 is formed on high-pressure channel 414, the head pressure Pd that is retained in the vane room 413 changes into middle pressure Pm, and promptly leaks from low-pressure channel 415.Therefore, the support force F1 of vane room 413 reduces sharp, so that allow second blade 440 promptly to be limited.
Fig. 9 illustrates its test result.That is, from Fig. 9, can notice do not have generation when dynamic mode is transformed into energy saver mode, to produce about 2.5 seconds peak noise as shown in Figure 4.
Similarly, when the pressing chamber of second cylinder 410 and suction chamber were connected to each other, the whole refrigeration agent that is drawn into the suction chamber of second cylinder 410 was not compressed, but moves in the suction chamber along the track of second rolling piston 430.Therefore, second compression member 400 is compressed refrigerant not, and compressor or air conditioner with this compressor are only carried out and the corresponding driving of the capacity of first compression member 300 thus.
Vane limits method according to the present invention can be applicable to another kind of variable capacity rotary compressor.
Promptly, in the foregoing embodiments, the operating mode of tube compressor is not at any time supplied the refrigeration agent of suction pressure Ps under the situation of import 412, vane room 413 is connected in import 412, make that the head pressure Pd of vane room 413 promptly leaks into import 412 when dynamic mode is transformed into energy saver mode.But, in these embodiments shown in Figure 10 and 11, further be provided with refrigeration agent changing valve 600 being connected on the sucking pipe (not shown) of import 412, make selectively the refrigeration agent of suction pressure Ps or head pressure Pd to be fed to import 41 2 according to operating mode.Here, when energy saver mode, the refrigeration agent of head pressure Pd is introduced among the second compression volume V2 of second cylinder 410 by import 41 2, thereby and second blade 440 correspondingly withdraw to be limited.
In this case, as shown in figure 10, what can implement is that according to the operating mode of compressor, perhaps head pressure Pd or suction pressure Ps selectively are fed to the rear side of second blade 440.In replaceable scheme, as shown in figure 11, what can implement is that head pressure Pd can be fed to the rear side of second blade 440 always.
For example, in the embodiment of Figure 10, the vane room 413 of separating from the seal space of shell 100 is formed on the rear side of second blade 440, and is connected in vane room 413 according to the back pressure changing valve 700 that the operating mode of compressor is used for selectively supplying suction pressure or head pressure.And in the embodiment of Figure 11, the seal space of shell 100 is connected in the outer surface of second blade groove 411, and vane limits unit 800, as magnet or pull spring, is arranged on the external peripheral surface place of second blade groove 411.
Even in the above-described embodiments, high-pressure channel 414 and low-pressure channel 415 are connected in the both sides of second blade groove 411.Therefore, when energy saver mode, second blade 440 can be limited effectively by the pressure difference between high-pressure channel 414 and low-pressure channel 415.
But, in these embodiments, when energy saver mode, because the refrigeration agent of head pressure Pd is introduced into by second import 412, so it is different with an aforesaid embodiment, high-pressure channel 414 preferably is formed between second import 412 and second blade groove 411, and low-pressure channel 415 preferably forms the suction pressure side connecting tube (not shown) that is connected to the outer surface that is arranged on shell 100 from the opposition side of high-pressure channel 414.
Like this, described typical dimorphism rotary compressor, but the present invention can similarly be applied to the monotype rotary compressor according to aforesaid embodiment.And it can similarly be used for each compression member of dimorphism rotary compressor, and it all explains with those aforesaid embodiments similar, therefore no longer repeats.
Because the present invention can implement in many ways in the situation that does not break away from spirit of the present invention or major character, it should be understood that equally, the above embodiments are not limited to any details described above, except as otherwise noted, otherwise should be by broad interpretation within the spirit and scope that its claims limit, and fall into therefore, that institute in the border of claim and the scope changes and modification or this border and scope in equivalent so and comprised by claims.
Claims (21)
1. variable capacity rotary compressor, wherein rolling piston is carried out the eccentric orbit motion in the inner space of the cylinder assembly of sealing, blade pass is crossed the touch scrolling piston and is being carried out linear motion in the radial direction, thereby the inner space is divided into pressing chamber and suction chamber, then when energy-conservation drive by being applied to pressure difference on the blade limit blade.
2. compressor as claimed in claim 1, wherein, suction pressure that the direction that the moving direction by edge and blade intersects applies and head pressure and limit blade.
3. compressor as claimed in claim 1, wherein, according to the operating mode of compressor, suction pressure and head pressure selectively are fed on the rear side of blade.
4. compressor as claimed in claim 3 wherein, forms connecting passage, makes to be communicated with on the pressure at the rear side place of blade and edge and the crossing direction applied pressure of pressure at the rear side place of blade.
5. compressor as claimed in claim 1, wherein, according to the operating mode of compressor, suction pressure and head pressure selectively are fed in the inner space of described cylinder assembly.
6. compressor as claimed in claim 5, wherein, when compressor is in energy-conservation driving, be fed to the direction that the moving direction of head pressure edge in the inner space of described cylinder assembly and blade intersects and be applied on the blade, and suction pressure is applied on the blade along the direction opposite with it.
7. variable capacity rotary compressor comprises:
Be installed in the cylinder of the cylinder assembly in the shell of sealing, this cylinder assembly comprises compression volume, import and blade groove, refrigeration agent is inhaled in this compression volume so that be compressed, and this import is connected to described compression volume, and described blade groove is formed on a side place of import;
Rolling piston, described rolling piston are used for transmitting refrigeration agent by carry out the eccentric orbit motion in the compression volume of described cylinder assembly;
Blade, described blade inserts in the blade groove of described cylinder assembly slidably, and has the inner that contacts with rolling piston, so that compression volume is divided into suction chamber and pressing chamber; And
Mode switching unit, described mode switching unit are used for operating mode according to compressor makes blade with the rolling piston contact or separate,
Wherein, suction pressure is applied on the side surface of blade, and head pressure is applied on the opposite side of blade, makes to allow blade contact with blade groove, thereby is limited when the energy-conservation driving of compressor execution.
8. compressor as claimed in claim 7, wherein, import is connected in sucking pipe, makes always to supply the refrigeration agent of suction pressure.
9. compressor as claimed in claim 7, wherein, described cylinder assembly comprises: be used for the high-pressure channel that is connected internally to blade groove with shell; With the low-pressure channel that is used for blade groove is connected to import.
10. compressor as claimed in claim 9, wherein, high-pressure channel and low-pressure channel form in the to-and-fro motion scope that is arranged on blade.
11. compressor as claimed in claim 7, wherein, described cylinder assembly comprises: cylinder, and described cylinder has annular shape; With a plurality of bearings, described a plurality of bearings are arranged on the upside and the downside place of cylinder, are used to form the inner space of sealing,
Wherein, described cylinder comprises: low-pressure channel, described low-pressure channel are formed between blade groove and the import; And high-pressure channel, described high-pressure channel is formed on the opposite sides of low-pressure channel, to be connected to blade groove.
12. compressor as claimed in claim 7, wherein, described cylinder assembly comprises: cylinder, and described cylinder has annular shape; With a plurality of bearings, described a plurality of bearings are arranged on the upside and the downside place of cylinder, are used to form the inner space of sealing,
Wherein, described cylinder comprises: low-pressure channel, described low-pressure channel are formed between blade groove and the import; And high-pressure channel, described high-pressure channel is formed on a bearing place in described a plurality of bearing, to be connected to blade groove.
13. compressor as claimed in claim 9, wherein, the section area of high-pressure channel is greater than the section area of low-pressure channel or identical with the section area of low-pressure channel.
14. compressor as claimed in claim 7, wherein, import is connected to compression volume, makes selectively to supply the refrigeration agent of suction pressure or head pressure according to the operating mode of compressor.
15. compressor as claimed in claim 14, wherein, described cylinder assembly comprises: low-pressure channel, described low-pressure channel are used for suction pressure is applied to a side surface of blade; And high-pressure channel, described high-pressure channel is used for blade groove is connected to import, thereby head pressure is applied on the opposite side surface of blade.
16. compressor as claimed in claim 15, wherein, high-pressure channel and low-pressure channel form in the to-and-fro motion scope that is arranged on blade.
17. compressor as claimed in claim 15, wherein, described cylinder assembly comprises: cylinder, and described cylinder has annular shape; With a plurality of bearings, described a plurality of bearings are arranged on the upside and the downside place of cylinder, are used to form the inner space of sealing,
Wherein, described cylinder comprises: low-pressure channel, described low-pressure channel are formed between blade groove and the import; And high-pressure channel, described high-pressure channel is formed on the opposite sides of low-pressure channel, to be connected to blade groove.
18. compressor as claimed in claim 15, wherein, described cylinder assembly comprises: cylinder, and described cylinder has annular shape; With a plurality of bearings, described a plurality of bearings are arranged on the upside and the downside place of cylinder, are used to form the inner space of sealing,
Wherein, described cylinder comprises: low-pressure channel, described low-pressure channel are formed between blade groove and the import; And high-pressure channel, described high-pressure channel is formed on a bearing place in described a plurality of bearing, to be connected to blade groove.
19. compressor as claimed in claim 7, wherein, described mode switching unit comprises:
Vane room, described vane room is connected in the outer end of blade groove, and and the seal space of shell be separated; And
The back pressure converting unit, described back pressure converting unit is connected in vane room, is used for selectively suction pressure or head pressure being fed to vane room according to the operating mode of compressor.
20. compressor as claimed in claim 7, wherein, described mode switching unit comprises:
The refrigeration agent converting unit, described refrigeration agent converting unit is connected in the import of cylinder assembly, is used for selectively the refrigeration agent of suction pressure or head pressure being fed to according to the operating mode of compressor the compression volume of described cylinder assembly;
Vane room, described vane room is connected in the outer end of blade groove, and and the seal space of shell be separated; And
The back pressure converting unit, described back pressure converting unit is connected in vane room, is used for selectively suction pressure or head pressure being fed to vane room according to the operating mode of compressor.
21. compressor as claimed in claim 7, wherein, described mode switching unit comprises:
The refrigeration agent converting unit, described refrigeration agent converting unit is connected in the import of described cylinder assembly, is used for selectively the refrigeration agent of suction pressure or head pressure being fed to according to the operating mode of compressor the compression volume of described cylinder assembly; And
Vane limits unit, described vane limits unit are arranged on the place, outer end of the blade groove of the seal space that is connected to shell, are used to limit described blade.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020060114770A KR100795958B1 (en) | 2006-11-20 | 2006-11-20 | Modulation type rotary compressor |
| KR1020060114770 | 2006-11-20 | ||
| US60/908,034 | 2007-03-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101187373A true CN101187373A (en) | 2008-05-28 |
| CN100564882C CN100564882C (en) | 2009-12-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007101485601A Expired - Fee Related CN100564882C (en) | 2006-11-20 | 2007-08-29 | Variable capacity rotary compressor |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR100795958B1 (en) |
| CN (1) | CN100564882C (en) |
| ES (1) | ES2554643T3 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101000054B (en) * | 2006-12-19 | 2013-03-27 | 广东美芝制冷设备有限公司 | Rotating type compressor sliding vane controlling apparatus and controlling method and application thereof |
| US8651841B2 (en) | 2008-08-05 | 2014-02-18 | Lg Electronics Inc. | Rotary compressor with improved connection |
| CN103629115A (en) * | 2012-08-22 | 2014-03-12 | 上海日立电器有限公司 | Inclined blade groove structure of rolling rotor compressor |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN105673504A (en) * | 2016-03-21 | 2016-06-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and cylinder assembly thereof |
| CN107917078A (en) * | 2017-11-08 | 2018-04-17 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of transfiguration control structure, compressor and its transfiguration control method |
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| KR101409875B1 (en) | 2008-06-24 | 2014-06-20 | 엘지전자 주식회사 | Variable capacity type rotary compressor |
| KR101474445B1 (en) | 2008-06-24 | 2014-12-19 | 엘지전자 주식회사 | Variable capacity type rotary compressor |
| KR101487821B1 (en) * | 2008-07-25 | 2015-01-29 | 엘지전자 주식회사 | Variable capacity type rotary compressor |
| CN104074763B (en) * | 2013-03-26 | 2018-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage enthalpy increasing rotor compressor and there is its air conditioner, Teat pump boiler |
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| JP3762043B2 (en) * | 1997-01-17 | 2006-03-29 | 東芝キヤリア株式会社 | Rotary hermetic compressor and refrigeration cycle apparatus |
| JP4343627B2 (en) | 2003-03-18 | 2009-10-14 | 東芝キヤリア株式会社 | Rotary hermetic compressor and refrigeration cycle apparatus |
| KR100565338B1 (en) * | 2004-08-12 | 2006-03-30 | 엘지전자 주식회사 | Capacity variable type twin rotary compressor and driving method thereof and airconditioner with this and driving method thereof |
| KR100595766B1 (en) | 2005-02-23 | 2006-07-03 | 엘지전자 주식회사 | Modulation apparatus for rotary compressor and airconditioner with this |
| KR100724442B1 (en) * | 2005-05-12 | 2007-06-04 | 엘지전자 주식회사 | Modulation type twin rotary compressor and airconditioner using this |
-
2006
- 2006-11-20 KR KR1020060114770A patent/KR100795958B1/en not_active IP Right Cessation
-
2007
- 2007-07-11 ES ES07013598.3T patent/ES2554643T3/en active Active
- 2007-08-29 CN CNB2007101485601A patent/CN100564882C/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101000054B (en) * | 2006-12-19 | 2013-03-27 | 广东美芝制冷设备有限公司 | Rotating type compressor sliding vane controlling apparatus and controlling method and application thereof |
| US8651841B2 (en) | 2008-08-05 | 2014-02-18 | Lg Electronics Inc. | Rotary compressor with improved connection |
| CN102124229B (en) * | 2008-08-05 | 2014-03-26 | Lg电子株式会社 | Rotary compressor |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN103629115A (en) * | 2012-08-22 | 2014-03-12 | 上海日立电器有限公司 | Inclined blade groove structure of rolling rotor compressor |
| CN103629115B (en) * | 2012-08-22 | 2016-09-28 | 上海日立电器有限公司 | Rolling rotor compressor inclined type blade groove structure |
| CN105673504A (en) * | 2016-03-21 | 2016-06-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and cylinder assembly thereof |
| CN105673504B (en) * | 2016-03-21 | 2018-05-18 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and its cylinder assembly |
| CN107917078A (en) * | 2017-11-08 | 2018-04-17 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of transfiguration control structure, compressor and its transfiguration control method |
| CN107917078B (en) * | 2017-11-08 | 2024-03-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Variable capacity control structure, compressor and variable capacity control method thereof |
| CN108708854A (en) * | 2018-05-29 | 2018-10-26 | 江苏昊科汽车空调有限公司 | The compressor of air conditioner of volume-variable |
| CN108708854B (en) * | 2018-05-29 | 2020-10-13 | 江苏昊科汽车空调有限公司 | Air conditioner compressor with variable capacity |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100564882C (en) | 2009-12-02 |
| ES2554643T3 (en) | 2015-12-22 |
| KR100795958B1 (en) | 2008-01-21 |
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