CN1769710A - Apparatus for changing capacity of multi-stage rotary compressor - Google Patents
Apparatus for changing capacity of multi-stage rotary compressor Download PDFInfo
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- CN1769710A CN1769710A CNA2005100849743A CN200510084974A CN1769710A CN 1769710 A CN1769710 A CN 1769710A CN A2005100849743 A CNA2005100849743 A CN A2005100849743A CN 200510084974 A CN200510084974 A CN 200510084974A CN 1769710 A CN1769710 A CN 1769710A
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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
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A multi-stage compressor with variable capacity comprises: a first cylinder provided with a first suction and a first discharge port, and divided into a first suction chamber and a first compression chamber by a first rolling piston which orbits and a first vane which makes a linear movement in contact with the first rolling piston; a second cylinder provided with a second suction port and a second discharge port, and divided into a second suction chamber and a second compression chamber by a second rolling piston which orbits and a second vane which makes a linear movement in contact with the second rolling piston; a middle bearing inserted between the first cylinder and the second cylinder, having a bypass hole to allow communication between the compression chambers of the first cylinder and the second cylinder, and having a valve hole for communication in the middle of the bypass hole; a sliding valve slidingly coupled to the valve hole of the middle bearing, and selectively opening or closing the bypass hole; and a pressure switching unit for selectively supplying discharge pressure to one side of the sliding valve, thereby changing a capacity using all the plural compression units, and obtaining power saving effect suitable for the saving mode.
Description
Technical field
The present invention relates to a kind of rotary compressor that carries out multistage compression, especially relate to a kind of multi-stage rotary compressor that can use whole compression units to reach optimal compression efficiency.
Background technique
Compressor is a kind of from come pressurized air, refrigerant gas or other special gas to come boost pressure and at industrial widely used device such as the power generator received energy of motor.According to how to compress, compressor can be divided into positive displacement compressor and turbocompressor.Positive displacement compressor compresses by such compression method, and pressure reduces to increase by volume in this method; And turbocompressor is converted into pressure energy by the kinetic energy with gas and compresses.
Be generally used for air bells conditioner as a kind of rotary compressor of positive displacement compressor such as air conditioner etc.In order to adapt to the needs that make air conditioner have various functions, need to change the rotary compressor of its capacity at present.
Rotary compressor uses the refrigeration agent that contains CFC-base chlorine.Yet, many allly know that such refrigeration agent can cause the destruction of ozonosphere, thereby can cause global warming.As a result, the use of this refrigeration agent is subjected to the restriction of law, and the alternative refrigerant with respect to existing refrigeration agent has been carried out extensive studies.Carbon dioxide can be expected as a kind of alternative refrigerant.And global warming causes improved problem of device energy efficiency and the problem that existing refrigeration agent is substituted.
Certainly, compressor is considered to the core of refrigeration system, and maximum misgivings are how to can be used in the existing compressor under the situation that does not produce performance loss for the harmless alternative refrigerant of grobal environment.
Have a kind of multi-stage rotary compressor with a plurality of compression units, wherein compression unit can change its capacity and use alternative refrigerant.
Fig. 1 shows the sectional view of an example of traditional multi-stage rotary compressor.
As shown in the figure, traditional multi-stage rotary compressor comprises: two sucking pipes 30 communicating with each other and the housing 1 of 31 and outlet pipes 40 are installed; Be installed in housing 1 upside and contain stator 3 and the electric motor units 2 of rotor 4, be used to produce rotating force; And first compression unit 10 and second compression unit 20 that are installed in housing 1 downside upper and lower, they come compressed refrigerant according to the rotating force that is produced by electric motor units 2 by running shaft 5 respectively.
One be used for from the cistern 6 that the refrigeration agent that sucks is isolated the refrigeration agent of liquefaction be installed between sucking pipe 30 and 31 and compression unit 10 and 20 between.First sucking pipe 30 is sent refrigeration agent into first cylinder 11 by linking to each other with first suction port 17, and second sucking pipe 31 is sent refrigeration agent into second cylinder 21 by linking to each other with second suction port 27.
First compression unit 10 comprises: one ringwise and be installed in first cylinder 11 of housing 1 inside; Upper bearing (metal) 12 and intermediate bearing 13 cover the both sides up and down of first cylinder 11, form first inner space 19 together, and at radial and axial direction upper support running shaft 5; First rolling piston 14 that is rotatably connected with the last eccentric part of running shaft 5, and its in first inner space 19 of first cylinder 11 moving (orbit) thus compressed refrigerant; The first blade (not shown) that links to each other with first cylinder is removable in the radial direction, thereby can contact with the external peripheral surface of first rolling piston 14, and first blade is divided into first suction chamber and first pressing chamber with first inner space 19 of first cylinder 11; And one link to each other with first exhaust port, 16 front ends that are arranged at upper bearing (metal) 12 and to open or to close first expulsion valve 15 of first exhaust port 16, is used to control the discharge of refrigerant gas.
Second compression unit 20 comprises: one ringwise and be installed in second cylinder 21 of housing 1 inside, first cylinder, 11 bottoms; Intermediate bearing 13 and lower bearing 22 cover the both sides up and down of second cylinder 21, form second inner space together, and at radial and axial direction upper support running shaft 5; Second rolling piston 23 that rotatably links to each other with the following eccentric part of running shaft, and its moving in second inner space of second cylinder 21 is come compressed refrigerant; The second blade (not shown) that links to each other with second cylinder 21 is removable in radial direction, thereby can contact with the external peripheral surface of second rolling piston 23, and second blade is divided into second suction chamber and second pressing chamber with second inner space 29; And one link to each other with second exhaust port, 26 front ends that are arranged at lower bearing 22 and to open or to close second expulsion valve 24 of second exhaust port 26, is used to control the discharge of refrigerant gas from second pressing chamber.
The operation that below description is had traditional multi-stage rotary compressor of this spline structure.
When the stator 3 of energy being sent into electric motor units 2 and during rotor 4 rotation, running shaft 5 is with rotor 4 rotations, thereby the rotating force of electric motor units 2 is passed to first compression unit 10 and second compression unit 20.Therefore, by rolling piston 14 and 23 and the blade (not shown), refrigerant gas is inhaled into the inner space 19 and 29 of compression unit 10 and 20, and is compressed therein.At this moment, in first compression unit 10 and second compression unit 20, suction, compression and discharge stroke hocket with about 180 differing of degree.
Because the internal diameter of rolling piston and cylinder is contacted with a bit, so conventional multi-stage rotary compressor carries out suction, compression and the discharge of refrigeration agent continuously.In order to produce big load and therefore to obtain big capacity (being called energy model (power mode) hereinafter), compression unit is driven respectively.At this moment, the capacity of compressor is the summation by the refrigeration agent of each compression unit discharge.In order to obtain to produce the energy-saving effect (being called save mode (saving mode) hereinafter) of low capacity owing to the load that reduces, cut off the refrigeration agent that some compression units suck, perhaps blade moves backward and waits by part (piece) and fixes, thereby remove the border between suction chamber and pressing chamber, thus rolling piston not compressed refrigerant but idle running.
As another method that realizes save mode, the variable-frequency motor that has controlling and driving by use makes velocity variations change volume of the cooling medium as driver element.
The structure of common rotary compressor and the method for driving that is used for it have following problem.
At first, at save mode, blade moves and the problem that has that is fixed is backward in this method, is not desirable such as the particular component of part etc. and the installing space of these parts, and has increased the quantity of manufacture process.
Secondly, because part clashes into blade repeatedly, As time goes on the surface of blade may be damaged, and may cause the integrity problem such as wearing and tearing, foreign matter generation etc.
The 3rd, because variable-frequency motor is normally expensive, therefore use variable-frequency motor may cause the increase of manufacture cost as driver element.Therefore, need to use relatively cheap constant speed motor to realize the change of capacity.
The 4th, when using existing constant speed motor, frequently repeat the ON/OFF operation with the control room temperature.For this reason, because the energy consumption of starting current is very big, quickened the generation of compression unit wearing and tearing like this, and can cause the reduction of compression unit reliability.And because in the ON/OFF of constant speed motor, the variation between setting temperature and the room temperature also is very big, therefore being difficult to control room temperature reaches a gratifying state.
The 5th, when compression unit idle running or refrigeration agent suck when being prevented from, some compression units use at all, have so also reduced the efficient of compressor.
Summary of the invention
Therefore, an object of the present invention is to provide a kind of multi-stage rotary compressor, it can use whole compression units to make the compression efficiency maximization, changes the capacity in the operation and reduce the energy of consumption and the wearing and tearing between parts.
In order to realize these and other advantage of the present invention and according to purpose of the present invention, here do and specialize and briefly description, a kind of device that is used to change the multistage compressor capacity that provides, comprise: be provided with first cylinder of first suction port and first exhaust port, this first cylinder is divided into first suction chamber and first pressing chamber by first rolling piston of moving with first blade of doing straight line motion and contact with first rolling piston; Be provided with second cylinder of second suction port and second exhaust port, this second cylinder is divided into second suction chamber and second pressing chamber by second rolling piston of moving with second blade of doing straight line motion and contact with second rolling piston; Insert the intermediate bearing between first cylinder and second cylinder, this intermediate bearing has the by-pass hole that is communicated with between the pressing chamber that makes first cylinder and second cylinder, and intermediate bearing has and is used for the valve opening that is communicated with by-pass hole middle part; Be slidably connected to the guiding valve of the valve opening of intermediate bearing, it can open or close by-pass hole selectively; And the pressure switch unit that is used for selectively head pressure being sent into guiding valve one side.
By below in conjunction with the accompanying drawing detailed description of the invention, aforementioned and other purpose, characteristics, aspect and advantage of the present invention will become more obvious.
Description of drawings
Accompanying drawing provides further to be understood of the present invention, incorporates and form the part of specification into.Embodiment shown in the present invention with specification in order to illustrate principle of the present invention.
In the accompanying drawings:
Fig. 1 shows the sectional view of an example of traditional multi-stage rotary compressor;
Fig. 2 shows the sectional view according to the multi-stage rotary compressor of first embodiment of the invention;
Fig. 3 shows the sectional view according to first embodiment of the invention by-pass hole closed condition;
Fig. 4 shows the sectional view according to first embodiment of the invention by-pass hole opening state;
Fig. 5 shows the view according to the part excision of the multi-stage rotary compressor of second embodiment of the invention;
Fig. 6 shows the part perspective exploded view according to the critical piece of second embodiment of the invention; And
Fig. 7,8 and 9 shows the sectional view according to the second embodiment of the invention operation.
Embodiment
To describe preferred embodiment of the present invention in detail below, example of the present invention be shown in the accompanying drawing.Identical reference character refer to conventional art in identical parts.
Fig. 2 shows the sectional view according to the multi-stage rotary compressor of first embodiment of the invention.
As shown in the figure, multi-stage rotary compressor according to the present invention comprises: the many sucking pipes 30 that communicate with each other and the housing 1 of 31 and outlet pipes 40 are installed; Be installed in housing 1 upside and produce the electric motor units 2 of rotating force; Be installed in first compression unit 10 and second compression unit 20 of housing 1 downside in multistage mode, be used for when receiving the rotating force that produces by electric motor units 2, coming compressed refrigerants respectively by running shaft 5; With first guiding valve 121 that two compression units 10 and 20 have selection to be communicated with, be used for changing selectively the capacity of compressor; And the first pressure switch unit 160 of selectively higher pressure refrigerant gas being sent into first guiding valve, 121 rear portions, be used for controlling independently the On/Off operation of first guiding valve 121.
Electric motor units 2 comprises: be fixed in the housing 1 and from the stator 3 of outside received energy; And it is inner and can rotor rotated 4 to be arranged in stator 3 with certain air gap, its can with stator 3 interworkings.
First compression unit 10 comprises: be installed in housing 1 inside, form first cylinder 11 of annular, and wherein have first suction port 17 that sucks refrigeration agent; Upper bearing (metal) 12 and intermediate bearing 110 cover the both sides up and down of first cylinder 11, form first inner space 19 together, and at radial and axial direction upper support running shaft 5; With first rolling piston (rolling piston) 14 that the last eccentric part of running shaft 5 rotatably links to each other, it is moving in first inner space 19 of first cylinder 11, thus compressed refrigerant; In the radial direction with first cylinder, the 1 removable first blade (not shown) that links to each other, it can contact with the external peripheral surface phase pressure of first rolling piston 14, and first blade is divided into first suction chamber and first pressing chamber with first inner space 19; And one link to each other with first exhaust port, 16 front ends that are arranged at upper bearing (metal) 12 central parts and to open or to close first expulsion valve 15 of first exhaust port 16, and this valve control refrigerant gas is discharged from first pressing chamber.
The inner space 19 of first cylinder 11 can have the volume identical with the inner space 29 of second cylinder of describing subsequently 21.Yet the volume of inner space 19 also can be different with the volume of inner space 29.
Second compression unit 20 comprises: be installed in first cylinder, 11 bottoms in the housing 1, form second cylinder 21 of annular, and wherein have second suction port 27 that sucks refrigeration agent; Intermediate bearing 110 and lower bearing 22 cover the upper and lower side of second cylinder 21, form second inner space 29 together, and at radial and axial direction upper support running shaft 5; Second rolling piston 23 that rotatably links to each other with the following eccentric part of running shaft 5, it is moving in second inner space 29 of second cylinder 21, thus compressed refrigerant; In the radial direction with second cylinder, the 21 removable second blade (not shown) that link to each other, thereby can contact with the external peripheral surface phase pressure of second rolling piston 23, and second blade is divided into second suction chamber and second pressing chamber with second inner space 29; And link to each other with second exhaust port, 26 front ends that are arranged at lower bearing 22 central parts and to open or to close second expulsion valve 24 of second exhaust port 26, its control refrigerant gas is discharged from second pressing chamber.
At this moment, first blade and second blade are arranged abreast in the horizontal direction, and first suction port 17 and second suction port 27 are arranged equally abreast in the horizontal direction, and first exhaust port 16 and second exhaust port, 26 conllinear ground are arranged in vertical direction.
110 one-tenth discs of intermediate bearing, the heart has the axis hole 111 that running shaft 5 passes therein.By-pass hole 114 penetrates and is formed at intermediate bearing 110 in the axial direction, thereby the inner space 19 and 29 of first cylinder 11 and second cylinder 21 communicates with each other.In more detail, first by-pass hole, 114 preferred such formation, thus the pressing chamber of first and second inner spaces 19 and 29 is interconnected.In the radial direction, first valve opening 112 that is communicated with first by-pass hole 114 is formed at intermediate bearing 110, thereby first guiding valve 121 can be slidingly connected with it.
Pressure switch unit 160 is a kind of pilot valve (pilot valve), and it comprises: the first switch valve shell 165 is provided with high pressure entry 162, low-pressure inlet 163 and conjoint outlet 164; First switch valve 166, be slidingly connected at the first switch valve shell 165 inner and selectively with high pressure entry 162 and common outlet 164 or with low-pressure inlet 163 with export 164 jointly and be connected; First electromagnet 167 is installed in the first switch valve shell, 165 1 sides and moves first switch valve 166 by the energy that applies; And first switch spring 168, when sending into the energy of first electromagnet 167, cut-out is used to reply first switch valve 166.
For the first pressure switch unit 160, high pressure entry 162 is connected to outlet pipe 40 by the first high pressure connecting tube 172, thereby the high pressure that forms in the housing 1 is sent into high pressure entry 162, and by first low-pressure connection tube 173, low-pressure inlet 163 is connected to the middle part of connecting tube 33, thereby low pressure is sent into low-pressure inlet 163, wherein refrigeration agent is sucked the cistern (accumulator) 6 that is used for separating the gas-liquid body from refrigeration agent by connecting tube 33.And first common connecting tube 174 conjoint outlet 164 is connected to the rear side of first guiding valve 121, thereby high pressure air pressure or low pressure gas force feed are gone into rear side.
Sectional view shown in Fig. 3 and 4, part shows the device that is used to change capacity of multi-stage rotary compressor of the present invention.
As shown in the figure, for when first guiding valve 121 cuts out, the prevention projection 123 that is formed on first guiding valve 121 by prevention limits the motion of first guiding valve 121, and a valve stops protruding 116 ladders to be formed on the inboard of first valve opening, 112 inner circumferential surfaces.When first guiding valve 121 was opened first by-pass hole 114, for by stoping this preventions projection 123 to limit the motion of first guiding valve 121, valve guard spare 131 was connected to the valve opening 112 from outside insertion.
Valve guard spare 131 has the intercommunicating pore 133 that links to each other with the common connecting tube 174 of the first pressure switch unit 160, thereby high pressure or low pressure refrigerant gas can be sent into the rear portion of first guiding valve 121.Spring with screw thread (not shown) fixedly is formed on the inner circumferential surface of intercommunicating pore 133 in rank 135, thereby is threaded with the valve spring of describing subsequently 141.
First guiding valve becomes the cylinder bodily form, and its internal side diameter (being called front end hereinafter) seals.External peripheral surface (being called the rear end hereinafter) in first guiding valve, 121 the other end stops projection 123 to form highlightedly, and it is by stoping projection 116 to block the displacement distance that limits first guiding valve 121 by valve.Equally, having the spring that is used for the screw thread (not shown) by the standing valve spring 141 that is threaded fixedly forms at the inner circumferential surface ladder of first guiding valve, 121 front ends on rank 125.
Valve spring 141 can be replaced by other elastic member.
As shown in Figure 4, valve spring 141 is installed in the inside of first guiding valve.Here, valve spring is a coil tension spring (extended spring), this spring is compressed when balancing each other at the pressure that puts on the one side by intercommunicating pore 133 with by the pressure that first by-pass hole 114 puts on its opposite side, opens first by-pass hole 114 thereby first guiding valve 121 is pulled towards the direction of valve guard spare 131.In contrast, as shown in Figure 3, when the pressure that puts on first guiding valve, 121 1 sides by intercommunicating pore 133 when putting on the pressure of its opposite side by first by-pass hole 114, valve spring 141 elongations, thus first guiding valve 121 cuts out first by-pass hole 114.
In Fig. 2, unaccounted reference character 7 is condensers, the 8th, and expansion gear, the 9th, vaporizer and 150 are O shape rings.
Be used to change according to the device of rotary compressor capacity of the present invention is following and operate.
That is, when energy is sent into electric motor units 2, running shaft 5 rotations, and also rotating force is passed to first compression unit 10 and second compression unit 20.Therefore, first rolling piston 14 and second rolling piston, 23 movings, and contact with 29 inner circumferential surface pressure with cylinder 11 and 21 inner spaces 19 respectively.At this moment, each of the first and second blade (not shown) is divided into suction chamber and pressing chamber with inner space 19 and 29.Refrigeration agent sucks by the suction port 17 and 27 that is formed at suction chamber, compresses by the volume-variation in pressing chamber, and enters housing 1 by exhaust port 16 and 26.The refrigeration agent of discharging is injected into the condenser 7 of freeze cycle by outlet pipe 40, and passes through expansion gear 8 and vaporizer 9 successively, sucks the inner space 19 and 29 of each cylinder 11 and 21 then once more by sucking pipe 30 and 31.Repeat such process.
Here, multi-stage rotary compressor operation changes its capacity according to the serviceability of the air regulator that uses it.Energy model and save mode are described respectively below.
At first, when first compression unit 10 and second compression unit 20 were operated respectively, multi-stage rotary compressor was operated at energy model.That is, as shown in Figure 3, the electromagnet 167 (pilot valve) of the first pressure switch unit 160 is opened, thus first switch valve 166 overcome switch spring 168 and make high pressure entry 162 and conjoint outlet 164 between be communicated with.Here, high pressure entry 162 links to each other with the first high pressure connecting tube 172, and the first high pressure connecting tube 172 links to each other with outlet pipe 40.For this reason, by the first common connecting tube 174 and intercommunicating pore 133 head pressure is applied to a side of first guiding valve 121.At this moment, by first by-pass hole 114 cylinder 11 and 21 each internal pressures are applied to first guiding valve, 121 opposite sides, and this internal pressure is less than head pressure.Therefore, valve spring 140 elongations are blocked first by-pass hole 114 thereby move forward first guiding valve 121.Therefore, the refrigerant gas that is sucked into first cylinder 11 does not mix with the refrigerant gas that is sucked into second cylinder 21, but is compressed and drains into housing 1 respectively.
Then, the operation of multi-stage rotary compressor at save mode will be described below.As shown in Figure 4, the electromagnet 167 of the first pressure switch unit 160 is closed to make between low-pressure inlet 163 and the conjoint outlet 164 and is communicated with.Low-pressure inlet 163 links to each other with connecting tube 33 with first low-pressure connection tube 173, thereby low pressure refrigerant flows therein.Such refrigeration agent is sent into the posterior face of first guiding valve 121 by intercommunicating pore 13.When reaching such state, first guiding valve 121 moves backward by the compressive force of valve spring 141, thereby opens first by-pass hole 114.By the unlatching of first by-pass hole 114, the pressing chamber (not shown) of cylinder 11 and 21 inner spaces 19 communicates with each other.First rolling piston 14 and second rolling piston 23 differ layout with 180 degree, volume first compression unit, 10 inner spaces 19, that first by-pass hole 114 is exposed to first pressing chamber wherein and internal pressure and second compression unit, 20 inner spaces 29, that first bypass 114 is exposed to the volume and the internal pressure of second pressing chamber wherein is different.That is, if the pressure of first pressing chamber greater than the pressure of second pressing chamber, therefore refrigeration agent moves to second pressing chamber by first by-pass hole 114 by first pressing chamber, can not be compressed.
From by first rolling piston 14 or go up eccentric part since continuously rotation close the position of first by-pass hole 114, refrigeration agent is bypass no longer, but compression and discharge by first exhaust port 16 in first pressing chamber.That is, because a part of refrigerant bypass and a part are compressed and discharge, so reduced the volume of the cooling medium of discharging.
With the same manner, if the pressure of second pressing chamber greater than the pressure of first pressing chamber, therefore refrigeration agent moves to first pressing chamber by first by-pass hole 114 by second pressing chamber, can not be compressed.Then, close the position of first by-pass hole 114 from second rolling piston 23 or eccentric part, refrigeration agent no longer bypass but be compressed is then discharged.
When each of compression unit 10 and 20 was operated with save mode, refrigeration agent was not to compress with the whole volume of each pressing chamber, and part of refrigerant by high pressure compressed chamber bypass to the low pressure pressing chamber.Only some refrigeration agent is compressed and discharges.Repeat such process, therefore reduced the discharge capacity of refrigeration agent.By this way, can be implemented in the change of capacity in energy model or the save mode.
Below, second embodiment of the present invention will be described.In a second embodiment, be formed with a plurality of by-pass holes, therefore can realize the variation of multistage capacity.
Fig. 5 shows the view according to the part excision of the multi-stage rotary compressor of second embodiment of the invention; And Fig. 6 shows the perspective exploded view according to the intermediate bearing of second embodiment of the invention.Same reference character refer to first embodiment in identical or corresponding parts.
As shown in the figure, 210 one-tenth discs of intermediate bearing, the heart has the axis hole 311 that running shaft 5 passes therein, and second by-pass hole 234 and the 3rd by-pass hole 235 penetrate a side that is formed at blade in the axial direction.
Second by-pass hole 234 and the 3rd by-pass hole 235 in turn form based on the sense of rotation of blade along running shaft.For example, along the sense of rotation of running shaft, second by-pass hole 234 is formed at apart near first blade, 160 degree, and the 3rd by-pass hole can be formed near 240 degree.
Equally, second valve opening 243 and the 3rd valve opening 244 with predetermined depth are communicated with second by-pass hole 234 and the 3rd by-pass hole 235 in radial direction, and second guiding valve 231 and the 3rd guiding valve 232 are slidingly connected with two valve openings respectively.
The second pressure switch unit 211 is a kind of pilot valves, and it comprises: the second switch valve shell 215 that is formed with high pressure entry 212, low-pressure inlet 213 and conjoint outlet 214; Be slidingly connected at the second switch valve 216 of second switch valve shell 215 inside, be used for selectively high pressure entry 212 being connected with common outlet 214 with common outlet 214 or with low-pressure inlet 213; Be installed in second electromagnet 217 of second switch valve shell 215 1 sides, be used for coming mobile second switch valve 216 by the energy that applies; And when the energy of second electromagnet 217 is sent in cut-out, be used to reply the second switch spring 218 of second switch valve 216.
In the second pressure switch unit 211, high pressure entry 212 links to each other with outlet pipe 40 by the second high pressure connecting tube 312, thereby the high pressure that is formed in the housing 1 can be sent into high pressure entry 212, and by second low-pressure connection tube 313, low-pressure inlet 213 links to each other with middle part with refrigeration agent suction pipe 30 and each connecting tube that links to each other 33 of 31, thereby low pressure is sent into low-pressure inlet 213.Equally, conjoint outlet 213 links to each other with the rear portion of second guiding valve 231 by the second common connecting tube 314, thereby can be with high pressure or low pressure gas force feed to rear side.
Pressure switch unit, the 3rd rear portion 221 is a kind of pilot valves, and it comprises: the 3rd switch valve shell 225 that is formed with high pressure entry 222, low-pressure inlet 223 and conjoint outlet 224; Be slidingly connected at the 3rd switch valve 226 of the 3rd switch valve shell 225 inside, be used for selectively high pressure entry 222 or low-pressure inlet 223 being connected with common outlet 224; Be installed in the 3rd electromagnet 227 of the 3rd switch valve shell 225 1 sides, be used for moving the 3rd switch valve 226 by the energy that applies; And when the energy of the 3rd electromagnet 227 is sent in cut-out, be used to reply the 3rd switch spring 228 of the 3rd switch valve 226.
In the 3rd pressure switch unit 221, high pressure entry 222 links to each other with outlet pipe 40 by the 3rd high pressure connecting tube 322, thereby the high pressure that will be formed in the housing 1 is sent into high pressure entry 222, and by the 3rd low-pressure connection tube 323, low-pressure inlet 223 links to each other with middle part with refrigeration agent suction pipe 30 and each connecting tube that links to each other 33 of 31, thereby low pressure is sent into low-pressure inlet 223.Equally, conjoint outlet 224 links to each other with the rear side of the 3rd guiding valve 232 by the 3rd common connecting tube 324, thereby can be with high pressure or low pressure gas force feed to rear side.
As shown in Figure 6, for when second guiding valve 231 cuts out, limit the motion of second guiding valve 231 by the prevention projection 223 that stops second guiding valve 231, a valve stops protruding 236 ladders to be formed on the inside of second valve opening, 243 inner circumferential surfaces.And when second guiding valve 231 was opened, for by stoping this preventions projection 223 to limit moving of second guiding valve 231, valve guard spare (not shown) was connected to the valve opening 243 from outside insertion.
And with the same manner, when the 3rd guiding valve 232 cut out, in order to limit moving of the 3rd guiding valve 232 by the prevention projection 233 that stops the 3rd guiding valve 232, a valve stoped protruding 237 ladders to be formed on the inside of the 3rd valve opening 244 inner circumferential surfaces.And when the 3rd guiding valve 232 was opened, for by stoping this preventions projection 233 to limit moving of the 3rd guiding valve 232, valve guard spare (not shown) was connected to the valve opening 244 from outside insertion.
Identical among the structure of valve guard spare and first embodiment.Equally, as first embodiment, be provided be used for the screw thread by be threaded standing valve spring 241 and 242 spring fixedly the rank (not shown) form at the inner circumferential surface ladder of the second and the 3rd guiding valve 231 and 232 each front end.
The operation and the effect of second embodiment of the invention will be described below.
Fig. 7,8 and 9 is the sectional views that are used to illustrate according to the second embodiment of the invention operation.
At first, energy model is described below.In energy model, compression unit 10 and 20 is operated respectively, thereby discharges the refrigeration agent of 100% flux.As shown in Figure 7, when the electromagnet 217 (pilot valve) of the second pressure switch unit 211 when opening, second switch valve 216 overcome switch spring 218 and make high pressure entry 212 and conjoint outlet 214 between be communicated with.When reaching such state, in each, the head pressure that puts on second guiding valve, 231 1 sides is higher than the internal pressure that puts on second guiding valve, 231 opposite sides, thereby moves forward second guiding valve 231 and block second by-pass hole 234 at cylinder 11 and 21.Equally, open and make when being communicated with between high pressure entry 222 and the conjoint outlet 224 when the electromagnet 227 of the 3rd pressure switch unit 221, the 3rd guiding valve 232 moves forward and blocks the 3rd by-pass hole 235.Therefore, the refrigerant gas that is sucked into the refrigerant gas of first cylinder 11 and is sucked into second cylinder 21 does not mix, but is alternately compressed fully and drain into housing 1.
Then, the operation of multi-stage rotary compressor at save mode will be described below.As shown in Figure 8, when the electromagnet 217 of the second pressure switch unit 211 is opened, second switch valve 216 overcome switch spring 218 and make high pressure entry 212 and conjoint outlet 214 between be communicated with.When reaching such state, the head pressure that puts on second guiding valve, 231 1 sides is higher than cylinder 11 and 21 each internal pressures, cylinder 11 and 21 each internal pressures are the pressure that puts on second guiding valve, 231 opposite sides, thereby move forward second guiding valve 231 and block second by-pass hole 234.In contrast, by the electromagnet 227 of closing the 3rd pressure switch unit 221, low-pressure inlet 223 is communicated with common outlet 224.Because low-pressure inlet 233 links to each other with connecting tube with the 3rd low-pressure connection tube, so low pressure refrigerant flows therein.Such refrigeration agent is sent into the rear portion of the 3rd guiding valve 232 by intercommunicating pore.When reaching such state, the 3rd guiding valve 232 moves backward by the compressive force of valve spring, is communicated with thereby open the 3rd by-pass hole 235 and make between the pressing chamber in cylinder interior space.That is, when being in first embodiment's save mode, refrigeration agent moves to the low pressure pressing chamber by the 3rd by-pass hole 235 by the high pressure compressed chamber, so refrigeration agent can not be compressed.Then, close the position of the 3rd by-pass hole 235 from rolling piston or eccentric part, refrigeration agent is bypass but be compressed and be discharged from no longer.In save mode, refrigeration agent can not compress with the whole volume of each pressing chamber, and by high pressure compressed chamber bypass to the low pressure pressing chamber.Therefore, only some refrigeration agent is compressed and discharges.Repeat such process, therefore reduced the discharge capacity of refrigeration agent.
Then, in order to realize another discharge capacity at save mode, as shown in Figure 9, second by-pass hole 234 is opened and the 3rd by-pass hole 235 is closed by operating the second and the 3rd pressure switch unit 211 and 221.Along the sense of rotation of running shaft 14, second by-pass hole, 234 to the three by-pass holes 235 more approach blade 410,420 (for example second by-pass hole 160 is spent, the 3rd by-pass hole 240 degree).Therefore, when rolling piston or eccentric part are closed second by-pass hole 234 compression and the volume of the cooling medium of discharging greater than the volume of the cooling medium of discharge when the 3rd by-pass hole 235 is closed.Therefore, even also can change the volume of the cooling medium of discharge at save mode.
Certainly, in the same way, by form the variation that three or more by-pass holes can realize multistage capacity at intermediate bearing.
With regard to present description, multi-stage rotary compressor according to the present invention has following effect.
At first, different with blade method mobile backward and that be fixed, the invention has the advantages that does not need special parts and installing space, and has simplified manufacture process.Equally,, therefore can not produce problem, therefore improve reliability such as wearing and tearing, foreign matter generation etc. because do not need to move backward the part that reaches stator blade.
Secondly, even, improved the efficient of motor and compressor and can realize the energy saving effect owing to also all use at a plurality of compression units of save mode.
The 3rd, owing to use cheap constant speed motor to come the change capacity, can reduce manufacture cost.
Because the present invention can implement under the situation that does not break away from spirit of the present invention or essential feature in many ways, it will also be appreciated that above-mentioned embodiment is not limited by any details of aforementioned specification, unless it is dated especially, can very wide in range explanation in the defined spirit and scope of claims, therefore belong to the border of claim and the institute in the scope and change and revise, therefore the equivalent structure of perhaps this border and scope also is contained in the appended claim.
Claims (15)
1. device that is used to change the multistage compressor capacity comprises:
Be provided with first cylinder of first suction port and first exhaust port, this first cylinder is divided into first suction chamber and first pressing chamber by first rolling piston of moving with first blade of doing straight line motion and contact with first rolling piston;
Be provided with second cylinder of second suction port and second exhaust port, this second cylinder is divided into second suction chamber and second pressing chamber by second rolling piston of moving with second blade of doing straight line motion and contact with second rolling piston;
Insert the intermediate bearing between first cylinder and second cylinder, this intermediate bearing has the by-pass hole that is communicated with between the pressing chamber that makes first cylinder and second cylinder, and intermediate bearing has and is used for the valve opening that is communicated with by-pass hole middle part;
Be slidably connected to the guiding valve of the valve opening of intermediate bearing, it opens or closes by-pass hole selectively; And
Be used for selectively head pressure being sent into the pressure switch unit of guiding valve one side.
2. device as claimed in claim 1, the volume in the first cylinder interior space that wherein has first suction chamber and first pressing chamber is different with the volume in the second cylinder interior space with second suction chamber and second pressing chamber.
3. device as claimed in claim 1, wherein first suction port and second suction port are arranged abreast in the horizontal direction, first exhaust port and the second exhaust port conllinear ground are arranged in vertical direction, and first blade and second leaf are arranged abreast in the horizontal direction.
4. device as claimed in claim 1, the by-pass hole that wherein is formed at intermediate bearing is a plurality of.
5. device as claimed in claim 1, wherein the pressure switch unit forms a plurality of.
6. device as claimed in claim 1, wherein the pressure switch unit is a pilot valve.
7. device as claimed in claim 1, wherein differing between first rolling piston and second rolling piston is 180 degree.
8. device as claimed in claim 1, wherein said guiding valve forms the cylinder bodily form, for close valve orifice, its internal diameter be sealing and also its opposite side open wide.
9. device as claimed in claim 8, wherein stop projection to be formed on the end of guiding valve open side, and when the guiding valve closing operation, in order to limit moving of guiding valve by the prevention projection that stops guiding valve, valve is formed on the inner circumferential surface of valve opening with stoping raised step.
10. device as claimed in claim 9, one of them valve guard spare is arranged at the outside of valve opening, thereby when the guiding valve open operation, limits moving of guiding valve by unlimited the bringing in that stops guiding valve.
11. device as claimed in claim 10, one of them elastic member inserts between guiding valve and the valve guard spare.
12. device as claimed in claim 11, wherein this elastic member is a coil tension spring, and when the pressure of guiding valve cylinder side and rear portion pressure balance, elastic member is opened by-pass hole towards valve guard spare pulling guiding valve.
13. device as claimed in claim 1, wherein the pressure switch unit comprises:
Be formed with the first switch valve shell of high pressure entry, low-pressure inlet and conjoint outlet;
Be slidingly connected at the switch valve of switch valve enclosure, it is connected high pressure entry or low-pressure inlet selectively with common outlet;
Be installed in the electromagnet of switch valve shell one side, come the moving switch valve by the energy that applies; And
When the energy of electromagnet is sent in cut-out, be used for the switch spring of reversion switch valve.
14. device as claimed in claim 13, wherein the pressure switch unit is connected with the high pressure connecting tube that links to each other with outlet pipe, thereby high pressure is sent into high pressure entry,
Low-pressure connection tube is connected with suction pipe, thereby low pressure is sent into low-pressure inlet, and
Common connecting tube is connected to the rear portion of guiding valve with conjoint outlet, thereby high pressure or low pressure are sent into.
15. device as claimed in claim 14, wherein low-pressure connection tube is connected to the middle part of connecting tube with low-pressure inlet, refrigeration agent is sucked the cistern that is used for divided gas flow-liquid refrigerant by this connecting tube.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR20040088013 | 2004-11-01 | ||
| KR1020040088013 | 2004-11-01 | ||
| KR1020050004710 | 2005-01-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1769710A true CN1769710A (en) | 2006-05-10 |
| CN100400883C CN100400883C (en) | 2008-07-09 |
Family
ID=36751194
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100849743A Expired - Fee Related CN100400883C (en) | 2004-11-01 | 2005-07-26 | Apparatus for changing capacity of multi-stage rotary compressor |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR100619767B1 (en) |
| CN (1) | CN100400883C (en) |
| DE (1) | DE602005013883D1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102052318A (en) * | 2009-11-04 | 2011-05-11 | 株式会社电装 | Compressor |
| CN101611229B (en) * | 2007-02-28 | 2012-07-04 | 大金工业株式会社 | Rotary compressor |
| CN106322604A (en) * | 2016-07-29 | 2017-01-11 | 广东美的制冷设备有限公司 | Single cooling type air conditioner and control method |
| CN106403342A (en) * | 2016-07-29 | 2017-02-15 | 广东美的制冷设备有限公司 | Single cooling type air conditioner and control method |
| CN109026693A (en) * | 2018-08-31 | 2018-12-18 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
| CN111379705A (en) * | 2020-03-18 | 2020-07-07 | 广东美芝制冷设备有限公司 | Compressor, operation control method of compressor and refrigeration equipment |
| WO2020211450A1 (en) * | 2019-04-17 | 2020-10-22 | 上海海立电器有限公司 | Variable capacity compressor |
| CN112412789A (en) * | 2019-08-23 | 2021-02-26 | 广东美芝制冷设备有限公司 | Compressor and refrigeration cycle device |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5873993U (en) | 1981-11-12 | 1983-05-19 | 三菱電機株式会社 | 2 cylinder rotary compressor |
| JPS6270686A (en) * | 1985-09-20 | 1987-04-01 | Sanyo Electric Co Ltd | Multicylinder rotary compressor |
| JPH01113596A (en) * | 1987-10-27 | 1989-05-02 | Matsushita Electric Ind Co Ltd | Capacity control compressor and control method therefor |
| JP3174202B2 (en) * | 1993-07-22 | 2001-06-11 | 東芝キヤリア株式会社 | Multi-cylinder rotary compressor |
| JP3414797B2 (en) * | 1993-08-12 | 2003-06-09 | 東芝キヤリア株式会社 | Multi-cylinder rotary compressor |
| KR20000021810A (en) * | 1998-09-30 | 2000-04-25 | 구자홍 | Rotary compressor variable in capacity |
| TW568996B (en) * | 2001-11-19 | 2004-01-01 | Sanyo Electric Co | Defroster of refrigerant circuit and rotary compressor for refrigerant circuit |
| KR100466620B1 (en) * | 2002-07-09 | 2005-01-15 | 삼성전자주식회사 | Variable capacity rotary compressor |
| KR20040100078A (en) * | 2003-05-21 | 2004-12-02 | 삼성전자주식회사 | Variable capacity rotary compressor |
-
2005
- 2005-01-18 KR KR1020050004710A patent/KR100619767B1/en not_active IP Right Cessation
- 2005-06-09 DE DE602005013883T patent/DE602005013883D1/en active Active
- 2005-07-26 CN CNB2005100849743A patent/CN100400883C/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101611229B (en) * | 2007-02-28 | 2012-07-04 | 大金工业株式会社 | Rotary compressor |
| CN102052318A (en) * | 2009-11-04 | 2011-05-11 | 株式会社电装 | Compressor |
| CN106322604A (en) * | 2016-07-29 | 2017-01-11 | 广东美的制冷设备有限公司 | Single cooling type air conditioner and control method |
| CN106403342A (en) * | 2016-07-29 | 2017-02-15 | 广东美的制冷设备有限公司 | Single cooling type air conditioner and control method |
| CN109026693A (en) * | 2018-08-31 | 2018-12-18 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
| CN109026693B (en) * | 2018-08-31 | 2023-10-03 | 珠海格力电器股份有限公司 | Pump body assembly, compressor and air conditioner |
| WO2020211450A1 (en) * | 2019-04-17 | 2020-10-22 | 上海海立电器有限公司 | Variable capacity compressor |
| US11384761B2 (en) | 2019-04-17 | 2022-07-12 | Shanghai Highly Electrical Appliances Co., Ltd. | Variable capacity compressor |
| CN112412789A (en) * | 2019-08-23 | 2021-02-26 | 广东美芝制冷设备有限公司 | Compressor and refrigeration cycle device |
| CN112412789B (en) * | 2019-08-23 | 2022-09-06 | 广东美芝制冷设备有限公司 | Compressor and refrigeration cycle device |
| CN111379705A (en) * | 2020-03-18 | 2020-07-07 | 广东美芝制冷设备有限公司 | Compressor, operation control method of compressor and refrigeration equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100400883C (en) | 2008-07-09 |
| KR100619767B1 (en) | 2006-09-11 |
| DE602005013883D1 (en) | 2009-05-28 |
| KR20060038893A (en) | 2006-05-04 |
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