CN1127625C - Rotary sealed compressor and refrigeration cycle device thereof - Google Patents
Rotary sealed compressor and refrigeration cycle device thereof Download PDFInfo
- Publication number
- CN1127625C CN1127625C CN98103667A CN98103667A CN1127625C CN 1127625 C CN1127625 C CN 1127625C CN 98103667 A CN98103667 A CN 98103667A CN 98103667 A CN98103667 A CN 98103667A CN 1127625 C CN1127625 C CN 1127625C
- Authority
- CN
- China
- Prior art keywords
- blade
- cylinder
- mentioned
- pushing
- enclosing housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/10—Stators
-
- 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
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
In a rotary type closed compressor wherein a high pressure at the interior of a closed case is formed, a compression mechanism part comprises a plurality of cylinders 8A and 8B in which respective eccentric rollers are eccentrically rotatably contained; and vanes 15a and 15b arranged at the cylinders and pressed by a press energizing means that the tip edges thereof make contact with the peripheral surface of the eccentric roller and dividing cylinder chambers 14a and 14b into two chambers along the rotation direction of the eccentric roller. Meanwhile, a coil spring 26 is used as a press energizing means to press one vane and high pressure gas in a closed case is used as a press energizing means to press the other vane.
Description
The present invention relates to the rotary sealed compressor of the configuration example such as the air conditioner refrigeration circulatory system and the refrigerating circulatory device that constitutes refrigeration cycle by this compressor.
The structure of general rotary sealed compressor is that motor and the compression mechanical part that is connected with this motor are housed in enclosing housing, and in a single day the gas that is compressed by above-mentioned compressor structure portion be discharged in the enclosing housing, promptly becomes high pressure conditions in the enclosing housing.
In above-mentioned compressor structure portion, eccentric roller can be contained in the cylinder to free eccentric rotary.And, design blade receiving groove on cylinder, blade can be contained in this groove with being free to slide.Because be subjected to pushing the pushing of force application device, the front-end edge of blade contacts with the side face of above-mentioned eccentric roller.
Therefore, cylinder internal is divided into two chambers by blade along the sense of rotation of eccentric roller.One side room is communicated with suction portion, and another side room is communicated with discharge portion.Connect suction pipe in the suction portion, the opening of discharge portion is in enclosing housing.
Pushing force application device as the above-mentioned blade of pushing normally adopts helical spring as resilient member.The inner peripheral surface of this helical spring end and enclosing housing is joined, and the back side of the other end and blade joins, thereby make the blade that joins with its free end be subjected to the elasticity pushing.Because above-mentioned helical spring is pressed on the blade all the time, so, just begin to produce compression after starting.
And, particularly become the situation of this multi-cylinder rotary hermetic motor compressor of 2 cylinders of main flow recently, the wall thickness attenuation of cylinder monomer, and also be provided with and hold helical spring space, the rigidity of cylinder is descended.Therefore, need to design the external diameter of cylinder bigger, remedying the influence that the cylinder rigidity descends, thereby cause the diameter of enclosing housing to increase.
And, owing to being provided with, each cylinder is used to insert helical spring cross-drilled hole, so, the manufacturing procedure complexity.Because be 2 cylinders, thus need 2 helical springs, thus part cost is increased.After each helical spring insertion operation finishes, must keep it can not eject again, so operation is very complicated.
In addition, because each cylinder is provided with the cross-drilled hole that helical spring inserts usefulness, so, prevent the reduction in strength that blade groove is out of shape.Therefore, when means such as adopting for example arc spot welding were fixedly mounted on each cylinder on the enclosing housing, the stress influence that produces during owing to welding made the blade groove distortion, thereby blade can not be moved smoothly, produces serious consequence.
On the other hand, as be about to replace the new refrigerant that uses more R22 refrigeration agent all the time, the not HFC of chloride atom (fluorohydrocarbon) mix refrigerant will be adopted.
The compression of this HFC mix refrigerant become high pressure-temperature gas and in refrigeration system the circuit compressor, rotational efficienty is good, therefore, the rotary sealed compressor that the most suitable compression performance is high.
And the HFC mix refrigerant, its theoretical refrigerating capacity is stronger than the refrigerating capacity of traditional used refrigeration agent.If particularly refrigeration agent is used instead the refrigeration agent R410A of the high ability of high pressure, just be expected to obtain the efficient higher (COP) than present R22 refrigeration agent.
But if be 1.5 times of R22 in order to make refrigerating capacity that refrigeration agent has and working pressure, and suffered pressure and the R22 of movable parts such as rotatingshaft is suitable, then can only reduce the wall thickness of cylinder.
Yet,, rigidity is descended if reduce the wall thickness of cylinder.If the rigidity of cylinder descends, the precision during part processing just can not get assurance certainly, thereby the distortion when assembling is increased, and makes gas leakage, causes efficient to reduce.
And, on the compressor of 2 cylinders, because the wall ratio single-cylinder type of each cylinder is thin, so, must increase the external diameter of cylinder etc. when using the R410A refrigeration agent, make this problem have more necessity.
The present invention be directed to that above situation carries out, its purpose is to provide a kind of rotary sealed compressor and adopts this rotary sealed compressor to constitute the refrigerating circulatory device of cooling cycle system.This rotary sealed compressor is when being provided with a plurality of cylinders, at least can save the blade pushing member of 1 cylinder, thereby reduce number of spare parts and manufacturing procedure, also not lower the rigidity of cylinder simultaneously, reach miniaturization, thin-walled property, and improved the reliability of equipment.
In order to achieve the above object, the rotary sealed compressor of the 1st scheme, motor and the compression mechanical part that is connected with this motor are housed in enclosing housing, and in a single day the gas that is compressed by above-mentioned compressor structure portion be discharged in the enclosing housing, promptly becomes high pressure conditions in the enclosing housing.It is characterized in that: above-mentioned compressor structure portion is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder, and blade is located on these cylinders, owing to be subjected to pushing the pushing of force application device, the side face of its front end and above-mentioned eccentric roller joins, and will be divided into two chambers in the cylinder along the sense of rotation of eccentric roller; The pushing force application device of above-mentioned pushing blade is the pressurized gas in resilient member and the enclosing housing.
As scheme 2, it is characterized in that: on scheme 1 described rotary sealed compressor, the pressurized gas of employing in the enclosing housing are as the cylinder of above-mentioned pushing force-applying piece, and its external diameter designs forr a short time as the outside dimension of the cylinder of above-mentioned pushing force-applying piece than adopting resilient member.
As scheme 3, it is characterized in that: be on scheme 1 described rotary sealed compressor, adopt that its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing with the cylinder of resilient member as above-mentioned pushing force application device.
As scheme 4, it is characterized in that: be that above-mentioned resilient member is a helical spring on scheme 1～3 described rotary sealed compressor.
As scheme 5, it is characterized in that: be on scheme 1 described rotary sealed compressor, to adopt above-mentioned compressor structure portion to come the high refrigeration agent of compression work pressure ratio R22.
As scheme 6, it is characterized in that: on scheme 1 described rotary sealed compressor, above-mentioned motor is electrically connected with control gear, control gear, being provided with the frequency variator that can change operation frequency, is low-frequency operation in the time of can making starting, is the high frequency operation when head pressure reaches setting pressure.
As scheme 7, it is characterized in that: be on scheme 1 described rotary sealed compressor, adopt that its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing with the cylinder of the pressurized gas in the enclosing housing as above-mentioned pushing force application device.
As scheme 8, it is characterized in that: be on scheme 1 described rotary sealed compressor, the blade of enclosing housing inner high voltage gas pushing will be subjected in the above-mentioned blade, it is the shape of circular arc that its back side forms section, and the radius R v of its circular arc, comparison to the vacuum side of blade setting and as blade receiving groove processing with the little (Rv＜Rc) of the inside radius Rc in withdrawing hole.
As scheme 9, it is characterized in that: be on scheme 1 described rotary sealed compressor, be subjected to the blade of enclosing housing inner high voltage gas pushing in the above-mentioned blade, the digonous part in its back side is carried out the chamfer machining of radius below 1mm.
Refrigerating circulatory device in order to achieve the above object, as scheme 10, rotary sealed compressor wherein, motor and the compression mechanical part that is connected with this motor are housed in enclosing housing, in a single day gas by the compression of above-mentioned compressor structure portion be discharged in the enclosing housing, promptly become high pressure conditions in the enclosing housing, it is characterized in that: its refrigeration cycle is made of rotary sealed compressor, condenser, expansion mechanism and vaporizer, above-mentioned compressor structure portion is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder; And blade is located on these cylinders, owing to be subjected to pushing the pushing of force body, the side face of its front end and above-mentioned eccentric roller joins, and two chambers will be divided in the cylinder along the sense of rotation of eccentric roller, wherein, the pushing force body of at least 1 pushing blade has adopted resilient member, and the pushing force body of at least 1 pushing blade adopts the pressurized gas in the enclosing housing.
By adopting the means of above-mentioned solution problem,, on the pushing blade, also has sufficient reliability even the wall thickness of foregoing invention cylinder is thinner.
Fig. 1 is the profile diagram of the rotary sealed compressor of one embodiment of the invention.
Fig. 2 is the perspective exploded view of middle and upper part embodiment illustrated in fig. 1 cylinder and bottom cylinder.
Fig. 3 (A) is the top cylinder chamber after the starting embodiment illustrated in fig. 1 and the view of bottom cylinder chamber; (B) be the view of compression top cylinder chamber and bottom cylinder chamber when stablizing.
The profile diagram of the rotary sealed compressor of Fig. 4 another embodiment of the present invention.
Fig. 5 (A) is the planimetric map of middle and upper part embodiment illustrated in fig. 4 cylinder; (B) be the planimetric map of top cylinder.
The planimetric map in the another embodiment's of Fig. 6 vacuum side of blade and vertical hole.
Fig. 7 vacuum side of blade of an embodiment again reaches the planimetric map of indulging the hole.Among the figure: 1 ... enclosing housing; 3 ... motor; 2 ... compression mechanical part; 13a, 13b ... eccentric roller; 8A, 80A ... the top cylinder; 8B, 80B ... the bottom cylinder; 26 ... pushing force body (helical spring); 15a, 15b ... blade; 30 ... frequency variator; 40 ... control gear (control device); 24a, 24b ... vertical hole.
Below, the embodiment to rotary sealed compressor describes with reference to accompanying drawing.The cooling cycle system of this compressing mechanism precedent such as air conditioner is the HFC mix refrigerant at this used refrigeration agent.And, in the HFC mix refrigerant, preferably adopt R410A.
This R410A is mixed respectively to account for 50% weight ratio by difluoromethane (R32) and pentafluoroethane (R125).
As shown in Figure 1, rotary sealed compressor is provided with enclosing housing 1.In this enclosing housing 1, the bottom is provided with the said compression mechanical part 2 in back, and top is provided with motor 3.Connect by rotatingshaft 4 between compression mechanical part 2 and the motor 3.
Above-mentioned motor 3 is connected with the frequency variator 30 that can change operation frequency, simultaneously, is electrically connected with control device 40 by frequency variator 30, and this control section 40 is control gear of control frequency variator 30.
Above-mentioned compressor structure portion 2 disposes 2 cylinder 8A, 8B in the bottom of rotatingshaft 4 up and down by dividing plate 7.Because the refrigeration agent that this cylinder 8A, 8B use is the R410A high-pressure refrigerant, so the hot conveying capacity of unit volume is big.Therefore, its wall thickness tradition uses the cylinder of R22 refrigeration agent thin, is expected to reduce insulation volume.
Main bearing 9 overlaps with the upper surface of said cylinder 8A, and with valve gap a, is fixed on the cylinder 8A by construction bolt 10.Supplementary bearing 11 overlaps with the lower surface of said cylinder 8B, and with valve gap b, is fixed on the cylinder 8B by construction bolt 12.
On the other hand, above-mentioned rotatingshaft 4, intermediate portion and end portion are supported on above-mentioned main bearing 9 and the supplementary bearing 11 free to rotately.And rotatingshaft 4 connects the inside of cylinder 8A, 8B, and with roughly 180 ° phase difference integrally formed 2 eccentric part 4a, 4b. Eccentric part 4a, 4b are positioned at each cylinder 8A, 8B, and at its periphery setting-in roller 13a, 13b.
In each cylinder 8A, 8B, be provided with the blade 15a, the 15b that the 14a of cylinder chamber, 14b are divided into high pressure side and low voltage side.Each blade 15a, 15b are used as the pushing force body of the pushing force application device of narrating later and press the application of force to eccentric roller 13a, 13b thruster.
Two cylinder 8A, 8B are connected with suction pipe 16a, 16b respectively, and the other end of suction pipe collaborates in the outside of enclosing housing 1, and links to each other with storage 17.In addition, in the upper end portion of enclosing housing 1, connect delivery line 18.This delivery line 18 is connected with above-mentioned storage 17 by condenser 19, expansion mechanism 20 and vaporizer 21.Like this, just constituted for example refrigeration cycle of air conditioner.
Below, be elaborated with reference to Fig. 2 countercylinder 8A, 8B and above-mentioned pushing force body.
Be provided with opening portion on top cylinder 8A and bottom cylinder 8B, this opening portion forms the identical 14a of cylinder chamber, the 14b of diameter, and, around the 14a of this cylinder chamber, 14b, be provided with a plurality of erection openings 22 with same pitch diameter ...The erection opening 22 of top cylinder 8A side is a tapped hole, and the erection opening 22 of bottom cylinder 8B side is a through hole.
From the 14a of cylinder chamber, the 14b of each cylinder 8A, cylinder 8B, design blade receiving groove 23a, 23b respectively to radial outside with same width, same length.Because this blade receiving groove 23a, 23b are processed to form by for example broaching, so, the vertical hole 24a, the 24b that withdraw from for broaching tool also be provided with in the end of two receiving grooves.
Only design cross-drilled hole 25 on cylinder 8A, this cross-drilled hole 25 is communicated with the vertical hole 24a of outer circumferential faces and blade receiving groove 23a.Income is as the helical spring 26 of the elastic element of pushing force body in cross-drilled hole 25.The external diameter of this cylinder 8A and the internal diameter of above-mentioned enclosing housing 1 are roughly the same.
Again as shown in Figure 1, the outer peripheral portion of top cylinder 8A is mounted on the internal face of enclosing housing 1.Under this state, an end of above-mentioned helical spring 26 joins with a side wall surface that is received in the blade 15a in the blade receiving groove 23a, and the internal face of the other end and enclosing housing 1 joins.
Above-mentioned helical spring 26 imposes elastic pressure to blade 15a to eccentric roller 13a side.When forming to look squarely for the form of semicircle and with looking squarely, the front-end edge of blade 15a is the eccentric roller 13a perisporium of circle almost fricton-tight resistance the time, no matter how many angle of swing of eccentric roller 13a is, always blade 15a contacts with its retention wire.
Therefore, if eccentric roller 13a carries out eccentric rotary along the inner circle wall of the 14a of cylinder chamber, blade 15a is then along blade receiving groove 23a back and forth movement.
Again as shown in Figure 2, on the cylinder 8A of top, with the pitch diameter greater than above-mentioned erection opening 22 pitch diameters, formation is looked squarely and is forniciform a plurality of gas discharge holes 27 respectively.
And bottom cylinder 8B, its external diameter is littler than the external diameter of top cylinder 8A.In fact, only the minimum outer diameter that erection opening 22 and blade receiving groove 23b can be set need be arranged, and the opening portion that its periphery forms the 14b of cylinder chamber relatively is eccentric.
Can receive blade 15b in above-mentioned blade receiving groove 23b, blade 15b and the blade 15a that is located on the cylinder 8A of top are measure-alike with being free to slide.With the pushing force body of this blade 15b, by cylinder 8A, 8B compress, are discharged to the pressurized gas in the enclosing housing 1 up and down to the eccentric roller 13b thruster pressure application of force.
So when control device 40 passed through frequency variator 30 to motor 3 transmission run signal, rotatingshaft 4 was driven in rotation, eccentric roller 13a, 13b about being located on cylinder 8A, the 8B carry out eccentric rotary in the 14a of cylinder chamber, 14b.
Like that, on the cylinder 8A of top, because blade 15a is pushed by helical spring 26 elasticity usually, therefore, the perisporium of the front-end edge of blade 15a and eccentric roller 13a slides and joins, and will be divided into two-part in the 14a of cylinder chamber shown in Fig. 3 (A).
When the contact position of the rotation contact position of eccentric roller 13a and the 14a of cylinder chamber inner circle wall and blade 15a and eccentric roller roughly in same position, under this state, it is maximum that the spatial volume of the 14a of cylinder chamber reaches.Refrigerant gas promptly as the R410A gas of low pressure HFC mix refrigerant, sucks and is full of the 14a of cylinder chamber from storage 17 by suction pipe 16a.
Eccentric rotary along with eccentric roller 13a, the rotation contact position of eccentric roller 13a on the 14a of cylinder chamber inner circle wall is moved, make the 14a of cylinder chamber from rotating contact position in rotational direction to the cylinder chamber's volume reducing the contact position of blade 15a and eccentric roller.That is, the gas that imports before this in the 14a of cylinder chamber is gradually reduced.
Along with rotatingshaft 4 is rotated further, the capacity of the 14a of cylinder chamber further reduces, and makes the gas of importing be compressed into the pressure of regulation at this, opens not shown expulsion valve then, pressurized gas are entered and is full of enclosing housing 1 by valve gap a.And the pressurized gas that are full of enclosing housing 1 are discharged by the delivery line 18 on enclosing housing top.
In addition, when motor 3 has just started, in the 14a of cylinder chamber, be compressed and enter in the enclosing housing 1 the high pressure air scale of construction seldom, be not complete high pressure conditions in the enclosing housing.
Therefore, on the cylinder 8B of bottom, there are not pressurized gas to the blade 15a pushing application of force.Shown in figure (A), eccentric roller 13b rotates in the 14b of cylinder chamber, and blade 15b takes in the receiving groove 23b fully, and its front-end edge is not given as security on eccentric roller and is projected into cylinder chamber.
We can say that on the 14b of bottom cylinder chamber, eccentric roller 13b only dallies, some compressions of this cylinder chamber all do not have.
When through behind the set time, the amount of the pressurized gas of discharging from the 14b of top cylinder chamber increases, and reaches the condition of high voltage of setting in the enclosing housing 1.Like this, be located at the effect that blade 15b on the cylinder 8B of bottom is subjected to big back pressure, shown in figure (B), blade is subjected to the pushing effect and joins with the perisporium of eccentric roller 13b.
Therefore, even in the 14b of bottom cylinder chamber, also begun foregoing compression.At the 14a of top cylinder chamber, then continue the performance compression.After this, before running stops, owing to keep high pressure in the enclosing housing 1, so the compression work in the 14b of bottom cylinder chamber also will continue.
As shown in Figure 1, the pressurized gas of discharging from enclosing housing 1 by delivery line 18, successively in condenser 19 condensation liquefaction, in expansion mechanism 20 adiabatic expansion, in vaporizer 21, capture the latent heat of vaporization of heat exchange air, thereby reach the effect of refrigeration.And the guiding of the refrigeration agent after evaporation storage 17 carries out gas-liquid separation, and the compression mechanical part 2 from suction pipe 16a, 16b suction compressor carries out above-mentioned circulation again.
In addition, when the time that hope begins the 14b of bottom cylinder chamber to compress shifts to an earlier date, available control device 40 control frequency variators 30, the rotating speed of raising rotatingshaft 4 makes the pressure in the housing rise to setting pressure at short notice during from the running beginning.
On the contrary, when the elapsed time is turned round in the hope postponement, available control device 40 control frequency variators 30, the rotating speed of reduction rotatingshaft 4 during from the running beginning, making the interior pressure of housing rise to setting pressure needs certain hour.And, can also after being projected into action in the 14b of bottom cylinder chamber and finishing, blade 15b improve rotating speed thinking.
The blade 15b of the 14b of bottom cylinder chamber side utilizes in the enclosing housing 1 and the pressure reduction between the 14b of bottom cylinder chamber and outstanding, is positioned at the low voltage side of system before the compression in the 14b of bottom cylinder chamber begins.If but high 0.1 megapascal (MPa) of pressure (MPa) of the pressure ratio cylinder chamber in the housing, then almost the thrust with the helical spring 26 of pushing blade 15a in the 14a of top cylinder chamber is suitable, can make blade 15b outstanding, and can follow rotatablely moving of eccentric roller 13b.
Usually, utilize source power supply (50/60Hz), can produce and make blade 15b to the outstanding pressure of the 14b of bottom cylinder chamber if in the several seconds, utilize variable-frequency power sources to begin at most in 10 seconds from 10Hz.
So the pressurized gas that utilize enclosing housing 1 to the 14b of the bottom cylinder chamber pushing application of force, are fully feasible to blade 15b on the function as the pushing force application device.
By the way, under the condition of running continuation, system stability, the housing internal pressure is to the pushing active force of blade 15b, tens of times of the pushing active force (elastic force) that is located at the helical spring 26 on the cylinder 8A of top are arranged, originally, on function, can not need helical spring, but can increase a few thing amount.
And, on compressor of the present invention, have only 1 cylinder (is top cylinder 8A at this) to produce compression during starting, so its characteristics are that suffered load such as rotatingshaft 4 slide members such as grade reduces half.That is, on this machine that more refrigeration agent is housed of air conditioner,, then cause the damage of each slide member easily if just a large amount of liquid refrigerants are carried out liquid compression in moment suction cylinder chamber when the starting according to service condition.
If adopt structure of the present invention, because the suffered load minimizing of slide member, so, can prevent that member from damaging.And the storage 17 that often uses on this rotary compressor also can remove.
Which kind of situation no matter, at least on the bottom cylinder 8B of the pressurized gas in utilizing enclosing housing 1 as the pushing force application device that blade 15b is pushed the application of force, must not design the cross-drilled hole 25 that is used for inserting helical spring 26, therefore, even the wall thickness of this cylinder, also be expected to improve its rigidity, make the distortion of blade accepting groove 23b drop to minimum degree.
In addition, above-mentioned blade 15b flies out rapidly, is the main cause that produces collision noise between eccentric roller 13b and the blade, so, preferably avoid increasing fast operating frequency.As the means of avoiding the housing internal pressure to rise rapidly, can adopt such method: by control device 40 control frequency variators 30, make the operating frequency of motor 3 when starting less, the housing internal pressure must just reach high pressure conditions through after a while, to slow down the speed of stretching out of blade 15b, afterwards, improve operating frequency again.In addition, slow down the expansion valve that constitutes expansion mechanism 20 throttling action, to open not shown defrost valve etc. also effective.
In the above-described embodiments, top cylinder 8A is provided with helical spring 26 and is mounted on the inner circle wall of enclosing housing 1 as the peripheral part of the pressing device that pushes blade 15a with its top cylinder, and bottom cylinder 8B utilizes the pressing device of the interior pressurized gas of enclosing housing as pushing blade 15b.But the present invention has more than and is limited to this form, also can constitute as following.
That is, constitute rotary sealed compressor as shown in Figure 4.Compare with aforementioned compressor illustrated in fig. 1, as described below, have only the pressing device of top cylinder 80A pushing blade 15a different with it with the pressing device of bottom cylinder 80B pushing blade 15b.
Though the thin bilge construction on the drawing also has a little difference in addition, be to constitute basically fully by same member, so, adopt same label, no longer explanation.And the structure of electrical control and refrigeration cycle is identical with the front, so, in this description will be omitted.
Top cylinder 80A is such form shown in Fig. 5 (A) plane view.That is, formation is as the 14a of cylinder chamber and the circular concentric cylinder body 80a of circular open portion.
In the part of this cylinder body 80a side face, one is prominent establish be roughly fan-shaped, have larger area the 1st 80b of edge portion.And, roughly differing 180 ° place at center with the 1st 80b of edge portion, prominent establishing is roughly the 2nd 80c of edge portion rectangle, that area is little than the 1st edge portion.
The outer circumferential face of the outer circumferential face of above-mentioned the 1st 80b of edge portion and the 2nd 80c of edge portion, concentric with 14a of cylinder chamber and cylinder body 80a, and, form and the enclosing housing 1 interior circular arc that has same radius week.
On cylinder body 80a, be provided with in the 14a of cylinder chamber upper shed and be used to hold the blade receiving groove 23a of blade 15a.And hole 24a is indulged in design on the interface portions of cylinder body 80a and the 1st 80b of edge portion, adds the withdrawing hole in man-hour as blade receiving groove 23a.
In addition, design a plurality of installations with bolts hole 22, be used for main bearing 9 is fixedly mounted on top cylinder 80A by bolt 10 at the assigned position of cylinder body 80a.
Bottom cylinder 80B is such form shown in Fig. 5 (B) plane view.That is, formation is as the 14b of cylinder chamber and the circular concentric cylinder body 80a of circular open portion.In the part of this cylinder body 80a side face, outstanding design is roughly the 80d of edge portion of rectangle.
On cylinder body 80a, design is in the 14b of cylinder chamber upper shed and be used to hold the blade receiving groove 23b of blade 15b.And hole 24b is indulged in design on the boundary of cylinder body 80a and the 80d of edge portion, adds the withdrawing hole in man-hour as blade receiving groove 23b.
And then, at the middle part of this vertical hole 24b design cross-drilled hole 25, be communicated with above-mentioned blade receiving groove 23b.In this cross-drilled hole 25, insert elastic element---helical spring 26 as the pushing force application device.And the end of cross-drilled hole 25 is blocked by lid 28 only shown in Figure 4.
In addition, design a plurality of through holes 22, be used for bottom cylinder 80B and dividing plate 7 and supplementary bearing 11 are fixedly mounted on top cylinder 80A by bolt 12 at the assigned position of cylinder body 80a.
Again as shown in Figure 4, the outer peripheral portion of top cylinder 80A is mounted on the inner circle wall of enclosing housing 1, therefore, though do not draw among the figure, but particularly between the inner circle wall of aforesaid cylinder body 80a, the 1st 80b of edge portion, the 2nd 80c of edge portion and enclosing housing 1, form the space portion that gas is discharged usefulness.
And eccentric roller 13a can be contained in to free eccentric rotary in the 14a of cylinder chamber, and blade 15a is received in the blade receiving groove 23a, owing to utilize pressurized gas in the enclosing housing 1 as the device of this blade of pushing, so, except that blade, there is not the member that other will be packed into.
The rotary sealed compressor of Gou Chenging like this, after motor 3 starting just, in the 14b of bottom cylinder chamber compression and enter in the enclosing housing 1 the high pressure air scale of construction seldom, be not complete high pressure conditions in the enclosing housing.
Therefore, on the cylinder 80A of top, there are not pressurized gas to the blade 15a pushing application of force, though eccentric roller 13a rotates in the 14a of cylinder chamber, but because blade 15a is received in the blade receiving groove 23a fully, its front-end edge is not given prominence in cylinder chamber and is pressed on the roller, so in fact just in idle running, 1 compression of the 14a of this cylinder chamber does not all have eccentric roller 13a.
When through behind the set time,, reach the condition of high voltage of setting in the enclosing housing 1 from the high pressure air scale of construction increase that the 14b of bottom cylinder chamber discharges.At this moment, be located at the effect that blade 15a on the cylinder 80A of top is subjected to big back pressure, blade is subjected to the pushing effect and joins with the perisporium of eccentric roller 13a.
Therefore, in the 14a of top cylinder chamber, also begun foregoing compression.In the 14b of bottom cylinder chamber, then continue the performance compression.After this, before running stops, owing to keep high pressure in the enclosing housing 1, so the compression work in the 14a of top cylinder chamber also will continue.
In addition,, be subjected to the blade 15a of enclosing housing 1 inner high voltage gas pushing application of force effect, the back side of 15b, can be designed to Fig. 6 or form shown in Figure 7 no matter be Fig. 1 or compressor shown in Figure 4.
Earlier begin explanation from Fig. 6, when establishing when being Rc as the processing of blade accepting groove with the radius of vertical hole 24a, the 24b in withdrawing hole, blade 15a, 15b are the shape of circular arc by the back side, the end formation section of indulging the hole side, and the radius of circular arc is Rv.And the radius R v of blade 15a, 15b section circular arc is than the little (Rv＜Rc) of the radius R c in vertical hole.
Particularly, when the blade that utilizes housing internal pressure pushing begins to start, difference to housing internal pressure and this cylinder chamber's pressure reaches the utmost point of 0.1MPa in the short time, owing to interrupted contact takes place between blade front end and the eccentric roller peripheral wall surfaces and between vacuum side of blade and the vertical hole side face, thereby may produce interrupted noise.
If utilize the structure of Fig. 6, being in contact with one another of the front end of blade 15a, 15b yes arc surface also is being in contact with one another of arc surface overleaf, so, can further suppress the generation of interrupted noise.And, do not form breach and damage on the blade of employing fragility material, the cylinder, can prevent blade and cylinder interlock etc.
Below, Fig. 7 is described.At this, the radius of vertical hole 24a, 24b can be the radius of regulation.But, be the circular arc part of radius below 1mm with blade 15a, the digonous partial design in the 15b back side.
Therefore, owing to be being in contact with one another of arc surface at the back side of blade 15a, 15b, so, the generation of interrupted noise can further be suppressed.And, do not form breach and damage on the blade of employing fragility material, the cylinder, can prevent blade and cylinder interlock etc.
In addition, be the 2 cylinder type compressors that are provided with 2 cylinder chamber though illustrated the foregoing description relates to, be not limited to this, also applicable to the multi-cylinder rotary hermetic motor compressor more than 2 cylinders.
Such as mentioned above, if the invention of employing scheme 1, because the device of at least 1 pushing blade is the device of employing resilient member and at least 1 pushing blade is the pressurized gas in adopting enclosing housing, so, reduced and adopted the number of spare parts of pressurized gas, played the effect of simplifying processing as the cylinder side of blade pressing device.
If the invention of employing scheme 2 then can be removed the blade pushing of at least one side's cylinder and use resilient member, thereby be expected to dwindle the setting outside dimension of cylinder.
If the invention of employing scheme 3 is expected to simplify the assembling of compression mechanical part part.
If the invention of employing scheme 4 can be shortened the trench length of holding blade, can dwindle the external diameter of cylinder like this.
If the invention of employing scheme 5 can be used the such high-pressure refrigerant of HFC mix refrigerant, particularly R410A.
If the invention of employing scheme 6 with the cylinder side of pressurized gas as the blade pressing device, can be eliminated the collision noise of blade and cylinder.
If the invention of employing scheme 7 is expected to simplify the assembling of compression mechanical part part.
If the invention of employing scheme 8 and scheme 9, because blade and cylinder are to touch along slipping, so, can suppress the generation of interrupted noise.
If the invention of employing scheme 10 is expected to reduce in the cooling cycle system, the particularly quantity of compressor structural components, and minimizing assembling procedure.
Claims (10)
1, a kind of rotary sealed compressor, this compressor is equipped with motor and the rotary compressor structure portion that is connected with this motor in enclosing housing, in a single day gas by the compression of above-mentioned compressor structure portion be discharged in the enclosing housing, promptly become high pressure conditions in the enclosing housing, it is characterized in that: above-mentioned compressor structure portion is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder, and blade is located in these cylinders, owing to be subjected to pushing the pushing of force application device, the side face of its front end and above-mentioned eccentric roller joins, and will be divided into two chambers in the cylinder along the sense of rotation of eccentric roller; The pushing force application device of above-mentioned pushing blade is the pressurized gas in resilient member and the enclosing housing.
2, rotary sealed compressor as claimed in claim 1.It is characterized in that: adopt the interior pressurized gas of enclosing housing to design forr a short time as the cylinder outside dimension of above-mentioned pushing force application device than adopting resilient member as the cylinder external diameter of above-mentioned pushing force application device.
3, rotary sealed compressor as claimed in claim 1 is characterized in that: adopt the cylinder of resilient member as above-mentioned pushing force application device, its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing.
4, as each described rotary sealed compressor of claim 1～3, it is characterized in that: above-mentioned resilient member as the pushing force application device is a helical spring.
5, rotary sealed compressor as claimed in claim 1 is characterized in that: the high refrigeration agent of the compression work pressure ratio R22 of above-mentioned compressor structure portion.
6, rotary sealed compressor as claimed in claim 1, it is characterized in that: above-mentioned motor is electrically connected with frequency variator that can change operation frequency and control gear, utilize control gear, be low operating frequency in the time of can making starting, and be high operating frequency when head pressure rises to setting pressure.
7, rotary sealed compressor as claimed in claim 1 is characterized in that: adopt the cylinder of the interior pressurized gas of enclosing housing as above-mentioned pushing force application device, its peripheral part is mounted on the inner circle wall of above-mentioned enclosing housing.
8, rotary sealed compressor as claimed in claim 1, it is characterized in that: will be subjected to the blade of enclosing housing inner high voltage gas pushing in the above-mentioned blade, it is the shape of circular arc that its back side forms section, and its circular arc radius R v than to the vacuum side of blade setting and as the processing of blade receiving groove with the little (Rv＜Rc) of the inside radius Rc in withdrawing hole.
9, rotary sealed compressor as claimed in claim 1.It is characterized in that: be subjected to the blade of enclosing housing inner high voltage gas pushing in the above-mentioned blade, the digonous part in its back side is carried out the chamfer machining of radius below 1mm.
10, a kind of refrigerating circulatory device, rotary sealed compressor wherein, motor and the rotary compressor structure portion that is connected with this motor are housed in enclosing housing, and in a single day the gas that is compressed by above-mentioned compressor structure portion be discharged in the enclosing housing, promptly becomes high pressure conditions in the enclosing housing; It is characterized in that: its refrigeration cycle is made of rotary sealed compressor, condenser, expansion mechanism and vaporizer,
The above-mentioned compressor structure portion of rotary sealed compressor is provided with a plurality of cylinders and blade, wherein, eccentric roller is housed to free eccentric rotary in each cylinder, and blade is located on these cylinders, owing to be subjected to pushing the pushing of force body, the side face of its front end and above-mentioned eccentric roller joins, and will be divided into two chambers in the cylinder along the sense of rotation of eccentric roller;
The pushing force body of at least 1 pushing blade is to adopt resilient member, and the pushing force body of at least 1 pushing blade adopts the pressurized gas in the enclosing housing.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6478/97 | 1997-01-17 | ||
| JP647897 | 1997-01-17 | ||
| JP6478/1997 | 1997-01-17 | ||
| JP149153/1997 | 1997-06-06 | ||
| JP149153/97 | 1997-06-06 | ||
| JP14915397A JP3762043B2 (en) | 1997-01-17 | 1997-06-06 | Rotary hermetic compressor and refrigeration cycle apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1190160A CN1190160A (en) | 1998-08-12 |
| CN1127625C true CN1127625C (en) | 2003-11-12 |
Family
ID=26340632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98103667A Expired - Fee Related CN1127625C (en) | 1997-01-17 | 1998-01-17 | Rotary sealed compressor and refrigeration cycle device thereof |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3762043B2 (en) |
| KR (1) | KR100299590B1 (en) |
| CN (1) | CN1127625C (en) |
| TW (1) | TW360753B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100408859C (en) * | 2003-11-19 | 2008-08-06 | 三菱电机株式会社 | Double cylinder closed rotary compressor and refrigerating air-conditioning device |
| CN100516531C (en) * | 2004-01-22 | 2009-07-22 | 三菱电机株式会社 | Double cylinder rotary compressor |
Families Citing this family (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100351150B1 (en) * | 2000-04-25 | 2002-09-05 | 엘지전자주식회사 | Enclosed compressor |
| KR100471992B1 (en) * | 2001-11-20 | 2005-03-08 | 기아자동차주식회사 | assembly having a rotor in a vehicles |
| JP2004245073A (en) * | 2003-02-12 | 2004-09-02 | Matsushita Electric Ind Co Ltd | Electric compressor |
| 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 |
| TW200530509A (en) * | 2004-03-15 | 2005-09-16 | Sanyo Electric Co | Multicylinder rotary compressor and compressing system and refrigerating unit with the same |
| KR100758403B1 (en) * | 2004-06-11 | 2007-09-14 | 도시바 캐리어 가부시키 가이샤 | Hermetic rotary compressor |
| TWI363137B (en) * | 2004-07-08 | 2012-05-01 | Sanyo Electric Co | Compression system, multicylinder rotary compressor, and refrigeration apparatus using the same |
| JP2006022723A (en) * | 2004-07-08 | 2006-01-26 | Sanyo Electric Co Ltd | Compression system and refrigerating apparatus using the same |
| JP2006022766A (en) * | 2004-07-09 | 2006-01-26 | Sanyo Electric Co Ltd | Multi-cylinder rotary compressor |
| TW200619505A (en) * | 2004-12-13 | 2006-06-16 | Sanyo Electric Co | Multicylindrical rotary compressor, compression system, and freezing device using the compression system |
| WO2007023904A1 (en) * | 2005-08-25 | 2007-03-01 | Toshiba Carrier Corporation | Hermetic compressor and refrigeration cycle device |
| KR100727881B1 (en) | 2006-03-20 | 2007-06-14 | 삼성전자주식회사 | Variable capacity rotary compressor |
| KR100795958B1 (en) * | 2006-11-20 | 2008-01-21 | 엘지전자 주식회사 | Modulation type rotary compressor |
| JP5005579B2 (en) * | 2008-02-27 | 2012-08-22 | 東芝キヤリア株式会社 | Hermetic compressor and refrigeration cycle apparatus |
| JP5366856B2 (en) * | 2010-02-17 | 2013-12-11 | 三菱電機株式会社 | Vane rotary type fluid apparatus and compressor |
| CN103189653B (en) * | 2010-12-24 | 2015-09-23 | 东芝开利株式会社 | Multi-cylinder rotary compressor and refrigerating circulatory device |
| JP2014070596A (en) * | 2012-09-28 | 2014-04-21 | Fujitsu General Ltd | Rotary compressor |
| JP2016106194A (en) * | 2013-03-27 | 2016-06-16 | 東芝キヤリア株式会社 | Multiple cylinder rotary compressor and refrigeration cycle apparatus |
| AU2013386506B2 (en) | 2013-10-31 | 2016-01-28 | Guangdong Meizhi Compressor Co., Ltd. | Rotary Compressor and Refrigerating Cycle Device |
| CN103775357A (en) * | 2014-01-06 | 2014-05-07 | 广东美芝制冷设备有限公司 | Rotating compressor |
| CN104912599A (en) * | 2014-05-16 | 2015-09-16 | 摩尔动力(北京)技术股份有限公司 | Round cylinder multistage fluid mechanism, and apparatus comprising mechanism |
| CN110332114A (en) * | 2019-06-10 | 2019-10-15 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor pump structure, assembly method and rotor compressor |
| JPWO2023152799A1 (en) * | 2022-02-08 | 2023-08-17 |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86104225A (en) * | 1985-10-25 | 1987-04-29 | 特库姆塞制品公司 | Blade groove has the rotary compressor of pressure ditch |
| CN1118041A (en) * | 1994-08-24 | 1996-03-06 | 东芝株式会社 | Rotative compressor |
| US5542831A (en) * | 1995-05-04 | 1996-08-06 | Carrier Corporation | Twin cylinder rotary compressor |
| CN1138365A (en) * | 1994-10-31 | 1996-12-18 | 大金工业株式会社 | Rotary compressor and refrigerating apparatus |
| US5586876A (en) * | 1995-11-03 | 1996-12-24 | Carrier Corporation | Rotary compressor having oil pumped through a vertical drive shaft |
-
1997
- 1997-06-06 JP JP14915397A patent/JP3762043B2/en not_active Expired - Fee Related
- 1997-11-06 TW TW086116548A patent/TW360753B/en not_active IP Right Cessation
- 1997-12-03 KR KR1019970065482A patent/KR100299590B1/en not_active IP Right Cessation
-
1998
- 1998-01-17 CN CN98103667A patent/CN1127625C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86104225A (en) * | 1985-10-25 | 1987-04-29 | 特库姆塞制品公司 | Blade groove has the rotary compressor of pressure ditch |
| CN1118041A (en) * | 1994-08-24 | 1996-03-06 | 东芝株式会社 | Rotative compressor |
| CN1138365A (en) * | 1994-10-31 | 1996-12-18 | 大金工业株式会社 | Rotary compressor and refrigerating apparatus |
| US5542831A (en) * | 1995-05-04 | 1996-08-06 | Carrier Corporation | Twin cylinder rotary compressor |
| US5586876A (en) * | 1995-11-03 | 1996-12-24 | Carrier Corporation | Rotary compressor having oil pumped through a vertical drive shaft |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100408859C (en) * | 2003-11-19 | 2008-08-06 | 三菱电机株式会社 | Double cylinder closed rotary compressor and refrigerating air-conditioning device |
| CN100516531C (en) * | 2004-01-22 | 2009-07-22 | 三菱电机株式会社 | Double cylinder rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3762043B2 (en) | 2006-03-29 |
| TW360753B (en) | 1999-06-11 |
| KR19980070128A (en) | 1998-10-26 |
| KR100299590B1 (en) | 2002-01-17 |
| CN1190160A (en) | 1998-08-12 |
| JPH10259787A (en) | 1998-09-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1127625C (en) | Rotary sealed compressor and refrigeration cycle device thereof | |
| CN1219982C (en) | Turbine compressor | |
| US20060057012A1 (en) | Scroll compressor having function of preventing outflow of lubrication oil | |
| JPH1182331A (en) | Scroll compressor | |
| JP2005299653A (en) | Rolling piston and rotary compressor gas leakage preventing device equipped therewith | |
| CN101052808A (en) | Capacity varying type rotary compressor | |
| CN1135300C (en) | Rotary compressor, refrigerating circulation and ice house using same | |
| US20060093506A1 (en) | Scroll compressor | |
| US20050152792A1 (en) | Compressor | |
| EP1662146A1 (en) | Rotary fluid machine | |
| CN1178872A (en) | Volumetric liquid machinery | |
| CN110714921A (en) | Linear compressor | |
| US6663363B2 (en) | Driving pin structure for scroll compressor | |
| CN1607332A (en) | Variable capacity rotary compressor | |
| CN1576592A (en) | Variable capacity rotary compressors | |
| CN1598322A (en) | Variable capacity rotary compressor | |
| JP2008121481A (en) | Scroll fluid machine | |
| CN114026328A (en) | Scroll compressor and air conditioner using the same | |
| US20050063837A1 (en) | Hermetic scroll compressor | |
| JP2003269335A (en) | Rotary compressor | |
| JP7493627B2 (en) | Two-Stage Scroll Compressor | |
| KR102182171B1 (en) | Scroll compressor | |
| JP2004100660A (en) | Scroll compressor | |
| JP4923954B2 (en) | Compressor | |
| JPH1082378A (en) | Compressor for refrigerator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20031112 Termination date: 20140117 |