CN101498306B - Rotary compressor - Google Patents
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- CN101498306B CN101498306B CN2008100067148A CN200810006714A CN101498306B CN 101498306 B CN101498306 B CN 101498306B CN 2008100067148 A CN2008100067148 A CN 2008100067148A CN 200810006714 A CN200810006714 A CN 200810006714A CN 101498306 B CN101498306 B CN 101498306B
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Abstract
The invention discloses a rotary type compressor which comprises a shell (1), a cylinder body (2), a rotor (3), a sliding plate (4) and an exhaust valve (7), wherein an air suction hole (6) and an exhaust hole (8) are arranged on the shell (1), rotating central axes of the cylinder body (2) and the rotor (3) are offset into a state that the outer circumferential surface of the rotor (3) is tangential with the inner circumferential surface of the cylinder body (2), the head of the sliding plate (4) is embedded into a cylinder of the cylinder body (2), the main body of the sliding plate (4) extends into a sliding plate groove of the rotor (3), the exhaust valve (7) is arranged on the outer circumference of the rotor (3) and the front of the rotating direction of the sliding plate (4), a cylinder body air inlet (12) which is positioned at the rear of the rotating direction of the sliding plate (4) is arranged on the cylinder body (2), and the sliding plate (4) and an internally tangent point are used for dividing crescent working volume between the inner circumferential surface of the cylinder body (2) and the outer circumferential surface of the rotor (3) into an air inlet cavity and an exhaust cavity.
Description
Technical field
The present invention relates to a kind of air compressor, FLUID TRANSPORTATION pump and refrigeration air conditioner compressor, the synchronous rotary compressor tool of particularly a kind of rotor and cylinder body.
Background technique
The compressor that uses at present has reciprocal compressor, compressor with rolling rotor, slide vane compressor, scroll compressor and helical-lobe compressor etc.Reciprocal compressor is owing to be difficult to the inertial force of balance, and vibration is big, and rotating speed is low, and volume is big.Exist bigger speed of related movement between piston of its motion and the static cylinder body in addition, fretting wear is serious.Air inlet and exhaust valve, piston ring that next is this compressor etc. all belongs to easily damaged parts, and this also is its fatal shortcoming, causes the poor reliability of machine run, and efficient is low.The cylinder body of compressor with rolling rotor is static, and the internal surface contact points of it and rotor moves with very big relative velocity in movement process, also exists very big relative velocity between rotor and the slide plate, and its fretting wear is very serious.The cylinder body of slide vane compressor also is static; Rotor when rotated, slide plate is thrown away from groove by action of centrifugal force, its end is close on the static inner surface of cylinder block; The main shortcoming of this compressor is that the relative moving speed between slide plate and the cylinder body is big; Mechanical friction is serious, produces bigger wearing and tearing and energy loss, so working life and efficient are lower.Although scroll compressor and helical-lobe compressor have overcome the shortcoming of reciprocal compressor, for scroll compressor, quiet dish is actionless; Exist bigger relative velocity between it and the Moving plate, and the complex process machining accuracy is high, and the helical-lobe compressor cylinder body also is static; Rotor moves in cylinder body; Exist bigger relative velocity between them, caused bigger fretting wear, the more important thing is that the machining accuracy high technology is complicated.The compressor of the above-mentioned type all has a common problem, is exactly that fretting wear is serious, energy loss big, leaks big, inefficiency; Or processing technology is complicated, precision is high.Its main factor is: always exist very big relative movement between the parts of static parts and a motion, its fretting wear is big, leakage seriously is inevitable the result.Reciprocal compressor is because the inertial force of motion is difficult to balance, vibration is big, the easily damaged parts life-span is short and poor reliability in addition.Scroll compressor and helical-lobe compressor are then because machining accuracy is high, and complex process causes cost high.
Pct international patent application WO 2005/052373 discloses a kind of rotary compressor, and it comprises a casing, a freely rotating axle bush and a rotor.This casing has some inlets and outlet.This axle bush has some openings longitudinally, and is arranged in this casing.This rotor has 4 slide dampers, and is pressed in prejudicially on this axle bush inner circumferential surface, in this casing, has bearing to carry this rotor, and the inlet of this casing and the sense of rotation of this axle bush are tangent.This rotary compressor working procedure is following: force to rotate down at rotor, above-mentioned 4 slide dampers because of centrifugal force oneself pressing to the axle bush inner circumferential surface, rotor rotates through slide damper drive axle bush like this.
Summary of the invention
The present invention provides a kind of rotor and cylinder body respectively around the rotation of rotating center separately and through single slide plate the cavity between rotor and the cylinder body to be separated be the synchronous rotary compressor in two chambeies that work alone.
Rotary compressor of the present invention comprises casing, cylinder body, rotor, main shaft, slide plate, outlet valve, eccentric mounting, spring bearing, rack bearing; Wherein said casing is provided with intakeport and relief opening; Described cylinder body rotating center axis and described rotor rotating center axis are biased to rotor outer peripheral surface and cylinder body inner peripheral surface inscribe mutually; Described slide plate head is embedded in the cylinder body cylindrical body; In the skateboards slot of slide plate Subject Extension to rotor; Described outlet valve is arranged on the described rotor excircle the place ahead with the sense of rotation of slide plate, and cylinder body is provided with the cylinder body suction port that is positioned at slide plate sense of rotation rear, and name a person for a particular job meniscate swept volume between the external peripheral surface of inner circumferential surface and rotor of cylinder body of described slide plate and said inscribe is mutually separated and is air-inlet cavity and exhaust cavity.Wherein eccentric mounting is tightened to an integral body through bolt and described casing, main shaft through the spring bearing cantilever be supported on the eccentric mounting, the inboard end of main shaft is connected with the centre of rotor axis hole with the keyway cooperation through key.One side shaft of cylinder body is bearing on the casing through rack bearing to the end, and the opposite side axial end portion of cylinder body is through on the rack bearing supporting eccentric mounting.
Described rotor exhaust passage has constituted the exhaust passage with the cylinder body central shaft hole and has communicated, and often is communicated with the relief opening of casing again; Cavity, described cylinder body suction port, air-inlet cavity often are communicated with each other between the intakeport of described casing, casing and the cylinder body.
When the corner of main shaft was β=0, air inlet began to finish with exhaust; When the corner of main shaft was 0＜β, the pressurized gas process began, and the intakeport of rotation is just continuous air-breathing simultaneously; When the corner of main shaft is β=180 when spending, air aspiration cavity in the active chamber and exhaust cavity swept volume equate; When the corner of main shaft is 0＜β＜360 when spending, active chamber is continuous compression process, and when β=ψ; Exhaust begins; We are defined as the exhaust angle with ψ, and at this moment the pressure in the exhaust cavity is greater than the working pressure of peripheral hardware, and outlet valve will be opened automatically; Exhaust this moment begins, and compressed gas is discharged through outlet valve, exhaust passage and relief opening from exhaust cavity.The gas that is compressed in the exhaust cavity is all discharged, and at this moment outlet valve will be closed automatically.When the corner of main shaft is β=360 when spending, promptly main axis rotation is after one week, and rotary compressor of the present invention has been accomplished a work cycle, and at this moment air aspiration cavity is full of by gas.
Rotary compressor of the present invention is for a swept volume; Gas suction, compression and exhaust are in two weeks of rotor, to accomplish; But, air-breathing and compression process hocket simultaneously because being active chamber in the slide plate both sides; Therefore concerning complete machine, remain whenever to circle and just accomplish a work cycle, promptly rotor whenever circles and just accomplishes once air-breathing and exhaust process.So not only machine run is steady, and gas is low at air-breathing and flow velocity relief opening, and flow losses reduce greatly, and its flow losses are about the half the of reciprocal compressor.The compressor of this structure relies on the intakeport of rotation directly air-breathing, need not add Aspirating valves, does not have the air inlet heating phenomena, so volumetric efficiency is high.In addition, the component of rotary compressor of the present invention are few and do not have easily damaged parts, and volume reduces 50-60% than reciprocating compressor, and weight alleviates about 60% approximately, and indicated efficiency improves 30-40% than piston compressor.
The rotor of rotary compressor of the present invention and cylinder body are made up of two cylinders, and the speed of related movement between the two is minimum, and fretting wear reduces greatly, and the leakage of working medium simultaneously also solves quite easily.Because the slide plate quality is very little, the distance of its motion is very short, and therefore the reciprocal inertia force on only slide plate is also very little, can ignore fully, and owing to the inhomogeneous rotatory inertia force unbalance that causes of material, this can be easy to solve on structure fully in addition.The cylinder body of two rotations and rotor are rotating around separately rotating center respectively, therefore do not have unbalanced force separately, so machine run very steadily, vibrates little and noise is low.The morphology of main parts size is a cylinder in addition, so machining accuracy is easy to guarantee, is convenient to utilize high efficiency working machine tool and flow of tissue waterline to produce; Also be easy to assembling and maintenance; Especially the bent axle that does not have eccentric motion, thus can improve output greatly, reduce cost.
Another characteristics of rotary compressor of the present invention are; A swept volume is an air-inlet cavity, is again exhaust cavity, and air-inlet cavity and exhaust cavity are alternately worked again continuously; The component of machine had so both been reduced; Compact structure has increased reliability, has reduced the energy loss that gas caused simultaneously again.
Description of drawings
Fig. 1 is the plan view of rotary compressor first mode of execution of the present invention;
Fig. 2 is that angle of eccentricity is the cross-sectional schematic cross-section of β=0 first mode of execution when spending;
Fig. 3 is that angle of eccentricity is the cross-sectional schematic cross-section of 0＜β, first mode of execution when spending;
Fig. 4 is that angle of eccentricity is the cross-sectional schematic cross-section of β=180 first mode of execution when spending;
Fig. 5 is that angle of eccentricity is ψ＜cross-sectional schematic cross-section of first mode of execution when β exhaust begins;
Fig. 6 is the plan view of rotary compressor second mode of execution of the present invention;
Fig. 7 is the plan view of rotary compressor the 3rd mode of execution of the present invention;
Fig. 8 is the cross-sectional schematic cross-section of rotary compressor the 4th mode of execution of the present invention;
Fig. 9 A, 9B are the schematic representation of a kind of mode of execution of rotary compressor slide plate of the present invention, and wherein Fig. 9 A is a rotary compressor slide plate end view of the present invention, the plan view of Fig. 9 B rotary compressor slide plate of the present invention;
Figure 10 A, 10B are the schematic representation of the another kind of mode of execution of rotary compressor slide plate of the present invention, and wherein Figure 10 A is a rotary compressor slide plate end view of the present invention, the plan view of Figure 10 B rotary compressor slide plate of the present invention;
Figure 11 A, 11B are the schematic representation of rotary compressor rotor of the present invention and cylinder body end surface seal structure, and wherein Figure 11 A is rotary compressor rotor of the present invention and cylinder body end face partial schematic sectional view, Figure 11 B rotary rotor of the present invention and cylinder body end view.
Embodiment
Below in conjunction with accompanying drawing, describe the embodiment of rotary compressor of the present invention in detail.
Fig. 1-5 shows first mode of execution of rotary compressor of the present invention; Wherein Fig. 1 is the plan view of rotary compressor first mode of execution of the present invention; Fig. 2 is that angle of eccentricity is that the central shaft of β=0 first mode of execution when spending is to the vertical cross-section schematic representation; Fig. 3 is that angle of eccentricity is that the central shaft of 0 degree＜β＜180, first mode of execution when spending is to schematic cross section; Fig. 4 is that angle of eccentricity is the schematic cross section of β=180 first mode of execution when spending, and Fig. 5 is the schematic cross section of angle of eccentricity first mode of execution when being ψ＜β.
Shown in Fig. 1-2, first mode of execution of rotary compressor of the present invention comprises casing 1, cylinder body 2, rotor 3, slide plate 4, main shaft 5, intakeport 6, outlet valve 7, relief opening 8, rack bearing 9, eccentric mounting 10, spring bearing 11, cylinder body suction port 12.
Wherein eccentric mounting 10 is tightened to an integral body through bolt and casing 1; Main shaft 5 through spring bearing 11 cantilevers be supported on the eccentric mounting 10; Main shaft 5 inboard ends cooperate with keyway through key and are connected with the central shaft hole of rotor 3, and promptly rotor 3 rotates around main shaft 5 central axis.
Because cylinder body 2 and rotor 3 all are to rotate around separately gyration center, so itself all there is not unbalanced inertial force in cylinder body 2 with rotor 3, its running very steadily.
Shown in Fig. 9 A, 9B, rotary compressor slide plate 4 heads of the present invention are cylindric, its main body is tabular, its slide plate 4 heads are embedded in cylinder body 2 cylindrical bodys, in slide plate 4 Subject Extension to rotor 3 skateboards slot radially.Slide plate 4 cylindric head two ends slightly stretch out slide plate 4 main bodys outside; Slide plate 4 cylindric head two ends extend to respectively in two axial end portions of cylinder body 2; Two gudgeons of radial location when constituting slide plate 4 swings, thus guarantee that slide plate 4 can not skid off in the cylindrical body of cylinder body 2.The length of slide plate 4 main bodys just in time equals the inside axial width of cylinder body 2, and fluid can not be crossed slide plate 4 body rim slits easily like this.Guarantee that simultaneously slide plate 4 vacillates now to the left, now to the right along rotor 3 radial direction, to adapt to the phase difference between cylinder body 2 and the rotor 3.
When motor driving main shaft 5 rotation, rotor 3 rotates around main shaft 5, and rotor 3 drives cylinder bodies 2 servo-actuateds through slide plate 4, but cylinder body 2 is when cylinder body 2 central axis rotate, and when angle of eccentricity is 0 degree＜β＜180 when spending, cylinder body 2 rotation phase are ahead of the corner of rotor 3; When angle of eccentricity is that 180 degree＜β＜360 are when spending; Cylinder body 2 rotation phase lag behind the corner of rotor 3, thus slide plate 4 need vacillate now to the left, now to the right and adapt to the phase difference of cylinder body 2 and rotor 3, simultaneously power is delivered on the cylinder body 2 from rotor 3; And guarantee that angle of eccentricity β is 0 degree, both were zero phase difference when 180 degree, 360 were spent; So it drives cylinder body 2 and rotor 3 do rotation motions fully in the same way, it is identical that they turn over the time in a week, so the present invention also is referred to as synchronous rotary compressor.
When it rotates; The inner circumferential surface of cylinder body 2 is tangent all the time in vertical minimum point with the external peripheral surface of rotor 3; Slide plate 4 and this points of tangency are divided into two different air cavitys with the meniscate swept volume between the external peripheral surface of the inner circumferential surface of cylinder body 2 and rotor 3; Be referred to as air-inlet cavity and exhaust cavity respectively, its whole active chamber that constitutes compressor.But because rotor 3 is different with the turning radius of cylinder body 2 and its gyration center is also different, so when rotating, their contact surface is being made slide relative extremely slowly, but relative velocity is extremely low, greatly reduces friction and wear between the two like this.
In service at rotary compressor of the present invention; Fluid is from the top intakeport 6 entering casings 1 of casing 1 and the cavity between the cylinder body 2, and through the air-inlet cavity between cylinder body suction port 12 entering cylinder bodies 2 and the rotor 3, Fig. 1-5 usefulness arrow shows airintake direction then; As shown in Figure 3; Along with the corner β of main shaft 5 constantly increases, the volume of the air-inlet cavity between cylinder body 2 and the rotor 3 constantly increases thereupon, and the gas flow of its entering also constantly increases.When main axis rotation 180 was spent, as shown in Figure 4, the working medium that gets into air-inlet cavity had occupied the half the of swept volume that cylinder body 2 and rotor 3 form.Because in the turning course of rotary compressor of the present invention; Cylinder body suction port 12 communicates with intakeport 6 all the time, is not provided with any Aspirating valves between wherein, thereby guarantees under any angle of eccentricity; Gas can pass through cylinder body suction port 12 smoothly, gets into the air-inlet cavity between cylinder body 2 and the rotor 3.Simultaneously; As shown in Figure 5, Fig. 5 has represented the gas flow direction after the compression, when pressure in the exhaust cavity during greater than the working pressure of peripheral hardware; Outlet valve 7 will be opened automatically; Compressed gas passes outlet valve 7, gets into the exhaust passage of rotor center axis hole shown in Figure 1 and the exhaust passage that cylinder body 2 central shaft holes constitute through the radially exhaust passage on the rotor 3, is finally discharged by relief opening shown in Figure 18.
Because rotary compressor of the present invention is in turning course, the exhaust passage communicates with relief opening 8 all the time, has so just accomplished continuous exhaust process, has also avoided the unsafe factor that liquid hammer brought simultaneously.
As shown in Figure 2, when the corner of main shaft was β=0, air inlet began to finish with exhaust; When the corner of main shaft is 0＜β when spending, as shown in Figure 3, the pressurized gas process begins, and the suction port of rotation is air-breathing continuously always simultaneously; As shown in Figure 4, when the corner of main shaft is β=180 when spending, air aspiration cavity in the active chamber and exhaust cavity swept volume equate; As shown in Figure 5, when the corner of main shaft is ψ＜β＜360 when spending, and when β=ψ; Exhaust begins, and we are defined as the exhaust angle with ψ, and at this moment the pressure in the exhaust cavity is greater than the working pressure of peripheral hardware; Outlet valve 7 will be opened automatically, and exhaust this moment begins, and compressed gas is discharged through outlet valve 7, exhaust passage and relief opening 8 from exhaust cavity; Along with the corner of main shaft constantly increases, be compressed gas all by discharging in the exhaust cavity in the exhaust cavity, at this moment outlet valve 7 will be closed again automatically; When the corner of main shaft is β=360 when spending, promptly main axis rotation is after one week, and as shown in Figure 2, rotary compressor of the present invention has been accomplished a work cycle, and at this moment air aspiration cavity is full of by gas.
Above-mentioned outlet valve 7 can adopt reed valve plate of cantilever and so on, also can use mechanisms such as ring valve, and when the pressure in the exhaust cavity during greater than the working pressure of peripheral hardware, air-flow is washed the valve block of cantilever open, and gas gets into the exhaust passage from exhaust cavity; After exhaust finished, when promptly the pressure in the exhaust cavity was less than the working pressure of peripheral hardware, the valve block of cantilever resetted, automatically closes vent passage.
Rotary compressor first mode of execution of the present invention is for a swept volume; Gas suction, compression and exhaust are in two weeks of rotor 3, to accomplish; But, air-breathing and compression process hocket simultaneously because being active chamber in slide plate 4 both sides; Therefore concerning complete machine, remain whenever to circle and just accomplish a work cycle, promptly rotor 3 whenever circles and just accomplishes once air-breathing and exhaust simultaneously.So not only machine run is steady, and gas is low at air-breathing and flow velocity relief opening, and flow losses reduce greatly, and its flow losses are about the half the of reciprocal compressor.The compressor of this structure relies on the intakeport of rotation directly air-breathing, need not add Aspirating valves, does not have the air inlet heating phenomena, so volumetric efficiency is high, power loss is little.In addition, the component of rotary compressor first mode of execution of the present invention are few and do not have easily damaged parts, and volume reduces 50-60% than reciprocating compressor, and weight alleviates about 60% approximately, and indicated efficiency improves 30-40% than piston compressor.
The rotor 3 and the cylinder body 2 of rotary compressor first mode of execution of the present invention are made up of two cylindrical bodys, and the speed of related movement between the two is minimum, and friction and wear reduces greatly, and the leakage of working medium simultaneously also solves quite easily.Because slide plate 4 quality are very little, the distance of its motion is very short, and the quality of slide plate 4 is very little; Therefore the reciprocal inertia force of slide plate 4 is also very little; Can ignore fully, even because the inhomogeneous rotatory inertia force unbalance that causes of material can be easy to solution fully on structure.
The cylinder body 2 of two rotations and rotor 3 rotate around separately rotating center respectively, therefore itself do not have unbalanced force separately, so machine run very steadily, vibrates little and noise is low.The morphology of main parts size is a cylinder in addition, so machining accuracy is easy to guarantee, is convenient to utilize high efficiency working machine tool and flow of tissue waterline to produce; Also be easy to assembling and maintenance; Especially the bent axle that does not have eccentric motion, thus can improve output greatly, reduce cost.
Another characteristics of rotary compressor first mode of execution of the present invention are; A swept volume is an air-inlet cavity, is again exhaust cavity, and air-inlet cavity and exhaust cavity are alternately worked again continuously; So not only component are few; Compact structure has increased reliability, has also reduced the energy loss that gas caused simultaneously.
As shown in Figure 6, Fig. 6 shows rotary compressor second mode of execution of the present invention.Rotary compressor second mode of execution of the present invention comprises casing 1, cylinder body 2, rotor 3, slide plate 4, main shaft 5, intakeport 6, relief opening 8 and rack bearing 9.Casing 1 becomes an integral body for dividing body structure through bolt, and its tip portion side is provided with intakeport 6, and the outer circumferentially direction of the shaft end of casing 1 is provided with relief opening 8.Main shaft 5 on 1 two axle heads of casing, can significantly reduce the moment of flexure of rotor 3 for main shaft 5 through the dual-gripper bearings like this, improves the stress of main shaft, to adapt to than the large revolving compressor.Because main shaft 5 runs through whole rotor 3 central shaft holes; Therefore need the central shaft hole setting of rotor 3 be designed to stairstepping; Main shaft 5 is connected with the central shaft hole of the minor diameter of rotor 3 through key and keyway cooperation; Be that rotor 3 rotates around main shaft 5 central axis, the gap between big axis hole of the ladder of rotor 3 and the main shaft 5 then constitutes the exhaust passage.All the other structures are identical with rotary compressor first mode of execution of the present invention, and for succinctly, same structure has just no longer been described at this.
As shown in Figure 7, Fig. 7 shows rotary compressor the 3rd mode of execution of the present invention.Rotary compressor the 3rd mode of execution of the present invention comprises casing 1, cylinder body 2, rotor 3, slide plate 4, main shaft 5, intakeport 6, relief opening 8.Be with the rotary compressor first mode of execution difference of the present invention: the intakeport 6 of rotary compressor the 3rd mode of execution of the present invention is arranged on casing 1 end, and promptly axial position uses on different occasions to make things convenient for this rotary compressor.
As shown in Figure 8, Fig. 8 shows rotary compressor the 4th mode of execution of the present invention.Rotary compressor the 4th mode of execution of the present invention comprises casing 1, cylinder body 2, rotor 3, slide plate 4, main shaft 5, intakeport 6, outlet valve 7.Be with the rotary compressor first mode of execution difference of the present invention: the rotary compressor first mode of execution slide plate 4 Subject Extension of the present invention are to rotor 3 skateboards slot radially.And rotary compressor the 4th mode of execution slide plate 4 of the present invention tilting setting on rotor 3 though increased difficulty of processing so a little, can improve the stress of its slide plate 4 greatly.
Shown in Fig. 9 A, 10A; The slide plate of rotary compressor of the present invention embeds the head of cylinder body can be arranged to different structural forms; The cylinder body 2 cylindrical body inner arc surface structures of holding the slide plate head like this are different; Slide plate cylindrical head below shown in Fig. 9 A is provided with collar, thereby the motion of slide plate embedding cylinder interior is more flexible; Slide plate cylindrical head below shown in Figure 10 B is not provided with collar, and it is more shallow that the slide plate cylindrical head embeds cylinder interior, but be easy to processing, also can guarantee the flexible motion of slide plate 4.
Shown in Fig. 9 B, the pilot groove along the skateboarding direction is arranged in the side of the slide plate of rotary compressor of the present invention; Also can be arranged to the cross shape pilot groove shown in Figure 10 B, when oil lubrication is arranged, play storage lubricant oil, thereby alleviate the friction and wear between slide plate 4 and rotor 3 skateboards slot radially.
Shown in Figure 11 A, 11B, Figure 11 A, 11B show rotary compressor rotor 3 of the present invention and cylinder body 2 end face seal structures.Owing to exist the low speed relative movement between rotary compressor cylinder body 2 of the present invention and the rotor 3; So exist certain gas leakage between them; Can be provided with seal ring 13 at the end face of cylinder body 2 and the end face of rotor 3, because rotor 3 is different with the turning radius of cylinder body 2 and its gyration center is also different, so when rotating; Their contact surface is being made slide relative extremely slowly; But relative velocity is extremely low, and sealing circle 13 will significantly reduce the leakage of gas, improves the volumetric efficiency of its rotary compressor.
In rotary compressor; The gap of the inner circumferential surface that main escape of liquid passage is a cylinder body 2 and the external peripheral surface of rotor 3; Be rotor 3 bottom external peripheral surfaces with cylinder body 2 bottom inner circumferential surfaces mutually in the gap at point of contact; The size in this gap directly affects the volumetric efficiency and the processing cost of rotary compressor, and for air compressor and air conditioner refrigerating compressor, the gap control of the end face junction of described cylinder body 2 and rotor 3 is within 2 millimeters.For rotary oil pump, the gap control of the external peripheral surface of the inner circumferential surface of described cylinder body 2 and rotor 3 is within 3 millimeters.
But the present invention does not limit to above-mentioned cited embodiment; Those skilled in the art can be according to the present invention working principle with above the embodiment that provides; Can make the various modifications that are equal to, the replacement that is equal to, parts increase and decrease and reconfigure, thereby constitute more how new mode of execution.
Though the present invention has provided when it rotates; The inner circumferential surface of cylinder body 2 is tangent all the time in vertical minimum point with the external peripheral surface of rotor 3; But this only is schematic; The external peripheral surface points of tangency of the inner circumferential surface of cylinder body 2 and rotor 3 can be arranged on the circumference arbitrary phase, only requires that slide plate 4 is divided into two different air cavitys with this points of tangency with meniscate swept volume, thereby constitutes air-inlet cavity and exhaust cavity.
Though the present invention has provided intakeport 6 and has been arranged on casing 1 top and axial end, should be appreciated that according to different machine types this intakeport can be arranged on the possible arbitrarily position of casing.For the air type rotary compressor, this intakeport can also be set to a plurality of, even can casing 1 be designed to the open type frame, as long as guarantee the suction port 12 and atmosphere of cylinder body 2.
Though the present invention has provided the cylindrical shape of casing 1 main body, should be appreciated that according to different machine types this casing 1 main body also can oval in shape or other shape.Can get into air-inlet cavity through cylinder body suction port 12 as long as guarantee stable support and fluid.
Though the present invention has provided suction port 12 at cylinder body 2, should be appreciated that this suction port 12 can be arranged to one or a row or vertically and circumferentially plurality of rows vertically.
Describe though the present invention is working medium with gas, should be appreciated that the present invention can be widely used in various fields such as air compressor, FLUID TRANSPORTATION pump and refrigeration air conditioner compressor.
Claims (21)
1. rotary compressor; It comprises casing (1), cylinder body (2), rotor (3), slide plate (4), outlet valve (7); It is characterized in that described casing (1) is provided with intakeport (6) and relief opening (8); Described cylinder body (2) rotating center axis and described rotor (3) rotating center axis are biased to rotor (3) outer peripheral surface and cylinder body (2) inner peripheral surface inscribe mutually; Described slide plate (4) head is embedded in cylinder body (2) cylindrical body; Slide plate (4) Subject Extension is to the skateboards slot of rotor (3); Described outlet valve (7) is arranged on described rotor (3) excircle and the place ahead of the sense of rotation of slide plate (4), and cylinder body (2) is provided with the cylinder body suction port (12) that is positioned at slide plate (4) sense of rotation rear, and the meniscate swept volume between the inner circumferential surface of described slide plate (4) and the cylinder body of naming a person for a particular job (2) of said inscribe mutually and the external peripheral surface of rotor (3) is separated and is air-inlet cavity and exhaust cavity.
2. rotary compressor as claimed in claim 1; It is characterized in that also comprising main shaft (5), eccentric mounting (10), spring bearing (11); Wherein eccentric mounting (10) is tightened to an integral body through bolt and described casing (1); Main shaft (5) through spring bearing (11) cantilever be supported on the eccentric mounting (10), the inboard end of main shaft (5) cooperates through key and keyway and is connected with the central shaft hole of rotor (3).
3. rotary compressor as claimed in claim 1; It is characterized in that also comprising main shaft (5), rack bearing (9), spring bearing (11); Main shaft (5) is supported on casing (1) two axial ends through two spring bearings (11); Two axial ends of cylinder body (2) are bearing on the casing (1) through rack bearing (9), are connected with the central shaft hole of rotor (3) with the keyway cooperation through key in the middle of the main shaft (5).
4. rotary compressor as claimed in claim 2; It is characterized in that also comprising rack bearing (9); One side shaft of cylinder body (2) is bearing on the casing (1) through rack bearing (9) to the end, and the opposite side axial end portion of cylinder body (2) is through on rack bearing (9) the supporting eccentric mounting (10).
5. rotary compressor as claimed in claim 1 it is characterized in that described rotor (3) is provided with the radially exhaust passage of exhaust passage and central shaft hole, and radially the exhaust passage often is communicated with the exhaust passage of central shaft hole.
6. rotary compressor as claimed in claim 5 is characterized in that described rotor (3) exhaust passage and cylinder body (2) central shaft hole have constituted the exhaust passage and connected, and often is communicated with the relief opening (8) of casing (1) again.
7. like claim 1 or 5 described rotary compressors, cavity, described cylinder body suction port (12), air-inlet cavity often are communicated with between the intakeport (6), casing (1) that it is characterized in that described casing (1) and the cylinder body (2).
8. rotary compressor as claimed in claim 1; It is characterized in that described outlet valve (7) is set to and rotor (3) the outer round surface coupling that matches; Pressure in exhaust cavity is greater than the working pressure of external setting-up; Outlet valve (7) will be opened automatically, and the gas that is compressed in the exhaust cavity is all discharged, and at this moment outlet valve (7) will be closed automatically.
9. rotary compressor as claimed in claim 1; It is characterized in that described slide plate (4) head is cylindric; Its main body is tabular, the cylindric head of slide plate (4) two ends slightly stretch out slide plate (4) main body outside, radially fixing two gudgeons when constituting slide plate (4) swing; The length of slide plate (4) main body just in time is complementary with the inside axial width of cylinder body (2), and fluid can not be crossed slide plate (4) body rim slit easily.
10. rotary compressor as claimed in claim 1 is characterized in that the skateboards slot of described rotor (3) is positioned at rotor (3) in the radial direction
11. rotary compressor as claimed in claim 1, the skateboards slot that it is characterized in that described rotor (3) with respect to the radial direction of rotor (3) tilting.
12. rotary compressor as claimed in claim 1 is characterized in that described intakeport (6) is arranged on the axial position of casing (1).
13. rotary compressor as claimed in claim 1 is characterized in that described intakeport (6) is arranged on the radial position of casing (1).
14. rotary compressor as claimed in claim 9 is characterized in that described slide plate (4) cylindrical head below is provided with collar.
15., it is characterized in that described slide plate (4) is provided with the pilot groove of storage lubricant oil like claim 9 or 14 described rotary compressors.
16. rotary compressor as claimed in claim 15 is characterized in that said pilot groove is cross shape.
17. rotary compressor as claimed in claim 1 is characterized in that also comprising seal ring (13), sealing circle (13) is separately positioned on the junction of said cylinder body (2) end face and rotor (3) end face.
18. rotary compressor as claimed in claim 1, the gap control of external peripheral surface of inner circumferential surface and rotor (3) that it is characterized in that described cylinder body (2) is within 3 millimeters.
19. rotary compressor as claimed in claim 17, the gap control of end face junction that it is characterized in that described cylinder body (2) and rotor (3) is within 2 millimeters.
20. rotary compressor as claimed in claim 1 is characterized in that the interior mutually point of contact of described rotor (3) outer peripheral surface and cylinder body (2) inner peripheral surface is tangent all the time on vertical minimum point.
21. rotary compressor as claimed in claim 1 is characterized in that the interior mutually point of contact of described rotor (3) outer peripheral surface and cylinder body (2) inner peripheral surface, as required can be tangent all the time at the outer peripheral surface of rotor (3) and any point of cylinder body (2) inner peripheral surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008100067148A CN101498306B (en) | 2008-01-29 | 2008-01-29 | Rotary compressor |
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| CN2008100067148A CN101498306B (en) | 2008-01-29 | 2008-01-29 | Rotary compressor |
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| CN101498306A CN101498306A (en) | 2009-08-05 |
| CN101498306B true CN101498306B (en) | 2012-07-25 |
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Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102135095A (en) * | 2011-03-13 | 2011-07-27 | 深圳乐满商务服务有限公司 | Eccentric birotor pump |
| CN102606475B (en) * | 2012-03-30 | 2015-03-25 | 陕西天赋翔宇特种泵业有限公司 | Synchronously rotary multi-phase pressurization oil-gas transport pump |
| FR3001172B1 (en) * | 2013-01-18 | 2015-06-05 | Illinois Tool Works | ELECTROPNEUMATIC GAS FIXING APPARATUS |
| WO2015196351A1 (en) * | 2014-06-24 | 2015-12-30 | 江苏策略自动化系统有限公司 | Rotary fluid machinery and method for eliminating axial rotor displacement |
| CN104863853B (en) * | 2014-06-24 | 2017-10-27 | 江苏策略自动化系统有限公司 | Rotary type fluid machine and rotor axial play removing method |
| CN110873048B (en) * | 2018-08-29 | 2023-01-20 | 朱秋萍 | Multi-type sliding plate plane rotary compressor |
| CN111963432B (en) * | 2020-07-24 | 2022-06-28 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN117329127B (en) * | 2023-12-01 | 2024-02-02 | 成都理工大学 | Sliding vane type and centrifugal type combined compression machine |
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| CN85200749U (en) * | 1985-09-18 | 1987-02-18 | 李铁民 | Air compressor |
| CN87200274U (en) * | 1987-01-12 | 1988-10-05 | 刘风云 | Compressor |
| RU2105885C1 (en) * | 1993-06-10 | 1998-02-27 | Иван Яковлевич Райков | Vane-type blower |
| CN1351230A (en) * | 2000-10-28 | 2002-05-29 | 汤科儿 | Rotary-drum air compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85200749U (en) * | 1985-09-18 | 1987-02-18 | 李铁民 | Air compressor |
| CN87200274U (en) * | 1987-01-12 | 1988-10-05 | 刘风云 | Compressor |
| RU2105885C1 (en) * | 1993-06-10 | 1998-02-27 | Иван Яковлевич Райков | Vane-type blower |
| CN1351230A (en) * | 2000-10-28 | 2002-05-29 | 汤科儿 | Rotary-drum air compressor |
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| CN101498306A (en) | 2009-08-05 |
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