CN104302923A - Gas compressor - Google Patents
Gas compressor Download PDFInfo
- Publication number
- CN104302923A CN104302923A CN201380025764.XA CN201380025764A CN104302923A CN 104302923 A CN104302923 A CN 104302923A CN 201380025764 A CN201380025764 A CN 201380025764A CN 104302923 A CN104302923 A CN 104302923A
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- China
- Prior art keywords
- rotor
- lateral mass
- chamber
- pressing chamber
- gas
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
Abstract
In order to reduce manufacturing costs by eliminating parts such as delivery valves, a gas compressor comprises, in a housing (10), a compressor main unit (60) having a rotor (50) that rotates around an axial center (C), a cylinder (40), vanes (58), a front side block (20), and a rear side block (30), wherein: a delivery chamber (14), from which high pressure refrigerant gas (G: gas) is delivered, is formed in the housing (10); a plurality of compression chambers (43) that are partitioned by the rotor (50), the cylinder (40), both side blocks (20, 30), and two vanes (58, 58) are formed; a notch (54) and delivery apertures (38, 39: delivery channels) are formed to pass to connect the compression chamber (43) and delivery chamber (14) within a prescribed rotational angle range around the axial center (C) of the rotor (50); and the refrigerant gas (G) is delivered from the compression chamber (43) to the delivery chamber (14) through the delivery channels in the prescribed rotational angle range.
Description
Technical field
The present invention relates to a kind of gas compressor, in detail, relate to the improvement of the gas compressor to blade rotary form.
Background technique
In air-conditioning system, be used for the gases such as refrigerant gas being carried out compressing and the gas compressor that gas is circulated in air-conditioning system.
In this gas compressor, rotary actuation and the compressor main body of gas compression is housed in the inside of housing, in the inside of housing, divided by housing and compressor main body and be formed with discharge chamber, gas from compressor main body high pressure is discharged in this discharge chamber, and then the gas of high pressure is discharged to the outside of housing from this discharge chamber.
Compressor main body has the running shaft pivoted, the roughly columned rotor rotated integrally with this running shaft, cylinder, the blade of multiple tabular and two lateral mass, described cylinder have by this rotor from the outer circumferential face of the outside of its outer circumferential face and rotor across space around the inner peripheral surface of contour shape, described blade is arranged from the outer circumferential face of rotor with freely stretching out laterally, described two lateral mass are formed with the bearing rotatably supporting the running shaft given prominence to from the both ends of the surface of rotor respectively, meanwhile, contact with the both ends of the surface of rotor and cylinder and cover this both ends of the surface; By the face of each inner side of the outer circumferential face of rotor, the inner peripheral surface of cylinder and two lateral mass formed carry out gas suction, compression, discharge the cylinder chamber in space.
At this, contacted, thus this cylinder chamber is divided into multiple space by the front end, side of stretching out of each blade stretched out from the outer circumferential face of rotor with the inner peripheral surface of cylinder, multiple spaces that these segmentations are formed form pressing chamber respectively.
That is, the face of each pressing chamber by the outer circumferential face of rotor, the inner peripheral surface of cylinder, each inner side of two lateral mass and the face along tandem two blades of sense of rotation of rotor divide and form.
Further, the volume of each pressing chamber changes along with the rotation of running shaft and rotor, and in the stroke that volume increases, gas is sucked in pressing chamber; In the stroke of volume reducing, the gas in pressing chamber is compressed; In the stroke that the volume of pressing chamber reduces further, the gas being become high pressure in pressing chamber by compressing is discharged to discharge chamber.
At this, the structure realizing the stroke that the gas of high pressure is discharged from pressing chamber has such as discharge side, tap hole and expulsion valve, described discharge side is the space that the gas of discharging from pressing chamber is passed through between the cylinder of the periphery wall becoming pressing chamber and the housing being configured in outside more, described tap hole makes pressing chamber and discharge side be connected to form path in cylinder, and described expulsion valve carrys out switch pair according to the pressure of gas of the pressing chamber inside acting on tap hole and portals; Separate discharge side and the lateral mass of discharge chamber and be formed with exhaust port as the path being communicated with these two spaces, the gas that will be discharged to discharge side by this exhaust port flows into discharge chamber (patent documentation 1).
Prior art document
Patent documentation
Patent documentation 1: Japan Patent 2004-300925 publication
Summary of the invention
The problem that invention will solve
But, according to the technology recorded in prior art document, cylinder not only forms tap hole, also needs to arrange expulsion valve and this expulsion valve is assembled into cylinder, therefore produce parts expense, the expense corresponding with assembly working amount of expulsion valve and assembling part etc., these also become manufacture cost.
The present invention completes in view of the foregoing, and its object is to provides a kind of gas compressor can cut down the parts such as expulsion valve, reduce manufacture cost.
The means of dealing with problems
The gas compressor that the present invention relates to, by the rotor in compressor main body, each pressing chamber and towards being separated in the lateral mass of the discharge chamber formed by housing and compressor main body, in the rotation angle range of the regulation around axle of rotor, form the drain passageway that pressing chamber is communicated with discharge chamber, thus cut down the parts such as expulsion valve and reduce manufacture cost.
Namely, the gas compressor that the present invention relates to possesses compressor main body in the inside of housing, described compressor main body has the roughly columned rotor, cylinder, the blade of multiple tabular and two lateral mass that pivot, described cylinder have by described rotor from the outer circumferential face of the outside of its outer circumferential face and described rotor across space around the inner peripheral surface of contour shape, described blade is arranged from the outer circumferential face of described rotor with freely stretching out laterally, and described lateral mass contacts with the both ends of the surface of described rotor and described cylinder and covers this both ends of the surface; Be formed with discharge chamber in the inside of described housing, the pressurized gas of discharging from described compressor main body are discharged to described discharge chamber; Be formed with pressing chamber in the inside of described compressor main body, described pressing chamber is separated by the face of the inner peripheral surface of the outer circumferential face of described rotor, described cylinder, each inner side of described two lateral mass and described blade and is formed; Described in described rotor in the rotation angle range of the regulation of axle, be formed with the drain passageway that described pressing chamber is communicated with described discharge chamber in described rotor and described lateral mass; In the rotation angle range of described regulation, described discharge chamber is discharged to by described drain passageway by the gas compressed in described pressing chamber.
Invention effect
According to the gas compressor that the present invention relates to, the parts such as expulsion valve can be cut down and reduce manufacture cost.
Accompanying drawing explanation
Fig. 1 is the stereogram of the blade rotary compressor of the mode of execution representing the gas compressor that the present invention relates to.
Fig. 2 is the exploded perspective view of the compressor shown in Fig. 1.
Fig. 3 is the longitudinal section of the compressor shown in Fig. 1.
Fig. 4 represents the figure along the cross section of the A-A line in Fig. 3.
Fig. 5 is the stereogram representing rotor.
Fig. 6 represents that the vaned rotor set of assembling loads the stereogram of the state in cylinder.
Fig. 7 A is the stereogram representing rear portion lateral mass.
Fig. 7 B represents the figure along the cross section of the B-B line in Fig. 7 A.
Schematic important part sectional view that Fig. 8 A is the effect of the compressor that mode of execution is described, that be equivalent to Fig. 7 B, represents that the drain passageway of the upstream side of the sense of rotation of rotor starts the state be communicated with.
Schematic important part sectional view that Fig. 8 B is the effect of the compressor that mode of execution is described, that be equivalent to Fig. 7 B, represents that the drain passageway of upstream side terminates the state be communicated with.
Schematic important part sectional view that Fig. 8 C is the effect of the compressor that mode of execution is described, that be equivalent to Fig. 7 B, represents that the drain passageway in the downstream side of the sense of rotation of rotor starts the state be communicated with.
Schematic important part sectional view that Fig. 8 D is the effect of the compressor that mode of execution is described, that be equivalent to Fig. 7 B, represents that the drain passageway in downstream side terminates the state be communicated with.
Fig. 9 represents important part sectional view that two tap holes of rear portion lateral mass collaborate into the variation of, that be equivalent to Fig. 8 A ~ 8D.
Figure 10 is the stereogram of the rotor represented in the compressor of other mode of executions.
Figure 11 is for representing the stereogram with an example of the rear portion lateral mass of the rotor combination shown in Figure 10.
Figure 12 A is the effect of the compressor that other mode of executions are described, schematic important part sectional view, represents that the drain passageway of the upstream side of the sense of rotation of only rotor starts the state be communicated with.
Figure 12 B is the effect of the compressor that other mode of executions are described, schematic important part sectional view, represents the state that the drain passageway of only upstream side is communicated with.
Figure 12 C is the effect of the compressor that other mode of executions are described, schematic important part sectional view, represents the state that the drain passageway of upstream side of the sense of rotation of rotor is communicated with the drain passageway in downstream side simultaneously.
Figure 12 D is the effect of the compressor that other mode of executions are described, schematic important part sectional view, represents the state that the drain passageway in only downstream side is communicated with.
Embodiment
Below, be described in detail with reference to the embodiment of accompanying drawing to the gas compressor that the present invention relates to.
The blade rotary compressor 100 of a mode of execution of the gas compressor that the present invention relates to is (following, be only called compressor 100), be used as in middle settings such as automobiles and the gas compressor had in the air-conditioning system of vaporizer, gas compressor, condenser and expansion valve.This air-conditioning system forms freeze cycle by making refrigerant gas G (gas) circulate.
As shown in Figure 1, 2, the structure of compressor 100 contains compressor main body 60 in the inside of housing 10, and described housing 10 is formed primarily of body shell 11 and protecgulum 12.
Body shell 11 is substantially cylindrical shape, and an end of this drum is formed in closed mode, and another end forms opening.
Protecgulum 12 is formed as lid, and block this opening with the state of the ends contact of the opening side with this body shell 11, in this condition, to be linked with body shell 11 by connecting member 18 and be integrated with body shell 11 one-tenth, being formed as the housing 10 that inside has space accordingly.
Protecgulum 12 is formed with suction port 12a, and described suction port 12a makes the inside of housing 10 and ft connection and the refrigerant gas G of low pressure is directed into the inside of housing 10 from the vaporizer of air-conditioning system.
On the other hand, body shell 11 is formed with exhaust port 11a, and described exhaust port 11a makes the inside of housing 10 and ft connection and the refrigerant gas G of high pressure is discharged to the condenser of air-conditioning system from the inside of housing 10.
The compressor main body 60 being housed in housing 10 inside has the running shaft 51 rotated freely around axle center C, the roughly columned rotor 50 rotated integrally with running shaft 51, cylinder 40, the blade 58 of 3 tabulars and two lateral mass (anterior lateral mass 20, rear portion lateral mass 30), described cylinder 40 have by this rotor 50 from the outer ring of its outer circumferential face 52 around the inner peripheral surface 41 of contour shape, described blade 58 is arranged from the outer circumferential face 52 of rotor 50 towards the inner peripheral surface 41 of cylinder 40 with freely stretching out, described two lateral mass (anterior lateral mass 20, rear portion lateral mass 30) blocking rotor 50 and the two ends of cylinder 40.
At this, as shown in Figure 3, running shaft 51 by be formed at protecgulum 12 bearing 12b, be formed at respectively each lateral mass 20,30 of compressor main body 60 bearing 27,37 and can support rotatably around axle center C, running shaft 51, the part of externally giving prominence to from protecgulum 12 possesses pulley etc., these pulleys etc. accept the power transmitted from the motor etc. of vehicle, thus running shaft 51 rotates around axle center C.
In addition, the inner space of housing 10 is divided into the leftward space and rightward space that clip compressor main body 60 by compressor main body 60.
Further, contacted with protecgulum 12 by anterior lateral mass 20 and keep the airtight of leftward space, on the other hand, contacted with body shell 11 by rear portion lateral mass 30 and keep the airtight of rightward space.
In two spaces that the inside of these housings 10 separates, the space being diagram left side relative to compressor main body 60 is the suction chamber 13 of environment under low pressure, and the suction chamber 13 of described environment under low pressure imports the refrigerant gas G of low pressure from vaporizer by suction port 12a; The space being diagram right side relative to compressor main body 60 is the discharge chamber 14 of hyperbaric environment, and the refrigerant gas G of high pressure is discharged to condenser by exhaust port 11a by the discharge chamber 14 of described hyperbaric environment.
As shown in Figure 4, the inside of compressor main body 60 is formed with the single cylinder chamber 42 of the substantially C-shaped of being surrounded by the outer circumferential face 52 of the inner peripheral surface 41 of cylinder 40, rotor 50 and two lateral mass 20,30.
Particularly, the contour shape of the inner peripheral surface 41 of cylinder 40 be configured to the inner peripheral surface 41 of cylinder 40 and the outer circumferential face 52 of rotor 50 the axle center C around running shaft 51 rotate a circle (angle 360 [degree]) scope in only close at a place, accordingly, cylinder chamber 42 forms single space.
In addition, in the contour shape of the inner peripheral surface 41 of cylinder 40, the approach portion 48 formed as the inner peripheral surface 41 of cylinder 40 and the immediate part of outer circumferential face 52 of rotor 50, its be formed in from as the inner peripheral surface 41 of cylinder 40 and the outer circumferential face 52 of rotor 50 farthest away from part and the portion that is far apart 49 that formed along the position of more than the downstream side separation angle 270 [degree] of the sense of rotation W () of rotor 50 (being less than 360 [degree]) Fig. 4 counterclockwise.
The contour shape of the inner peripheral surface 41 of cylinder 40 is set to: along the sense of rotation W of running shaft 51 and rotor 50 from being far apart portion 49 until approach portion 48, the shape that the distance between the outer circumferential face 52 of rotor 50 and the inner peripheral surface 41 of cylinder 40 reduces gradually.
Blade 58 is embedded in the blade groove 59 that rotor 50 is formed, and is stretched out laterally from the outer circumferential face 52 of rotor 50 by the back pressure brought by the refrigerator oil R being supplied to blade groove 59.
In addition, single cylinder chamber 42 is separated into multiple pressing chamber 43 by blade 58, forms a pressing chamber 43 by tandem two blades 58 of sense of rotation W along running shaft 51 and rotor 50.Therefore, arrange in the present embodiment of 3 blades 58 around running shaft 51 with the equal angles interval of angle 120 [degree], form three to four pressing chambers 43.
In addition, about the pressing chamber that there is approach portion between two blades 58,58, owing to being formed a closed space by approach portion and blade, result, the pressing chamber 43 that there is approach portion between two blades 58,58 forms two pressing chambers, even therefore three blades also can form four pressing chambers 43.
Separate cylinder chamber 42 by blade 58 and the volume of the inside of the pressing chamber 43 obtained, pressing chamber 43 diminishes gradually along sense of rotation W from being far apart portion's 49 to approach portion 48, sharply increases from approach portion 48 to being far apart portion 49.
This cylinder chamber 42, rotate in the scope of 1 week along sense of rotation W, the part of the side, most upstream being benchmark with approach portion 48 is towards being formed at anterior lateral mass 20 and the inlet hole 23 be communicated with suction chamber 13, be arranged in the pressing chamber 43 in approach portion 48 downstream side, along with the rotation of rotor 50, volume with this pressing chamber 43 increases, and sucks refrigerant gas G by inlet hole 23 from suction chamber 13.
When the volume that rotor 50 rotates pressing chamber 43 in 1 week becomes maximum, inlet hole 23 is formed near the position of the blade 58 of the upstream side (rear side of sense of rotation W) separating this pressing chamber 43, therefore, pressing chamber 43 comprises in the rotation angle range in the portion of being far apart 49, until when its volume becomes maximum, suck refrigerant gas G to pressing chamber 43.
Then, if the blade of this upstream side 58 crosses inlet hole 23, then this pressing chamber 43 becomes closed space, and refrigerant gas G is sealed in the inside of pressing chamber 43.
So, pressing chamber 43, towards during inlet hole 23, becomes induction stroke refrigerant gas G being drawn into pressing chamber 43 inside.
The contour shape of inner peripheral surface 41 is configured to pressing chamber 43 along sense of rotation W from being far apart portion 49 towards the rotation angle range of approach portion 48, towards the downstream side of sense of rotation W, interval between the inner peripheral surface 41 of cylinder 40 and the outer circumferential face 52 of rotor 50 diminishes gradually, therefore, along with the rotation of rotor 50, the volume reducing of pressing chamber 43, the refrigerant gas G being sealed in pressing chamber 43 inside is compressed.Therefore, this stroke becomes compression stroke.
At this, as shown in Figure 5,6, the part of the rotor 50 corresponding with each pressing chamber 43 is formed with breach 54 (being formed in a part for epitrochanterian drain passageway) respectively, this breach 54 be positioned at separate sense of rotation W upstream side blade 58 near, and from the outer circumferential face 52 of rotor 50 to the end face 53 (hereinafter referred to as rear portion lateral mass opposed faces 53) of the side towards rear portion lateral mass 30.
On the other hand, as shown in Fig. 7 A, 7B, the face 35 (hereinafter referred to as rotor opposed faces 35) towards this rear portion lateral mass opposed faces 53 of rear portion lateral mass 30 is formed with the tap hole 38,39 (being formed in a part for the drain passageway lateral mass) be communicated with discharge chamber 14 from this rotor opposed faces 35.
Tap hole 38,39 is made up of shallow slot 38b, 39b (elongated hole) and through hole 38a, 39a respectively, described shallow slot 38b, 39b are circular shape along the sense of rotation W (being clockwise in Fig. 7 A) of rotor and do not have through to discharge chamber 14, and described through hole 38a, 39a are through to discharge chamber 14 in a part of these shallow slots 38b, 39b.
Shallow slot 38b is formed at the approach portion 48 of cylinder 40 for benchmark, from the rotation angle range β (=θ 3-θ 4) of rotary angle position θ 4 to the rotary angle position θ 3 (θ 4 < θ 3) of the sense of rotation W along rotor 50.
On the other hand, shallow slot 39b is formed at the approach portion 48 of cylinder 40 for benchmark, from the rotation angle range α (=θ 1-θ 2) of rotary angle position θ 2 to the rotary angle position θ 1 (θ 2 < θ 1) of the sense of rotation W along rotor 50.
Through hole 38a is formed at the end (side near rotary angle position θ 3) corresponding with the downstream side of the sense of rotation W of rotor 50 in the shallow slot 38b of circular shape.
Through hole 39a is formed at the end (side near rotary angle position θ 1) corresponding with the downstream side of the sense of rotation W of rotor 50 in the shallow slot 39b of circular shape.
Further, the breach of rotor 50 54 and the tap hole 38,39 of rear portion lateral mass 30 are formed on the roughly equal position of radius from the C of axle center, as shown in Fig. 8 A, 8B, 8C, 8D, are formed communicatively in the rotation angle range of the regulation of rotor 50.
Therefore, in this rotation angle range, by breach 54 and tap hole 38 or tap hole 39, pressing chamber 43 is communicated with discharge chamber 14, is discharged to discharge chamber 14 in the inside of pressing chamber 43 by the refrigerant gas G compressed.
At this, when rotary angle position when consistent with approach portion 48 with breach 54 is for benchmark (rotary angle position 0 [degree]), the rotation angle range of regulation that breach 54 is communicated with tap hole 38, rotor 50 is the neighbouring scope (Fig. 8 A, 8B) near rotary angle position θ 3 of rotary angle position θ 4 be communicated with tap hole 38 from breach 54.
When rotary angle position when consistent with approach portion 48 with the front end of blade 58 (contacting the end of side with the inner peripheral surface 41 of cylinder 40) is benchmark (rotary angle position 0 [degree]), " rotation angle range of regulation " becomes than the position of the rotary angle position when consistent with approach portion 48 with breach 54 for position phase (angle) bias of " rotation angle range of regulation " during benchmark only between the position of forward blade 58 front end and the position of breach 54.
Same when being communicated with tap hole 38 with breach 54, when rotary angle position when consistent with approach portion 48 with breach 54 is for benchmark (rotary angle position 0 [degree]), the rotation angle range of regulation that breach 54 is communicated with tap hole 39, rotor 50 is near the rotary angle position θ 2 that is communicated with tap hole 39 from breach 54 until scope (Fig. 8 C, 8D) near rotary angle position θ 1.
Be discharged to the refrigerant gas G in discharge chamber 14, the condenser be discharged to the outside by exhaust port 11a.
According to the compressor 100 of present embodiment as constructed as above, breach 54 be communicated with tap hole 38, the rotation angle range of the regulation of rotor 50, and breach 54 be communicated with tap hole 39, in the rotation angle range of the regulation of rotor 50, the refrigerant gas G of pressing chamber 43 inside can be made respectively to be discharged to discharge chamber 14.
That is, do not need to arrange in the past such expulsion valve etc. in cylinder 40.
Accordingly, while cutting down such expulsion valve, being used for fixing the number of components such as the connecting member of expulsion valve, also can comprise the workload of cutting down and fixing needed for this expulsion valve, can manufacture cost be reduced.
In addition, about the compressor 100 of present embodiment, corresponding with each pressing chamber 43 of the rotor 50 rotated, as the breach 54 of a part for the drain passageway to discharge chamber 14, only when the angle of swing of rotor 50 is the rotation angle range of regulation and the tap hole 38 of the part as drain passageway of rear portion lateral mass 30, 39 are communicated with, therefore, when the rotary angle position of rotor 50 is outside the rotation angle range of regulation, the breach 54 of rotor 50 not with the tap hole 38 of rear portion lateral mass 30, 39 are communicated with, the compression of refrigerant gas G can be carried out in pressing chamber 43 as in the past, simultaneously, refrigerant gas G can be prevented from discharge chamber 14 to the inside adverse current of pressing chamber 43.
About the compressor 100 of present embodiment, the shallow slot 38b of tap hole 38 formed in rear portion the lateral mass 30 and shallow slot 39b of tap hole 39 is respectively the elongated hole that the sense of rotation W along rotor 50 extends, therefore, not only make the breach 54 formed in rotor 50 only be communicated with in specific rotary angle position with the tap hole 38,39 formed in rear portion lateral mass 30, be communicated with in the entire scope of the rotation angle range that this elongated hole can also be made to extend.
The compressor 100 of mode of execution as constructed as above, no matter the pressure size of the refrigerant gas G of pressing chamber 43 inside, when the volume ratio of pressing chamber 43 is for being specifically worth, can both be discharged to discharge chamber 14 by refrigerant gas G from pressing chamber 43.
In addition, the compressor 100 of present embodiment, breach 54 be communicated with tap hole 38, the rotation angle range of the regulation of rotor 50 is communicated with tap hole 39 with breach 54, between the rotation angle range of the regulation of rotor 50, pressing chamber 43 is not communicated with discharge chamber 14, therefore, there is the rotation angle range of discharging and interrupting.
But, by to form at least one party breach 54 and tap hole 38,39 than from the mode that the rotation angle range of breach rotary angle position θ 2 to rotary angle position θ 3 is large with the width of breach 54 (length along the sense of rotation W around axle center C), thus the interruption of this discharge can be eliminated, and can discharge continuously.
In addition, according to making shallow slot 38b and shallow slot 39b from shallow slot 38b side along the structure that sense of rotation W (from shallow slot 39b side along with sense of rotation W opposite direction) is communicated with, discharge also can be made continuous.
According to this structure making shallow slot 38b be communicated with shallow slot 39b, interrupt continuously and not from rotary angle position θ 4 to rotary angle position θ 1, the refrigerant gas G of pressing chamber 43 inside can be made to be discharged to discharge chamber.
In addition, when adopting this structure making shallow slot 38b be communicated with shallow slot 39b, the side (such as, through hole 38a) in two through holes 38a, 39a can be omitted, as shown in Figure 9, only forming a through hole (such as, through hole 39a).
And, according to such as shown in Figure 9, compressor main body 60 along rotor 50 while the sense of rotation W of axle center C rotates and carries out compressing with the ratio of 1 time between 1 week, there is multiple (three) pressing chamber 43 and the tap hole 38 formed in rear portion lateral mass 30, the compressor 100 of 39 mode of executions be communicated with, when starting to be communicated with from the breach 54 of rotor 50 with tap hole 38 (rotary angle position), when terminating to be communicated with to the breach 54 of rotor 50 with tap hole 39 (rotary angle position) during (rotation angle range), this breach 54 towards pressing chamber 43 and discharge chamber continual communication, therefore, refrigerant gas G can be made from being arranged in this rotation angle range, along two pressing chambers 43 that the sense of rotation W of rotor 50 is one in front and one in back adjacent, 43 are communicated with discharge chamber 14 simultaneously.
The compressor 100 of above-mentioned mode of execution is that shallow slot 38b, 39b of the tap hole 38,39 of the side part by being formed at rear portion lateral mass 30 in drain passageway is formed as elongated hole, but also the part (in above-mentioned mode of execution for breach 54) being formed at the side of rotor 50 can be formed as the elongated hole that extends in the rotation angle range γ of the regulation of the sense of rotation W along rotor 50.
Namely, as shown in Figure 10, in the rear portion lateral mass opposed faces 53 of rotor 50, formed with shown in Fig. 7, shallow slot 38b, 39b of being formed in the rotor opposed faces 35 of rear portion lateral mass 30 are same, as the elongated slot 55b of a part for the elongated hole extended in the rotation angle range γ of the regulation at rotor 50, simultaneously, form the vent 55a extending to elongated slot 55b from the outer circumferential face 52 of the rotor 50 towards pressing chamber 43, form tap hole 55 (being formed at the part in rotor in drain passageway) by these vents 55a and elongated slot 55b.
This tap hole 55 is corresponding with each pressing chamber 43 respectively and formed.
On the other hand, in rear portion lateral mass 30, as shown in figure 11, be formed from rotor opposed faces 35 through to discharge chamber 14 towards face tap hole 38,39 (being formed at the part in lateral mass drain passageway).
Be ε along the rotation angle range between the outer ledge of sense of rotation W between tap hole 38,39, the rotation angle range between inside edge is δ.
And, in the rotation angle range of the regulation around axle center C of rotor 50, the tap hole 55 of rotor 50 is communicated with the tap hole 38,39 of rear portion lateral mass 30, accordingly, pressing chamber 43 is communicated with discharge chamber 14, and the refrigerant gas G of pressing chamber 43 inside is discharged to discharge chamber 14.
Namely, as illustrated in fig. 12, rotary angle position θ 4 place in the rotation angle range of the regulation of rotor 50, the tap hole 55 of rotor 50 starts to be communicated with the tap hole 38 of rear portion lateral mass 30, as shown in Figure 12 A, 12B, 12C, 12D, during the tap hole 55 of rotor 50 is communicated with the tap hole 38 of rear portion lateral mass 30, by this drain passageway (tap hole 55 and tap hole 38), the refrigerant gas G of pressing chamber 43 inside is discharged to discharge chamber 14.
Rotation angle range δ between the inside edge of two tap holes 38,39 of rear portion lateral mass 30, is formed along the angle intervals (δ < γ) that the rotation angle range γ of sense of rotation W is shorter with the elongated slot 55b than tap hole 55.
Accordingly, carry out the rotation of the sense of rotation W along rotor 50 further, as indicated in fig. 12 c, when being communicated with and interrupting of the tap hole 55 of rotor 50 and the tap hole 38 of rear portion lateral mass 30, the tap hole 55 of rotor 50 starts to be communicated with the tap hole 39 of rear portion lateral mass 30.
Under the state that tap hole 55 is communicated with tap hole 39, as shown in Figure 12 C, 12D, by drain passageway (tap hole 55 and tap hole 39), the refrigerant gas G of pressing chamber 43 inside is discharged to discharge chamber 14.
Result, when starting to be communicated with from the tap hole 55 of rotor 50 and the tap hole 38 of rear portion lateral mass 30 (Figure 12 A), the rotary angle position θ 4 of rotor, when terminating to be communicated with to the tap hole 55 of rotor 50 and the tap hole 39 of rear portion lateral mass 30 (Figure 12 D), in the entire scope of rotation angle range Δ θ (=θ 1-θ 4=γ+ε) the rotary angle position θ 1 of rotor, the refrigerant gas G of pressing chamber 43 inside can be made to be discharged to discharge chamber 14 without interruption.
Further, the condenser that the refrigerant gas G being discharged to discharge chamber 14 is discharged to the outside by exhaust port 11a.
In addition, in the compressor 100 of above-mentioned each mode of execution, except the form shown in Fig. 9, all there are two drain passageways (using tap hole 38 as the drain passageway of a part, and using tap hole 39 as the drain passageway of a part) form, but be positioned at the drain passageway of the upstream side of the sense of rotation W of rotor 50 in these two drain passageways (using tap hole 38 as the drain passageway of a part, below, be called the drain passageway of upstream side), the pressure of pressing chamber 43 inside be communicated with the drain passageway of this upstream side, in during the drain passageway of this upstream side is communicated with, might not always reach desired head pressure.
Namely, when the drain passageway of this upstream side starts to be communicated with, the pressure of this pressing chamber 43 inside not yet reaches desired head pressure, but along with the rotation of rotor 50, in during the drain passageway of this upstream side is communicated with, there is the pressure of this pressing chamber 43 inside can reach the situation of desired head pressure.
In this case, when the drain passageway of this upstream side starts to be communicated with, the refrigerant gas G not reaching desired head pressure is discharged to discharge chamber 14 by the drain passageway of upstream side from pressing chamber 43, but prevent this situation and the refrigerant gas G making to reach desired head pressure is discharged to discharge chamber 14 time, in the drain passageway of this upstream side of rear portion lateral mass 30, only arrange expulsion valve also can, open tap hole 38 when this expulsion valve is set to more than desired head pressure, close tap hole 38 when the head pressure desired by deficiency.
But, even if in this case, drain passageway about the sense of rotation W downstream side being positioned at rotor 50 (take tap hole 39 as the drain passageway of a part, below, be called the drain passageway in downstream side), the pressure of pressing chamber 43 inside be communicated with the drain passageway in this downstream side, during the drain passageway in this downstream side is communicated with, be set to and always form more than desired head pressure, therefore do not need the expulsion valve of the tap hole 39 that this drain passageway of switch is set.
The compressor 100 of above-mentioned mode of execution has three blades 58, but gas compressor involved in the present invention is not limited to this form, the quantity of blade suitably can be chosen as two, 4,5,6 etc., use the gas compressor of the blade of the number selected like this, also can obtain the effect same with above-mentioned mode of execution and compressor 100, effect.
In addition, gas compressor involved in the present invention is not only limited to and rotates between 1 week at running shaft, only carry out once by the stroke sucking, compress, discharge 1 circulation formed, i.e. so-called unistage type gas compressor, also can be two section type gas compressor, but preferably be applicable to the unistage type gas compressor that can guarantee during longer compression stroke and discharge stroke.
Namely, unistage type gas compressor only carries out the suction of gas (refrigerant gas G) of 1 circulation, compression and discharge during rotor rotates 1 week, therefore, with rotate at rotor carry out the gas that two circulate during 1 week suction, compression and discharge two section type gas compressor compared with, can gently pressurized gas, the power that abatement needs, can reduce the pressure reduction between two one in front and one in back adjacent in a rotational direction pressing chambers simultaneously, suppress the leakage of the gas between pressing chamber.
And, the approach portion of the inner peripheral surface of cylinder can from being far apart the sense of rotation of portion along rotor in downstream side significantly away from (such as, more than angle 270 [degree]) and formed, therefore, with have approach portion only away from be far apart portion's angle 180 [degree] left and right contour shape inner peripheral surface gas compressor compared with, can more gently pressurized gas, the degree that efficiency reduces can be reduced further.
The cross-reference of related application
The Patent 2012-114244 CLAIM OF PRIORITY that the application filed an application to the Japanese Patent Room based on May 18th, 2012, its all disclosed content is by referring to adding in this specification completely.
Symbol description
10 housings;
13 suction chambers;
14 discharge chambers;
20 anterior lateral mass;
30 rear portion lateral mass;
35 rotor opposed faces;
38,39 tap holes (being formed at the part in the lateral mass of rear portion in drain passageway);
38a, 39a through hole;
38b, 39b shallow slot;
40 cylinders;
43 pressing chambers;
50 rotors;
52 outer circumferential faces;
53 rear portion lateral mass opposed faces;
54 breach (being formed at the part in rotor in drain passageway);
58 blades;
60 compressor main bodies;
Δ θ, α, β, γ, δ, ε rotation angle range;
θ 1, θ 2, θ 3, θ 4 rotary angle position;
100 blade rotary compressors (gas compressor);
C axle center (axle);
G refrigerant gas (gas);
W sense of rotation.
Claims (4)
1. a gas compressor, it is characterized in that, compressor main body is possessed in the inside of housing, described compressor main body has the roughly columned rotor, cylinder, the blade of multiple tabular and two lateral mass that pivot, described cylinder have by described rotor from the outer circumferential face of the outside of its outer circumferential face and described rotor across space around the inner peripheral surface of contour shape, described blade is arranged from the outer circumferential face of described rotor with freely stretching out laterally, described two lateral mass contact with the both ends of the surface of described rotor and described cylinder and cover these both ends of the surface
The inside of described housing is formed with discharge chamber, and the pressurized gas of discharging from described compressor main body are discharged to described discharge chamber,
The inside of described compressor main body is formed with pressing chamber, and described pressing chamber is separated by the face of the inner peripheral surface of the outer circumferential face of described rotor, described cylinder, each inner side of described two lateral mass and described blade and formed,
In the rotation angle range of the described regulation around axle of described rotor, in described rotor and described lateral mass, be formed with the drain passageway that described pressing chamber and described discharge chamber are communicated with, in described pressing chamber, in the rotation angle range of described regulation, be discharged to described discharge chamber by described drain passageway by the gas compressed.
2. gas compressor according to claim 1, it is characterized in that, in described drain passageway, the part be formed in described rotor is formed in the mode be only communicated with in the rotation angle range of the described regulation of described rotor with the part be formed in described lateral mass.
3. gas compressor according to claim 2, is characterized in that, in described drain passageway, the part being formed at described rotor and at least one party be formed in the part of described lateral mass, is the elongated hole extended along the sense of rotation of described rotor.
4. the gas compressor according to any one in claims 1 to 3, is characterized in that, described compressor main body rotates between 1 week at described rotor and compresses with the ratio of 1 time, has multiple described pressing chamber simultaneously,
In specific rotation angle range in the rotation angle range of described regulation, described drain passageway is formed in the mode be communicated with described discharge chamber along two pressing chambers that the sense of rotation of described rotor is one in front and one in back adjacent in described multiple pressing chamber simultaneously.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012114244A JP2013241851A (en) | 2012-05-18 | 2012-05-18 | Gas compressor |
| JP2012-114244 | 2012-05-18 | ||
| PCT/JP2013/061378 WO2013172144A1 (en) | 2012-05-18 | 2013-04-17 | Gas compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104302923A true CN104302923A (en) | 2015-01-21 |
Family
ID=49583558
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380025764.XA Pending CN104302923A (en) | 2012-05-18 | 2013-04-17 | Gas compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2013241851A (en) |
| CN (1) | CN104302923A (en) |
| WO (1) | WO2013172144A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20170342982A1 (en) * | 2015-01-28 | 2017-11-30 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Sliding Vane Type Compressor and Exhaust Structure Thereof |
| CN109611336A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
| CN109611334A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of double atmospheric pressure compressor with rolling rotor |
| CN109611337A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
| CN109611332A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor of double atmospheric pressure |
| CN111963432A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN111963433A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN111963435A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN112145417A (en) * | 2020-07-24 | 2020-12-29 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
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| JPS5112007U (en) * | 1974-07-13 | 1976-01-29 |
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| JPS57146088A (en) * | 1981-03-04 | 1982-09-09 | Mitsubishi Heavy Ind Ltd | Rotary compressor |
| JPS6397893A (en) * | 1986-10-09 | 1988-04-28 | Diesel Kiki Co Ltd | Vane type rotary compressor |
| JPS63255588A (en) * | 1987-04-13 | 1988-10-21 | Seiko Seiki Co Ltd | Gas compressor |
| JPH08177769A (en) * | 1994-12-20 | 1996-07-12 | Zexel Corp | Side block of vane type compressor |
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Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10451070B2 (en) * | 2015-01-28 | 2019-10-22 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Sliding vane compressor and exhaust structure thereof |
| US20170342982A1 (en) * | 2015-01-28 | 2017-11-30 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Sliding Vane Type Compressor and Exhaust Structure Thereof |
| CN109611336B (en) * | 2017-10-05 | 2023-09-22 | 桂林航天工业学院 | Rolling rotor type compressor |
| CN109611336A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
| CN109611334A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of double atmospheric pressure compressor with rolling rotor |
| CN109611337A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor |
| CN109611332A (en) * | 2017-10-05 | 2019-04-12 | 桂林航天工业学院 | A kind of rolling rotor compressor of double atmospheric pressure |
| CN109611337B (en) * | 2017-10-05 | 2023-09-26 | 桂林航天工业学院 | Rolling rotor type compressor |
| CN109611332B (en) * | 2017-10-05 | 2023-09-22 | 桂林航天工业学院 | Double-exhaust-pressure rolling rotor type compressor |
| CN109611334B (en) * | 2017-10-05 | 2023-09-22 | 桂林航天工业学院 | Double-row-pressure rolling rotor compressor |
| CN111963432A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN111963435B (en) * | 2020-07-24 | 2022-08-05 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN112145417A (en) * | 2020-07-24 | 2020-12-29 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN111963435A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN111963433A (en) * | 2020-07-24 | 2020-11-20 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2013172144A1 (en) | 2013-11-21 |
| JP2013241851A (en) | 2013-12-05 |
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Application publication date: 20150121 |