CN1670372A - Vortex type compressor - Google Patents
Vortex type compressor Download PDFInfo
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- CN1670372A CN1670372A CNA2005100550229A CN200510055022A CN1670372A CN 1670372 A CN1670372 A CN 1670372A CN A2005100550229 A CNA2005100550229 A CN A2005100550229A CN 200510055022 A CN200510055022 A CN 200510055022A CN 1670372 A CN1670372 A CN 1670372A
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- pressure
- hole
- movable orbiting
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- 230000006835 compression Effects 0.000 claims abstract description 25
- 238000007906 compression Methods 0.000 claims abstract description 25
- 239000012530 fluid Substances 0.000 claims abstract description 22
- 238000004891 communication Methods 0.000 claims abstract description 13
- 238000013000 roll bending Methods 0.000 claims description 38
- 230000003068 static effect Effects 0.000 claims description 37
- 230000009471 action Effects 0.000 claims description 10
- 230000008676 import Effects 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 239000003507 refrigerant Substances 0.000 claims 1
- 239000000314 lubricant Substances 0.000 description 10
- 238000000034 method Methods 0.000 description 4
- 239000003795 chemical substances by application Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000010355 oscillation Effects 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000029058 respiratory gaseous exchange Effects 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000002153 concerted effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
A scroll compressor is provided with: a back-pressure chamber 18 which is provided on the back side of the rotating scroll 8 rotatably provided opposite the stationary scroll 7 and which an intermediate pressure between a discharge pressure and a suction pressure is introduced into; a back-pressure adjustment valve 2 which releases fluid in the back-pressure chamber into a suction chamber or a compression chamber in an initial stage of compression through a communication passage 2f formed at an addendum of the outermost circumference lap 7e of the stationary scroll, according to a difference between a suction pressure introduced through the communication passage 2f or a compression initial pressure and a pressure in the back-pressure chamber. The rotating scroll 8 is provided with a through hole 1 which communicates a compression chamber 13 uncommunicated with the communication passage 2f, with the back-pressure chamber 18, and the compression loss due to reexpansion is reduced by releasing part of an excessive pressure of the back-pressure chamber 18 into the compression chamber 13. So the loss which due to a back-pressure adjustment to adjust an attracting force between a stationary scroll and a rotating one can reduce.
Description
Technical field
The present invention relates to scroll compressor.
Background technique
Scroll compressor, to on end plate, uprightly be provided with the static vortex disk of vortex shape roll bending and movable orbiting scroll respectively, dispose and make the roll bending engagement Face to face, make the movable orbiting scroll rotation, dwindle the volume that is formed at a plurality of pressing chambers between the roll bending successively, come compressed fluid thus.By this compression, produced axial force that static vortex disk and movable orbiting scroll will be broken away from mutually (below, be referred to as tripping force).If two whirlpools dishes leaves, then between the crown of roll bending and end plate, produce the gap and destroy the sealing of pressing chamber, reduce the efficient of compressor.For this reason, form back pressure chamber at the end plate back side of movable orbiting scroll, and import intermediate pressure with compressor discharge pressure and suction pressure as back pressure, utilize back pressure to push movable orbiting scroll to the static vortex disk side to this back pressure chamber, with the elimination tripping force, and between static vortex disk and movable orbiting scroll, produce drawing gravitation.
But, if drawing gravitation is excessive, has then strengthened the axial force between movable orbiting scroll and the static vortex disk, and increased the sliding friction at the bottom of each roll bending crown and the tooth, reduce the efficient of compressor.At this moment, drawing gravitation must be adjusted into suitable size, so patent documentation 1 described scroll compressor, it is adjusted valve by back pressure and has been communicated with back pressure chamber and suction chamber, make the direction of flow suction chamber of back pressure chamber according to the pressure reduction of back pressure chamber and suction chamber, to adjust the size of back pressure.
[patent documentation 1] spy opens flat 10-110688 communique
But adjust method according to the described back pressure of patent documentation 1, owing to the fluid expansion that makes the intermediate pressure that obtains by compression and return suction chamber, so on the whole, have the problem that has produced compression loss and reduced compressor efficiency from scroll compressor.
In addition, adjust method according to the described back pressure of patent documentation 1, it is adjusted into automatically: back pressure=suction pressure+α (certain value), but according to the operating conditions of compressor, best sometimes back pressure value departs from suction pressure+α widely.Consequently, increased slippage loss when back pressure is excessive, increased leakage loss when too small, in any case therefore produced the problem that has all reduced compressor efficiency.
Summary of the invention
The objective of the invention is to reduce the loss that produces along with the back pressure adjustment of adjusting drawing gravitation between static vortex disk and the movable orbiting scroll.
In order to address the above problem, scroll compressor of the present invention has static vortex disk, movable orbiting scroll, back pressure chamber and back pressure and adjusts valve, and wherein, described static vortex disk uprightly is provided with the vortex shape roll bending on end plate; Described movable orbiting scroll, uprightly be provided with in the face of this static vortex disk and can rotate, and the roll bending of described static vortex disk between the vortex shape roll bending of a plurality of pressing chambers of formation; Described back pressure chamber is set at the back side of described movable orbiting scroll and imports head pressure and the intermediate pressure of suction pressure; Described back pressure is adjusted valve, according to the suction pressure that imports by the communication passage that is formed on the described static vortex disk most peripheral roll bending crown or compression initial pressure pressure difference, make the fluid of described back pressure chamber flow into the pressing chamber at the described suction chamber or the initial stage of compression by described communication passage with described back pressure chamber; It is characterized in that: on described movable orbiting scroll, be provided with the through hole that the pressing chamber that will not be communicated with described communication passage is communicated with described back pressure chamber.
Like this, owing on movable orbiting scroll, be provided with the through hole that is communicated with back pressure chamber and pressing chamber, so when the pressure of back pressure chamber is excessive, fluid in the back pressure chamber, adjust the pressing chamber that valve and communication passage flow to suction chamber or compression initial stage by back pressure, simultaneously a part by through hole to flowing out than suction chamber or the high pressing chamber of the pressing chamber pressure at compression initial stage.Consequently, the fluid of the back pressure chamber that obtains with adjustment for back pressure is compressed, the expansion-loss when all flowing into the suction chamber or the pressing chamber at compression initial stage are compared, because a part is flowed into than in the high pressing chamber of suction chamber pressure, so from scroll compressor on the whole, can reduce loss.
In this case, preferably through hole is formed the crown that penetrates into roll bending from end plate in the face of the movable orbiting scroll of back pressure chamber.In addition, also can be formed on the end plate in the face of the movable orbiting scroll of back pressure chamber.No matter the sort of situation is led to the through-hole aperture of pressing chamber side, and is preferably all little than the aperture that leads to the back pressure chamber side.
Particularly, be set to extend through at through hole under the situation of crown of roll bending from the end plate of movable orbiting scroll, when the fluid in the back pressure chamber enters pressing chamber by through hole, can be by the micro-gap of the static vortex disk end plate (tooth bottom) that slides with the roll bending crown.Because this gap becomes resistance on the stream, thus compare during with direct connection back pressure chamber with pressing chamber, can suppression fluid freely flows out inflows, so can be with the inhibition of the pressure oscillation in the back pressure chamber very little.In addition, movable orbiting scroll whenever turn around during, change once from back pressure chamber to pressing chamber, from the flow direction of pressing chamber to back pressure chamber, compression loss (or being called breathing loss) can be suppressed for very little with this.
(invention effect)
According to the present invention, can reduce and follow the back pressure adjustment of adjusting drawing gravitation between static vortex disk and the movable orbiting scroll and the loss that produces.
Description of drawings
Fig. 1 is the whole longitudinal section of the scroll compressor of one embodiment of the invention.
Fig. 2 (A) is the movable orbiting scroll plan view of one embodiment of the invention, (B) is the B B sectional view of (A).
The plan view of Fig. 3 pressing chamber that to be expression be made of Fig. 2 embodiment's movable orbiting scroll and static vortex disk.
Fig. 4 is the plan view of the static vortex disk of one embodiment of the invention.
Fig. 5 is the longitudinal section that the back pressure of one embodiment of the invention is adjusted valve.
Fig. 6 is the plotted curve of presentation graphs 1 embodiment's back pressure and suction pressure relation.
Among the figure: the 1-through hole, the 2-back pressure is adjusted valve, the 7-static vortex disk, 7a, 8a-end plate, 7b, 8b-roll bending, at the bottom of 7c, the 8c-tooth, 7e-most peripheral roll bending, 8-movable orbiting scroll, 13-pressing chamber, 14-suction port, 15-exhaust port, 18-back pressure chamber.
Embodiment
Below, with reference to description of drawings one embodiment of the invention.Fig. 1 is the whole longitudinal section of the scroll compressor of one embodiment of the invention.Fig. 2 (A) is the plan view from the being seen movable orbiting scroll of roll bending side of present embodiment feature portion, (B) is the B B sectional view of Fig. 1 (A).
As shown in Figure 1, static vortex disk 7 is made of the supporting portion 7d that forms discoideus end plate 7a, uprightly is located at gyrate roll bending 7b on this end plate 7a, is positioned at end plate 7a outer circumferential side and is formed the tubular that can surround roll bending 7b.Uprightly being provided with the end plate 7a surface of roll bending 7b, is 7c at the bottom of the tooth.In addition, static vortex disk 7 is fixed on the frame 17 with bolt etc. at supporting portion 7d, utilizes fixation method such as welding grade to be fixed on the casing 9 with the frame 17 that static vortex disk 7 becomes one.
On the other hand, movable orbiting scroll 8 disposes face-to-face with static vortex disk 7, and is set at revolvably in the frame 17.Movable orbiting scroll 8 be have discoideus end plate 8a, with the roll bending 7b of static vortex disk 7 similarly from the upright swirl shape roll bending 8b that is provided with, being located at the structure of the shaft sleeve part 8d of end plate 8a back side central authorities as 8c at the bottom of the tooth on end plate 8a surface.
Casing 9 has been taken in the scroll portion that is made of static vortex disk 7 and movable orbiting scroll 8, motor 16, and lubricant oil and be formed airtight construction in inside.Have the axle 10 of motor 16 rotor 16a, can be set at rotatably flexibly on the frame 17, with the axis coaxle of static vortex disk 7.Front end at axle 10 is provided with crank 10a, and the shaft sleeve part 8d of movable orbiting scroll 8 is installed on the crank 10a revolvably by swivel bearing 11.Movable orbiting scroll 8 is installed with respect to the state of an axis eccentric gauge set a distance δ of static vortex disk 7 with its axis.In addition, the roll bending 8b of movable orbiting scroll 8 overlaps at the circumferencial direction predetermined angular that only staggers with the roll bending 7b of static vortex disk 7.And, cross slip ring 12 has been installed with respect to static vortex disk 7 rotations and can relatively be rotated the mechanism of motion as being used to retrain movable orbiting scroll 8, under this state, when making movable orbiting scroll 8 be rotated motion, between roll bending 7b, 8b, a plurality of crescent shape pressing chambers 13 that dwindled volume along with moving have continuously been formed to central part.For example, under the situation of asymmetric roll bending, as shown in Figure 3,, rotation interior lines side pressing chamber 13a and rotation outside line side pressing chamber 13b have been formed respectively in the interior lines of movable orbiting scroll 8 side and outside line side.
At this, the feature structure of present embodiment is described.As Fig. 2 (A), (B) and shown in Figure 1, on the roll bending 8b of movable orbiting scroll 8, be provided with the through hole 1 that is communicated with back pressure chamber 18 and pressing chamber 13.That is, through hole 1 as shown in Figure 2, is formed the crown that penetrates into roll bending 8b from the movable orbiting scroll end plate 8a in the face of back pressure chamber 18.The position of through hole 1 on roll bending 8b is to make the pressure of pressing chamber 13 sides of through hole 1 be in the approaching suitably position of the value of back pressure value.As shown in Figure 3, pressing chamber 13 side pressure of through hole 1 are in the intermediate value of vortex interior lines side pressing chamber 13a and vortex outside line side pressing chamber 13b pressure.In addition, because during movable orbiting scroll 8 turned around, the pressure oscillation in vortex interior lines side pressing chamber 13a and vortex outside line side pressing chamber 13b was so the intermediate value of each middle pressure in the circle is the pressure of through hole 1 pressing chamber 13 sides.
In addition, through hole 1, shown in Fig. 2 (B), its aperture d1 that leads to pressing chamber 13 sides is formed forr a short time than the aperture d2 that leads to back pressure chamber 18 sides.That is, the roll bending 8b facewidth that suppress as far as possible to slide at the bottom of the tooth with static vortex disk 7 is reduced because of through hole 1.
Below, the action of the scroll compressor of the present embodiment that constitutes like this is described.At first, when by motor 16 rotating driveshafts 10, this rotation is passed to movable orbiting scroll 8 from the crank 10a of axle 10 by swivel bearing 11.Like this, movable orbiting scroll 8 is that to carry out with predetermined distance δ be rotatablely moving of turning radius at the center with the axis of static vortex disk 7.When this rotatablely moved, movable orbiting scroll 8 was retrained by cross slip ring 12 and can not rotation.And, by rotatablely moving of movable orbiting scroll 8, be formed at 13 of pressing chambers between each roll bending 7b, 8b continuously to central mobile, along with it moves, the volume of pressing chamber 13 dwindles continuously.Therefore, in each pressing chamber 13, will compress successively, and discharge compressed fluid from exhaust port 15 from the fluid that suction port 14 sucks.Compressed fluid is by supplying to for example refrigerating circulation system from discharge tube 6 in the casing 9.
On the other hand, stored lubricant oil, and pressure on every side is in head pressure in the bottom of casing 9.Because the pressure ratio head pressure in the back pressure chamber 18 is low, flow into back pressure chamber 18 by the through hole 3 that is located on the axle 10 so be stored in the lubricant oil of casing 9 bottoms.Concrete is that the part of lubricant oil arrives back pressure chamber 18 by cross-drilled hole 4 lubricated main bearings 5 backs that are located on the axle 10.In addition, other lubricant oil, by the crank 10a top of through hole 3 arrival axles 10, lubricated swivel bearing 11 backs flow into back pressure chambers 18.At this moment, lubricant oil was holding 11 o'clock by main bearing 5 and rotating shaft, entered back pressure chamber 18 because of the bearing play is little by throttling and with the pressure that is lower than head pressure.Enter the lubricant oil of back pressure chamber 18, when back pressure raises, open be located at the suction chamber communication passage on back pressure adjust valve 2 and enter suction chamber.And, discharge from exhaust port 15 by pressing chamber 13, its part is discharged to refrigerating circulation system from discharge tube 6, remaining casing 9 in, separate with refrigeration agent and be stored in bottom.
Below, the structure and the action of back pressure adjustment valve 2 are described with reference to Fig. 4, Fig. 5.Back pressure is adjusted valve 2, and its valve body 2a is configured to: can lead to back pressure chamber 18 space 2d, and the communication passage 2f of the crown of the roll bending 7e by the being arranged on static vortex disk 7 most peripherals space 2e that leads to suction chamber (or, compress the pressing chamber 13 at initial stage) separate.Valve body 2a is pressed against towards the opening portion of space 2d by spring 2b.Valve body 2a, when the pressure ratio in the 2e of space imports suction chamber in the 2e of space or the pressure in the pressing chamber at compression initial stage, and the making a concerted effort when high of pressure corresponding with the pushing force of spring 2b by communication passage 2f, be moved upward and space 2d and space 2e connection.Therefore, if be Ps, be α (steady state value) that with the pressure of the pressing chamber at pressure of suction chamber (suck and press) or compression initial stage then the pressure of back pressure chamber (back pressure) Pb is controlled like that as shown in the formula 1 with pressure corresponding to spring 2b.
(several 1)
Pb＝Ps+α
Below, the effect of present embodiment latent structure is described.At first, when flowing into the lubricant oil of back pressure chamber 18 and dissolve in wherein refrigeration agent back pressure when raising because of normal, a part of fluids in the back pressure chamber 18 flow in the pressing chamber 13 by through hole 1.Meanwhile, the fluid in the back pressure chamber 18 is by back pressure adjustment valve 2 inflow suction chambers or than being in the pressing chamber 13 that compresses A-stage that suction pressure raises a little.At this moment, so-called back pressure rises and opens back pressure and adjust valve 2, is that compressed fluid expand into suction pressure or the compression indoor pressure approaching with it again, so produce compression loss.This point, in the present embodiment, because the fluids in the back pressure chamber 18 not have all to expand into by back pressure adjustment valve 2 pressure in suction pressure or the pressing chamber approaching with it again, its part enters pressure by hole 1 all and rises to pressing chamber 13 near back pressure, so can realize can reducing the scroll compressor of expansion-loss and high compression efficiency again.In addition, owing to only be provided with through hole 1 on movable orbiting scroll 8, cost rises so can not produce significantly.
In addition, in the present embodiment owing on the roll bending 8b of movable orbiting scroll 8, be provided with through hole 1, thus when the fluid back pressure chamber 18 in enters pressing chamber 13 by through hole 1, can pass through movable orbiting scroll 8 roll bending 8b crown, and static vortex disk 7 teeth at the bottom of the micro-gap of 7c.This gap becomes the resistance of runner, compares during with pressing chamber 13 with direct connection back pressure chamber 18, can suppression fluid flow freely into outflow, therefore can suppress the pressure oscillations in the back pressure chamber 18 very little.In addition, movable orbiting scroll 8 whenever turn around during, change once from back pressure chamber 18 to pressing chamber 13, from the flow direction of pressing chamber 13 to back pressure chamber 18, can suppress compression loss (or being called breathing loss) very little with this.
Below, with reference to Fig. 6, the action that back pressure of the present invention is adjusted is described.Fig. 6 is the plotted curve of pattern ground expression back pressure Pb and suction pressure Ps relation, and transverse axis is represented suction pressure Ps, and the longitudinal axis is represented back pressure Pb.Under the operating conditions of compressor,, increase leakage loss when too small, so there is best back pressure value because back pressure Pb increases slippage loss when excessive.This best back pressure value, because of the various operating conditionss of compressor different.Now for the optimum value of the representative operating conditions of compressor, do the curve that becomes the mode and be the some 19a～19d among the figure.
Now, adjust valve 2 with the back pressure that can be communicated with back pressure chamber and suction chamber and adjust back pressures, shown in following formula 1, Pb=Ps+ α, and represent with the line C-E-D in scheming.In addition, when adjusting valve 2 with back pressure and be communicated with pressure and be elevated to the pressing chamber of the initial stage compressive state higher a little than suction pressure, Pb=kPs+ α then, though not shown, represent with the straight line that moves to line C-E-D top.Wherein, k is the compressibility coefficient of initial stage compressive state.
At this moment, when adjusting back pressure from utilizing the back pressure that is communicated with back pressure chamber and suction chamber to adjust valve 2,19b is almost consistent with best back pressure value at a 19a, point, but the back pressure Pb at some 19a, some 19b place is more much bigger than best back pressure value.On the other hand, since utilization be located at through hole 1 on the movable orbiting scroll 8 when adjusting back pressure back pressure Pb become middle pressure by the pressing chamber 13 of through hole 1, therefore can on suction pressure Ps, multiply by the certain compressibility coefficient β that is equivalent to pressing chamber 13 middle pressures, can represent with following formula 2:
(several 2)
Pb＝Ps×β
The back pressure Pb of this moment represents with the straight line A-E-B in scheming.This straight line A-E-B, the unanimity almost at best back pressure value point 19b, some 19c, 19d place, but more much bigger at the 19a place than optimum value.
This point is according to present embodiment, owing to through hole 1 both sides that adjust valve 2 with back pressure and be located on the movable orbiting scroll 8 adjust back pressure, so when back pressure Pb uprises, flow in the space of the big multidirectional more low-pressure of the fluids in the back pressure chamber 18.That is,, arranged by the back pressure adjustment that dotted line is represented with through hole 1 at the operating condition of the conduct that E the is ordered suction pressure lower, promptly by the zone on the left of the some E than suction pressure.In addition, at the operating condition of the conduct of the E suction pressure higher, promptly by the zone on some E right side, adjust the back pressure adjustment of valve 2 by back pressure and arranged than suction pressure.The characteristic of Fig. 6 is described in other words, it is characterized in that: back pressure adjust the suction pressure of valve 2 and back pressure action straight line (C-ED), with the action straight line of the suction pressure and the back pressure of through hole 1 (A-E-B) on the way intersects, and back pressure adjustment valve 2 to move the action straight slope of slope ratio through hole 1 of straight lines little.
Therefore, adjusting valve 2 with back pressure and being located at through hole 1 both sides on the movable orbiting scroll 8 when adjusting back pressure, along the A-E among the figure-D action.At this moment, adjust constant and through hole 1 position of the spring 2b of valve 2 by adjusting back pressure, can be with the representational operating condition of 19a～19d, make itself and best back pressure value roughly the same.That is, improve the degrees of freedom that back pressure is adjusted, and can realize the scroll compressor of the high compression efficiency that operating range is wideer.
And in the right side area of the some E of Fig. 6, the middle pressure of pressing chamber 13 that leads to through hole 1 is than the pressure height in the back pressure chamber 18.Therefore, in through hole 1, from the mobile effect that become main flow and can reduce again expansion-loss of pressing chamber 13 to back pressure chamber 18.But because the refrigeration agent that is stored in the lubricant oil of casing 9 bottoms that are under the head pressure atmosphere and dissolves in lubricant oil has reduced the amount that flows into back pressure chamber 18, so, only, can not reduce compression efficiency from the fluid section of pressing chamber 13 to back pressure chamber 18 adverse currents.
As described above described, according to present embodiment,, can lower the loss of expanding again because of compressed fluid along with the back pressure adjustment of the drawing gravitation of adjusting static vortex disk and movable orbiting scroll.Particularly, can realize the scroll compressor of the high compression efficiency that operating range is wideer.
In the above-described embodiments, explanation be on the roll bending of movable orbiting scroll, to run through the example that is provided with through hole 1, but by the invention be not limited to this, as long as the through hole that can be communicated with pressing chamber and back pressure chamber is set.For example, also can establish through hole and be communicated with pressing chamber and back pressure chamber in the header portion of movable orbiting scroll.At this moment, preferably dwindle the aperture of through hole as far as possible, preferably have flow path resistance.
Claims (6)
1. a scroll compressor has static vortex disk, movable orbiting scroll, back pressure chamber and back pressure and adjusts valve, and wherein, described static vortex disk uprightly is provided with the vortex shape roll bending on end plate; Described movable orbiting scroll, uprightly be provided with in the face of this static vortex disk and can rotate, and the roll bending of described static vortex disk between the vortex shape roll bending of a plurality of pressing chambers of formation; Described back pressure chamber is set at the back side of described movable orbiting scroll and imports head pressure and the intermediate pressure of suction pressure; Described back pressure is adjusted valve, pressure difference according to the suction pressure that imports by the communication passage that is formed on the described static vortex disk most peripheral roll bending crown or compression initial pressure and described back pressure chamber makes the fluid of described back pressure chamber flow into described suction chamber or pressing chamber by described communication passage; It is characterized in that:
On described movable orbiting scroll, be provided with the through hole that the pressing chamber that will not be communicated with described communication passage is communicated with described back pressure chamber.
2. scroll compressor according to claim 1 is characterized in that: described through hole, from the face of the end plate of the described movable orbiting scroll of described back pressure chamber, penetrate into the crown of roll bending.
3. scroll compressor according to claim 1 is characterized in that: described through hole is formed on the end plate of the described movable orbiting scroll of facing described back pressure chamber.
4. according to claim 2 or 3 described scroll compressors, it is characterized in that: described through hole is little by the aperture of described back pressure chamber side by the aperture ratio of described pressing chamber side.
5. according to any described scroll compressor in the claim 1～4, it is characterized in that: described fluid is a refrigerant gas.
6. scroll compressor according to claim 1, it is characterized in that: described back pressure adjust the suction pressure of valve and back pressure the action straight line, intersect halfway with the suction pressure of described through hole and the action straight line of back pressure, and the action straight slope of the slope ratio through hole of back pressure adjustment valve events straight line is little.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004073092A JP4519489B2 (en) | 2004-03-15 | 2004-03-15 | Scroll compressor |
| JP2004073092 | 2004-03-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1670372A true CN1670372A (en) | 2005-09-21 |
| CN100362238C CN100362238C (en) | 2008-01-16 |
Family
ID=35041767
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100550229A Expired - Fee Related CN100362238C (en) | 2004-03-15 | 2005-03-14 | Vortex type compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4519489B2 (en) |
| KR (1) | KR100604282B1 (en) |
| CN (1) | CN100362238C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101165350B (en) * | 2006-10-20 | 2012-09-05 | 日立空调·家用电器株式会社 | Vortex compressor |
| CN103189650A (en) * | 2010-11-01 | 2013-07-03 | 大金工业株式会社 | Scroll compressor |
| WO2014008835A1 (en) * | 2012-07-10 | 2014-01-16 | 艾默生环境优化技术(苏州)有限公司 | Pressure control valve and scroll compressor |
| CN104343682A (en) * | 2013-08-07 | 2015-02-11 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN108474377A (en) * | 2016-07-15 | 2018-08-31 | 翰昂汽车零部件有限公司 | Compression set and the separation method for controlling quality stream |
| US10072659B2 (en) | 2012-07-10 | 2018-09-11 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Pressure control valve and scroll compressor |
| US10400772B2 (en) | 2013-08-07 | 2019-09-03 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Scroll compressor having valve component arranged in passage of back pressure cavity and providing openings for passage of fluid |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007138868A (en) * | 2005-11-21 | 2007-06-07 | Hitachi Appliances Inc | Scroll compressor |
| JP5022010B2 (en) * | 2006-12-05 | 2012-09-12 | 日立アプライアンス株式会社 | Scroll compressor |
| JP2009036069A (en) * | 2007-08-01 | 2009-02-19 | Sanden Corp | Scroll type fluid machine |
| JP4542161B2 (en) * | 2008-01-09 | 2010-09-08 | 日立アプライアンス株式会社 | Hermetic electric compressor |
| JP4951586B2 (en) * | 2008-05-30 | 2012-06-13 | 日立アプライアンス株式会社 | Scroll fluid machinery |
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| KR101827829B1 (en) | 2011-01-07 | 2018-02-12 | 삼성전자주식회사 | Scroll compressor |
| CN105073887B (en) * | 2013-03-22 | 2017-03-22 | 日产化学工业株式会社 | Polyester resin composition containing amino-triazine derivative |
| KR101642178B1 (en) | 2013-07-02 | 2016-07-25 | 한온시스템 주식회사 | Scroll compressor |
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| JPS62178789A (en) * | 1986-02-03 | 1987-08-05 | Hitachi Ltd | Scroll compressor |
| JPH02277991A (en) * | 1989-04-20 | 1990-11-14 | Tokico Ltd | Scroll type fluid machine |
| JP2557533B2 (en) * | 1989-10-18 | 1996-11-27 | 株式会社日立製作所 | Hermetic variable speed scroll compressor |
| JPH04132889A (en) * | 1990-09-20 | 1992-05-07 | Tokico Ltd | Scroll type fluid machine |
| JP3874469B2 (en) * | 1996-10-04 | 2007-01-31 | 株式会社日立製作所 | Scroll compressor |
| JPH10110689A (en) * | 1996-10-04 | 1998-04-28 | Hitachi Ltd | Sealed type scroll compressor |
| US5762483A (en) * | 1997-01-28 | 1998-06-09 | Carrier Corporation | Scroll compressor with controlled fluid venting to back pressure chamber |
| JP2000213477A (en) * | 1999-01-21 | 2000-08-02 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| JP3560492B2 (en) * | 1999-02-25 | 2004-09-02 | 株式会社日本自動車部品総合研究所 | Scroll compressor |
| JP4472860B2 (en) * | 2000-11-07 | 2010-06-02 | 三菱電機株式会社 | Refrigerant compressor |
| JP2002285980A (en) * | 2001-03-26 | 2002-10-03 | Toyota Industries Corp | Scroll-type compressor and method for lubricating the same |
| JP3743343B2 (en) * | 2001-10-29 | 2006-02-08 | 松下電器産業株式会社 | Scroll compressor |
| JP4107903B2 (en) * | 2002-07-29 | 2008-06-25 | 株式会社デンソー | Scroll compressor |
-
2004
- 2004-03-15 JP JP2004073092A patent/JP4519489B2/en not_active Expired - Fee Related
-
2005
- 2005-03-14 KR KR1020050020834A patent/KR100604282B1/en active IP Right Grant
- 2005-03-14 CN CNB2005100550229A patent/CN100362238C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101165350B (en) * | 2006-10-20 | 2012-09-05 | 日立空调·家用电器株式会社 | Vortex compressor |
| CN103189650A (en) * | 2010-11-01 | 2013-07-03 | 大金工业株式会社 | Scroll compressor |
| CN103189650B (en) * | 2010-11-01 | 2015-09-02 | 大金工业株式会社 | Scroll compressor |
| WO2014008835A1 (en) * | 2012-07-10 | 2014-01-16 | 艾默生环境优化技术(苏州)有限公司 | Pressure control valve and scroll compressor |
| US10072659B2 (en) | 2012-07-10 | 2018-09-11 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Pressure control valve and scroll compressor |
| CN104343682A (en) * | 2013-08-07 | 2015-02-11 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN104343682B (en) * | 2013-08-07 | 2016-12-28 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| US10400772B2 (en) | 2013-08-07 | 2019-09-03 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Scroll compressor having valve component arranged in passage of back pressure cavity and providing openings for passage of fluid |
| CN108474377A (en) * | 2016-07-15 | 2018-08-31 | 翰昂汽车零部件有限公司 | Compression set and the separation method for controlling quality stream |
| CN108474377B (en) * | 2016-07-15 | 2019-12-13 | 翰昂汽车零部件有限公司 | compression device and separation method for controlling mass flow |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4519489B2 (en) | 2010-08-04 |
| CN100362238C (en) | 2008-01-16 |
| KR100604282B1 (en) | 2006-07-25 |
| KR20060044336A (en) | 2006-05-16 |
| JP2005256809A (en) | 2005-09-22 |
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