CN1526951A - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- CN1526951A CN1526951A CNA200410033021XA CN200410033021A CN1526951A CN 1526951 A CN1526951 A CN 1526951A CN A200410033021X A CNA200410033021X A CN A200410033021XA CN 200410033021 A CN200410033021 A CN 200410033021A CN 1526951 A CN1526951 A CN 1526951A
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- Prior art keywords
- refrigerant gas
- rotor housing
- bank rotor
- compressor
- bulge
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- 239000003507 refrigerant Substances 0.000 claims abstract description 154
- 238000010521 absorption reaction Methods 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 12
- 238000007789 sealing Methods 0.000 claims description 7
- 238000005192 partition Methods 0.000 claims description 4
- 230000010349 pulsation Effects 0.000 abstract description 6
- 230000009467 reduction Effects 0.000 abstract description 2
- 239000007789 gas Substances 0.000 description 135
- 230000006835 compression Effects 0.000 description 30
- 238000007906 compression Methods 0.000 description 30
- 238000007599 discharging Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000000284 resting effect Effects 0.000 description 2
- 239000006200 vaporizer Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
Abstract
The present invention relates to a compressor that can reduce the refrigerant gas pulsation pressure in multi-step when a refrigerant gas is discharged into a rear refrigerant gas discharge chamber toward the outside of the compressor and into a front refrigerant gas discharge chamber toward the outside of the compressor, thereby obtaining excellent reduction in the refrigerant gas pulsation pressure and remarkably reducing a noise due to the refrigerant gas pulsation.
Description
Technical field
The present invention relates to compressor, particularly when refrigerant emission gas, can reduce the compressor of refrigerant gas fluctuation pressure effectively.
Background technique
The compressor that is used for the motor vehicle air regulating system can receive by the magnetic clutch intermittent action selectively by the engine power of pulley transmission, and a refrigerant gas of coming from vaporizer is drawn to wherein, compression refrigerant gas is to drain into condenser with this compression refrigerant gas simultaneously.Compressor is divided dissimilar according to compression structure, and the type that is widely used in the Motor Vehicle is a swash-plate-type compressor.
Fig. 1 to 4 shows a kind of structure of common swash-plate-type compressor.
As illustrated in fig. 1 and 2, common swash-plate-type compressor is constructed according to following mode: the wobbler 40 that live axle 30 is installed on it is respectively fitted with a pair of cylinder body 10 and 20, and a plurality of pistons 50 are arranged on wobbler 40 outer surfaces in this manner, promptly are accommodated in a plurality of cylinder-bore that form on cylinder body 10 and 20.When wobbler 40 rotations, under the assistance of piston boots portion 60, each piston 50 is done linear reciprocating motion in corresponding cylinder-bore, and piston absorbs and compression refrigerant gas with this.In this mode, be provided with the valve unit 70 of admission air valve 71, valve plates 72 and drain tap 73 and pad respectively according to the outside of aforementioned assembled in sequence in cylinder body 10 and 20.In order to hold and to protect above-mentioned parts in the cylinder body, front case 80 is connected with cylinder body 10, and rear case 90 is connected with cylinder body 20.
After adopting said structure, when the pulley from magnetic clutch 31 applies power, this common swash-plate-type compressor just makes wobbler 40 rotations, and no matter when wobbler 40 rotates a circle, the above-mentioned a plurality of pistons 50 that are arranged on wobbler 40 outer surface all begin to move reciprocatingly, thereby finish stroke one time.Therefore, in above-mentioned a plurality of piston 50 some are towards front case 80 motions, and at the same time, other then move towards rear case 90 by wobbler 40, like this, the refrigerant gas that flows into front case 80 and rear case 90 by air collecting chamber 96 is transported in compression chamber 81 and 91, and air collecting chamber 96 wherein has air suction silencer 94 and muffler 95, and compression chamber 81 and 91 madial walls by front case 80 and rear case 90 form.By a predetermined passage, the refrigerant gas that compressed in compression chamber is transported in the rear case 90, and mixes with the compression refrigerant gas that discharges from rear case 90, thus to the compressor outside drain.
To illustrate in greater detail channel design and operation of components mode below to the outside drain compression refrigerant gas.Shown in Fig. 2 to 4, the compression chamber 81 of store compressed refrigerant gas is formed on the central part of front case 80 internal surfaces, a pair of cylinder body 10 and 20 is provided with bullport 11 and 21, these two bullports 11 and 21 are arranged on precalculated position on the cylinder body to correspond to each other, like this, bullport can cause the refrigerant gas in the compression chamber 81 in the compression chamber 91 that forms in rear case 90.Identical with the mode of front case 80, rear case 90 is provided with compression chamber 91 and exhaust passage 92, wherein compression chamber 91 is arranged in the central part of its internal surface, and in order to connect exhaust chamber 93, extend with the form of curve along the peripheral wall of compression chamber 91 exhaust passage 92, is used for by hole H compression refrigerant gas being caused the outside.
Therefore, when wobbler 40 high speed rotating, above-mentioned a plurality of piston 50 to-and-fro motion, like this, difference compression refrigerant gas in the compression chamber 81 and 91 of front case 80 and rear case 90.Then, through the bullport 11 and 21 on the cylinder body 10 and 20, the refrigerant compressed gas delivery is to the exhaust chamber 93 of rear case 90 in the compression chamber 81 of front case 80, and refrigerant compressed gas also is delivered to exhaust chamber 93 by exhaust passage 92 in the compression chamber 91 of rear case 90.The compression chamber 81 of rear case and 91 gases of discharging just mix in exhaust chamber 93 and drain into the outside by outlet end 94 like this, in the past.
But in common swash-plate-type compressor, because be used for refrigerant compressed gaseous emissions in the rear case 90 92 are individually formed a side in compression chamber 91 with semicircle usually to outside exhaust passage, so must use anti-leakage device to seal the upper opening that is positioned at compression chamber's 91 opposite sides as the packing ring.In addition, be the sealing exhaust passage, need to install separate part, this makes the compressor arrangement complexity.
In addition, exhaust passage 92 narrow and long semicircular structures become the obstacle that refrigerant gas flows, final build-up of pressure loss.The inner peripheral wall of higher pressure refrigerant gas collision exhaust passage 92, this has caused the undesirable generation that is caused noise by the refrigerant gas pulsation of people.
Because exhaust passage 92 occupies the certain zone of air-breathing chamber, this reduces the volume of air-breathing chamber, and among the suction port of valve plates 72, exhaust passage 92 partly covers the suction port 72a that is provided with on it, therefore, the operation operation that sucks refrigerant gas often will be born very big resistance.
And the formation of exhaust passage 92 makes that the structure of compressor is complicated more separately.In order to improve it, some modifications have appearred with regard to compression chamber 91 structures of rear case 90, and peripheral components related with exhaust passage 92 as packing ring also must be changed.Opposite with needs, this has increased the quantity of operation, and causes cost of production to improve greatly.In addition, because the suction of refrigerant gas and discharging are not steady, and the exhaust pressure of refrigerant gas reduces, and owing to the refrigerant gas pulsation produces noise.
For addressing these problems, No. 6068453 U.S. Patent Publication that this assignee proposes a kind of swash-plate-type compressor, it is provided with the exhaust passage that is arranged on the rear case, improves the exhaust structure of refrigerant gas with this.
Fig. 5 is the front elevation of compressor rear case of the prior art.
As shown in the figure, rear case 100 is provided with: from its inside bottom surface to many side inner walls 101 of upper process, stretch out and the extension 102 that forms, the air-breathing chamber 103 and the exhaust chamber 104 that are isolated from each other by the inner peripheral wall of inwall 101 and rear case 100 from the part of inwall 101, and also be provided with outlet pipe 106, the compression refrigerant gas that this outlet pipe will enter in the exhaust chamber 104 is carried to the compressor outside, described outlet pipe 106 1 ends stretch certain length in exhaust chamber 104, and its other end communicates with outlet chamber 105.
The outlet pipe 106 of rear case 100 is about some B on inwall 101 internal surfaces with respect to the spread length of its center line and connects half of crow flight distance L between the some A of extension 102.
Be located at the structure of rear case 100 inboards according to aforementioned outlet pipe 106, compression refrigerant gas in the front case and the compression refrigerant gas in the rear case mix in outlet chamber 105 by outlet pipe 106, to eliminate interactive two refrigerant gas pulsating waves (waves), enter the compressor outside then.
But, in this prior art, when refrigerant gas from front case during to the compressor outside drain owing to can not reduce the fluctuation pressure of refrigerant gas effectively, so as a complete unit, the reducing of refrigerant gas fluctuation pressure is restricted.And, in order to address this problem, in the compressor arranged outside have the big muffler of gas collecting tube, this has brought the another one problem: the volume of compressor finally must increase.
Summary of the invention
Therefore, the present invention aims to provide a kind of compressor, and it has solved substantially because of the restriction of correlation technique and the not enough one or more problems that cause.
An object of the present invention is to provide a kind of compressor that when refrigerant emission gas, can reduce the refrigerant gas fluctuation pressure effectively.
Other advantage, purpose and characteristics part of the present invention can be illustrated in the following description, to those skilled in the art, after the following content of research, part advantage, purpose and characteristics will be apparent, perhaps also can know from implement practice of the present invention.Purpose of the present invention and other advantage can realize by the structure that particularly points out in written explanation and claim and the accompanying drawing and obtain.
According to the present invention, a kind of compressor is provided, it comprises: the front case of sealing front-bank rotor housing one end; The rear case of sealing rear-bank rotor housing one end; Be arranged to interconnected front-bank rotor housing and rear-bank rotor housing between front case and rear case; The refrigerant gas entry end and the outlet end that form in front-bank rotor housing and rear-bank rotor housing at least one or the more peripheral surfaces; In preceding refrigerant gas absorption chamber, pass the front exhaust pipe of first dividing plate, refrigerant gas discharge chamber before above-mentioned first dividing plate defines so that its isolate with preceding refrigerant gas absorption chamber, with this refrigerant gas in the outside conveying of compressor is drained into the preceding refrigerant gas discharge chamber of front case; In the refrigerant gas absorption chamber of back, pass the front exhaust pipe of second partition, above-mentioned second partition defines back refrigerant gas discharge chamber so that it is isolated with back refrigerant gas absorption chamber, with this to the outside refrigerant gas of carrying in the back refrigerant gas discharge chamber that is drained into rear case of compressor; The auxiliary bulge in preceding auxiliary bulge that communicates with the outlet side of front exhaust pipe and final vacuum pipe and back; Be arranged on front-bank rotor housing exhaust connecting passage interior with rear-bank rotor housing and that link to each other with the auxiliary bulge of preceding auxiliary bulge and back; And the main bulge that between the exhaust connecting passage, is provided with according to the mode that communicates with the refrigerant gas outlet end.
According to the present invention, preferably, main bulge extends to an end of the exhaust connecting passage of front-bank rotor housing or rear-bank rotor housing, constitutes an integral body in front-bank rotor housing or rear-bank rotor housing.
According to the present invention, preferably, main bulge is individually formed the outside at front-bank rotor housing or rear-bank rotor housing.
According to the present invention, preferably, in front exhaust pipe and the final vacuum pipe at least one or more multidigit on such position, i.e. beeline place between the central part of the preceding refrigerant gas discharge chamber of front case and rear case and back refrigerant gas discharge chamber and front exhaust pipe and final vacuum tube inlet end.
According to the present invention, preferably, the volume of at least one or more volume ratio front exhaust pipe and final vacuum pipe is big in the auxiliary bulge of preceding auxiliary bulge and back.
According to the present invention, preferably, at least one or more channel cross-sectional area are than big or the two the same size of channel cross-sectional area of front exhaust pipe and final vacuum pipe in the exhaust connecting passage.
According to the present invention, preferably, big or the two the same size of the volume sum of auxiliary bulge and the auxiliary bulge in back before the volume ratio of main bulge.
According to the present invention, preferably, in front exhaust pipe and the final vacuum pipe at least one or manyly communicate with lower surface of the auxiliary bulge of auxiliary bulge and back before any one.
According to the present invention, preferably, at least one or more channel cross-sectional area become greatly or increase step by step from inlet to outlet in front exhaust pipe and the final vacuum pipe.
According to the present invention, preferably, between the front exhaust pipe of front case and the refrigerant gas exhaust end between the final vacuum pipe of passage length and rear case and the refrigerant gas exhaust end passage length equate.
Be understandable that the general introduction of front of the present invention and following detailed description all are exemplary and illustrative, and are intended to as claim invention is described further.
Description of drawings
Accompanying drawing shows embodiments of the invention, and is used for illustrating principle of the present invention with specification, and these accompanying drawings provide further to be understood of the present invention, comprises in this application and constituted the application's a part.In these accompanying drawings:
Fig. 1 is the perspective exploded view of common compressor;
Fig. 2 is the front sectional elevation of compressor shown in Figure 1;
Fig. 3 is the front elevation of the front case of compressor shown in Figure 1;
Fig. 4 is the front elevation of the rear case of compressor shown in Figure 1;
Fig. 5 is the front elevation of a kind of rear case of compressor in the prior art;
Fig. 6 is the side view of first embodiment of the invention compressor;
Fig. 7 is the side sectional view of compressor shown in Figure 6;
Fig. 8 is the front elevation of the front case that adopts in the compressor shown in Figure 6;
Fig. 9 is the front elevation of the rear case that adopts in the compressor shown in Figure 6; And
Figure 10 is the side sectional view of second embodiment of the invention compressor.
Embodiment
Below in detail with reference to the preferred embodiments of the present invention, these embodiments' shown in the drawings example.
Fig. 6 is the side view of first embodiment of the invention compressor; Fig. 7 is the side sectional view of compressor shown in Figure 6; Fig. 8 is the front elevation of the front case that adopts in the compressor shown in Figure 6; Fig. 9 is the front elevation of the rear case that adopts in the compressor shown in Figure 6.
In first embodiment of the invention, shown in Fig. 6 and 7, compressor comprises: the front case 200 of sealing front-bank rotor housing 400 1 ends; The rear case 300 of sealing rear-bank rotor housing 500 1 ends; Be arranged to the front-bank rotor housing 400 and the rear-bank rotor housing 500 that between front case 200 and rear case 300, interosculate; Rotatably be supported on the live axle 600 in front-bank rotor housing 400 and the rear-bank rotor housing 500; Be arranged on the wobbler 700 on the live axle 600; With a plurality of pistons 900 that are connected with wobbler 700 peripheral surfaces with can operating operation by piston shoe (shoe) 800.For explanation for purpose of brevity, hereinafter to conventional practice in similar or identical structure will no longer illustrate.
Shown in accompanying drawing 7 and 8, the rear aperture of front case 200, and refrigerant gas absorption chamber 210 and preceding refrigerant gas discharge chamber 220 before (being on the internal surface of its antetheca) is provided with on the inner circle wall of front case.Wherein preceding refrigerant gas absorption chamber 210 is used for the refrigerant gas that cylinder-bore (not shown) supply on front-bank rotor housing 400 (see figure 7)s flows into compressor, and the compression refrigerant gas that preceding refrigerant gas discharge chamber 220 is used for flowing out from cylinder-bore is towards the compressor outside drain.By dividing plate 230 preceding refrigerant gas absorption chamber 210 is isolated with preceding refrigerant gas discharge chamber 220.The shape of this dividing plate 230 adopts the form of closed curve usually, is positioned on the outer surface of preceding refrigerant gas discharge chamber 220.The in the past front of central part front case 200 front faces of refrigerant gas discharge chamber 220, be provided with a pulley (not shown) of rotatably installing by the bearing (not shown), nose 202 (seeing accompanying drawing 8) of supporting driving shaft 600 rotatably stretches out, and live axle 600 passes this nose portion.
In addition, shown in Fig. 7 and 9, rear case 300 open front also are equipped with rear-bank rotor housing 500.Rear case 300 within it on the perisporium (being on the internal surface of rear wall) be provided with back refrigerant gas absorption chamber 310 and back refrigerant gas discharge chamber 320, back refrigerant gas absorption chamber 310 wherein is used for the refrigerant gas of the cylinder-bore (not shown) supply inflow compressor on rear-bank rotor housing 500 (seeing accompanying drawing 7), and then refrigerant gas discharge chamber 320 is used for to the compression refrigerant gas of compressor outside drain from the cylinder-bore outflow.By dividing plate 330 back refrigerant gas absorption chamber 310 is isolated with back refrigerant gas discharge chamber 320.The shape of this dividing plate 330 adopts the form of closed curve usually, is located on the outer surface of back refrigerant gas discharge chamber 320.
As shown in Figure 7, front-bank rotor housing 400 is provided with exhaust connecting passage 410, and rear-bank rotor housing 500 is provided with exhaust connecting passage 510, and exhaust connecting passage 410 and 510 interconnects, like this, the refrigerant gas from front case 200 and rear case 300 discharges discharges to refrigerant gas outlet end 530.Exhaust connecting passage 410 is connected with the preceding auxiliary bulge 250 of front case 200, and exhaust connecting passage 510 is connected with the back auxiliary bulge 350 of rear case 300.Exhaust connecting passage 410 and 510 extends to form as a unitarily formed main bulge 420 in front-bank rotor housing and rear-bank rotor housing in its end.
In a preferred embodiment of the invention, refrigerant gas entry end 520 and refrigerant gas outlet end 530 are positioned on the peripheral surface of rear-bank rotor housing 500, but they also can be positioned on the peripheral surface of front-bank rotor housing 400.In addition, if one of them is arranged on the peripheral surface of front-bank rotor housing 400, then another can be arranged on the peripheral surface of rear-bank rotor housing 500.
Referring to these passages, as shown in Figure 7, live axle 600 is by carrying the motivational drive of coming from power source and rotating, and wobbler 700 is rotation together thereupon also, like this, phase place (phases) according to wobbler 700, a plurality of pistons 900 move reciprocatingly in each cylinder bore of front-bank rotor housing 400 and rear-bank rotor housing 500, at this moment, and by these passages, in the compressor that adopts said structure, refrigerant gas is sucked, compresses discharging then.In the to-and-fro motion process of above-mentioned a plurality of pistons 900, form negative pressure in the cylinder bore, like this, refrigerant gas flows into wobbler chamber S by the refrigerant gas entry end 520 that links to each other with vaporizer (omitting among the figure).
The refrigerant gas of introducing wobbler chamber S is sucked respectively in the cylinder-bore of front-bank rotor housing 400 and rear-bank rotor housing 500.
When the refrigerant gas that sucks cylinder-bore being compressed along with the compression stroke of piston 900, by the opening that in valve plates, forms and the opening on the air-breathing needle-valve, gas is to the preceding refrigerant gas discharge chamber 220 and 320 dischargings of back refrigerant gas discharge chamber of front case 200 and rear case 300, and the opening that forms in the above-mentioned valve plates is opened by the exhaust needle-valve.
Referring to such passage, wherein pass through this passage, the preceding refrigerant gas discharge chamber 220 of inflow front case 200 and rear case 300 and the refrigerant gas of back refrigerant gas discharge chamber 320 are to the compressor outside drain, be delivered to refrigerant gas discharge end 530 from the refrigerant gas of front case 200 and rear case 300 dischargings by the exhaust connecting passage 410 and 510 of front-bank rotor housing 400 and rear-bank rotor housing 500 respectively, refrigerant gas by this discharge end to the compressor outside drain.
In this mode, shown in accompanying drawing 6 and 7, front case 200 and rear case 300 are provided with front exhaust pipe 240 and final vacuum pipe 340, front exhaust pipe 240 and final vacuum pipe 340 be refrigerant gas discharge chamber 220 and 320 extensions of this discharge chamber of back refrigeration agent gas in the past, pass dividing plate 230 and 330, and be provided with auxiliary bulge 250 and 350 at the opening of front exhaust pipe 240 and final vacuum pipe 340.
Like this, by back discharge tube 340 and auxiliary bulge 350, refrigerant gas in the back refrigerant gas discharge chamber 320 is delivered in the exhaust connecting passage 510 of rear-bank rotor housing 500, by front exhaust pipe 240 and auxiliary bulge 250, refrigerant gas in the preceding refrigerant gas discharge chamber 220 is delivered in the exhaust connecting passage 410 of front-bank rotor housing 400, then, this part refrigerant gas and carry the refrigerant gas of coming to pass main bulge 420 together from the exhaust connecting passage 510 of rear-bank rotor housing 500.After this, by refrigerant gas discharge end 530 with refrigerant gas to the compressor outside drain.
In addition, in a preferred embodiment of the invention, the length of passage and the final vacuum pipe 340 of rear case 300 equate with passage length between the refrigerant gas exhaust end 530 between the front exhaust pipe 240 of front case 200 and the refrigerant gas exhaust end 530, the result, cardinal principle is identical each other from the difference between the fluctuation pressure of front case 200 and rear case 300 discharging refrigerant gases, has so just reduced the fluctuation pressure of refrigerant gas.
In addition, in a preferred embodiment of the invention, for the fluctuation pressure that reduces effectively to produce during to the compressor outside drain from front case 200 and rear case 300 when refrigerant gas, preferably, the volume of auxiliary bulge 250 and 350 volume ratio front exhaust pipe 240 and final vacuum pipe 340 is big.That is to say, front exhaust pipe 240 and final vacuum pipe 340 by little volume, refrigerant gas discharge chamber 220 and back refrigerant gas discharge chamber 320 carry the refrigerant gas of coming to flow into the auxiliary bulge 250 and 350 of big volume in the past, and this has reduced the fluctuation pressure of refrigerant gas.In addition, in a preferred embodiment of the invention, in front exhaust pipe 240 and the final vacuum pipe 340 at least one or the sectional area with such passage more, this sectional area exports from entering the mouth to and becomes greatly or increase step by step, in front exhaust pipe 240 and the final vacuum pipe 340 at least one or a plurality ofly be positioned at such position, i.e. beeline L1 and L2 place between the central part of the preceding refrigerant gas discharge chamber 220 of front case 200 and rear case 300 and back refrigerant gas discharge chamber 320 and its entry end.
In addition, if the channel cross-sectional area of front exhaust pipe 240 and final vacuum pipe 340 is bigger than the channel cross-sectional area of exhaust connecting passage 410 and 510, the refrigerant gas quantitative change that then flows into preceding auxiliary bulge 250 and the auxiliary bulge 350 in back must be than big from the refrigerant gas amount of wherein outflow, so that refrigerant gas assists bulge 250 and back to assist in the bulge 350 before resting on.Therefore, preferably, exhaust connecting passage 410 and 510 channel cross-sectional area are bigger or the two is big or small the same than the channel cross-sectional area of front exhaust pipe 240 and final vacuum pipe 340.
As top discussion, especially, in order to prevent that refrigerant gas from resting on the auxiliary bulge 350 of preceding auxiliary bulge 250 and back, the volume of main bulge 420 is greater than volume sum or the two equal and opposite in direction of preceding auxiliary bulge 250 and the auxiliary bulge 350 in back.
Because the sectional area of exhaust connecting passage 410,510 and main bulge 420 does not wait each other, so at refrigerant conveying gas to the process of exhaust connecting passage 410,510 and main bulge 420, just reached the effect of noise reduction, this has reduced the fluctuation pressure of refrigerant gas widely.
Before refrigerant gas that the refrigerant gas that will drain into the compressor outside is discharged into back refrigerant gas discharge chamber 320 and will drains into the compressor outside is drained into during refrigerant gas discharge chamber 220, the preferred embodiments of the present invention adopt a plurality of steps to reduce the fluctuation pressure of refrigerant gas, have obtained the effect that reduces the refrigerant gas fluctuation pressure admirably with this.
Figure 10 is the side sectional view of second embodiment of the invention compressor.
As shown in figure 10, in the second embodiment of the present invention, except following difference, the structure of compressor and course of action are identical with the first embodiment of the present invention, this difference is: main bulge 420 and front-bank rotor housing 400 are connected with final vacuum connecting passage 510 with front exhaust connecting passage 410 in the rear-bank rotor housing 500, and main bulge 420 is individually formed on the peripheral surface of front-bank rotor housing 400 or rear-bank rotor housing 500.
In this mode, because reduced the fluctuation pressure of refrigerant emission gas by outlet pipe 240,340 and preceding auxiliary bulge 250, the auxiliary bulge 350 in back, so compare with the air collecting chamber or the muffler of routine, the size of main bulge 420 has reduced greatly, therefore, this mode can reduce the size of compressor whole assembly.
Though the preferred embodiments of the present invention are applicable in such compressor arrangement, wherein front case 200 and rear case 300 interconnect according to by front case 200 and rear case 300 a kind of like this mode being sealed in the end of front-bank rotor housing 400 and rear-bank rotor housing 500, but, these preferred embodiments also can be applied in such compressor means in an identical manner, and wherein front case 200 and rear case 300 inside are arranged and be assemblied in to front-bank rotor housing 400 and rear-bank rotor housing 500.
As top clearly explanation, before refrigerant gas that the refrigerant gas that will drain into the compressor outside is discharged into back refrigerant gas discharge chamber and will drains into the compressor outside is drained into during refrigerant gas discharge chamber, the compressor of the preferred embodiments of the present invention can reduce the fluctuation pressure of refrigerant gas in the mode of a plurality of steps, obtain the effect that reduces the refrigerant gas fluctuation pressure admirably with this, reduced the noise that causes by the refrigerant gas pulsation simultaneously significantly.
Thereby, needn't form the independent expansion space part that has than the major path sectional area in the compressor outside, even and be provided with independently expansion space part in the compressor outside, compressor of the present invention is very compact on size of components.
Foregoing embodiment only is exemplary, not as a limitation of the invention.Instruction of the present invention can easily be applied in the device of other type.Specification of the present invention is used as explanation, is not used for limiting the protection domain of claim.To those skilled in the art, obviously can make a lot of replacements, modification and conversion to the present invention.
Claims (10)
1. compressor comprises:
The front case of sealing front-bank rotor housing one end;
The rear case of sealing rear-bank rotor housing one end;
Be arranged to interconnected front-bank rotor housing and rear-bank rotor housing between front case and rear case;
The refrigerant gas entry end and the outlet end that in front-bank rotor housing and rear-bank rotor housing, form on the peripheral surface of at least one;
In preceding refrigerant gas absorption chamber, pass the front exhaust pipe of first dividing plate, refrigerant gas discharge chamber before above-mentioned first dividing plate defines so that its isolate with preceding refrigerant gas absorption chamber, with this refrigerant gas in the outside conveying of compressor is drained into the preceding refrigerant gas discharge chamber of front case;
In the refrigerant gas absorption chamber of back, pass the front exhaust pipe of second partition, above-mentioned second partition defines back refrigerant gas discharge chamber so that it is isolated with back refrigerant gas absorption chamber, with this to the outside refrigerant gas of carrying in the back refrigerant gas discharge chamber that is drained into rear case of compressor;
The auxiliary bulge in preceding auxiliary bulge that communicates with the outlet side of front exhaust pipe and final vacuum pipe and back;
Be arranged on front-bank rotor housing exhaust connecting passage interior with rear-bank rotor housing and that link to each other with the auxiliary bulge of preceding auxiliary bulge and back; With
The main bulge that between the exhaust connecting passage, is provided with according to the mode that communicates with the refrigerant gas outlet end.
2. compressor according to claim 1, wherein main bulge extends to an end of the exhaust connecting passage of front-bank rotor housing or rear-bank rotor housing, constitutes an integral body in front-bank rotor housing or rear-bank rotor housing.
3. compressor according to claim 1, wherein main bulge is formed on the outside of front-bank rotor housing or rear-bank rotor housing.
4. compressor according to claim 1, wherein at least one or a plurality of being positioned on the such position in front exhaust pipe and the final vacuum pipe, i.e. beeline place between the central part of the preceding refrigerant gas discharge chamber of front case and rear case and back refrigerant gas discharge chamber and its entry end.
5. compressor according to claim 1, wherein before in the auxiliary bulge of auxiliary bulge and back the volume of at least one or a plurality of volume ratio front exhaust pipe and final vacuum pipe big.
6, compressor according to claim 1, wherein at least one in the exhaust connecting passage or a plurality of sectional area ratio front exhaust pipe or the two the same sizes big with final vacuum tube passage sectional area.
7. compressor according to claim 1, wherein big or the two the same size of the volume sum of auxiliary bulge and the auxiliary bulge in back before the volume ratio of main bulge.
8. compressor according to claim 1, wherein in front exhaust pipe and the final vacuum pipe in the auxiliary bulge at least one or a plurality of and preceding auxiliary bulge and back any one lower surface communicate.
9. compressor according to claim 1, wherein in front exhaust pipe and the final vacuum pipe at least one or a plurality ofly have such channel cross-sectional area, this channel cross-sectional area becomes greatly or increases step by step from inlet to outlet.
10. compressor according to claim 1, wherein the length of passage and the final vacuum pipe of rear case equate with passage length between the refrigerant gas outlet end between the front exhaust pipe of front case and the refrigerant gas outlet end.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR0009992/2003 | 2003-02-18 | ||
| KR1020030009992A KR100659570B1 (en) | 2003-02-18 | 2003-02-18 | Compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1526951A true CN1526951A (en) | 2004-09-08 |
| CN100543305C CN100543305C (en) | 2009-09-23 |
Family
ID=32733143
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200410033021XA Expired - Fee Related CN100543305C (en) | 2003-02-18 | 2004-02-18 | Compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20040161346A1 (en) |
| EP (1) | EP1450043B1 (en) |
| JP (1) | JP3921522B2 (en) |
| KR (1) | KR100659570B1 (en) |
| CN (1) | CN100543305C (en) |
| DE (1) | DE602004010443T2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994047A (en) * | 2014-05-26 | 2014-08-20 | 合肥达因汽车空调有限公司 | Rotating inclined disc type compressor |
| CN113550801A (en) * | 2021-08-17 | 2021-10-26 | 南京久鼎制冷空调设备有限公司 | CO with turbine expansion mechanism2Refrigeration piston compressor |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101172693B1 (en) | 2005-07-25 | 2012-08-09 | 한라공조주식회사 | Compressor |
| KR101184577B1 (en) * | 2005-07-25 | 2012-09-21 | 한라공조주식회사 | Compressor |
| JP4663462B2 (en) * | 2005-09-21 | 2011-04-06 | サンデン株式会社 | Reciprocating compressor |
| KR100872478B1 (en) * | 2006-06-15 | 2008-12-05 | 한국델파이주식회사 | Refrigerant inside Discharge Structure of Swash Plate type Compressor |
| KR101058652B1 (en) | 2008-09-25 | 2011-08-22 | 한라공조주식회사 | compressor |
| KR101221311B1 (en) | 2010-09-13 | 2013-01-10 | 한라공조주식회사 | Swash plate type compressor |
| CN101943153B (en) * | 2010-09-15 | 2012-07-04 | 奉化市华南汽车空调配件有限公司 | Split air condition compressor of automobile |
| JP3168382U (en) * | 2011-03-30 | 2011-06-09 | 株式会社ヴァレオジャパン | Reciprocating compressor |
| JP6164135B2 (en) | 2014-03-27 | 2017-07-19 | 株式会社豊田自動織機 | Compressor |
| JP2016053321A (en) * | 2014-09-03 | 2016-04-14 | サンデンホールディングス株式会社 | Compressor |
| CN108361178A (en) * | 2018-03-26 | 2018-08-03 | 合肥达因汽车空调有限公司 | A kind of oil-gas separated-type noise reduction swash-plate-type compressor |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60152077U (en) * | 1984-03-21 | 1985-10-09 | 株式会社豊田自動織機製作所 | Swash plate compressor |
| US4929157A (en) * | 1987-11-23 | 1990-05-29 | Ford Motor Company | Pulsation damper for air conditioning compressor |
| JPH10103228A (en) * | 1996-09-30 | 1998-04-21 | Toyota Autom Loom Works Ltd | Double ended piston type compressor |
| US6068453A (en) * | 1997-06-30 | 2000-05-30 | Halla Climate Control Corp. | Reciprocating piston type refrigerant compressor |
| US6608453B2 (en) * | 1997-08-26 | 2003-08-19 | Color Kinetics Incorporated | Methods and apparatus for controlling devices in a networked lighting system |
| JP3924985B2 (en) * | 1999-04-15 | 2007-06-06 | 株式会社豊田自動織機 | Compressor discharge pulsation damping device |
| JP2000320456A (en) * | 1999-05-11 | 2000-11-21 | Toyota Autom Loom Works Ltd | Piston-type compressor |
-
2003
- 2003-02-18 KR KR1020030009992A patent/KR100659570B1/en not_active IP Right Cessation
-
2004
- 2004-02-13 US US10/777,246 patent/US20040161346A1/en not_active Abandoned
- 2004-02-17 EP EP04003502A patent/EP1450043B1/en not_active Expired - Fee Related
- 2004-02-17 DE DE602004010443T patent/DE602004010443T2/en not_active Expired - Lifetime
- 2004-02-17 JP JP2004040404A patent/JP3921522B2/en not_active Expired - Fee Related
- 2004-02-18 CN CNB200410033021XA patent/CN100543305C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994047A (en) * | 2014-05-26 | 2014-08-20 | 合肥达因汽车空调有限公司 | Rotating inclined disc type compressor |
| CN103994047B (en) * | 2014-05-26 | 2016-09-07 | 合肥达因汽车空调有限公司 | A kind of swash-plate-type compressor |
| CN113550801A (en) * | 2021-08-17 | 2021-10-26 | 南京久鼎制冷空调设备有限公司 | CO with turbine expansion mechanism2Refrigeration piston compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1450043A3 (en) | 2005-10-19 |
| CN100543305C (en) | 2009-09-23 |
| JP2004251282A (en) | 2004-09-09 |
| KR20040074382A (en) | 2004-08-25 |
| JP3921522B2 (en) | 2007-05-30 |
| EP1450043B1 (en) | 2007-12-05 |
| DE602004010443D1 (en) | 2008-01-17 |
| KR100659570B1 (en) | 2006-12-19 |
| US20040161346A1 (en) | 2004-08-19 |
| EP1450043A2 (en) | 2004-08-25 |
| DE602004010443T2 (en) | 2008-11-27 |
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Owner name: HALLA VISTEON CLIMATE CONTROL CORP. Free format text: FORMER NAME: HANNA AIR CONDITIONER CO. LTD. |
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| CP01 | Change in the name or title of a patent holder |
Address after: South Korea field wide area Patentee after: Halla Climate Control Corp Address before: South Korea field wide area Patentee before: Hanna Air Conditioner Co., Ltd. |
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| CP01 | Change in the name or title of a patent holder |
Address after: South Korea field wide area Patentee after: Hanang System Co., Ltd. Address before: South Korea field wide area Patentee before: Halla Climate Control Corp |
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Address after: South Korea field wide area Patentee after: Hanang Beijing Great Automotive Components Company Limited Address before: South Korea field wide area Patentee before: Hanang System Co., Ltd |
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| CF01 | Termination of patent right due to non-payment of annual fee |
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| CF01 | Termination of patent right due to non-payment of annual fee |