CN201486799U - Inclined disc type double-head piston type compressor - Google Patents
Inclined disc type double-head piston type compressor Download PDFInfo
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- CN201486799U CN201486799U CN2009200434908U CN200920043490U CN201486799U CN 201486799 U CN201486799 U CN 201486799U CN 2009200434908 U CN2009200434908 U CN 2009200434908U CN 200920043490 U CN200920043490 U CN 200920043490U CN 201486799 U CN201486799 U CN 201486799U
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- swash plate
- piston
- rotor housing
- bank rotor
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Abstract
The utility model relates to an inclined disc type double-head piston type compressor, which comprises a main shaft (8), an inclined disc (7), a front cylinder body (1) and a back cylinder body (2), wherein a plurality of piston cavities are arranged between the front cylinder body (1) and the back cylinder body (2), a double-head hollow piston (5) is respectively arranged in each piston cavity, and the inclined disc (7) is arranged on the main shaft (8). The utility model is characterized in that two small hemispherical pits are symmetrically arranged in each double-head hollow piston (5), a small hemisphere (6) is respectively arranged in each small hemispherical pit, the inclined disc (7) is inserted between the two small hemispheres (6), the sum of the height of the two small hemispheres (6) and the thickness of the inclined disc (7) does not exceed the spherical diameter of the small hemispheres (6), atmospheric pressure support ring grooves used for compensating and bearing the load are arranged on the inclined disc (7), a supporting piston ring (10) with the diameter not larger than the inner diameter of the piston cavity is arranged on each double-head hollow piston (5), and a wear-resistance layer is arranged on the contact surface of the inclined disc (7) and the small hemispheres (6). The utility model has the advantages of simple structure, convenient manufacture and installation, long service life and high efficiency.
Description
Technical field
The utility model relates to a kind of Vehicular air-conditioner compressor, especially inclined disc type Vehicular air-conditioner compressor, specifically a kind of swash plate double-headed piston compressor.
Background technique
As everyone knows, common Vehicular air-conditioner compressor has rotary compressor (Scroll Compressor/Rotary Vane Compressor), rocking plate type compressor (Wobble Plate Compressor) and oblique tray type compressor (Swash Plate Compressor), wherein rotary compressor is that type is efficient before grew up in recent years a kind of, the vehicular compressed machine of small size, but its shortcoming is the manufacturing process complexity, the cost height, inconvenient maintenance, and oblique tray type compressor is a kind of of a kind of traditional vehicular compressed machine, it has simple in structure, make, install, advantage easy to maintenance, therefore its efficient and size still have sizable market at present between rotary and rocking plate type compressor.
Existing oblique tray type compressor generally is five cylinder bipitch structures, swash plate inserts in two hemisphere that separate and forms spherical hinge structure, when main shaft drives the swash plate rotation, swash plate drives double-head piston move left and right in piston cavity, swash plate rotates a circle, piston is finished one back and forth, realize twice suction and discharge, therefore its overall dimensions can shorten to half with discharge capacity pot type piston formula compressor, but owing to be subjected to the speed approximately of traditional design theory, the size of existing spherical hinge structure is bigger than normal, and especially spherical hinge structure adopts big semiglobe mostly, two big hemisphere add the diameter of the thickness of swash plate greater than a spheroid, inconvenience not only make is installed in this design, is easy to stuckly, and makes the entity size of piston become big, overall weight is difficult to descend, influence the raising of efficient, in addition, still had many local deficiencies that exist, wear resistance as swash plate, there are many deficiencies in aspects such as piston traveling comfort, are necessary to be improved.
Summary of the invention
Problems such as the purpose of this utility model is that the efficient that exists at existing oblique tray type compressor is not high, oversize, assembling difficulty is big, and the life-span is short design a kind of swash plate double-headed piston compressor.
The technical solution of the utility model is:
A kind of swash plate double-headed piston compressor, comprise main shaft 8, swash plate 7, front-bank rotor housing 1 and rear-bank rotor housing 2, front-bank rotor housing 1 links to each other with rear-bank rotor housing 2, front-bank rotor housing 1 is connected with protecgulum 4, rear-bank rotor housing 2 is connected with bonnet 3, be provided with the several pistons chamber between front-bank rotor housing 1 and the rear-bank rotor housing 2, double end box type piston 5 all is installed in each piston cavity, swash plate 7 is installed on the main shaft 8, on the main shaft 8, the both sides of swash plate 1 respectively are equipped with a thrust-bearing 11, main shaft 8 is bearing on two heavy bearings 9 that are installed in respectively in front-bank rotor housing 1 and the rear-bank rotor housing 2, it is characterized in that being arranged with in the described double end box type piston 5 two smaller part ball-and-sockets, be separately installed with a smaller part spheroid 6 in each smaller part ball-and-socket, swash plate 7 inserts between described two smaller part spheroids 6, and the insertion end of two smaller part spheroids 6 and swash plate 7 forms ball pivot 12 structures, and the height of two smaller part spheroids 6 adds that the thickness of swash plate 7 is not more than the sphere diameter of described smaller part spheroid 6; Be that a side of acute angle offers near thrust-bearing 11 positions and is used to compensate and bearing load air pressure just supports annular groove at the angle of described swash plate 7 and main shaft 8; The support piston ring 10 that diameter is not more than the piston cavity internal diameter is installed on the described double end box type piston 5; On contacted of described swash plate 7 and little hemisphere, be provided with wearing layer.
The thickness of described swash plate 7 is by traditional reducing between the 6-10mm more than 10 millimeters, and the displacement variation of its thickness and compressor is irrelevant, and the discharge capacity of compressor is only relevant with the inclination angle of swash plate.
Described wearing layer comprises the porous copper metal human body and the lubriation material that be coated in described porous copper metal human body on of sintering at swash plate 7 matrix surfaces, and described lubriation material teflon and molybdenum disulfide combine, and the part by weight of the two is 1: 1～9.
The thickness of described porous copper metal human body is 0.01～0.03mm.
Swash plate 7 with inclination angle links together with the main shaft 8 that rotates, be supported on front-bank rotor housing 1 and the rear-bank rotor housing 2 by two heavy bearings 9, simultaneously by thrust-bearing 11 restriction and bear the support reaction that comes from swash plate 7, the swash plate 7 of rotation carries out compressed refrigerant by ball pivot 12 to-and-fro motion that is converted into the piston 5 that distributes vertically that will rotatablely move.Front-bank rotor housing 1 and rear-bank rotor housing 2 are undertaken airtight by protecgulum 4 and bonnet 3, form the autonomous channel, and bolt 13 links together front-bank rotor housing 1 and rear-bank rotor housing 2 by protecgulum 4 and bonnet 3.Because gas is subjected to the compression of piston 5, the reaction force of piston 5 is delivered on the swash plate 7 by ball pivot 12, and the moment of flexure that produces is by heavy-duty bearing 9 carryings on the one hand, and axial force is by alternately carrying of thrust-bearing 11 on the other hand.
The beneficial effects of the utility model:
1, the utility model is by reducing the hemispheroidal volume of ball pivot part, changed traditional big semiglobe, adopt little semiglobe, and make itself and swash plate form a complete spherical hinge structure that is of a size of sphere diameter, not only operation is more steady, and reduced axial dimension, make the entity part size of piston can dwindle about 33%, weight reduction 33%, help reducing operating inertial force, improve system coefficient (COP) more than 3%, make also that simultaneously installation is more convenient, the dead angle can not occur installing, stuck phenomenon can not occur.
2, the utility model has improved wear resistance by carry out the processing of wearing layer on swash plate.
3, the utility model broken through the size of piston ring in the past must be greater than the idea of piston cavity size, be not more than the piston ring of piston cavity internal diameter by employing, it is more all steady to make oil film set up, and helps improving the lubrication effect of piston.
4, the utility model supports annular groove by increase air pressure on thrust-bearing, favourable timely compensation and bear live load.
5, the utility model has adopted the swash plate of little thickness size, makes overall weight alleviate, and can make the swash plate size constancy and only realize the purpose that discharge capacity is adjusted, the organization arrangement that helps producing by the inclination angle that changes swash plate.
Description of drawings
Fig. 1 is a structural representation of the present utility model.
Fig. 2 is a lightweight holotype structure of piston schematic representation of the present utility model.
Fig. 3 is the structural representation of ball pivot of the present utility model.
Fig. 4 is the size relationship figure of the size and the piston cavity of piston ring of the present utility model.
Fig. 5 is the structural representation of swash plate of the present utility model.
Fig. 6 is the structural representation figure of the lubricated face of thrust-bearing of the present utility model.
Fig. 7 has structural representation for the lubricated face of heavy-duty bearing of the present utility model.
Embodiment
Below in conjunction with drawings and Examples the utility model is further described.
Shown in Fig. 1-7.
A kind of swash plate double-headed piston compressor, comprise main shaft 8, swash plate 7, front-bank rotor housing 1 and rear-bank rotor housing 2, front-bank rotor housing 1 links to each other with rear-bank rotor housing 2, front-bank rotor housing 1 is connected with protecgulum 4, rear-bank rotor housing 2 is connected with bonnet 3, be provided with the several pistons chamber between front-bank rotor housing 1 and the rear-bank rotor housing 2, double end box type piston 5 all is installed in each piston cavity, swash plate 7 is installed on the main shaft 8, on the main shaft 8, the both sides of swash plate 1 respectively are equipped with a thrust-bearing 11, main shaft 8 is bearing on two heavy bearings 9 that are installed in respectively in front-bank rotor housing 1 and the rear-bank rotor housing 2, be arranged with two smaller part ball-and-sockets in the described double end box type piston 5, be separately installed with a smaller part spheroid 6 in each smaller part ball-and-socket, swash plate 7 inserts between described two smaller part spheroids 6, and the insertion end of two smaller part spheroids 6 and swash plate 7 forms spherical hinge structure 12, and the height of two smaller part spheroids 6 adds that the thickness of swash plate 7 is not more than the sphere diameter of described smaller part spheroid 6; Be that a side of acute angle offers near thrust-bearing 11 positions and is used to compensate and the air pressure of bearing load supports annular groove 14 at the angle of described swash plate 7 and main shaft 8; The support piston ring 10 that diameter is not more than the piston cavity internal diameter is installed on the described double end box type piston 5; On 6 contacted of described swash plate 7 and smaller part spheroids, be provided with wearing layer.As shown in Figure 1.
In addition, the thickness of swash plate 7 can be by traditional reducing between the 6-10mm more than 10 millimeters when specifically implementing, and the displacement variation of its thickness and compressor is irrelevant, and the discharge capacity of compressor is only relevant with the inclination angle of swash plate.
Wearing layer is by forming at porous copper metal human body that swash plate 7 matrix surfaces form and the lubriation material that is coated on the described porous copper metal human body by sintering method, the thickness of porous copper metal human body is good with 0.01～0.03mm, described lubriation material can be the mixture of teflon and molybdenum disulfide, and the weight ratio of the two is 1: 1～9.
Details are as follows:
See figures.1.and.2, the cylinder bore dia of front-bank rotor housing 1 and rear-bank rotor housing 2 is equal CD, and the diameter of piston 5 is PD, for guaranteeing lubricated and sealing, has the gap between piston and cylinder hole, and this gap will guarantee the foundation of lubricant film.
In the utility model, because the existence in gap has formed long and narrow passage between the cylinder hole of piston 5 and front-bank rotor housing 1 and rear-bank rotor housing 2, quick compressed gas is by this gallery the time, be subjected to the obstruction of oil film on the one hand, the long more resistance of passage is big more on the other hand.This just means that the loss when as far as possible little and long as far as possible passage will make compressor compresses reduces relatively, and energy conversion efficiency will increase.Can set up long and narrow piston 5 pressure channels by rational size CD, PD configuration.Long piston and cylinder hole are stressed when relative movement to be to be better than short piston, and long and narrow clearance channel not only can reduce the leakage of pressurized gas, but also the stability can improve pistons work the time.
Formula F=ma knows by mechanics, and m reduces and will the inertial force of object be reduced, the minimizing of useless power consumption just.In the utility model, piston adopts hollow making, and weight reduces to 60g by contrast piston 90g, and weight reduces by 33%, helps improving the refrigeration transformation efficiency.
The articulated mechanism of piston is designed to sphere, and the process of processing becomes simply, reliable.
In the double-head piston refrigeration compressor of the compressor of routine, the variation of swashplate angle will cause relevant a plurality of dimensional changes.
In the utility model (Fig. 5), selected swash plate 7 thickness SL thickness SL when inclination angle A changes is constant, and this can reduce makes and difficulty of processing, improves versatility.
Whole ball-and-socket hinge device 12 is divided into three parts (Fig. 3), and the non-whole spheroid 6 of two symmetries is containing swash plate 7, and all constitute a complete spheroid again and are included among the ball-and-socket of piston 5, like this, can be in any direction goes up and rotates and can not deviate from.
Piston in cylinder since gravity or stressed all can Off center, form the single face contact: this single face contact can cause gap deflection one side, forms 2 times setting gap, increases leakage.This single face contact also will cause stressed monolateral, destroy the oil film of having set up, and cause monolateral rapid inefficacy wearing and tearing, reduce the compressor life-span.Therefore, it is necessary centring means being installed.In the utility model, adopt centering type piston ring to solve above-mentioned two problems.Piston ring at the casing bore periphery, bears the biasing driving force that comes from swash plate with the gap uniform distribution simultaneously.See Fig. 4, the maximum diameter of piston ring is identical with the maximum diameter CD in cylinder hole.The making of piston ring is not limited to common punching press method for making, and is also extensible for adopting the piston ring of the more accurate CD size that the injection moulding mode makes.
Compressor approaches not have oil condition when initial start, initial the lubricating when therefore guaranteeing to start is necessary.Professional visitors and some patents of having announced have adopted various methodologies, spray Teflon, non-ferrous metal surface flame lacquer special type lubriation material or the like after including zinc-plated behind the non-ferrous metal alumilite process, non-ferrous metal alumilite process, but there is processing difficulties in none, the cost height, bearing dirty property of surface and wearing and tearing back self-regeneration are poor, and performance and life-span do not reach expection and think.The utility model adopts the metal sintering method to solve this difficult problem preferably, and the utility model is by form porous copper metal human body at ferrous metal surface, afterwards at the surface-coated lubriation material.Simultaneously, the metal human body is not limited to ferrous metal, can also be non-ferrous metal or sintered metal product.
In the course of the work, the lubriation material and the common lubricate of oil-containing micropore on surface, simultaneously, the human body of sintering is supporting ball pivot with the power transmission.When running up, inner oil will be thrown out of again, and low-speed running is stored oil again again and provide lubricated when initial.
Front-bank rotor housing 1, rear-bank rotor housing 2 are by bolt 13 linking together tightly, and the swash plate 7 of rotation is seized on both sides by the arms in the centre by two thrust-bearings 11, and thrust load is dissolved by thrust-bearing 11.When compressor was worked lastingly, the driving load of alternation formed the micron order wearing and tearing on each surface, and after the gap that forms when wearing and tearing surpasses the permission gap, compressor will produce strong noise and vibrate until compressor failure.For this reason, (Fig. 6) adopted the atmospheric pressure compensating scheme in the utility model.The bearing of rotation forms low pressure area, enters the thrust-bearing back side by offering air chamber by gas, forms pressure difference, and load is played " damping " effect, reduces noise, improves the life-span.
In the field of business, needle roller bearing without inner ring is widely applied on automobile air conditioner compressor.But its operation produces the very strong noise of permeability, to lubricated having relatively high expectations.In the utility model, by adopt can anti-initial start dry friction then solved this problem well from oil-impregnated bearing, it can not only reduce noise, and can improve working life.Under original state (Fig. 7), it is initial lubricated that the lubriation material of bearing surface provides, and simultaneously, contained lubricant oil flows out rapidly and is lubricated, cools off in the porous material, goes round and begins again.Simultaneously, the moment of flexure of being transmitted by swash plate 7 is by the internal surface of bearing and oil film carrying, and lifting surface area is big, carrying be oil film, stressing conditions is better than needle bearing, the long lifetime that obtains expecting, low noise.
The utility model does not relate to the part prior art that maybe can adopt all same as the prior art to be realized.
Claims (2)
1. swash plate double-headed piston compressor, comprise main shaft (8), swash plate (7), front-bank rotor housing (1) and rear-bank rotor housing (2), front-bank rotor housing (1) links to each other with rear-bank rotor housing (2), front-bank rotor housing (1) is connected with protecgulum (4), rear-bank rotor housing (2) is connected with bonnet (3), be provided with the several pistons chamber between front-bank rotor housing (1) and the rear-bank rotor housing (2), double end box type piston (5) all is installed in each piston cavity, swash plate (7) is installed on the main shaft (8), the both sides of swash plate (7) respectively are equipped with a thrust-bearing (11), main shaft (8) is bearing on two heavy bearings (9) that are installed in respectively in front-bank rotor housing (1) and the rear-bank rotor housing (2), it is characterized in that being arranged with in the described double end box type piston (5) two smaller part ball-and-sockets, be separately installed with a little hemisphere (6) in each smaller part ball-and-socket, swash plate (7) inserts between described two little hemispheres (6), the insertion end of two little hemispheres (6) and swash plate (7) forms ball pivot (12) structure, and the height of two little hemispheres (6) adds that the thickness of swash plate (7) is not more than the sphere diameter of described little hemisphere (6); Be that a side of acute angle offers near thrust-bearing (11) position and is used to compensate and bearing load air pressure just supports annular groove at the angle of described swash plate (7) and main shaft (8); The support piston ring (10) that diameter is not more than the piston cavity internal diameter is installed on the described double end box type piston (5); On contacted of described swash plate (7) and little hemisphere (6), be provided with wearing layer.
2. swash plate double-headed piston compressor according to claim 1, the thickness that it is characterized in that described swash plate (7) is 6-10mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200434908U CN201486799U (en) | 2009-07-09 | 2009-07-09 | Inclined disc type double-head piston type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200434908U CN201486799U (en) | 2009-07-09 | 2009-07-09 | Inclined disc type double-head piston type compressor |
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| Publication Number | Publication Date |
|---|---|
| CN201486799U true CN201486799U (en) | 2010-05-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009200434908U Expired - Fee Related CN201486799U (en) | 2009-07-09 | 2009-07-09 | Inclined disc type double-head piston type compressor |
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| CN (1) | CN201486799U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101598121B (en) * | 2009-07-09 | 2011-04-13 | 南京奥特佳冷机有限公司 | Swash plate double-headed piston compressor |
| US11408407B2 (en) | 2016-07-25 | 2022-08-09 | Caire Inc. | Wobble plate compressor and oxygen concentrator using the same |
-
2009
- 2009-07-09 CN CN2009200434908U patent/CN201486799U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101598121B (en) * | 2009-07-09 | 2011-04-13 | 南京奥特佳冷机有限公司 | Swash plate double-headed piston compressor |
| US11408407B2 (en) | 2016-07-25 | 2022-08-09 | Caire Inc. | Wobble plate compressor and oxygen concentrator using the same |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100526 Termination date: 20120709 |