CN102444581A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN102444581A CN102444581A CN201010503273XA CN201010503273A CN102444581A CN 102444581 A CN102444581 A CN 102444581A CN 201010503273X A CN201010503273X A CN 201010503273XA CN 201010503273 A CN201010503273 A CN 201010503273A CN 102444581 A CN102444581 A CN 102444581A
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Abstract
The invention discloses a rotary compressor; a compressing mechanism part is arranged inside a sealed housing, wherein the compressing mechanism part comprises an air cylinder with an air cylinder compression cavity, a piston which is accommodated in the air cylinder compression cavity, an eccentric crankshaft which drives the piston to rotate in an eccentric manner by an eccentric shaft, and a primary bearing and a secondary bearing supporting the eccentric crankshaft; the primary bearing and the secondary bearing are arranged on the air cylinder; a tip end of a slip sheet is fixed against the periphery of the piston; the piston comprises a piston which can be at least divided into two sections in an extensible manner on the axis of the piston. An oil sot which is provided with an opening towards the inside of the small piston is arranged on the contact surface between the two sections of the small piston; the end part of at least one small piston in the two sections of the small piston is provided with an inner circular slot which faces towards the inside of the small piston and is used for reducing the thickness of the end part wall. The rotary compressor has the characteristics of a rational and simple structure, flexible operation, effectively improving the high pressure air loss leaking to the air cylinder compression cavity from the inside of the rotary compressor piston, improving the energy efficiency of the compressor and a broad application range.
Description
Technical field
The present invention relates to a kind of rotary compressor, relevant with the efficiengy-increasing of rotary compressor in being applied in air conditioner or refrigerating plant.
Background technique
From preventing the viewpoint of global greenhouse effectization, the efficiengy-increasing of the rotary compressor that carries in the air conditioner is a very big problem.The depth pistion gap that forms between the piston of rotary compressor and the bearing, the efficient that expands again to rotary compressor of the pressurized gas that leak to the cylinder compression chamber from internal piston through this depth pistion gap has very big influence.
Summary of the invention
The object of the invention aim to provide a kind of simple and reasonable, flexible operation, fabricating cost low, can effectively improve the pressurized gas loss of leaking to the cylinder compression chamber from the inside of rotary piston for compressor; Improve the efficiency of compressor and a kind of rotary compressor applied widely, to overcome deficiency of the prior art.
A kind of rotary compressor by this purpose design; Be provided with compression mechanical part in the housing of sealing; This compression mechanical part comprises the cylinder that has the cylinder compression chamber, be accommodated in piston in the cylinder compression chamber, make the eccentric crankshaft of eccentric rotary and main bearing and the supplementary bearing that supports eccentric crankshaft through the eccentric shaft driven plunger; Main bearing and supplementary bearing are arranged on the cylinder; The tip of slide plate is resisted against on the periphery of piston, and to be piston be made up of two sections the small piston of being divided at least that can stretch at its axis its structure characteristic.
Surface of contact between said two sections small pistons is provided with the oil groove towards the small piston internal openings.
The end of at least one small piston in said two sections small pistons is provided with inner and in order to the interior circular groove of this end wall thickness of attenuate towards this small piston.
The internal diameter of internal diameter＜this small piston of the end of at least one small piston in said two sections small pistons.
Said rotary compressor is connected in series the formation refrigeration plant successively with condenser, expansion valve, vaporizer.
The piston that the present invention is generally inside high pressure is divided into two sections small pistons along its axial direction; These two sections small pistons can stretch according to the variation in pressure of cylinder compression chamber; Thereby the depth pistion gap is optimized; Therefore can reduce the gas that comes out from the depth pistion clearance leakage, thereby the efficient that prevents compressor reduces.And rotary compressor also starts easily.
That the present invention has is simple and reasonable, flexible operation, fabricating cost are low, can effectively improve inside from rotary piston for compressor to the pressurized gas loss that the cylinder compression chamber leaks, and improves the efficiency and the advantage of wide range of application of compressor.
Description of drawings
Fig. 1 is one embodiment of the invention structural representation.
Fig. 2 is the broken section structure for amplifying schematic representation of the compression mechanical part among the present invention.
Fig. 3 is the cross-sectional structure schematic representation of the compression mechanical part among the present invention.
Fig. 4 is the efficiency curve diagram of rotary compressor in the past.
Fig. 5 is the piston stress analysis chart among the present invention.
Fig. 6 is the example of the application implementation among the present invention structural representation.
Among the figure: 1 is rotary compressor, and 2 is housing, and 5 is condenser, and 6 is vaporizer, and 7 is expansion valve, and 13 is liquid-storage container, and 14 is sucking pipe; 15 is exhaust port, and 16 is eccentric crankshaft, and 17 is eccentric shaft, and 18 is the eccentric shaft oilhole, and 19 is oil groove, and 20 is the piston cutting lines; 21 is compression mechanical part, and 22 is motor section, and 23 is cylinder, and 24 is the cylinder compression chamber, and 25 is main bearing, and 26 is supplementary bearing; 28 is piston, and 28a is first small piston, and 28b is second small piston, and 28c is a thin-walled, and 28d is the upper end portion, and 28e is the underpart; 29 is slide plate, and 31a is a low pressure chamber, and 31b is a hyperbaric chamber, and 32 is interior circular groove, and 33 is oil, and 40 is the cylinder screw.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is further described.
Referring to Fig. 1, rotary compressor 1 is made up of compression mechanical part in the housing that is installed in columniform sealing 2 21 and the motor section 22 that is configured in compression mechanical part 21 tops.Compression mechanical part 21 comprises cylinder 23, carry out in cylinder compression chamber 24 inside eccentric rotation piston 28, carry out the slide plate 29 of reciprocating action, the eccentric crankshaft 16 of driven plunger 28 and the main bearing 25 and the supplementary bearing 26 of sliding support eccentric crankshaft with the periphery butt of this piston.
Piston 28 is divided into two sections small pistons through piston cutting lines 20, i.e. the first small piston 28a of coaxial line and the second small piston 28b, and two sections small pistons that fit together just move as same piston.
The compression mechanical part 21 that more than constitutes is accomplished through 40 assemblings of cylinder screw.Accomplish on the inwall of housing 2 that the peripheral part of compression mechanical part 21 through cylinder 23 after the assembling be fixed on sealing.Oil 33 is stored in the bottom of housing 2.
In the system of carrying rotary compressor 1, the low-pressure gas that sucks from suction pipe 14 is compressed into pressurized gas enter the housing 2 of sealing from exhaust port 15 inside in cylinder compression chamber 24.Therefore, the internal pressure of the housing 2 of sealing is the high pressure side that equates with head pressure.After this, the pressurized gas from outlet pipe (not having diagram) is discharged get into liquid-storage container 13 through expansion valve 7, vaporizer 6 backs successively from condenser 5 beginnings, flow into sucking pipe 14 at last, are inhaled into cylinder compression chamber 24 once again.
Referring to Fig. 2, be the detail drawing of compression mechanical part 21.The oil 33 that has the eccentric crankshaft 16 of eccentric shaft 17, housing 2 bottoms are detained is upwards inhaled through centrifugal force.Therefore, the inner space of piston 28 has been full of enough oil.Oil from eccentric shaft oilhole 18 comes out does not still lubricate the periphery of eccentric shaft 17, and gives fuel feeding in the oil groove 19 that is arranged on piston cutting lines 20 internal side diameters.
Referring to Fig. 3, be compression mechanical part 21 cross-sectional views.The cylinder compression chamber 24 that is fixed on the central part configuration of the inner cylinder 28 of the housing 2 of sealing is divided into low pressure chamber 31a and hyperbaric chamber 31b through piston 28 and slide plate 29.
The piston 28 that is driven by the eccentric shaft of eccentric crankshaft 16 17 carries out off-centre synchronously with the rotation of motor section 22 along clockwise direction and rotates by direction shown in the arrow among the figure in cylinder compression chamber 24.Low pressure chamber 31a and hyperbaric chamber 31b can change volume at a high speed.Pressure in the hyperbaric chamber 31b by low pressure Ps become with housing in press identical high pressure P d.
Referring to Fig. 4, for displacement volume is approximately the air-conditioning rotary compressor in the past of 20cc, the size of its depth pistion clearance delta r and the relation of compressor efficiency.Depth pistion clearance delta r is the summation in each gap of forming between the planar surface portion of upper and lower planar surface portion and main bearing relative with it and supplementary bearing of piston 28.
As can be seen from the figure, refrigerating capacity, refrigerating capacity just, and power consumption, just consumes electric power is very responsive for the variation of depth pistion clearance delta r.Its result, efficiency COP when depth pistion clearance delta r is in the scope of 14～17 μ m, can think that efficiency COP is qualified for the highest when depth pistion clearance delta r is 15 μ m.
But, when depth pistion clearance delta r than 14 μ m hours because depth pistion clearance delta r is too small, the upper and lower planar surface portion of piston and 2 bearings, the sliding friction that just produces between the planar surface portion of main bearing and supplementary bearing loss will become greatly, power consumption will increase.And the meeting compressor start is bad; The insufficient generation sometimes of the oil slick thickness of the slide member in the compression mechanical part worn and torn.
When depth pistion clearance delta r is bigger than 17 μ m, the pressurized gas that leak into the low pressure chamber of cylinder compression chamber from the upper and lower plane of internal piston through piston will reexpand, thereby reduce refrigerating capacity.Equally, leak into the pressurized gas in the hyperbaric chamber the compression from internal piston, reexpanding has herein also increased power consumption.The hyperbaric chamber of this moment is an intermediate pressure.
So, to the pressurized gas that the cylinder compression chamber leaks, still can not reduce refrigerating capacity, and can increase power consumption and reduce efficiency COP significantly from internal piston.
For solving this problem, need be optimized depth pistion clearance delta r.The present invention is divided into two sections for solving above-mentioned problem with piston, and purpose is that the compression pressure through the cylinder compression chamber reduces depth pistion clearance delta r.
Referring to Fig. 5, in the inside of cylinder compression chamber 24, make the small piston that is divided into two sections since the pressure P d of internal piston along the axial direction of original piston 28 separately, the principle that depth pistion clearance delta r diminishes describes.Eccentric crankshaft has been omitted in explanation among the figure for ease.
The size of arrow representes to act on two sections small pistons among the figure, i.e. the distribution of the pressure on the first small piston 28a and the second small piston 28b.Because the common high pressure side of piston 28 pressure inside, so high pressure P d works to the upper and lower wall of oil groove 19 simultaneously.
But, because the pressure in the low pressure chamber 31a is generally low pressure Ps, act on the planar surface portion of two sections small pistons, just on the end, pressure from the internal piston of high pressure P d to piston outside diminishing progressively, up to identical with the pressure P s of low pressure chamber 31a.Therefore, its pressure distribution has inclination.This pressure pattern is called pattern L.
The pressure of hyperbaric chamber 31b and exhaust pressure Pd, just with piston 28 pressure inside Pd, when equating, the pressure that the upper and lower wall of oil supply 19 and the above and below of piston 28 take place can balance.This pressure pattern is called pattern H.
Pressure in the hyperbaric chamber 31b begins between exhaust pressure Pd, to change from low pressure Ps according to the angle of swing of piston 28, and therefore, pressure pattern changes between pattern L and pattern H.
Because the pressure P d in the piston 28 can be not lower than the pressure of low pressure chamber 31a and hyperbaric chamber 31b; So two sections small pistons; Just the first small piston 28a and the second small piston 28b separate in the direction of main bearing 25 and supplementary bearing 26 respectively, and depth pistion gap separately can diminish.
Owing in this depth pistion gap, formed oil film, so in the depth pistion gap, the scope internal clearance that does not carry out Metal Contact in the piston planar surface portion and the planar surface portion of main bearing, supplementary bearing is minimum.When piston 28 carried out the off-centre rotation, because the form error of the planar surface portion of main bearing and supplementary bearing, two sections small piston one side knee-actions were Yi Bian make the depth pistion gap smaller.
In embodiment 1,, need not change this design so if the depth pistion gap was optimized according to former design.On the basis of the design before this, if appended the technological scheme that is provided of present embodiment 1, the depth pistion gap is optimised so just can obtain the above-mentioned effect of improving.
According to the present invention; When the depth pistion gap is set greatlyyer; Two sections small pistons also can be adjusted automatically, make the depth pistion gap smaller, therefore; The gas that leaks into the cylinder compression chamber from internal piston can reduce, and can improve the loss of the compression efficiency cause of expanding again of the pressurized gas of rotary compressor.
When compressor just started, whole gas pressures was identical, and it is maximum that the depth pistion gap reaches, and the piston slippage loss of this moment is minimum, so can reach the effect that compressor starts easily.
Can occur upper and lowerly separating respectively for the first small piston 28a and the second small piston 28b; And cause having produced the problem in gap at piston cutting lines 20 places; Made following processing in this enforcement: two sections gap values that small piston produces; According to the concrete structure that provides of Fig. 5, its maximum also just is about 8 μ m; And the gap at piston cutting lines 20 places is to be full of by the oil that oil groove 19 supplies, so few to ignoring from the leakage of oil amount in this gap.
Referring to Fig. 6; Application examples for embodiment 1; At the upper end portion of piston 28 28d and underpart 28e, just, appended interior circular groove 32 respectively at the upper end portion 28d of the first small piston 28a and the underpart 28e of the second small piston 28b; Should in circular groove 32 respectively towards the inside of each self-corresponding small piston and in order to the end wall thickness of this small piston of attenuate, and constituted thin-walled 28c in end separately.Consequently; Outside piston 28 is made up of two sections small pistons; Owing to the existence of pressure reduction, the direction to the depth pistion gap smaller produces distortion easily, so its effect is further to have reduced to the gas leakage of cylinder compression chamber 24 from the inside of piston 28 at above-mentioned thin-walled 28c place.
Can the inside diameter D 2 of the underpart 28e of the upper end portion 28d of first small piston or second small piston be reduced with respect to the inside diameter D 1 of first small piston or second small piston; Thereby can strengthen the gas seal length of above-mentioned each end, so can reduce the gas that comes out from the depth pistion clearance leakage.And can accomplish that D2＜D1 also can improve and piston 28 is divided into two sections effect.
Claims (5)
1. rotary compressor; Be provided with compression mechanical part (21) in the housing (2) of sealing; This compression mechanical part (21) comprises the cylinder (23) that has cylinder compression chamber (24), be accommodated in piston (28) in the cylinder compression chamber (24), make the eccentric crankshaft (16) of eccentric rotary and the main bearing (25) and the supplementary bearing (26) of support eccentric crankshaft (16) through eccentric shaft (17) driven plunger (28); Main bearing (25) and supplementary bearing (26) are arranged on the cylinder (23); The tip of slide plate (29) is resisted against on the periphery of piston (28), it is characterized in that piston (28) is made up of two sections the small piston of being divided at least that can stretch at its axis.
2. rotary compressor according to claim 1 is characterized in that the surface of contact between said two sections small pistons is provided with the oil groove (19) towards the small piston internal openings.
3. rotary compressor according to claim 1, the end that it is characterized in that at least one small piston in said two sections small pistons are provided with inner and in order to the interior circular groove (32) of this end wall thickness of attenuate towards this small piston.
4. rotary compressor according to claim 1 is characterized in that the internal diameter (D1) of internal diameter (D2)＜this small piston of the end of at least one small piston in said two sections small pistons.
5. according to the arbitrary described rotary compressor of claim 1 to 4, it is characterized in that said rotary compressor (1) and condenser (5), expansion valve (7), vaporizer (6) are connected in series the formation refrigeration plant successively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010503273XA CN102444581A (en) | 2010-09-30 | 2010-09-30 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010503273XA CN102444581A (en) | 2010-09-30 | 2010-09-30 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102444581A true CN102444581A (en) | 2012-05-09 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010503273XA Pending CN102444581A (en) | 2010-09-30 | 2010-09-30 | Rotary compressor |
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| CN (1) | CN102444581A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104986007A (en) * | 2015-06-11 | 2015-10-21 | 广东美芝制冷设备有限公司 | Air conditioning system for electric vehicle and electric vehicle having same |
| CN107120286A (en) * | 2016-02-25 | 2017-09-01 | 珠海凌达压缩机有限公司 | Low-pressure cavity compressor and air-conditioning |
| CN112343820A (en) * | 2020-09-25 | 2021-02-09 | 珠海格力节能环保制冷技术研究中心有限公司 | Multilayer roller type compressor and air conditioner using same |
| CN114483581A (en) * | 2021-12-08 | 2022-05-13 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body subassembly and compressor |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6134378A (en) * | 1984-07-26 | 1986-02-18 | Matsushita Electric Ind Co Ltd | Piston device of rotary compressor |
| JPS63113785U (en) * | 1987-01-20 | 1988-07-22 | ||
| CN1510276A (en) * | 2002-12-25 | 2004-07-07 | 乐金电子(天津)电器有限公司 | Compressor for preventing rotary compressor from refrigerant leakage |
| CN1934335A (en) * | 2004-03-16 | 2007-03-21 | 大金工业株式会社 | Rotary type expansion machine |
| CN201187450Y (en) * | 2008-03-11 | 2009-01-28 | 上海日立电器有限公司 | Piston structure with oil groove for rolling rotor type compressor |
| WO2009093701A1 (en) * | 2008-01-23 | 2009-07-30 | Daikin Industries, Ltd. | Compressor |
-
2010
- 2010-09-30 CN CN201010503273XA patent/CN102444581A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6134378A (en) * | 1984-07-26 | 1986-02-18 | Matsushita Electric Ind Co Ltd | Piston device of rotary compressor |
| JPS63113785U (en) * | 1987-01-20 | 1988-07-22 | ||
| CN1510276A (en) * | 2002-12-25 | 2004-07-07 | 乐金电子(天津)电器有限公司 | Compressor for preventing rotary compressor from refrigerant leakage |
| CN1934335A (en) * | 2004-03-16 | 2007-03-21 | 大金工业株式会社 | Rotary type expansion machine |
| WO2009093701A1 (en) * | 2008-01-23 | 2009-07-30 | Daikin Industries, Ltd. | Compressor |
| CN201187450Y (en) * | 2008-03-11 | 2009-01-28 | 上海日立电器有限公司 | Piston structure with oil groove for rolling rotor type compressor |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104986007A (en) * | 2015-06-11 | 2015-10-21 | 广东美芝制冷设备有限公司 | Air conditioning system for electric vehicle and electric vehicle having same |
| CN107120286A (en) * | 2016-02-25 | 2017-09-01 | 珠海凌达压缩机有限公司 | Low-pressure cavity compressor and air-conditioning |
| CN107120286B (en) * | 2016-02-25 | 2024-05-17 | 珠海凌达压缩机有限公司 | Low-pressure cavity compressor and air conditioner |
| CN112343820A (en) * | 2020-09-25 | 2021-02-09 | 珠海格力节能环保制冷技术研究中心有限公司 | Multilayer roller type compressor and air conditioner using same |
| CN112343820B (en) * | 2020-09-25 | 2023-01-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Multilayer roller type compressor and air conditioner using same |
| CN114483581A (en) * | 2021-12-08 | 2022-05-13 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body subassembly and compressor |
| CN114483581B (en) * | 2021-12-08 | 2024-01-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly and compressor |
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Application publication date: 20120509 |