CN102032187A - Control method and application of cold energy variable type rotary compressor - Google Patents
Control method and application of cold energy variable type rotary compressor Download PDFInfo
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- CN102032187A CN102032187A CN2009101929601A CN200910192960A CN102032187A CN 102032187 A CN102032187 A CN 102032187A CN 2009101929601 A CN2009101929601 A CN 2009101929601A CN 200910192960 A CN200910192960 A CN 200910192960A CN 102032187 A CN102032187 A CN 102032187A
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Abstract
The invention relates to a control method and application of a cold energy variable type rotary compressor. The cold energy variable type rotary compressor comprises a variable frequency motor part and a compressing mechanism part, wherein the variable frequency motor part can change the rotating speed; and the compressing mechanism part can switch cold energy into a two-section volume control type rotary compressor by continuing and stopping the compression effect of any of a first cylinder and a second cylinder. The control method is characterized in that: the rotating speed of the motor part is reduced in advance, and the volume is controlled. When the difference between high pressure and lower pressure of the rotary compressor is more than 0.5MPa after the rotary compressor is started, the volume is controlled. A control method for making the rotary compressor have high efficiency is selected to operate by comparing a control method for purely changing the rotating speed of the motor part and a control method for purely controlling the volume, wherein by both methods, the same cold energy can be obtained. The invention has the characteristics of flexible operation, low manufacturing cost, high energy efficiency ratio and wide application range.
Description
Technical field
The present invention relates to a kind of controlling method and application thereof of cold changable type rotary compressor.
Background technique
The variable-frequency type motor part of both having deposited technology in combination with the compression mechanical part of capacity control rotary compressor, have in the rotary compressor of ability changable type, be to solve slide plate sound that compression mechanical part takes place, and make the maximized compressor control technology of compressor efficiency.As described in following patent documentation:
[patent documentation 1] patent disclosure 2008-128231
[patent documentation 2] patent disclosure is put down into 15-31114
Summary of the invention
Purpose of the present invention aims to provide a kind of flexible operation, avoid piston and the slide plate bruit de froissement that takes place when volume controlled is switched and make the controlling method and the application thereof of compressor efficiency optimization, fabricating cost is low, Energy Efficiency Ratio is high, applied widely cold changable type rotary compressor, to overcome deficiency of the prior art.
Press the controlling method of a kind of cold changable type rotary compressor of this purpose design, cold changable type rotary compressor comprises the variable-frequency type motor part that can change rotating speed, with by continuing with the compression that stops any cylinder in first cylinder and second cylinder, can switching to cold the compression mechanical part of two sections capacity control rotary compressor, after it is characterized in that reducing the rotating speed of motor part in advance, carry out volume controlled again.
The above-mentioned rotating speed that reduces motor part is in advance carried out volume controlled after arriving below the 75rps again.
A kind of controlling method of cold changable type rotary compressor, cold changable type rotary compressor comprises the variable-frequency type motor part that can change rotating speed, with by continuing with the compression that stops any cylinder in first cylinder and second cylinder, can switching to cold the compression mechanical part of two sections capacity control rotary compressor, it is characterized in that when the height pressure difference of this rotary compressor after rotary compressor starts, when arrival 0.5Mpa is above, carry out volume controlled again.
A kind of controlling method of cold changable type rotary compressor, cold changable type rotary compressor comprises the variable-frequency type motor part that can change rotating speed, with by continuing with the compression that stops any cylinder in first cylinder and second cylinder, can switching to cold the compression mechanical part of two sections capacity control rotary compressor, the controlling method that it is characterized in that the rotating speed of the simple change motor part by relatively obtaining identical cold, with the controlling method of simple volume controlled, select one of them to make the high controlling method operation of rotary compressor efficient.
A kind of application of controlling method of cold changable type rotary compressor is characterized in that described controlling method is applied in the refrigeration plant, and this refrigeration plant comprises cold changable type rotary compressor, indoor heat exchanger, expansion gear and outdoor heat exchanger.
Refrigeration plant among the present invention is by the variable-frequency type rotary compressor both deposited and advanced commercial capacity control rotary compressor to make up the back to realize; By in advance the rotating speed of rotary compressor being reduced the back, carries out volume controlled, can prevent unusual bruit de froissement; And, in the controlling method by control rotary compressor winding number and two identical colds that the controlling method of the combination of volume controlled obtains, select the high controlling method of compressor efficiency by the efficient of comparison rotary compressor.
The invention solves when carrying out volume controlled, the slide plate that the compression mechanical part of rotary compressor takes place collides sound and slide plate damaging problem, can reach the purpose that makes compressor energy efficiency optimization, it has flexible operation, fabricating cost is low, Energy Efficiency Ratio is high, advantage of wide range of application.
Description of drawings
Fig. 1 is the vertical section structure schematic representation of one embodiment of the invention.
Fig. 2 is that Y-Y among Fig. 1 is to the sectional structure schematic representation.
Fig. 3 is the collision experimental data figure of slide plate and piston.
Fig. 4 is the graph of a relation of cold and rotating speed.
Fig. 5 is the structural representation of refrigeration plant.
Among the figure: R is a cold changable type rotary compressor, and 2 is seal casinghousing, and 3 is discharge tube, 4 is four-way valve, and 5 is outdoor heat exchanger, and 6 is expansion gear, 7 is indoor heat exchanger, and 11 is liquid container, and 12 is suction pipe, 13 is the pressure switching valve, and 16 for pressure switches pipe, and 17a is first discharging valve device, 17b is second discharging valve device, 21 compression mechanical parts, and 22 is mechanism portion, 23a is first cylinder, and 23b is second cylinder, and 24 is intermediate plate, 25a is first cylinder chamber, and 25b is second cylinder chamber, and 27 is main bearing, 28 is supplementary bearing, and 29a is first baffler, and 29b is second baffler, 31a is first slide plate, and 31b is second slide plate, and 32a is a first piston, 32b is second piston, and 33a is first eccentric shaft, and 33b is second eccentric shaft, 34a is the first slide plate chamber, 34b is the second slide plate chamber, and 36 is bent axle, and 37 is helical spring, 42 is vane slot, 43 is suction chamber, and 44 is pressure hole, and 45 is the low pressure hole.
Embodiment
Below in conjunction with drawings and Examples the present invention is further described.
Referring to Fig. 1, be the longitudinal section of the cold changable type rotary compressor R that uses in the present embodiment, cold changable type rotary compressor R is hereinafter to be referred as rotary compressor R.
Rotary compressor R is made of the compression mechanical part 21 of the variable-frequency type motor part 22 that can change rotating speed with capacity control rotary compressor, and these all are fixed on seal casinghousing 2 internal diameters.
Compression mechanical part 21 has two cylinders: the first cylinder 23a and the second cylinder 23b, these cylinders are divided by intermediate plate 24 betwixt, constitute the first cylinder chamber 25a and the second cylinder chamber 25b respectively.In this embodiment 1, the discharge capacity of two cylinders equates.But the discharge capacity of two cylinders need not equate.Such as if the discharge capacity of the second cylinder 23b is littler than the discharge capacity of the first cylinder 23a, that just can enlarge the minimum ability of rotary compressor R and the ratio of maximum capacity.Therefore, the discharge capacity that is suitable for the second cylinder 23b is less than or equal to the situation of the discharge capacity of the first cylinder 23a.
Be welded on the suction pipe 12 of seal casinghousing 2 sides, link to each other, from liquid container 11, import low pressure refrigerant gas to the first cylinder chamber 25a and the second cylinder chamber 25b with the side of the first cylinder 23a.These two cylinders are accompanied by intermediate plate 24, the screw (omitting among the figure) by separately, are installed on the planar surface portion of main bearing 27 and supplementary bearing 28.And the first baffler 29a and the second baffler 29b that include the first discharging valve device 17a and the second discharging valve device 17b are installed on main bearing 27 and the supplementary bearing 28.
The first piston 32a and the second piston 32b that the first eccentric shaft 33a and the second eccentric shaft 33b of bent axle 36 freely turns round installation respectively, is mounted are along internal diameter, the revolution revolution of the first cylinder chamber 25a and the second cylinder chamber 25b.And, insert cylinder vane slot 42 separately, as shown in Figure 2, the first slide plate 31a and the second slide plate 31b are usually in vane slot inside, reciprocatingly slide synchronously with above-mentioned piston periphery.And the chamber, space that separately slide plate rear portion is formed is called the first slide plate chamber 34a and the second slide plate chamber 34b.Above-mentioned parts as shown in Figure 1, the rotary compressor structure portion 21 that the formation group is upright, this compression mechanical part is connected with the internal diameter of seal casinghousing 2 in the outer radius of the first cylinder 23a.
The first slide plate chamber 34a is to the inside of seal casinghousing 2, and promptly the high pressure side is open, therefore, and under the on-stream state of compressor, often be positioned at the high pressure side.And helical spring 37 is installed in slide plate 31a, is accompanied by first piston 32a, often carries out compression operation.On the other hand, second slide plate chamber 34b sealing is switched pipe 16 with pressure and is connected.Pressure switches pipe 16 and links to each other with the pressure switching valve that is installed in seal casinghousing 2 outsides, and the pressure in the second slide plate chamber 34 can switch between high pressure side Pd and low voltage side Ps.
When the second slide plate chamber 34b was positioned at the high pressure side, masterpiece was used for the second slide plate 31b back, and the second slide plate 31b follows the second piston 32b, and therefore, the second cylinder 23b can compress.But after the second slide plate chamber 34b switched to low voltage side, the second slide plate 31b broke away from from the second piston 32b, and is static and be incorporated among the second slide plate chamber 34b, and therefore, the second cylinder 23b interrupts compression.
Thereafter, the pressure of the second slide plate chamber 34b switched to the high pressure side after, interruption, the second cylinder 23b that can contact compression once more can begin compression once more.Based on above principle, rotary compressor R has and can be called H pattern and L pattern to this operation mode respectively cold 100% and 50% feature of freely switching.Above control procedure can change compressor displacement, so this controlling method is capacity controlled.
Referring to Fig. 2, for the Y-Y among Fig. 1 to sectional view.In Fig. 2, the pressure of the second slide plate chamber 34b is low voltage side Ps, and therefore, after the second slide plate 31b broke away from from the second piston 32b, being fixed was accommodated in the vane slot 42 and the second slide plate chamber 34b.Therefore, the second slide plate 32b fixes, and the second cylinder 23b interrupts compression.At this moment, have only the first cylinder 23a often to continue compression, rotary compressor R is positioned at the operating condition of the L pattern that can bring into play 50% cold.
In the side of the second cylinder 23b, dispose perforate on high-tension side enclosure interior and the pressure hole 44 that communicates with vane slot 42, with the low pressure hole 45 of these pressure hole 44 suction chambers 43 relative, from vane slot 42 perforates in the low-pressure gas path.Pressure hole 44 and low pressure hole 45 by the pressure difference Δ p=(Pd-Ps) of this generation, play a part the second slide plate 31b is fixed in the vane slot 42.
That is to say that the directed force F v that Δ p is taken place often plays a part to make the static braking force of the second slide plate 31b.Therefore, when the pressure in the second slide plate chamber 34 switched to low voltage side, after the tip of the second slide plate 31b was given as security the power Fh vanishing of pressing the second piston 32b, the second slide plate 31b was still in vane slot 42, is fixed.
At this moment, the first end of the second slide plate 31b is usually located on the interior radial line of the second cylinder chamber 25b, not with make this line in the scope that contacts of the external diameter of the second piston 32b that revolves round the sun, keep very little gap.This gap is called slide plate tip minimum clearance.As shown in Figure 2, the moment that the second piston 32b is broken away from from the first end of the tip 31b of second slide plate is called slide plate tip maximal clearance.Slide plate tip maximal clearance equates with the stroke of slide plate, is 2 times of eccentric amount e of the second eccentric shaft 33b.
Rotary compressor R switches to the moment of L mode operation from the H mode operation, the second slide plate 31b tip breaks away from from the second piston 32b periphery, be accommodated in the vane slot 42, in static very short time, in other words, the second slide plate 31b tip and the second piston 32b periphery are collided repeatedly.Such as the rotating speed of rotary compressor R is regarded the time that second slide plate 31b elder generation splaying becomes between the 2e of maximal clearance as 0.1 second under 60rps, and the second slide plate 31b tip and the second piston 32b periphery are carried out 6 times repeatedly and collided.This phenomenon, takes place when the L mode operation switches to the H mode operation too at rotary compressor R.
As above-mentioned, what this collision was also had a significant impact is the rotating speed of the second piston 32b, and the ratio of impulsive contact force is 2 powers of winding number.And by the control of frequency conversion, after winding number increased, colliding number of times increased.As a result, the collision sound of the second slide plate 31b and the second piston 32b, with second slide plate 31b breakage the causing reliability problem.As the means of avoiding this problem, followingly state brightly, be necessary to reduce rotating speed, the switch mode of rotary compressor R.
Referring to Fig. 3, for testing data one example that is obtained.The amplitude of the longitudinal axis has shown the intensity of the collision sound that collision took place of the second slide plate 31b and the second piston 32b, and transverse axis has shown the time of origin that collides sound.And the number of the collision sound that ripple separately is shown has shown the number of times that collides.The part that waveform is little is the running sound of rotary compressor.Can distinguish from laboratory data, the unusual collision sound and the intensity of collision with collide number of times and and the time of origin that collides very big relation is arranged.That is to say that the rotating speed of rotary compressor R has very big coherence with the size of colliding sound.After surpassing 75rps, unusual collision sound takes place, and the danger of the second slide plate 31b breakage is very high.
Conclusion: when mode switching, for the generation of the unusual collision of avoidance sound and the breakage of the second slide plate 31b more safely, during (1) mode switching, after the reduction rotating speed; (2) run up down, winding number is reduced to below the 75rps, just is necessary to carry out volume controlled, just the switching of pattern.
In concrete running, by Fig. 4, the control example of avoiding unusual conflict is described.
Referring to Fig. 4, shown an example of two volume controlled of rotary compressor R and the rotating speed cold in changing.Transverse axis is rotating speed rps, and the longitudinal axis is cold kw.As the feature of rotary compressor R because respectively in L pattern and H pattern, rotating speed is changed, so as shown, can represent two colds with straight line.
As an example of running, the little situation of air conditioning load is regarded as the L mode operation, the big situation of air conditioning load is regarded as the H mode operation.And, according to the change of air conditioning load, rotary compressor is stopped, carrying out mode switching between the two.For example, under the L pattern, with L30, i.e. the rotary compressor R of the rotating speed of 30rps startup makes rotating speed rise, pass through L75, arrives the highest cold 5kw as the L pattern under the highest winding number L120.At this, increase cold, by switching to H pattern, moment arrival H120, arrive the highest cold 10kw.
But, because the rotating speed of rotary compressor R is 120rps, as slide plate sound above-mentioned, that fierceness takes place.As the means of avoiding this problem, before the switch mode, the winding number of L120 is reduced to L75 after, it is best to carry out mode switching again.As a result, can carry out the transition to H75, and increase winding number, can arrive H120 from L75.On the contrary, in the H120 running, need under the situation from the H mode switching to the L pattern winding number to be reduced to below the H75, just can switch mode.
Next, as the feature of rotary compressor R, as shown in Figure 4,, under the running of L pattern and H pattern, can obtain the cold that equates in the scope from 1.0kw to 5.0kw.For example, the cold of L60 and H30 is 2.5kw altogether.Usually, the efficient COP of rotary compressor is by the value of the efficient decision of motor part and compression mechanical part, particularly along with the rotating speed of compressor, alters a great deal.In the situation of selecting operation modes from these two options, should efficiency of selection high one.Such as, relatively L60 and H30 if the COP of L60 has superiority, so just select L60.
Referring to Fig. 5, be the refrigeration and the refrigeration periodogram that heats under the running of the air conditioner that carries rotary compressor R.In the drawings, solid arrow has shown flowing of the gas coolant under the cooling operation, and dotted arrow has shown and heats the mobile of running gas coolant down.
The pressurized gas that spue from the discharge pipe 3 that is configured in rotary compressor R upper end become the condensation refrigerant outdoor heat exchanger 5.From three expansion gears, in the indoor heat exchanger 7 that be connected in these evaporate, and to indoor freeze thereafter.Thereafter, the gas coolant shunting, the liquid container 11 via compressor turns back to compression mechanical part 21 from suction pipe 12.
Usually, when rotary compressor R starts, start the load minimizing, rotating speed is reduced to about 20～30rps in order to make, and, only under the L pattern of the first cylinder chamber 25a, begin to start.Thereafter, slowly increase rotating speed after, high side pressure Pd rises, low-pressure lateral pressure Ps reduces, therefore, Δ p enlarges.But, till Δ p arrives 0.5Mpa, need the time about 10～20 seconds usually.
When such Δ p is positioned at the following time point of 0.5Mpa, the operation mode of rotary compressor R from the L mode switching after the H pattern, with respect to the Fv of the static force of slide plate, the size of the directed force F H at slide plate back is not enough, and second slide plate 31b time that arrives cylinder chamber that flies out is delayed.Consequently, piston increases with the collision number of times, collides sound bigger problem takes place.Because this reason, when Δ p be more than the 0.5Mpa after, need from the L mode switching to the H pattern.
The capacity control rotary compressor of Shi Yonging in the present embodiment, also can adopt to put down among the 15-31114 and put down in writing, substitute by the capacity control rotary compressor that the internal pressure of one of them cylinder of two cylinders is switched, carried out the ability control mode between high pressure side and low voltage side as patent disclosure.And the refrigeration plant that present embodiment shows is not limited only to air conditioner, also can use on refrigerating machine.
And about the control device of the rotary compressor of above explanation, formation as shown in this embodiment is not only method, and in the scope of invention main idea, the possibility that all distortion are implemented is mathematical.
Claims (5)
1. the controlling method of a cold changable type rotary compressor, cold changable type rotary compressor comprises the variable-frequency type motor part (22) that can change rotating speed, with by continuing with the compression that stops any cylinder in first cylinder and second cylinder, can switching to cold the compression mechanical part (21) of two sections capacity control rotary compressor, after it is characterized in that reducing the rotating speed of motor part in advance, carry out volume controlled again.
2. the controlling method of cold changable type rotary compressor according to claim 1, the rotating speed that it is characterized in that reducing in advance motor part (22) to 75rps following after, carry out volume controlled again.
3. the controlling method of a cold changable type rotary compressor, cold changable type rotary compressor comprises the variable-frequency type motor part (22) that can change rotating speed, with by continuing with the compression that stops any cylinder in first cylinder and second cylinder, can switching to cold the compression mechanical part (21) of two sections capacity control rotary compressor, it is characterized in that when the height pressure difference of this rotary compressor after rotary compressor starts, when arrival 0.5Mpa is above, carry out volume controlled again.
4. the controlling method of a cold changable type rotary compressor, cold changable type rotary compressor comprises the variable-frequency type motor part (22) that can change rotating speed, with by continuing and the compression that stops any cylinder in first cylinder and second cylinder, cold can be switched to the compression mechanical part (21) of two sections capacity control rotary compressor, the controlling method that it is characterized in that the rotating speed of the simple change motor part (22) by relatively obtaining identical cold, with the controlling method of simple volume controlled, select one of them to make the high controlling method operation of rotary compressor efficient.
5. application according to the controlling method of claim 1,3 or 4 described cold changable type rotary compressors, it is characterized in that described controlling method is applied in the refrigeration plant, this refrigeration plant comprises cold changable type rotary compressor, indoor heat exchanger, expansion gear and outdoor heat exchanger.
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| CN2009101929601A CN102032187A (en) | 2009-09-30 | 2009-09-30 | Control method and application of cold energy variable type rotary compressor |
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| CN2009101929601A CN102032187A (en) | 2009-09-30 | 2009-09-30 | Control method and application of cold energy variable type rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103883527A (en) * | 2014-03-25 | 2014-06-25 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle device with same |
| CN107570273A (en) * | 2017-08-29 | 2018-01-12 | 徐州汉唐瑞清科技有限公司 | A kind of abrasive disk type spring becomes loading middling speed pulverized coal preparation equipment |
| CN109441820A (en) * | 2018-10-19 | 2019-03-08 | 珠海格力电器股份有限公司 | Positive displacement compressor starts control method, device and positive displacement compressor, storage medium |
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| CN1890468A (en) * | 2003-12-03 | 2007-01-03 | 东芝开利株式会社 | Freezing cycle device |
| JP2007077976A (en) * | 2005-09-12 | 2007-03-29 | Samsung Electronics Co Ltd | Variable displacement rotary compressor |
| CN101012833A (en) * | 2007-02-04 | 2007-08-08 | 美的集团有限公司 | Control method of rotary compressor |
| CN101065580A (en) * | 2004-08-12 | 2007-10-31 | Lg电子株式会社 | Capacity variable type twin rotary compressor and driving method thereof and airconditioner with this and driving method thereof |
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| US6796773B1 (en) * | 2003-05-21 | 2004-09-28 | Samsung Electronics Co., Ltd. | Variable capacity rotary compressor |
| CN1590769A (en) * | 2003-09-02 | 2005-03-09 | 东芝开利株式会社 | Air conditioner |
| CN1890468A (en) * | 2003-12-03 | 2007-01-03 | 东芝开利株式会社 | Freezing cycle device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103883527A (en) * | 2014-03-25 | 2014-06-25 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle device with same |
| CN107570273A (en) * | 2017-08-29 | 2018-01-12 | 徐州汉唐瑞清科技有限公司 | A kind of abrasive disk type spring becomes loading middling speed pulverized coal preparation equipment |
| CN109441820A (en) * | 2018-10-19 | 2019-03-08 | 珠海格力电器股份有限公司 | Positive displacement compressor starts control method, device and positive displacement compressor, storage medium |
| CN109441820B (en) * | 2018-10-19 | 2020-11-24 | 珠海格力电器股份有限公司 | Variable-capacity compressor starting control method and device, variable-capacity compressor and storage medium |
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Application publication date: 20110427 |