CN101839239A - Digital rotor type compressor - Google Patents
Digital rotor type compressor Download PDFInfo
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- CN101839239A CN101839239A CN200910047934A CN200910047934A CN101839239A CN 101839239 A CN101839239 A CN 101839239A CN 200910047934 A CN200910047934 A CN 200910047934A CN 200910047934 A CN200910047934 A CN 200910047934A CN 101839239 A CN101839239 A CN 101839239A
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- 230000006835 compression Effects 0.000 claims abstract description 22
- 238000007906 compression Methods 0.000 claims abstract description 22
- 230000001815 facial effect Effects 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 abstract description 6
- 230000001932 seasonal effect Effects 0.000 abstract description 2
- 238000000034 method Methods 0.000 description 8
- 238000007789 sealing Methods 0.000 description 4
- 101100008050 Caenorhabditis elegans cut-6 gene Proteins 0.000 description 3
- 238000010992 reflux Methods 0.000 description 3
- 235000014676 Phragmites communis Nutrition 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
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- 238000007599 discharging Methods 0.000 description 1
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Abstract
The invention relates to a digital rotor type compressor, which comprises a cylinder, a piston, and a blade. The piston and the blade are connected and arranged in the cylinder. The compressor also comprises an electromagnetic valve, wherein the electromagnetic valve is arranged between the cylinder and an air suction pipe and connects a back pressure cavity of the cylinder with the air suction pipe of the compressor. By adjusting the opening and closing of the electromagnetic valve, the pressure of the blade back pressure cavity is controlled, so that the pressure of the back pressure cavity is switched between the pressure of a compression cavity and the air suction pressure. Therefore, the compressor can be switched between the full load and the zero load by controlling the motion of the blade. By controlling the time scale of the full load and zero load operation in a certain time period, the load of the rotor compressor is subjected to 0 to 100 percent of stepless regulation, and the digital control of a rotary compressor is realized. Compared with the prior art, the digital rotor type compressor has the advantages of simple structure, easy control, the capacities of improving the contact force between the blade and the piston, reducing the friction, improving the reliability and year-round seasonal energy efficiency ratio of the compressor, and the like.
Description
Technical field
The present invention relates to rotor-type compressor, especially relate to a kind of digital rotor type compressor.
Background technique
In order to alleviate global energy crisis, energy saving improves the travelling comfort and the reliability of air-conditioning system simultaneously, and frequency conversion and varying capacity Study on Technology are hot issues always.
Frequency-changeable compressor need dispose a frequency variator, and cost is higher, and simultaneously compressor moves in very wide in range speed range, and the reliability of compressor is also proposed higher requirement.
The varying capacity technology of rotor compressor adopts pressurized gas to be back to air aspiration cavity, has reduced discharge capacity, but has also reduced operational efficiency simultaneously; What have adopts special construction that two cylinders can be switched between parallel running or polyphone operation to two-spool compressor, can regulate between 50% and 100% load like this.More than two kinds of methods all can not realize the step-less adjustment of capacity from 0%～100%.
Fig. 1 is traditional cylinder, exhaust angular cut 6, blade groove 8, blade backpressure is the high pressure in the compressor housing, this high pressure air muscle power and leaf spring power make blade and piston external diameter tightly fit, guarantee sealing, but when gas pressure in the compression chamber was not high, the contact force of blade tip and piston external diameter was excessive, had a strong impact on the reliability of blade and piston.
Summary of the invention
Purpose of the present invention is exactly to provide a kind of simple in structure in order to overcome the defective that above-mentioned prior art exists, and can realize that compressor capacity carries out the digital rotor type compressor of step-less adjustment between 0～100%.
Purpose of the present invention can be achieved through the following technical solutions: a kind of digital rotor type compressor, this compressor comprises cylinder, piston, blade, described piston is connected with blade and places in the cylinder, it is characterized in that, also comprise solenoid valve, this solenoid valve is arranged between cylinder and the sucking pipe, the back pressure cavity of cylinder and the sucking pipe of compressor are coupled together, by regulating the time scale that solenoid valve opens and cuts out, the motion of control blade, make the rotor compressor load from 0～100% step-less adjustment, realize the control of digital rotary compressor.
Described back pressure cavity is positioned at the blade afterbody, by back pressure hole back pressure cavity is connected with the compression chamber of cylinder, during the operation of compressor full load, the back pressure of blade equals the pressure of compression chamber, back pressure cavity closely cooperates by the cylinder cap up and down of cylinder and compressor or the intermediate plate end face plane of twin-tub, forms with blade again.
Described back pressure hole is by opening a groove and cooperating formation with the head side facial plane at the end face of cylinder, described back pressure hole is communicated with exhaust angular cut and back pressure cavity.
Described back pressure hole is opened on the intermediate plate of cylinder cap or twin-tub.
Described back pressure hole is opened on the blade.
Described solenoid valve is provided with one, and described compressor is a single-rotor compressor, and the back pressure cavity of this compressor connects sucking pipe by solenoid valve, when solenoid valve is opened, Pressure in Back-pressure Cavity is a pressure of inspiration(Pi), and compressor blade separates with piston, the operation of compressor zero load.
Described solenoid valve is provided with two, and described compressor is a two-spool compressor, and two cylinders of this compressor connect sucking pipe by solenoid valve respectively.
Compared with prior art, the present invention is connected the blade backpressure chamber with a solenoid valve with compressor suction duct, control the pressure in blade backpressure chamber, make Pressure in Back-pressure Cavity between compression chamber pressure and pressure of inspiration(Pi), switch, thereby the motion of control blade, make compressor between full load and zero load, to switch, realize that by the time scale that is controlled at full load and zero load operation in the cycle regular hour compressor load can carry out step-less adjustment from 0%～100%, so be referred to as the digital rotor compressor.When the compressor full load was moved, blade backpressure equaled the pressure of compression chamber, but not is exhaust pressure always, can improve the contact force between blade and the piston, reduced friction, had improved the reliability of compressor; The step-less adjustment of compressor load does not have extra energy loss, and both compressor COP in 0%～100% load regulation process almost loseed, and can improve the annual seasonal energy efficiency ratio (seer) of air-conditioning system.The present invention is applicable to single rotor and two-spool compressor, is applicable to that the housing internal pressure is the rotor compressor of low pressure and high pressure.
Description of drawings
Fig. 1 is the structural representation of traditional cylinder;
Fig. 2 is the structural representation of cylinder of the present invention;
Fig. 3 is the structural representation that the back pressure hole of the back pressure cavity of the embodiment of the invention 1 is about to open;
Structural representation when Fig. 4 opens for back pressure hole among Fig. 3;
The structural representation that Fig. 5 continues to open for back pressure hole among Fig. 4;
Structural representation when Fig. 6 closes for back pressure hole among Fig. 5;
Fig. 7 is the structural representation of the back pressure hole of the embodiment of the invention 2;
Fig. 8 is the structural representation that the back pressure hole of the back pressure cavity of the embodiment of the invention 2 is about to open;
Structural representation when Fig. 9 opens for back pressure hole among Fig. 8;
The structural representation that Figure 10 continues to open for back pressure hole among Fig. 9;
Structural representation when Figure 11 closes for back pressure hole among Figure 10;
Figure 12 is the structural representation of the blade of the embodiment of the invention 3;
Figure 13 is the structural representation that the back pressure hole of the back pressure cavity of the embodiment of the invention 3 is about to open;
Structural representation when Figure 14 opens for back pressure hole among Figure 13;
The structural representation that Figure 15 continues to open for back pressure hole among Figure 14;
Structural representation when Figure 16 closes for back pressure hole among Figure 15;
The structural representation of Figure 17 single-rotor compressor of the present invention;
The structural representation of Figure 18 two-spool compressor of the present invention.
Embodiment
The present invention is described in detail below in conjunction with the drawings and specific embodiments.
As shown in figure 17, a kind of digital single rotor formula compressor, this compressor single cylinder is provided with a solenoid valve 9, and this solenoid valve 9 is arranged between cylinder 4 and the sucking pipe 10, and the sucking pipe 41 of the back pressure cavity of cylinder 4 and compressor is coupled together the control that realizes digital rotary compressor.For single cylinder, when the compressor zero load moved, solenoid valve 9 was opened, the pressure in blade backpressure chamber is pressure of inspiration(Pi), leaf spring power is very little, and gas differential pressure makes blade and piston external diameter can occur separating before and after the blade, reaches the purpose of unloading, up to blade pressure reduction and leaf spring equilibrium of forces, owing to there is not big pressure reduction, the collision problem of blade and piston can not take place, this moment, compression chamber pressure only needed to overcome leaf spring power, so it is load is very little, almost nil.When the compressor full load was moved, solenoid valve 9 cut out, and the pressure in blade backpressure chamber is the pressure of compression chamber, and blade closely contacts with piston, the operation of compressor full load.
By in cycle regular hour, regulating the time scale of solenoid valve 9 opening and closing, can realize the step-less adjustment of rotor compressor load from 0～100%.
Shown in Fig. 2～6, cylinder 4 and up and down the head side facial plane closely cooperate and blade 3 forms the back pressure cavity 1 of blade together.Blade 3 places blade groove 8, opens a groove and the cooperation of head side facial plane at the end face of cylinder 4, forms back pressure hole 2, is communicated with exhaust angular cut 6 and back pressure cavity 1.
The opening and closing of back pressure hole 2 are by blade 3 controls.When the compressor full load was moved, the back pressure change procedure of back pressure cavity 1 was shown in Fig. 3～6.Fig. 3 is firm through intakeport 7 at piston 5, and back pressure hole 2 is about to open; Bent axle continues rotation, and in Fig. 4, the pressurized gas that back pressure hole 2 is opened back back pressure cavity 1 flow to compression chamber, make back pressure reduce, and avoid blade and piston contact force excessive; In Fig. 5, pressure is along with compression chamber pressure continues to change in the back pressure cavity 1; In Fig. 6, exhaust angular cut 6 and intakeport 7 are communicated with, and blade 3 sealing back pressure cavity 1 avoid back pressure cavity 1 gas to reflux to air aspiration cavity.
As shown in figure 18, a kind of digital dual-rotator compressor, this compressor twin-tub is provided with two solenoid valves 9,9 ', solenoid valve 9 is arranged between cylinder 4 and the sucking pipe 10, the back pressure cavity of cylinder 4 and the sucking pipe 10 of compressor are coupled together, and solenoid valve 9 ' is arranged between cylinder 4 ' and the sucking pipe 10 ', and the back pressure cavity of cylinder 4 ' and the sucking pipe 10 ' of compressor are coupled together, unload lower cylinder 4 by opens solenoid valve 9, opens solenoid valve 9 ' unloads upper cylinder 4 '.When solenoid valve 9 cuts out, the operation of lower cylinder 4 full load; When solenoid valve 9 ' cuts out, the operation of upper cylinder 4 ' full load.
By in cycle regular hour, regulating the time scale of the opening and closing of two solenoid valves respectively, can realize the step-less adjustment of rotor compressor load from 0～100%.
The intermediate plate end face plane of cylinder and twin-tub closely cooperates and blade forms the back pressure cavity of blade together.Back pressure hole is opened on the intermediate plate of the twin-tub that cooperates with cylinder, and as shown in Figure 7, back pressure hole 2 is communicated with back pressure cavity 1 by passage 21 respectively, is communicated with compression chamber by passage 22.
When the compressor full load was moved, the back pressure change procedure of back pressure cavity was shown in Fig. 8～11: the motion by piston 5 comes opening and closing back pressure hole 2.Fig. 8 is firm through intakeport 7 at piston 5, and back pressure hole 2 is about to open; Bent axle continues rotation, in Fig. 9, after back pressure hole 2 is opened, the pressurized gas of back pressure cavity 1 flowed to compression chamber before this, made back pressure reduce, and avoided blade and piston contact force excessive, along with the rising of compression chamber pressure, Pressure in Back-pressure Cavity also raises, and guarantees that blade has suitable back pressure; In Figure 10, pressure is along with compression chamber pressure continues to change in the back pressure cavity 1, and when compressor air-discharging arrived this position, piston 5 was about to seal back pressure hole 2; In Figure 11, exhaust finishes, and piston 5 sealing back pressure hole 2 avoid the gas in back pressure cavity 1 and the back pressure hole 2 to reflux to air aspiration cavity.
Referring to Figure 17～18, a kind of digital rotor type compressor, this compressor comprises cylinder, piston, blade, described piston is connected with blade and places in the cylinder, also comprise solenoid valve, this solenoid valve is arranged between cylinder and the sucking pipe, and the back pressure cavity of cylinder and the sucking pipe of compressor are coupled together.During the operation of compressor full load, closed electromagnetic valve; During the operation of compressor zero load, solenoid valve is opened.By being adjusted in the time scale of certain hour opening and closing of solenoid valve in the cycle, Pressure in Back-pressure Cavity is switched between compression chamber pressure and pressure of inspiration(Pi), thereby reach the purpose of control blade movement, make the rotor compressor load from 0～100% step-less adjustment, realize the number control of rotary compressor.
Cylinder and up and down cylinder cap (or intermediate plate of twin-tub) end face plane closely cooperate and blade forms the back pressure cavity of blade together.Back pressure hole 2 is opened on the blade 3 that cooperates with cylinder blade groove high pressure surface, and the structural representation of blade 3 as shown in figure 12.
When the compressor full load was moved, the back pressure change procedure of back pressure cavity 1 was shown in Figure 13～16: the motion by blade 3 comes the opening and closing back pressure hole.Figure 13 is firm through intakeport 7 at piston 5, and back pressure hole 2 is about to open; Bent axle continues rotation, in Figure 14, after back pressure hole 2 is opened, the pressurized gas of back pressure cavity 1 flowed to compression chamber before this, made back pressure reduce, and avoided blade and piston contact force excessive, along with the rising of compression chamber pressure, back pressure cavity 1 pressure also raises, and guarantees that blade has suitable back pressure; In Figure 15,1 pressure is along with compression chamber pressure continues to change in the back pressure cavity; In Figure 16, exhaust finishes, and blade 3 sealing back pressure hole 2 avoid the gas in back pressure cavity 1 and the back pressure hole 2 to reflux to air aspiration cavity.
By said method, back pressure hole and back pressure cavity only and compression chamber be communicated with, the clearance volume of having avoided back pressure to cause is lost.
The present invention is applicable to single rotor and two-spool compressor, is applicable to that the housing internal pressure is the rotor compressor of low pressure and high pressure.
Claims (7)
1. digital rotor type compressor, this compressor comprises cylinder, piston, blade, described piston is connected with blade and places in the cylinder, it is characterized in that, also comprise solenoid valve, this solenoid valve is arranged between cylinder and the sucking pipe, the back pressure cavity of cylinder and the sucking pipe of compressor are coupled together, by regulating the time scale that solenoid valve opens and cuts out, make the rotor compressor load from 0～100% step-less adjustment, realize the control of digital rotary compressor.
2. a kind of digital rotor type compressor according to claim 1, it is characterized in that, described back pressure cavity is positioned at the blade afterbody, by back pressure hole back pressure cavity is connected with the compression chamber of cylinder, make the back pressure of blade equal the pressure of compression chamber, back pressure cavity closely cooperates by the cylinder cap up and down of cylinder and compressor or the intermediate plate end face plane of twin-tub, forms with blade again.
3. a kind of digital rotor type compressor according to claim 2 is characterized in that, described back pressure hole is by opening a groove and cooperating formation with the head side facial plane at the end face of cylinder, and described back pressure hole is communicated with exhaust angular cut and back pressure cavity.
4. a kind of digital rotor type compressor according to claim 2 is characterized in that described back pressure hole is opened on the intermediate plate of cylinder cap or twin-tub.
5. a kind of digital rotor type compressor according to claim 2 is characterized in that described back pressure hole is opened on the blade.
6. a kind of digital rotor type compressor according to claim 1 is characterized in that, described solenoid valve is provided with one, described compressor is a single-rotor compressor, and this compressor connects sucking pipe by solenoid valve, when solenoid valve is opened, back pressure cavity is connected with sucking pipe, Pressure in Back-pressure Cavity is a pressure of inspiration(Pi), and blade and piston break away from, the operation of compressor zero load, when closed electromagnetic valve, it is compression chamber pressure that back pressure cavity has pressure, and blade closely contacts with piston, the operation of compressor full load.
7. a kind of digital rotor type compressor according to claim 1 is characterized in that, described solenoid valve is provided with two, and described compressor is a two-spool compressor, and two cylinders of this compressor connect sucking pipe by solenoid valve respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910047934A CN101839239A (en) | 2009-03-20 | 2009-03-20 | Digital rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910047934A CN101839239A (en) | 2009-03-20 | 2009-03-20 | Digital rotor type compressor |
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|---|---|
| CN101839239A true CN101839239A (en) | 2010-09-22 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200910047934A Pending CN101839239A (en) | 2009-03-20 | 2009-03-20 | Digital rotor type compressor |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072529A (en) * | 2010-11-26 | 2011-05-25 | 广东美的制冷设备有限公司 | Air conditioner using variable volume compressor and control method thereof |
| CN104343685A (en) * | 2014-10-17 | 2015-02-11 | 广东美芝制冷设备有限公司 | Compressor |
| CN109882413A (en) * | 2019-04-01 | 2019-06-14 | 安徽美芝精密制造有限公司 | Rotary compressor and refrigeration system with it |
| CN114087180A (en) * | 2021-12-08 | 2022-02-25 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor, air conditioner |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57165694A (en) * | 1981-04-07 | 1982-10-12 | Nippon Denso Co Ltd | Refrigerant compressor |
| JP2003201982A (en) * | 2002-01-08 | 2003-07-18 | Sanyo Electric Co Ltd | Rotary compressor |
| JP2003254276A (en) * | 2002-03-04 | 2003-09-10 | Sanyo Electric Co Ltd | Rotary compressor |
| CN1789718A (en) * | 2004-12-13 | 2006-06-21 | 三洋电机株式会社 | Multi-cylindrical rotary compressor, compression system, and freezing device using the compression system |
| CN101052808A (en) * | 2005-02-23 | 2007-10-10 | Lg电子株式会社 | Capacity varying type rotary compressor |
| US20080314053A1 (en) * | 2004-08-06 | 2008-12-25 | Ozu Masao | Capacity Variable Type Rotary Compressor and Driving Method Thereof and Driving Method for Air Conditioner Having the Same |
-
2009
- 2009-03-20 CN CN200910047934A patent/CN101839239A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57165694A (en) * | 1981-04-07 | 1982-10-12 | Nippon Denso Co Ltd | Refrigerant compressor |
| JP2003201982A (en) * | 2002-01-08 | 2003-07-18 | Sanyo Electric Co Ltd | Rotary compressor |
| JP2003254276A (en) * | 2002-03-04 | 2003-09-10 | Sanyo Electric Co Ltd | Rotary compressor |
| US20080314053A1 (en) * | 2004-08-06 | 2008-12-25 | Ozu Masao | Capacity Variable Type Rotary Compressor and Driving Method Thereof and Driving Method for Air Conditioner Having the Same |
| CN1789718A (en) * | 2004-12-13 | 2006-06-21 | 三洋电机株式会社 | Multi-cylindrical rotary compressor, compression system, and freezing device using the compression system |
| CN101052808A (en) * | 2005-02-23 | 2007-10-10 | Lg电子株式会社 | Capacity varying type rotary compressor |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072529A (en) * | 2010-11-26 | 2011-05-25 | 广东美的制冷设备有限公司 | Air conditioner using variable volume compressor and control method thereof |
| CN104343685A (en) * | 2014-10-17 | 2015-02-11 | 广东美芝制冷设备有限公司 | Compressor |
| CN109882413A (en) * | 2019-04-01 | 2019-06-14 | 安徽美芝精密制造有限公司 | Rotary compressor and refrigeration system with it |
| CN114087180A (en) * | 2021-12-08 | 2022-02-25 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor, air conditioner |
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Application publication date: 20100922 |