CN110617218B - Control method of two-stage compressor and air conditioning unit - Google Patents
Control method of two-stage compressor and air conditioning unit Download PDFInfo
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- CN110617218B CN110617218B CN201910860829.1A CN201910860829A CN110617218B CN 110617218 B CN110617218 B CN 110617218B CN 201910860829 A CN201910860829 A CN 201910860829A CN 110617218 B CN110617218 B CN 110617218B
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- compressor
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- 238000000034 method Methods 0.000 title claims abstract description 17
- 238000004378 air conditioning Methods 0.000 title claims abstract description 8
- 230000007246 mechanism Effects 0.000 claims abstract description 85
- 238000007906 compression Methods 0.000 claims abstract description 74
- 230000006835 compression Effects 0.000 claims abstract description 60
- 239000003507 refrigerant Substances 0.000 claims abstract description 24
- 230000009977 dual effect Effects 0.000 claims abstract description 10
- 230000008859 change Effects 0.000 abstract description 6
- 230000001276 controlling effect Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The application provides a control method of a two-stage compressor and an air conditioning unit. The dual stage compressor includes a low pressure stage and a high pressure stage in series with the low pressure stage. The two-stage compressor further comprises a volume ratio adjusting mechanism arranged on the low-pressure stage and used for changing the volume ratio of the low-pressure stage to refrigerant compression. By applying the technical scheme of the invention, when the compression end pressure of the high-pressure stage is less than the exhaust pressure, the volume ratio of the low-pressure stage to the refrigerant compression is increased by the operation volume ratio adjusting mechanism, so that the compression end pressure of the high-pressure stage is equal to the exhaust pressure; when the compression end pressure of the high-pressure stage is more than the exhaust pressure, the volume ratio of the low-pressure stage to the refrigerant compression is reduced by the volume ratio adjusting mechanism, so that the compression end pressure of the high-pressure stage is equal to the exhaust pressure, the over-compression and under-compression conditions are improved, the environment condition change is adapted, the energy efficiency of the compressor is improved, and the noise of the compressor is reduced.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a control method of a two-stage compressor and an air conditioning unit.
Background
In the conventional unipolar compressor, a capacity adjustment mechanism is employed. That is, under some conditions, the unit is required to run under a smaller load condition, and the compressor slide block is controlled to move so as to change the capacity to meet the requirement.
However, in a dual stage compressor, capacity is generally changed by only performing variable frequency modulation on the high pressure stage of the compressor. The internal volume ratio of the two-stage compressor cannot be effectively regulated, which results in the situation that over-compression and under-compression occur in the compressor at a high pressure stage when the compression end pressure and the discharge pressure are not equal, and the two situations can cause additional energy loss and strong periodic discharge noise.
Disclosure of Invention
The embodiment of the invention provides a control method of a two-stage compressor and an air conditioner unit, which are used for solving the technical problems of energy loss and noise caused by unequal pressure of the end of compression of a high-pressure stage and the exhaust pressure of the two-stage compressor in the prior art.
The embodiment of the application provides a two-stage compressor, including low pressure level and with the serial high pressure level of low pressure level, two-stage compressor still includes: and the volume ratio adjusting mechanism is arranged on the low-pressure stage and is used for changing the volume ratio of the low-pressure stage to the refrigerant compression.
In one embodiment, the compressor is a screw compressor and the volume ratio adjustment mechanism is a first slide valve adjustment mechanism for changing the output position of the low pressure stage discharge port.
In one embodiment, the dual-stage compressor further comprises a capacity adjustment mechanism disposed on the high-pressure stage for varying an output capacity of the high-pressure stage for refrigerant compression.
In one embodiment, the capacity adjustment mechanism is a second spool valve adjustment mechanism for varying the output of the bypass port of the high pressure stage.
In one embodiment, the capacity adjustment mechanism is a plunger adjustment mechanism for effecting capacity adjustment by a fixed point bypass intake.
In one embodiment, the capacity adjustment mechanism is a rotational speed adjustment mechanism that effects capacity adjustment by varying the rotational speed of the motor to control the amount of suction.
In one embodiment, the dual stage compressor further comprises a first drive mechanism coupled to the first slide valve adjustment mechanism for driving the first slide valve adjustment mechanism in motion.
In one embodiment, the dual stage compressor further comprises a second drive mechanism coupled to the second slide valve adjustment mechanism for driving movement of the second slide valve adjustment mechanism.
The application also provides a control method of the two-stage compressor, wherein the control method is used for controlling the compressor, and the control method comprises the following steps: when the final compression pressure of the high-pressure stage is less than the exhaust pressure, the volume ratio of the low-pressure stage to the refrigerant compression is increased by the operation volume ratio adjusting mechanism; when the final compression pressure of the high-pressure stage is more than the exhaust pressure, the volume ratio adjusting mechanism is operated to reduce the volume ratio of the low-pressure stage to the refrigerant compression.
The application also provides an air conditioning unit, which comprises a two-stage compressor, wherein the two-stage compressor is the two-stage compressor.
In the above embodiment, when the high-pressure stage compression end pressure < the discharge pressure, the operating volume ratio adjusting mechanism increases the volume ratio of the low-pressure stage to the refrigerant compression, so that the high-pressure stage compression end pressure is equal to the discharge pressure; when the compression end pressure of the high-pressure stage is more than the exhaust pressure, the volume ratio of the low-pressure stage to the refrigerant compression is reduced by the volume ratio adjusting mechanism, so that the compression end pressure of the high-pressure stage is equal to the exhaust pressure, the over-compression and under-compression conditions are improved, the environment condition change is adapted, the energy efficiency of the compressor is improved, and the noise of the compressor is reduced.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 is a schematic overall construction of an embodiment of a dual stage compressor according to the present invention;
FIG. 2 is a schematic diagram of the low pressure stage of the dual stage compressor of FIG. 1;
fig. 3 is a schematic view of the structure of the high pressure stage of the dual stage compressor of fig. 1.
Detailed Description
The present invention will be described in further detail with reference to the following embodiments and the accompanying drawings, in order to make the objects, technical solutions and advantages of the present invention more apparent. The exemplary embodiments of the present invention and the descriptions thereof are used herein to explain the present invention, but are not intended to limit the invention.
Fig. 1 and 2 show an embodiment of a two-stage compressor of the present invention comprising a low pressure stage 10 and a high pressure stage 20 in series with the low pressure stage 10. The two-stage compressor further includes a volume ratio adjusting mechanism 30 provided on the low pressure stage 10 for changing the volume ratio of the low pressure stage 10 to the refrigerant compression.
By applying the technical scheme of the invention, when the compression end pressure of the high-pressure stage 20 is less than the exhaust pressure, the volume ratio of the low-pressure stage 10 to the refrigerant compression is increased by operating the volume ratio adjusting mechanism 30, so that the compression end pressure of the high-pressure stage 20 is equal to the exhaust pressure; when the compression end pressure of the high-pressure stage 20 is greater than the exhaust pressure, the volume ratio adjusting mechanism 30 is operated to reduce the volume ratio of the low-pressure stage 10 to refrigerant compression, so that the compression end pressure of the high-pressure stage 20 is equal to the exhaust pressure, the over-compression and under-compression conditions are improved, the change of external conditions is adapted, the energy efficiency of the compressor is improved, and the noise of the compressor is reduced.
Alternatively, in the technical solution of the present embodiment, as shown in fig. 2, the compressor is a screw compressor, and the volume ratio adjusting mechanism 30 is a first slide valve adjusting mechanism for changing the output position of the discharge port 11 of the low-pressure stage. By changing the output position of the low-pressure stage exhaust port 11, refrigerants having different volume ratios can be discharged from the low-pressure stage 10. Specifically, the lower the volume ratio of the refrigerant at the output position of the low-pressure stage exhaust port 11, which is closer to the screw input end, the higher the volume ratio of the refrigerant at the output position of the low-pressure stage exhaust port 11, which is closer to the screw output end. When the low-pressure stage 10 is used, the slide block is adjusted to move leftwards, and at the moment, the position of the exhaust port 11 of the low-pressure stage is leftwards, so that the compression end pressure of the low-pressure stage 10 is reduced, namely the suction pressure of the high-pressure stage 20 is reduced, and the compression end pressure of the high-pressure stage 20 is equal to the exhaust pressure. The first slide valve adjusting mechanism is controlled to a set position, and the internal volume ratio is changed to enable the compression end pressure to be matched with the exhaust pressure, so that the noise of the compressor is reduced, and the energy efficiency of the compressor is improved.
As a further alternative, the form of the volume ratio adjustment mechanism 30 is also not limited to spool valves.
In addition, as shown in fig. 1, the dual stage compressor further includes bearings 80 for mounting the low pressure stage 10 and the high pressure stage 20 and a motor 70 for driving the low pressure stage 10 and the high pressure stage 20 to rotate.
As shown in fig. 1 and 3, in the technical solution of the present embodiment, the two-stage compressor further includes a capacity adjustment mechanism 40 disposed on the high-pressure stage 20, for changing the output capacity of the high-pressure stage 20 for compressing the refrigerant. Thus, the technical scheme of the invention not only has the functions of capacity adjustment and internal volume ratio adjustment. The capacity of the compressor can be adjusted according to external requirements, and the requirements of different load operation are met. Meanwhile, the internal volume ratio can be adjusted according to the change of the external pressure, the compression end pressure of the compressor is changed, the conditions of over-compression and under-compression are avoided, the noise is reduced, and the energy efficiency of the compressor is improved.
In the conventional compressor, capacity adjustment and internal volume ratio adjustment are used separately. Alternatively, as shown in fig. 3, in the technical solution of the present embodiment, the capacity adjustment mechanism 40 is a second spool valve adjustment mechanism for changing the output of the bypass port 21 of the high-pressure stage. When the front end of the second slide valve adjusting mechanism is in full contact with the stopper, the bypass port 21 of the high-pressure stage is closed at this time, and the compressor is in a full load state. When there is a partial load operation demand, the system moves rightward through the second slide valve adjusting mechanism, and at this time, the bypass port 21 of the high-pressure stage is communicated with the suction side, that is, the partially compressed gas is bypassed to the suction side, and the actual suction amount is changed, so that partial compliance with the demand can be realized.
As another alternative, the capacity adjustment mechanism 40 may be selected as a plunger adjustment mechanism for effecting capacity adjustment by a fixed point bypass intake.
As another alternative, the capacity adjustment mechanism 40 may be a rotation speed adjustment mechanism that controls the intake air amount by changing the rotation speed of the motor to achieve capacity adjustment. Specifically, in the technical solution of the present embodiment, the capacity adjustment mechanism 40 is a frequency converter, but the rotation speed adjustment mechanism is not limited to the frequency converter.
As an alternative implementation manner, in the technical solution of the present embodiment, the two-stage compressor further includes a first driving mechanism 50, where the first driving mechanism 50 is connected to the first slide valve adjusting mechanism, and is used to drive the first slide valve adjusting mechanism to move. Optionally, the dual-stage compressor further comprises a second driving mechanism 60, and the second driving mechanism 60 is connected with the second slide valve adjusting mechanism and is used for driving the second slide valve adjusting mechanism to move. Preferably, the first driving mechanism 50 and the second driving mechanism 60 are movable cylinders, and the output ends of the movable cylinders are connected with the first slide valve adjusting mechanism or the second slide valve adjusting mechanism, so that the movable cylinders can drive the first slide valve adjusting mechanism and the second slide valve adjusting mechanism to move. Optionally, the movable cylinder is a hydraulic cylinder or an air cylinder or an electric cylinder.
The above embodiment is exemplified by selecting one of the capacity adjustment and the internal volume ratio adjustment, and the single-stage two-stage screw compressor of the present invention may take other forms that can achieve the capacity adjustment and the internal volume ratio adjustment.
The invention also provides a control method of the two-stage compressor, which is used for controlling the compressor and comprises the following steps:
when the compression end pressure of the high-pressure stage 20 is less than the exhaust pressure, the volume ratio adjusting mechanism 30 is operated to increase the volume ratio of the low-pressure stage 10 to refrigerant compression;
when the compression end pressure of the high-pressure stage 20 is greater than the discharge pressure, the volume ratio adjusting mechanism 30 is operated to reduce the volume ratio of the low-pressure stage 10 to the refrigerant compression.
When the compressor is running, after the exhaust pressure changes, the compression end pressure of the high-pressure stage 20 of the compressor is unequal to the exhaust pressure, and the conditions of over-compression and under-compression can occur at the moment, so that the problems of high noise and high power consumption of the compressor are caused. Therefore, the compressor can detect and compare the compression end pressure and the exhaust pressure, and judge the pressure relationship to give an instruction of the moving direction of the sliding block. When the compression end pressure of the high pressure stage 20 is detected to be unequal to the discharge pressure, the discharge pressure of the low pressure stage is adjusted so as to change the pressure of the gas entering the high pressure stage 20, thereby achieving the purpose of changing the compression end pressure of the high pressure stage 20. When the compression end pressure of the high-pressure stage 20 is less than the exhaust pressure, the volume ratio adjusting mechanism 30 is operated to increase the volume ratio of the low-pressure stage 10 to refrigerant compression; when the compression end pressure of the high-pressure stage 20 is greater than the discharge pressure, the volume ratio adjusting mechanism 30 is operated to reduce the volume ratio of the low-pressure stage 10 to the refrigerant compression.
Specifically, as shown in fig. 2, in combination with the embodiment of the slide valve adjusting mechanism, when the compression end pressure of the high-pressure stage is less than the discharge pressure, an instruction is issued to the first slide valve adjusting mechanism to move to the right, and at this time, the position of the discharge orifice moves backward, so that the compression end pressure of the low-pressure stage 10 is increased, that is, the suction pressure of the high-pressure stage 20 is increased, and the compression end pressure of the high-pressure stage 20 is equal to the discharge pressure; when the compression end pressure of the high-pressure stage 20 is greater than the exhaust pressure, an instruction is issued to the first slide valve adjusting mechanism to move leftwards, and at the moment, the position of the exhaust hole is moved forwards, so that the compression end pressure of the low-pressure stage 10 is reduced, namely the suction pressure of the high-pressure stage 20 is reduced, and the compression end pressure of the high-pressure stage 20 is equal to the exhaust pressure. The first slide valve adjusting mechanism is controlled to move to the set position, and the internal volume ratio is changed to enable the compression end pressure to be matched with the exhaust pressure, so that the noise of the compressor is reduced, and the energy efficiency of the compressor is improved.
By applying the technical scheme of the invention, when the external pressure changes, the relation between the compression end pressure and the exhaust pressure can be judged by detecting the compression end pressure and the exhaust pressure, and an instruction is issued to the internal volume ratio adjusting structure to adjust the position of the low-pressure-stage exhaust orifice, so that the compression end pressure is similar to the exhaust pressure, the over-compression and under-compression conditions are improved, the external condition changes are adapted, the energy efficiency of the compressor is improved, and the noise of the compressor is reduced.
The invention also provides an air conditioning unit comprising the two-stage compressor. By adopting the two-stage compressor, the energy efficiency of the air conditioning unit can be improved.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, and various modifications and variations can be made to the embodiments of the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. A control method of a two-stage compressor, characterized in that the two-stage compressor comprises a low-pressure stage (10), a high-pressure stage (20) connected in series with the low-pressure stage (10) and a volume ratio adjusting mechanism (30), wherein the low-pressure stage (10) is provided with a volume ratio adjusting mechanism for changing the volume ratio of the low-pressure stage (10) to refrigerant compression, the compressor is a screw compressor, the volume ratio adjusting mechanism (30) is a first slide valve adjusting mechanism for changing the output position of an exhaust port (11) of the low-pressure stage, and the two-stage compressor further comprises a volume adjusting mechanism (40) arranged on the high-pressure stage (20) for changing the output capacity of the high-pressure stage (20) to refrigerant compression; the control method comprises the following steps:
when the compression end pressure of the high-pressure stage (20) is less than the exhaust pressure, the volume ratio adjusting mechanism (30) is operated to increase the volume ratio of the low-pressure stage (10) to refrigerant compression;
when the compression end pressure of the high-pressure stage (20) is larger than the exhaust pressure, the volume ratio adjusting mechanism (30) is operated to reduce the volume ratio of the low-pressure stage (10) to refrigerant compression.
2. A control method according to claim 1, characterized in that the capacity adjustment mechanism (40) is a second spool adjustment mechanism for changing the output of the bypass port (21) of the high pressure stage.
3. The control method according to claim 1, characterized in that the capacity adjustment mechanism (40) is a plunger adjustment mechanism for effecting capacity adjustment by a fixed point bypass intake.
4. The control method according to claim 1, wherein the capacity adjustment mechanism (40) is a rotation speed adjustment mechanism that performs capacity adjustment by controlling an intake air amount by changing a rotation speed of the motor.
5. The control method of claim 1, wherein the dual stage compressor further comprises a first drive mechanism (50), the first drive mechanism (50) being coupled to the first slide valve adjustment mechanism for driving movement of the first slide valve adjustment mechanism.
6. The control method of claim 2, wherein the dual stage compressor further comprises a second drive mechanism (60), the second drive mechanism (60) being coupled to the second slide valve adjustment mechanism for driving movement of the second slide valve adjustment mechanism.
7. An air conditioning unit comprising a two-stage compressor, characterized in that it employs the control method of the two-stage compressor according to any one of claims 1 to 6.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910860829.1A CN110617218B (en) | 2019-09-11 | 2019-09-11 | Control method of two-stage compressor and air conditioning unit |
| PCT/CN2019/128046 WO2021047108A1 (en) | 2019-09-11 | 2019-12-24 | Two-stage compressor, control method for two-stage compressor, and air conditioning unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910860829.1A CN110617218B (en) | 2019-09-11 | 2019-09-11 | Control method of two-stage compressor and air conditioning unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110617218A CN110617218A (en) | 2019-12-27 |
| CN110617218B true CN110617218B (en) | 2023-12-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910860829.1A Active CN110617218B (en) | 2019-09-11 | 2019-09-11 | Control method of two-stage compressor and air conditioning unit |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN110617218B (en) |
| WO (1) | WO2021047108A1 (en) |
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| GB9825737D0 (en) * | 1997-11-26 | 1999-01-20 | Kobe Steel Ltd | Two-stage screw compressor |
| JP2007138919A (en) * | 2005-10-17 | 2007-06-07 | Kobe Steel Ltd | Two-stage screw compressor and two-stage compression refrigerator using this compressor |
| JP2013092091A (en) * | 2011-10-25 | 2013-05-16 | Mitsubishi Electric Corp | Double stage screw compressor |
| WO2013146674A1 (en) * | 2012-03-30 | 2013-10-03 | 株式会社神戸製鋼所 | Two-stage compression device |
| CN104912800A (en) * | 2015-07-10 | 2015-09-16 | 金鑫 | Stand-alone two-stage variable frequency screw rod compressor with adjustable internal volume ratio |
| CN105782036A (en) * | 2014-12-25 | 2016-07-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and internal volume ratio adjusting method for compressor |
| CN207454269U (en) * | 2017-10-30 | 2018-06-05 | 珠海格力电器股份有限公司 | Screw compressor and air conditioner |
| CN211259012U (en) * | 2019-09-11 | 2020-08-14 | 珠海格力电器股份有限公司 | Two-stage compressor and air conditioning unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US6881040B2 (en) * | 2001-02-15 | 2005-04-19 | Mayekawa Mfg. Co., Ltd. | Multi-stage screw compressor unit accommodating high suction pressure and pressure fluctuations and method of operation thereof |
| KR102060470B1 (en) * | 2013-06-05 | 2019-12-30 | 엘지전자 주식회사 | 2-stage compressor |
| CN108035880B (en) * | 2017-12-15 | 2019-11-05 | 同济大学 | A kind of variable speed becomes the more rotor compressors of discharge capacity and its becomes displacement control |
-
2019
- 2019-09-11 CN CN201910860829.1A patent/CN110617218B/en active Active
- 2019-12-24 WO PCT/CN2019/128046 patent/WO2021047108A1/en active Application Filing
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB9825737D0 (en) * | 1997-11-26 | 1999-01-20 | Kobe Steel Ltd | Two-stage screw compressor |
| JP2007138919A (en) * | 2005-10-17 | 2007-06-07 | Kobe Steel Ltd | Two-stage screw compressor and two-stage compression refrigerator using this compressor |
| JP2013092091A (en) * | 2011-10-25 | 2013-05-16 | Mitsubishi Electric Corp | Double stage screw compressor |
| WO2013146674A1 (en) * | 2012-03-30 | 2013-10-03 | 株式会社神戸製鋼所 | Two-stage compression device |
| CN105782036A (en) * | 2014-12-25 | 2016-07-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and internal volume ratio adjusting method for compressor |
| CN104912800A (en) * | 2015-07-10 | 2015-09-16 | 金鑫 | Stand-alone two-stage variable frequency screw rod compressor with adjustable internal volume ratio |
| CN207454269U (en) * | 2017-10-30 | 2018-06-05 | 珠海格力电器股份有限公司 | Screw compressor and air conditioner |
| CN211259012U (en) * | 2019-09-11 | 2020-08-14 | 珠海格力电器股份有限公司 | Two-stage compressor and air conditioning unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110617218A (en) | 2019-12-27 |
| WO2021047108A1 (en) | 2021-03-18 |
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