CN107489618B - Rotary compressor and air conditioning system with same - Google Patents
Rotary compressor and air conditioning system with same Download PDFInfo
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- CN107489618B CN107489618B CN201710752485.3A CN201710752485A CN107489618B CN 107489618 B CN107489618 B CN 107489618B CN 201710752485 A CN201710752485 A CN 201710752485A CN 107489618 B CN107489618 B CN 107489618B
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- stage compression
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- rotary compressor
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 15
- 230000006835 compression Effects 0.000 claims abstract description 270
- 238000007906 compression Methods 0.000 claims abstract description 270
- 230000007246 mechanism Effects 0.000 claims abstract description 38
- 238000002347 injection Methods 0.000 claims abstract description 36
- 239000007924 injection Substances 0.000 claims abstract description 36
- 238000005192 partition Methods 0.000 claims description 15
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 238000004891 communication Methods 0.000 claims description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 238000005057 refrigeration Methods 0.000 description 6
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
-
- 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
-
- 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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- 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
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
-
- 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
- F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
- F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
-
- 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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- F04C2240/00—Components
- F04C2240/10—Stators
Abstract
The invention discloses a rotary compressor and an air conditioning system with the same, the rotary compressor comprises: a housing; the compression mechanism is arranged in the shell and comprises a single-stage compression cylinder and a two-stage compression cylinder, the single-stage compression cylinder is provided with a single-stage compression cavity, a single-stage air suction port and a single-stage exhaust port, the two-stage compression cylinder comprises a first-stage compression cylinder and a second-stage compression cylinder, the first-stage compression cylinder is provided with a first-stage compression cavity and a first air suction port, the second-stage compression cylinder is provided with a second-stage compression cavity and a second-stage air suction port, the compression mechanism is provided with a mixing cavity communicated with the first-stage compression cavity and the second-stage compression cavity and a first air injection flow path communicated with the mixing cavity, and the first-stage compression cylinder can be switched between a cylinder rest operation state and a cylinder rest release operation state; and the motor component is arranged in the shell and is suitable for driving the compression mechanism to work. The rotary compressor provided by the embodiment of the invention can simultaneously give consideration to the capacity and the energy efficiency, and improves the working performance.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a rotary compressor and an air conditioning system with the same.
Background
As the ambient temperature decreases, the specific volume of the refrigerant increases, and the unit intake amount of the rolling rotor compressor decreases, resulting in a significant decrease in the heating capacity of the compressor. While the lower the temperature, the greater the heat demand of the room, the two-stage compressor in the related art cannot fully satisfy the heat demand.
In some occasions, such as a multi-split system (one external unit and a plurality of internal units), the system load changes with the opening and closing amounts of the internal units, when the compressor is in full load, the compressor is expected to meet the requirement of high capacity, and when the compressor is in partial load, the compressor is expected to operate efficiently. Conventional compressors are fixed capacity, and even with up-conversion techniques, it is difficult to combine both requirements.
The conventional common refrigeration and heating circulation device is easy to generate excessive refrigeration capacity under a small-load working condition, such as an intermediate refrigeration condition, so that energy waste is caused, and meanwhile, under a large-load working condition, such as ultralow-temperature heating, the phenomenon of insufficient heating capacity is easy to generate, and the efficiency is low. In addition, the system can realize rapid cooling and heating in the requirement of users, and the flow of the refrigerant cannot be rapidly increased.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the invention proposes a rotary compressor that can combine both capacity and energy efficiency.
The invention also provides an air conditioning system with the rotary compressor.
According to an embodiment of the present invention, a rotary compressor includes: a housing; the compression mechanism is arranged in the shell and comprises a single-stage compression cylinder and a two-stage compression cylinder, the single-stage compression cylinder is provided with a single-stage compression cavity, a single-stage air suction port and a single-stage exhaust port, the two-stage compression cylinder comprises a first-stage compression cylinder and a second-stage compression cylinder, the first-stage compression cylinder is provided with a first-stage compression cavity and a first air suction port, the second-stage compression cylinder is provided with a second-stage compression cavity and a second-stage air suction port, the compression mechanism is provided with a mixing cavity communicated with the first-stage compression cavity and the second-stage compression cavity and a first air injection flow path communicated with the mixing cavity, and the first-stage compression cylinder is switchable between a cylinder-rest running state and a cylinder-rest running releasing state; and the motor component is arranged in the shell and is suitable for driving the compression mechanism to work.
The rotary compressor provided by the embodiment of the invention can simultaneously give consideration to the capacity and the energy efficiency, and improves the working performance.
In addition, the rotary compressor according to the above embodiment of the present invention may have the following additional technical features:
according to some embodiments of the invention, the single stage compression chambers, the first stage compression chambers and the second stage compression chambers are arranged randomly along an axial direction of the compression mechanism.
Optionally, an exhaust cavity communicated with the first exhaust port is further arranged in the compression mechanism.
Further, the discharge chamber is defined by two stacked diaphragms disposed between any two of the single stage compression chamber, the first stage compression chamber and the second stage compression chamber.
According to some embodiments of the invention, the mixing chamber is defined by two stacked baffles disposed between any two of the single stage compression chamber, the first stage compression chamber, and the second stage compression chamber, or the mixing chamber is defined by a bearing of the compression mechanism and a cover plate disposed on the bearing.
The rotary compressor according to the embodiment of the present invention further includes: and the second air injection flow path is communicated with the single-stage compression cavity.
Optionally, the first stage compression cylinder realizes the switching of the cylinder-rest running state and the cylinder-rest releasing running state by controlling the pressure of the first jet flow path.
Optionally, a sliding vane back pressure cavity with variable pressure is arranged in the first stage compression cylinder, so that the first compression cylinder is switched between a cylinder rest running state and a cylinder rest releasing running state by controlling the back pressure of the sliding vane.
Further, the pressure of the back pressure cavity of the sliding vane and the pressure of the mixing cavity synchronously change.
Further, a pressure channel for communicating the sliding vane back pressure cavity and the mixing cavity is arranged in the compression mechanism.
According to some embodiments of the invention, the first jet port of the first jet flow path is provided on the first stage compression cylinder, the second stage compression cylinder, a bearing, a partition plate, or a cover plate.
Optionally, the second air jet of the second air jet flow path is arranged on a single-stage compression cylinder, a bearing, a partition plate or a cover plate.
According to some embodiments of the invention, the slide in the first stage compression chamber is configured to be controlled in position by adjusting the pressure in the slide back pressure chamber.
In some embodiments of the present invention, the compression mechanism is provided with a magnetic element that acts on the slide in the first stage compression chamber to brake the slide when the first stage compression cylinder is in a cylinder-rest operating state.
Optionally, the working displacement of the single-stage compression cylinder is V1, and the working displacement of the first-stage compression cylinder is V3, wherein V1/v3=0.4-1.6.
According to some embodiments of the invention, the working displacement of the second stage compression cylinder is V2 and the working displacement of the first stage compression cylinder is V3, wherein V2/v3=0.40-0.95.
An air conditioning system according to an embodiment of the present invention includes a rotary compressor according to an embodiment of the present invention.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:
fig. 1 is a schematic structural view of a rotary compressor according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view of a compression mechanism of a rotary compressor according to one embodiment of the present invention;
FIG. 3 is another cross-sectional view of a compression mechanism of a rotary compressor according to one embodiment of the present invention;
fig. 4 is a sectional view of a compression mechanism of a rotary compressor according to another embodiment of the present invention;
fig. 5 is a sectional view of a compression mechanism of a rotary compressor according to still another embodiment of the present invention;
FIG. 6 is a schematic illustration of the position of a second gas jet of a rotary compressor according to an embodiment of the present invention;
FIG. 7 is a graph of COP versus V2/V3 for a rotary compressor according to an embodiment of the present invention;
FIG. 8 is a graph of COP versus V1/V3 for a rotary compressor according to an embodiment of the present invention;
fig. 9 is a schematic structural view of an air conditioning system according to an embodiment of the present invention;
fig. 10 is a schematic structural view of an air conditioning system according to another embodiment of the present invention.
Reference numerals:
an air conditioning system 1000;
a rotary compressor 100; a condenser 200; flash vessel 300; an evaporator 400; a first throttle device 500; a second throttle device 600; a four-way valve 700; a reservoir 800;
a housing 10;
a compression mechanism 20;
a single stage compression cylinder 21; a single stage compression chamber 210; a single stage suction port 211; a second jet flow path 212; a second air injection passage 213; a second gas jet 2131; a slide back pressure chamber 215; a back pressure chamber line 217;
a two-stage compression cylinder 22; a first stage compression cylinder 22a; a second stage compression cylinder 22b; a first stage compression chamber 220; a first suction port 221; a second stage compression chamber 230; a mixing chamber 240; a first jet flow path 241; a first jet channel 2411; a discharge chamber 250; a pressure channel 260;
a crankshaft 23; a piston 24; a slide 25; a partition 26; a bearing 27; a cover plate 28; an elastic element 291; a magnetic element 292;
a motor assembly 30; a stator 31; a rotor 32;
and a three-way valve 40.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below by referring to the drawings are exemplary for the purpose of illustrating the present invention and are not to be construed as limiting the present invention, and various changes, modifications, substitutions and alterations may be made therein by one of ordinary skill in the art without departing from the spirit and scope of the present invention as defined by the appended claims and their equivalents.
In the description of the present invention, it should be understood that the terms "upper", "lower", "front", "rear", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly.
A rotary compressor 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
Referring to fig. 1 to 6, a rotary compressor 100 according to an embodiment of the present invention may include: a housing 10, a compression mechanism 20 and a motor assembly 30.
Specifically, the compression mechanism 20 is provided in the casing 10, and the compression mechanism 20 includes a single stage compression cylinder 21 and a two stage compression cylinder 22, the single stage compression cylinder 21 having a single stage compression chamber 210, a single stage suction port 211, and a single stage discharge port, both of which are in communication with the single stage compression chamber 210. The single stage compression cylinder 21 may suck air through the single stage suction port 211 and then be discharged from the single stage discharge port into the inner space of the casing 10 after being compressed in the single stage compression chamber 210.
The two-stage compression cylinder 22 includes a first-stage compression cylinder 22a and a second-stage compression cylinder 22b, the first-stage compression cylinder 22a having a first-stage compression chamber 220 and a first intake port 221, the second-stage compression cylinder 22b having a second-stage compression chamber 230 and a first exhaust port, the two-stage compression cylinder 22 further being provided with a mixing chamber 240 and a first air injection flow path 241, the mixing chamber 240 communicating with the first-stage compression chamber 220 and the second-stage compression chamber 230, and the mixing chamber 240 further communicating with the first air injection flow path 241. Thus, the first suction port 221, the first stage compression chamber 220, the mixing chamber 240, the second stage compression chamber 230, and the first discharge port may be sequentially communicated. Accordingly, the gas may be sucked through the first suction port 221, compressed in the first stage compression chamber 220, and then flowed into the mixing chamber 240, and at the same time, the mixing chamber 240 may be introduced through the first gas injection flow path 241, and then mixed with the compressed gas, and then flowed into the second stage compression chamber 230, and then again compressed in the second stage compression chamber 230, and then discharged from the first discharge port and introduced into the inner space of the casing 10.
In actual use, the pressure of the gas entering the first suction port 221, the single-stage suction port 211, and the first gas injection flow path 241 may be controlled according to circumstances, for example, the single-stage compression cylinder 21 may suck low-pressure gas from the single-stage suction port 211, the low-pressure gas may be compressed in the single-stage compression chamber 210 to form high-pressure gas, and then may be discharged from the single-stage exhaust port into the housing 10; the two-stage compression cylinder 22 may suck low-pressure gas from the first suction port 221, compress the low-pressure gas in the first-stage compression chamber 220, and then discharge the low-pressure gas into the mixing chamber 240, and simultaneously, may introduce medium-pressure gas into the mixing chamber 240 through the first gas injection flow path 241, mix the medium-pressure gas with the gas compressed by the first-stage compression chamber 220, then enter the second-stage compression chamber 230 to be compressed to form high-pressure gas, and then discharge the high-pressure gas into the internal space of the casing 10 from the first gas discharge port. The specific pressure values of the low pressure, the medium pressure and the high pressure may be specifically set according to the actual rotary compressor.
Thus, the single-stage compression cylinder 21 can realize single-stage compression of the gas, and the two-stage compression cylinder 22 can realize two-stage compression of the gas. Therefore, under the conditions such as ultralow temperature low-pressure, the single-stage compression cylinder 21 and the two-stage compression cylinder 22 work simultaneously, so that the compressor discharge capacity during ultralow temperature low-pressure can be increased, the two-stage compression under the conditions can have a proper large pressure ratio and a large pressure difference, the discharge capacity can be increased simultaneously, the refrigeration cycle is optimized, the effect of increasing the capacity and improving the energy efficiency is achieved simultaneously, and the device is particularly suitable for the working condition of low temperature low-pressure.
Further, the first stage compression cylinder 22a may be switchable between a cylinder-rest operating condition and a cylinder-release operating condition. Here, the cylinder-rest operation state refers to a state in which the gas is not compressed in the first-stage compression chamber 220, and the cylinder-release operation state refers to a state in which the gas can be compressed in the first-stage compression chamber 220 when the first-stage compression cylinder 22a is normally intake. Thus, the first stage compression cylinder 22a, which is a low pressure stage cylinder, may be formed as a variable capacity cylinder, that is, may or may not be operated.
Therefore, under the working condition of low load, the single-stage compression cylinder 21 and the second-stage compression cylinder 22b in the two-stage compression cylinder 22 can be adopted for single-stage compression, so that the displacement of the rotary compressor 100 is smaller, the overpressure is reduced, the displacement is proper, and the energy efficiency is higher. Under the working condition of heavy load, such as ultralow temperature low-pressure, the single-stage compression cylinder 21, the first-stage compression cylinder 22a and the second-stage compression cylinder 22b can all operate, the rotary compressor 100 can work in full displacement, under the working condition of large pressure difference and large pressure ratio, the two-stage jet compression cycle optimizes the system circulation, leakage of each stage of cylinders can be effectively reduced, and meanwhile, the jet saves more power, so that under the condition, the two-stage compression work can improve the energy efficiency while the capacity is increased.
The motor assembly 30 may be disposed within the housing 10 and may drive the compression mechanism 20 in operation. The motor assembly 30 may include a stator 31 and a rotor 32, where the crankshaft 23 of the compression mechanism 20 is connected to the rotor 32, the single-stage compression chamber 210, the first-stage compression chamber 220 and the second-stage compression chamber 230 are respectively provided with a piston 24 and a sliding vane 25, the piston 24 is sleeved on the crankshaft 23 to rotate with the crankshaft 23, and the crankshaft 23 can drive the piston 24 to rotate in the corresponding compression chamber and cooperate with the sliding vane 25 under the driving of the rotor 32, so as to compress the gas. The motor assembly 30 and the associated structure with the crankshaft 23 and the piston 24, etc., are well known to those skilled in the art and will not be described in further detail herein.
According to the rotary compressor 100 of the embodiment of the present invention, by providing the single-stage compression cylinder 21 and the two-stage compression cylinder 22, and providing the mixing chamber 240 communicating the first-stage compression chamber 220 and the second-stage compression chamber 230 in the two-stage compression cylinder 22 and setting the first-stage compression cylinder 22a of the two-stage compression cylinder 22 as a variable capacity cylinder, the effects of simultaneously taking into consideration the operation capacity and the energy efficiency of the compressor can be achieved, and the refrigeration cycle can be optimized.
Alternatively, the single stage compression chambers 210, the first stage compression chambers 220, and the second stage compression chambers 230 may be arbitrarily arranged in the axial direction of the casing 10 according to some embodiments of the present invention. In other words, the rotary compressor 100 has three compression chambers arranged in the axial direction of the compression mechanism 20, which are in one-to-one correspondence with the single-stage compression chamber 210, the first-stage compression chamber 220, and the second-stage compression chamber 230, respectively, and any one of the three compression chambers may be provided as any one of the single-stage compression chamber 210, the first-stage compression chamber 220, and the second-stage compression chamber 230. The arrangement of the three compression chambers can be flexibly set by a person skilled in the art according to actual requirements.
For example, in the embodiment shown in fig. 1-4, the rotary compressor 100 has an upper compression chamber, an intermediate compression chamber, and a lower compression chamber, the upper compression chamber may be a single stage compression chamber 210, the lower compression chamber may be a first stage compression chamber 220, and the intermediate compression chamber may be a second stage compression chamber 230. Thus, the first stage compression chambers 220 and the second stage compression chambers 230 may be positioned adjacent to each other, providing for easier placement and better gas flow properties.
According to some embodiments of the present invention, an exhaust chamber 250 may also be provided within the compression mechanism 20, the exhaust chamber 250 being in communication with the first exhaust port, as shown in fig. 2-4. Thus, the high pressure gas compressed in two stages may be introduced into the discharge chamber 250 through the first discharge port and then discharged into the inner space of the casing 10, thereby improving the discharge performance.
In the embodiment of the present invention, the arrangement position of the discharge chamber 250 is not particularly limited, and alternatively, in some embodiments of the present invention, the discharge chamber 250 may be defined by two stacked partitions 26 provided between any two of the single stage compression chamber 210, the first stage compression chamber 220, and the second stage compression chamber 230. That is, two partitions 26 may be disposed between any two of the single stage compression chambers 210, the first stage compression chambers 220, and the second stage compression chambers 230, the two partitions 26 may be disposed in a stacked manner, the discharge chamber 250 may be defined by the two stacked partitions 26, the arrangement is more convenient, and the adjustment of the discharge chamber 250 may be achieved by replacing the partition 26.
For example, in the embodiment shown in fig. 1-4, one partition 26 may be disposed between the first stage compression chamber 220 and the second stage compression chamber 230, two stacked partitions 26 may be disposed between the single stage compression chamber 210 and the second stage compression chamber 230, and the discharge chamber 250 may be defined by the two partitions 26.
In the embodiment of the present invention, the mixing chamber 240 may be flexibly disposed at a plurality of positions according to the structure, and the present invention is not particularly limited thereto. For example, according to some specific examples of the invention, the mixing chamber 240 may be defined by a stacked baffle 26 disposed between any two of the single stage compression chamber 210, the first stage compression chamber 220, and the second stage compression chamber 230. As another example, the mixing chamber 240 may be defined by the bearing 27 of the compression mechanism 20 and the cover plate 28 provided on the bearing 27, wherein the bearing 27 may be an upper bearing or a lower bearing, and as shown in fig. 1 to 4, the mixing chamber 240 is defined by the bearing 27 located at the lower side and the cover plate 28 provided under the bearing 27. In the case of a structure in which the mixing chamber 240 is provided between the two partitions 26, a high-pressure chamber may be provided on the bearing 27 located at the lower side to serve as a discharge chamber, as shown in fig. 5. Alternatively, in the embodiment shown in fig. 5, the cover plate 28 may be removed and the muffler may be provided directly on the bearing 27 on the lower side.
Optionally, a first air injection channel 2411 may be disposed in the two-stage compression cylinder 22, as shown in fig. 2, at least a portion of the first air injection channel 241 is formed by the first air injection channel 2411, and a first air injection port of the first air injection channel 241 may be disposed on the second-stage compression cylinder 22b, the bearing 27, the partition 26 or the cover plate 28, so that the position of the first air injection port of the first air injection channel 241 may be flexibly set according to the specific structure of the compression mechanism 20, thereby realizing more flexible setting of an external structure and convenient installation.
Optionally, the rotary compressor 100 further includes a second air injection flow path 212, as shown with reference to fig. 6, 9 and 10, the second air injection flow path 212 being in communication with the single stage compression chamber 210. Therefore, the single-stage compression cylinder 21 can jet air, the refrigeration cycle of single-stage compression can be further optimized, the single-stage compression capacity is improved, and the low-temperature heating quantity of single-stage compression is improved.
A second air injection channel 213 may be disposed in the single stage compression cylinder 21, as shown in fig. 6, the second air injection channel 213 may be used as a part of the second air injection flow path 212, where the second air injection port 2131 of the second air injection flow path 212 may be flexibly disposed on the single stage compression cylinder 21, the bearing 27, the partition 26 or the cover plate 28, so as to better adapt to other structures of the compression mechanism 20.
Further, according to some embodiments of the present invention, a check valve may be further disposed on the second gas injection flow path 212, where the check valve may control the unidirectional delivery of the gas to the single-stage compression chamber 210, that is, the gas on the second gas injection flow path 212 may flow into the single-stage compression chamber 210 through the check valve, and the gas in the single-stage compression chamber 210 may not flow outward through the check valve.
In the embodiment of the present invention, the capacity variation manner of the first stage compression cylinder 22a is not particularly limited. Alternatively, in some embodiments of the present invention, the first stage compression cylinder 22a may switch between the cylinder-rest operation state and the cylinder-rest release operation state by controlling the pressure of the first injection flow path 241, as shown in fig. 3 and 7, and the switching operation is convenient and reliable. For example, in some specific examples of the present invention, when the mixing chamber 240 is filled with medium pressure gas (i.e., the pressure of the first injection flow path 241 is medium pressure), the exhaust of the first stage compression cylinder 22a is medium pressure, the intake of the second stage compression cylinder 22b is medium pressure, and at this time, the first stage compression cylinder 22a and the second stage compression cylinder 22b form two-stage compression; when the low-pressure gas is introduced into the mixing chamber 240 (i.e., the pressure of the first air injection flow path 241 is low), the exhaust of the first stage compression cylinder 22a is low, the first stage compression cylinder 22a enters the rest cylinder, the gas is not compressed, the suction pressure of the second stage compression cylinder 22b is low, and the discharge pressure is high, so that single stage compression is formed.
As shown in fig. 7 and 8, the rotary compressor 100 further includes a three-way valve 40, three ports of the three-way valve 40 being respectively communicated with the first gas injection flow path 241, the accumulator outlet, and the flash evaporator 300. Thus, the low-pressure gas or the medium-pressure gas can be introduced into the first air injection flow path 241 by controlling the three-way valve 40, and the air intake is convenient to control.
Alternatively, in other embodiments of the present invention, the capacity-variable mode of the first stage compression cylinder 22a is a vane back pressure switching, specifically, a vane back pressure chamber 215 is provided in the compression mechanism 20, as shown in fig. 4, the switching operation is convenient and reliable by controlling the back pressure of the vane 25 to switch between the cylinder-rest operation state and the cylinder-rest release operation state of the first stage compression cylinder 22 a.
For example, in the embodiment shown in fig. 9, a three-way valve 40 may be provided on the back pressure chamber line 217 communicating with the slide back pressure chamber 215, and three ports of the three-way valve 40 communicate with the slide back pressure chamber 215, the reservoir inlet, and the flash vessel 300, respectively. Thus, the low-pressure gas or the medium-pressure gas can be introduced into the sliding vane back pressure cavity 215 by controlling the three-way valve 40, and the air inlet is convenient to control. When low-pressure gas is introduced, the back pressure and the head pressure of the slide vane 25 are approximately the same, the slide vane 25 does not work, the first-stage compression cylinder 22a is in a cylinder-rest state, and when medium-pressure gas is introduced, the slide vane 25 is in a normal working state, and the first-stage compression cylinder 22a releases the cylinder-rest state.
Further, the pressure of the vane back pressure chamber 215 of the first stage compression cylinder 22a may be varied in synchronization with the pressure of the mixing chamber 240. Thus, when the pressure in the mixing chamber 240 is low, the slide back pressure chamber 215 is low, and the slide 25 does not work; when the mixing chamber 240 is at medium pressure, the sliding vane back pressure chamber 215 is also at medium pressure, and the sliding vane 25 can work normally, so that the friction loss during partial capacity work can be further reduced, the abrasion of the sliding vane 25 can be reduced, and the reliability of the sliding vane 25 is facilitated.
Alternatively, as shown in fig. 4 and 10, a pressure channel 260 may be provided in the compression mechanism 20, and the pressure channel 260 may be in communication with the vane back pressure chamber 215 and the mixing chamber 240, so that the vane back pressure chamber 215 and the mixing chamber 240 may be in communication through the pressure channel 260, and thus synchronous pressure changes may be achieved. Therefore, the sliding vane back pressure cavity 215 and the mixing cavity 240 can be communicated through the internal channel of the compression mechanism 20, so that the external pipeline can be reduced, the installation is convenient, and the cost is saved.
Alternatively, the vane 25 in the first stage compression chamber 220 may be configured to be positioned to be controlled by adjusting the pressure of the vane back pressure chamber 215. That is, the slide 25 in the first stage compression chamber 220 is not controlled by the elastic element 291 any more, and is realized by adjusting the pressure of the gas, so that not only the elements can be saved and the production cost of the compressor can be reduced, but also the slide 25 does not abut against the piston 24 without the action of the elastic element 291 such as a spring when the first stage compression cylinder 22a is depressurized, the friction between the head of the slide 25 and the piston 24 can be avoided, and the abrasion and the power can be reduced. For example, as shown in fig. 3 and fig. 4, a suction port communicating with the vane back pressure chamber 215 may be provided on the first stage compression cylinder 22a, and the pressure of the vane back pressure chamber 215 may be controlled by controlling the air inlet and outlet condition of the suction port, so as to realize adjustment of the position of the vane 25, which is convenient and reliable to control.
According to some embodiments of the present invention, the compression mechanism 20 may be provided with a magnetic element 292, as shown in fig. 3 and 4, the magnetic element 292 may interact with the slide 25 in the first stage compression chamber 220 to brake the slide 25 when the first stage compression cylinder 22a is in the cylinder-rest operating state. Therefore, the slide vane 25 can be more stably kept in the slide vane groove when the first-stage compression cylinder 22a is in a cylinder rest state, the slide vane 25 is prevented from colliding with the piston 24 or the cylinder due to movement caused by internal air pressure fluctuation, parts are damaged, and the reliability of the compressor is improved.
Assuming that the working displacement of the single stage compression cylinder 21 is V1, the working displacement of the second stage compression cylinder 22b is V2, and the working displacement of the first stage compression cylinder 22a is V3, as shown in fig. 7, in order to maintain a high energy efficiency, the ratio of V2/v3=0.40 to 0.95, that is, the ratio of V2 to V3 may be in the range of 0.40 to 0.95 (including two end values). For example, in some embodiments of the present invention, V2/V3 has values of 0.45, 0.55, 0.60, 0.65, 0.70, 0.75, 0.80, 0.85, etc., respectively. As shown in fig. 8, in order to maintain high energy efficiency, V1/v3=0.4-1.6, i.e., the ratio of V1 to V3 can be in the range of 0.4-1.6 (including both end points). For example, in some embodiments of the present invention, V1/V3 has a value of 0.55, 0.75, 0.95, 1.15, 1.35, etc., respectively.
Aiming at different areas and using conditions, different energy efficiency is brought by different future V2/V3 and V1/V3, and when the temperature difference between evaporation and condensation is large (such as a heat pump working condition), V2/V3 can be set to be a smaller value; when the temperature difference is smaller, a larger value can be taken, and V1/V3 is opposite to V2/V3, so that the energy efficiency of the compressor can be improved according to different areas and different using conditions.
As shown in fig. 9 and 10, an air conditioning system 1000 according to an embodiment of the present invention includes a rotary compressor 100 according to an embodiment of the present invention. Since the rotary compressor 100 according to the embodiment of the present invention has the above advantageous technical effects, the air conditioning system 1000 according to the embodiment of the present invention can be compatible with both capacity and energy efficiency, especially in the case of ultra-low temperature and low-temperature.
The air conditioning system 1000 may further include: the condenser 200, the flash evaporator 300, the evaporator 400, the first throttling device 500, the second throttling device 600, the four-way valve 700, the accumulator 800, etc., as shown with reference to fig. 9 and 10, may be connected to the rotary compressor 100 to form a compression system loop, the connection structure, etc., of which will be understood by those skilled in the art, and will not be described in detail herein.
The air conditioning system 1000 according to the embodiment of the present invention may be applied to a refrigerating apparatus, and other configurations and operations of the air conditioning system 1000 will be known to those skilled in the art, and will not be described in detail herein.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples without interference or conflict.
Claims (16)
1. A rotary compressor, comprising:
a housing;
the compression mechanism is arranged in the shell and comprises a single-stage compression cylinder and a two-stage compression cylinder, the single-stage compression cylinder is provided with a single-stage compression cavity, a single-stage air suction port and a single-stage exhaust port, the two-stage compression cylinder comprises a first-stage compression cylinder and a second-stage compression cylinder, the first-stage compression cylinder is provided with a first-stage compression cavity and a first air suction port, the second-stage compression cylinder is provided with a second-stage compression cavity and a second-stage air suction port, the compression mechanism is provided with a mixing cavity communicated with the first-stage compression cavity and the second-stage compression cavity and a first air injection flow path communicated with the mixing cavity, and the first-stage compression cylinder is switchable between a cylinder-rest running state and a cylinder-rest running releasing state;
the motor component is arranged in the shell and is suitable for driving the compression mechanism to work;
a second jet flow path in communication with the single stage compression chamber;
and the second jet flow path is provided with a one-way valve for controlling the one-way delivery of the gas to the single-stage compression cavity.
2. The rotary compressor of claim 1, wherein the single stage compression chambers, the first stage compression chambers, and the second stage compression chambers are arranged arbitrarily along an axial direction of the compression mechanism.
3. The rotary compressor of claim 1, wherein a discharge chamber in communication with the first discharge port of the second stage compression cylinder is further provided within the compression mechanism.
4. A rotary compressor according to claim 3, wherein the discharge chamber is defined by two stacked diaphragms disposed between any two of the single stage compression chamber, first stage compression chamber and second stage compression chamber.
5. The rotary compressor of claim 1, wherein the mixing chamber is defined by two stacked diaphragms disposed between any two of the single stage compression chamber, the first stage compression chamber, and the second stage compression chamber, or the mixing chamber is defined by a bearing of the compression mechanism and a cover plate disposed on the bearing.
6. The rotary compressor of any one of claims 1 to 5, wherein the first stage compression cylinder is switched between a cylinder-rest operation state and a cylinder-rest release operation state by controlling a pressure level of the first injection flow path.
7. The rotary compressor of any one of claims 1 to 5, wherein a sliding vane back pressure chamber with variable pressure is provided in the first stage compression cylinder, so as to realize switching of the first stage compression cylinder between a cylinder-rest operation state and a cylinder-rest release operation state by controlling the back pressure of the sliding vane.
8. The rotary compressor of claim 7, wherein the pressure of the vane back pressure chamber is varied in synchronization with the pressure of the mixing chamber.
9. The rotary compressor of claim 8, wherein a pressure passage is provided in the compression mechanism for communicating the slide back pressure chamber and the mixing chamber.
10. The rotary compressor of claim 1, wherein the first gas injection port of the first gas injection flow path is provided on the first stage compression cylinder, the second stage compression cylinder, a bearing, a partition plate, or a cover plate.
11. The rotary compressor of claim 1, wherein the second gas injection port of the second gas injection flow path is provided on a single stage compression cylinder, bearing, baffle, or cover plate.
12. The rotary compressor of claim 1, wherein the vane in the first stage compression chamber is configured to be controlled in position by adjusting the pressure of the vane back pressure chamber.
13. The rotary compressor of claim 1, wherein the compression mechanism is provided with a magnetic element that acts on a slide in the first stage compression chamber to brake the slide when the first stage compression cylinder is in a cylinder-rest operating state.
14. The rotary compressor of claim 1, wherein the single stage compression cylinder has a working displacement V1 and the first stage compression cylinder has a working displacement V3, wherein V1/v3 = 0.4-1.6.
15. The rotary compressor of claim 1, wherein the working displacement of the second stage compression cylinder is V2 and the working displacement of the first stage compression cylinder is V3, wherein V2/v3 = 0.40-0.95.
16. An air conditioning system comprising a rotary compressor according to any one of claims 1-15.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710752485.3A CN107489618B (en) | 2017-08-28 | 2017-08-28 | Rotary compressor and air conditioning system with same |
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| CN201710752485.3A CN107489618B (en) | 2017-08-28 | 2017-08-28 | Rotary compressor and air conditioning system with same |
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| CN107489618B true CN107489618B (en) | 2023-10-24 |
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| CN108825502A (en) * | 2018-08-13 | 2018-11-16 | 珠海凌达压缩机有限公司 | A kind of twin-tub double-stage compressor and refrigeration system |
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| CN101460789A (en) * | 2006-06-01 | 2009-06-17 | 开利公司 | Multi-stage compressor unit for a refrigeration system |
| JP2010156498A (en) * | 2008-12-26 | 2010-07-15 | Daikin Ind Ltd | Refrigerating device |
| KR20130096859A (en) * | 2012-02-23 | 2013-09-02 | 엘지전자 주식회사 | Compressor and air conditioner |
| CN104454528A (en) * | 2014-12-03 | 2015-03-25 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor and refrigerating device with same |
| CN207297357U (en) * | 2017-08-28 | 2018-05-01 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its air-conditioning system |
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| CN101460789A (en) * | 2006-06-01 | 2009-06-17 | 开利公司 | Multi-stage compressor unit for a refrigeration system |
| JP2010156498A (en) * | 2008-12-26 | 2010-07-15 | Daikin Ind Ltd | Refrigerating device |
| KR20130096859A (en) * | 2012-02-23 | 2013-09-02 | 엘지전자 주식회사 | Compressor and air conditioner |
| CN104454528A (en) * | 2014-12-03 | 2015-03-25 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor and refrigerating device with same |
| CN207297357U (en) * | 2017-08-28 | 2018-05-01 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its air-conditioning system |
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