CN115030900A - Pump body subassembly, compressor, two temperature air conditioning system - Google Patents
Pump body subassembly, compressor, two temperature air conditioning system Download PDFInfo
- Publication number
- CN115030900A CN115030900A CN202210842633.1A CN202210842633A CN115030900A CN 115030900 A CN115030900 A CN 115030900A CN 202210842633 A CN202210842633 A CN 202210842633A CN 115030900 A CN115030900 A CN 115030900A
- Authority
- CN
- China
- Prior art keywords
- air
- cylinder
- port
- pressure compression
- compression part
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
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
- 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
- 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
Abstract
The invention provides a pump body assembly, a compressor and a dual-temperature air conditioning system, wherein the pump body assembly comprises a high-pressure compression part and a low-pressure compression part, the high-pressure compression part comprises a first air cylinder and a first sliding sheet, the low-pressure compression part comprises a second air cylinder and a second sliding sheet, the high-pressure compression part is provided with a first air supplement port, the low-pressure compression part is provided with a second air supplement port, the first sliding sheet is superposed with the second sliding sheet, a first central included angle beta based on the center of the first air cylinder is formed between the air supplement central line of the first air supplement port and the symmetrical central line of the first sliding sheet, a second central included angle alpha based on the center of the second air cylinder is formed between the air supplement central line of the second air supplement port and the symmetrical central line of the second sliding sheet, and alpha is larger than beta. According to the invention, different requirements of the high-pressure compression part and the low-pressure compression part in the aspect of suction pressure are met, and the energy efficiency of the system is effectively improved; the structure is more compact, the miniaturization design of the compressor is facilitated, and the volumetric efficiency of the compressor can be improved.
Description
Technical Field
The invention belongs to the technical field of air conditioning, and particularly relates to a pump body assembly, a compressor and a dual-temperature air conditioning system.
Background
As a device for adjusting the comfort of the environment, an air conditioning system has been developed from a single temperature adjustment with more diversified functions to satisfy the demand for the comfort of the living environment that people are continuously improving. The main dehumidification mode of the existing air conditioning system is refrigeration dehumidification, namely, the surface temperature of an indoor heat exchanger is reduced to be lower than the dew point temperature of air, and when indoor air flows through the surface of the heat exchanger, water vapor in the air is condensed to remove air moisture. The mode is suitable for a high-temperature environment, the indoor temperature reduction is completed while dehumidification is carried out, but under the condition that the temperature is not high but the relative humidity is high in the 'plum rain season' of Yangtze river basin or the 'return south day' period of south China, when the conventional household variable frequency air conditioner carries out refrigeration and dehumidification in a transition season, the indoor return air temperature and the return air dew point are gradually reduced, and the indoor relative humidity is not reduced or even increased after being reduced to a certain degree, so that the indoor cooling is carried out but not dried; on the other hand, the reduction in the evaporating temperature and the return air dew point leads to a significant reduction in the unit energy consumption dehumidification capacity of the air conditioner. Therefore, in humid weather in transition seasons, the conventional household variable frequency air conditioner cannot meet the dehumidification comfort requirement, and is usually in an idle state.
The air conditioning system can realize indoor dual-temperature step heat exchange in a refrigeration mode, the parallel cylinders can effectively reduce the dryness of the inlet of the evaporator, improve the refrigerating capacity of the indoor evaporator and improve the refrigerating energy efficiency ratio, and the system also has the functions of reheating and dehumidifying and realizing the functions of dehumidifying and not cooling in transition seasons. However, in the scheme, the three-cylinder compressor is adopted, and the air supplementing cylinder is independently arranged for supplementing air, so that the cost is high, when the total displacement is low, the small cylinder (air supplementing cylinder) is limited by the diameter of the crankshaft, the diameter of the small cylinder cannot be miniaturized, and the cylinder parameters cannot reach the optimal design, so that the volume efficiency is low, the mechanical damage is large, and the system performance is poor; meanwhile, in a double-evaporation-temperature (namely double-temperature) air conditioning system, the suction pressures of two cylinders are different, the same angle between the air supplementing ports of the two cylinders and the corresponding sliding sheets obviously does not adapt to the requirement of the double-temperature air conditioning system in the conventional double-cylinder quasi-two-stage compressor in the prior art, the respective angles of the two cylinders are required to be optimized, and the invention is provided for solving the problems.
Disclosure of Invention
Therefore, the invention provides a pump body assembly, a compressor and a dual-temperature air conditioning system, which can overcome the defects that the manufacturing cost of the compressor is higher due to the independent arrangement of the air supplementing cylinder and the air supplementing cylinder is limited by the size of the diameter of the crankshaft, so that the compressor cannot be designed in a miniaturized manner in the related art.
In order to solve the above problems, the present invention provides a pump assembly, including a high pressure compression part and a low pressure compression part, where the high pressure compression part includes a first cylinder and a first slide plate disposed corresponding to the first cylinder, the low pressure compression part includes a second cylinder and a second slide plate disposed corresponding to the second cylinder, the high pressure compression part has a first air supplement port, the low pressure compression part has a second air supplement port, and projects on a radial surface of the pump assembly, the first slide plate and the second slide plate are overlapped, a first center included angle β based on a center of the first cylinder is provided between an air supplement center line of the first air supplement port and a symmetric center line of the first slide plate, a second center included angle α based on a center of the second cylinder is provided between an air supplement center line of the second air supplement port and a symmetric center line of the second slide plate, and α > β.
In some embodiments, 56 ≦ β ≦ 238; and/or alpha is more than or equal to 63 degrees and less than or equal to 273 degrees.
In some embodiments, when the pump body assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system operates in a cooling mode, the first cylinder is connected in series with an indoor windward side heat exchanger, the second cylinder is connected in series with an indoor leeward side heat exchanger, the volume ratio of the first cylinder to the second cylinder is a, the load ratio of the indoor windward side heat exchanger to the indoor leeward side heat exchanger is b, and a/b is greater than or equal to 0.7 and less than or equal to 1.1.
In some embodiments, 0.9 ≦ a ≦ 1.3; and/or b is more than or equal to 0.72 and less than or equal to 1.04; and/or, a/b is 0.8.
In some embodiments, a middle partition plate is sandwiched between the first cylinder and the second cylinder, the first air supplement port and the second air supplement port are respectively arranged on two opposite end surfaces of the middle partition plate, and an air supplement channel communicated with the first air supplement port and the second air supplement port is configured in the middle partition plate, and the air supplement channel is provided with a main air supplement port connected with an external air supplement pipeline.
The invention also provides a pump body assembly, which comprises a high-pressure compression part and a low-pressure compression part, wherein the high-pressure compression part comprises a first air cylinder and a first sliding sheet arranged corresponding to the first air cylinder, the low-pressure compression part comprises a second air cylinder and a second sliding sheet arranged corresponding to the second air cylinder, one of the high-pressure compression part and the low-pressure compression part is provided with an air supplementing port, the projection is performed on a radial surface of the pump body assembly, the first sliding sheet and the second sliding sheet are overlapped, when the high-pressure compression part is provided with the air supplementing port, a first center included angle beta based on the center of the first air cylinder is formed between the air supplementing central line of the air supplementing port and the symmetrical central line of the first sliding sheet, and the beta is not less than 56 degrees and not more than 144 degrees; or when the low-pressure compression part is provided with the air supplementing port, a second center included angle alpha based on the center of the second cylinder is formed between the air supplementing center line of the air supplementing port and the symmetrical center line of the second slide piece, and the angle alpha is larger than or equal to 63 degrees and smaller than or equal to 166 degrees.
In some embodiments, a middle partition plate is sandwiched between the first cylinder and the second cylinder, the air supplement port is arranged on one end face of the middle partition plate, an air supplement channel communicated with the air supplement port is constructed in the middle partition plate, and the air supplement channel is provided with a main air supplement port connected with an external air supplement pipeline.
The invention also provides a compressor, which comprises the pump body assembly.
The invention also provides a double-temperature air conditioning system which comprises a compressor, wherein the compressor is the compressor.
In some embodiments, the dual-temperature air conditioning system further includes a first four-way reversing valve, a second four-way reversing valve, an indoor windward heat exchanger, an indoor leeward heat exchanger, an outdoor heat exchanger, and a first throttling element, wherein D ports of the first four-way reversing valve and the second four-way reversing valve are collectively communicated with an exhaust port of the compressor, C port of the first four-way reversing valve is communicated with one end of the outdoor heat exchanger away from the first throttling element, E port and S port of the first four-way reversing valve and C port of the second four-way reversing valve are collectively communicated with one end of the indoor windward heat exchanger away from the first throttling element and communicated with a first suction port of the high-pressure compression part, a one-way valve is disposed on a connection branch of C port of the second four-way reversing valve, and the one-way valve allows the refrigerant to flow into the C port to be reversely cut off, and an S port of the second four-way reversing valve is communicated with a second air suction port arranged in the low-pressure compression part, and an E port of the second four-way reversing valve is communicated with one end, far away from the first throttling element, of the indoor leeward side heat exchanger.
According to the pump body assembly, the compressor and the dual-temperature air conditioning system, on one hand, dislocation is formed on the axial projection of the pump body assembly by the first air supplement port and the second air supplement port which are respectively arranged on the high-pressure compression part and the low-pressure compression part, so that different requirements of the high-pressure compression part and the low-pressure compression part on the aspect of suction pressure are met, and the System Energy Efficiency (SEER) can be effectively improved; on the other hand, set up corresponding tonifying qi mouth respectively to high pressure compression portion and low pressure compression portion, do not set up the benefit cylinder alone (also be the minimum jar of diameter among the three-cylinder compressor), reduced the manufacturing cost of compressor, simultaneously when the compressor discharge capacity is less, need not to consider the relation of benefit cylinder and bent axle diameter, can carry out optimal design to the parameter of first cylinder and second cylinder, the structure is compacter is favorable to the miniaturized design of compressor, and can improve compressor volumetric efficiency.
Drawings
FIG. 1 is a schematic view (simplified schematic view) of a pump body assembly according to an embodiment of the present invention, as viewed in an axial direction thereof;
FIG. 2 is a schematic view (simplified schematic view) of the internal structure of a compressor according to another embodiment of the present invention;
FIG. 3 is a schematic structural view of the middle partition plate in FIG. 2;
FIG. 4 is a schematic view (simplified schematic view) of the internal structure of a compressor according to still another embodiment of the present invention;
FIG. 5 is a schematic view of the structure of the middle partition plate in FIG. 4;
fig. 6 is a schematic view of a state of the dual-temperature air conditioning system (including a refrigerant flow direction schematic) in a cooling mode according to the embodiment of the present invention;
fig. 7 is a schematic diagram (including a schematic diagram of a refrigerant flow direction) of a dual-temperature air conditioning system in a heating mode according to an embodiment of the present invention;
fig. 8 is a schematic diagram of a state of the dual-temperature air conditioning system in the dehumidification reheating mode (including a refrigerant flow direction) according to the embodiment of the present invention;
FIG. 9 is a graphical illustration of the correlation of α/β with the magnitude of the energy efficiency boost compared to a single stage system in the pump block assembly of FIG. 1;
FIG. 10 is a graph showing the correlation of the volume ratio a to the relative optimum;
FIG. 11 is a graph illustrating the dependence of α/β on the magnitude of the energy efficiency increase compared to a single stage system in the pump block assembly shown in FIG. 4.
The reference numerals are represented as:
11. a first cylinder; 12. a first slip sheet; 13. a first air supplement port; 14. a first roller; 21. a second cylinder; 22. a second slip sheet; 23. a second air supplement port; 24. a second roller; 3. a middle partition plate; 31. a total air supplement port; 100. a compressor; 101. an exhaust port; 102. a first air intake port; 103. a second air suction port; 201. an indoor windward side heat exchanger; 202. an indoor leeward side heat exchanger; 203. an outdoor heat exchanger; 301. a first four-way reversing valve; 302. a second four-way reversing valve; 3021. a one-way valve; 400. a first throttling element; 401. a second throttling element; 402. a third throttling element; 500. a flash tank.
Detailed Description
Referring to fig. 1 to 11 in combination, according to an embodiment of the present invention, there is provided a pump assembly, applied to a dual-temperature air conditioning system, including a high-pressure compression portion and a low-pressure compression portion, wherein the high-pressure compression portion includes a first cylinder 11, and a first vane 12 and a first roller 14 disposed corresponding thereto, the low-pressure compression portion includes a second cylinder 21, and a second vane 22 and a second roller 24 disposed corresponding thereto, the high-pressure compression portion has a first air supplement port 13, the low-pressure compression portion has a second air supplement port 23, and a projection is performed on a radial surface of the pump assembly (specifically, see fig. 1), the first vane 12 and the second vane 22 are overlapped, a first center included angle β based on a center of the first cylinder 11 is formed between an air supplement center line of the first air supplement port 13 and a symmetric center line of the first vane 12, a second center angle α based on a center of the second cylinder 21 is formed between an air supplement center line of the second air supplement port 23 and a symmetric center line of the second vane 22, alpha is more than beta. In the technical scheme, on one hand, the first air supplement port 13 and the second air supplement port 23 which are respectively arranged on the high-pressure compression part and the low-pressure compression part are staggered on the axial projection of the pump body assembly, so that different requirements of the high-pressure compression part and the low-pressure compression part on the air supplement amount of the cylinder are met, and the System Energy Efficiency (SEER) can be effectively improved; on the other hand, corresponding air supplementing ports are respectively arranged for the high-pressure compression part and the low-pressure compression part, the air supplementing cylinder (namely the cylinder with the minimum diameter in the three-cylinder compressor) is not independently arranged, the manufacturing cost of the compressor is reduced, meanwhile, when the compressor displacement is small, the relation between the air supplementing cylinder and the diameter of the crankshaft does not need to be considered, the structure is more compact, the miniaturization design of the compressor is facilitated, and the volumetric efficiency of the compressor can be improved. It can be understood that the corresponding compressor in this embodiment is a double suction double supplement quasi-two stage compressor. In addition, the angle between α and β covers the corresponding air inlet.
Specifically, the gas supply center line is, for example, a center of a circular hole when the first gas supply port 13 is the circular hole, or a geometric center of a corresponding shape when the first gas supply port 13 is any other regular shape, such as a triangle, a quadrangle, etc., and the aforementioned symmetric center line refers to a symmetric center line of the sliding vane in the sliding direction.
It can be understood that the specific installation positions of the first air supplement port 13 and the second air supplement port 23 should be located at the position covered by the compression cavity before the discharge pressure after the corresponding compression portion compresses the refrigerant to the corresponding intermediate pressure, and the intermediate pressure may be given according to the actual system requirements.
In one specific embodiment, as shown in FIG. 9, 56 ≦ β ≦ 238; alpha is more than or equal to 63 degrees and less than or equal to 273 degrees, and the specific design value is obtained by comprehensively calculating parameters such as air suction pressure, air supply pressure, exhaust pressure, compressor size and the like. The value range enables the corresponding volumetric efficiency of the compressor and the energy efficiency of the system to be at a high level.
In some embodiments, when the pump body assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system operates in a cooling mode, the first cylinder 11 is connected in series with the indoor windward side heat exchanger 201, the second cylinder 21 is connected in series with the indoor leeward side heat exchanger 202, the volume ratio of the first cylinder 11 to the second cylinder 21 is a, the load ratio of the indoor windward side heat exchanger 201 to the indoor leeward side heat exchanger 202 is b, 0.7 ≦ a/b ≦ 1.1, preferably, a/b ≦ 0.8, and in a preferred embodiment, 0.9 ≦ a ≦ 1.3 (as shown in fig. 10); and/or b is more than or equal to 0.72 and less than or equal to 1.04, and the values of the specific relevant parameters need to be reasonably selected according to the configuration of the specifically selected heat exchanger. In the technical scheme, the volume ratio of the two cylinders, the load ratio of the heat exchanger and the ratio of the two are limited, so that the energy efficiency of the corresponding air conditioning system can be further improved.
Referring to fig. 3, a middle partition plate 3 is interposed between the first cylinder 11 and the second cylinder 21, the first air supplement port 13 and the second air supplement port 23 are respectively disposed on two opposite end surfaces of the middle partition plate 3, an air supplement channel communicated with the first air supplement port 13 and the second air supplement port 23 is configured in the middle partition plate 3, and the air supplement channel has a main air supplement port 31 connected with an external air supplement pipeline. Through setting up tonifying qi passageway and first tonifying qi mouth 13, second tonifying qi mouth 23 on median septum 3, realize the tonifying qi to two cylinders, can further optimize the structure of compressor.
As shown in fig. 4, the present invention further provides a pump assembly, which includes a high-pressure compression portion and a low-pressure compression portion, wherein the high-pressure compression portion includes a first cylinder 11 and a first sliding vane 12 disposed corresponding to the first cylinder 11, the low-pressure compression portion includes a second cylinder 21 and a second sliding vane 22 disposed corresponding to the second cylinder 21, one of the high-pressure compression portion and the low-pressure compression portion has an air supplementing port, and when the high-pressure compression portion has an air supplementing port, a first center included angle β based on the center of the first cylinder 11 is formed between an air supplementing center line of the air supplementing port and a symmetric center line of the first sliding vane 12, and the first center included angle β is greater than or equal to 56 ° and less than or equal to 144 ° (see fig. 11 specifically); alternatively, when the low pressure compression part has the air supplement port, a second center angle α between the air supplement center line of the air supplement port and the symmetric center line of the second vane 22 is 63 ° or more and 166 ° or less based on the center of the second cylinder 21 (see fig. 11 for details). The specific design values of the alpha and the beta are obtained by comprehensive calculation according to parameters such as air suction pressure, air supply pressure, exhaust pressure, compressor size and the like. The value range enables the corresponding volumetric efficiency of the compressor and the energy efficiency of the system to be at a high level. It can be understood that the corresponding compressor in this embodiment is a double suction single air make-up quasi-two stage compressor.
Referring to fig. 5, a middle partition plate 3 is interposed between the first cylinder 11 and the second cylinder 21, the air supplement port is disposed on one end surface of the middle partition plate 3, and an air supplement channel communicated with the air supplement port is configured in the middle partition plate 3, and the air supplement channel has a main air supplement port 31 connected with an external air supplement pipeline. By providing the air supplement channel and the corresponding air supplement port (e.g., the first air supplement port 13 or the second air supplement port 23) on the middle partition plate 3, the air supplement to the low pressure compression part or the high pressure compression part is realized, and the structure of the compressor can be further optimized.
According to an embodiment of the invention, a compressor is also provided, which comprises the pump body assembly.
According to an embodiment of the present invention, there is also provided a dual-temperature air conditioning system, including a compressor 100, where the compressor 100 is the above-mentioned compressor. Specifically, the dual-temperature air conditioning system further includes a first four-way reversing valve 301, a second four-way reversing valve 302, an indoor windward heat exchanger 201, an indoor leeward heat exchanger 202, an outdoor heat exchanger 203, a first throttling element 400, and a flash device 500, wherein D ports of the first four-way reversing valve 301 and the second four-way reversing valve 302 are collectively communicated with the exhaust port 101 of the compressor 100, a C port of the first four-way reversing valve 301 is communicated with one end of the outdoor heat exchanger 203 away from the first throttling element 400, a sum of E port and S port of the first four-way reversing valve 301 and a C port of the second four-way reversing valve 302 is communicated with one end of the indoor windward heat exchanger 201 away from the first throttling element 400 and communicated with the first suction port 102 of the high-pressure compression part, a one-way valve 3021 is arranged on a connection branch of the C port of the second four-way reversing valve 302, the one-way valve 3021 allows a refrigerant to flow into the C port to be reversely stopped, the S port of the second four-way reversing valve 302 is communicated with the second air suction port 103 of the low-pressure compression part, the E port of the second four-way reversing valve 302 is communicated with one end, far away from the first throttling element 400, of the indoor leeward side heat exchanger 202, the inlet of the flash device 500 is connected with one end, far away from the outdoor heat exchanger 203, of the first throttling element 400, the air supply outlet of the flash device 500 is communicated with the main air supply port 31 of the pump body assembly, one outlet of the flash device 500 is communicated with one end, close to the first throttling element 400, of the indoor windward side heat exchanger 201, and the other outlet of the flash device 500 is communicated with one end, close to the first throttling element 400, of the indoor leeward side heat exchanger 202. In the technical scheme, by optimally designing the pipe orifices of the two four-way pipes and the check valve 3021, the pipeline design is simplified and the system construction cost is reduced (only one check valve is used) while the switching requirements of the heating mode, the refrigerating mode and the reheating and dehumidifying mode of the dual-temperature air conditioning system are met.
Regarding the operation process of the dual-temperature air conditioning system, the following detailed description is made in combination with the dual-suction dual-air-supply single-exhaust quasi-secondary compressor, and the operation process of the dual-temperature air conditioning system applied to the dual-suction dual-air-supply single-exhaust quasi-secondary compressor is basically the same, and is not repeated herein:
when the air conditioner operates in the cooling mode, as shown in fig. 6, the first four-way selector valve 301 and the second four-way selector valve 302 are de-energized and in the first conduction state, the tube E is conducted with the tube S, and the tube C is conducted with the tube D. After the high-temperature and high-pressure exhaust gas of the compressor 100 is discharged, the exhaust gas flows through the D pipe and the C pipe of the second four-way reversing valve 302 and enters the outdoor heat exchanger 203, condensation and heat release are performed in the outdoor heat exchanger 203, then the exhaust gas is throttled and reduced in pressure by the first throttling element 400 (electronic expansion valve) and enters the flash evaporator 500, the throttled medium-pressure refrigerant flashes in the flash evaporator 500, and the gaseous refrigerant enters the first cylinder 11 and the second cylinder 21 through the main gas supplementing port 31; the liquid refrigerant is divided into two paths: one path of refrigerant enters the indoor leeward side heat exchanger 202 for evaporation and heat absorption after being throttled and depressurized by the third throttling element 402, the evaporated and heat-absorbed gaseous refrigerant enters the second cylinder 21 through the E pipe and the S pipe of the second four-way reversing valve 302, and after being compressed to the intermediate pressure in the second cylinder 21, the medium-pressure refrigerant entering from the second air supplementing port 23 is mixed and then is continuously compressed to the high-temperature and high-pressure refrigerant in the second cylinder 21; the other path of the refrigerant is throttled and depressurized by the second throttling element 401, enters the indoor windward side heat exchanger 201 for evaporation and heat absorption, the evaporated and heat-absorbed gaseous refrigerant enters the first cylinder 11 of the compressor through the tube E and the tube S of the first four-way reversing valve 301, and the medium-pressure refrigerant entering the first cylinder 11 from the first air supplementing port 13 is mixed and then continuously compressed to the high-temperature and high-pressure refrigerant after being compressed to the intermediate pressure. The high-temperature and high-pressure refrigerant passing through the second cylinder 21 and the first cylinder 11 is discharged together, completing the cycle.
When the heating mode is operated, as shown in fig. 7, the first four-way reversing valve 301 and the second four-way reversing valve 302 are energized and are both in the second conduction state, the D pipe is communicated with the E pipe, and the S pipe is communicated with the C pipe; after the high-temperature and high-pressure exhaust gas of the compressor 100 is discharged, the high-temperature and high-pressure exhaust gas is divided into two paths, one path of the high-temperature and high-pressure exhaust gas flows through the tube D and the tube E of the second four-way reversing valve 302, enters the indoor leeward side heat exchanger 202 to be condensed and release heat, and the condensed high-pressure liquid refrigerant is throttled and depressurized by the third throttling element 402; the other path of the refrigerant passes through a tube D and a tube E of the first four-way reversing valve 301 and enters the indoor windward side heat exchanger 201 to be condensed and release heat, and the condensed high-pressure liquid refrigerant is throttled and depressurized through a second throttling element 401. The two paths of throttled and depressurized refrigerants are converged to enter the flash tank 500 for flash, and a medium-pressure gaseous refrigerant main air supplement port 31 in the flash tank 500 enters the first cylinder 11 and the second cylinder 21; the liquid refrigerant is throttled and depressurized by the first throttling element 400 and then enters the outdoor heat exchanger 203 to evaporate and absorb heat. The gaseous refrigerant after evaporation and heat absorption is divided into two paths: one path of refrigerant enters the first cylinder 11 through a pipe C and a pipe S of the first four-way reversing valve 301 and is compressed to medium-pressure refrigerant, and then the refrigerant is mixed with the medium-pressure refrigerant entering through the first air supplementing port 13 and is continuously compressed to high-temperature and high-pressure refrigerant in the first cylinder 11; the other path of the refrigerant enters the second cylinder 21 through the check valve 3021 and the C pipe and the S pipe of the second four-way reversing valve 302 and is compressed to the medium-pressure refrigerant, and then the refrigerant is mixed with the medium-pressure refrigerant entering through the second air supplement port 23 and is continuously compressed to the high-temperature and high-pressure refrigerant in the second cylinder 21. The high-temperature and high-pressure refrigerant compressed in the second cylinder 21 and the first cylinder 11 is discharged together, completing the cycle.
When the reheating and dehumidifying mode is operated, as shown in fig. 8, the second four-way reversing valve 302 is energized, the pipe D is communicated with the pipe E, and the pipe C is communicated with the pipe S; the first four-way reversing valve 301 is powered off, the tube D is communicated with the tube C, and the tube E is communicated with the tube S; after the high-temperature and high-pressure exhaust gas of the compressor 100 is discharged, the exhaust gas is divided into two paths, one path of the exhaust gas flows through a D tube and an E tube of the second four-way reversing valve 302 and enters the indoor leeward side heat exchanger 202 for condensation and heat release, and the condensed high-pressure liquid refrigerant is throttled and depressurized by a third throttling element 402; the other path of the refrigerant passes through a tube D and a tube C of the first four-way reversing valve 301, enters the outdoor heat exchanger 203 for condensation and heat release, and the condensed high-pressure liquid refrigerant enters the flash tank 500 for flash evaporation after being throttled and depressurized by the first throttling element 400. The gaseous refrigerant in the flash tank 500 enters the first cylinder 11 and the second cylinder 21 through the main air supplementing port 31; the liquid refrigerant is merged with the refrigerant throttled and depressurized by the third throttling element 402, throttled and depressurized by the second throttling element 401, and then enters the indoor windward side heat exchanger 201 to evaporate and absorb heat. The evaporated and heat-absorbed gaseous refrigerant is divided into two paths: one path of refrigerant enters the first cylinder 11 through an E pipe and an S pipe of the first four-way reversing valve 301 to be compressed, and is further compressed to high-temperature and high-pressure refrigerant in the first cylinder 11 after being mixed with medium-pressure refrigerant entering the first air supplementing port 13 after being compressed to medium pressure; the other path of the refrigerant enters the second cylinder 21 through the check valve 3021 to be compressed, and the compressed refrigerant is mixed with the medium-pressure refrigerant entering through the second air supplement port 23 and further compressed to high-temperature and high-pressure refrigerant in the second cylinder 21. The high-temperature and high-pressure gaseous refrigerant compressed in the second cylinder 21 and the first cylinder 11 is discharged together, completing the cycle.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The present invention is not limited to the above preferred embodiments, and any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention. The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the technical principle of the present invention, and these improvements and modifications should also be regarded as the protection scope of the present invention.
Claims (10)
1. A pump body assembly comprises a high-pressure compression part and a low-pressure compression part, wherein the high-pressure compression part comprises a first air cylinder (11) and a first sliding sheet (12) correspondingly arranged with the first air cylinder, the low-pressure compression part comprises a second air cylinder (21) and a second sliding sheet (22) correspondingly arranged with the second air cylinder, and the pump body assembly is characterized in that the high-pressure compression part is provided with a first air supplement port (13), the low-pressure compression part is provided with a second air supplement port (23) and is projected on a radial surface of the pump body assembly, the first sliding sheet (12) is superposed with the second sliding sheet (22), a first central included angle beta based on the center of the first air cylinder (11) is arranged between the air supplement central line of the first air supplement port (13) and the symmetrical central line of the first sliding sheet (12), a second central included angle alpha based on the center of the second air cylinder (21) is arranged between the air supplement central line of the second air supplement port (23) and the symmetrical central line of the second sliding sheet (22), alpha > beta.
2. The pump body assembly of claim 1, wherein β is 56 ° or more and 238 ° or less; and/or alpha is more than or equal to 63 degrees and less than or equal to 273 degrees.
3. The pump body assembly according to claim 1, wherein when the pump body assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system operates in a cooling mode, the first cylinder (11) is connected in series with an indoor windward side heat exchanger (201), the second cylinder (21) is connected in series with an indoor leeward side heat exchanger (202), the volume ratio of the first cylinder (11) to the second cylinder (21) is a, the duty ratio of the indoor windward side heat exchanger (201) to the indoor leeward side heat exchanger (202) is b, and a/b is greater than or equal to 0.7 and less than or equal to 1.1.
4. The pump body assembly of claim 3, wherein a is 0.9 ≦ 1.3; and/or b is more than or equal to 0.72 and less than or equal to 1.04; and/or, a/b is 0.8.
5. The pump body assembly according to claim 1, characterized in that a middle partition plate (3) is sandwiched between the first cylinder (11) and the second cylinder (21), the first air supplement port (13) and the second air supplement port (23) are respectively arranged on two opposite end surfaces of the middle partition plate (3), an air supplement channel communicated with the first air supplement port (13) and the second air supplement port (23) is constructed in the middle partition plate (3), and the air supplement channel is provided with a main air supplement port (31) connected with an external air supplement pipeline.
6. A pump body assembly, comprising a high-pressure compression part and a low-pressure compression part, wherein the high-pressure compression part comprises a first cylinder (11) and a first sliding vane (12) arranged corresponding to the first cylinder, the low-pressure compression part comprises a second cylinder (21) and a second sliding vane (22) arranged corresponding to the second cylinder, and the pump body assembly is characterized in that one of the high-pressure compression part and the low-pressure compression part is provided with an air supplementing port, the projection is performed on a radial surface of the pump body assembly, the first sliding vane (12) and the second sliding vane (22) are overlapped, when the high-pressure compression part is provided with the air supplementing port, a first center included angle β based on the center of the first cylinder (11) is formed between the air supplementing center line of the air supplementing port and the symmetric center line of the first sliding vane (12), and β is greater than or equal to 56 ° and less than or equal to 144 °; or when the low-pressure compression part is provided with the air supplementing port, a second center included angle alpha based on the center of the second cylinder (21) is formed between the air supplementing center line of the air supplementing port and the symmetrical center line of the second slide sheet (22), and the angle alpha is more than or equal to 63 degrees and less than or equal to 166 degrees.
7. The pump block assembly according to claim 6, characterized in that a middle partition (3) is interposed between the first cylinder (11) and the second cylinder (21), the air supplement port is arranged on one end face of the middle partition (3), an air supplement channel communicated with the air supplement port is constructed in the middle partition (3), and the air supplement channel is provided with a main air supplement port (31) connected with an external air supplement pipeline.
8. A compressor, characterized by comprising a pump body assembly according to any one of claims 1 to 7.
9. A dual temperature air conditioning system, characterized in that it comprises a compressor (100), said compressor (100) being a compressor according to claim 8.
10. The dual temperature air conditioning system according to claim 9, further comprising a first four-way reversing valve (301), a second four-way reversing valve (302), an indoor windward side heat exchanger (201), an indoor leeward side heat exchanger (202), an outdoor heat exchanger (203), and a first throttling element (400), wherein the first four-way reversing valve (301) and the second four-way reversing valve (302) have respective D ports that collectively communicate with the air outlet (101) of the compressor (100), the C port of the first four-way reversing valve (301) communicates with the end of the outdoor heat exchanger (203) away from the first throttling element (400), the E port and the S port of the first four-way reversing valve (301) and the C port of the second four-way reversing valve (302) collectively communicate with the end of the indoor windward side heat exchanger (201) away from the first throttling element (400) and communicate with the first air inlet (102) of the high pressure compression section, a one-way valve (3021) is arranged on a connection branch of a port C of the second four-way reversing valve (302), the one-way valve (3021) allows a refrigerant to flow into the port C and is cut off in a reverse direction, a port S of the second four-way reversing valve (302) is communicated with a second air suction port (103) of the low-pressure compression part, and a port E of the second four-way reversing valve (302) is communicated with one end, far away from the first throttling element (400), of the indoor leeward side heat exchanger (202).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210842633.1A CN115030900A (en) | 2022-07-18 | 2022-07-18 | Pump body subassembly, compressor, two temperature air conditioning system |
| PCT/CN2023/087846 WO2024016748A1 (en) | 2022-07-18 | 2023-04-12 | Pump body assembly, compressor and double-temperature air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210842633.1A CN115030900A (en) | 2022-07-18 | 2022-07-18 | Pump body subassembly, compressor, two temperature air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115030900A true CN115030900A (en) | 2022-09-09 |
Family
ID=83128010
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210842633.1A Pending CN115030900A (en) | 2022-07-18 | 2022-07-18 | Pump body subassembly, compressor, two temperature air conditioning system |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN115030900A (en) |
| WO (1) | WO2024016748A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024016748A1 (en) * | 2022-07-18 | 2024-01-25 | 珠海格力电器股份有限公司 | Pump body assembly, compressor and double-temperature air conditioning system |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6331786B2 (en) * | 2014-07-08 | 2018-05-30 | 株式会社富士通ゼネラル | Compressor |
| CN207195203U (en) * | 2017-09-04 | 2018-04-06 | 珠海凌达压缩机有限公司 | The gas supplementary structure of compressor and there is its compressor |
| CN110792602A (en) * | 2019-11-29 | 2020-02-14 | 珠海凌达压缩机有限公司 | Injection needle assembly, air supplementing structure and compressor |
| CN114046248A (en) * | 2021-12-15 | 2022-02-15 | 珠海格力电器股份有限公司 | Pump body structure, compressor and air conditioning system |
| CN115030900A (en) * | 2022-07-18 | 2022-09-09 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor, two temperature air conditioning system |
| CN217813968U (en) * | 2022-07-18 | 2022-11-15 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor, two temperature air conditioning system |
-
2022
- 2022-07-18 CN CN202210842633.1A patent/CN115030900A/en active Pending
-
2023
- 2023-04-12 WO PCT/CN2023/087846 patent/WO2024016748A1/en unknown
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024016748A1 (en) * | 2022-07-18 | 2024-01-25 | 珠海格力电器股份有限公司 | Pump body assembly, compressor and double-temperature air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2024016748A1 (en) | 2024-01-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111780254A (en) | Air conditioning system and control method thereof | |
| CN107576085B (en) | Refrigerating system | |
| CN101691960B (en) | Three-pipe heating and reclaiming air-conditioning system | |
| CN111765568A (en) | Air conditioning system and control method thereof | |
| CN102506520B (en) | Refrigeration equipment of air conditioner | |
| CN105444453A (en) | Double-temperature refrigerating and heating system | |
| CN107576090B (en) | Refrigerating system | |
| CN203464560U (en) | Air conditioning refrigeration equipment | |
| CN107560210B (en) | Refrigerating system | |
| CN111765567A (en) | Air conditioning system and control method thereof | |
| CN217813968U (en) | Pump body subassembly, compressor, two temperature air conditioning system | |
| WO2024016748A1 (en) | Pump body assembly, compressor and double-temperature air conditioning system | |
| CN100342189C (en) | Three-pressure air conditioning apparatus with refrigerating, pyrogenicity and water heating | |
| CN205373127U (en) | Two temperature refrigeration and heating | |
| CN216742004U (en) | Compressor and air conditioning system | |
| WO2020143169A1 (en) | Air conditioning system and control method therefor | |
| CN101487643A (en) | Ultra-low temperature heat pump air conditioning system | |
| CN213090173U (en) | Air conditioning system | |
| CN114046248A (en) | Pump body structure, compressor and air conditioning system | |
| CN114484623A (en) | Temperature-adjusting dehumidifying air-conditioning system and control method thereof | |
| CN215638112U (en) | Refrigerating system | |
| CN212339674U (en) | Air conditioning system | |
| CN114608075A (en) | Temperature-adjusting dehumidifying air-conditioning system and control method thereof | |
| CN113187727B (en) | Single-stage compression mechanism, rotor compressor and air conditioning device | |
| US11300329B2 (en) | Two-pipe enhanced-vapor-injection outdoor unit and multi-split system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |