An enthalpy-increasing double-cylinder compressor, double-evaporation enthalpy-increasing refrigerating system and air conditioner

Abstract

This invention provides an enthalpy-increasing dual-cylinder compressor, a dual-evaporation enthalpy-increasing refrigeration system, and an air conditioner. The enthalpy-increasing dual-cylinder compressor includes: a first cylinder, a second cylinder, a low-pressure intake pipe, a medium-pressure intake pipe, a make-up gas pipe, and an exhaust chamber. One end of the medium-pressure intake pipe is connected to an external medium-pressure intake, and the other end can be connected to the second cylinder. One end of the make-up gas pipe is connected to an external medium-pressure make-up gas, and the other end can be connected to the second cylinder. The pressure of the medium-pressure intake is greater than the pressure of the low-pressure intake, and the pressure of the medium-pressure make-up gas is greater than the pressure of the low-pressure intake. The exhaust gas from the first cylinder enters the exhaust chamber, and the exhaust gas from the second cylinder also enters the exhaust chamber, so that the exhaust gas from the first cylinder and the exhaust gas from the second cylinder mix before being discharged from the compressor. Compared with conventional single-stage or two-stage throttling two-stage compression or quasi-two-stage compression refrigeration cycle systems, this invention can effectively improve refrigeration energy efficiency.

Description

Technical Field

[0001] This invention relates to the field of refrigeration technology, specifically to an enthalpy-increasing dual-cylinder compressor, a dual-evaporation enthalpy-increasing refrigeration system, and an air conditioner. Background Technology

[0002] Energy conservation and emission reduction are core tasks of the global energy industry. For the energy-intensive air conditioning industry, the demand for highly efficient and energy-saving products is urgent. Patent document CN105115181B proposes a dual-evaporation temperature system, in which two high- and low-temperature evaporators are arranged in a heat exchange channel. Indoor return air passes through both evaporators for heat exchange. Simultaneously, the outlets of the two evaporators are connected to two independent compression cylinders of the compressor, ensuring that the evaporation temperature of the high-temperature evaporator is higher than that of a conventional system, thus improving system energy efficiency to some extent. However, the improvement is relatively small and further performance improvements are needed. Patent document CN210290144U proposes a three-cylinder, two-stage variable-capacity compressor for the dual-evaporation temperature system; however, the complexity of the three-cylinder compressor and its high application cost are significant factors.

[0003] Due to the difficulty in optimizing the efficiency of existing single-stage compression cycle refrigeration systems and the difficulty in optimizing the efficiency of conventional two-stage throttling two-stage compression or quasi-two-stage compression refrigeration cycles, this invention studies and designs an enthalpy-increasing dual-cylinder compressor, a dual-evaporation enthalpy-increasing refrigeration system, and an air conditioner. Summary of the Invention

[0004] Therefore, the technical problem to be solved by the present invention is to overcome the shortcomings of insufficient refrigeration efficiency and high difficulty in improving the refrigeration efficiency of existing single-stage compression cycle refrigeration systems and two-stage throttling two-stage compression or quasi-two-stage compression refrigeration cycle systems, thereby providing an enthalpy-increasing dual-cylinder compressor, a dual-evaporation enthalpy-increasing refrigeration system and an air conditioner.

[0005] To address the above problems, the present invention provides an enthalpy-increasing dual-cylinder compressor, comprising:

[0006] The system comprises a first cylinder, a second cylinder, a low-pressure intake pipe, a medium-pressure intake pipe, a make-up air pipe, and an exhaust chamber. One end of the low-pressure intake pipe is connected to an external low-pressure intake, and the other end is connected to the first cylinder to introduce low-pressure intake air into the first cylinder. One end of the medium-pressure intake pipe is connected to an external medium-pressure intake, and the other end is connected to the second cylinder to introduce medium-pressure intake air into the second cylinder. One end of the make-up air pipe is connected to an external medium-pressure make-up air, and the other end is connected to the second cylinder to introduce medium-pressure make-up air into the second cylinder. The pressure of the medium-pressure intake air is greater than the pressure of the low-pressure intake air, and the pressure of the medium-pressure make-up air is greater than the pressure of the low-pressure intake air. The exhaust from the first cylinder enters the exhaust chamber, and the exhaust from the second cylinder also enters the exhaust chamber, so that the exhaust from the first cylinder and the exhaust from the second cylinder are mixed and discharged from the compressor.

[0007] In some embodiments, the system further includes a first flange, a second flange, and a partition assembly. The first flange is disposed on the end face of the first cylinder away from the second cylinder. The partition assembly is disposed between the first cylinder and the second cylinder. The second flange is disposed on the end face of the second cylinder away from the first cylinder. The low-pressure intake pipe is directly connected to the first cylinder. The medium-pressure intake pipe is directly connected to the second cylinder or connected to the second cylinder through the partition assembly. The air supply pipe is directly connected to the second cylinder or connected to the second cylinder through the partition assembly.

[0008] In some embodiments, the partition assembly is provided with an air intake chamber, and the air supply pipe is connected to the air intake chamber to supply air to the air intake chamber. One end of the air intake chamber is connected to the air supply pipe, and the other end is connected to the interior of the second cylinder. The medium-pressure air intake pipe is directly connected to the second cylinder. Alternatively, the partition assembly is provided with an air intake chamber, and the medium-pressure air intake pipe is connected to the air intake chamber to supply air to the air intake chamber. One end of the air intake chamber is connected to the medium-pressure air intake pipe, and the other end is connected to the interior of the second cylinder. The air supply pipe is directly connected to the second cylinder.

[0009] In some embodiments, the medium-pressure intake line is directly connected to the second cylinder, and the air supply line is directly connected to the second cylinder.

[0010] In some embodiments, a first muffler and a second muffler are also included. The first muffler is disposed on the end face of the first flange away from the first cylinder and forms a medium-pressure chamber with the first flange. One end of the medium-pressure chamber is connected to the exhaust of the first cylinder, and the other end of the medium-pressure chamber is connected to the exhaust chamber.

[0011] The second muffler is disposed on the end face of the second flange away from the second cylinder, and forms the exhaust chamber between the muffler and the second flange.

[0012] In some embodiments, the second cylinder is provided with an intake channel and a replenishment channel. One end of the intake channel can be connected to the medium-pressure intake pipeline and the other end can be connected to the compression chamber of the second cylinder. One end of the replenishment channel can be connected to the replenishment pipeline and the other end can be connected to the compression chamber of the second cylinder through the intake channel or directly to the compression chamber of the second cylinder.

[0013] In some embodiments, when the other end of the air replenishment channel is connected to the compression chamber of the second cylinder through the air intake channel, the air replenishment channel and the air intake channel are connected by a connecting channel, which is located on the second cylinder; when the other end of the air replenishment channel is directly connected to the compression chamber of the second cylinder, the air replenishment channel and the air intake channel are not connected.

[0014] The present invention also provides a dual-evaporation enthalpy-increasing refrigeration system, which includes the aforementioned enthalpy-increasing dual-cylinder compressor, and further includes: a condenser, a high-pressure evaporator, a low-pressure evaporator, a first-stage throttling device, a second-stage throttling device, and a flash evaporator. The condenser is connected to the exhaust end of the enthalpy-increasing dual-cylinder compressor, the first-stage throttling device is connected between the inlet ends of the condenser and the flash evaporator, the gas outlet of the flash evaporator is connected to the second cylinder, the high-pressure evaporator is connected between the liquid outlet of the flash evaporator and the second cylinder, the low-pressure evaporator and the second-stage throttling device are connected between the liquid outlet of the flash evaporator and the first cylinder, and the evaporation pressure of the refrigerant in the high-pressure evaporator is higher than the evaporation pressure of the low-pressure evaporator.

[0015] In some embodiments, the system further includes a first pipeline, a second pipeline, and a third pipeline. One end of the first pipeline is connected to the exhaust end of the enthalpy-increasing dual-cylinder compressor, and the other end is connected to one end of the first-stage throttling device. The condenser is disposed on the first pipeline. One end of the second pipeline is connected to the other end of the first-stage throttling device, and the other end of the second pipeline is connected to the inlet end of the flash evaporator. One end of the make-up gas pipeline is connected to the gas outlet of the flash evaporator, and the other end is connected to the second cylinder. One end of the third pipeline is connected to the liquid outlet of the flash evaporator, and the other end is connected to one end of the second-stage throttling device. One end of the medium-pressure intake pipeline is connected to the third pipeline, and the other end is connected to the second cylinder. The high-pressure evaporator is disposed on the medium-pressure intake pipeline. One end of the low-pressure intake pipeline is connected to the other end of the second-stage throttling device, and the other end of the low-pressure intake pipeline is connected to the first cylinder. The low-pressure evaporator is disposed on the low-pressure intake pipeline.

[0016] In some embodiments, the exhaust pressure Q1 of the second cylinder, the pressure Q2 of the air supply line, the exhaust pressure Q3 of the first cylinder, the displacement V1 of the second cylinder, the displacement V2 of the first cylinder, the flash coefficient is K, and the following are also included:

[0017]

[0018] In some implementations, the flash coefficient K = 0.65 to 0.9.

[0019] The present invention also provides an air conditioner comprising the aforementioned dual-evaporation enthalpy-increasing refrigeration system.

[0020] The enthalpy-increasing dual-cylinder compressor, dual-evaporation enthalpy-increasing refrigeration system, and air conditioner provided by this invention have the following beneficial effects:

[0021] This invention, by configuring a dual-cylinder compressor including first and second cylinders, and low-pressure and medium-pressure intake pipes, allows for air intake to the first cylinder via a low-pressure intake pipe, and air intake to the second cylinder via a medium-pressure intake pipe. A make-up air pipe also connects to the second cylinder for air intake. Furthermore, the exhaust gas from both the first and second cylinders is mixed within the exhaust chamber. Compared to conventional dual-temperature systems with two-stage compressors, this invention reduces the introduction of exhaust gas from the first cylinder into the second cylinder for secondary compression, thus reducing the compression power consumption of the second cylinder. Additionally, the mixing of exhaust gas from the first and second cylinders reduces the compressor's exhaust pressure compared to a two-stage compressor, thereby lowering the overall compression power consumption. This is also evident in the pressure-enthalpy diagram, which effectively reduces the overall compression power consumption of both the first and second cylinders. Furthermore, this invention achieves dual-temperature evaporation, dual-cylinder compression, and enthalpy enhancement through a dual-cylinder compressor, eliminating the need for a three-cylinder configuration. This effectively reduces the number of cylinders, simplifies the structure, saves costs, increases space utilization, and allows for a smaller compressor size. 2. This invention achieves a two-stage throttling refrigeration cycle with dual evaporation temperatures through independent compression by two cylinders. Compared to conventional single-stage compression refrigeration systems, by connecting the two cylinders to the low-pressure and medium-pressure intake pipes respectively, it achieves the evaporation effect of a dual-temperature evaporator, increasing cooling capacity and improving refrigeration efficiency (energy efficiency). Compared to conventional two-stage throttling dual-compression or quasi-two-stage compression refrigeration cycle systems, it effectively reduces compression power consumption and improves refrigeration energy efficiency. In summary, this invention effectively increases refrigeration efficiency (energy efficiency) compared to various existing solutions, achieving a significant improvement in the energy efficiency of the refrigeration system. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the dual-evaporation enthalpy-increasing refrigeration system of the present invention;

[0023] Figure 2 This is a schematic diagram of the internal structure of the enthalpy-increasing dual-cylinder compressor of the present invention;

[0024] Figure 3 This is a structural diagram of the second cylinder (intermediate pressure cylinder) of the present invention for mixed compression (i.e., having a connecting channel);

[0025] Figure 4 This is a structural diagram of the non-mixed compression of the second cylinder (intermediate pressure cylinder) of the present invention (i.e., without a connecting channel);

[0026] Figure 5 This is a schematic diagram of the internal structure of the enthalpy-increasing dual-cylinder compressor in an alternative embodiment of the present invention;

[0027] Figure 6 This is a graph showing the improvement in EER of the refrigeration cycle of the present invention compared to a conventional single-stage cycle;

[0028] Figure 7 This is the pressure-enthalpy diagram of the operation process of a two-stage, two-temperature refrigeration system in the prior art;

[0029] Figure 8 This is the pressure-enthalpy diagram of the operating process of the dual-evaporation enthalpy-increasing refrigeration system of the present invention.

[0030] The reference numerals in the attached figures are as follows:

[0031] 1. First cylinder; 2. Second cylinder; 3. Low-pressure intake pipe; 4. Medium-pressure intake pipe; 5. Make-up air pipe; 6. Exhaust chamber; 7. First flange; 8. Second flange; 9. Baffle assembly; 10. Medium-pressure chamber; 11. Intake chamber; 12. Intake passage; 13. Make-up air passage; 14. Connecting passage; 15. Condenser; 16. High-pressure evaporator; 17. Low-pressure evaporator; 18. First-stage throttling device; 19. Second-stage throttling device; 20. Flash evaporator; 21. Enthalpy-increasing twin-cylinder compressor; 22. Motor; 23. Crankshaft; 24. Make-up air assembly; 25. First muffler; 26. Second muffler; 101. First pipe; 102. Second pipe; 103. Third pipe. Detailed Implementation

[0032] like Figure 1-8 As shown, the present invention provides an enthalpy-increasing dual-cylinder compressor, which includes:

[0033] The system comprises a first cylinder 1, a second cylinder 2, a low-pressure intake pipe 3, a medium-pressure intake pipe 4, a make-up air pipe 5, and an exhaust chamber 6. One end of the low-pressure intake pipe 3 is connected to an external low-pressure intake, and the other end is connected to the first cylinder 1 to introduce low-pressure intake air into the first cylinder 1. One end of the medium-pressure intake pipe 4 is connected to an external medium-pressure intake, and the other end is connected to the second cylinder 2 to introduce medium-pressure intake air into the second cylinder 2. One end of the make-up air pipe 5 is connected to an external medium-pressure make-up air, and the other end is connected to the second cylinder 2 to introduce medium-pressure make-up air into the second cylinder 2. The pressure of the medium-pressure intake air is greater than the pressure of the low-pressure intake air, and the pressure of the medium-pressure make-up air is greater than the pressure of the low-pressure intake air. The exhaust from the first cylinder 1 enters the exhaust chamber 6, and the exhaust from the second cylinder 2 also enters the exhaust chamber 6, so that the exhaust from the first cylinder 1 and the exhaust from the second cylinder 2 are mixed and discharged from the compressor.

[0034] This invention, by setting up a dual-cylinder compressor including first and second cylinders, and low-pressure and medium-pressure intake pipes, enables air intake into the first cylinder through the low-pressure intake pipe, and air intake into the second cylinder through the medium-pressure intake pipe. A make-up air pipe is also connected to the second cylinder for air intake. Furthermore, by setting up an exhaust chamber, the exhaust from both the first and second cylinders is introduced into the exhaust chamber for mixing. 1. Compared to conventional dual-temperature systems with two-stage compressors, this invention reduces the introduction of exhaust from the first cylinder into the second cylinder for secondary compression, thus reducing the compression power consumption of the second cylinder. Furthermore, due to the mixing of exhaust from the first and second cylinders, the exhaust pressure of the compressor is reduced compared to a two-stage compressor, thereby lowering the overall compression power consumption. (In the pressure-enthalpy diagram...) Figure 8 This can also be seen from the fact that it effectively reduces the overall compression power consumption of the first and second cylinders (relative to...). Figure 7 2. Furthermore, this invention achieves dual-temperature evaporation, dual-cylinder compression, and enthalpy enhancement through a dual-cylinder compressor, eliminating the need for a three-cylinder configuration. This effectively reduces the number of cylinders, simplifies the structure, saves costs, increases space utilization, and allows for a smaller compressor size. 3. This invention achieves a two-stage throttling refrigeration cycle with dual evaporation temperatures through independent compression by two cylinders. Compared to conventional single-stage compression refrigeration systems, this invention achieves dual-temperature evaporation by connecting the two cylinders to the low-pressure and medium-pressure intake pipes, thereby increasing cooling capacity and refrigeration efficiency (energy efficiency). Compared to conventional two-stage throttling dual-compression or quasi-two-stage compression refrigeration cycle systems, this invention effectively reduces compression power consumption and improves refrigeration energy efficiency. In summary, this invention effectively increases refrigeration efficiency (energy efficiency) compared to various existing solutions, resulting in a significant improvement in the energy efficiency of the refrigeration system.

[0035] This invention ingeniously combines a twin-cylinder compressor, twin evaporators, and a two-stage throttling refrigeration cycle without increasing the cost of the refrigeration system, achieving a significant improvement in refrigeration efficiency. (See attached image) Figure 6 The following technical problems were solved: 1. Optimizing the efficiency of traditional dual-evaporation temperature systems is difficult. 2. Optimizing conventional three-cylinder two-stage variable-capacity compressors is costly, and their application is currently difficult and limited.

[0036] This invention provides a compressor for use with a dual-evaporation enthalpy-increasing system. The dual-evaporation enthalpy-increasing compressor includes three gas-liquid separators, a crankshaft, a muffler, an intermediate-pressure cylinder consisting of an upper cylinder, upper rollers, upper vanes, and an upper flange, and a low-pressure cylinder consisting of a lower cylinder, lower rollers, lower vanes, and a lower flange. A partition assembly separates the intermediate-pressure cylinder and the low-pressure cylinder.

[0037] In some embodiments, the system further includes a first flange 7, a second flange 8, and a partition assembly 9. The first flange 7 is disposed on the end face of the first cylinder 1 away from the second cylinder 2. The partition assembly 9 is disposed between the first cylinder 1 and the second cylinder 2. The second flange 8 is disposed on the end face of the second cylinder 2 away from the first cylinder 1. The low-pressure intake pipe 3 is directly connected to the first cylinder 1. The medium-pressure intake pipe 4 is directly connected to the second cylinder 2 or connected to the second cylinder 2 through the partition assembly 9. The air supply pipe 5 is directly connected to the second cylinder 2 or connected to the second cylinder 2 through the partition assembly 9.

[0038] This is a preferred structural form of the enthalpy-increasing dual-cylinder compressor of the present invention. The first flange and partition assembly can form a sealing effect on the first cylinder, and the second flange and partition assembly can form a sealing effect on the second cylinder. The low-pressure intake pipe is connected to the first cylinder to directly introduce low-pressure gas into the first cylinder for compression. The medium-pressure intake pipe can be directly or indirectly connected to the second cylinder to enter the second cylinder for compression. The make-up gas pipe can also be directly or indirectly connected to the second cylinder. The make-up gas and the medium-pressure intake gas are compressed together by the rollers in the second cylinder. This achieves that the same cylinder can both introduce refrigerant evaporated in the dual-temperature evaporator for compression and perform make-up gas to increase enthalpy. This saves compression power consumption, improves refrigeration energy efficiency, and completes dual-temperature evaporation, thereby improving refrigeration efficiency.

[0039] Main embodiment, such as Figure 2In some embodiments, the partition assembly 9 is provided with an air intake chamber 11, and the air supply pipe 5 is connected to the air intake chamber 11 to supply air to the air intake chamber 11. One end of the air intake chamber 11 is connected to the air supply pipe 5, and the other end is connected to the interior of the second cylinder 2. The medium-pressure air intake pipe 4 is directly connected to the second cylinder 2. Alternatively, the partition assembly 9 is provided with an air intake chamber 11, and the medium-pressure air intake pipe 4 is connected to the air intake chamber 11 to supply air to the air intake chamber 11. One end of the air intake chamber 11 is connected to the medium-pressure air intake pipe 4, and the other end is connected to the interior of the second cylinder 2. The air supply pipe 5 is directly connected to the second cylinder 2.

[0040] This is a preferred structural form of the partition assembly of the present invention. Through the air inlet chamber provided thereon, one of the medium-pressure air inlet pipe and the gas replenishment pipe can directly enter the second cylinder for compression, while the other enters the air inlet chamber first for buffering and then enters the second cylinder for compression. Through the buffering effect of the air inlet chamber, the pressure fluctuation caused by gas mixing can be reduced, making the refrigerant pressure in the flash evaporation path (i.e., gas replenishment pipe 5) more stable and enhancing the gas replenishment effect.

[0041] Alternative embodiments, such as Figure 5 In some embodiments, the medium-pressure intake pipe 4 is directly connected to the second cylinder 2, and the air supply pipe 5 is directly connected to the second cylinder 2. This is a preferred connection method for the medium-pressure intake pipe and the air supply pipe in an alternative embodiment of the present invention, i.e., there is no structure with an intake chamber on the partition assembly, and the flash evaporation path (air supply pipe 5) is directly connected to the second cylinder (medium-pressure cylinder). Compared with the main embodiment, the structure is simpler, the cost is lower, the space occupied is saved, and the structure is more compact.

[0042] In some embodiments, a first muffler 25 and a second muffler 26 are also included. The first muffler 25 is disposed on the end face of the first flange 7 away from the first cylinder 1 and forms a medium-pressure chamber 10 between it and the first flange 7. One end of the medium-pressure chamber 10 is connected to the exhaust of the first cylinder 1, and the other end of the medium-pressure chamber 10 can be connected to the exhaust chamber 6.

[0043] The second muffler 26 is disposed on the end face of the second flange 8 away from the second cylinder 2, and forms the exhaust chamber 6 between the muffler 2 and the second flange 8.

[0044] This invention describes the exhaust connection method of the low-pressure cylinder (first cylinder) and the formation method of the exhaust chamber. Specifically, a first silencer is installed on the side of the first flange away from the first cylinder, forming a medium-pressure chamber between the first silencer and the first flange. This effectively buffers the exhaust from the first cylinder and guides the buffered gas into the exhaust chamber, where it mixes with the gas discharged from the second cylinder. Compared to existing dual-temperature, two-stage refrigeration systems, this effectively reduces compressor power consumption and improves the energy efficiency of the refrigeration system. Preferably, the exhaust chamber of this invention is formed between the second silencer and the second flange, allowing for the mixing of the low-pressure exhaust from the first cylinder and the high-pressure exhaust from the second cylinder. This reduces the compressor's exhaust pressure and output power, thereby effectively improving refrigeration efficiency. Furthermore, mixing the exhaust from both cylinders in this exhaust chamber buffers and silences the compressor exhaust, reducing pressure fluctuations and noise, effectively forming a quasi-two-stage compression. This significantly improves refrigeration efficiency compared to both single-stage and dual-temperature, two-stage compression.

[0045] like Figure 3-4 In some embodiments, the second cylinder 2 is provided with an intake channel 12 and a replenishment channel 13. One end of the intake channel 12 can be connected to the medium-pressure intake pipeline 4, and the other end can be connected to the compression chamber of the second cylinder 2. One end of the replenishment channel 13 can be connected to the replenishment pipeline 5, and the other end can be connected to the compression chamber of the second cylinder 2 through the intake channel 12 or directly to the compression chamber of the second cylinder 2. This invention, through a unique structure on the second cylinder, enables the intake channel to guide gas from the medium-pressure intake pipeline into the compression chamber, and the replenishment channel to guide gas from the replenishment pipeline into the compression chamber. The intake channel directly guides gas into the compression chamber, and the replenishment channel can directly or indirectly guide gas into the compression chamber, completing the mixing and compression of medium-pressure intake and medium-pressure replenishment in the same cylinder. This ensures both the cooling and evaporation of the high-pressure evaporator and the purpose of replenishment circulation, improving the energy efficiency of the entire refrigeration system.

[0046] In some embodiments, when the other end of the replenishing air passage 13 is connected to the compression chamber of the second cylinder 2 via the intake passage 12, the replenishing air passage 13 and the intake passage 12 are connected by a connecting passage 14, which is located on the second cylinder 2; when the other end of the replenishing air passage 13 is directly connected to the compression chamber of the second cylinder 2, the replenishing air passage 13 and the intake passage 12 are not connected. These are two different structural forms of the present invention where the replenishing air passage and the compression chamber are indirectly or directly connected. Indirect connection, such as... Figure 3This means that the supplementary gas in the supplementary gas channel is introduced into the intake channel through the connecting channel on the second cylinder for mixing, and then introduced into the compression chamber together. The refrigerant from the flash tank, after being discharged into the supplementary gas channel through the baffle assembly, can directly mix with the refrigerant in the intake channel and be compressed together, achieving the effect of increasing cooling capacity and lowering temperature, and reducing intake leakage or loss of cooling capacity caused by the misalignment of the supplementary gas channel and the intake channel; direct connection as... Figure 4 This means that the make-up air channel and the intake air channel are not connected, and they are connected to the compression chamber separately. This means that a non-mixed make-up air method is used. Since the pressure of the flash evaporation flow path is greater than that of the medium pressure flow path, the make-up air flow and intake air recirculation can be reduced. However, since there is a certain angle between the flash evaporation flow path (make-up air channel) and the intake air channel (medium pressure flow path), the intake leakage increases. The larger the angle, the larger the intake closing angle, which will cause the loss of cooling capacity at this angle.

[0047] The present invention also provides a dual-evaporation enthalpy-increasing refrigeration system, which includes the aforementioned enthalpy-increasing dual-cylinder compressor, and further includes: a condenser 15, a high-pressure evaporator 16, a low-pressure evaporator 17, a first-stage throttling device 18, a second-stage throttling device 19, and a flash evaporator 20. The condenser 15 is connected to the exhaust end of the enthalpy-increasing dual-cylinder compressor 21. The first-stage throttling device 18 is connected between the condenser 15 and the inlet end of the flash evaporator 20. The gas outlet of the flash evaporator 20 is connected to the second cylinder 2. The high-pressure evaporator 16 is connected between the liquid outlet of the flash evaporator 20 and the second cylinder 2. The low-pressure evaporator 17 and the second-stage throttling device 19 are connected between the liquid outlet of the flash evaporator 20 and the first cylinder 1. The evaporation pressure of the refrigerant in the high-pressure evaporator 16 is higher than the evaporation pressure of the low-pressure evaporator 17.

[0048] This invention, through the aforementioned connection method, effectively forms a dual-temperature evaporator for evaporation, and the injection of gas for enthalpy enhancement and medium-pressure intake for compression are performed in the same cylinder. With this structure, 1. compared to a conventional dual-temperature system with a two-stage compressor, this invention reduces the introduction of exhaust gas from the first cylinder into the second cylinder for secondary compression, thus reducing the compression power consumption of the second cylinder. Furthermore, because the exhaust gas from the first and second cylinders is mixed (forming quasi-secondary compression rather than secondary compression), the exhaust pressure of the compressor is reduced compared to a two-stage cylinder, thereby lowering the overall compression power consumption. (In the pressure-enthalpy diagram...) Figure 8 This can also be seen from the fact that it effectively reduces the overall compression power consumption of the first and second cylinders (relative to...). Figure 72. Furthermore, this invention achieves dual-temperature evaporation, dual-cylinder compression, and enthalpy enhancement through a dual-cylinder compressor, eliminating the need for a three-cylinder configuration. This effectively reduces the number of cylinders, simplifies the structure, saves costs, increases space utilization, and allows for a smaller compressor size. 3. This invention achieves a two-stage throttling refrigeration cycle with dual evaporation temperatures through independent compression by two cylinders. Compared to conventional single-stage compression refrigeration systems, this invention achieves dual-temperature evaporation by connecting the two cylinders to the low-pressure and medium-pressure intake pipes, thereby increasing cooling capacity and refrigeration efficiency (energy efficiency). Compared to conventional two-stage throttling dual-compression or quasi-two-stage compression refrigeration cycle systems, this invention effectively reduces compression power consumption and improves refrigeration energy efficiency. In summary, this invention effectively increases refrigeration efficiency (energy efficiency) compared to various existing solutions, resulting in a significant improvement in the energy efficiency of the refrigeration system.

[0049] like Figure 1 Refrigerant from the two evaporators enters two independent distributors on the suction side, and then each enters its corresponding cylinder for compression. Medium-pressure superheated gas from the high-pressure evaporator enters the second cylinder (i.e., the medium-pressure cylinder). Medium-pressure saturated gas from the flash evaporator is compressed and enters the baffle assembly. It is discharged into the second cylinder through the gas injection valve device (gas injection assembly 24) and compressed together. Finally, it is discharged into the upper flange cavity (exhaust cavity 6). Low-pressure saturated or superheated gas is drawn into the low-pressure cylinder of the compressor. The low-pressure refrigerant is compressed into high-pressure superheated gas and discharged into the lower flange silencer cavity (i.e., the medium-pressure cavity 10). After passing through the lower flange vent, baffle vent, upper cylinder vent, and lower flange vent, it mixes with the refrigerant discharged from the high-pressure cylinder (mixed in the exhaust cavity 6) and enters the compressor housing. It is then discharged through the compressor exhaust pipe into the condenser. Because the exhaust is contained within a single chamber, the dual-evaporation enthalpy-increasing compressor has only one exhaust pressure. Both cylinders share a single crankshaft, and the displacement ratio of the two cylinders is determined by the load ratio at the two evaporation temperatures and the operating conditions. Furthermore, compared to a two-stage compression system, it reduces compression power consumption and improves refrigeration efficiency; compared to a single-stage compression system, it increases evaporative cooling capacity and also improves refrigeration efficiency and overall energy efficiency.

[0050] Table 1 below shows several different disclosed parameter values ​​of the present invention, which represent a significant improvement over the energy efficiency (EER) of a conventional single-stage cycle. See also... Figure 6 .

[0051] Table 1 Refrigeration Operating Parameters

[0052] R410A High evaporation temperature low evaporation temperature Condensation temperature Operating Condition 1 19 10 50 Operating Condition 2 16 10 46 Operating Condition 3 22 12 41 Operating Condition 4 16 14 38

[0053] In some embodiments, the system further includes a first pipeline 101, a second pipeline 102, and a third pipeline 103. One end of the first pipeline 101 is connected to the exhaust end of the enthalpy-increasing twin-cylinder compressor, and the other end is connected to one end of the first-stage throttling device 18. The condenser 15 is mounted on the first pipeline 101. One end of the second pipeline 102 is connected to the other end of the first-stage throttling device 18, and the other end of the second pipeline 102 is connected to the inlet end of the flash evaporator 20. One end of the make-up gas pipeline 5 is connected to the gas outlet of the flash evaporator 20, and the other end is connected to the... The second cylinder 2 is connected, one end of the third pipeline 103 is connected to the liquid outlet of the flash evaporator 20 and the other end is connected to one end of the secondary throttling device 19, one end of the medium-pressure air intake pipeline 4 is connected to the third pipeline 103 and the other end is connected to the second cylinder 2, the high-pressure evaporator 16 is installed on the medium-pressure air intake pipeline 4, one end of the low-pressure air intake pipeline 3 is connected to the other end of the secondary throttling device 19 and the other end of the low-pressure air intake pipeline 3 is connected to the first cylinder 1, and the low-pressure evaporator 17 is installed on the low-pressure air intake pipeline 3.

[0054] This is the preferred connection direction of the dual-temperature (dual-evaporation) enthalpy-increasing refrigeration system of the present invention. Through multiple pipelines, the gas from the flash evaporator gas outlet can be connected to the second cylinder for enthalpy-increasing gas replenishment, and the liquid from the flash evaporator liquid outlet can be connected to the high-pressure evaporator for evaporation, and then also enter the second cylinder for compression, forming a medium-pressure evaporation gas and a medium-pressure replenishment enthalpy-increasing gas mixed in the same cylinder. While ensuring the evaporation refrigeration capacity, it also ensures the effective circulation of refrigerant gas, thereby improving the energy efficiency of the system.

[0055] In some embodiments, the exhaust pressure Q1 of the second cylinder 2, the pressure Q2 of the air supply line 5, the exhaust pressure Q3 of the first cylinder 1, the displacement V1 of the second cylinder 2, the displacement V2 of the first cylinder 1, the flash coefficient is K, and the following conditions are met:

[0056]

[0057] This configuration effectively reduces pressure differential and the pressure on the balance crankshaft, thereby reducing vibration and improving reliability.

[0058] In some embodiments, the flash coefficient K is 0.65 to 0.9. By further preferably setting the flash coefficient K in the range of 0.65 to 0.9, the pressure difference can be further reduced, the pressure on the balance crankshaft can be reduced, thereby reducing vibration and improving reliability.

[0059] The present invention also provides an air conditioner, characterized in that it includes the dual-evaporation enthalpy-increasing refrigeration system as described in any one of claims 8-11.

[0060] In this invention, refrigerant from two evaporators enters two independent distributors on the suction side, and then each enters its corresponding cylinder for compression. Medium-pressure superheated gas from the high-temperature evaporator enters the medium-pressure cylinder. A portion of the liquid separated from the flash evaporator undergoes a two-stage throttling process to evaporate in the low-pressure evaporator to produce cooling capacity. Figure 8 As shown, compared to a conventional dual-medium-pressure single-stage cycle system, the increased unit cooling capacity effectively improves system performance. In this invention, another portion separated from the flash evaporator enters the high-pressure evaporator. After evaporation to produce cooling capacity, it is drawn into the medium-pressure cylinder (i.e., the second cylinder 2) of the compressor, where it is compressed and mixed with the supplementary gas from the flash evaporator until it reaches the system's exhaust pressure. Then, it is discharged through a baffle or upper flange into the compressor housing cavity, where it mixes with the gas discharged from the low-pressure cylinder and enters the system together, thus completing a full cycle. Compared to conventional supplementary gas enthalpy-increasing two-stage refrigeration systems, this effectively reduces compression work (the evaporation cooling capacity is basically the same, see [reference]). Figure 8 and Figure 7 (Comparison), thus effectively improving the cooling energy efficiency of the system.

[0061] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A supercharged dual cylinder compressor characterized by: include: The system comprises a first cylinder (1), a second cylinder (2), a low-pressure intake pipe (3), a medium-pressure intake pipe (4), a make-up air pipe (5), and an exhaust chamber (6). One end of the low-pressure intake pipe (3) is connected to an external low-pressure intake, and the other end is connected to the first cylinder (1) to introduce low-pressure intake air into the first cylinder (1). One end of the medium-pressure intake pipe (4) is connected to an external medium-pressure intake, and the other end is connected to the second cylinder (2) to introduce medium-pressure intake air into the second cylinder (2). The make-up air pipe (5)... 5) One end is connected to the external medium-pressure air supply, and the other end can be connected to the second cylinder (2) to introduce the medium-pressure air supply into the second cylinder (2). The pressure of the medium-pressure air supply is greater than the pressure of the low-pressure air supply, and the pressure of the medium-pressure air supply is greater than the pressure of the low-pressure air supply. The exhaust of the first cylinder (1) enters the exhaust chamber (6), and the exhaust of the second cylinder (2) also enters the exhaust chamber (6), so that the exhaust of the first cylinder (1) and the exhaust of the second cylinder (2) are mixed and discharged from the compressor.

2. The enthalpy-increasing dual-cylinder compressor according to claim 1, characterized in that: It also includes a first flange (7), a second flange (8), and a partition assembly (9). The first flange (7) is disposed on the side end face of the first cylinder (1) away from the second cylinder (2). The partition assembly (9) is disposed between the first cylinder (1) and the second cylinder (2). The second flange (8) is disposed on the side end face of the second cylinder (2) away from the first cylinder (1). The low-pressure air intake pipe (3) is directly connected to the first cylinder (1). The medium-pressure air intake pipe (4) is directly connected to the second cylinder (2) or connected to the second cylinder (2) through the partition assembly (9). The air supply pipe (5) is directly connected to the second cylinder (2) or connected to the second cylinder (2) through the partition assembly (9).

3. The enthalpy-increasing dual-cylinder compressor according to claim 2, characterized in that: The partition assembly (9) is provided with an air intake chamber (11), and the air supply pipe (5) is connected to the air intake chamber (11) to supply air to the air intake chamber (11). One end of the air intake chamber (11) is connected to the air supply pipe (5), and the other end is connected to the interior of the second cylinder (2). The medium-pressure air intake pipe (4) is directly connected to the second cylinder (2). Alternatively, the partition assembly (9) is provided with an air intake chamber (11), and the medium-pressure air intake pipe (4) is connected to the air intake chamber (11) to supply air to the air intake chamber (11). One end of the air intake chamber (11) is connected to the medium-pressure air intake pipe (4), and the other end is connected to the interior of the second cylinder (2). The air supply pipe (5) is directly connected to the second cylinder (2).

4. The enthalpy-increasing dual-cylinder compressor according to claim 2, characterized in that: The medium-pressure intake pipe (4) is directly connected to the second cylinder (2), and the supplementary air pipe (5) is directly connected to the second cylinder (2).

5. The enthalpy-increasing dual-cylinder compressor according to claim 2, characterized in that: It also includes a first muffler (25) and a second muffler (26). The first muffler (25) is disposed on the side end face of the first flange (7) away from the first cylinder (1) and forms a medium pressure chamber (10) between it and the first flange (7). One end of the medium pressure chamber (10) is connected to the exhaust of the first cylinder (1), and the other end of the medium pressure chamber (10) can be connected to the exhaust chamber (6). The second muffler (26) is disposed on the side end face of the second flange (8) away from the second cylinder (2), and forms the exhaust chamber (6) between the second flange (8).

6. The enthalpy-increasing twin-cylinder compressor according to any one of claims 2-4, characterized in that: The second cylinder (2) is provided with an air intake channel (12) and an air replenishment channel (13). One end of the air intake channel (12) can be connected to the medium-pressure air intake pipeline (4), and the other end can be connected to the compression chamber of the second cylinder (2). One end of the air replenishment channel (13) can be connected to the air replenishment pipeline (5), and the other end can be connected to the compression chamber of the second cylinder (2) through the air intake channel (12) or directly connected to the compression chamber of the second cylinder (2).

7. The enthalpy-increasing dual-cylinder compressor according to claim 6, characterized in that: When the other end of the replenishing air passage (13) is connected to the compression chamber of the second cylinder (2) through the intake passage (12), the replenishing air passage (13) and the intake passage (12) are connected through a connecting passage (14), which is located on the second cylinder (2); when the other end of the replenishing air passage (13) is directly connected to the compression chamber of the second cylinder (2), the replenishing air passage (13) and the intake passage (12) are not connected.

8. A dual evaporation enthalpy augmentation refrigeration system characterized by: The enthalpy-increasing twin-cylinder compressor according to any one of claims 1-7 further comprises: a condenser (15), a high-pressure evaporator (16), a low-pressure evaporator (17), a first-stage throttling device (18), a second-stage throttling device (19), and a flash evaporator (20). The condenser (15) is connected to the exhaust end of the enthalpy-increasing twin-cylinder compressor (21). The first-stage throttling device (18) is connected between the condenser (15) and the inlet end of the flash evaporator (20). The gas outlet of the flash evaporator (20) is connected to the second cylinder (2). The high-pressure evaporator (16) is connected between the liquid outlet of the flash evaporator (20) and the second cylinder (2). The low-pressure evaporator (17) and the second-stage throttling device (19) are connected between the liquid outlet of the flash evaporator (20) and the first cylinder (1). The evaporation pressure of the refrigerant in the high-pressure evaporator (16) is higher than the evaporation pressure of the low-pressure evaporator (17).

9. The dual-evaporation enthalpy-increasing refrigeration system according to claim 8, characterized in that: It also includes a first pipeline (101), a second pipeline (102), and a third pipeline (103). One end of the first pipeline (101) is connected to the exhaust end of the enthalpy-increasing dual-cylinder compressor, and the other end is connected to one end of the first-stage throttling device (18). The condenser (15) is installed on the first pipeline (101). One end of the second pipeline (102) is connected to the other end of the first-stage throttling device (18), and the other end of the second pipeline (102) is connected to the inlet end of the flash evaporator (20). One end of the gas supply pipeline (5) is connected to the gas outlet of the flash evaporator (20), and the other end is connected to the second cylinder (2). The third pipeline (103) is connected to the liquid outlet of the flash evaporator (20) at one end and to the second secondary throttling device (19) at the other end. The medium-pressure air intake pipeline (4) is connected to the third pipeline (103) at one end and to the second cylinder (2) at the other end. The high-pressure evaporator (16) is installed on the medium-pressure air intake pipeline (4). The low-pressure air intake pipeline (3) is connected to the second secondary throttling device (19) at one end and to the first cylinder (1) at the other end. The low-pressure evaporator (17) is installed on the low-pressure air intake pipeline (3).

10. The dual-evaporation enthalpy-increasing refrigeration system according to claim 8, characterized in that: The exhaust pressure Q1 of the second cylinder (2), the pressure Q2 of the air supply line (5), the exhaust pressure Q3 of the first cylinder (1), the displacement V1 of the second cylinder (2), the displacement V2 of the first cylinder (1), the flash coefficient is K, and the following are also given: 。 11. The dual-evaporation enthalpy-increasing refrigeration system according to claim 10, characterized in that: The flash evaporation coefficient K = 0.65~0.

9.

12. An air conditioner characterized by comprising: The dual-evaporation enthalpy-increasing refrigeration system includes any one of claims 8-11.

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