Multi-machine-head air-cooled water chilling unit refrigerating system and refrigerating equipment
By sharing the air-cooled condenser in a multi-head air-cooled chiller and arranging the refrigerant distribution pipes in reverse order, the problem of unbalanced compressor pressure ratios was solved, and energy consumption was reduced and cooling capacity was increased.
Patent Information
- Application Number
- CN202422837314.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-20
- Publication Date
- 2025-09-30
- Estimated Expiration
- 2034-11-20
AI Technical Summary
In existing multi-head air-cooled chillers, the pressure ratios of multiple compressors are unbalanced when they are running, resulting in low cooling capacity and high energy consumption.
Multiple refrigerant circulation paths share an air-cooled condenser, and the refrigerant pipes are arranged in reverse order between the air inlet and air outlet sides of each condenser to ensure that the inlet air temperature of each refrigerant circulation path is different, optimize the difference between evaporation temperature and condensation temperature, and balance the compressor pressure ratio.
By optimizing the arrangement of the refrigerant circulation flow path, energy consumption is significantly reduced, cooling capacity is increased, and pressure ratio balance of multiple compressors is achieved.
Smart Images
Figure CN223399959U_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the field of refrigeration technology, and in particular to a multi-head air-cooled chiller refrigeration system and refrigeration equipment. Background Art
[0002] In existing air-cooled screw units or air-cooled magnetic levitation centrifugal units, when multiple compressors (multiple compressors corresponding to multiple refrigeration systems) are running simultaneously, the general design scheme is: each compressor is equipped with an independent refrigerant circuit, the evaporator uses a shell and tube heat exchanger, and the condenser uses an air-cooled fin tube or microchannel structure. The condenser inlet air temperature of all refrigerant circuits is the same, while the evaporator side adopts a two-pass or multi-pass design of hot water exchange pipelines to form multiple independent refrigerant loops. This design can ensure that the evaporation pressure of multiple refrigerant loops is not much different, and their condensation pressure is not much different, so their pressure ratio is not much different, but the efficiency is not high.
[0003] Another design employs a series-connected evaporator arrangement, where the outlet water from the first refrigeration system flows into the evaporator of the second refrigeration system. However, the condensers of both refrigeration systems still use the same inlet air temperature. While this solution increases the evaporation temperature of the first refrigeration system, meaning the evaporation temperature on the water inlet side is higher, the first refrigeration system can produce a higher cooling capacity compared to the previous solution. However, the condensation temperature on the water outlet side of the evaporator of the second refrigeration system still corresponds to a higher pressure ratio, resulting in higher energy consumption. Utility Model Content
[0004] In view of this, the main purpose of this application is to provide a multi-head air-cooled chiller refrigeration system and refrigeration equipment, which is conducive to solving the problem of low cooling capacity and high energy consumption caused by uneven operating pressure ratios of multiple compressors in the prior art.
[0005] The present application provides a multi-head air-cooled chiller refrigeration system, which includes N refrigerant circulation flow paths, each of the refrigerant circulation flow paths includes: a refrigerant main pipeline, an electronic expansion valve, a refrigerant pipeline for an evaporator, a compressor, and multiple refrigerant branch pipelines in parallel, wherein the multiple refrigerant branch pipelines are respectively connected to M air-cooled condensers, wherein N is a natural number greater than or equal to 2, and M is a natural number greater than or equal to 1, and the M air-cooled condensers are shared by the N refrigerant circulation flow paths; a hot water exchange water pipeline, wherein the water pipelines of the evaporators in the N refrigerant circulation flow paths arranged in positive sequence are connected in series between the head and the tail, wherein the corresponding refrigerant branch pipelines in the N refrigerant circulation flow paths arranged in reverse sequence are connected to the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
[0006] From the above, N refrigerant circulation paths share M air-cooled condensers, that is, the refrigerant branch pipes arranged in each refrigerant circulation path are connected to M air-cooled condensers, and the arrangement order of the N refrigerant circulation paths between the water inlet end of the hot water exchange pipe and the water outlet end is opposite to the arrangement order between the air inlet side and the air outlet side of each air-cooled condenser. Through this design, in each air-cooled condenser, the inlet air temperature of the refrigerant in the refrigerant branch pipes in the N refrigerant circulation paths is different, so that the evaporation temperature of the evaporator in the refrigerant circulation path adjacent to the water outlet end of the hot water exchange pipe corresponds to a lower condensing temperature, thereby reducing the operating pressure ratio of the compressor in the refrigerant circulation path, significantly reducing the energy consumption of this part, balancing the compressor pressure ratios in the N refrigerant circulation paths, and achieving the purpose of increasing the cooling capacity and reducing energy consumption.
[0007] Optionally, when N is 2 and M is 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path and a second refrigerant circulation flow path, wherein the first refrigerant circulation flow path is arranged adjacent to the water inlet end of the hot water exchange pipe, and the second refrigerant circulation flow path is arranged adjacent to the water outlet end of the hot water exchange pipe.
[0008] Optionally, the refrigerant branch pipes in the first refrigerant circulation circuit are respectively connected in parallel to the refrigerant inlets and outlets on the air outlet sides of the two air-cooled condensers.
[0009] As described above, the first refrigerant circulation flow path is connected in parallel at the air outlet sides of the two air-cooled condensers through multiple refrigerant branch pipes arranged in parallel; when each air-cooled condenser adopts a V-shaped fin tube structure, the first refrigerant circulation flow path is provided with four refrigerant branch pipes in parallel, and every two refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the V-shaped fin tubes of each air-cooled condenser, and are arranged close to the air outlet side of each air-cooled condenser. When each air-cooled condenser adopts an inverted M-shaped fin tube structure, the first refrigerant circulation flow path is provided with eight refrigerant branch pipes in parallel, and every four refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the inverted M-shaped fin tubes of each air-cooled condenser, and are arranged close to the air outlet side of each air-cooled condenser.
[0010] Optionally, the refrigerant branch pipes in the second refrigerant circulation circuit are respectively connected in parallel to the refrigerant inlets and outlets on the air inlet sides of the two air-cooled condensers.
[0011] As described above, the second refrigerant circulation flow path is connected in parallel at the air inlet side of the two air-cooled condensers through multiple refrigerant branch pipes arranged in parallel; when each air-cooled condenser adopts a V-shaped fin tube structure, the second refrigerant circulation flow path is provided with four refrigerant branch pipes in parallel, and every two refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the V-shaped fin tube of each air-cooled condenser, and are arranged close to the air inlet side of each air-cooled condenser. When each air-cooled condenser adopts an inverted M-shaped fin tube structure, the first refrigerant circulation flow path is provided with eight refrigerant branch pipes in parallel, and every four refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the inverted M-shaped fin tube of each air-cooled condenser, and are arranged close to the air inlet side of each air-cooled condenser.
[0012] Optionally, when N is a natural number greater than 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path, a second refrigerant circulation flow path to an Nth refrigerant circulation flow path, wherein the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in sequence between the water inlet end and the water outlet end of the hot water exchange pipe.
[0013] Optionally, the refrigerant branch pipes in the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in reverse order and connected to the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
[0014] Optionally, the refrigerants in the N refrigerant circulation circuits have the same flow direction in their respective corresponding refrigerant branch pipes.
[0015] From the above, when the refrigerant in all refrigerant pipes flows in the same direction, it can ensure that the temperature distribution in the entire system is more uniform.
[0016] On the other hand, the present application also provides a refrigeration device, which includes any of the multi-head air-cooled chiller refrigeration systems described above.
[0017] From the above, the refrigeration equipment is not limited to small or large chillers, household air conditioners, industrial cooling systems and other occasions, nor is it limited to application fields such as hospitals, scientific research institutions, office buildings, and production plants.
[0018] In summary, the multi-head air-cooled chiller refrigeration system and refrigeration equipment provided by the present application. In the multi-head air-cooled chiller refrigeration system, the refrigerant branch pipe in the refrigerant circulation flow path arranged closer to the water outlet end of the hot water exchange pipe is arranged closer to the air inlet side of each air-cooled condenser, so that the temperature of the refrigerant in the refrigerant branch pipe in each refrigerant circulation flow path is different, so as to balance the compressor pressure ratio in multiple refrigerant circulation flow paths, thereby achieving the purpose of increasing the cooling capacity of the refrigerant circulation flow path arranged closer to the water outlet of the hot water exchange pipe and reducing its energy consumption. BRIEF DESCRIPTION OF THE DRAWINGS
[0019] The following further illustrates the various technical features of the present application and the relationships between them with reference to the accompanying drawings. The accompanying drawings are exemplary, and some technical features are not shown in actual proportion. In addition, some drawings may omit technical features that are commonly used in the technical field to which the present application belongs and are not essential for understanding and implementing the present application, or additional technical features that are not essential for understanding and implementing the present application may be shown. In other words, the combination of the various technical features shown in the accompanying drawings is not intended to limit the present application. In addition, throughout the present application, the same figure numbers refer to the same content. The specific description of the drawings is as follows:
[0020] Figure 1 This is an embodiment diagram of a multi-head air-cooled chiller refrigeration system in this application;
[0021] Figure 2 This is an example diagram of the prior art in this application.
[0022] Description of Reference Numerals
[0023] 11-first flooded evaporator, 12-first compressor, 13-first electronic expansion valve, 21-second flooded evaporator, 22-second compressor, 23-second electronic expansion valve, 31-first air-cooled condenser, 32-second air-cooled condenser, 11′-high-temperature side evaporator, 12′-high-temperature side compressor, 13′-high-temperature side electronic expansion valve, 21′-low-temperature side evaporator, 22′-low-temperature side compressor, 23′-low-temperature side electronic expansion valve, 31′-high-temperature side condenser, 32′-low-temperature side condenser.
[0024] The above drawings illustrate specific embodiments of the present application, which will be described in more detail below. These drawings and the textual description are not intended to limit the scope of the present application in any way, but rather to illustrate the concepts of the present application to those skilled in the art by reference to specific embodiments. DETAILED DESCRIPTION
[0025] The preferred embodiments of the present application are described in detail below in conjunction with the accompanying drawings so that the advantages and features of the present application can be more easily understood by those skilled in the art, thereby making a clearer and more definite definition of the protection scope of the present application.
[0026] It should be noted that, in this document, relational terms such as first and second, etc., are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any actual relationship or order between these entities or operations. Moreover, the terms "comprises," "comprising," or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article, or device comprising a series of elements includes not only those elements, but also other elements not explicitly listed, or elements inherent to such process, method, article, or device. In the absence of further limitations, the elements defined by the phrase "comprising..." do not exclude the presence of other identical elements in the process, method, article, or device comprising the elements.
[0027] Figure 2 A traditional two-compressor refrigeration system is shown, each with an independent refrigerant circuit. Because the water temperature at the water inlet of the hot water exchange pipe is higher, the refrigeration system located there is a high-temperature side refrigeration system (referred to as the high-temperature side). Similarly, the refrigeration system located at the water outlet of the hot water exchange pipe is a low-temperature side refrigeration system (referred to as the low-temperature side). The inlet air temperature of the high-temperature side condenser 31′ and the low-temperature side condenser 32′ are the same, while the inlet water temperature of the high-temperature side evaporator 11′ is higher. The outlet water temperature of the high-temperature side evaporator 11′ is equal to the inlet water temperature of the low-temperature side evaporator 21′. The high-temperature side refrigeration system has higher evaporation and condensation temperatures, while the outlet water of the low-temperature side evaporator 21′ of the low-temperature side evaporator 21′ continues heat exchange and cooling, resulting in the outlet water temperature of the low-temperature side evaporator 21′ being lower than the outlet water temperature of the high-temperature side evaporator 11′. Therefore, the evaporation pressure of the low-temperature side refrigeration system is lower than that of the high-temperature side refrigeration system. Although the air inlet temperatures of the condensers (31′, 32′) of the two refrigeration systems are the same, their air outlet temperatures will be slightly different due to the difference in evaporation pressure, which will cause the operating pressure ratio of the low-temperature side compressor 22′ to be greater than the operating pressure ratio of the high-temperature side compressor 12′, and thus the cooling capacity of the low-temperature side compressor 22′ is lower than the cooling capacity of the high-temperature side compressor 12′, and the operating energy consumption of the low-temperature side compressor 22′ is greater than the operating energy consumption of the high-temperature side compressor 12′.
[0028] For large water-cooled centrifugal units, a series countercurrent solution can be used to balance the pressure ratio of the two refrigeration systems, improve energy efficiency and increase cooling capacity. Taking a two-compressor refrigeration system as an example, the compressor in the first refrigeration system corresponds to the water inlet side of the system's evaporator, while the compressor in the first refrigeration system corresponds to the water outlet side of the system's condenser. The evaporator's water inlet temperature is high, and the condenser's water outlet temperature is also high, that is, high evaporation temperature and high condensation temperature. The compressor in the second refrigeration system corresponds to the water outlet side of the system's evaporator and the water inlet side of the system's condenser. This means that a low evaporation temperature corresponds to a lower condensing temperature, which ensures that the condensing temperature of the second refrigeration system is reduced, thereby reducing the corresponding compressor pressure ratio and energy consumption. A lower pressure ratio usually increases the cooling capacity output to a certain extent.
[0029] This application optimizes system performance by varying the air inlet temperature of the condensers in different refrigeration systems. Specifically, the air inlet temperature of the low-temperature side condenser is the ambient air temperature. After absorbing heat, the air temperature rises before entering the high-temperature side condenser to continue absorbing heat. This design ensures that the operating pressure ratio of the low-temperature side refrigeration system is significantly lower than that of traditional air cooling, thereby increasing the cooling capacity of the low-temperature side refrigeration system and reducing the operating energy consumption of its compressor.
[0030] The following describes in detail the technical solution of the present application and how the technical solution of the present application solves the above-mentioned technical problems using specific embodiments. The specific embodiments described below can be combined with each other to form new embodiments. The same or similar ideas or processes described in one embodiment may not be repeated in other embodiments. The embodiments of the present application will be described below in conjunction with the accompanying drawings.
[0031] The present application provides a multi-head air-cooled chiller refrigeration system, which includes N refrigerant circulation flow paths, each of the refrigerant circulation flow paths includes: a refrigerant main pipeline, an electronic expansion valve, a refrigerant pipeline for an evaporator, a compressor, and multiple refrigerant branch pipelines in parallel, wherein the multiple refrigerant branch pipelines are respectively connected to M air-cooled condensers, wherein N is a natural number greater than or equal to 2, and M is a natural number greater than or equal to 1, and the M air-cooled condensers are shared by the N refrigerant circulation flow paths; a hot water exchange water pipeline, wherein the water pipelines of the evaporators in the N refrigerant circulation flow paths arranged in positive sequence are connected in series between the head and the tail, wherein the corresponding refrigerant branch pipelines in the N refrigerant circulation flow paths arranged in reverse sequence are connected to the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
[0032] Specifically, N refrigerant circulation paths share M air-cooled condensers, that is, the refrigerant branch pipes arranged in each refrigerant circulation path are connected to M air-cooled condensers, and the arrangement order of the N refrigerant circulation paths between the water inlet end of the hot water exchange pipe and the water outlet end is opposite to the arrangement order between the air inlet side and the air outlet side of each air-cooled condenser. Through this design, in each air-cooled condenser, the inlet air temperature of the refrigerant in the refrigerant branch pipes in the N refrigerant circulation paths is different, so that the evaporation temperature of the evaporator in the refrigerant circulation path adjacent to the water outlet end of the hot water exchange pipe corresponds to a lower condensing temperature, thereby reducing the operating pressure ratio of the compressor in the refrigerant circulation path, significantly reducing the energy consumption of this part, and balancing the compressor pressure ratios in the N refrigerant circulation paths, achieving the purpose of increasing the cooling capacity and reducing energy consumption.
[0033] In this embodiment, the evaporator is divided into a refrigerant pipeline and a water pipeline. High-temperature water to be cooled undergoes heat exchange in the evaporator, while the refrigerant in the refrigerant pipeline cools the high-temperature water in the water pipeline. N refrigerant circulation paths are sequentially arranged between the water inlet and outlet of the hot water exchange pipeline through the evaporator.
[0034] Optionally, when N is 2 and M is 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path and a second refrigerant circulation flow path, wherein the first refrigerant circulation flow path is arranged adjacent to the water inlet end of the hot water exchange pipe, and the second refrigerant circulation flow path is arranged adjacent to the water outlet end of the hot water exchange pipe.
[0035] Optionally, the refrigerant branch pipes in the first refrigerant circulation circuit are respectively connected in parallel to the refrigerant inlets and outlets on the air outlet sides of the two air-cooled condensers.
[0036] Specifically, the first refrigerant circulation flow path is connected in parallel at the air outlet sides of the two air-cooled condensers through multiple refrigerant branch pipes arranged in parallel. When each air-cooled condenser adopts a V-shaped fin tube structure, the first refrigerant circulation flow path is provided with four refrigerant branch pipes in parallel, with each two refrigerant branch pipes being sequentially connected to the refrigerant inlet and outlet ends of the V-shaped fin tubes of each air-cooled condenser and being arranged near the air outlet side of each air-cooled condenser. When each air-cooled condenser adopts an inverted M-shaped fin tube structure, the first refrigerant circulation flow path is provided with eight refrigerant branch pipes in parallel, with each four refrigerant branch pipes being sequentially connected to the refrigerant inlet and outlet ends of the inverted M-shaped fin tubes of each air-cooled condenser and being arranged near the air outlet side of each air-cooled condenser.
[0037] Optionally, the refrigerant branch pipes in the second refrigerant circulation circuit are respectively connected in parallel to both ends of the refrigerant inlet and outlet on the air inlet side of the two air-cooled condensers.
[0038] Specifically, the second refrigerant circulation flow path is connected in parallel at the air inlet side of the two air-cooled condensers through multiple refrigerant branch pipes arranged in parallel; when each air-cooled condenser adopts a V-shaped fin tube structure, the second refrigerant circulation flow path is provided with four refrigerant branch pipes in parallel, and every two refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the V-shaped fin tubes of each air-cooled condenser, and are arranged close to the air inlet side of each air-cooled condenser. When each air-cooled condenser adopts an inverted M-shaped fin tube structure, the first refrigerant circulation flow path is provided with eight refrigerant branch pipes in parallel, and every four refrigerant branch pipes are sequentially connected to the refrigerant inlet and outlet ends of the inverted M-shaped fin tubes of each air-cooled condenser, and are arranged close to the air inlet side of each air-cooled condenser.
[0039] Optionally, when N is a natural number greater than 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path, a second refrigerant circulation flow path to an Nth refrigerant circulation flow path, wherein the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in sequence between the water inlet end and the end of the hot water exchange pipe.
[0040] Optionally, the refrigerant branch pipes in the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in reverse order and connected to the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
[0041] Optionally, the refrigerants in the N refrigerant circulation circuits have the same flow direction in their respective corresponding refrigerant branch pipes.
[0042] Specifically, when the refrigerant in all refrigerant sub-pipes flows in the same direction, a more uniform temperature distribution in the entire system can be ensured.
[0043] In an optional embodiment of the present application, the evaporator can employ a single-pass or multi-pass structure. Based on actual heat exchange requirements, pressure drop requirements, and cost, the evaporator can be selected to optimize performance using a single-pass, dual-pass, triple-pass, or even multi-pass structure. The evaporator must be a shell-and-tube structure. In the preferred embodiment of the present application, a flooded evaporator can be employed.
[0044] In addition, the single-flow structure means that the medium to be cooled (such as water) passes through the tube bundle inside the evaporator only once, that is, it enters from one end and flows out from the other end. The single-flow structure is simple, the water flow path is short, and the pressure drop is small; the three-flow structure means that the medium to be cooled passes through the tube bundle inside the evaporator three times, and multiple round trips are achieved through baffles or other guide devices; the three-flow structure is complex, the water flow path is long, the heat exchange area is large, and the heat exchange efficiency is high, but the pressure drop is large.
[0045] In an optional embodiment of the present application, in N refrigerant circulation paths, if each refrigerant circulation path is to be connected in parallel to M air-cooled condensers, each refrigerant circulation path can be achieved by providing O refrigerant branch pipes. When the air-cooled condenser adopts a single-fin tube structure, O equals M, that is, each refrigerant circulation path is provided with O refrigerant branch pipes, and the O refrigerant branch pipes are sequentially connected in parallel to the single-fin tubes of the M air-cooled condensers. When the air-cooled condenser adopts a V-shaped fin tube structure, O equals 2M, that is, each refrigerant circulation path is provided with 2M refrigerant branch pipes, and every two refrigerant branch pipes are respectively connected to the refrigerant inlet and outlet ends of the V-shaped fin tube of each air-cooled condenser. When the air-cooled condenser adopts an inverted M-shaped fin tube structure, O equals 4M, that is, each refrigerant circulation path is provided with 4M refrigerant branch pipes, and every four refrigerant branch pipes are respectively connected to the refrigerant inlet and outlet ends of the inverted M-shaped fin tube of each air-cooled condenser.
[0046] Taking N=2, M=2, O=2 as an example, the two refrigerant circulation flow paths are respectively recorded as the first refrigerant circulation flow path and the second refrigerant circulation flow path, the two refrigerant branch pipes in the first refrigerant circulation flow path are respectively recorded as the 11th refrigerant branch pipe and the 12th refrigerant branch pipe, the two refrigerant branch pipes in the second refrigerant circulation flow path are respectively recorded as the 21st refrigerant branch pipe and the 22nd refrigerant branch pipe, and the two air-cooled condensers are respectively recorded as the first air-cooled condenser and the second air-cooled condenser. At this time, the first air-cooled condenser and the second air-cooled condenser can adopt a single-fin tube folded arrangement structure.
[0047] In this embodiment, the first evaporator in the first refrigerant circulation flow path is arranged after the water inlet end of the hot water exchange pipe, and the high-temperature water that needs to be cooled is cooled once through the first evaporator. The second evaporator in the second refrigerant circulation flow path is arranged before the water outlet end of the hot water exchange pipe, and the high-temperature water that has been cooled once is cooled twice through the second evaporator. In the first refrigerant circulation flow circuit, a first electronic expansion valve, a first evaporator, and a first compressor are arranged in sequence on the first refrigerant main pipeline along the direction of refrigerant circulation, and the 11th refrigerant branch pipeline and the 12th refrigerant branch pipeline are connected in parallel with the first refrigerant main pipeline, and the 11th refrigerant branch pipeline is connected to the air outlet side of the first air-cooled condenser, and the 12th refrigerant branch pipeline is connected to the air outlet side of the second air-cooled condenser. After the refrigerant is discharged through the first air-cooled condenser and the second air-cooled condenser, it circulates again through the first electronic expansion valve, the first evaporator, and the first compressor; similarly, the setting of the second refrigerant circulation flow circuit is the same as the setting principle of the first refrigerant circulation flow circuit, but the 21st refrigerant branch pipeline in the second refrigerant circulation flow circuit is connected to the air inlet side of the first air-cooled condenser, and the 22nd refrigerant branch pipeline is connected to the air inlet side of the second air-cooled condenser. When the first air-cooled condenser is operating, the air inlet side is air with a lower ambient temperature. After the refrigerant in the 21st refrigerant branch pipe absorbs heat, the air temperature rises, and then after the refrigerant in the 11th refrigerant branch pipe continues to absorb heat, the air with a higher temperature is discharged through the air outlet side of the first air-cooled condenser. Similarly, when the second air-cooled condenser is operating, the air inlet side is air with a lower ambient temperature. After the refrigerant in the 22nd refrigerant branch pipe absorbs heat, the air temperature rises, and then after the refrigerant in the 12th refrigerant branch pipe continues to absorb heat, the air with a higher temperature is discharged through the air outlet side of the second air-cooled condenser; thus, the first refrigerant circulation flow path and the second refrigerant circulation flow path are connected in series at the air path of the first air-cooled condenser, and at the same time, the first refrigerant circulation flow path and the second refrigerant circulation flow path are connected in series at the air path of the second air-cooled condenser. The refrigerant in the 11th refrigerant branch pipeline and the 12th refrigerant branch pipeline is condensed by the first air-cooled condenser and the second air-cooled condenser and then flows into the first evaporator, so that the system high-temperature water is cooled once; the refrigerant in the 21st refrigerant branch pipeline and the 22nd refrigerant branch pipeline is condensed by the first air-cooled condenser and the second air-cooled condenser and then flows into the second evaporator, so that the system high-temperature water that has been cooled once is cooled twice.
[0048] In the above embodiment, the evaporating temperature of the first evaporator corresponds to the condensing temperature of the two air-cooled condensers, wherein the evaporating temperature and the condensing temperature are both relatively high; the evaporating temperature of the second evaporator corresponds to the condensing temperature of the two air-cooled condensers, wherein the evaporating temperature and the condensing temperature are both relatively low, so that the operating pressure ratio of the second refrigerant circulation flow path is greatly reduced compared with the traditional air-cooling system, the cooling capacity of the second refrigerant circulation flow path will increase, and the energy consumption of the second compressor of the second refrigerant circulation flow path will be reduced.
[0049] Figure 1 This is a specific implementation diagram of the multi-head air-cooled chiller refrigeration system of this application. Figure 1 In the specific embodiment shown, N=2, M=2, O=4 is taken as an example, and the evaporator adopts a full-liquid evaporator and the air-cooled condenser adopts a V-shaped fin tube as an example. The two refrigerant circulation flow paths are respectively recorded as the first refrigerant circulation flow path and the second refrigerant circulation flow path, the four refrigerant branch pipes in the first refrigerant circulation flow path are respectively recorded as the 11th refrigerant branch pipe, the 12th refrigerant branch pipe, the 13th refrigerant branch pipe and the 14th refrigerant branch pipe, and the four refrigerant branch pipes in the second refrigerant circulation flow path are respectively recorded as the 21st refrigerant branch pipe, the 22nd refrigerant branch pipe, the 23rd refrigerant branch pipe and the 24th refrigerant branch pipe, and the two air-cooled condensers are respectively recorded as the first air-cooled condenser 31 and the second air-cooled condenser 32. At this time, the first air-cooled condenser 31 and the second air-cooled condenser 32 both adopt a V-shaped fin tube structure, that is, the two groups of fin tubes are arranged in a V shape, and one of the fin tubes can contain two or more base tubes, that is, a multi-channel fin tube. A first electronic expansion valve 13, a first flooded evaporator 11 and a first compressor 12 are provided on the first refrigerant main pipeline in the first refrigerant circulation flow path, and a second electronic expansion valve 23, a second flooded evaporator 21 and a second compressor 22 are provided on the second refrigerant main pipeline in the second refrigerant circulation flow path.
[0050] A first refrigerant circulation flow path and a second refrigerant circulation flow path are arranged between the water inlet end and the water outlet end of the hot water exchange pipe, wherein the water inlet end of the hot water exchange pipe is connected to the water inlet end of the water pipe inside the first full-liquid evaporator 11, and the water outlet end of the water pipe inside the first full-liquid evaporator 11 is connected to the water inlet end of the water pipe inside the second full-liquid evaporator 21 through the hot water exchange pipe, and the water outlet end of the water pipe inside the second full-liquid evaporator 21 is the water outlet end of the hot water exchange pipe; the water inlet end of the water pipe inside the first full-liquid evaporator 11 is generally arranged on its side, opposite to its water outlet end, and the high-temperature water to be cooled passes through the water inlet end of the water pipe inside the first full-liquid evaporator 11 It enters its internal coil and flows out through the water outlet of the internal water pipeline of the first flooded evaporator 11, and enters the second flooded evaporator 21 for secondary cooling; the refrigerant inlet of the refrigerant pipeline inside the first flooded evaporator 11 is generally set at its bottom, and its refrigerant outlet is generally set at the top. After the liquid first refrigerant is reduced in pressure by the first electronic expansion valve 13, it enters the bottom of the first flooded evaporator 11 and fills the entire shell of the first flooded evaporator 11. The first refrigerant absorbs heat inside the first flooded evaporator 11 and gradually evaporates into a gaseous state. The gaseous first refrigerant is discharged through the refrigerant outlet, sucked into the first compressor 12, and enters the next cycle.
[0051] In the first refrigerant circulation flow path, the first flooded evaporator 11 is arranged on the first refrigerant main pipeline and the hot water exchange pipeline. The refrigerant inlet of the refrigerant pipeline inside the first flooded evaporator 11 is connected to the first electronic expansion valve 13, and the refrigerant outlet of the refrigerant pipeline inside the first flooded evaporator 11 is connected to the inlet of the first compressor 12. The outlet of the first compressor 12 is connected to the first air-cooled condenser 31 and the second air-cooled condenser 32 through multiple refrigerant branch pipelines. Among them, the 11th refrigerant branch pipeline and the 12th refrigerant branch pipeline are connected to the first air-cooled condenser. The 13th refrigerant branch pipe and the 14th refrigerant branch pipe are connected to the refrigerant inlet and outlet on the air outlet side of the two groups of fin tubes of the second air-cooled condenser 32. At the same time, the 21st refrigerant branch pipe and the 22nd refrigerant branch pipe in the second refrigerant circulation flow path are connected to the refrigerant inlet and outlet on the air inlet side of the two groups of V-shaped fin tubes of the first air-cooled condenser 31, and the 23rd refrigerant branch pipe and the 24th refrigerant branch pipe are connected to the refrigerant inlet and outlet on the air inlet side of the two groups of fin tubes of the second air-cooled condenser 32.
[0052] In the first refrigerant circulation flow path, after the first refrigerant is discharged from the first flooded evaporator 11, it enters the first compressor 12. The first compressor 12 compresses the low-temperature, low-pressure, gaseous first refrigerant through the operation of the motor, and then discharges the high-temperature, high-pressure, gaseous first refrigerant. At this time, the first refrigerant enters the first air-cooled condenser 31 and the second air-cooled condenser 32 at the same time. After heat exchange, it is gradually cooled and finally condensed into a low-temperature, high-pressure, liquid first refrigerant. After the low-temperature, high-pressure, liquid first refrigerant is depressurized by the first electronic expansion valve 13, it enters the first flooded evaporator 11 and exchanges heat with the high-temperature water of the system. The low-temperature, low-pressure, liquid first refrigerant absorbs heat and becomes a low-temperature, low-pressure, gaseous first refrigerant, thereby completing the first-stage refrigeration cycle.
[0053] Similarly, the secondary refrigeration cycle of the second refrigerant circulation flow path has the same principle and configuration as the first refrigerant circulation flow path, and will not be described in detail here.
[0054] In the above embodiment, in the first-stage refrigeration cycle, the evaporation temperature of the first flooded evaporator 11 corresponds to the condensation temperature of the two air-cooled condensers, wherein the evaporation temperature and the condensation temperature are both relatively high; in the second-stage refrigeration cycle, the evaporation temperature of the second flooded evaporator 21 corresponds to the condensation temperature of the two air-cooled condensers, wherein the evaporation temperature and the condensation temperature are both relatively low, so that the operating pressure ratio of the second refrigerant circulation flow path is greatly reduced compared with the traditional air-cooling system, the cooling capacity of the second refrigerant circulation flow path will increase, and the energy consumption of the second compressor of the second refrigerant circulation flow path will be reduced.
[0055] When N=3, the three refrigerant circulation flow paths are designated as the first refrigerant circulation flow path, the second refrigerant circulation flow path, and the third refrigerant circulation flow path. The first evaporator in the first refrigerant circulation flow path is located after the water inlet end of the hot water exchange pipe, the second evaporator in the second refrigerant circulation flow path is located in the middle of the hot water exchange pipe, and the third evaporator in the third refrigerant circulation flow path is located before the water outlet end of the hot water exchange pipe. The refrigerant branch pipe in the first refrigerant circulation flow path is located near the air outlet side of each air-cooled condenser, the refrigerant branch pipe in the third refrigerant circulation flow path is located near the air inlet side of each air-cooled condenser, and the refrigerant branch pipe in the second refrigerant circulation flow path is located between the air inlet and air outlet sides of each air-cooled condenser.
[0056] Similarly, when N=4, 5, ..., the refrigerant branch pipe in the first refrigerant circulation flow path is arranged close to the air outlet side of each air-cooled condenser, and the refrigerant branch pipe in the Nth refrigerant circulation flow path is arranged close to the air inlet side of each air-cooled condenser, that is, the refrigerant branch pipes in the Nth, N-1, N-2, ..., 2, 1 refrigerant circulation flow paths are connected in sequence.
[0057] Similarly, no matter whether the air-cooled condenser uses V-shaped fin tubes or inverted M-shaped fin tubes, the fin tubes arranged in a V-shape or inverted M-shape have an air outlet side and an air inlet side. No matter how large a natural number N is, the refrigerant branch pipe in the refrigerant circulation flow path is arranged closer to the water outlet end of the hot water exchange pipe, and the closer it is arranged to the air inlet side of each air-cooled condenser.
[0058] When multiple refrigerant circulation paths use their respective corresponding air-cooled condensers to form separate circulation loops, the air inlet temperatures of the air-cooled condensers of the multiple refrigerant circulation paths are the same, but their air outlet temperatures are slightly different. This will result in the compressor of the refrigerant circulation path being set closer to the water outlet of the hot water pipe having a larger operating pressure ratio and greater operating energy consumption. Therefore, multiple refrigerant circulation paths need to use multiple air-cooled condensers at the same time to reduce the difference in air outlet temperature.
[0059] On the other hand, the present application also provides a refrigeration device, which includes any of the multi-head air-cooled chiller refrigeration systems described above.
[0060] Specifically, the refrigeration equipment is not limited to occasions such as small or large chillers, household air conditioners, industrial cooling systems, etc., nor is it limited to application fields such as hospitals, scientific research institutions, office buildings, and production plants.
[0061] In summary, the multi-head air-cooled chiller refrigeration system and refrigeration equipment provided by the present application. In the multi-head air-cooled chiller refrigeration system, the refrigerant branch pipe in the refrigerant circulation flow path arranged closer to the water outlet end of the hot water exchange pipe is arranged closer to the air inlet side of each air-cooled condenser, so that the temperature of the refrigerant in the refrigerant branch pipe in each refrigerant circulation flow path is different, so as to balance the compressor pressure ratio in multiple refrigerant circulation flow paths, thereby achieving the purpose of increasing the cooling capacity of the refrigerant circulation flow path arranged closer to the water outlet of the hot water exchange pipe and reducing its energy consumption.
[0062] Unless otherwise defined, all technical and scientific terms used in this application are the same as those commonly understood by those skilled in the art to which this application belongs. In the event of any inconsistency, the meaning described in the full text of this application or the meaning derived from the content recorded in the full text of this application shall prevail. In addition, the terms used in this description are only for the purpose of describing the embodiments of the present application and are not intended to limit this application.
[0063] Note that the above are only preferred embodiments of the present application and the technical principles employed. Those skilled in the art will understand that the present application is not limited to the specific embodiments described herein, and that various obvious changes, readjustments, and substitutions can be made by those skilled in the art without departing from the scope of protection of the present application. Therefore, although the present application has been described in more detail through the above embodiments, the present application is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the technical concept of the present application, all of which fall within the scope of protection of the present application.
[0064] It should be noted that, in the description herein, the terms "middle", "front", "back", "top", "bottom", "left", "right", "vertical", "horizontal", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on this application.
[0065] Furthermore, the terms "installed," "disposed," "connected," and "connected" should be interpreted broadly. For example, they can refer to fixed connections, removable connections, or integral structures; mechanical connections; direct connections, indirect connections through an intermediary, or internal communication between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in this utility model based on the specific circumstances.
[0066] The above description is merely an embodiment of the present application and does not limit the patent scope of the present application. Any equivalent structural transformation made using the contents of the present application specification and drawings, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present application.
Claims
1. A multi-head air-cooled chiller refrigeration system, characterized in that: include: N refrigerant circulation flow paths, each of the refrigerant circulation flow paths comprising: a refrigerant main pipeline, a refrigerant pipeline with an electronic expansion valve and an evaporator connected in series between the beginning and the end of the refrigerant main pipeline, a compressor, and a plurality of refrigerant branch pipelines connected in parallel, the plurality of refrigerant branch pipelines being respectively connected to M air-cooled condensers, wherein N is a natural number greater than or equal to 2, M is a natural number greater than or equal to 1, and the M air-cooled condensers are shared by the N refrigerant circulation flow paths; The hot water exchange pipe has the water pipes of the evaporator in the N refrigerant circulation circuits arranged in positive sequence connected in series between its head and tail, wherein the corresponding refrigerant branch pipes in the N refrigerant circulation circuits arranged in reverse sequence are connected at the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
2. The multi-head air-cooled chiller refrigeration system according to claim 1, characterized in that: include: When N is 2 and M is 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path and a second refrigerant circulation flow path, wherein the first refrigerant circulation flow path is arranged adjacent to the water inlet end of the hot water exchange pipe, and the second refrigerant circulation flow path is arranged adjacent to the water outlet end of the hot water exchange pipe.
3. The multi-head air-cooled chiller refrigeration system according to claim 2, characterized in that: The refrigerant branch pipes in the first refrigerant circulation flow path are respectively connected in parallel to the refrigerant inlets and outlets on the air outlet sides of the two air-cooled condensers.
4. The multi-head air-cooled chiller refrigeration system according to claim 3, characterized in that: The refrigerant branch pipes in the second refrigerant circulation flow path are respectively connected in parallel to the refrigerant inlets and outlets on the air inlet sides of the two air-cooled condensers.
5. The multi-head air-cooled chiller refrigeration system according to claim 1, characterized in that: Also includes: When N is a natural number greater than 2, the refrigerant circulation flow path includes a first refrigerant circulation flow path, a second refrigerant circulation flow path to an Nth refrigerant circulation flow path, wherein the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in sequence between the water inlet end and the water outlet end of the hot water exchange pipe.
6. The multi-head air-cooled chiller refrigeration system according to claim 5, characterized in that: The refrigerant branch pipes in the first refrigerant circulation flow path, the second refrigerant circulation flow path to the Nth refrigerant circulation flow path are arranged in reverse order and connected to the refrigerant inlet and outlet between the air inlet side and the air outlet side of each air-cooled condenser.
7. The multi-head air-cooled chiller refrigeration system according to claim 1, characterized in that: The refrigerants in the N refrigerant circulation paths have the same flow direction in their corresponding refrigerant branch pipes.
8. A refrigeration device, characterized in that: A refrigeration system comprising a multi-head air-cooled chiller as described in any one of claims 1 to 7.