Large-temperature-difference absorption type heat exchanger unit for multi-partition heat supply

Abstract

The invention discloses a large-temperature-difference absorption heat exchanger unit for multi-partition heat supply, which comprises a generator (1), an evaporator (2), an absorber (3), a condenser (4), at least one water-water heat exchanger (5) and a pipeline system for connecting the components, the pipeline system comprises a primary network pipeline and a secondary network pipeline. The system is characterized in that the secondary network pipeline is configured to serve at least two independent heat supply subareas, and the absorber (3) and the condenser (4) are independently configured to bear heat supply loads of different subareas through the parallel flow dividing type flow path design. Through the innovative flow path design, the problems that a traditional series flow path is large in resistance and loads are difficult to accurately match are effectively solved, independent and efficient heat supply for multiple partitions in a single unit is achieved, system resistance is remarkably reduced, and the operation energy efficiency, heat supply stability and working condition adaptability of the unit are improved.

Description

Technical Field

[0001] This invention relates to the field of heating engineering technology, and in particular to a large temperature difference absorption heat exchanger unit for multi-zone heating. Background Technology

[0002] In urban centralized heating systems, absorption heat exchangers have become the mainstream technology for achieving large temperature difference operation to reduce transmission and distribution costs. In practical applications, a single unit often needs to handle the heat exchange needs of multiple heating zones simultaneously. Currently, existing absorption heat exchangers with large temperature difference operation for two-zone heating systems mainly adopt the following two typical schemes: like Figure 1 As shown, in the first scheme, the secondary network return water of the first heating zone flows only through another independent water-to-water heat exchanger, while the secondary network return water of the second heating zone is divided into two parallel paths: one path flows sequentially through the absorber and condenser for a series-stage temperature increase, and the other path flows through an independent water-to-water heat exchanger for temperature increase. The two paths are then mixed to supply heat to the corresponding zones. The working fluid in the unit's primary network pipeline flows sequentially through the generator, the water-to-water heat exchanger of the first heating zone, the water-to-water heat exchanger of the second heating zone, and the evaporator, providing independent driving force for both zones.

[0003] like Figure 2 As shown, in the second scheme, the secondary network return water for both heating zones is divided into two parallel paths: one path flows sequentially through its corresponding absorber and condenser for series heating, while the other path flows through its corresponding water-to-water heat exchanger. The heated water from both paths mixes to supply heat to their respective zones. The working fluid in the unit's primary network flows through the generator, water-to-water heat exchanger, and evaporator of each of the two heating zones, providing independent driving force for each zone.

[0004] The common core feature of the above-mentioned existing technical solutions is that in the secondary network pipelines of each heating zone, the main heat exchange path requires the return water to flow in series through the two key heat exchange components, the absorber and the condenser.

[0005] Since the above schemes all employ a design where the secondary network return water flows in series through the absorber and condenser, the fluid needs to continuously overcome the flow resistance of two heat exchange components. In applications with large heating loads and high secondary network circulation flow rates, this series flow path leads to a significant increase in the overall flow resistance of the unit's secondary side piping system. Excessive system resistance not only increases the energy consumption of the circulating water pump but may also limit the system's flow rate regulation range, adversely affecting the unit's applicability (especially at sites requiring high flow rate operation or with strict limitations on system pressure drop).

[0006] Existing technologies attempt to distribute the load and optimize heat exchange by configuring multiple heat exchange paths (such as parallel water-to-water heat exchangers), but their fundamental flow path architecture remains unchanged due to the series connection. Therefore, they cannot fundamentally solve the inherent high resistance problem caused by the series arrangement of the absorber and condenser. As long as the main heat exchange flow path still needs to pass through these two components in series, the technical bottleneck of high system resistance will always exist under operating conditions requiring large temperature differences and high flow rates, restricting the efficient and flexible application of the unit in a wider range of scenarios. Summary of the Invention

[0007] The purpose of this invention is to provide a large temperature difference absorption heat exchanger unit for multi-zone heating. It aims to efficiently serve multiple independent heating zones within a single unit through an innovative parallel flow path design of the absorber and condenser, thereby achieving a significant reduction in system operating resistance, precise matching of heat loads in each zone, and a synergistic improvement in overall unit energy efficiency and operational stability.

[0008] To address the aforementioned problems, a first aspect of the present invention provides a large temperature difference absorption heat exchanger unit for multi-zone heating, the unit comprising: a generator (1), an evaporator (2), an absorber (3), a condenser (4), and at least one water-to-water heat exchanger (5), and a piping system connecting the aforementioned components; the piping system comprising a primary network and a secondary network; the primary network is configured to flow through the high-temperature side of the generator (1) and / or the at least one water-to-water heat exchanger (5), and / or the evaporator (2); the secondary network is configured to serve at least two independent heating zones, wherein the absorber (3) and the condenser (4) are respectively configured to bear the heating load of different heating zones.

[0009] This invention, through an innovative parallel-split flow path design, decouples the absorber and condenser, which operate in series in traditional absorption heat pumps, transforming them into two independent heat sources capable of directly serving different heating zones. Simultaneously, in conjunction with at least one water-to-water heat exchanger for synergistic and peak-shaving operations, a novel system can be constructed under the drive of the primary network, enabling a single unit to provide independent, precise, and low-resistance heating to multiple zones. This fundamentally solves the technical problems of high resistance and difficulty in accurately matching loads in traditional series flow paths, significantly improving the system's energy efficiency, flexibility, and operational stability.

[0010] Furthermore, the secondary network pipeline serves two heating zones, and the number of water-to-water heat exchangers (5) is one. The secondary network return water of the first heating zone is divided into two parallel paths. One path flows through the absorber (3), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5). After merging, they supply heat to the first heating zone. The secondary network return water of the second heating zone flows separately through the condenser (4). After being heated, it supplies heat to the second heating zone.

[0011] Furthermore, the secondary network pipeline serves two heating zones, and the number of water-to-water heat exchangers (5) is one. Specifically, the return water from the secondary network of the first heating zone flows separately through the absorber (3) and is heated to supply heat to the first heating zone. The return water from the secondary network of the second heating zone is divided into two parallel paths, one of which flows through the condenser (4) and the other flows through the low-temperature side of the water-to-water heat exchanger (5). After merging, they supply heat to the second heating zone.

[0012] Furthermore, the secondary network pipeline serves two heating zones, and there are two water-to-water heat exchangers (5), namely, the first heating zone water-to-water heat exchanger (5-1) and the second heating zone water-to-water heat exchanger (5-2). In the primary network pipeline, the working fluid flows out of the generator (1) and is diverted to the high-temperature side of the first zone water-to-water heat exchanger (5-1) and the second zone water-to-water heat exchanger (5-2), respectively. The water from the secondary network of the first heating zone is divided into two parallel paths. One path flows through the absorber (3), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5-1) of the first zone. After they merge, the water supplies heat to the first heating zone. The water from the secondary network of the second heating zone is divided into two parallel paths. One path flows through the condenser (4), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5-2) of the second zone. After they merge, the water supplies heat to the second heating zone.

[0013] Furthermore, after flowing through the generator (1), the primary network pipeline is connected to the first zone water-to-water heat exchanger (5-1) and the second zone water-to-water heat exchanger (5-2) through a three-way valve (8). The three-way valve (8) is used to regulate the flow distribution of the primary network working fluid entering the two water-to-water heat exchangers (5).

[0014] Furthermore, the secondary network pipeline serves three independent heating zones, and the number of the water-to-water heat exchanger (5) is one, wherein: the secondary network return water of the first heating zone flows separately through the absorber (3), and after being heated, it supplies heat to the first heating zone; the secondary network return water of the second heating zone flows separately through the condenser (4), and after being heated, it supplies heat to the second heating zone; the secondary network return water of the third heating zone flows separately through the low-temperature side of the water-to-water heat exchanger (5), and after being heated, it supplies heat to the third heating zone.

[0015] Furthermore, regulating valves (6) are provided on the inlet and / or outlet pipes of the secondary network pipes of the absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5) to regulate the flow rate of the fluid flowing through the corresponding equipment, balance the resistance of each branch, or realize the on-demand distribution of the heating load.

[0016] Furthermore, a bypass line is connected across the secondary network consisting of the absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5), and a bypass valve (7) is installed on the bypass line to allow fluid to bypass the corresponding absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5).

[0017] Furthermore, the at least one water-to-water heat exchanger (5) is a plate heat exchanger; and on the secondary network pipeline side, the water-to-water heat exchanger (5) is connected in parallel with the absorber (3) or the condenser (4) or the water-to-water heat exchanger (5) works independently to reduce the overall flow resistance of the secondary network pipeline system to which it is connected.

[0018] The above-described technical solution of the present invention has the following beneficial technical effects: 1. Compact structure and space-saving: By decoupling the absorber and condenser and having them independently undertake the core heating tasks of different heating zones, the system architecture is simplified, the complex series pipeline layout is reduced, and the overall layout of the unit is more compact, effectively reducing the equipment footprint and making it more suitable for application scenarios where the space of the heating station is limited.

[0019] 2. Significantly Reduced System Operating Resistance: Since the secondary return water from each heating zone can flow independently and in parallel through the corresponding main heat exchange equipment (absorber or condenser), it breaks the traditional model where secondary water must flow through multiple devices in series. This parallel flow design can significantly reduce the overall flow resistance of the secondary piping system when the secondary network circulation flow is large, reducing pump energy consumption and broadening the unit's adaptability to high-flow conditions.

[0020] 3. Improved operational efficiency and thermal stability: This design allows for precise adjustment and allocation of the working fluid flow into each parallel branch (absorber, condenser, water-to-water heat exchanger) according to the actual load demand of each heating zone, enabling dynamic matching of heat exchange capacity and heat load. This fundamentally avoids the phenomenon of insufficient or excessive heat exchange in some areas caused by rigid flow distribution in traditional series water circuits, thereby significantly improving the overall heating efficiency and operational thermal stability of the unit. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the structure of an absorption chiller with a large temperature difference and two-zone heating in the prior art; Figure 2 This is a schematic diagram of another type of absorption chiller with large temperature difference for two-zone heating in the existing technology; Figure 3 This is a schematic diagram of the structure of the first type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention. Figure 4 This is a schematic diagram of the structure of the second type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention; Figure 5 A schematic diagram of the structure of the third type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention. Figure 6 A schematic diagram of a large temperature difference absorption heat exchanger unit for three-zone heating in an embodiment of the present invention.

[0022] Figure label: 1: Generator; 2: Evaporator; 3: Absorber; 4: Condenser; 5: Water-to-water heat exchanger; 5-1: Water-to-water heat exchanger for the first heating zone; 5-2: Water-to-water heat exchanger for the second heating zone; 6: Regulating valve; 7: Bypass valve; 8: Three-way valve. Detailed Implementation

[0023] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments and the accompanying drawings. It should be understood that these descriptions are merely exemplary and not intended to limit the scope of the invention. Furthermore, descriptions of well-known structures and techniques are omitted in the following description to avoid unnecessarily obscuring the concept of the invention.

[0024] The following is combined Figures 3 to 6 The present invention describes the large temperature difference absorption heat exchanger unit for multi-zone heating provided by the present invention.

[0025] Figure 3 This is a schematic diagram of the structure of the first type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention.

[0026] like Figure 3As shown, in some embodiments, the large temperature difference absorption heat exchanger unit for heating two independent zones provided by the present invention comprises an absorption heat pump unit, a water-to-water heat exchanger (5), several regulating valves and bypass valves, and a connecting pipeline system. The absorption heat pump unit includes four core components: a generator 1, an evaporator 2, an absorber 3, and a condenser 4. During operation, the high-temperature primary network working fluid (such as hot water) first enters the generator 1 to provide the driving heat source, then flows sequentially through the high-temperature side of the water-to-water heat exchanger 5 and the evaporator 2, achieving cascaded energy release and deep utilization, and finally flows out from the return port of the primary network pipeline at the evaporator 2. The key innovation of this embodiment lies in the parallel-diverted flow path design of the secondary network pipeline: the return water of the first heating zone is divided into two paths, one flowing through the absorber 3 to absorb heat, and the other flowing through the water-to-water heat exchanger 5 to recover waste heat at the low temperature side. Then, the two return water paths are heated and merged into one to supply heat to the first heating zone. At the same time, the return water of the second heating zone flows entirely through the condenser 4 to absorb condensation heat, and after being heated, it independently supplies heat to the second heating zone. Through this design, the absorber and condenser are decoupled from the traditional series mode, becoming independent heat sources serving different zones. This not only significantly reduces the system flow resistance but also achieves precise directional heat delivery according to the load demand of each zone, thereby effectively improving the overall energy efficiency, operational stability, and adaptability of the unit while maintaining a compact structure.

[0027] In some embodiments, furthermore, for the purpose of facilitating precise control and system optimization, regulating valves 6 are installed on the inlet and outlet pipes of the secondary network of the absorber 3, condenser 4, and water-to-water heat exchanger 5. By operating these regulating valves 6, the flow rate of the fluid flowing through each heat exchange device can be flexibly controlled, thereby achieving precise matching and dynamic adjustment of the heat load of the two heating zones.

[0028] In some embodiments, to further improve system reliability and adaptability to operating conditions, a bypass pipeline is connected across the secondary network pipeline consisting of absorber 3, condenser 4 and water-to-water heat exchanger 5. A bypass valve 7 is installed on the bypass pipeline. When the flow required by a certain heating zone is extremely large, or when absorber 3 / condenser 4 needs to be isolated for maintenance due to a fault, the corresponding bypass valve 7 can be opened to allow some or all of the fluid to bypass the equipment, thereby effectively reducing the system flow resistance on the secondary side of the zone, maintaining system pressure balance, and ensuring the continuity of heating service.

[0029] Figure 4 This is a schematic diagram of the structure of the second type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention.

[0030] like Figure 4As shown, in some embodiments, the large temperature difference absorption heat exchanger unit for heating two independent zones provided by the present invention includes an absorption heat pump unit, a water-to-water heat exchanger 5, and a matching valve and piping system. The absorption heat pump unit consists of a generator 1, an evaporator 2, an absorber 3, and a condenser 4. During operation, the high-temperature primary network working fluid (e.g., hot water) flows sequentially through the generator 1, the high-temperature side of the water-to-water heat exchanger 5, and the evaporator 2, achieving a stepped release and efficient utilization of heat energy, and finally flows out from the return port of the primary network pipeline at the evaporator 2. The core innovation of this embodiment lies in the parallel-diverted flow path design of the secondary network pipeline: for the first heating zone, all return water from its secondary network pipeline flows through absorber 3, which independently bears the entire basic heating load of the zone; while for the second heating zone, the return water from its secondary network pipeline is divided into two parallel paths: one flows through condenser 4 to obtain condensation heat, and the other flows through the low-temperature side of water-to-water heat exchanger 5 to recover waste heat. Then, the two return water paths are heated and merged into one path to jointly supply heat to users in the second heating zone. This design decouples the absorber and condenser again, allowing them to serve as independent heat sources for different zones. This not only effectively reduces the overall flow resistance of the system, but also demonstrates the significant advantages of this invention in adapting to different zone load characteristics and optimizing precise heat distribution through the flexible combination of "independent heating by the absorber" and "parallel heating by the condenser and water-to-water heat exchanger." This comprehensively improves the unit's operating efficiency, stability, and adaptability to operating conditions.

[0031] In some embodiments, to further improve the control accuracy, operational reliability, and adaptability of the unit, the unit integrates two types of control valves, namely regulating valves 6 and bypass valves 7, on the secondary network pipelines of the absorber 3, condenser 4, and water-to-water heat exchanger 5. Specifically, regulating valves 6 are installed on the inlet and outlet pipelines of the secondary network pipelines of the above-mentioned heat exchange equipment to regulate the flow rate of fluid flowing through each branch in real time, thereby achieving precise matching and dynamic distribution of heat load for different heating zones; at the same time, bypass valves 7 are installed across the secondary side pipelines of the absorber 3 and condenser 4 to guide fluid bypass when the flow rate is too high or equipment failure occurs, so as to maintain system pressure balance, avoid equipment overload, and ensure heating continuity. By synergistically using the above two types of valves, the unit of the present invention can not only achieve fine and flexible adjustment of heat load, but also effectively cope with abnormal operation and extreme conditions, thereby significantly improving the overall control capability, operational stability, safety reliability, and long-term adaptability of the system.

[0032] Figure 5 A schematic diagram of the structure of the third type of large temperature difference absorption heat exchanger unit for two-zone heating in this embodiment of the invention.

[0033] like Figure 5As shown, in some embodiments, the large temperature difference absorption heat exchanger unit for heating two independent zones provided by the present invention includes an absorption heat pump unit consisting of a generator 1, an evaporator 2, an absorber 3 and a condenser 4, two independent water-to-water heat exchangers, namely the first zone water-to-water heat exchanger 5-1 and the second zone water-to-water heat exchanger 5-2, necessary valves and connecting pipeline system, wherein the necessary valves are a regulating valve 6, a bypass valve 7 and a three-way valve 8. During operation, the high-temperature primary network working fluid (such as hot water) first enters the generator 1 as a driving heat source. After flowing out, it is divided into two paths by the three-way valve 8, which enter the high-temperature side of the first zone water-to-water heat exchanger 5-1 and the second zone water-to-water heat exchanger 5-2 respectively to continue releasing heat. Then the two paths merge and finally enter the evaporator 2 to complete deep cooling, thereby realizing the efficient cascade utilization of primary network energy. The three-way valve (8) can adjust and distribute the flow rate of the primary network working fluid (such as hot water) entering the first zone water-to-water heat exchanger 5-1 and the second zone water-to-water heat exchanger 5-2. The core innovation of this embodiment lies in the more symmetrical and independent parallel-diverted flow path design of the secondary network pipeline: For the first heating zone, the return water of its secondary network pipeline is divided into two parallel paths. One path flows through the absorber 3 to acquire absorbed heat, and the other path flows through the low-temperature side of the first zone's water-to-water heat exchanger 5-1 to recover waste heat. After the two paths are heated, they are combined into one path to supply heat to the first heating zone. For the second heating zone, the return water of its secondary network pipeline is also divided into two parallel paths. One path flows through the condenser 4 to acquire condensed heat, and the other path flows through the low-temperature side of the second zone's water-to-water heat exchanger 5-2 to recover waste heat. After the two paths are heated, they are combined into one path to supply heat to the second heating zone. By configuring a three-way valve 8, the flow distribution of the primary network working fluid between the water-to-water heat exchanger 5-1 and the water-to-water heat exchanger 5-2 can also be flexibly adjusted. This design not only continues the core concept of decoupling the absorber and condenser and allowing them to independently handle the heating loads of different zones, but also achieves complete independence and high symmetry of the secondary network heat exchange links by configuring a dedicated water-to-water heat exchanger 5 for each zone (i.e., water-to-water heat exchanger 5-1 for the first zone and water-to-water heat exchanger 5-2 for the second zone). This further enhances the system's ability to accurately and independently regulate the heat load of each zone, significantly improving operational efficiency and stability while also enhancing the unit's modularity and adaptability to various operating conditions. Furthermore, the unit integrates two types of control valves, regulating valve 6 and bypass valve 7, on the secondary network piping of the absorber 3, condenser 4, and water-to-water heat exchanger 5. Specifically, regulating valves 6 are installed on the inlet and outlet pipes of the secondary network of each heat exchanger to regulate the flow rate of fluid flowing through each branch in real time, thereby achieving precise matching and dynamic distribution of heat load for different heating zones; at the same time, bypass valves 7 are installed across the secondary network of absorber 3 and condenser 4 to guide fluid bypass when the flow rate is too high or the equipment fails, so as to maintain system pressure balance, avoid equipment overload and ensure heating continuity.

[0034] Figure 6 A schematic diagram of a large temperature difference absorption heat exchanger unit for three-zone heating in an embodiment of the present invention.

[0035] like Figure 6 As shown, in some embodiments, the large temperature difference absorption heat exchanger unit for heating three independent zones provided by the present invention includes an absorption heat pump unit consisting of a generator 1, an evaporator 2, an absorber 3, and a condenser 4, a water-to-water heat exchanger 5, and a matching valve and piping system, wherein the water-to-water heat exchanger 5 is a plate heat exchanger. During operation, the high-temperature primary network working fluid (such as hot water) first enters the generator 1 as a driving heat source, then flows through the high-temperature side of the water-to-water heat exchanger 5 to release medium-temperature heat, and finally enters the evaporator 2 to complete deep cooling, thereby realizing the cascade utilization of primary network energy. The core innovation of this embodiment lies in its more extended independent diversion flow path design for the secondary network pipeline, which serves three heating zones: the return water of the secondary network pipeline of the first heating zone flows entirely through the absorber 3, using the heat absorbed from the absorber 3 to independently heat the first heating zone; the return water of the secondary network pipeline of the second heating zone flows entirely through the condenser 4, using the condensation heat obtained from the condenser 4 to independently heat the second heating zone; the return water of the secondary network pipeline of the third heating zone flows entirely through the low-temperature side of the water-to-water heat exchanger 5, at which time the water-to-water heat exchanger 5 operates independently on the secondary network pipeline side, independently heating the third heating zone by recovering the waste heat from the primary network. This design completely decouples the absorber, condenser, and water-to-water heat exchanger, making them three independent heat sources, each handling the entire heating load of its respective zone. This not only completely avoids any form of series flow path and the high resistance it brings, but also achieves complete independence and precise heat supply to the three zones. This greatly enhances the system's modularity, expansion flexibility, and excellent adaptability to complex multi-zone and differentiated load scenarios, thus achieving comprehensive optimization of system energy efficiency, operational stability, and configuration flexibility on a larger scale. Furthermore, the unit integrates two types of control valves, regulating valve 6 and bypass valve 7, on the secondary network piping of absorber 3, condenser 4, and water-to-water heat exchanger 5. Specifically, regulating valves 6 are installed on the inlet and outlet pipes of the secondary network side of each heat exchanger to regulate the flow rate of fluid flowing through each branch in real time, thereby achieving precise matching and dynamic distribution of heat load for different heating zones; at the same time, bypass valves 7 are installed across the secondary network side pipes of absorber 3, condenser 4 and water-to-water heat exchanger 5 to guide fluid bypass when the flow rate is too high or the equipment fails, so as to maintain system pressure balance, avoid equipment overload and ensure heating continuity.

[0036] It should be understood that the term "and / or" in this article is merely a description of the relationship between related objects. For example, A and / or B indicates that there can be three relationships: A alone, A and B simultaneously, and B alone. Another example is A and / or B and / or C, which indicates that there can be eight relationships: A alone, B alone, C alone, A and B simultaneously, A and C simultaneously, B and C simultaneously, A, B, and C simultaneously, and A, B, and C simultaneously not existing. Furthermore, the character " / " in this article indicates that the preceding and following related objects have an "or" relationship.

[0037] In the embodiments of this application, "multiple" refers to two or more items, and "more than" refers to two or more items.

[0038] It should be understood that the specific embodiments described above are merely illustrative or explanatory of the principles of the invention and do not constitute a limitation thereof. Therefore, any modifications, equivalent substitutions, improvements, etc., made without departing from the spirit and scope of the invention should be included within the protection scope of the invention. Furthermore, the appended claims are intended to cover all variations and modifications falling within the scope and boundaries of the appended claims, or equivalent forms of such scope and boundaries.

Claims

1. A large temperature difference absorption heat exchanger unit for multi-zone heating, characterized in that, include: The generator (1), evaporator (2), absorber (3), condenser (4) and at least one water-to-water heat exchanger (5), and the piping system connecting the above components; The pipeline system includes a primary network pipeline and a secondary network pipeline; The primary network is configured to flow through the high-temperature side of the generator (1) and / or the at least one water-to-water heat exchanger (5) and / or the evaporator (2); The secondary network is configured to serve at least two independent heating zones, wherein the absorber (3) and the condenser (4) are configured to bear the heating load of different heating zones respectively.

2. The unit according to claim 1, wherein, The secondary network serves two heating zones, and the number of water-to-water heat exchangers (5) is one, wherein: The secondary network return water of the first heating zone is divided into two parallel paths. One path flows through the absorber (3), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5). After they merge, they supply heat to the first heating zone. The secondary return water of the second heating zone flows separately through the condenser (4), and after being heated, it supplies heat to the second heating zone.

3. The unit according to claim 1, wherein, The secondary network serves two heating zones, and the number of water-to-water heat exchangers (5) is one, wherein: The secondary network return water of the first heating zone flows separately through the absorber (3), and after being heated, it supplies heat to the first heating zone; The secondary return water of the second heating zone is divided into two parallel paths. One path flows through the condenser (4), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5). After they merge, they supply heat to the second heating zone.

4. The unit according to claim 1, wherein, The secondary network serves two heating zones, and there are two water-to-water heat exchangers (5), namely, a water-to-water heat exchanger (5-1) for the first heating zone and a water-to-water heat exchanger (5-2) for the second heating zone, wherein: In the primary network pipeline, the primary network working fluid flows out of the generator (1) and is split into the high-temperature side of the first zone water-to-water heat exchanger (5-1) and the second zone water-to-water heat exchanger (5-2), respectively, and then merges and enters the evaporator (2); The secondary network return water of the first heating zone is divided into two parallel paths. One path flows through the absorber (3), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5-1) of the first zone. After they merge, they supply heat to the first heating zone. The secondary network return water of the second heating zone is divided into two parallel paths. One path flows through the condenser (4), and the other path flows through the low-temperature side of the water-to-water heat exchanger (5-2) of the second zone. After they merge, they supply heat to the second heating zone.

5. The unit according to claim 4, wherein, After passing through the generator (1), the primary network pipeline is connected to the first zone water-to-water heat exchanger (5-1) and the second zone water-to-water heat exchanger (5-2) through a three-way valve (8). The three-way valve (8) is used to regulate the flow distribution of the primary network working fluid entering the two water-to-water heat exchangers (5).

6. The unit according to claim 1, wherein, The secondary network serves three independent heating zones, and the number of water-to-water heat exchangers (5) is one, wherein: The secondary network return water of the first heating zone flows separately through the absorber (3), and after being heated, it supplies heat to the first heating zone; The secondary network return water of the second heating zone flows separately through the condenser (4), and after being heated, it supplies heat to the second heating zone; The secondary return water of the third heating zone flows separately through the low-temperature side of the water-to-water heat exchanger (5) and is heated to supply heat to the third heating zone.

7. The unit according to any one of claims 1 to 6, wherein, A regulating valve (6) is provided on the inlet and / or outlet pipes of the secondary network of the absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5) to regulate the flow rate of the fluid flowing through the corresponding equipment, balance the resistance of each branch, or realize the on-demand distribution of the heating load.

8. The unit according to any one of claims 1 to 7, wherein, A bypass line is connected across the secondary network consisting of the absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5), and a bypass valve (7) is installed on the bypass line to allow fluid to bypass the corresponding absorber (3), and / or the condenser (4), and / or the water-to-water heat exchanger (5).

9. The unit according to any one of claims 1 to 8, wherein, The at least one water-to-water heat exchanger (5) is a plate heat exchanger; and on the secondary network pipeline side, the water-to-water heat exchanger (5) is connected in parallel with the absorber (3) or the condenser (4) or the water-to-water heat exchanger (5) works independently to reduce the overall flow resistance of the secondary network pipeline system to which it is connected.

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